EP1724536A2 - Echangeur de chaleur avec partie accumulatrice - Google Patents

Echangeur de chaleur avec partie accumulatrice Download PDF

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Publication number
EP1724536A2
EP1724536A2 EP06007946A EP06007946A EP1724536A2 EP 1724536 A2 EP1724536 A2 EP 1724536A2 EP 06007946 A EP06007946 A EP 06007946A EP 06007946 A EP06007946 A EP 06007946A EP 1724536 A2 EP1724536 A2 EP 1724536A2
Authority
EP
European Patent Office
Prior art keywords
container
chamber
heat exchanger
tube
longitudinal wall
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
Application number
EP06007946A
Other languages
German (de)
English (en)
Other versions
EP1724536A3 (fr
EP1724536B1 (fr
Inventor
Hubertus R. Dipl.-Ing. Kamsma
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.)
Modine Manufacturing Co
Original Assignee
Modine Manufacturing Co
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 Modine Manufacturing Co filed Critical Modine Manufacturing Co
Publication of EP1724536A2 publication Critical patent/EP1724536A2/fr
Publication of EP1724536A3 publication Critical patent/EP1724536A3/fr
Application granted granted Critical
Publication of EP1724536B1 publication Critical patent/EP1724536B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • 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
    • F28D7/10—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
    • 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
    • F28D7/16—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 in parallel spaced relation
    • F28D7/1684—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 in parallel spaced relation the conduits having a non-circular cross-section
    • 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
    • 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
    • F28F1/126—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 consisting of zig-zag shaped fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/005—Other auxiliary members within casings, e.g. internal filling means or sealing means
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/044—Condensers with an integrated receiver
    • F25B2339/0441—Condensers with an integrated receiver containing a drier or a filter
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/044—Condensers with an integrated receiver
    • F25B2339/0446—Condensers with an integrated receiver characterised by the refrigerant tubes connecting the header of the condenser to the receiver; Inlet or outlet connections to receiver
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components

