EP2445377B1 - Gekühltes gehäuse - Google Patents

Gekühltes gehäuse Download PDF

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Publication number
EP2445377B1
EP2445377B1 EP10801028.1A EP10801028A EP2445377B1 EP 2445377 B1 EP2445377 B1 EP 2445377B1 EP 10801028 A EP10801028 A EP 10801028A EP 2445377 B1 EP2445377 B1 EP 2445377B1
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EP
European Patent Office
Prior art keywords
heat exchanger
refrigerant
air
flowpath
bars
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Active
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EP10801028.1A
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English (en)
French (fr)
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EP2445377A2 (de
Inventor
Markus Schuster
Thomas Krieger
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Carrier Corp
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Carrier Corp
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Publication of EP2445377A2 publication Critical patent/EP2445377A2/de
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Publication of EP2445377B1 publication Critical patent/EP2445377B1/de
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Classifications

    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47F—SPECIAL FURNITURE, FITTINGS, OR ACCESSORIES FOR SHOPS, STOREHOUSES, BARS, RESTAURANTS OR THE LIKE; PAYING COUNTERS
    • A47F3/00—Show cases or show cabinets
    • A47F3/04—Show cases or show cabinets air-conditioned, refrigerated
    • A47F3/0439—Cases or cabinets of the open type
    • A47F3/0443—Cases or cabinets of the open type with forced air circulation
    • A47F3/0447—Cases or cabinets of the open type with forced air circulation with air curtains
    • 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
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • 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
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/02—Safety or protection arrangements; Arrangements for preventing malfunction in the form of screens or covers

