WO2007136379A1 - Échangeur de chaleur à tube plat en spirale - Google Patents

Échangeur de chaleur à tube plat en spirale Download PDF

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Publication number
WO2007136379A1
WO2007136379A1 PCT/US2006/019920 US2006019920W WO2007136379A1 WO 2007136379 A1 WO2007136379 A1 WO 2007136379A1 US 2006019920 W US2006019920 W US 2006019920W WO 2007136379 A1 WO2007136379 A1 WO 2007136379A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
flat tube
flat
spiral
tubes
Prior art date
Application number
PCT/US2006/019920
Other languages
English (en)
Inventor
Michel Granbon
Original Assignee
Carrier Corporation
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 Carrier Corporation filed Critical Carrier Corporation
Priority to US12/302,239 priority Critical patent/US20090114380A1/en
Priority to EP06770957A priority patent/EP2029952A4/fr
Priority to PCT/US2006/019920 priority patent/WO2007136379A1/fr
Priority to CN200680055382.1A priority patent/CN101490494A/zh
Publication of WO2007136379A1 publication Critical patent/WO2007136379A1/fr

Links

Classifications

    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0025—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes
    • F28D7/0033—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes the conduits for one medium or the conduits for both media being bent
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/04—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being spirally coiled
    • 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
    • F28D2021/007—Condensers
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F2013/005—Thermal joints
    • F28F2013/006—Heat conductive materials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2260/00—Heat exchangers or heat exchange elements having special size, e.g. microstructures
    • F28F2260/02—Heat exchangers or heat exchange elements having special size, e.g. microstructures having microchannels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/02—Fastening; Joining by using bonding materials; by embedding elements in particular materials
    • F28F2275/025—Fastening; Joining by using bonding materials; by embedding elements in particular materials by using adhesives
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/4935—Heat exchanger or boiler making

