EP1217319B1 - Echangeur de chaleur pour le transfert thermique entre un réfrigérant et un mélange eau/glycol - Google Patents

Echangeur de chaleur pour le transfert thermique entre un réfrigérant et un mélange eau/glycol Download PDF

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Publication number
EP1217319B1
EP1217319B1 EP00128034A EP00128034A EP1217319B1 EP 1217319 B1 EP1217319 B1 EP 1217319B1 EP 00128034 A EP00128034 A EP 00128034A EP 00128034 A EP00128034 A EP 00128034A EP 1217319 B1 EP1217319 B1 EP 1217319B1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
heat exchanger
spiral
heat
exchanger according
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.)
Expired - Lifetime
Application number
EP00128034A
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German (de)
English (en)
Other versions
EP1217319A1 (fr
Inventor
Dienhart Bernd
Lorenz-Börnert Marion
Fröhling Jörn
Hoffmann Hanskarl
Heyl Peter Dr.
Kubitz Bernd
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.)
Visteon Global Technologies Inc
Original Assignee
Visteon Global Technologies Inc
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 Visteon Global Technologies Inc filed Critical Visteon Global Technologies Inc
Priority to AT00128034T priority Critical patent/ATE354070T1/de
Priority to EP00128034A priority patent/EP1217319B1/fr
Priority to DE50014069T priority patent/DE50014069D1/de
Publication of EP1217319A1 publication Critical patent/EP1217319A1/fr
Application granted granted Critical
Publication of EP1217319B1 publication Critical patent/EP1217319B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • 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
    • 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
    • F28F1/26—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 being integral with the element
    • 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
    • F28F1/34—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 obliquely
    • F28F1/36—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 obliquely the means being helically wound fins or wire spirals
    • 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
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/12—Safety or protection arrangements; Arrangements for preventing malfunction for preventing overpressure