Definitions

  • the invention relates to a refrigerated case comprising a plate fin heat exchanger and a method for using said refrigerated case.
  • a number of refrigerated case configurations have the compressor and heat rejection heat exchanger in the base of the case below the refrigerated compartment (e.g., an open-front case, a door- front case, an open-top case, and the like).
  • a fan drives an airflow along a flowpath through the heat rejection heat exchanger.
  • the heat rejection heat exchanger will be referred to as a "condenser" which is intended to comprehend both true condensers and gas coolers.
  • the fan drives the airflow along the flowpath.
  • the airflow across the condenser is front-to-back with relatively cool room air entering a grille at the front of the base and passing essentially straight through and exiting the rear of the base.
  • the proximity of the base to the floor causes this airflow to be particularly dirty (e.g., dusty).
  • the decrease can include a combination of insulating the condenser from the airflow and blocking the airflow.
  • This contamination or fouling occurs not merely on the tube sections of the condenser but also, and especially, on fins.
  • An exemplary fin heat exchanger is a round tube plate fin (RTPF) heat exchanger wherein there is typically a lateral array of plates extending vertically and front-to-back. Each of the tube sections extends through and is in thermal contact with the plates.
  • RTPF round tube plate fin
  • the fan may be reversed to reverse the airflow to backflush the condenser. This may, for example, be done during the defrost cycle.
  • backflushing is not fully effective and, from time to time, there must be a manual cleaning (e.g., vacuuming/brushing).
  • JP 8-189752 and FR 2724873 disclose plate fin heat exchangers of the type described in the preamble of claim 1.
  • US 2902264 A relates to a radiator core to be installed in tractor type vehicles and GB 590806 A relates to heat exchanging devices employed with liquid heaters.
  • JPS6032682U shows a further example of a heat exchanger and JP2000123238A discloses a refrigerated case according to the preamble of claim 1.
  • the invention provides a refrigerated case comprising a plate fin heat exchanger comprising: a plurality of tube sections extending across an air flowpath, including a first group of sections forming a leading group of tube sections; and means for shielding portions of the fins ahead of the leading group against debris accumulation; characterised in that the means comprises a plurality of bars immediately in front of and respectively associated with individual ones of the tube sections of the leading group, at the same height thereas, and each bar extending no more than 15% of the tube diameter above or below the associated tube sections, when the heat exchanger is in use with vertically arranged tube sections, and not out of phase therewith; and wherein the bars have trailing ends, and wherein the trailing ends have a spacing ahead of the associated ones of the tube sections.
  • the bars have a v-shaped cross section and have trailing ends having a spacing ahead of the fins that is up to 30mm.
  • a method for using the refrigerated case is also claimed.
  • FIGS. 1 and 2 show a refrigerated case 20 having a body 22 at least partially enclosing a refrigerated compartment (interior) 24.
  • the exemplary case/body is an open- front case having a left wall 26 at a left side 28, a right wall 30 at a right side 32, a top panel (wall) 34 at a top 36, a base 38 at a bottom 40, and a rear (back) panel 42 at a back (rear end) 44.
  • An opening 46 extends at least partially along a front of 48 of the case.
  • a vertical array of shelves 50 is positioned within the compartment 24.
  • the exemplary case 20 includes a refrigeration system 60 ( FIG. 3 ).
  • the refrigeration system comprises a compressor 62 along a refrigerant flowpath 64.
  • the compressor has an inlet (suction port) 66 and an outlet (discharge port) 68.
  • the refrigeration system includes a first refrigerant-air heat exchanger 70 and a second refrigerant-air heat exchanger 72.
  • An expansion device 74 may be along the refrigerant fiowpath 64 between the heat exchangers 70 and 72 opposite the compressor.
  • Fans 80 and 82 may respectively drive airflows 84 and 86 across the heat exchangers 70 and 72.
  • refrigerant compressed by the compressor exits the outlet 68 and proceeds to the first heat exchanger 70 which acts as a condenser or gas cooler (heating the air flow 84 to reduce the temperature of refrigerant as it flows through the first heat exchanger 70).
  • Refrigerant proceeds downstream along the refrigerant fiowpath 64 to the expansion device 74 where it is expanded and its temperature further reduced.
  • the cold refrigerant enters the second heat exchanger 72 (which acts as an evaporator, absorbing heat from the airflow 86 and heating the refrigerant as it flows through the second heat exchanger 72).
  • Refrigerant discharged from the second heat exchanger 72 returns to the compressor inlet 66.
  • Other details, including accumulators, valves, and sensors may be present but are not shown for ease of illustration.
  • FIG. 2 shows further details of a base air fiowpath 98 and a recirculating cabinet/case air fiowpath 100 and exemplary positioning of components of the refrigeration system 60.
  • the compressor 62 and first heat exchanger 70 are positioned within a compartment of the base 38.
  • a rear duct is located between the rear wall 42 and the compartment 24.
  • the rear duct extends from a base duct at a lower end of the compartment which has an inlet 108 at a lower end of the front opening.
  • the second heat exchanger 72 is positioned within the base outlet.
  • the rear duct feeds a top duct 110 which has an outlet 112.
  • the flow 86 produces a discharge flow 114 from the outlet which may initiate/form an air curtain along the opening 46.
  • Additional branching flows 115 may branch off the flow 86 and pass into the compartment 24. At least a portion of the flow 114 and any branching flows returns to the inlet 108 as an inlet flow 116.
  • the fan 82 is positioned near the front (upstream) end of base duct.
