EP1068478A1 - Unite collecteur-echangeur de chaleur integree - Google Patents

Unite collecteur-echangeur de chaleur integree

Info

Publication number
EP1068478A1
EP1068478A1 EP99966865A EP99966865A EP1068478A1 EP 1068478 A1 EP1068478 A1 EP 1068478A1 EP 99966865 A EP99966865 A EP 99966865A EP 99966865 A EP99966865 A EP 99966865A EP 1068478 A1 EP1068478 A1 EP 1068478A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
collector
channel
housing
collecting
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Withdrawn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
EP99966865A
Other languages
German (de)
English (en)
Inventor
Bernd Dienhart
Hans-Joachim Krauss
Hagen Mittelstrass
Karl-Heinz Staffa
Christoph Walter
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.)
Ford Werke GmbH
Original Assignee
Ford Werke 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 Ford Werke GmbH filed Critical Ford Werke GmbH
Publication of EP1068478A1 publication Critical patent/EP1068478A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00321—Heat exchangers for air-conditioning devices
    • B60H1/00342—Heat exchangers for air-conditioning devices of the liquid-liquid type
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • 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
    • F28D7/02—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 helically coiled
    • F28D7/022—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 helically coiled the conduits of two or more media in heat-exchange relationship being helically coiled, the coils having a cylindrical configuration
    • 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
    • F28D7/02—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 helically coiled
    • F28D7/024—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 helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/051—Compression system with heat exchange between particular parts of the system between the accumulator and another part of the cycle
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Definitions

