EP1739375A1 - Wärmetauscher mit erhöhter Kompaktheit und Druckfestigkeit - Google Patents

Wärmetauscher mit erhöhter Kompaktheit und Druckfestigkeit Download PDF

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Publication number
EP1739375A1
EP1739375A1 EP06013318A EP06013318A EP1739375A1 EP 1739375 A1 EP1739375 A1 EP 1739375A1 EP 06013318 A EP06013318 A EP 06013318A EP 06013318 A EP06013318 A EP 06013318A EP 1739375 A1 EP1739375 A1 EP 1739375A1
Authority
EP
European Patent Office
Prior art keywords
channels
collector
exchanger according
fluid
exchanger
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Withdrawn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
EP06013318A
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English (en)
French (fr)
Inventor
Jimmy Lemee
Philippe Doucet
Patrick Hoger
Stéphane MEUNIER
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.)
Valeo Systemes Thermiques SAS
Original Assignee
Valeo Systemes Thermiques SAS
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 Valeo Systemes Thermiques SAS filed Critical Valeo Systemes Thermiques SAS
Publication of EP1739375A1 publication Critical patent/EP1739375A1/de
Withdrawn legal-status Critical Current

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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
    • 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
    • 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
    • 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
    • F28F9/02—Header boxes; End plates
    • 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 heat exchanger, for example for a motor vehicle air conditioning circuit.
  • a heat exchanger has the function of ensuring a heat exchange between a first fluid and a second fluid circulating in the exchanger.
  • Exchangers comprising an elongate body in which are formed first and second longitudinal channels for the circulation of the first fluid and third longitudinal channels for the circulation of the second fluid are also known.
  • the channels are arranged in one or more rows.
  • Exchangers of this type are used in particular in the case of fluids flowing at high pressure.
  • the channels being formed in a relatively massive body, they have good resistance to pressure.
  • a collector is provided in which the first channels open at one end.
  • a collector for the second channels and a collector for the third channels are generally provided.
  • a collector for collecting the first fluid leaving the first channels to a first fluid outlet.
  • collectors are more generally provided for the second and third channels.
  • JP 2002098486 describes an exchanger comprising six collectors.
  • the space occupied by the collectors is a disadvantage. As the body is generally elongated and of small thickness, the bulk of the collectors appears to be important in comparison. The congestion of the collectors finally defines the bulk of the congestion of the exchanger, for the same reason. The size of the exchanger must be minimized in order to allow, facilitate and / or optimize its integration into the front part of a motor vehicle.
  • the exchanger must be able to be manufactured simply for a minimum cost and offer optimal heat transfer performance.
  • the object of the invention is to overcome the aforementioned drawbacks by proposing a heat exchanger comprising an elongated body in which are arranged at least one row of first longitudinal channels and at least one row of second longitudinal channels, in which a first fluid circulates, the first ones channels and the second channels being disposed on either side of at least one row of third longitudinal channels, in which a second fluid circulates, to allow a heat exchange between the first fluid and the second fluid.
  • the invention provides that the first channels and the second channels are shaped in the vicinity of at least one of their ends so as to be received in the same opening provided in a first collector while the third channels are shaped in the vicinity of the at least one of their ends so as to be received in the same opening provided in a second collector.
  • the number of collectors is thus reduced. In addition their individual size is also reduced.
  • the channels being received by the same opening with respect to the first collector, the resistance of the latter at high pressures is improved. It is known that the junction between the channels and the collectors is often a delicate point because of the pressures involved. As a result, the reduction in the number of openings allows simpler manufacture and assembly.
  • the first channels and the second channels each have a length substantially greater than a length of the third channels so that each end of the first channels and the second channels protrude from each end of the third channels.
  • the first channels and the second channels are further shaped in the vicinity of each end so as to jointly define a free space of material adapted to accommodate the second collector, each end of the third channels opening at said space.
  • optimum compactness of the exchanger is obtained.
  • the number of collectors is reduced.
  • the second collector integrating at the body of the exchanger, it does not occupy space at the ends of the body, where are usually arranged the first collectors.
  • a more homogeneous bulk of the exchanger according to more homogeneous space of the exchanger according to its length is obtained.
  • a heat exchange between the first and the second fluid can take place at the second collector with the second channels bordering the free space of material.
  • the first channels and the second channels have a generally semicircular portion longitudinally, so that said space has a generally cylindrical shape of substantially semicircular section.
