EP1790931A2 - Ensemble coaxial ou tube dans tube, en particulier pour échangeur de chaleur - Google Patents

Ensemble coaxial ou tube dans tube, en particulier pour échangeur de chaleur Download PDF

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Publication number
EP1790931A2
EP1790931A2 EP06022998A EP06022998A EP1790931A2 EP 1790931 A2 EP1790931 A2 EP 1790931A2 EP 06022998 A EP06022998 A EP 06022998A EP 06022998 A EP06022998 A EP 06022998A EP 1790931 A2 EP1790931 A2 EP 1790931A2
Authority
EP
European Patent Office
Prior art keywords
tube
coaxial
arrangement according
ribs
pressure side
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Withdrawn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
EP06022998A
Other languages
German (de)
English (en)
Other versions
EP1790931A3 (fr
Inventor
Julian Dipl.-Ing. Helfen
Wolfgang Dipl.-Ing. Seewald
Karl-Heinz Dipl.-Ing. Staffa
Uli Dipl.-Ing. Vedder
Christoph Dipl.-Ing. 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.)
Mahle Behr GmbH and Co KG
Original Assignee
Behr GmbH and Co KG
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 Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP1790931A2 publication Critical patent/EP1790931A2/fr
Publication of EP1790931A3 publication Critical patent/EP1790931A3/fr
Withdrawn legal-status Critical Current

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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
    • F28D7/10—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 arranged one within the other, e.g. concentrically
    • F28D7/106—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 arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • 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
    • 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
    • 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