Definitions

  • the invention relates to a device for the treatment of the refrigerant, which in a
  • Air circulating circulates comprising: compressor, gas cooler, evaporator (heat exchanger) and expansion element and thereby passes through a high pressure side and a low pressure side, in which the refrigerant has different temperature, the device having a tube through which flows the one side and in a container is arranged, through which the other side flows to serve as an intermediate heat exchanger, wherein in the container, an accumulator chamber and a heat exchanger chamber is formed.
  • This device which is often referred to as an internal heat exchanger in trans-critical air conditioning circuits, is from the DE 196 35 454A1 is known and can be considered advanced, because the achievable heat exchange rate meets the requirements and because it also includes a Akkumulatorhunt.
  • the fabrication of this device - lying in the installation space of the motor vehicle - seems to be rather expensive, since the tubes are deformed as spirals and the insertion of the heat-conducting fins between the turns of the coils could also be complicated.
  • German patent DE 199 18 617 C2 were an accumulator and - separately - and an internal heat exchanger combined with the gas cooler, creating a very compact design was created.
  • the accumulator is connected to a manifold of the gas cooler.
  • the inner heat exchanger is located at the upper or lower edge of the gas cooler, ie parallel to the tubes, and thus directly in the influence of the cooling air, which has a temperature of about 30 - 40 ° C in summer, whereby the intended effect of the inner heat exchanger is counteracted , The degree of intended cooling of the refrigerant on the high pressure side is somewhat reduced by the relatively high temperature of the cooling air.
  • the inner heat exchanger is also quite expensive to produce. Its connection with the gas cooler also seems to be structurally difficult to carry out.
  • the object of the invention is to propose with other design features comparable in terms of compactness and functionality device that can be produced cheaper.
  • the container containing the tube is connected to the manifold of the heat exchanger, preferably the gas cooler, to a structural unit, wherein the accumulator chamber and the heat exchanger chamber present in the container extend parallel to the manifold and over a substantial portion of the length of the container achieved a good result in terms of compactness.
  • the favorable possibility of arranging a dryer and optionally also a filter in the accumulator chamber and / or the heat exchanger chamber of the container, since the space available for this measure is sufficient.
  • the filter and dryer ensure the desired drying and cleaning (treatment) of the transcritical refrigerant, which can be CO2, for example.
  • the accumulator serves the functionality of the system, since it contributes to the fact that only vaporous refrigerant reaches the compressor and thereby ensures its proper operation.
  • the vaporous refrigerant shortly before leaving the heat exchanger chamber in the direction of the compressor via an opening in the longitudinal wall small amounts of oil and liquid refrigerant are supplied.
  • the refrigerant vapor is in such a state that the supply of oil and liquid refrigerant results in further cooling by evaporative cooling.
  • the vaporous state of the refrigerant at the compressor is thereby assisted and the refrigerant inlet temperature at the compressor is lowered again.
  • the refrigerant must overcome a more or less large slope after the return of the oil, resulting in losses.
  • the recirculation is made bypassing the inner heat exchanger directly into the suction line, whereby a more favorable heat transfer is present.
  • the mentioned tube is preferably an extruded multi-chamber tube that extends substantially straight over at least one extends substantial length of the container, whereby, inter alia, the relatively inexpensive production of the device is effected.
  • the multi-chamber tube is covered around its entire circumference with the heat exchange rib.
  • a longitudinal wall is formed in the container, which divides the container into two parts, namely an accumulator chamber and a heat exchanger chamber.
  • the longitudinal wall has at least one opening at one end to allow the refrigerant to flow from the accumulator chamber into the heat exchanger chamber.
  • another opening is provided, via which accumulated in the accumulator oil can get into the refrigerant.
  • a drying agent and also a filter can be arranged in the accumulator chamber.
  • An inlet tube is disposed in the accumulator chamber to assist in the settling of any liquid refrigerant present in the low pressure phase.
  • the dryer In or on the introduction tube, the dryer can be located and immediately below the filter can be arranged.
  • a plastic wall can be inserted into the container which suppresses the undesired heat transfer between the accumulator chamber and the heat exchanger chamber.
  • the heat exchange should take place essentially in the heat exchanger chamber, since this was specially equipped for it. Overall, this results in slightly higher temperature differences between the low pressure side and the high pressure side in the heat exchange chamber itself, resulting in improved efficiency of heat exchange.
  • the independent claim 19 relates to a not with a heat exchanger, preferably the gas cooler, united device, which is rather at a suitable location in the air conditioning circuit and which is particularly inexpensive to produce and has high efficiency.