  • the cylindrical shape is particularly advantageous in the case of high pressures due to the balancing of the forces exerted by the fluid.
  • the second collector advantageously comprises a tube portion of generally circular section of diameter adapted to be housed in said space, the tube portion being externally in contact with the first channels and the second channels.
  • the production of the second collector in the form of a tube portion is simple to implement and can be expensive.
  • the contact between the tube and the channels allows additional heat exchange between the first and the second fluid.
  • the second collector comprises said space.
  • the compactness of the exchanger is further improved since the thickness of the collector does not have to be housed in the interior space. This saves raw material. The number of parts needed to assemble the exchanger is further reduced.
  • the second collector then further comprises plugs of suitable shape to close said space.
  • At least one of these plugs has an opening adapted to be connected to a tubular element.
  • the tubing element can then ensure the arrival or the exit of the second fluid and be connected to the rest of a circulation circuit of fluid.
  • the first and second channels each have a length substantially shorter than a length of the third channels so that each end of the third channels protrudes from each end of the first and second channels.
  • the first collector has a shape adapted to house the second collector.
  • the overall size of these collectors is also decreased. An additional heat exchange can take place since the second collector can be surrounded by first fluid, improving the performance of the exchanger.
  • the first collector advantageously comprises a portion of tube of generally circular section of diameter adapted to house the second collector.
  • This configuration offers the advantage of good resistance to pressure thanks to the geometry of the collectors (circular section). In addition, it allows a simple and inexpensive realization.
  • the second collector comprises a tube portion of generally circular section.
  • first collector and the second collector are made in one piece in one piece, said piece being preferably in the form of a single piece in which are formed a first recess forming the first collector and a second obviously forming the second collector.
  • the exchanger advantageously comprises stop means between at least one of the first and second collectors and the first, second and third channels respectively.
  • stop means allow positioning these elements together. They possibly offer a temporary position in waiting for a subsequent soldering operation. They also confer good behavior of the elements relative to each other.
  • abutment means preferably comprise at least one channel of length substantially greater than the length of the other channels received, this channel coming into abutment against the bottom of the respective collector, which constitutes a simple and inexpensive way to achieve these abutment means .
  • the abutment means may comprise in addition or in replacement a notch arranged externally in the vicinity of said at least one end of the channels and a lug protruding internally from the opening of the collector, the lug being movable in the notch until to reach a stop position, which is another simple and inexpensive way to achieve or complete the abutment means.
  • the abutment means comprise a generally flat surface formed in the upper part of at least one of the plugs, the generally flat surface bearing against the first collector.
  • At least one of the collectors prefferably comprise a tubing element adapted to be connected to the remainder of a fluid circulation circuit.
  • the elongated body comprises a first portion and a second generally flat portion in which are formed respectively the first channels and the second channels, the first and second parts resting on either side of a third generally flat part in which are formed the third channels.
  • This multi-part body configuration avoids complicated body machining that would otherwise be required.
  • the exchanger is designed as an internal heat exchanger for an air conditioning circuit traversed by a refrigerant fluid operating in the supercritical state.
  • the first and second fluids are a same fluid flowing at high pressure.
  • the configuration of the exchanger according to the invention in this case offers advantageous characteristics of resistance to pressure, in particular when the fluid flowing in the third channels is at a pressure greater than that of the fluid flowing in the first and second channels.
  • the heat exchanger 1 partially shown in FIG. 1 comprises an elongate body 3 in which longitudinal channels are provided for the circulation of either a first fluid or a second fluid, the first and second fluids being able to exchange with one another heat. Only one part of the body 3 is shown in Figure 1, the other part can be deduced by symmetry.
  • the channels pass through the body 3 and open at their ends into collectors.
  • the channels in which the first fluid flows open at their ends into first collectors 5 (only one is shown in FIG. 1), whereas the channels in which the second fluid flows open into second collectors 7 (only one is shown in Figure 1).
  • the collectors 5 and 7 can be respectively connected to the remainder of first and second fluid flow circuits.
  • the body 3 may consist of three elongate portions, each comprising at least one row of longitudinal channels.
  • An elongated portion comprising one or more rows of channels will be called “tube” in the remainder of this description.
  • the body 3 thus comprises a first tube 9 in the form of a generally rectangular, elongated, flat and monobloc piece.
  • a row of first longitudinal channels 11 is formed in the tube 9 allowing a longitudinal fluid flow.
  • the tube 9 could comprise several rows of channels 11.
  • the body 3 further comprises a second tube 13 similar to the tube 9 and comprising a row of second longitudinal channels 15.