  • the invention is based on the technical problem of providing an integrated collector-heat exchanger assembly of the type mentioned at the outset, which has a comparatively simple structure, can be produced with relatively little effort and realizes a compact integration of the heat exchanger unit in a collector housing with good heat transfer efficiency.
  • the collecting container is open at the top, and the associated flow channel leading from the collecting container to the outside of the housing runs from the open top collecting container area downwards through the corresponding helical heat exchanger channel to at least the lower collecting container area, where it is connected to a or several oil suction holes made in the collecting container.
  • oil suction hole is to be understood here to mean any fine opening through which a fluid which is carried along by the actual heat transfer medium and is, on the other hand, clearly viscous is entrained, which may or may not be oil. When used in air conditioning systems, it is mostly lubricating oil for the compressor that is entrained by the refrigerant. Via the oil suction holes, this can be carried away in a controlled manner by the refrigerant sucked out of the collecting container after it has previously settled down in the collecting container.
  • both housing-side connection points of the continuous, not in the collecting space are located.
  • the first flow channel ends on a common housing side, preferably facing one end region of the helical heat exchanger channels, and the flow channel is guided with a straight pipe section in the collector housing to the opposite heat exchanger channel end region.
  • the inlet and outlet on the housing side can also be provided for the heat transfer medium to be temporarily stored in the collecting space, so that all connections for the integrated collector-heat exchanger assembly are accessible from one side.
  • the coaxial tubular coil merges in one end region into a U-shaped coaxial tubular section which is located radially within the spiral region and with which the flow length effective for heat transfer can be further increased without enlarging the structural unit itself.
  • FIG. 7 shows cross-sectional views of various coaxial tube coils that can be used in the structural unit from FIGS.
  • FIG. 10 is a sectional view corresponding to FIG. 6, but for a unit with only one connection side,
  • FIG. 11 is a schematic plan view of the connection side of the assembly of FIGS. 10 and
  • the collector-heat exchanger assembly shown in FIG. 1 contains, in the interior of a collector housing 1, a cylindrical collecting container 2 which functions as a collecting space and which is seated on an intermediate floor 3. Between the collecting container 2 and the collector housing 1, a coiled tubing 5 is introduced, the windings of which are spaced apart from one another in the axial direction and bear fluid-tight radially on the inside against the outside of the collecting container and radially on the outside against the inside wall of the collector housing. In this way, a corresponding helical space 6 is formed, which is axially delimited by two adjacent coiled tubing turns, radially inwards by the collecting container wall and radially outwards by the collector housing wall.
  • the pipe coil 5 ends on the upper side of the housing with an outlet pipe 5a led out of the housing 1 and on the lower side of the housing with an inlet pipe 5b which passes through the intermediate floor 3 and a bottom wall 1a of the collector housing 1 is passed through. While the inlet connection 5b is guided in a fluid-tight manner through the housing base wall 1a, a passage, not shown in detail, is provided in the intermediate base 3, via which the spiral intermediate space 6 is in fluid communication with a discharge space 7 delimited by the intermediate base 3 and the housing base wall 1a. An outlet 8 leads from the collector space 1 out of the collector housing 1. An inlet port 4 is introduced via a further opening on the upper side 1b of the housing and opens into the collecting container 2 which is open at the top.
  • the helical tube 5 in the collecting container area on the one hand and the spiral space 6 together with the upper collecting container mouth and the discharge space 7 on the other hand form a first or second flow channel
  • the two flow channels along their helical sections, i.e., along the spiral tube 5 and the spiral space 6 are in thermal contact with one another and thus form a first or second heat exchanger channel of a heat exchanger unit integrated in the collector housing 1.
  • a first heat transfer medium M1 is passed through the pipe flow channel which runs continuously from the inlet connector 5b to the outlet connector 5a in the collector housing 1 and which consists of the tube coil 5 in the heat transfer active area.
  • a second heat transfer medium M2 to be brought into thermal contact with the first reaches the collecting container 2 via the inlet connection 4 and is temporarily stored there. From there, it can be withdrawn from the collecting container 2 in the vapor state at the top, flowing down along the spiral space 6, then entering the discharge space 7 and being drawn off from there via the outlet connection 8.
  • the second, helical flow path means that the second heat transfer medium M2 is in countercurrent thermal contact via the wall of the tube coil 5, which is made of a good heat-conductive material, with the first heat transfer medium M1 passed through the tube coil 5.
  • one or more oil suction bores 9 are provided in the lower region of the side of the container, which are dimensioned such that the more viscous fluid depends on the suction effect in a certain, desired amount is sucked out of the collecting container 2.
  • the collector-heat exchanger assembly constructed in this way can be used in particular for the refrigerant circuit of a motor vehicle air conditioning system in which CO 2 or another conventional refrigerant is used.