Definitions

  • the invention relates to a heat exchanger for heat transfer between a refrigerant and a water / glycol mixture.
  • Heat exchangers are apparatuses or components in which an indirect heat transfer takes place. In this case, heat is transferred from a fluid stream of higher temperature to another fluid stream of lower temperature. The two streams flow through the heat exchanger, without mixing, so are spatially separated from each other.
  • the refrigerant circuit is a material cycle in which heat is absorbed in the evaporator with evaporation of the refrigerant and in the condenser, heat is released from the refrigerant.
  • Such heat exchangers are e.g. from documents DE 19808893, DE 19635454, US 3340588, DE 19623259 and EP 0529819.
  • heat exchangers are used according to the preamble of the present invention.
  • Carbon dioxide is increasingly being studied as a refrigerant and the production of such systems is being considered.
  • Carbon dioxide is referred to as a high-pressure refrigerant, since the critical temperature of the carbon dioxide in the range of the ambient temperature (31 ° C) and the associated pressure is significantly higher than that of today's conventional refrigerants (R134a, R290, R212).
  • the maximum occurring high pressure is in systems with carbon dioxide as a refrigerant in a range of 100 to 170 bar, depending on the application of the system.
  • Heat exchangers are already known for the use of the refrigerant carbon dioxide in the refrigeration plant - heat pump process, which operate with very small flow cross sections and capacities in the heat exchangers.
  • the object is achieved with a heat exchanger according to claim 1.
  • the spiral package is structurally designed so that the safety requirements are met by maintaining low flow cross-sections in the refrigerant channels and small filling volume in the spiral package.
  • the spiral packages consist of flat tube with refrigerant channels, wherein the flat tube is wound along its length.
  • the position of winding axis of the spiral pack and cylinder axis of the heat exchanger is identical.
  • the flat tube is advantageously formed with ribs for spacing between adjacent windings and channeling for the heat / cold carrier in the wound state and for enlarging the surface.
  • the advantages of the heat exchanger according to the invention are that in a confined space a heat exchanger is provided, which has a large heat-transferring surface and also by its design meets the safety requirements for use in a circuit with refrigerant.
  • FIG. 1 An advantageous embodiment of the heat exchanger according to the invention is shown in Fig. 1 in longitudinal section.
  • the cylindrical jacket of the heat exchanger 1 is designed as a circular cylinder in the form of a tube which is tapered at its ends to connecting piece 7.
  • In the interior of the heat exchanger 1 is at least one, in the present case three spiral packets 2 are arranged, which are flowed around in order from the heat / brine.
  • the heat exchanger 1 further has connection possibilities for the refrigerant supply 3 and the Refrigerant discharge 4, the heat / refrigerant supply 5 and the heat / refrigerant removal 6 on.
  • the spiral packets 2 are flowed through by a refrigerant and flows around it by a heat / refrigerant, wherein heat is transferred between the high-pressure refrigerant and the heat / refrigerant in the cross-flow or funnelurgi- or cross-direct current.
  • the spiral packages 2 are formed of a flat tube 9 having the width (B) of five to one hundred and twenty millimeters (5 to 120 mm) and the height (H) of one to ten millimeters (1 to 10 mm).
  • the flat tube 9, which has at least one refrigerant channel 10, is flowed through by these refrigerant channels of refrigerant.
  • the spiral packets 2 are formed from wound flat tube 9, which is wound along its length (L) in a double layer.
  • the winding axis 13 of the spiral package 2 is shown in FIG. 1 advantageously in the same position as the cylinder axis 13 of the heat exchanger. 1
  • the flat tube 9 ribs 11 for spacing between adjacent windings within the spiral pack 2 and channel formation for the heat / cold carrier in the wound state and to increase the surface area.
  • the heat exchanger 1 also has a safety device 8 against overpressure, for example in the form of a rupture disk or a safety valve and is equipped at a suitable location with a venting device.
  • a safety device 8 against overpressure for example in the form of a rupture disk or a safety valve and is equipped at a suitable location with a venting device.
  • FIG. 2 a shows the cross section of a heat exchanger 1 with a double-flow refrigerant flow in the spiral pack 2.
  • the double spiral is then flowed through in multiple flutes spirally from inside to outside by refrigerant and exits at the refrigerant discharge 4 from the spiral pack 2 and leaves the heat exchanger 1.
  • FIG. 2 b shows the cross section of a heat exchanger 1 with a single-flow refrigerant flow in the spiral package 2.
  • the double spiral is first flowed through by the refrigerant supply 3 from the outside to the inside of the refrigerant and after reaching the winding and cylinder axis 13, the refrigerant flows from the inside to the outside to the refrigerant discharge 4, through which the spiral pack 2 and after the heat exchanger 1 is left.
  • Fig. 2c shows an embodiment of a spiral package 2 as a single spiral with single-flow refrigerant flow from the inside to the outside or from outside to inside, which is not part of the invention.
  • Fig. 3a shows a perspective view of the flat tube with a transverse and longitudinal section. Arrows indicate the flow of the refrigerant through the refrigerant channels 10 and the flow of the water / glycol mixture between the ribs 11.
  • the refrigerant channels 10 are shown in cross section also in FIG. 3b in their sectional view as a circle. Equally possible, but less advantageous because of the pressure resistance, the formation of the refrigerant channels 10 in an oval or polygonal cross-sectional geometry.
  • the ribs 11 of the flat tube 9 are shown in Fig. 3a and the penetration of the flat tube 9 of refrigerant channels 10 along the length L of the flat tube is to be seen by the longitudinal section in the refrigerant flow direction.
  • the flat tubes 9 are advantageously formed with a large width B and height H ratio.
  • the flat tube 9 is flattened at the ends of its width B, which is aerodynamically advantageous in the flow and outflow of heat / brine and from the spiral package 2 and large-volume accumulation areas along the height H of the flat tube are thereby avoided.
  • FIG. 4a The formation of the flat tube 9 with ribs 11 on the upper side is shown in FIG. 4a.
  • the ribs 11 are shown as rectangular elevations on the flat tube 9. This form is favorable in terms of manufacturing and easily results in the winding of the flat tube 9 along its length L channel formation for the flow of heat / refrigerant, however, wide rib shapes are also advantageously used , Both round, oval or triangular shapes are possible embodiments for ribs 11 of the flat tube 9.
  • the flat tube 9 according to FIG. 4 a is preferably to be used in simple spiral windings of the flat tube 9, wherein in each case one upper side comes into contact with the underside of the flat tube 9 and the spaces forming between the ribs 11 form the channels for the heat / cold carrier.
  • the formation of the flat tube 9 according to FIG. 4b is advantageous because in the production of the spiral package 2, the flat tube 9 is bent in the region of the winding axis 13 by 180 ° and thus the top and bottom of the flat tube 9 to each other lie.
  • the flat tube 9 is provided with ribs 11 both on the upper and lower side.
  • FIG. 4c shows an embodiment in which the flat tube 9 was provided with ribs 11 along a region A with ribs 11 on the upper side and along a region B on the underside.
  • This design is advantageous for the production of a double spiral, provided that the winding axis 13 is placed in the region of the transition of the change of the ribs 11 from the top to the bottom.
  • the ribs themselves have a height of 0.01 to 10 mm.
  • the range from 4 to 10 mm is used for large flow cross sections.
  • a preferred embodiment of the ribs 11 for smaller flow cross sections, such as for heat exchangers for use in refrigeration systems or heat pumps in motor vehicles consists at a height of 0.1 to 2 mm.
  • For special applications with thin thin tube 9 and correspondingly many windings ribs 11 are used from 0.01 to 0.1 mm.
  • the ribs 11 according to FIG. 5a extend at an angle of 90 ° to the refrigerant channels 10, whereby the heat transfer between the heat / cold carrier and the high-pressure refrigerant takes place in crossflow.
  • the flat tube 9 is shown in plan view.
  • the heat / refrigerant flows through the channels formed between the ribs 11 and the refrigerant 3 flows in the flat tube 9 through the refrigerant channels 10. If, according to FIG. 1, the refrigerant supply 3 is displaced after the refrigerant discharge 4 in the flow direction of the heat / cold carrier, then there is a coupled cross counterflow.
  • Other circuit variants, such as the cross-direct current or mixed forms can also be realized with the heat exchanger 1 according to the invention.
  • the ribs 11 extend at an angle ⁇ according to FIG. 5b of greater than 0 ° and less than 90 ° or greater than 90 ° and less than 180 ° to the refrigerant channels 10, whereby the heat transfer between the heat - / Brine and the high pressure refrigerant is carried out directly in cross-counter or DC.
  • a particularly good heat transfer is achieved, wherein the angle ⁇ is to be selected for a particularly efficient heat transfer between 30 ° and 50 °.
  • carbon dioxide R744
  • tetrafluoroethane R134a
  • propane R290

