EP1217319A1 - Wärmeübertrager, insbesondere zur Wärmeübertragung zwischen einem Kältemittel und einem Wasser/Glykol-Gemisch - Google Patents
Wärmeübertrager, insbesondere zur Wärmeübertragung zwischen einem Kältemittel und einem Wasser/Glykol-Gemisch Download PDFInfo
- Publication number
- EP1217319A1 EP1217319A1 EP00128034A EP00128034A EP1217319A1 EP 1217319 A1 EP1217319 A1 EP 1217319A1 EP 00128034 A EP00128034 A EP 00128034A EP 00128034 A EP00128034 A EP 00128034A EP 1217319 A1 EP1217319 A1 EP 1217319A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- heat
- heat exchanger
- refrigerant
- coolant
- flat tube
- 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.)
- Granted
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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, in particular for Heat transfer between a refrigerant and a water / glycol mixture.
- Heat exchangers are devices or components in which an indirect Heat transfer takes place. Here, heat is generated by a fluid stream higher temperature to another fluid stream lower Transfer temperature. The two material flows flow through the Heat exchangers without mixing are spatially separated from one another Cut.
- the evaporator and the condenser / gas cooler but often also an internal heat exchanger.
- the Refrigerant circuit is a material cycle, whereby heat is lost in the evaporator Evaporation of the refrigerant is absorbed and heat in the condenser is released by the refrigerant.
- heat exchangers according to the Preamble of the present invention used.
- Carbon dioxide as a refrigerant has been increasingly studied and the manufacture of such systems is being considered.
- Carbon dioxide (R744) is referred to as a high-pressure refrigerant because the critical temperature of the carbon dioxide in the area of the ambient temperature (31 ° C) and the associated pressure is significantly higher than that of the refrigerants currently used (R134a, R290, R212).
- the maximum high pressure that occurs in systems with carbon dioxide as refrigerant is in a range from 100 to 170 bar, depending on the application of the system.
- Carbon dioxide is increasingly used as a refrigerant in vehicle air conditioning mobile refrigeration systems, heat pumps or combinations of these, used. In such a case there is heat between a water / glycol mixture and transfer carbon dioxide or other refrigerant.
- a heat exchanger for this application increase several ways. Both from a security perspective, Susceptibility to failure and destructibility as well from the point of view of Minimum space requirements exist that are in the state of the art known heat exchangers can not be achieved.
- the object is achieved in that in one cylindrical heat exchanger at least one spiral package is arranged, wherein the spiral package is flowed through by a refrigerant and the Heat exchanger with the spiral package from a heat / coolant is flowed through, with heat between the refrigerant and the heat / cooling medium in cross flow or in cross countercurrent or crosscurrent is transferred and that the heat exchanger can be connected for the refrigerant supply, the refrigerant discharge, the heat / coolant supply as well as heat / coolant removal.
- the spiral package is constructively so designed to meet the safety requirements through compliance small flow cross sections in the refrigerant channels and small Filling volume in the spiral package.
- the spiral packs advantageously consist of flat tube with refrigerant channels, the flat tube being wound along its length.
- the position of the winding axis of the Spiral package and cylinder axis of the heat exchanger are identical.
- the flat tube is advantageous with ribs for spacing between adjacent windings and for channel formation for the heat / cooling medium in the wound state and to enlarge the surface educated.
- the advantages of the heat exchanger according to the invention are that a heat exchanger is provided in a confined space, the one has a large heat-transferring surface and, thanks to its Design the safety requirements for use in one Circuit with refrigerant fulfilled.
- FIG. 1 An advantageous embodiment of the heat exchanger according to the invention is shown in longitudinal section in FIG. 1.
- 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.
- At least one, in the present case, three spiral packs 2 are arranged in the interior of the heat exchanger 1, and the heat / coolant flows around them in sequence.
- the heat exchanger 1 also has connection options for the coolant supply 3 and the coolant discharge 4, the heat / coolant supply 5 and the heat / coolant discharge 6.
- the spiral packs 2 are flowed through by a refrigerant and by one Heat / coolant flows around, with heat between the High pressure refrigerant and the heat / coolant in cross flow or in Cross-counter or cross-direct current is transmitted.