  • the heat exchanger unit 5, 6 integrated in the collector functions as an internal heat exchanger between the refrigerant flowing on the high pressure side of the refrigerant circuit, which in this case represents the first heat transfer medium M1, and the refrigerant flowing on the low pressure side, which in this case is the second heat transfer medium M2 represents.
  • the collector part of the assembly connects to an evaporator with the collecting container 2 and passes into the internal heat exchanger 5, 6, while the latter is on the high pressure side between a condenser or gas cooler and an expansion valve.
  • the first heat transfer medium M1 can also be passed through the associated first flow channel in the opposite direction from that shown, in which case it then flows downwards through the coiled tubing 5 in direct current to the second heat transfer medium M2 in the spiral space 6 , ie the integrated heat exchanger unit works in this case on the direct current principle.
  • the turns of the tube coil 5 lie not only linearly on their radial inside but also flat against the outer wall of the collecting container, which on the one hand facilitates the fluid tightness of this connection, which is not absolutely necessary, but is generally desirable, and on the other hand improves heat transfer between that in the collecting container 2a temporarily stored and extracted from this heat transfer medium on the one hand and the heat transfer medium passed through the coiled tubing 5 on the other hand.
  • an outside profiling of the coiled tubing can be provided in order to increase its heat-transferring surface.
  • FIG. 4 shows an example of such a tubular coil 5a with an enlarged surface on the outside.
  • the increased heat transfer surface also allows a higher flow rate of the heat transfer media without reducing the heat transfer performance.
  • Fig. 5 shows a further collector-heat exchanger assembly, which is modified compared to those of Figs. 1 and 2 in that no intermediate floor is provided. Insofar as there are corresponding functional elements, they are provided with the same reference numerals as in FIG. 1, so that reference can be made to that of FIG. 1 for their description.
  • the collecting container 2 sits in this example directly on a flat floor 1c of a modified collector housing V.
  • the inlet connection 5b for the coiled tubing 5 is carried out, while the outlet connection 8 for the second heat transfer medium M2 is inserted into a second bore in the base 1c and opens into the lower end region of the spiral space 6, with which the one also or several oil suction bores 9 which are introduced into the collecting container side wall.
  • FIG. 6 shows an integrated collector-heat exchanger assembly, in which a collector housing 10 is provided, which delimits an internal collecting space 11 when an independent collecting container is omitted.
  • a coaxial tubular coil 12 which contains a radially inner channel 12a and a radially outer channel 12b.
  • the coaxial tube coil 12 is shortened at its two end sections, bent over into an inlet connection 12c and an outlet connection 12d, in its radially outer channel 12b in such a way that it respectively opens out inside the collector housing 10, while the radially inner channel 12a emerges on both sides from the Collector housing 10 is brought out.
  • the outer coaxial tube duct 12b opens into a discharge space 14, which is separated from the collecting space 11 above by an intermediate floor 12 and which is delimited at the bottom by a housing base 10a, into which an outlet connection 15 is introduced.
  • the inner coaxial tube channel 12a forms the flow channel for the first heat transfer medium MI
  • the outer coaxial tube channel 12b forms the flow channel for the second heat transfer medium M2 and is in thermal contact with the radially inner flow channel 12a along its entire, modified flow profile.
  • the coaxial tube is made of a highly thermally conductive material.
  • the coaxial tube coil 12 thus forms the heat exchanger unit integrated in the collector housing 10, in which the two heat transfer media M1, M2 are preferably in countercurrent, alternatively in cocurrent, in heat-transferring connection with one another.
  • the second heat transfer medium M2 is introduced into the collecting space 11 via a side inlet 16.
  • the second heat transfer medium M2 can, as indicated by dashed lines, also be introduced into the collecting space 11 via an inlet connection 16a provided on the upper side of the housing.
  • the coaxial tube is provided with one or more oil suction bores 17, via which accumulated viscous fluid can be entrained in the desired amount by the second heat transfer medium M2 flowing in the outer coaxial tube channel 12b and drawn off from the collecting space 11.
  • the second heat transfer medium M2 is preferably sucked into the vaporized or gaseous state in the upper collecting space area in the outer coaxial tube channel 12b and leaves it at its opposite, lower end, from where it then arrives in the exhaust chamber 14 and from there out of the collector housing 10.
  • FIGS. 1 to 5 are in an analogous manner with the same properties and advantages, for example for a motor vehicle air conditioning system usable, as indicated for the examples of FIGS. 1 to 5 described above.
  • FIG. 7 shows a completely extruded coaxial tube 18 with a one-piece inner channel 12a and an outer channel 12b consisting of several parallel, circumferentially spaced channel branches.
  • FIG. 8 shows a coaxial tube 19 which is made in two parts from a thick-walled high-pressure tube 19a and a thin-walled cladding tube 19b.
  • the high-pressure pipe 19a contains the inner channel 12a and is provided on the outside with spacing ribs 20, which preferably lie in a fluid-tight manner against the inner surface of the cladding tube 19b, so that an outer channel 12b, which again consists of several parallel branches, is formed.