  • the container is designed as a slender, preferably produced by extrusion hollow body with a longitudinal wall or with holders for holding a longitudinal wall inserted, wherein the longitudinal wall has at least one opening to flow the refrigerant from the accumulator into the heat exchanger chamber and that the tube is formed as a preferably produced by the same extrusion process multi-chamber tube which extends through the heat exchanger chamber and is covered on all sides with heat exchange ribs.
  • the device is particularly easy to manufacture and is also characterized by its slim Design that helps to accommodate a conventional air conditioning system and transcritical refrigerant air conditioning system, such as CO2, with substantially the same space requirements, which is a not inconsiderable advantage for automobile manufacturers, who are thus not constrained by their space concepts within a range of Change automobiles depending on the type of air conditioning.
  • CO2 transcritical refrigerant air conditioning system
  • Fig. 1 shows a longitudinal section through a device according to the invention.
  • FIG. 2 shows a cross section through the device according to FIGS. 1 or 3.
  • Fig. 3 shows a longitudinal section in a preferred embodiment of the invention.
  • Fig. 4 shows an alternative design in a cross section through the container.
  • Fig. 5 shows a flat multi-chamber tube in a cross section according to another alternative.
  • Figs. 6, 7 and 8 show different embodiments of the container in cross section.
  • FIGS. 9-12 show, purely schematically, the connection of the device to a heat exchanger, preferably to the gas cooler.
  • the devices described in the exemplary embodiments are preferably intended for use in air conditioning systems of motor vehicles in an approximately vertical arrangement.
  • the device for the treatment of the refrigerant according to FIGS. 1 and 3 differs by the arrangement of a filter 23 in the accumulator chamber 21 and in the heat exchanger chamber 22. They otherwise agree that they have a container 20 with a longitudinal wall 26, the was produced by extrusion.
  • the longitudinal wall 26 divides the container 20 into the two mentioned chambers 21, 22 which extend in parallel and substantially over the entire length of the container 20.
  • a dryer 24 In the accumulator chamber 21 is a dryer 24, which in this embodiment, outside a Introducer tube 25 has been arranged.
  • a flat multi-chamber tube 10 Through the heat exchanger chamber 22 extends a flat multi-chamber tube 10, which is equipped with a heat conducting rib 11 which largely fills the remaining cross section of the heat exchanger chamber 22 in order to achieve good results in terms of heat exchange efficiency can.
  • an insulation 50 was provided in both embodiments, which covers the surface of the container 20 . This measure is particularly suitable where you would like to avoid temperature effects from the environment on the heat exchange in the container 20 . Usually these are too high outside temperatures.
  • the lower-pressure side, cooler refrigerant flows through an opening 40 in the upper lid 80 into the accumulator chamber 21 a.
  • an introduction tube 25 projects into the accumulator chamber 21 . In the case of FIG. 1, this refrigerant flows through a filter basket 25 at the end of the introduction tube 25. Oil present in the refrigerant and residual liquid refrigerant settle in the accumulator chamber 21 at the bottom.
  • the gaseous refrigerant flows above an inlet opening 31 in the longitudinal wall 26 in the heat exchanger chamber 22 to pass through the heat conducting rib 11 down in the direction of exit 41 , which is arranged in the wall of the container 20 .
  • the high-pressure side and warmer refrigerant flows through a channel 70 in the upper lid 80 in the multi-chamber tube 10 , flows in the multi-chamber tube 10 down to the exit channel 71 in the lower lid 80, after heat release to the low-pressure side refrigerant and further cooled and therefore the performance-improving state of leaving the container 20 toward an expansion device (not shown) and the evaporator.
  • the described direction of flow only serves to understand the figures. It is, moreover, determined in an appropriate manner.
  • FIG. 2 Down in the longitudinal wall 26 is a channel 30 and a bore 32 to supply the low-pressure side refrigerant after passing through the heat exchanger chamber 22 in the accumulator 21 settled oil.
  • FIG. 2 In the exemplary embodiment according to FIG. 3, two flat filter elements 24 have been provided. One of these was placed in front of the channel 30 and the second is located in front of the already mentioned exit 41 in the heat exchanger chamber 22. With this configuration it should be pointed out that the present invention offers greater design freedom for the designer with regard to the placement of such elements the state of the art.
  • Fig. 4 shows the cross section through the container 20 of another particularly noteworthy embodiment.
  • a larger or specially designed accumulator chamber 21 is required, which was achieved according to FIG. 4 in that the flat multi-chamber tube 10 was formed with a shape adapted to the contour of the container 20 and thus extends along part of the container wall.
  • a longitudinal wall 26 was used, which is also adapted to the mentioned contour.
  • On the inside of the container wall there are receiving grooves 27 into which the longitudinal edges of the longitudinal wall 26 can be inserted.