- the spiral packs 2 are made from a flat tube 9 with the width (B) from five to one hundred and twenty millimeters (5 to 120 mm) and the height (H) from one to ten millimeters (1 to 10 mm).
- the spiral packs 2 are advantageously made of wound Flat tube 9 formed, which along its length (L) in double or simple position is wrapped.
- the winding axis 13 of the spiral package 2 lies 1 advantageously in the same position as the cylinder axis 13 of the Heat exchanger 1.
- the flat tube 9 has ribs 11 for spacing between adjacent windings within the Spiral package 2 and for channel formation for the heat / coolant in the wound state and to enlarge the surface.
- the heat exchanger 1 also has a safety device 8 against Overpressure, for example in the form of a rupture disc or Safety valve on and is in a suitable place with a Venting device equipped.
- a safety device 8 against Overpressure for example in the form of a rupture disc or Safety valve on and is in a suitable place with a Venting device equipped.
- spiral packs 2 are in the Figures 2a and 2b shown in cross section. Can be seen in each case Double spirals, which can be produced in a particularly simple manner, however, heat exchangers 1 with spiral packs 2 are made of simple spirals, 2c, also formed according to the invention.
- Fig. 2a shows the cross section of a heat exchanger 1 with a double flow Refrigerant flow in spiral package 2.
- the double spiral then becomes multi-flow Refrigerant flows through from inside to outside and occurs at the Refrigerant discharge 4 from the spiral pack 2 and leaves the Heat exchanger 1.
- 2b is the cross section of a heat exchanger 1 with a single-flow Refrigerant flow shown in spiral package 2.
- the double spiral first through the refrigerant supply 3 from the outside to the inside of the refrigerant flows through and flows after reaching the winding and cylinder axis 13 Refrigerant from the inside to the refrigerant discharge 4, through which the Spiral package 2 and then the heat exchanger 1 is left.
- FIG. 2c shows the advantageous embodiment of the spiral package 2 as a single spiral single-flow refrigerant flow from inside to outside or from outside to outside Inside.
- 3a shows a perspective view of the flat tube with cross and longitudinal section. Arrows flow through the Refrigerant through the refrigerant channels 10 and the flow of water / glycol - Mixture indicated between the ribs 11.
- the refrigerant channels 10 are in cross section represented as a circle. Likewise possible, but because of Pressure resistance is less advantageous, the formation of the refrigerant channels 10 in an oval or angular cross-sectional geometry.
- the ribs 11 of the flat tube 9 are also 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 through the longitudinal section in the refrigerant flow direction to see.
- the flat tubes 9 are advantageous with a large width B and height H. Relationship trained.
- FIG. 4a The formation of the flat tube 9 with ribs 11 on the top is shown in FIG. 4a.
- the ribs 11 are shown as rectangular elevations on the flat tube 9. This shape is cheap in terms of production technology and easily leads to Winding the flat tube 9 along its length L to form channels for the Flow of the heat / coolant, but wide rib shapes are also can be used advantageously. Both are round, oval or triangular shapes possible configurations for ribs 11 of the flat tube 9.
- the flat tube 9 according to FIG. 4a is preferably to be used with simple ones Spiral windings of the flat tube 9, each having an upper side in contact comes with the bottom of the flat tube 9 and which is between the ribs 11 forming rooms form the channels for the heat / coolant.
- Flat tube 9 for double spiral windings according to the invention, the formation of Flat tube 9 according to FIG. 4b advantageous because in the manufacture of the Spiral package 2, the flat tube 9 in the region of the winding axis 13 by 180 ° is bent and thus the top and bottom of the flat tube 9 on top of each other lie.
- the flat tube 9 is to be realized on both the top and bottom Ribs 11 provided.
- FIG. 4c shows an embodiment in which the flat tube 9 has been provided with ribs 11 on the upper side along an area A and with ribs 11 along an area 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 area where the ribs 11 change from the top to the bottom.
- the ribs themselves have a height of 0.01 to 10 mm. Taking the area from 4 to 10 mm is used for large flow cross sections. A preferred formation of the ribs 11 for smaller flow cross sections, for example for heat exchangers for use in refrigeration systems or heat pumps in Motor vehicles exist at a height of 0.1 to 2 mm. For Special applications with thin flat tube 9 and a corresponding number Windings with ribs 11 of 0.01 to 0.1 mm are used.