  • the spacer webs 22 are preferably fluid-tight against the high-pressure pipe 21a, so that in turn a plurality of parallel channel branches forming the outer flow channel 12b are formed.
  • the outer channel 12b can be shortened on both sides compared to the inner channel 12a, as mentioned, by machining, this can alternatively be achieved in the case of the coaxial tubes 19, 21 of FIGS. 8 and 9, that a shorter outer sheath compared to the inner high-pressure tube is used.
  • FIG. 10 shows a variant of the assembly of FIG. 6, elements which are functionally the same again being provided with the same reference numerals and reference is made to the description of FIG. 6.
  • 10 are characteristically all four Inlet and outlet connections for introducing and discharging the two heat transfer media MM, M2 into and out of the collector housing 10 are jointly provided on the upper side 10b thereof.
  • the inner coaxial tube channel 12a is bent at its lower end in the extraction space 14 and is guided to the upper side 10b of the housing 10 through a straight-line inlet connection 23 which leads through the intermediate base 13 and the collecting space 11.
  • a rectilinear suction connection 24 which penetrates the collecting space 11 and the intermediate floor 13 as far as the discharge space 14, is introduced into the upper side 10b of the housing, via which the second heat transfer medium M2 coming out of the collecting space 11 and through the converted outer coaxial tube channel 12b into the discharge space 14 is directed upwards is withdrawn through the collector housing 10.
  • the second heat transfer medium M2 is supplied to the collecting space 11 via an inlet connection 25 likewise inserted into the upper side 10b of the housing, which ends on the collecting space side with a tangential curve 25a.
  • the resulting tangential supply of the second heat transfer medium M2, e.g. of refrigerant from an air conditioning system on the low-pressure side into the collecting space 11 proves to be advantageous, since the resulting rotating flow e.g. a desired separation of refrigerant and entrained oil due to their different densities.
  • the assembly of FIG. 10 is particularly suitable for applications in which it is desirable or necessary to be able to access all connections of the integrated collector-heat exchanger assembly from one side.
  • FIG. 12 shows a further variant of the assembly of FIG. 6, the same reference numerals being used again for functionally identical elements and reference is made to the above description of FIG. 6.
  • the coaxial tube used in the integrated collector-heat exchanger assembly of FIG. 12 is bent at its upper end to a U-shaped coaxial tube section 27 following its heat-transferring coil region 12, which returns to the lower collecting chamber region and from there is led up again through the collector housing 10.
  • an oil suction bore 28 is again provided, which connects the lower collecting space region to the outer coaxial tube channel 12b.
  • the U-shaped coaxial tube section 27 increases the heat transfer active flow length of the integrated heat exchanger unit formed by the coaxial tube.
  • the invention provides an integrated collector-heat exchanger assembly, in which a collector and a heat exchanger are integrated in a common assembly with few components in a compact design with little effort.
  • the structural unit can be produced by welded connections alone, without additional soldered connections being necessary. Accordingly, there are no problems in this case that excess flux and solder flake off during operation and lead to malfunctions, for example in a refrigerant circuit, so that in the present case there is a high degree of internal cleanliness of the flow channels.
  • the integrated collector-heat exchanger assembly according to the invention is particularly suitable for use in motor vehicle air conditioning systems, especially also for those with the refrigerant C0 2 .
  • the heat exchanger unit here forms an internal heat exchanger integrated in the low-pressure collector.
  • the high-pressure refrigerant on the back is passed through the collector housing in a pipe designed for a correspondingly high pressure, so that no soldering or welding connection of the structural unit is loaded with the high-pressure refrigerant pressure.
  • the collector housing is then only loaded with the low-pressure refrigerant pressure and can therefore be made with a relatively small wall thickness.
  • the forcibly helical flow guide for both heat transfer media in the heat exchanger unit results in a high heat transfer capacity given a given, compact design, which can be further increased by countercurrent guide of the two media.
  • the heat transfer performance can be further improved by profiling the coiled tubing and / or a possible collecting container.
  • Another advantage of the compact design is that essentially the entire collector housing can be used for the heat exchanger unit.
  • the intermediate floor which may be provided can be quite thin, since there is a similar pressure on both sides. For this reason, the pipe section passed through the intermediate floor does not necessarily have to be welded to the intermediate floor, it may be sufficient to simply push it
  • the unit can be manufactured with a low weight. External leaks can be easily remedied from the outside. Leakages between the high and low pressure sides at connection points, as stated, cannot occur in the collector housing due to the design.
  • the inlet and outlet connections can be placed at practically any desired location on the collector be placed so that the conditions prevailing in the respective application can be taken into account well.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