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)

Claims (11)

  1. Echangeur thermique pour la transmission thermique entre un réfrigérant et un agent caloporteur/agent de refroidissement, comportant une enveloppe cylindrique, dans lequel se trouve au moins un paquet de spirales (2) en tube plat enroulé (9), avec des conduits (10) pour la circulation du réfrigérant et des écarteurs d'enroulement situés sur le dessus, prévus pour la création du conduit pour une circulation de l'agent caloporteur/de l'agent de refroidissement, des branchements pour l'alimentation en réfrigérant (3) et l'évacuation de réfrigérant (4), ainsi que l'alimentation (5) et l'évacuation (6) de l'agent caloporteur/de l'agent de refroidissement étant prévus,
    caractérisé en ce que
    un paquet de spirales (2) présente la forme d'une double spirale autour d'un axe d'enroulement (13),
    - le tube plat (2) étant enroulé en double couche, le long de sa longueur L, à partir d'une région entourant l'axe d'enroulement
    - un tour en forme de S du tube plat (9) recourbé sous un angle de 180° étant présent autour de l'axe d'enroulement (13), sur le tour en forme de S, la face supérieure et la face inférieure du tube plat (9) étant superposées.
  2. Echangeur thermique selon la revendication 1
    caractérisé en ce qu'en tant qu'écarteur d'enroulement du tube plat enroulé (9) et pour la formation de conduits pour la circulation de l'agent caloporteur/de l'agent de refroidissement, on a prévu sur le tube plat (9) des nervures (11), qui sont ménagées sur la face supérieure et/ou sur la face inférieure du tube plat (9).
  3. Echangeur thermique selon la revendication 1,
    caractérisé en ce que des écarteurs orientés en direction radiale, qui sont reliés avec l'enroulement final en spirale du type d'un cylindre sont associés à l'enveloppe cylindrique.
  4. Echangeur thermique selon la revendication 1 à 3,
    caractérisé en ce que la double spirale (2) est conçue pour un courant de réfrigérant à un seul flux, les raccords pour réfrigérant (3, 4) de la double spirale (2) étant présents dans la région centrale, autour de l'axe d'enroulement (13) et dans la région de l'enveloppe cylindrique.
  5. Echangeur thermique selon la revendication 1 à 3,
    caractérisé en ce que la double spirale (2) est conçue pour un courant de réfrigérant à deux flux, les raccords pour réfrigérant (3, 4) du tube plat (9) étant prévus dans la région de l'enveloppe cylindrique.
  6. Echangeur thermique selon la revendication 1 à 5,
    caractérisé en ce qu'à partir de l'axe d'enroulement (13) en direction de sa première région (A) de l'une des spirales (2), le tube plat (9) de la double spirale (2) est muni de nervures (11) sur la face supérieure et dans la région (B) de l'autre spirale, il est muni de nervures (11) situées en sens opposé sur la face inférieure.
  7. Echangeur thermique selon l'une quelconque des revendications 2 ou 6,
    caractérisé en ce que les nervures (11) s'étendent sous un premier angle α supérieur à 0° et inférieur à 9° par rapport aux conduits de réfrigérant (10), en conséquence de quoi, le transfert thermique entre les conduits de l'agent caloporteur/de l'agent de refroidissement (10) soutenus par nervures est assuré à l'intérieur du tube plat (9) à contre-courant croisé ou à courant identique croisé.
  8. Echangeur thermique selon l'une quelconque des revendications 1 à 7,
    caractérisé en ce que plusieurs paquets de spirales (2) sont disposés en rangée ou en parallèle à l'intérieur de l'enveloppe cylindrique.
  9. Echangeur thermique selon l'une quelconque des revendications 1 à 8, caractérisé en ce qu'au moins un dispositif de sécurité (8) et /ou un dispositif de purge (12) est prévu.
  10. Echangeur thermique selon l'une quelconque des revendications 1 à 9
    caractérisé en ce que l'agent caloporteur /l'agent de refroidissement est un mélange eau/glycol
  11. Echangeur thermique selon l'une quelconque des revendications 1 à 10
    caractérisé en ce que les réfrigérants : dioxyde de carbone R744, tétrafluoréthane R134 ou propane sont prévus en tant que réfrigérant haute pression.
EP00128034A 2000-12-21 2000-12-21 Echangeur de chaleur pour le transfert thermique entre un réfrigérant et un mélange eau/glycol Expired - Lifetime EP1217319B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
AT00128034T ATE354070T1 (de) 2000-12-21 2000-12-21 Wärmeübertrager zur wärmeübertragung zwischen einem kältemittel und einem wasser/glykol-gemisch
EP00128034A EP1217319B1 (fr) 2000-12-21 2000-12-21 Echangeur de chaleur pour le transfert thermique entre un réfrigérant et un mélange eau/glycol
DE50014069T DE50014069D1 (de) 2000-12-21 2000-12-21 Wärmeübertrager zur Wärmeübertragung zwischen einem Kältemittel und einem Wasser/Glykol-Gemisch

