EP0537650A2 - Echangeur de chaleur avec un rendement amélioré et hygiénique - Google Patents

Echangeur de chaleur avec un rendement amélioré et hygiénique Download PDF

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Publication number
EP0537650A2
EP0537650A2 EP92117349A EP92117349A EP0537650A2 EP 0537650 A2 EP0537650 A2 EP 0537650A2 EP 92117349 A EP92117349 A EP 92117349A EP 92117349 A EP92117349 A EP 92117349A EP 0537650 A2 EP0537650 A2 EP 0537650A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
recesses
exchanger according
boards
plates
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
EP92117349A
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German (de)
English (en)
Other versions
EP0537650A3 (en
EP0537650B1 (fr
Inventor
Karl-Hermann Becker
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.)
Individual
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Individual
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Filing date
Publication date
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Publication of EP0537650A2 publication Critical patent/EP0537650A2/fr
Publication of EP0537650A3 publication Critical patent/EP0537650A3/de
Application granted granted Critical
Publication of EP0537650B1 publication Critical patent/EP0537650B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities

Definitions

  • the invention relates to a high-performance steel heat exchanger for spontaneous freezing, in particular of foodstuffs, with a number of tube coils, which are formed in an S-shaped manner within a common plane and are formed by tubes connected to one another by means of tube elbows, the core tubes of which are arranged in predetermined divisions Reach through lamellas, which are provided with holes provided in rows, the edge areas of which project laterally like a collar.
  • the fins assigned to the cooling coils are arranged on the inlet side in a relatively wide division and are only provided in narrower division in the sections following in the direction of passage of the air. This ensures that in the last section, by means of narrow division, considerable areas that promote heat transfer are to be accommodated, while on the inlet side, moisture is removed from the incoming air without the frost crystals that settle on the fins due to the water which has separated out prematurely removing the distance remaining between the fins are able to add and thus make an early defrost cycle necessary.
  • the invention is therefore based on the object of further developing the type of fins of heat exchangers made of steel in such a way that the number of required exchange zones which reduce the heat transfer surfaces is reduced to a minimum and at the same time the distances of fins exceeding the possible collar height are also safe be respected.
  • Fig. 1 is a schematic, broken and interrupted in the middle areas, a single coil 1 is shown. It is made of hairpin-shaped tubes, the straight legs of which are referred to as core tubes 2, the free ends of two core tubes being connected by welded-on tube bends 3, so that a continuous, meandering tube is formed, the core tubes of which take up the heat transfer-transmitting fins 4 capital. A section of a lamella 4 is enlarged, cut and shown broken off on both sides in Fig. 2. To reach through the core tubes, recesses 5 are provided, the edge regions of which are folded into a collar-like shape by punching, pressing and the like to form lugs 6, which are able to determine their mutual distance and thus their division when lamellae are strung together.
  • the slightly conical taper of the extension 6 towards its free end makes it easier, on the one hand, to push the lamella 5 onto the core tubes 2 with the slightly funnel-shaped opening 5 ahead.
  • this taper of the extension 6, with a corresponding press fit of its free end may also allow assembly at intervals which exceed the possible maximum length of the heel 6, once the positions of the slats have been reliably adhered to, without securing wooden strips or the like to secure the distance would be needed.
  • strip-shaped fins are usually used which each have only one row of recesses 5 and which, for example, extend over a coil of pipes. Since, when lining up fins 4 on core tubes 2, their lugs 6 determine the spacing of the fins and thus their pitch, these distances can only be maintained within wide tolerances, fins arranged one behind the other in the direction of air flow are usually not within a common plane , but they are more or less staggered behind each other. In this way, however, the free passage space for the air is divided and split, and narrow gaps are formed between the mutually facing ends in the air flow of successive slats, which on the one hand hold entrained dirt, e.g.
  • Unwanted zinc bridges give starting points and thus additionally narrow the gaps locally in such a way that water which sets in as ripening can prematurely block the passage channels.
  • strip-shaped fins In heat exchangers made of steel, strip-shaped fins have also been used, which have two rows of recesses and, in exceptional cases, also three rows of recesses, so that accordingly two or three coils are encompassed. However, this only results in a gradual enlargement of the areas causing the heat transfer due to the elimination of some of the exchange zones to be kept clear between groups of strip lamellae.
  • plate-like fins made of sheet steel which have at least as many rows 8 of recesses 5 as a section of the heat exchanger with the same fin division has coils, while within the rows 8 there are as many recesses 5, like the pipe coil in question has extensive core tubes.
  • the circuit board 7 of FIG. 3 is shown broken off and shows only six of the rows 8, while only seven recesses 5 are shown within a row.
  • a heat exchanger designed according to the invention is shown schematically in perspective in FIG. 4, but in order to facilitate the overview, circuit boards are only shown in regions.
