EP3869129A1 - Réfrigérateur pourvu d'évaporateur à lamelles - Google Patents

Réfrigérateur pourvu d'évaporateur à lamelles Download PDF

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Publication number
EP3869129A1
EP3869129A1 EP21152456.6A EP21152456A EP3869129A1 EP 3869129 A1 EP3869129 A1 EP 3869129A1 EP 21152456 A EP21152456 A EP 21152456A EP 3869129 A1 EP3869129 A1 EP 3869129A1
Authority
EP
European Patent Office
Prior art keywords
evaporator
lamellar
module
blocks
refrigerant line
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.)
Withdrawn
Application number
EP21152456.6A
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German (de)
English (en)
Inventor
Niels Liengaard
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.)
BSH Hausgeraete GmbH
Original Assignee
BSH Hausgeraete GmbH
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
Application filed by BSH Hausgeraete GmbH filed Critical BSH Hausgeraete GmbH
Publication of EP3869129A1 publication Critical patent/EP3869129A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
    • F25D17/06—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation
    • F25D17/062—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation in household refrigerators
    • 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
    • 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
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
    • 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • 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
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators

Definitions

  • the present invention relates to a refrigeration device, in particular a household refrigeration device, with an evaporator chamber and a first evaporator module arranged in the evaporator chamber.
  • a refrigeration device also referred to as a no-frost device
  • a storage chamber is cooled in that air is exchanged between the evaporator chamber and the storage chamber.
  • the evaporator chamber generally extends either between a rear wall of a body of the refrigeration device and a vertical partition wall to the storage chamber, and the lamellar evaporator therein is oriented on edge, or it extends between a ceiling of the body and a partition sloping in the depth direction of the body, and the lamellar evaporator is inclined parallel to the partition wall.
  • liquid refrigerant can collect at the lowest point of a refrigerant line running through the evaporator, so that circulated air, regardless of where its cross-section passes the evaporator, comes close enough to a line section filled with liquid refrigerant to be effectively cooled to become.
  • each chamber should have its own evaporator, if possible.
  • Most of these chambers are arranged one above the other, ie the more storage chambers have to be accommodated in a body of given external dimensions, the lower the storage chambers have to be.
  • a refrigeration device with two storage chambers arranged one above the other is known, each of which has its own evaporator. While the evaporator of the upper chamber, as described above, is arranged on a rear wall of the body and flowed through vertically, the lower storage chamber is assigned a vertically elongated, horizontally flowed-through evaporator. The internal structure of the evaporator is not described. It can therefore be assumed that if the evaporator is not completely filled with liquid refrigerant, an upper area of the evaporator will only contain vapor. In contact with air flowing through, this part can heat up to above the evaporation temperature and then only insufficiently cools the air.
  • a well-known design of a lamellar evaporator which is used, for example, in an installation situation such as that of the upper chamber of KR 19980018857 U can be used, comprises several blocks of mutually parallel fins, each lamella each having a first hole through which a first pipe section of a refrigerant line extends, and a second hole through which a second pipe section of the refrigerant line extends, wherein the blocks adjoin one another in the vertical direction, an inlet connection and an outlet connection of the refrigerant line is assigned to an uppermost one of the blocks, each block is connected to a preceding or following block via two bends of the refrigerant line and, in the case of a lowermost of the blocks, the first and second pipe sections are connected to one another via an bend.
  • the liquid refrigerant collects in the pipe sections of the lowest block, its fins are practically kept at the evaporation temperature even when only partially filled, and air flowing vertically through the evaporator is at a temperature close to the evaporation temperature at least in this lower block chilled.
  • air flowing vertically through the evaporator is at a temperature close to the evaporation temperature at least in this lower block chilled.
  • no effective cooling of the air would be possible in a block that does not contain any liquid refrigerant.