Definitions

  • the invention relates to a coaxial tube or a tube-in-tube arrangement according to the preamble of claim 1.
  • From the EP 1 202 016 A2 is a one-piece heat exchanger tube with a multi-chamber profile known, according to which a plurality of outer channels are provided around a central channel.
  • the outer channels are divided by intermediate walls which extend in the radial direction.
  • projections are provided which extend into the central channel. These projections serve to reduce the cross-sectional area and thus increase the flow velocity.
  • the cross-sectional area of the central channel is significantly smaller than the sum of the cross-sectional areas of the outer channels.
  • the ribs / projections may also be helical, wherein constant, changing or alternating gradients may be provided.
  • the inner channel is used as a high pressure side, the outer channels as a low pressure side.
  • Spiral-shaped webs which separate the outer channels from each other, and the provision of turbulence elements on the webs are from the DE 199 44 951 A1 in turn, in turn, the inner channel, the high pressure side and the outer channels form the low pressure side.
  • the cross-sectional area of the inner channel is smaller than the sum of the cross-sectional areas of the outside of the inner channel disposed outer channels.
  • a coaxial tube or a tube-in-tube arrangement for the separate line of at least two media, which is preferably refrigerant, is provided, whose pressure level differs, wherein in the coaxial tube or the tube-in-tube arrangement the Low pressure side is arranged in the radial direction closer to the central longitudinal axis than the high pressure side.
  • the twisted arrangement, the inner tube may be formed with a smaller wall thickness, which reduces the total weight, the material requirements and thus the cost of the coaxial tube or the tube-in-tube arrangement.
  • the dimensions can be slightly reduced, which also reduces the heat input from the outside into the system and thus the performance can be increased.
  • the term "pipe” is to be interpreted in the following very broad and refers not only to round cross-sections, but in particular also oval, rounded rectangular or any other cross-sections.
  • the tube may also be two tubes arranged inside one another which do not have any have direct connections (tube-in-tube arrangement).
  • positioning elements for the inner tube may be provided in the outer tube, such as provided on the outer and / or inner tube, radially inwardly or outwardly projecting ribs to optionally ensure a coaxial arrangement.
  • the arrangement of the inner tube or of the inner region in the outer tube is preferably coaxial, but does not have to be, so that eccentric arrangements are also possible.
  • several inner tubes may be provided, which are connected by means of several sleeves.
  • the inner tube may also be soldered or otherwise connected to the outer tube in the contact regions.
  • the free flow cross section of the high pressure side is preferably smaller overall than the free flow cross section of the low pressure side.
  • the free flow cross sections differ in such a way that the free flow cross section of the.
  • High pressure side is preferably at most half as large and preferably at least a quarter as large, more preferably about one-third +/- 10% is as large as the free flow area of the low pressure side.
  • the outer diameter of the outer tube is preferably 10 to 18 mm, in particular 12 to 16 mm.
  • the inner diameter of the inner tube is preferably 6 to 12 mm, in particular 8 to 10 mm.
  • the width of the ribs between the inner and outer tubes is preferably 0.3 to 0.8 mm, particularly preferably 0.4 to 0.7 mm.
  • the inlet openings of the two media are arranged on different sides of the coaxial tube or the tube-in-tube arrangement, so that the coaxial tube or the tube-in-tube arrangement is flowed through in countercurrent operation.
  • the outer tube is preferably subdivided into at least six, in particular at least ten, in particular preferably at least twelve subchannels and a maximum of twenty, preferably a maximum of sixteen subchannels.
  • This subdivision allows optimal strength properties of the tube, combined with a large heat transfer area for the medium flowing in the outer region.
  • the wall thickness of the outer wall is preferably greater than the wall thickness of the wall between the outer tube and the inner tube. Due to the greater pressure difference from the outer tube to the environment than from the outer tube to the inner region, the wall thickness to the inner tube can be made smaller, so that a material saving is possible. Is - as in conventional coaxial tubes - the maximum pressure in the inner tube provided, the outer tube, however, must also be able to withstand the corresponding pressure, which is why it should have a corresponding wall thickness and therefore designed in conventional coaxial tubes according to the inner tube, making the coaxial tube heavier and thus more expensive than a coaxial tube according to the invention. Incidentally, an improvement in the heat transfer performance can be achieved by the thinner wall.
  • the width of the ribs or webs, which divide the individual sub-channels of the outer tube, is preferably smaller than the wall thickness of the wall of the outer tube, which can also save material.
  • the width of the webs, which divide the individual sub-channels of the outer tube greater than or equal to the wall thickness of the wall between the outer tube and the inner tube.
  • At least one turbulence generator is preferably provided, which is preferably an inner tube coil.
  • at least one inner rib and / or at least one chord which in this case also means a web extending in the radial direction from one to the other side of the inner wall, may be provided in the inner tube.
  • At least one of the turbulence generators and / or at least one of the inner ribs and / or at least one of the webs and / or at least one of the ribs between the inner and outer tubes is preferably inclined with respect to arranged the pipe axis.
  • the slope can also change over the total length of the tube, as well as the direction of rotation.
  • At least one of the turbulence generators and / or at least one of the inner ribs and / or at least one of the webs and / or at least one of the ribs between the inner and outer tubes is formed obliquely with respect to the tube longitudinal axis with such a pitch that a 360 ° rotation over a tube length of 15 to 35 mm, in particular from 20 to 25 mm, takes place.