L'invention concerne une unité collecteur-échangeur de chaleur intégrée comportant un corps de collecteur (1) dans lequel se trouvent une chambre collectrice (2) et une unité d'échange de chaleur comportant deux canaux d'échange de chaleur (5, 6) en contact thermique. Un canal d'échange de chaleur (5) constitue une partie d'un premier canal d'écoulement s'étendant, de façon hélicoïdale, d'une entrée du corps à une sortie du corps, dans le corps de collecteur, et l'autre canal d'échange de chaleur (6), le second, constitue une partie d'un second canal d'écoulement qui s'étend entre la chambre collectrice et un raccordement du corps. Selon l'invention, le second canal d'échange de chaleur (6) s'étend également de façon hélicoïdale, ses spires étant respectivement en contact avec au moins une spire adjacente du premier canal d'échange de chaleur (5). Cette unité peut être utilisée, par exemple, dans des installations de climatisation pour véhicules automobiles.
EP99966865A 1999-02-01 1999-12-15 Unite collecteur-echangeur de chaleur integree Withdrawn EP1068478A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19903833 1999-02-01
DE19903833A DE19903833A1 (de) 1999-02-01 1999-02-01 Integrierte Sammler-Wärmeübertrager-Baueinheit
PCT/DE1999/003989 WO2000046558A1 (fr) 1999-02-01 1999-12-15 Unite collecteur-echangeur de chaleur integree