  • the object is achieved by a lamellar evaporator with at least a first and a second evaporator module of the type described above, the blocks of which adjoin one another in a first direction parallel to the surfaces of the lamellae, the evaporator modules adjoining one another in a second direction parallel to the surfaces of the lamellae and the Refrigerant lines of the first and second evaporator modules are connected in series.
  • each tube section is connected to each lamella in a thermally conductive manner over at least two thirds of its circumference, preferably over its entire circumference.
  • the second direction is preferably orthogonal to the first direction; in this way, when installed, the first direction can coincide with the vertical and the second with the width direction of the body.
  • the evaporator modules can form a cuboid with edges running in the first and second spatial directions.
  • Such a lamellar evaporator can easily be manufactured in different dimensions adapted to different heights and widths of the storage chamber by varying the number of blocks in each evaporator module or the number of evaporator modules.
  • each evaporator module are preferably rectangular and border along at least one long edge to an adjacent block of the same evaporator module and along a short edge to a block of another Evaporator module. In this way, one of the two pipe sections of a block can be placed in the flow shadow of the other.
  • the refrigerant lines of various evaporator modules are preferably soldered to one another and / or plug-connected.
  • the modules can be manufactured inexpensively in large numbers; lamellar evaporators with different widths can be provided at low cost by connecting different numbers of modules as required.
  • connections between the refrigerant lines are preferably arranged along a single edge of the cuboid.
  • the distance between the fins of an evaporator module located upstream with respect to the air flow or the refrigerant flow can be selected to be greater than the distance between the fins of an evaporator module located downstream with respect to this flow.
  • the heat absorption capacity of a lamella that is only cooled by refrigerant vapor is significantly smaller than that of a lamella that is cooled by liquid refrigerant, so that if the modules connected in series are supplied with refrigerant to different degrees, the lamellae of the evaporator module located foremost in the refrigerant flow will achieve the highest growth rate of the frost layer can.
  • the distance between the fins should be uniform within an evaporator module.
  • the invention also relates to a refrigeration device with at least one storage chamber, an evaporator chamber and a lamellar evaporator as described above, which is accommodated in the evaporator chamber.
  • the refrigeration device preferably has a plurality of storage chambers, each of which communicates with an evaporator chamber in order to be temperature-controlled by its evaporator.
  • each storage chamber can be regulated to its own temperature, preferably by means of its own temperature sensor, which, with a suitable design of the refrigerant circuit for individual storage chambers, can also be above the ambient temperature.
  • a specific humidity level for each storage chamber can be achieved by regulating a temperature difference between the evaporator and the storage chamber. Mixing of differently tempered or differently humid amounts of air from different storage chambers does not take place.
  • the novel structure of the lamellar evaporator described above allows the lamellar evaporator to be attached to a rear wall in a space-saving manner, even with a storage chamber of low height, instead of further reducing the usable height of the storage chamber by mounting the evaporator on the ceiling in a conventional manner.
  • any storage chamber in which the height is the smallest dimension under height, width and depth, but in particular those where the height is not more than two thirds of the width or depth, can generally be regarded as a storage chamber of small height.
  • the evaporator according to the invention also allows economical cooling of storage chambers with edge length ratios that were previously not common in refrigeration equipment because they could not be economically cooled with conventional evaporators - especially from the point of view of space utilization and energy efficiency - e.g. with a maximum height half the height or width.
  • a storage chamber that is low in the sense of the present invention can also be recognized, for example, by the fact that it is filled by a single pull-out box, because even with a pull-out box, the height of all three dimensions is the smallest, otherwise quick access to it the contents of the box is not possible.
  • a radial fan is preferably located at the outlet is arranged, the axis of which is oriented in a direction parallel to the surfaces of the lamellae, in particular the second direction.
  • the outlet and the inlet can each be slots elongated in the first direction on edges of a partition between the storage compartment and the evaporation chamber which are spaced apart in the second direction.