  • the length of at least one of the turbulence generators and / or at least one of the inner ribs and / or at least one of the webs and / or at least one of the ribs between the inner and outer tube is 0.3 times to 0, 5 times, preferably equal to 0.4 times the tube length. It is also conceivable, however, for the length of at least one of the aforementioned devices to correspond essentially to the tube length.
  • the inflow of the low-pressure medium is preferably carried out substantially coaxially, for which purpose the corresponding connecting piece is designed accordingly.
  • a coaxial tube according to the invention or a tube-in-tube arrangement according to the invention can be used in particular for heat exchangers, preferably for motor vehicle air conditioners, particularly preferably for high-pressure air conditioning systems (such as in R744 air conditioners) of motor vehicles, however, other applications are also possible.
  • heat exchangers preferably for motor vehicle air conditioners, particularly preferably for high-pressure air conditioning systems (such as in R744 air conditioners) of motor vehicles, however, other applications are also possible.
  • Particularly preferred is the use as a so-called inner heat exchanger or internal heat exchanger.
  • the refrigerant used usually behaves, even if it is at least partially in the gaseous state, due to the usually very high density similar to a fluid. In particular, this makes it possible, for example, by use a turbulence generator to increase the heat transfer between the channels.
  • the proposed application of high or low pressure may prove to be particularly advantageous.
  • the high pressure usually has a higher temperature than the low pressure, so that particularly good additional heat energy can be dissipated from the high-pressure side refrigerant to the environment.
  • a heat exchanger 1 of which only a cross-section is shown in Fig. 1, but which may be formed in principle, as shown in Fig. 2 with an enlarged, shown another cross-section provided.
  • This heat exchanger 1 serves the heat exchange of a first medium and a second medium.
  • the first medium flows through the inner region 2 of an inner tube 3 and the second medium through the outer region 4 which between an outer tube 5 and the inner tube 3 is formed.
  • the inner tube 3 and the outer tube 5 together with them in the radial direction in the longitudinal direction continuously extending ribs 6 are integrally extruded as a coaxial tube 7 made of an aluminum alloy.
  • the outer diameter of the coaxial tube 7 is present 16 mm, the wall thickness of the outer tube 5 0.8 mm, the wall thickness of the inner tube 3 0.6 mm, the rib width 0.7 mm and the inner diameter 11 mm.
  • the free cross-sectional area of the inner tube 3 is about 95 mm 2
  • the sum of the free cross-sectional areas of the outer channels is about 35 mm 2 , that is about 60% smaller than that of the inner tube. 3
  • 7 connecting components 8 are provided at both ends of the coaxial tube, via which the media, which by the inner region 2 and the outer region 4 present in the Countercurrent flow, separately from each other or be derived.
  • a higher pressure is applied to the outer tube 5 (high pressure side) than to the inner tube 3 (low pressure side).
  • the operating pressure on low pressure side (low pressure p N ) is according to the present embodiment about 130 bar, the corresponding bursting pressure 264 bar, and the operating pressure on the high pressure side (high pressure p H ) is about 160 bar, the corresponding bursting pressure 352 bar.
  • the mentioned pressure values refer in particular to the use of CO 2 (R744) as refrigerant.
  • an improved flow of the low-pressure refrigerant can be realized via the corresponding connection piece 8; in particular, as shown in FIG. 3, a deflection-free flow of the low-pressure refrigerant is provided in the direction of the longitudinal axis of the inner tube, whereby the pressure loss can be reduced and thereby the cooling capacity can be improved.
  • the flow of the high-pressure refrigerant takes place in the radial direction with respect to the longitudinal axis of the coaxial tube. 1
  • a turbulence generator 11 in the form of a helix is provided in the interior of the inner tube 3, which can be arranged in the coaxial tube bend with the same.
  • the pitch of the helix in this case corresponds approximately to twice the inner diameter of the inner tube 3, that is about 22 mm, and is constant over the entire length of the coaxial tube.
  • the helix deflects the refrigerant flowing in the inner tube, so that no laminar flow is formed in the wall region, resulting in improved mixing and improved heat exchange.
  • the pitch of the helix changes over the length of the coaxial tube and / or changes the direction of rotation of the turning, wherein multiple changes can be provided.
  • Fig. 4 shows a second embodiment of a coaxial tube, wherein in the inner tube 3 both four evenly distributed over the circumference inner ribs 21 are provided with a length of about half the radius and two perpendicular to each other and at a gap to the inner ribs 21 webs 22 which the Divide the interior into four separate areas. These internals in the inner tube 3 enlarge the heat transfer surface and therefore improve the heat exchange.
  • the coaxial tube is extruded turned, i. the ribs, inner ribs and webs run helically, in this case with a constant pitch.
  • the coaxial tube is in turn rotated extruded, but changed with changing Rotational speed, so that the pitch of the ribs, inner ribs and webs changed over the length of the coaxial tube.
  • two tendons are provided opposite one another in the inner tube of the coaxial tube instead of the webs extending in the radial direction.
  • a third embodiment provides a tube-in-tube arrangement as a coaxial tube, wherein the outer tube ribs and the inner tube inner ribs and webs, and the outer tube is soldered at the end of the ribs to the inner tube, resulting in a configuration according to the second embodiment ,
  • a first variant of the third embodiment provides that the two tubes are extruded rotated in different directions, i. that the flow paths of the refrigerant flowing in the interior are rotated on the one hand in countercurrent operation and on the other hand in different directions, whereby the heat exchange is improved.
  • the rotations of the two tubes have mutually different slopes over the length, so that, for example, a smaller pitch can be provided in the inflow area and a larger pitch in the outflow area.