Publications (1)

Publication Number Publication Date
EP1068478A1 true EP1068478A1 (fr) 2001-01-17

Family

ID=7895973

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99966865A Withdrawn EP1068478A1 (fr) 1999-02-01 1999-12-15 Unite collecteur-echangeur de chaleur integree

Country Status (8)

Country Link
US (1) US6298687B1 (fr)
EP (1) EP1068478A1 (fr)
JP (1) JP4107461B2 (fr)
AU (1) AU2277200A (fr)
CA (1) CA2326558A1 (fr)
DE (1) DE19903833A1 (fr)
FR (1) FR2789159B1 (fr)
WO (1) WO2000046558A1 (fr)

Families Citing this family (66)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19944950B4 (de) 1999-09-20 2008-01-31 Behr Gmbh & Co. Kg Klimaanlage mit innerem Wärmeübertrager
DE19944951B4 (de) * 1999-09-20 2010-06-10 Behr Gmbh & Co. Kg Klimaanlage mit innerem Wärmeübertrager
CA2297598C (fr) 2000-01-28 2003-12-23 Ki-Sun Jason Ryu Accumulateur de systeme de conditionnement d'air
DE10053000A1 (de) * 2000-10-25 2002-05-08 Eaton Fluid Power Gmbh Klimaanlage mit innerem Wärmetauscher und Wärmetauscherrohr für einen solchen
JP3728722B2 (ja) * 2000-11-15 2005-12-21 株式会社カントー 浴槽用の熱交換器
US6463757B1 (en) * 2001-05-24 2002-10-15 Halla Climate Controls Canada, Inc. Internal heat exchanger accumulator
US6681597B1 (en) 2002-11-04 2004-01-27 Modine Manufacturing Company Integrated suction line heat exchanger and accumulator
US20040118148A1 (en) * 2002-12-24 2004-06-24 Ti Group Automotives Systems, Llc Accumulator with inlet diffuser\diverter
DE10313343B4 (de) * 2003-03-25 2005-12-15 Valeo Klimasysteme Gmbh Sammler
DE10322028B4 (de) * 2003-05-16 2005-03-10 Wieland Werke Ag Kälteanlage mit Wärmeaustauscher
JP2005106339A (ja) * 2003-09-29 2005-04-21 Calsonic Kansei Corp 熱交換器、および、熱交換器を用いたヒートポンプ式空調装置
US20050081559A1 (en) * 2003-10-20 2005-04-21 Mcgregor Ian A.N. Accumulator with pickup tube
US6848268B1 (en) 2003-11-20 2005-02-01 Modine Manufacturing Company CO2 cooling system
US7261151B2 (en) * 2003-11-20 2007-08-28 Modine Manufacturing Company Suction line heat exchanger for CO2 cooling system
JP2005226913A (ja) * 2004-02-12 2005-08-25 Sanyo Electric Co Ltd 遷臨界冷媒サイクル装置
CN100529598C (zh) * 2004-07-09 2009-08-19 谷俊杰 制冷系统
FR2875894B1 (fr) * 2004-09-24 2006-12-15 Valeo Climatisation Sa Dispositif combine d'echangeur de chaleur interne et d'accumulateur pour un circuit de climatisation
DE102004050409A1 (de) * 2004-10-15 2006-04-27 Valeo Klimasysteme Gmbh Akkumulator mit internem Wärmetauscher für eine Klimaanlage
JP2006273049A (ja) 2005-03-28 2006-10-12 Calsonic Kansei Corp 車両用空調装置
US20060225459A1 (en) * 2005-04-08 2006-10-12 Visteon Global Technologies, Inc. Accumulator for an air conditioning system
DE102005058153B4 (de) * 2005-04-22 2007-12-06 Visteon Global Technologies Inc., Van Buren Wärmeübertrager mit Mehrkanalflachrohren
DE102005021464A1 (de) * 2005-05-10 2006-11-16 Modine Manufacturing Co., Racine Vorrichtung zur Zwischenkühlung
DE102005021787A1 (de) * 2005-05-11 2006-11-16 Modine Manufacturing Co., Racine Vorrichtung zur Behandlung des Kältemittels
US20070000263A1 (en) * 2005-06-30 2007-01-04 Caterpillar Inc. Method and system for packaging HVAC components
DE102006017432B4 (de) * 2006-04-06 2009-05-28 Visteon Global Technologies Inc., Van Buren Innerer Wärmeübertrager mit kalibriertem wendelförmigen Rippenrohr
DE102006031197B4 (de) * 2006-07-03 2012-09-27 Visteon Global Technologies Inc. Innerer Wärmeübertrager mit Akkumulator
DE102006035784B4 (de) * 2006-08-01 2020-12-17 Gea Refrigeration Germany Gmbh Kälteanlage für transkritischen Betrieb mit Economiser und Niederdruck-Sammler
DE102006051687A1 (de) * 2006-10-30 2008-05-08 Visteon Global Technologies Inc., Van Buren Mechanische Verbindung eines Wärmeübertragerrohrs