  • the grooves 27 do not limit the manufacturability of the container 20 by means of extrusion molding, ie they can be realized by means of this method.
  • the multi-chamber tube 10 is preferably, but not necessarily, also an extruded tube, for example with two rows of apertures 12. More preferably, this configuration is then made when, as shown in Fig. 5, on the corrugated heat exchange ribs 11 is to be omitted as a single part by the multi-chamber tube 10 is equipped on the outside with rib-like channels.
  • FIG. 6, 7 and 8 show further embodiments in cross-section through an extruded container 20 with two longitudinal walls 26, which then form three chambers or compartments in the container 20 .
  • These chambers may be formed according to the desired application as a battery chamber 22 or as a heat exchanger chamber 21 .
  • the middle chamber was designed as a heat exchange chamber 22 and the other two chambers as accumulator chambers 21 .
  • the heat exchanger chamber 22 is a multi-chamber tube 10 which has already been described above with reference to FIG. 5.
  • FIG. 7 shows another example in which all three chambers are designed as heat exchanger chambers 22 .
  • the reference numeral 90 was a design option, which is to partially increase the wall thickness of the container 20 in order to form the cross section of the chambers - while maintaining the circular cross-sectional shape of the container 20 - so that the insertion of the tube 10 is facilitated with the heat exchange fin 11 .
  • It can be used in this case conventional corrugated fins 11 , which are spirally wound around the tube 10 .
  • such a "uniform" cross-section is also suitable for the collector chamber 21 .
  • the "uniformed" cross-section was achieved with another measure, namely a slight deviation from the round container shape, which is still acceptable despite the high pressures in the system.
  • four graduations 60 distributed on the circumference of the container 20 have been provided, which result in that the cross section of the upper and the lower heat exchanger chamber 22 can be approximately rectangular.
  • the middle chamber was designed here as an accumulator chamber 21 .
  • the device described so far was, as shown in the following Fig. 9-12, combined with the gas cooler 3 in order to achieve a particularly compact design of the entire system.
  • the container 20 may in principle be such as shown for example in FIG. 3 and already described above.
  • the container 20 is arranged parallel to and connected to a header 30 of the condenser, here the gas cooler 3 .
  • the difference further consists in that in the prior art it is only a collector, but in the present case an accumulator 21, combined with an internal heat exchanger 22, is connected to the gas cooler 3 .
  • the container 20 is secured by means of two holders 5 on the manifold 4 .
  • FIG. 9 the necessary components of the air conditioning circuit at the inflow and outflow points for the low-pressure side ND and the high-pressure side HD refrigerant have been indicated by appropriate labeling.
  • the gas cooler 3 receives high-pressure compressed gaseous HD refrigerant coming from the compressor, which is cooled in the gas cooler 3 by heat exchange with cooling air.
  • the serpentine flow through the gas cooler 3 by groups of parallel flat tubes was indicated by arrows.
  • the headers 4 of the gas cooler 3 are partitions, the described flow cause.
  • the HD - refrigerant into the heat exchanger chamber 22 occurs in the embodiment immediately, and indeed, as described in the extending through the chamber 22 multi-chamber tube 10 after leaving the gas cooler. 3
  • Fig. 9 has been provided to make the passage from the gas cooler 3 to the container 20 by means of a short line 6 from the manifold 4 in the multi-chamber tube 10 .
  • Fig. 12 shows a somewhat more compact design, which consists in that the conduit 6 passes through one of the holders 5 and is connected to the multi-chamber tube 10 .
  • the ND refrigerant coming from the evaporator is in the state of subcooling. It passes through the reaching in the accumulator 21 insertion tube 25 into the accumulator 21 a and passes the dryer 24 and a filter 23 25 at the end of the insertion tube Unlike the previously described embodiments, the opening of the oil is in the longitudinal wall 26 directly in the area of the soil.
  • FIG. 10 shows, likewise schematically, a section from a plan view of the device according to FIG. 9.
  • FIG. 11 shows a further development idea, which is that the container 20 produced by extrusion has no integrated longitudinal wall 26 , but was equipped only with receiving grooves 40 . These receiving grooves 40 serve to be able to use a longitudinal wall made of plastic, which is otherwise formed as described. Such a design brings advantages in terms of the efficiency of the heat exchange, and it is executable despite the prevailing high pressure, because there are no significant differences in pressure between the heat exchanger chamber 22 and the accumulator 21 .
  • the container 20 of the proposed device is also characterized by its slim design.
  • the ratio of its length L to its diameter D is at least 3: 1, preferably the ratio is about 6: 1.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (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)
EP06007946A 2005-05-11 2006-04-15 Echangeur de chaleur avec partie accumulatrice Expired - Fee Related EP1724536B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005021787A DE102005021787A1 (de) 2005-05-11 2005-05-11 Vorrichtung zur Behandlung des Kältemittels