- the ribs run 11 according to FIG. 5a at an angle of 90 ° to the refrigerant channels 10, whereby the Heat transfer between the heat / coolant and the High pressure refrigerant is carried out in cross flow.
- the flat tube 9 is in the Shown top view.
- the heat / cold medium 5 flows through itself between the ribs 11 forming channels and the refrigerant 3 flows in Flat tube 9 through the refrigerant channels 10.
- the Refrigerant supply 3 after the refrigerant discharge 4 in the flow direction of the Heat / cold carrier offset so there is a coupled cross-countercurrent.
- Other circuit variants, such as cross direct current or mixed forms can also be realized with the heat exchanger 1 according to the invention.
- the ribs 11 run in one 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 / coolant and the High-pressure refrigerant takes place directly in cross-countercurrent or cocurrent.
- Angle ⁇ for a particularly efficient heat transfer choose between 30 ° and 50 °.
- the arrangement of several spiral packs 2 in the heat exchanger 1 is depending on the application, designed so that the high-pressure refrigerant Flows through spiral packets 2 in a series connection or in parallel connection.
- refrigerants in the sense of the preamble of the invention are in particular Carbon dioxide (R744), tetrafluoroethane (R134a) and 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)
Abstract
Description
Ganz besondere Anforderungen werden an Wärmeübertrager gestellt, welche bei hohen Fluiddrücken der Stoffströme arbeiten.
Der maximal auftretende Hochdruck liegt in Anlagen mit Kohlendioxid als Kältemittel in einem Bereich von 100 bis 170 bar, je nach Anwendungsfall des Systems.
- Fig. 1:
- Längsschnitt eines Wärmeübertragers
- Fig. 2a:
- Querschnitt eines Wärmeübertragers mit einem zweiflutigen Kältemittelstrom im Spiralpaket
- Fig. 2b:
- Querschnitt eines Wärmeübertragers mit einem einflutigen Kältemittelstrom im Spiralpaket
- Fig. 2c:
- Querschnitt eines Wärmeübertragers mit einer Einfachspirale
- Fig. 3a:
- perspektivische Ansicht des Flachrohrs mit Quer- und Längsschnitt
- Fig. 3b:
- Querschnitt des Flachrohrs
- Fig. 4a:
- Längsschnitt des Flachrohrs mit Rippen auf der Oberseite
- Fig. 4b:
- Längsschnitt des Flachrohrs mit Rippen auf der Ober - und Unterseite
- Fig. 4c:
- Längsschnitt des Flachrohrs mit Rippen entweder auf der Ober - oder der Unterseite jeweils auf einem bestimmten Abschnitt
- Fig. 5a:
- Draufsicht auf ein Flachrohr mit Rippen quer zur Kältemittelströmungsrichtung
- Fig. 5b:
- Draufsicht auf ein Flachrohr mit Rippen schräg zur Kältemittelströmungsrichtung
Der zylindrische Mantel des Wärmeübertragers 1 ist als Kreiszylinder in Form eines Rohres ausgeführt, welches an seinen Enden zu Anschlussstutzen 7 verjüngt ist. Im Inneren des Wärmeübertragers 1 ist mindestens ein, im vorliegenden Fall sind drei Spiralpakete 2 angeordnet, welche der Reihe nach vom Wärme- / Kälteträger umströmt werden. Der Wärmeübertrager 1 weist weiterhin Anschlussmöglichkeiten für die Kältemittelzufuhr 3 und die Kältemittelabfuhr 4, die Wärme-/ Kälteträgerzufuhr 5 sowie die Wärme-/ Kälteträgerabfuhr 6 auf.
Diese Ausbildung ist für die Herstellung einer Doppelspirale vorteilhaft, sofern die Wickelachse 13 in den Bereich des Überganges des Wechsels der Rippen 11 von der Ober- auf die Unterseite gelegt wird.