DE102007039753B4 (de) * 2007-08-17 2017-12-21 Hanon Systems Kältemittelakkumulator für Kraftfahrzeugklimaanlagen
CN101398240B (zh) * 2007-09-29 2011-01-19 浙江三花制冷集团有限公司 一种回油装置和气液分离器
EP2216609B1 (fr) 2007-11-02 2016-03-30 Panasonic Intellectual Property Management Co., Ltd. Système d'alimentation en eau chaude
FR2930018B1 (fr) * 2008-04-15 2010-04-16 Valeo Systemes Thermiques Dispositif combine comprenant un echangeur de chaleur interne et un accumulateur.
WO2009133708A1 (fr) * 2008-04-30 2009-11-05 ダイキン工業株式会社 Echangeur de chaleur et système de conditionnement d’air
WO2009133712A1 (fr) * 2008-04-30 2009-11-05 ダイキン工業株式会社 Système d’échangeur thermique et de climatisation
CN100578119C (zh) * 2008-05-17 2010-01-06 苏权兴 热交换器
DE102008028853A1 (de) * 2008-06-19 2009-12-24 Behr Gmbh & Co. Kg Integrierte, einen Sammler und einen inneren Wärmeübertrager umfassende Baueinheit sowie ein Verfahren zur Herstellung der Baueinheit
CN102472594B (zh) * 2009-11-24 2014-08-20 M技术株式会社 热交换器
US8931305B2 (en) * 2010-03-31 2015-01-13 Denso International America, Inc. Evaporator unit
EP2676085B1 (fr) 2011-02-14 2018-09-19 Carrier Corporation Appareil de séparation de phases liquide et vapeur
AU2012229281B9 (en) * 2011-03-17 2015-08-27 Société des Produits Nestlé S.A. Systems and methods for heat exchange
KR101352260B1 (ko) 2012-05-14 2014-01-17 포스코에너지 주식회사 연료전지용 가습 열교환기
US10107525B2 (en) 2011-12-29 2018-10-23 Steve Kapaun Geothermal heating and cooling system
CN103453787B (zh) * 2012-05-29 2016-08-03 祥景精机股份有限公司 热交换装置
DE102012017405A1 (de) * 2012-09-03 2014-03-06 GM Global Technology Operations, LLC (n.d. Ges. d. Staates Delaware) Interner Wärmetauscher für eine Kraftfahrzeug-Klimaanlage
KR101249721B1 (ko) * 2012-09-05 2013-04-02 주식회사 화승알앤에이 열교환용 이중관
JP5719468B1 (ja) * 2014-06-20 2015-05-20 日本ガス開発株式会社 熱交換器
DE102014220403A1 (de) * 2014-10-08 2016-04-14 Mahle International Gmbh Verfahren zur Montage einer Wärmetauschereinrichtung und Wärmetauschereinrichtung
CN104697254B (zh) * 2015-03-27 2017-07-28 广东美的暖通设备有限公司 储液罐
US11255580B2 (en) * 2015-08-20 2022-02-22 Lennox Industries Inc. Carbon dioxide cooling system with subcooling
DE102015217634A1 (de) * 2015-09-15 2017-05-11 Mahle International Gmbh Vorrichtung einer Klimaanlage mit einem inneren Wärmetauscher und einem integrierten Sammler
FR3051037B1 (fr) * 2016-05-04 2018-11-09 Valeo Systemes Thermiques Echangeur thermique compact
JP2017219212A (ja) * 2016-06-03 2017-12-14 サンデンホールディングス株式会社 内部熱交換器一体型アキュムレータ及びこれを用いた冷凍サイクル
CN105928390B (zh) * 2016-06-08 2018-10-16 佛山市顺德区拓球明新空调热泵实业有限公司 一种耐压式高效换热装置
JP6889541B2 (ja) * 2016-11-08 2021-06-18 サンデンホールディングス株式会社 内部熱交換器一体型アキュムレータ及びこれを用いた冷凍サイクル
DE102017218973A1 (de) * 2017-10-24 2019-04-25 Hanon Systems Gegenstrom-Wärmeübertrager
EP3757485B1 (fr) 2018-02-24 2023-08-02 Zhejiang Sanhua Intelligent Controls Co., Ltd. Séparateur gaz-liquide
US11009275B2 (en) * 2018-10-12 2021-05-18 Rheem Manufacturing Company Compressor protection against liquid slug
KR20220024833A (ko) * 2019-06-25 2022-03-03 어플라이드 머티어리얼스, 인코포레이티드 진공 포어라인에서의 입자 수집을 위한 고효율 트랩
CN112229108B (zh) * 2019-12-18 2022-09-23 绍兴三花新能源汽车部件有限公司 气液分离器
CN112229107B (zh) * 2019-12-18 2022-09-23 绍兴三花新能源汽车部件有限公司 气液分离器
CN113739457A (zh) * 2020-05-29 2021-12-03 绍兴三花新能源汽车部件有限公司 一种热交换器以及气液分离器
FR3111966A1 (fr) * 2020-06-30 2021-12-31 Valeo Systemes Thermiques Bouteille séparatrice pour circuit de fluide réfrigérant.
CN112985109B (zh) * 2021-03-02 2022-08-16 江西益普生药业有限公司 一种甘油高效快速冷却装置
CN113266968A (zh) * 2021-04-28 2021-08-17 珠海格力电器股份有限公司 储液罐、制冷剂转移装置和制冷系统
CN113739601B (zh) * 2021-08-06 2023-03-14 澳柯玛股份有限公司 一种换热器结构及其制冷系统
CN115265234B (zh) * 2022-06-24 2023-05-16 广州五所环境仪器有限公司 环境测试设备及换热装置