Definitions

  • the present invention generally relates to heat exchangers. More particularly, the present invention relates to a counterflow heat exchanger having flat tubes configured to form concentric spirals.
  • the flat tubes may include interior microchannels.
  • Counterflow heat exchangers for gases and liquids are known, and typically include an inlet and an outlet for each of two or more fluids.
  • the fluids generally do not mix and follow separate flow paths within the heat exchanger.
  • the most common types of counterflow heat exchangers include flat plate, tube in tube and shell and tube heat exchangers.
  • Shell and tube heat exchangers generally have a series of small tubes within a larger pressure vessel or shell. Heat is transferred between a fluid flowing within the small tubes and another fluid flowing within the shell.
  • a flat plate heat exchanger heat is transferred between two fluids flowing in opposite directions along separate flow paths created between a series of parallel plates.
  • the plates are typically made of stainless steel and may contain chevron- shaped channels to increase heat transfer efficiency.
  • the plates may be sealed at their joints by using elastomer gaskets or by a brazing process.
  • the large surface area of the plates provides for greater heat transfer efficiency when compared to a shell and tube design.
  • Flat plate heat exchangers are usually lighter and more compact than shell and tube heat exchangers.
  • the fluid flowing through a flat plate heat exchanger must be in contact with the plates for a sufficient amount of time, meaning that the plates have to be of a certain length.
  • flat plate heat exchangers For chiller applications, (evaporation of refrigerant in one side of the wall and cooling of the water in the other side) flat plate heat exchangers must be installed vertically to facilitate refrigerant distribution in each adjacent plate. This configuration results in a relatively large height-to-footprint ratio. This height-to- footprint constraint limits the applications for flat plate heat exchangers.
  • the stainless steel typically used in flat plate heat exchangers is also relatively heavy, and has a relatively high thermal resistance and a low heat transfer coefficient, which also limits its performance.
  • MicroChannel tubes are also known, and have been commonly used in heat exchangers for automotive applications. However, this technology has been developed primarily for air-to-liquid heat exchangers.
  • a spiral flat tube heat exchanger comprising a first flat tube and a second flat tube thermally coupled to the first flat tube.
  • the first flat tube forms a first spiral and the second flat tube forms a second spiral, the first and second spirals being substantially concentric.
  • a first fluid flows through the first spiral in a first flow direction, and a second fluid flows through the second spiral in a second flow direction.
  • the flat tubes preferably contain microchannels and are preferably made of aluminium.
  • a heat exchanger having a plurality of modules comprises at least two collectors and a plurality of microchannel flat tubes.
  • the microchannel flat tubes are positioned vertically between the collectors so that a longitudinal axis of each of the microchannel flat tubes is substantially collinear with the longitudinal axis of each of the other microchannel flat tubes.
  • the plurality of modules wrap around each other in a spiral configuration so that the plurality of microchannel flat tubes are in thermal contact.
  • a method of making a spiral flat tube heat exchanger of the present invention comprises providing a first module having a first inlet collector connected to a first outlet collector by a first flat tube and providing a second module having a second inlet collector connected to a second outlet collector by a second flat tube.
  • the first module is then positioned adjacent to the second module with first inlet collector in proximity to second outlet collector and first outlet collector in proximity to second inlet collector.
  • the first outlet collector and the second inlet collector are then rotated together in the same direction while holding the first inlet collector and second outlet collector in a fixed position so as to deform the first flat tube and second flat tube to form two substantially concentric spirals.
  • the present invention thus provides an extremely efficient counter flow heat exchanger that provides greater flexibility in terms of physical dimensions as well as control of desired heat transfer properties. These features will allow the present invention to find use in a wide variety of applications.
  • FIG. 1 is a top view of the spiral flat tube heat exchanger of the present invention
  • FIG. 2 is a top view of a module of the heat exchanger of FIG. 1 ;
  • FIG. 3 is a front view of the module of FIG. 2;
  • FIG. 4 is a cross-sectional view of the heat exchanger module of FIG. 3 taken along the line IV-IV;
  • FIG. 5 is a cross-sectional view of a flat tube of the heat exchanger of FIGS. 1 through 4;
  • FIGS. 6 through 8 illustrate a method of making the heat exchanger shown in FIG. 1.
  • FIG. 1 an exemplary embodiment of a spiral flat-tube heat exchanger is illustrated.
  • Heat exchanger 100 includes a first tube 102 and a second tube 104.
  • First tube 102 is thermally coupled to second tube 102, and the tubes are configured to form alternating spirals that are preferably substantially concentric.
  • Substantially concentric means that a first spiral 106 formed by first tube 102 and a second spiral 108 formed by second tube 104 share a common central area 110.
  • spiral means an object wound around a fixed central area at a continuously increasing distance from the area.
  • a first working fluid 112 flows through first tube 102 and a second working fluid 114 flows through second tube
  • First tube 102 and second tube 104 are in thermal contact, so that heat may be transferred between the first working fluid 112 and the second working fluid 114.