- 1
- Wärmeübertrager
- 2
- Spiralpaket
- 3
- Kältemittelzufuhr
- 4
- Kältemittelabfuhr
- 5
- Wärme- / Kälteträgerzufuhr
- 6
- Wärme- / Kälteträgerabfuhr
- 7
- Anschlussstutzen
- 8
- Sicherheitseinrichtung
- 9
- Flachrohr
- 10
- Kältemittelkanal
- 11
- Rippe
- 12
- Entlüftungsvorrichtung
- 13
- Wickelachse / Zylinderachse
- B
- Flachrohrbreite
- H
- Flachrohrhöhe
- L
- Flachrohrlänge
Claims (10)
- Wärmeübertrager, insbesondere zur Wärmeübertragung zwischen einem Hochdruckkältemittel und einem Wärme-/ Kälteträger, vorzugsweise einem Wasser/Glykol-Gemisch, dadurch gekennzeichnet, dass im zylindrischen Wärmeübertrager (1) mindestens ein Spiralpaket (2) angeordnet ist, wobei das Spiralpaket (2) von einem Hochdruckkältemittel durchströmt und von einem Wärme-/ Kälteträger umströmt wird und dass dabei Wärme zwischen dem Hochdruckkältemittel und dem Wärme-/ Kälteträger im Kreuzstrom oder im Kreuzgegen- bzw Kreuzgleichstrom im Wärmeübertrager (1) übertragen wird und dass der Wärmeübertrager (1) dazu Anschlussmöglichkeiten für die Kältemittelzufuhr (3), die Kältemittelabfuhr (4), die Wärme-/ Kälteträgerzufuhr (5) sowie Wärme-/ Kälteträgerabfuhr (6) aufweist.
- Wärmeübertrager nach Anspruch 1, dadurch gekennzeichnet, dass das Spiralpaket (2) aus einem Flachrohr (9) mit der Breite (B) zwischen [Werte angeben] und der Höhe (H) zwischen [Werte angeben] gebildet wird und dass das Flachrohr (9) mindestens einen Kältemittelkanal (10) mit einem Durchmesser von [Werte angeben] aufweist, in welchem Hochdruckkältemittel strömen kann.
- Wärmeübertrager nach Anspruch 2, dadurch gekennzeichnet, dass der Wärmeübertrager (1) als Kreiszylinder ausgebildet ist und dass das Spiralpaket (2) aus gewickeltem Flachrohr (9) gebildet ist, welches entlang seiner Länge (L) gewickelt ist und dass die Wickelachse (13) des Spiralpaketes (2) gleich der Zylinderachse (13) des Wärmeübertragers (1) ist.
- Wärmeübertrager nach einem der Ansprüche 2 oder 3, dadurch gekennzeichnet, dass das Flachrohr (9) Rippen (11) nur an seiner Oberseite oder an Ober- und Unterseite zur Vergrößerung der Oberfläche, zur Abstandhaltung zwischen benachbarten Wicklungen und zur Kanalbildung für den Wärme-/ Kälteträger im gewickelten Zustand aufweist.
- Wärmeübertrager nach Anspruch 4, dadurch gekennzeichnet, dass die Rippen (11) des Flachrohres (9) eine Höhe von 0,1 mm bis 10 mm besitzen.
- Wärmeübertrager nach einem der Ansprüche 4 bis 5, dadurch gekennzeichnet, dass die Rippen (11) im Winkel von 90° zu den Kältemittelkanälen (10) verlaufen, wodurch die Wärmeübertragung zwischen dem Wärme-/ Kälteträger und dem Hochdruckkältemittel im Kreuzstrom erfolgt.
- Wärmeübertrager nach einem der Ansprüche 4 bis 5, dadurch gekennzeichnet, dass die Rippen (11) in einem Winkel α von größer als 0° und kleiner als 90° zu den Kältemittelkanälen (10) verlaufen, wodurch die Wärmeübertragung zwischen dem Wärme-/ Kälteträger und dem Hochdruckkältemittel im Kreuzgegen- oder Kreuzgleichstrom erfolgt.
- Wärmeübertrager nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass mehrere Spiralpakete (2) im Wärmeübertrager (1) vom Hochdruckkältemittel in Reihe oder parallel durchströmt werden.