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1254519A (en) * 1917-10-06 1918-01-22 Benjamin S Mcclellan Refrigerating apparatus.
US2121253A (en) * 1936-04-06 1938-06-21 Kold Hold Mfg Company Heat exchanger and accumulator
DE859479C (de) * 1951-01-17 1952-12-15 Brown Kaelteanlage mit Entoelung des Verdampfers
US3131553A (en) * 1962-04-12 1964-05-05 Ross Anthony John Refrigeration system including condenser heat exchanger
US3163998A (en) * 1962-09-06 1965-01-05 Recold Corp Refrigerant flow control apparatus
DE1451001A1 (de) * 1964-03-17 1969-05-14 Ross Anthony John Verfahren und Vorrichtung zum Betreiben eines Kaeltemaschinenprozesses
US3621673A (en) * 1969-12-08 1971-11-23 Trane Co Air-conditioning system with combined chiller and accumulator
US3765193A (en) * 1970-06-12 1973-10-16 Rech Dev Technologiques Soc Method and apparatus for the circular knitting of hook and loop fastener elements
US3955375A (en) * 1974-08-14 1976-05-11 Virginia Chemicals Inc. Combination liquid trapping suction accumulator and evaporator pressure regulator device including a capillary cartridge and heat exchanger
US4217765A (en) * 1979-06-04 1980-08-19 Atlantic Richfield Company Heat exchanger-accumulator
DE3127317A1 (de) * 1981-05-15 1983-01-27 Erich Schultze KG, 1000 Berlin "anlagen-waermeaustauscher fuer kaelteanlagen"
DE3119440A1 (de) * 1981-05-15 1982-12-09 Erich Schultze KG, 1000 Berlin "anlagen-waermeaustauscher fuer kaelteanlagen"
CA1291113C (fr) * 1985-03-22 1991-10-22 Keith Stuart Mclaren Echangeur thermique
US5075967A (en) * 1990-08-03 1991-12-31 Bottum Edward W Method of assembing a suction accumulator
US5233842A (en) * 1992-07-01 1993-08-10 Thermo King Corporation Accumulator for refrigeration system
KR0152286B1 (ko) * 1992-10-22 1998-11-02 윤종용 냉난방겸용 공기조화기 및 그 제어방법
DE9303177U1 (de) * 1993-03-04 1993-04-29 Pan, Chi Chuan, Taipeh/T'ai-pei Trennvorrichtung für eine Fahrzeugklimaanlage
DE19635454B4 (de) * 1996-08-31 2010-06-17 Behr Gmbh & Co. Kg Sammler-Wärmeübertrager-Baueinheit und damit ausgerüstete Klimaanlage

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0046558A1 *

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FR2789159A1 (fr) 2000-08-04
AU2277200A (en) 2000-08-25
WO2000046558A1 (fr) 2000-08-10
CA2326558A1 (fr) 2000-08-10
JP2000227289A (ja) 2000-08-15
FR2789159B1 (fr) 2006-02-03
US6298687B1 (en) 2001-10-09
DE19903833A1 (de) 2000-08-03

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