  • Fig. 1 shows two variants of lamellae 1, 1 'which are used to produce the lamellar evaporator according to the invention.
  • the lamellas 1, 1 ' are thin metal sheets, typically made of aluminum, of a substantially rectangular shape.
  • Two holes 2 are spaced from each other in a direction parallel to a long edge 3 of the rectangles; the distance d between the holes 2 is typically between a third and half the length of the edge 3.
  • the length of a short edge 4 can be between d and 2 d.
  • the holes 2 of the lamella 1 are circular with a diameter which, with minimal play, corresponds to the diameter of a pipe section of a refrigerant line to be inserted in order to enable a thermally conductive contact between the pipe section and the lamella along essentially the entire circumference of the holes 2.
  • the circular circumference is interrupted by notches 5, which allow the tongues 6 delimited by the notches 5 to evade when the pipe section is inserted;
  • the pressure of the tongues 6 deflected during insertion ensures an efficient heat transfer between the pipe section and the lamella.
  • Fig. 2 shows a top view of partially finished evaporator modules 7a-d.
  • Each evaporator module comprises a hairpin-shaped bent refrigerant line 8 with a first bend 9 and two straight pipe sections 10a and 10b that are integrally connected via the bend 9.
  • a plurality of parallel lamellae 1 are each pushed onto the pipe sections 10a-b and grouped into blocks 11a-d.
  • the extent of all blocks 11a-d in the longitudinal direction of the pipe sections 9 is the same; the number of lamellas 1 in a block 11a-d and their distance from one another can vary.
  • Fig. 3 shows a finished evaporator module 7. Areas of the pipe sections 10a-b, which are in the stage of Fig. 2 have remained free of lamellas are formed into semicircular second arcs 12, so that the blocks 11a-d form a stack in which long edges 3 of the lamellas of one block each face long edges of the lamellas of an adjacent block.
  • the block 11a adjacent to the first sheet 9 forms the bottom block of the stack.
  • the pipe sections 10a-b meander through the blocks 11b, 11c stacked on them up to inlet and outlet connections 13, 14.
  • One of these connections, here connection 13, is widened in order to enable the connection 14 of a structurally identical second evaporator module to be plugged in .
  • Fig. 4 shows four evaporator modules, denoted by 7a-d, the refrigerant lines 8 of which are connected in series by plugging into one another and soldering the connections 13, 14.
  • the connectors 13, 14 plugged into one another lie on a straight line which runs parallel to a long edge of the approximately cuboidal evaporator 15 formed by the evaporator modules 7a-d.
  • the evaporator modules 7a-d can be exactly identical; in the case of Fig. 4
  • the evaporator module 7a differs from the other modules 7b-d in that the distance between the lamellae 1 is greater. If air flows through the evaporator 15 horizontally, in the direction of the arrows 16, during operation, the evaporator module 7a is the most upstream module in relation to the airflow, and moisture carried along in the airflow is preferably deposited on the fins of the module 7a especially when the connection 13 is used as an inlet connection and therefore the evaporator module 7a is better supplied with liquid refrigerant than the others.
  • the increased spacing of the lamellas makes it possible to select a long time interval between two defrosting processes.
  • the connection 14 of the module 7d is used as an inlet connection for refrigerant; then the module 7d is best supplied with liquid refrigerant.
  • the frost formation can be distributed differently over the modules 7a-d. If only steam gets into the modules 7b-d, the formation of frost is so concentrated on the module 7d that it can make sense to provide an enlarged lamellar spacing in this. If the other modules also receive liquid refrigerant from time to time, frost formation takes place in these too, so that the frost is distributed over all modules and the fin spacing can be the same in all of them.
  • the connected connections 13, 14 represent the highest points of the refrigerant line in the evaporator 15, it is possible to completely fill the refrigerant line 8 of the module 7a or 7d which is furthest upstream in relation to the refrigerant flow with liquid refrigerant, even if the refrigerant lines 8 the following modules only contain steam. In this way, uniform cooling of the air flowing through is ensured over the entire cross section of the evaporator 15, even if the evaporator 15 is not completely filled.
  • Fig. 5 shows a section through the body 17 of a household refrigeration appliance with several storage chambers at different temperatures.
  • the sectional plane runs near a rear wall of the body 17 through evaporator chambers 18a-c extending on this rear wall, each of the evaporator chambers 18a-c each contains an evaporator 15a-c of the type described above and forms a closed air circuit with the associated storage chamber.