- Wärmeübertrager nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass mindestens eine Sicherheitseinrichtung (8) und / oder eine Entlüftungseinrichtung (12) vorgesehen ist.
- Wärmeübertrager nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass als Hochdruckkältemittel R744, R134a oder R290 einsetzbar ist.
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 |
DE50014069T DE50014069D1 (de) | 2000-12-21 | 2000-12-21 | Wärmeübertrager zur Wärmeübertragung zwischen einem Kältemittel und einem Wasser/Glykol-Gemisch |
EP00128034A EP1217319B1 (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 (de) | 2000-12-21 | 2000-12-21 | Wärmeübertrager zur Wärmeübertragung zwischen einem Kältemittel und einem Wasser/Glykol-Gemisch |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1217319A1 true EP1217319A1 (de) | 2002-06-26 |
EP1217319B1 EP1217319B1 (de) | 2007-02-14 |
Family
ID=8170742
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP00128034A Expired - Lifetime EP1217319B1 (de) | 2000-12-21 | 2000-12-21 | Wärmeübertrager zur Wärmeübertragung zwischen einem Kältemittel und einem Wasser/Glykol-Gemisch |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP1217319B1 (de) |
AT (1) | ATE354070T1 (de) |
DE (1) | DE50014069D1 (de) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2939187A1 (fr) * | 2008-12-01 | 2010-06-04 | 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 |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3340588A (en) * | 1960-10-19 | 1967-09-12 | Heinz E Mueller | Method of making heat exchangers |
EP0529819A2 (de) * | 1991-08-22 | 1993-03-03 | Modine Manufacturing Company | Wärmetauscher |
DE19623259A1 (de) * | 1996-06-11 | 1997-12-18 | Viessmann Gmbh & Co | Verdampfer bzw. Kondensator für Kältekreisläufe |
DE19635454A1 (de) * | 1996-08-31 | 1998-03-05 | Behr Gmbh & Co | Sammler-Wärmeübertrager-Baueinheit und damit ausgerüstete Klimaanlage |
DE19842019A1 (de) * | 1997-09-25 | 1999-04-01 | Denso Corp Kariya City Aichi P | Kühl- bzw. Kältemittelzyklus |
DE19808893A1 (de) * | 1998-03-03 | 1999-09-09 | Behr Gmbh & Co | Wärmeübertragereinheit und diese enthaltende Sammler-Wärmeübertrager-Baueinheit |
-
2000
- 2000-12-21 AT AT00128034T patent/ATE354070T1/de not_active IP Right Cessation
- 2000-12-21 EP EP00128034A patent/EP1217319B1/de not_active Expired - Lifetime
- 2000-12-21 DE DE50014069T patent/DE50014069D1/de not_active Expired - Fee Related
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3340588A (en) * | 1960-10-19 | 1967-09-12 | Heinz E Mueller | Method of making heat exchangers |
EP0529819A2 (de) * | 1991-08-22 | 1993-03-03 | Modine Manufacturing Company | Wärmetauscher |
DE19623259A1 (de) * | 1996-06-11 | 1997-12-18 | Viessmann Gmbh & Co | Verdampfer bzw. Kondensator für Kältekreisläufe |
DE19635454A1 (de) * | 1996-08-31 | 1998-03-05 | Behr Gmbh & Co | Sammler-Wärmeübertrager-Baueinheit und damit ausgerüstete Klimaanlage |
DE19842019A1 (de) * | 1997-09-25 | 1999-04-01 | Denso Corp Kariya City Aichi P | Kühl- bzw. Kältemittelzyklus |
DE19808893A1 (de) * | 1998-03-03 | 1999-09-09 | Behr Gmbh & Co | Wärmeübertragereinheit und diese enthaltende Sammler-Wärmeübertrager-Baueinheit |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2939187A1 (fr) * | 2008-12-01 | 2010-06-04 | Valeo Systemes Thermiques | Echangeur de chaleur a spires et dispositif de climatisation comprenant un tel echangeur de chaleur |
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. |
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 |
Also Published As
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DE50014069D1 (de) | 2007-03-29 |
EP1217319B1 (de) | 2007-02-14 |
ATE354070T1 (de) | 2007-03-15 |
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