  • a defrost mode may be initiated.
  • Exemplary defrost may be via a heating element (e.g., an electric resistance element) and/or via directing hot refrigerant to the heat exchanger 72 (instead of cold refrigerant).
  • the defrost operation melts the frost which may flow downward as a flow (e.g., of droplets) and reach a drain.
  • An exemplary drain is formed proximate a lower end of the rear duct.
  • the drain may include a trap (e.g., a conventional J or S trap or a more complex trap such as that shown in JP2004353909 ).
  • the drain in turn, may discharge water as one or more flows into an evaporation vessel or a drainline.
  • FIGS. 4 and 5 show an exemplary heat rejection heat exchanger 70 (hereinafter generically "condenser” which includes both true condensers and gas coolers).
  • the exemplary condenser 70 is an RTPF condenser having a plurality of sections of tube (e.g., an array) spanning first and second endplates 150 and 152. At the endplates, various of the tube sections are coupled to each other (e.g., via bends or U-shaped connectors to create the refrigerant circuit/flowpath through the condenser).
  • the exemplary condenser has a plurality of rows of tube sections (an exemplary four rows shown extending from a leading group or row 154 (shown oriented horizontally and arrayed vertically) to a trailing row 156 with two intermediate rows 158 and 160).
  • the leading and trailing direction is defined relative to the cooling mode direction of the airflow 84 along the flowpath 98.
  • FIG. 6 also shows the array of individual fin plates 162 extending between the endplates 150 and 152.
  • the plates thus, have leading edges 164 and trailing edges 166.
  • the exemplary fan 80 is normally a pull-through fan drawing the airflow 84 across the tube array.
  • the condenser may be otherwise a conventional condenser.
  • the condenser may, however, have added to it a shield 170 which helps mitigate fouling problems.
  • Such a shield may also be used with other heat exchanger constructions such as finned-tube or other non-plate finned constructions.
  • the shield may alternatively be defined as part of the condenser or as a separate element.
  • the shield 170 serves as means for reducing fouling in the wind shadow areas of the leading row of tubes (relative to accumulation in the inter-tube spaces between such areas). This compensates for the relative inability of backflushing to access/clean the wind shadow areas.
  • the exemplary shield 170 does this by serving as a means for preferentially shielding the leading group of tube sections (and the wind shadow areas of the fins) in the cooling mode. Specifically, the airflow is directed away from the front of the tube sections and toward the inter-tube spaces. The direction is "preferential" in that it is towards certain areas (the "preferred" inter-tube areas) relative to the wind shadow areas. Thus, the leading tubes and their wind shadow areas are preferentially shielded.
  • FIG. 10 shows the shield 170 as having an array of bars 180 directly and immediately (no intervening structures) in front of and respectively associated with individual ones of the tube sections of the leading group 154.
  • the bars 180 tend to block contaminants from accumulating in the wind shadow areas 182 while relatively freely allowing contaminants/fouling 184 to reach the inter-tube areas 186 between the wind shadow areas 182.
  • FIG. 11 shows the backflushing ejecting the fouling.
  • the bars 180 are formed as V-sectioned members having a leading end 190 at the vertex of the V and a trailing end 192 formed by the opposite ends of the legs of the V.
  • the exemplary bar height H is close to the tube height (diameter D for a round tube).
  • the trailing ends 192 have a spacing S 1 ahead of the associated tubes and S 2 ahead of the fins.
  • S 2 is up to about 30mm (more narrowly, 2-10mm, or 3-6mm, or about 5mm). As discussed below, this dimension can technically become negative if the fins are recessed into the bars.
  • Exemplary H is 80-120% of D (e.g., about 1.0 x D).
  • Exemplary tube outer diameter OD is 7.2mm or 3/8 of an inch.
  • the bars are registered with the associated tube sections (i.e. at the same height and not out-of-phase). According to the present invention, the bars extend no more than 15% of D above or below the associated tubes, more narrowly, no more than 10% or 5% above or below.
  • Exemplary bar materials are plastic (such as polyethylene, polypropylene, acrylonitrile styrene acrylate (ASA), or ABS-PMMA) or metal (e.g., aluminum or lacquered steel). It is desirable that the surface of the bar material be relatively smooth so as to hinder dust accumulation on the bars.
  • the bars may be secured in any of several ways.
  • FIGS. 4 and 5 show the bars mounted to endplates which are secured as extensions of the existing condenser endplates (sideplates). However, in a production environment this might be made by merely using larger condenser endplates.
  • FIG. 12 shows the bars mounted on a structure which is secured to the bottom of the base compartment ahead of the condenser.
  • FIG. 3 shows the bars (or a frame structure holding the bars) registered to the condenser via brackets 200 to engage one or more of the leading tube sections.
  • FIG. 14 shows recesses 220 in the bars which accommodate the fins (and thus the negative value of S 2 previously mentioned).
  • the system may be implemented with conventional manufacturing techniques and materials (e.g., brazing or welding metal bars to associated endplates or gripping or gluing metal or plastic bars).
  • the bar material may be stock angle material (e.g., right angle).
  • Use parameters may be essentially unchanged.
  • the backflushing may still occur in the defrost mode (e.g., under fully automated or semi-automated control).
  • the manual cleaning may still be performed via vacuuming.
  • the bars may be made removable (e.g., as a unit) for access to the fins. However, it is likely that the bars will merely be left in place during normal vacuuming.
  • the fins, tubes, and/or bars may have protective coatings such as that shown in WO2009/039874 . Yet other variations are possible.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (9)