  • Storage chambers (not shown) each have the same height as the associated evaporator chambers 18a-c and are separated from one another by intermediate floors 19 of the body 17 which are heat-insulating and which prevent air exchange between the various air circuits.
  • the lowest storage chamber here is a freezer compartment, the height of which roughly corresponds to its width.
  • the height of the evaporator chamber 18a is somewhat smaller than that of the storage chamber, since part of the rear wall is occupied by a machine room 20 in the usual manner.
  • the evaporator chamber 18a communicates with the storage chamber via an outlet opening 22a provided with an axial fan 21 in an upper region of a partition wall 24a and an inlet opening 23a in the form of a gap at a lower edge of the partition wall 24a.
  • the evaporator 15a comprises several, here five, in the width direction of the body 17 arranged side by side evaporator modules 7 with here five blocks 11, which are flown through from bottom to top during operation.
  • the next higher storage chamber and its evaporation chamber 18b are much flatter; if one wanted to provide a horizontal gap and an opening as in the evaporator chamber 18a, then there would be no space to accommodate evaporator modules 7 in sufficient number and size.
  • the number of evaporator modules 7 is therefore reduced in the evaporator 15b, so that space remains to the right and left of the evaporator 15b to provide an inlet opening 23b and an outlet opening 22b - here covered by a radial fan 25 - and the number of blocks 11 is also shown in Adjustment to the height of the evaporator chamber 18b reduced.
  • the blocks 11 themselves can be identical to those of the evaporator 15a; However, it is also conceivable to vary the number of lamellae 1 per block 11 from one evaporator 15a-c to the other in order to adapt to the capacities required in each case for the individual storage chambers. However, the smaller the number of fins, the less favorable the ratio of power to space requirement of the evaporator due to the protruding arches 9, 12. It can therefore be expedient to further reduce the number of modules 7 when the power requirement is low, as shown in the example of the evaporator 15c, so that the evaporator chamber 18c only occupies part of the width of the rear wall and the remaining width of the storage chamber 26c extends up to can extend to the rear wall.
  • the inlet opening 23c can then be designed as a gap between the rear wall and an end of the partition wall 24c facing away from the radial fan 25.
  • Fig. 6 shows a section through a rear part of the body 17 at the level of the line VI-VI Fig. 5 .
  • the already mentioned rear wall of the body 17 is denoted by 27, side walls by 28.
  • the arches 9, 12 of the evaporator 15b protruding in the depth direction of the body are received in bypass blockers 29, typically molded parts made of expanded polystyrene, in order to be removed from the storage chamber via the inlet opening 23b 26b to force air sucked in between the fins of the evaporator 15b.
  • a suction opening 30 of the radial fan 25 lies opposite a downstream end of the evaporator 15b.
  • the radial fan 25 comprises, in a manner known per se, a fan wheel which, within a housing 31, extends around a suction opening 30 concentric axis 34 parallel to the lamellae 1 rotates.
  • the diameter of the suction opening 30 corresponds approximately to the edge length of a block 11 in the direction perpendicular to the lamellas, that of the housing 31 corresponds approximately to the thickness of the evaporator 15b including the arches 9, 12.
  • a pull-out basket 32 or a pull-out box In order to be able to easily access the contents of the storage chamber 26b despite its small height, it is useful to provide a pull-out basket 32 or a pull-out box.
  • a rail guide or the shape of the basket 32 can ensure that it does not block the openings 22b, 23b.
  • the inlet opening 23b is flanked by a web 33 of the partition wall 24b projecting into the storage chamber 26b, and the depth of the basket 32 is adapted to that of the storage chamber 26b so that a door of the storage chamber 26b can only be closed when the basket 32, as shown in the figure, rests next to the web 33 on the partition wall 24b.
  • the outlet opening 22b can be shaped as a nozzle protruding over the partition wall 24b, so that the basket 32, if it blocks the outlet opening 22b, also prevents the door from closing.
  • the free cross-sections of inlet and outlet openings 23b, 22b are each elongated vertically in the shape of a slot in order to restrict as little as possible the width of the storage chamber 26b that can be used to accommodate items to be cooled or the basket 32.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Geometry (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP21152456.6A 2020-02-20 2021-01-20 Réfrigérateur pourvu d'évaporateur à lamelles Withdrawn EP3869129A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102020202173.2A DE102020202173A1 (de) 2020-02-20 2020-02-20 Kältegerät mit Lamellenverdampfer