  • heat exchanger 100 is a counterflow heat exchanger, meaning that the flow direction of first working fluid 112 is opposite the flow direction of second working fluid 114.
  • counterflow heat exchangers transfer heat more efficiently than cross flow or parallel flow heat exchangers.
  • first working fluid 112 enters heat exchanger 100 through first inlet collector 116, located in central area 110.
  • First working fluid 102 then flows in a clockwise direction through first spiral 106, and exits heat exchanger 100 through a first outlet collector 118, disposed near a periphery 124 of the heat exchanger.
  • second working fluid 114 enters heat exchanger 100 near periphery 124 through a second inlet collector 120.
  • Second working fluid 104 then flows in a counterclockwise direction through second spiral 108, and exits heat exchanger 100 through a second outlet collector 122 located in central area 110.
  • the spiral heat exchanger of the present invention may be a parallel flow heat exchanger, in which two working fluids each flow in the same direction, either clockwise or counterclockwise, within separate spirals.
  • the working fluids could enter at the periphery of the heat exchanger and exit at the center of the heat exchanger or enter at the center and exit at the periphery.
  • first working fluid 112 may be a cooler fluid than second working fluid 114.
  • heat would be transferred from first working fluid 112 to the walls of first tube 102, and then transferred by conduction to the walls of second tube 104 and finally transferred to second working fluid 114.
  • the spiral configuration of heat exchanger 100 provides a large surface area for heat transfer, providing greater heat transfer efficiency while requiring less space than prior art heat exchangers. Also, the spiral configuration of heat exchanger 100 provides for nearly complete counterflow within the heat exchanger, thus increasing heat transfer efficiency.
  • Working fluids 112, 114 may be a liquid, a gas, or a two-phase medium.
  • one of the working fluids 112, 114 is water
  • the other fluid is a refrigerant, such as, but not limited to, R134a, R404A, R410A, CO 2 , propane, ammonia, isobutene, and other commonly used refrigerants.
  • working fluids 112, 114 are water and ethylene glycol.
  • first inlet collector 116, first tube 102 and first outlet collector 118 form a first module 126
  • second inlet collector 120, second tube 104 and second outlet collector 122 form a second module 128.
  • first module 126 details of first module 126 are shown. It should be understood that second module 128 will have a similar structure. For clarity, first module 126 is shown in an unwound state, before being assembled with second module 128 into the spiral configuration of heat exchanger 100.
  • first tube 102 comprises a plurality of tubes.
  • the embodiment shown in FIG. 3 has five tubes 102 arranged vertically between first inlet collector 116 and first outlet collector 118.
  • any number of tubes 102 may be used, including a single large tube.
  • First inlet collector 116 is in fluid communication with first outlet collector 118 by way of flat tubes 102.
  • An inlet 128 is in fluid communication with first inlet collector 116, and an outlet 130 is in fluid communication with first outlet collector 118.
  • first working fluid 112 enters module 126 through inlet 128. After passing through inlet 128 into first inlet collector 116, first working fluid 112 travels through the plurality of flat tubes 102 into first outlet collector 118. Finally, the fluid flows out of first outlet collector 118 through outlet 130.
  • specific inserts may be applied inside inlet collector 116 to prevent refrigerant maldistribution among the plurality of flat tubes 102 operating in parallel.
  • First tube 102 may be of any cross-sectional shape that will allow heat to be transferred between adjacent tubes.
  • First tubes 102 are preferably flat tubes, that is tubes having substantially flat walls to aid in heat transfer.
  • the cross- sectional shape of first tube 102 is obround, that is a shape having two substantially semicircular ends connected by two substantially parallel lines.
  • An obround cross section of first tube 102 is illustrated in FIG. 5.
  • First tube 102 has a top semi-circular section 132, a bottom semi-circular section 134 and substantially parallel flat walls 136.
  • First tube 102 has a height, h and a width w, with the height preferably being greater than the width.
  • First tubes 102 may be manufactured using an extrusion process, a welding process, or any other process capable of producing a suitable cross-sectional shape.
  • the internal shape of tubes 102 may be specifically adapted to accommodate various fluid and operation types to maximize the heat transfer characteristics of tubes 102.
  • tubes 102 may be of a distinct shape when used for one phase cooling, refrigerant boiling, and condensation, respectively.
  • the quality of thermal contact between flat walls 136 of adjacent tubes is a major factor in the efficiency of heat transfer in heat exchanger 100.
  • Flat walls 136 of adjacent tubes should be as close together as possible.
  • dry contact may not provide sufficient thermal contact, since any air remaining between adjacent flat walls will act as an insulator, thus decreasing the heat transfer efficiency.
  • the preferred embodiment of the present invention uses metal tubes that are brazed together.
  • the brazing process eliminates air gaps, resulting in low thermal resistance between adjacent tubes.
  • the brazing process is also relatively easy to control.
  • the quality of thermal contact between adjacent tubes may be increased by using a high conductivity grease, a glue, or by means of a mechanical bonding process.
  • First tubes 102 are oriented vertically between first outlet collector 116 and first inlet collector 118, so that a longitudinal axis y of each of the first tubes 102 is substantially collinear with the longitudinal axis of the other first tubes 102.
  • Tubes 102 are preferably microchannel flat tubes.
  • MicroChannel flat tubes are flat tubes containing small interior channels.