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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)
EP06022998.6A 2005-11-25 2006-11-06 Ensemble coaxial ou tube dans tube, en particulier pour échangeur de chaleur Withdrawn EP1790931A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200510056651 DE102005056651A1 (de) 2005-11-25 2005-11-25 Koaxialrohr oder Rohr-in-Rohr-Anordnung, insbesondere für einen Wärmetauscher

Publications (2)

Publication Number Publication Date
EP1790931A2 true EP1790931A2 (fr) 2007-05-30
EP1790931A3 EP1790931A3 (fr) 2013-05-01

Family

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EP06022998.6A Withdrawn EP1790931A3 (fr) 2005-11-25 2006-11-06 Ensemble coaxial ou tube dans tube, en particulier pour échangeur de chaleur

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EP (1) EP1790931A3 (fr)
DE (1) DE102005056651A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1845326A2 (fr) 2006-04-13 2007-10-17 Eaton Fluid Power GmbH Echangeur thermique de machines frigorifiques interne
WO2009062721A3 (fr) * 2007-11-13 2010-03-18 Tracto-Technik Gmbh & Co. Kg Système géothermique
CN102667389A (zh) * 2009-09-28 2012-09-12 康蒂泰克屈纳有限及两合公司 尤其用于机动车辆空调设备的内部热交换器
CN103375656A (zh) * 2012-04-20 2013-10-30 Ti汽车海德堡有限公司 连接器特别是快速连接器
EP2287507A3 (fr) * 2009-07-07 2014-10-01 ELB-Form GmbH Tuyau à double paroi, son procédé de fabrication et d'utilisation
CN108106174A (zh) * 2017-12-08 2018-06-01 广东纽恩泰新能源科技发展有限公司 微通道管道换热器
CN114279249A (zh) * 2021-12-29 2022-04-05 思安新能源股份有限公司 一种双通道套管式换热储热结构及其使用方法

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DE102008007226A1 (de) 2008-02-01 2009-08-06 Fränkische Rohrwerke Gebr. Kirchner Gmbh & Co. Kg Verbundrohr mit schraubenförmiger Wellung und dessen Verwendung als Abwasserrohr oder Erdkollektor
DE102011012577A1 (de) * 2011-02-26 2012-08-30 Volkswagen Ag Wärmeaustauschvorrichtung
US10011155B2 (en) * 2016-03-11 2018-07-03 Ford Global Technologies Llc Nested HVAC lines
DE102018111542A1 (de) * 2018-05-15 2019-11-21 Friedhelm Meyer Kältekreislaufvorrichtung und Verfahren zum Betrieb einer Kältekreislaufvorrichtung mit einem Hybridverdampfer
DE102018216275A1 (de) 2018-09-25 2019-09-19 Audi Ag Wärmeübertrager für ein Elektrofahrzeug

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Publication number Priority date Publication date Assignee Title
US6098704A (en) 1997-06-06 2000-08-08 Denso Corporation Heat exchanger having a double pipe construction and method for manufacturing the same
DE19944951A1 (de) 1999-09-20 2001-03-22 Behr Gmbh & Co Klimaanlage mit innerem Wärmeübertrager
EP1202016A2 (fr) 2000-10-25 2002-05-02 Eaton Fluid Power GmbH Installation de climatisation avec échangeur de chaleur interne et tube d'échangeur de chaleur pour une telle installation