Publications (1)

Publication Number Publication Date
EP3869129A1 true EP3869129A1 (fr) 2021-08-25

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ID=74191668

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21152456.6A Withdrawn EP3869129A1 (fr) 2020-02-20 2021-01-20 Réfrigérateur pourvu d'évaporateur à lamelles

Country Status (3)

Country Link
EP (1) EP3869129A1 (fr)
CN (1) CN113280534A (fr)
DE (1) DE102020202173A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03169482A (ja) * 1989-11-29 1991-07-23 Showa Alum Corp 熱交換器の製造方法
JPH09159311A (ja) * 1995-12-08 1997-06-20 Toshiba Corp 冷蔵庫用熱交換器
KR19980018857U (ko) 1996-09-30 1998-07-06 배순훈 수평으로 냉기가 순환되는 냉장실을 갖는 냉장고
US6253839B1 (en) * 1999-03-10 2001-07-03 Ti Group Automotive Systems Corp. Refrigeration evaporator
JP2004239486A (ja) * 2003-02-05 2004-08-26 Hitachi Home & Life Solutions Inc 熱交換器およびその製造方法
CN1912504A (zh) * 2005-08-12 2007-02-14 昭和电工株式会社 蒸发器

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001108258A (ja) * 1999-10-08 2001-04-20 Daikin Ind Ltd 空気熱交換器及びこれを備えた空気調和機
NZ532668A (en) * 2001-10-22 2004-09-24 Showa Denko K Finned tube for heat exchangers, heat exchanger, process for producing heat exchanger finned tube, and process for fabricating heat exchanger
KR20050085449A (ko) * 2002-12-10 2005-08-29 쇼와 덴코 가부시키가이샤 열교환기용 핀형 튜브, 열교환기, 열교환기용 핀형 튜브제조 장치 및 열교환기용 핀형 튜브 제조 방법
US20110024083A1 (en) * 2009-07-31 2011-02-03 Steimel John C Heat exchanger
WO2018143619A1 (fr) * 2017-02-03 2018-08-09 Samsung Electronics Co., Ltd. Échangeur de chaleur et son procédé de fabrication
TR201706594A3 (tr) * 2017-05-04 2018-12-21 Arcelik As Isi pompasi i̇çeren bi̇r ev ci̇hazi

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03169482A (ja) * 1989-11-29 1991-07-23 Showa Alum Corp 熱交換器の製造方法
JPH09159311A (ja) * 1995-12-08 1997-06-20 Toshiba Corp 冷蔵庫用熱交換器
KR19980018857U (ko) 1996-09-30 1998-07-06 배순훈 수평으로 냉기가 순환되는 냉장실을 갖는 냉장고
US6253839B1 (en) * 1999-03-10 2001-07-03 Ti Group Automotive Systems Corp. Refrigeration evaporator
JP2004239486A (ja) * 2003-02-05 2004-08-26 Hitachi Home & Life Solutions Inc 熱交換器およびその製造方法
CN1912504A (zh) * 2005-08-12 2007-02-14 昭和电工株式会社 蒸发器

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DE102020202173A1 (de) 2021-08-26
CN113280534A (zh) 2021-08-20

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