  • the interior microchannels typically have channel widths between 10 and 1 ,000 ⁇ m. These channels increase both the rate of heat transfer and heat transfer efficiency by creating turbulent flow.
  • the use of microchannel flat tubes allows for optimization of the heat transfer coefficient and of the pressure drop within the tubes.
  • Tubes 102 have interior microchannels 140, as illustrated in FIG. 5.
  • Microchannels 140 may be of any size and shape
  • the present invention allows microchannel flat tubes to be used in a liquid to liquid or liquid to two-phase medium heat exchanger.
  • microchannel tubes had been used principally for air to liquid heat exchangers.
  • a working fluid flows through horizontally oriented microchannel flat tubes and transfers heat to air flowing across the tubes in a cross flow configuration, meaning that the air flows perpendicular to the flow direction of the working fluid.
  • the microchannel tubes were typically connected to a plurality of fins installed horizontally between the flat tubes.
  • the present invention uses flat microchannel tubes 102 arranged vertically between two collectors, without fins. Heat is transferred from a first working fluid to a second working fluid in a counterflow configuration.
  • the present invention thus applies microchannel technology in a new way to produce a liquid to liquid heat exchanger having exceptional heat transfer efficiency.
  • Flat tubes 102 are preferably made out of aluminum.
  • Aluminum provides several advantages over traditional steel or copper tubes that have been used in prior-art heat exchangers. Aluminum has a lower thermal resistance, is lighter and more easily deformable than steel or copper, and demonstrates good resistance to corrosion.
  • flat tubes 102 could be made of other metals or a plastic material.
  • First module 126 is positioned adjacent to second module 128 with first inlet collector 116 in proximity to second outlet collector 122, and first outlet collector 118 in proximity to second inlet collector 120.
  • the length of second module 128 may be greater than the length of first module 126.
  • First inlet collector 116 and second outlet collector 122 are held in a fixed position, while first outlet collector 118 and second inlet collector 120 are rotated together in the same direction so as to deform the first tube 102 and second tube 104 and form two substantially concentric spirals, 106 and 108.
  • a rolling mechanism 138 may be used to apply force to the tubes.
  • the arrows shown in FIGS. 6 through 8 illustrate the direction of movement of the rolling mechanism 138 and the collectors 118, 120 as heat exchanger 100 is being formed.
  • First tube 102 and second tube 104 may be deformed by rolling, using rolling mechanism 138.
  • Concentric spirals 106, 108 will share a common central area 110, with first inlet collector 116 and second outlet collector 122 being disposed in central region 110, and first outlet collector 118 and second inlet collector 120 being disposed near periphery 124 of the spiral heat exchanger 100.
  • the spiral heat exchanger 100 resulting from this method is shown in FIG. 1 .
  • the spiral heat exchanger may have three modules, comprising two refrigerant circuits and one water circuit, possibly for use in a two circuit chiller.
  • Another possibility includes a spiral heat exchanger having either three or four modules, with two water circuits and one or two refrigeration circuits, which would allow for a heat recovery option in a double bundle condenser.
  • first tubes 102 of heat exchanger 100 have different structures than adjacent second tubes 104, based on the working fluid being carried through the tube. For example, if first tubes 102 were carrying water and second tubes 104 were carrying refrigerant in boiling or condensation, the size and shape of the tube, as well as the size, shape, and number of microchannels within the tubes could be varied to compensate for the different heat transfer coefficients and pressure drops on the water side and on the refrigerant side.
  • the present invention allows for a flexible design of a heat exchanger, both in terms of physical dimensions and desired performance.
  • a flexible design of a heat exchanger both in terms of physical dimensions and desired performance.
  • critical properties such as fluid capacity and pressure drop within the device can be carefully controlled.
  • the spiral configuration of the inventive heat exchanger allows for a very compact design with flexibility in the selection of the height to footprint ratio. This flexibility makes the inventive heat exchanger suitable for a greater number of applications when compared to previous heat exchanger designs.
  • heat exchangers described herein can be utilized with various heat transfer systems that utilize heat exchangers.
  • the particular components of the heat transfer systems can be chosen by one of ordinary skill in the art to increase the thermal efficiency of the system.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un échangeur de chaleur à tube plat en spirale comprenant un premier tube plat et un second tube plat couplé thermiquement au premier tube plat, le premier tube plat et le second tube plat formant des spirales sensiblement concentriques. Un premier fluide s'écoule à travers le premier tube plat dans une première direction d'écoulement, et un second fluide s'écoule à travers le second tube plat dans une seconde direction d'écoulement. Les tubes plats contiennent, de préférence, des micro-canaux pour augmenter le rendement de transfert de chaleur.
PCT/US2006/019920 2006-05-23 2006-05-23 Échangeur de chaleur à tube plat en spirale WO2007136379A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US12/302,239 US20090114380A1 (en) 2006-05-23 2006-05-23 Spiral flat-tube heat exchanger
EP06770957A EP2029952A4 (fr) 2006-05-23 2006-05-23 Échangeur de chaleur à tube plat en spirale
PCT/US2006/019920 WO2007136379A1 (fr) 2006-05-23 2006-05-23 Échangeur de chaleur à tube plat en spirale
CN200680055382.1A CN101490494A (zh) 2006-05-23 2006-05-23 螺旋扁平管式换热器