  1. Gekühltes Gehäuse (20), umfassend:
    einen Körper (22), der ein gekühltes Fach (24) aufweist;
    ein Kühlsystem, umfassend:
    einen Kühlmittelströmungsweg (64);
    einen Verdichter (62) entlang des Kühlmittelströmungsweges; und
    einen Rippenplatten-Wärmetauscher (70), umfassend:
    eine Vielzahl von Rohrteilen (154, 156, 158, 160), die sich über einen Luftströmungsweg (98) erstrecken, die eine erste Gruppe (154) von Teilen beinhaltet, die eine vordere Gruppe der Rohrteile bildet; und
    ein Mittel (170) zum Abschirmen von Abschnitten (182) der Rippen (162) vor der vorderen Gruppe gegenüber einer Ansammlung von Schmutzteilchen,
    wobei der Rippenplatten-Wärmetauscher ein erster Kühlmittel-Luft-Wärmetauscher (70) in einem Kühlbetriebsmodus ist und ein Wärmeabführ-Wärmetauscher ist, der sich entlang des Kühlmittelströmungsweges stromabwärts des Verdichters befindet;
    wobei das gekühlte Gehäuse ferner Folgendes umfasst:
    einen zweiten Rippenplatten-Wärmetauscher (72), der ein Wärmeaufnahme-Wärmetauscher stromaufwärts des Verdichters in dem Kühlmodus ist; und
    eine Expansionsvorrichtung (74) entlang des Kühlmittelströmungsweges, stromabwärts des ersten Kühlmittel-Luft-Wärmetauschers und stromaufwärts des zweiten Kühlmittel-Luft-Wärmetauschers in dem Kühlmodus,
    wobei:
    der Luftströmungsweg (98) über den ersten Kühlmittel-Luft-Wärmetauscher führt;
    ein Gebläse (80) entlang des Luftströmungsweges positioniert ist;
    die vordere Gruppe der ersten Vielzahl von Rohrteilen (154, 156, 158, 160) eine vordere Gruppe in dem Kühlmodus ist;
    das Gehäuse das Mittel (170) zum Abschirmen der vorderen Gruppe gegenüber einer Ansammlung von Schmutzteilchen umfasst; dadurch gekennzeichnet, dass das Mittel eine Vielzahl von Stangen (180) direkt vor einzelnen der Rohrteile der vorderen Gruppe umfasst, die diesen jeweils zugeordnet sind und sich auf derselben Höhe wie diese befinden, und sich jede Stange um nicht mehr als 15 % von dem Rohrdurchmesser über oder unter die zugeordneten Rohrteile erstreckt, wobei der Wärmetauscher mit vertikal angeordneten Rohrteilen in Gebrauch ist und nicht phasenverschoben zu diesen ist; und
    wobei die Stangen (180) hintere Enden (192) aufweisen und wobei die hinteren Enden einen positiven Abstand (S1) vor den zugeordneten der Rohrteile aufweisen; und
    die Stangen (180) einen v-förmigen Querschnitt aufweisen und wobei die Stangen (180) hintere Enden (192) aufweisen, die einen Abstand (S2) vor den Rippen aufweisen, der bis zu 30 mm beträgt.
  2. Gekühltes Gehäuse nach Anspruch 1, wobei der Rippenplatten-Wärmetauscher ein Rippenplatten-Wärmetauscher mit runden Rohren ist.
  3. Gekühltes Gehäuse nach Anspruch 1, wobei:
    sich ein Rückführungsluftströmungsweg (100) von einem Einlass (108), der positioniert ist, um Luft aus dem Fach aufzunehmen, zu einem Auslass (112) erstreckt, der positioniert ist, um Luft in das Fach abzugeben;
    ein zweites Gebläse (82) einen Rückführungsluftstrom (86) entlang des Rückführungsluftströmungswegs lenkt; und
    sich der zweite Kühlmittel-Luft-Wärmetauscher (72) in dem Rückführungsluftströmungsweg befindet.
  4. Gekühltes Gehäuse nach Anspruch 1, wobei:
    keine ähnlichen Stangen benachbart zu einer hinteren Gruppe der Teile vorhanden sind.
  5. Gekühltes Gehäuse nach Anspruch 1, wobei:
    die Stangen einen Querschnitt aufweisen, der in dem Kühlmodus stromabwärts über mehr als die Hälfte einer Stangenspanne in Strömungsrichtung divergiert.
  6. Gekühltes Gehäuse nach Anspruch 1, wobei:
    die Stangen eine Höhe von 90-100 % einer Höhe der zugeordneten Teile aufweisen.
  7. Gekühltes Gehäuse nach Anspruch 1, wobei:
    die Stangen um nicht mehr als 30 mm vor den zugeordneten Teilen beabstandet sind.
  8. Gekühltes Gehäuse nach Anspruch 1, wobei:
    sich der Verdichter und der erste Kühlmittel-Luft-Wärmetauscher in einer Basis des Gehäuses und unter dem Fach befinden; und
    der Luftstrom in dem Kühlmodus von vorne nach hinten durch die Basis verläuft.
  9. Verfahren zum Verwenden des Gehäuses nach Anspruch 1, wobei das Verfahren Folgendes umfasst:
    Betreiben in einem Kühlmodus, wobei:
    ein Kühlmittel dem zweiten Kühlmittel-Luft-Wärmetauscher entlang des Kühlmittelströmungsweges zugeführt wird, um Luft entlang eines Rückführungsluftströmungsweges zu kühlen, wodurch Kondensat aus dem Rückführungsluftströmungsweg dazu veranlasst wird, als Eis an dem zweiten Kühlmittel-Luft-Wärmetauscher anzufrieren; und
    das Gebläse den Luftstrom in einer ersten Richtung über den ersten Kühlmittel-Luft-Wärmetauscher lenkt, sodass sich Schmutzteilchen an dem ersten Wärmetauscher ansammeln; und
    Betreiben in einem Abtaumodus, wobei:
    das Eis geschmolzen wird, wodurch das geschmolzene Eis dazu veranlasst wird, zu dem Ablauf zu strömen und aus dem Ablauf als das Wasser abgegeben zu werden; und
    das Gebläse den Luftstrom gegenüber der ersten Richtung lenkt, um die Schmutzteile auszustoßen.
EP10801028.1A 2010-02-26 2010-12-13 Gekühltes gehäuse Active EP2445377B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US30857110P 2010-02-26 2010-02-26
PCT/US2010/060028 WO2011106063A2 (en) 2010-02-26 2010-12-13 Refrigerated case