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DE10243726B4 (de) * 2002-09-20 2008-03-27 Erbslöh Aluminium Gmbh Wärmetauscher und Verfahren zur Herstellung eines Wärmetauschers sowie stranggepresstes Verbundprofil zur Verwendung in einem solchen Verfahren
US20040089439A1 (en) * 2002-11-07 2004-05-13 Treverton Andrew Clare Tube-to-tube heat exchanger assembly
DE10303595B4 (de) * 2003-01-30 2005-02-17 Visteon Global Technologies, Inc., Dearborn Mehrkanal-Wärmeübertrager- und Anschlusseinheit
JP2005001449A (ja) * 2003-06-10 2005-01-06 Denso Corp 車両用冷凍サイクル装置
JP4679827B2 (ja) * 2003-06-23 2011-05-11 株式会社デンソー 熱交換器
JP4196774B2 (ja) * 2003-07-29 2008-12-17 株式会社デンソー 内部熱交換器
DE102004003325A1 (de) * 2004-01-22 2005-08-18 Valeo Klimasysteme Gmbh Koaxial-Wärmetauscher, Verfahren zur Herstellung eines Koaxial-Wärmetauschers, Verfahren zum Anschließen eines Koaxial-Wärmetauschers und ringförmige Dichtung für einen Koaxial-Wärmetauscher
DE102004050409A1 (de) * 2004-10-15 2006-04-27 Valeo Klimasysteme Gmbh Akkumulator mit internem Wärmetauscher für eine Klimaanlage

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6098704A (en) 1997-06-06 2000-08-08 Denso Corporation Heat exchanger having a double pipe construction and method for manufacturing the same
DE19944951A1 (de) 1999-09-20 2001-03-22 Behr Gmbh & Co Klimaanlage mit innerem Wärmeübertrager
EP1202016A2 (fr) 2000-10-25 2002-05-02 Eaton Fluid Power GmbH Installation de climatisation avec échangeur de chaleur interne et tube d'échangeur de chaleur pour une telle installation

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1845326A2 (fr) 2006-04-13 2007-10-17 Eaton Fluid Power GmbH Echangeur thermique de machines frigorifiques interne
EP1845326A3 (fr) * 2006-04-13 2012-03-28 Eaton Fluid Power GmbH Echangeur thermique de machines frigorifiques interne
WO2009062721A3 (fr) * 2007-11-13 2010-03-18 Tracto-Technik Gmbh & Co. Kg Système géothermique
GB2467280A (en) * 2007-11-13 2010-07-28 Tracto Technik Geothermiesystem
GB2467280B (en) * 2007-11-13 2012-05-30 Tracto Technik Geothermal system
EP2287507A3 (fr) * 2009-07-07 2014-10-01 ELB-Form GmbH Tuyau à double paroi, son procédé de fabrication et d'utilisation
CN102667389A (zh) * 2009-09-28 2012-09-12 康蒂泰克屈纳有限及两合公司 尤其用于机动车辆空调设备的内部热交换器
CN102667389B (zh) * 2009-09-28 2014-04-30 康蒂泰克屈纳有限及两合公司 尤其用于机动车辆空调设备的内部热交换器
CN103375656A (zh) * 2012-04-20 2013-10-30 Ti汽车海德堡有限公司 连接器特别是快速连接器
EP2653770B1 (fr) * 2012-04-20 2018-07-25 TI Automotive (Heidelberg) GmbH Connecteur, en particulier connecteur rapide
CN108106174A (zh) * 2017-12-08 2018-06-01 广东纽恩泰新能源科技发展有限公司 微通道管道换热器
CN114279249A (zh) * 2021-12-29 2022-04-05 思安新能源股份有限公司 一种双通道套管式换热储热结构及其使用方法

Also Published As

Publication number Publication date
DE102005056651A1 (de) 2007-05-31
EP1790931A3 (fr) 2013-05-01

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