Publications (3)

Publication Number Publication Date
EP1724536A2 true EP1724536A2 (fr) 2006-11-22
EP1724536A3 EP1724536A3 (fr) 2008-07-16
EP1724536B1 EP1724536B1 (fr) 2011-01-26

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Family Applications (1)

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EP06007946A Expired - Fee Related EP1724536B1 (fr) 2005-05-11 2006-04-15 Echangeur de chaleur avec partie accumulatrice

Country Status (3)

Country Link
US (1) US20060254310A1 (fr)
EP (1) EP1724536B1 (fr)
DE (2) DE102005021787A1 (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1816424A1 (fr) * 2006-02-02 2007-08-08 Behr GmbH & Co. KG Echangeur thermique pour un cycle frigorifique
EP1892491A2 (fr) * 2006-07-12 2008-02-27 Behr GmbH & Co. KG Unité, comportant un refroidisseur de gaz et un échangeur thermique interne, et échangeur thermique
FR2930018A1 (fr) * 2008-04-15 2009-10-16 Valeo Systemes Thermiques Dispositif combine comprenant un echangeur de chaleur interne et un accumulateur.
EP2199709A2 (fr) * 2008-12-22 2010-06-23 Valeo Systemes Thermiques Dispositif combiné comprenant un échangeur de chaleur interne et un accumulateur
CN101776357B (zh) * 2009-01-09 2011-12-28 三花丹佛斯（杭州）微通道换热器有限公司 一种热交换器
WO2013114384A1 (fr) * 2011-12-26 2013-08-08 Robert Bosch Engineering And Business Solutions Limited Accumulateur destiné à un dispositif de récupération et de recharge de fluide frigorigène
EP2631566A1 (fr) * 2012-02-24 2013-08-28 Airbus Operations GmbH Agencement d'accumulateur avec super-refroidisseur intégré
EP2937658A1 (fr) * 2014-04-23 2015-10-28 MAHLE International GmbH Fluide caloporteur interne
EP2963362A1 (fr) * 2014-06-30 2016-01-06 Eaton Industrial IP GmbH & Co. KG Accumulateur destiné à un système de conditionnement d'air
EP3748269A1 (fr) * 2019-06-05 2020-12-09 Valeo Systemes Thermiques Échangeur de chaleur

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009024899A (ja) * 2007-07-17 2009-02-05 Showa Denko Kk エバポレータ
US7971441B2 (en) 2007-10-26 2011-07-05 GM Global Technology Operations LLC Receiver/dryer-accumulator-internal heat exchanger for vehicle air conditioning system
FR2940419B1 (fr) * 2008-12-22 2010-12-31 Valeo Systemes Thermiques Dispositif combine constitue d'un echangeur de chaleur interne et d'un accumulateur, et pourvu d'un composant interne multifonctions
FR2940420B1 (fr) * 2008-12-22 2010-12-31 Valeo Systemes Thermiques Dispositif combine comprenant un echangeur de chaleur interne et un accumulateur constitutifs d'une bouche de climatisation
DE102010040025A1 (de) * 2010-08-31 2012-03-01 Behr Gmbh & Co. Kg Kältemittelkondensatorbaugruppe
EP2724107B1 (fr) * 2011-06-27 2017-09-27 Carrier Corporation Échangeur de chaleur à enveloppe et à tubes avec microcanaux
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DE102017211529A1 (de) * 2017-07-06 2019-01-10 Mahle International Gmbh Einsatzrohr für den Eintrittskanal eines Plattenwärmetauschers
WO2020038437A1 (fr) * 2018-08-23 2020-02-27 杭州三花研究院有限公司 Séparateur gaz-liquide et système de conditionneur d'air

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EP1816424A1 (fr) * 2006-02-02 2007-08-08 Behr GmbH & Co. KG Echangeur thermique pour un cycle frigorifique
EP1892491A2 (fr) * 2006-07-12 2008-02-27 Behr GmbH & Co. KG Unité, comportant un refroidisseur de gaz et un échangeur thermique interne, et échangeur thermique
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EP2110624A1 (fr) * 2008-04-15 2009-10-21 Valeo Systèmes Thermiques Dispositif combiné comprenant un échangeur de chaleur interne et un accumulateur
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EP2631566A1 (fr) * 2012-02-24 2013-08-28 Airbus Operations GmbH Agencement d'accumulateur avec super-refroidisseur intégré
CN103292525A (zh) * 2012-02-24 2013-09-11 空中客车作业有限公司 具有集成式过冷器的蓄能器装置
CN103292525B (zh) * 2012-02-24 2015-10-21 空中客车作业有限公司 具有集成式过冷器的蓄能器装置
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EP2937658A1 (fr) * 2014-04-23 2015-10-28 MAHLE International GmbH Fluide caloporteur interne
EP2963362A1 (fr) * 2014-06-30 2016-01-06 Eaton Industrial IP GmbH & Co. KG Accumulateur destiné à un système de conditionnement d'air
EP3748269A1 (fr) * 2019-06-05 2020-12-09 Valeo Systemes Thermiques Échangeur de chaleur

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US20060254310A1 (en) 2006-11-16
DE102005021787A1 (de) 2006-11-16
EP1724536A3 (fr) 2008-07-16
EP1724536B1 (fr) 2011-01-26
DE502006008790D1 (de) 2011-03-10

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