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EP2445377A2 EP2445377A2 (de) 2012-05-02
EP2445377B1 true EP2445377B1 (de) 2019-11-13

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EP (1) EP2445377B1 (de)
CN (1) CN102770049B (de)
WO (1) WO2011106063A2 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4227608A4 (de) * 2020-10-12 2024-06-05 Gree Electric Appliances Inc Zhuhai Verdampfungsvorrichtung und steuerungsverfahren dafür sowie gekühlter schaukasten

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GB590806A (en) * 1945-02-19 1947-07-29 Leopold Friedman Improvements in and relating to heat exchangers
US2902264A (en) * 1957-10-24 1959-09-01 Allis Chalmers Mfg Co Radiator core for tractor vehicles
JPS5580693U (de) * 1978-11-30 1980-06-03
DE3110448C1 (de) * 1981-03-18 1983-06-01 Klöckner-Humboldt-Deutz AG, 5000 Köln Waermetauscher
JPS6032682U (ja) * 1983-08-03 1985-03-06 東洋ラジエーター グリッド付熱交換器
JPH0293299A (ja) * 1988-09-30 1990-04-04 Komatsu Ltd 風向き可変熱交換器
US20030141046A1 (en) * 2002-01-15 2003-07-31 Toru Ikeda Heat exchanger
JP2006349340A (ja) * 2006-08-09 2006-12-28 Matsushita Refrig Co Ltd 熱交換器とこの熱交換器を有する冷凍装置を備えた機器
EP2011976A1 (de) * 2006-04-25 2009-01-07 Calsonic Kansei Corporation Struktur eines schutzglieds für einen fahrzeugwärmetauscher

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US4449374A (en) * 1981-01-19 1984-05-22 Tyler Refrigeration Corporation Combination hot gas and air defrost refrigerated display case
JPH02115679A (ja) * 1988-10-20 1990-04-27 Sanyo Electric Co Ltd 低温ショーケース
FR2724873A1 (fr) 1994-09-23 1996-03-29 Socori Technologies Procede de realisation d'une unite de chauffage pour climatiseur de vehicules automobiles, moyens en vue de sa mise en oeuvre, unite de chauffage et climatiseur obtenus a l'aide de ce procede.
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WO2011106063A3 (en) 2011-12-22
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WO2011106063A2 (en) 2011-09-01
CN102770049B (zh) 2016-05-18

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