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP00128034A EP1217319B1 (fr) 2000-12-21 2000-12-21 Echangeur de chaleur pour le transfert thermique entre un réfrigérant et un mélange eau/glycol

Publications (2)

Publication Number Publication Date
EP1217319A1 EP1217319A1 (fr) 2002-06-26
EP1217319B1 true EP1217319B1 (fr) 2007-02-14

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Application Number Title Priority Date Filing Date
EP00128034A Expired - Lifetime EP1217319B1 (fr) 2000-12-21 2000-12-21 Echangeur de chaleur pour le transfert thermique entre un réfrigérant et un mélange eau/glycol

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EP (1) EP1217319B1 (fr)
AT (1) ATE354070T1 (fr)
DE (1) DE50014069D1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2939187B1 (fr) * 2008-12-01 2013-02-22 Valeo Systemes Thermiques Echangeur de chaleur a spires et dispositif de climatisation comprenant un tel echangeur de chaleur
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
DE102017217313A1 (de) * 2017-09-28 2019-03-28 Franz Josef Ziegler Wärmeübertrager

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3340588A (en) * 1960-10-19 1967-09-12 Heinz E Mueller Method of making heat exchangers
US5242015A (en) * 1991-08-22 1993-09-07 Modine Manufacturing Co. Heat exchanger
DE19623259C2 (de) * 1996-06-11 1998-07-30 Viessmann Gmbh & Co Wärmetauscher für Kältekreisläufe
DE19635454B4 (de) * 1996-08-31 2010-06-17 Behr Gmbh & Co. Kg Sammler-Wärmeübertrager-Baueinheit und damit ausgerüstete Klimaanlage
JP3365273B2 (ja) * 1997-09-25 2003-01-08 株式会社デンソー 冷凍サイクル
DE19808893A1 (de) * 1998-03-03 1999-09-09 Behr Gmbh & Co Wärmeübertragereinheit und diese enthaltende Sammler-Wärmeübertrager-Baueinheit

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EP1217319A1 (fr) 2002-06-26
DE50014069D1 (de) 2007-03-29
ATE354070T1 (de) 2007-03-15

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