  • the heat exchanger of the figure is made up of a number of serially arranged, three-pass coils 1, so that three connections 11 are connected to each of the collectors 9 and 10 effecting the supply and discharge of the refrigerant and the core pipes 2, which are only partially and symbolically represented, are connected Elbows 3, 12 and 13 are connected to each other, which bridge different widths.
  • the coils are held together by end plates 14 braced against them on both sides.
  • the fins of the heat exchanger are arranged over the entire length of the core tubes in a constant division, but, as already mentioned, only two groups of these fins are shown for reasons of simplification.
  • three sections 16, 17 and 18 follow one another, within which different divisions of the arrangement of the boards are used.
  • a division of 18 mm is provided in the exemplary embodiment over four pipe coils, in the following section 17 a division of 9 mm is provided over seven pipe coils, while in the last section 18 a division of over 12 pipes 7 mm is applied.
  • the gradual narrowing of the passage of air in the direction of the arrow takes into account a relatively strong water excretion on the first cooling, and that which has passed through on cooling further Air then falls off.
  • Sections 17 and 20 are provided alternately in section 17 and extend only over the entire section 17 and over both section 16 and section 17. It is thereby achieved that within the section 17 the pitch of 9 mm is determined by the collar-like projections 6 of the recesses 5 of the plates 19 and 20 receiving the core tubes 2, and since every second plate 20 additionally extends over the section 16, here twice the pitch. This separation distance of 18 mm could no longer be achieved by the collar-like projections 6, since these cannot be formed so cantilevered. If separate boards were to be provided, distance-keeping aids would also have to be used.
  • this is circumvented by the 9 mm lamella division being secured by the collar-like projections 6 of the alternately provided boards 19 and 20, the boards 20 additionally extending over the section 16 and therefore maintaining the double division here.
  • An additional stabilization is achieved by the slight press fit of the end regions of the conical projections 6.
  • the narrowest division and thus the essential heat transfer surfaces are provided in section 18.
  • the boards 21 arranged here in the exemplary embodiment have twelve rows 8 of recesses 5 for core tubes 2, and the collar-like projections 6 surrounding the recesses 5 extend over 7 mm and thus ensure the division of the slats which have been pushed on.
  • the heat exchanger is finished in a manner known per se: the second of the end plates 14 is pushed on and fastened, and the pipe bends 3, 12 and 13 are welded on to finish the three-pipe coils, that is to say they have three separate conduit paths.
  • the pipe coils, collectors and fins or blanks generally made of steel in heat exchangers of this size, but especially these hygienic requirements, are then protected against corrosion, for example by galvanizing, and at the same time also by a suitable galvanizing, for example hot-dip galvanizing further connection and definition of the individual components is achieved.
  • An unwanted zinc bridge formation is practically excluded or reduced to a minimum by the width of the only one gap 22.
  • FIG. 5 shows a heat exchanger in the representation corresponding to FIG. 4, in which gaps 22 in FIG. 4 could be completely dispensed with.
  • the boards 23 extend over the full depth of the heat exchanger, the boards 24 are made shorter, and the boards 25 have an even smaller depth.
  • the widest division of the boards 23 is achieved, while in the following areas boards 23 and 24 alternately result in half the division, and in the outlet-side section the boards 23, 24 and 25 have the narrowest division and offer the largest share of heat transfer surfaces.
  • FIG. 6 shows a heat exchanger of the same type for comparison, which in a manner known per se has a vertically running fin 26 for two levels of coils.
  • the lamellae are set to different pitches in individual rows or one behind the other and separated by gaps 27 to form a number of compensation zones. Since, in this example of a conventional construction, nine groups of fins are arranged one behind the other, there are eight gaps which are kept narrow to reduce the reduction in the size of heat-transfer surfaces.
  • FIG. 7 there is already the risk of zinc bridges 28 being formed during the galvanizing, and in operation there is a risk of foreign bodies being carried in the air to be cooled, which is further increased by zinc bridges that have already been formed becomes.
  • the heat exchangers designed according to the invention are characterized by extensive use of space as well as by favorable distribution of the approach of the water which is separated out on cooling, so that dead times given by thawing and cleaning the heat exchanger only occur after longer operating phases and thus the percentage useful life of the heat exchanger is increased.
  • the necessary cleaning processes can be carried out more easily and more completely than is the case with known heat exchangers by essentially smooth surfaces and avoidance of excess end faces as well as the mechanically stable and corrosion-resistant structure, so that the hygiene required for freezing or shock freezing of food is also improved .
  • the inventive design prevents the cleaning-resistant settling of organic residues and prevents the bacterial contamination that often occurs in such heat exchangers by removing nutrient media and improving cleaning options.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Nitrogen Condensed Heterocyclic Rings (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
  • Physical Or Chemical Processes And Apparatus (AREA)
  • Materials For Medical Uses (AREA)
EP92117349A 1991-10-12 1992-10-10 Echangeur de chaleur avec un rendement amélioré et hygiénique Expired - Lifetime EP0537650B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE9112704U 1991-10-12
DE9112704U DE9112704U1 (de) 1991-10-12 1991-10-12 Wärmetauscher hoher Leistung und Hygiene