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2006/019920 WO2007136379A1 (fr) 2006-05-23 2006-05-23 Échangeur de chaleur à tube plat en spirale

Publications (1)

Publication Number Publication Date
WO2007136379A1 true WO2007136379A1 (fr) 2007-11-29

Family

ID=38723595

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2006/019920 WO2007136379A1 (fr) 2006-05-23 2006-05-23 Échangeur de chaleur à tube plat en spirale

Country Status (4)

Country Link
US (1) US20090114380A1 (fr)
EP (1) EP2029952A4 (fr)
CN (1) CN101490494A (fr)
WO (1) WO2007136379A1 (fr)

Cited By (5)

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WO2009115284A1 (fr) * 2008-03-20 2009-09-24 Valeo Systemes Thermiques Echangeur de chaleur et ensemble integre de climatisation comprenant un tel echangeur
WO2010063897A1 (fr) 2008-12-01 2010-06-10 Valeo Systemes Thermiques Echangeur de chaleur à spires et dispositif de climatisation comprenant un tel échangeur de chaleur.
US20110104350A1 (en) * 2008-08-14 2011-05-05 Cluesserath Ludwig Method and device for heat-treating liquid foods
WO2018148534A1 (fr) * 2017-02-09 2018-08-16 Evapco, Inc. Échangeur de chaleur à condenseur évaporatif de réfrigérant
US10697708B2 (en) * 2016-04-18 2020-06-30 Hamilton Sunstrand Corporation Heat exchangers

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US8268060B2 (en) * 2007-10-15 2012-09-18 Green Comfort Systems, Inc. Dehumidifier system
US8721981B2 (en) * 2009-11-30 2014-05-13 General Electric Company Spiral recuperative heat exchanging system
US8858758B2 (en) * 2010-07-21 2014-10-14 Aquaback Technologies, Inc. Distiller
CN102636048A (zh) * 2011-08-27 2012-08-15 陈立德 蜗旋式热交换装置及其制造方法
CA3055348A1 (fr) * 2011-09-15 2013-03-21 Edward E. Durrant Systeme de nettoyage monte sur camion
JP2013164241A (ja) * 2012-02-13 2013-08-22 Denso Corp 熱交換装置
CN103522470A (zh) * 2013-10-31 2014-01-22 苏州市高精勤精密模具有限公司 一种工业降温用金属折弯流体扁平管道
DE102014223040A1 (de) 2013-11-13 2015-05-13 MAHLE Behr GmbH & Co. KG Sorptionswärmeübertrager-Modul, vorzugsweise für ein Kraftfahrzeug
CN106403655A (zh) * 2015-07-31 2017-02-15 杭州三花家电热管理系统有限公司 一种换热器及其在系统中的应用
CN106610241A (zh) * 2015-10-26 2017-05-03 北京肯思得能源科技有限公司 管壳式换热器及其管壳式换热器组
CN106943023A (zh) * 2016-01-06 2017-07-14 杭州三花家电热管理系统有限公司 换热器及具有其的制冷系统
CN106017146A (zh) * 2016-06-12 2016-10-12 洛阳文森科技有限公司 一种高温热泵换热器及工艺
CN106370025A (zh) * 2016-09-22 2017-02-01 北京机械设备研究所 一种微型螺旋式微通道平行流换热器
CN106440527B (zh) * 2016-11-04 2022-03-15 上海科凌能源科技有限公司 无翅片的微通道换热器
PL3622226T3 (pl) * 2017-05-10 2022-03-07 Gea Food Solutions Weert B.V. Ulepszone środki grzejne dla owijarki przepływowej
CA3071392C (fr) * 2017-07-28 2023-08-08 Fluid Handling Llc Procedes d'acheminement de fluide pour echangeur de chaleur en spirale a section transversale en treillis fabrique par fabrication additive
DE102017218973A1 (de) * 2017-10-24 2019-04-25 Hanon Systems Gegenstrom-Wärmeübertrager
CN108007244B (zh) * 2017-11-27 2019-08-23 西安交通大学 一种螺旋推流通道板式换热器
CN108151372A (zh) * 2017-12-28 2018-06-12 新昌县宏宇制冷有限公司 一种双重换热蒸发器
EP3842727B1 (fr) * 2019-12-23 2023-11-15 Hamilton Sundstrand Corporation Échangeur de chaleur en diamant à spirales fabriqué additivement
CN111426216B (zh) * 2020-04-03 2021-12-28 浙江大学 一种燃料电池温控系统高效换热器及其加工装置
CN111912255B (zh) * 2020-06-05 2021-10-15 广州新瑞新能源发展有限公司 一种高效旋流式换热器
KR20220027562A (ko) * 2020-08-27 2022-03-08 엘지전자 주식회사 열교환기
CN112437594A (zh) * 2020-11-26 2021-03-02 北京石油化工学院 一种扰流涡状微通道换热器

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WO2009115284A1 (fr) * 2008-03-20 2009-09-24 Valeo Systemes Thermiques Echangeur de chaleur et ensemble integre de climatisation comprenant un tel echangeur
FR2928997A1 (fr) * 2008-03-20 2009-09-25 Valeo Systemes Thermiques Echangeur de chaleur et ensemble integre de climatisation comprenant un tel echangeur.
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WO2018148534A1 (fr) * 2017-02-09 2018-08-16 Evapco, Inc. Échangeur de chaleur à condenseur évaporatif de réfrigérant

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CN101490494A (zh) 2009-07-22
US20090114380A1 (en) 2009-05-07
EP2029952A4 (fr) 2013-01-16
EP2029952A1 (fr) 2009-03-04

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