Publications (3)

Publication Number Publication Date
EP0537650A2 true EP0537650A2 (fr) 1993-04-21
EP0537650A3 EP0537650A3 (en) 1993-09-08
EP0537650B1 EP0537650B1 (fr) 1997-12-17

Family

ID=6872183

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92117349A Expired - Lifetime EP0537650B1 (fr) 1991-10-12 1992-10-10 Echangeur de chaleur avec un rendement amélioré et hygiénique

Country Status (5)

Country Link
EP (1) EP0537650B1 (fr)
AT (1) ATE161323T1 (fr)
DE (2) DE9112704U1 (fr)
ES (1) ES2112287T3 (fr)
FI (1) FI102412B (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003048660A1 (fr) * 2001-12-04 2003-06-12 Multibrás S.A. Eletrodomésticos Evaporateur de systemes de refrigeration
DE102012202883A1 (de) 2012-02-24 2013-08-29 Bayerische Motoren Werke Aktiengesellschaft Wärmetauscher
CN111412691A (zh) * 2020-03-13 2020-07-14 珠海格力电器股份有限公司 一种换热器和空调器

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE9112704U1 (de) * 1991-10-12 1992-01-16 Becker, Karl-Hermann, 5241 Friedewald Wärmetauscher hoher Leistung und Hygiene

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR962473A (fr) * 1950-06-10
DE2154487A1 (de) * 1970-11-02 1972-05-04 Peerless Of America Wärmetauscher und Verfahren zur seiner Herstellung
JPS608696A (ja) * 1983-06-27 1985-01-17 Matsushita Refrig Co 熱交換器
DE9112704U1 (de) * 1991-10-12 1992-01-16 Becker, Karl-Hermann, 5241 Friedewald Wärmetauscher hoher Leistung und Hygiene

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE395685C (de) * 1922-08-06 1925-02-14 Hugo Junkers Dr Ing Waermeaustauschvorrichtung
GB663468A (en) * 1949-03-26 1951-12-19 Serck Radiators Ltd Improvements relating to heat interchange apparatus
GB783925A (en) * 1955-08-16 1957-10-02 Serck Radiators Ltd Tubular heat exchange apparatus
FR1180908A (fr) * 1957-08-07 1959-06-10 Ensembles pour la transmission de la chaleur
DE2239086C2 (de) * 1972-08-09 1982-01-28 Motan Gmbh, 7972 Isny Wärmetauscher, insbesondere für Durchlauferhitzer
FR2529316B1 (fr) * 1982-06-29 1987-07-03 Valeo Echangeur de chaleur, en particulier pour vehicule automobile, et son dispositif d'etancheite laterale

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR962473A (fr) * 1950-06-10
DE2154487A1 (de) * 1970-11-02 1972-05-04 Peerless Of America Wärmetauscher und Verfahren zur seiner Herstellung
JPS608696A (ja) * 1983-06-27 1985-01-17 Matsushita Refrig Co 熱交換器
DE9112704U1 (de) * 1991-10-12 1992-01-16 Becker, Karl-Hermann, 5241 Friedewald Wärmetauscher hoher Leistung und Hygiene

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 9, no. 124 (M-383)(1847) 29. Mai 1985 & JP-A-60 008 696 ( MATSUSHITA REIKI K.K. ) *

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003048660A1 (fr) * 2001-12-04 2003-06-12 Multibrás S.A. Eletrodomésticos Evaporateur de systemes de refrigeration
US7065982B2 (en) 2001-12-04 2006-06-27 Multibras S.A. Eletrodomesticos Evaporator for refrigeration systems
DE102012202883A1 (de) 2012-02-24 2013-08-29 Bayerische Motoren Werke Aktiengesellschaft Wärmetauscher
CN111412691A (zh) * 2020-03-13 2020-07-14 珠海格力电器股份有限公司 一种换热器和空调器
CN111412691B (zh) * 2020-03-13 2021-09-07 珠海格力电器股份有限公司 一种换热器和空调器

Also Published As

Publication number Publication date
DE9112704U1 (de) 1992-01-16
FI102412B1 (fi) 1998-11-30
FI924614A0 (fi) 1992-10-12
DE59209072D1 (de) 1998-01-29
EP0537650A3 (en) 1993-09-08
ES2112287T3 (es) 1998-04-01
FI102412B (fi) 1998-11-30
EP0537650B1 (fr) 1997-12-17
ATE161323T1 (de) 1998-01-15
FI924614A (fi) 1993-04-13

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