  • body 3 finally comprises a third tube 17 in the form of a generally rectangular piece, flat and monobloc, in which are formed third longitudinal channels 19.
  • the tube 17 is interposed between the tubes 9 and 13, so that the channels 11 and the channels 15 are respectively disposed on either side of the channels 19.
  • each tube 9, 15 and 17 comprises two large substantially planar faces. Each large face of the tube 17 is in contact with a portion of one of the large faces of each of the tubes 9 and 13 respectively.
  • the tube 17 is shorter than the tubes 9 and 13 so that the ends of the latter protrude from the tube 17.
  • Each end of the tube 17 is received in a manifold 7 through an opening 21 (visible in Figure 8) whose contour is adapted to the contour of the tube 17.
  • the channels 19 thus provide a circulation of the second fluid of a collector 7 to the other manifold 7 (a single manifold 7 is shown in Figure 2).
  • Each end of the tubes 9 and 13 is received in a manifold 5 through the same opening 23 (visible in Figure 5) whose contour is adapted to the contour of the meeting of the contours of one end of each tube 9 and 13.
  • the tubes 9 and 13 thus each ensure a circulation of the first fluid of a manifold 5 to the other manifold 5.
  • Each tube 9 and 13 has over its entire width a deformation, respectively 25 and 27, over a portion of its length in the form of a curvature of the tubes 9 and 13 retaining the section of these tubes constant.
  • the body 3 assembled, the deformations 25 and 27 are arranged vis-à-vis so that they jointly define a free inner space 29, visible in Figure 3 in particular.
  • the deformations 25 and 27 are in the embodiment of Figure 2 half-cylindrical shape of semicircular section so that the space 29 has a general shape of cylinder circular section.
  • the collector 7 comprises a collecting portion 31 in which the opening 21 is formed in the form of a portion of straight cylindrical tube of substantially circular section.
  • the manifold 7 further comprises a connecting pipe 33, in the form of a cylindrical tube portion of circular section, connected to the portion 31 by an intermediate portion 35 in the form of a bent tube portion of also circular section.
  • the tubing 33 may be connected in fluid communication with the remainder of a second fluid circulation circuit.
  • the collector 7 may in particular be made from a straight cylindrical tube of circular section curved so as to form the portion 5 and to define the tubing 33 and the portion 31.
  • the collector 7 comprises a plug 37 closing sealing the end of the portion 31 opposite the portion 35. Any other means for closing this end can also be used.
  • the shape of the deformations 25 and 27 is adapted to allow the housing of the portion 31 in the space 29.
  • the outer surface of the portion 31 is in contact with the surface of the deformations 25 and 27, thus allowing a additional heat exchange between the second fluid flowing in the portion 31 and the first fluid flowing in this portion of the channels 11 and 15.
  • the collector 5 is made analogously to the collector 7 and thus comprises a collector portion 39 connected to a connection pipe 41 by an intermediate portion 43 bent.
  • the parts of the space 29 left free after the insertion of the part 31 and indicated in FIG. 3 by the circles A, B and C represent spaces in which the heat exchange between the first and second fluids is weak because of the absence of contact between the tubes 9 and 13 and the portion 31. These spaces A, B and C can be minimized to obtain better heat exchange performance.
  • the curvature 45 between the deformations 25 and 27 and the remaining tubes 9 and 13 respectively is such that the space A is reduced to the maximum.
  • the shape of the curvature 45 is dependent on the mechanical properties of the material used as well as geometric elements such as the thickness of the tube 9 (13 respectively) and / or its rigidity.
  • the portion 31 is surrounded by the tubes 9 and 13. At least partial compensation of the pressure forces applied internally against the portion 31 by the pressure force applied internally against the tubes 9 and 13 occurs. This leads to a better resistance to the pressure of the exchanger 1. Where appropriate this pressure compensation can be taken into account in the sizing of the tubes 9 and 13 and the portion 31 and lead in particular to a decrease in the thicknesses of these rooms. This results in a decrease in the mass of the exchanger, space and cost of raw material. It is known that in the case of a fluid flowing at high pressure (for example in the tube 17), the compensation, even partial, of the pressure forces has a particularly advantageous character.
  • the translational stop of the collector 5 and / or its positioning relative to the ends of the tubes 9 and 13 must be ensured. This contributes in particular to a temporary holding in position of the elements between them, for example while waiting for a soldering operation.
  • the purpose of the brazing operation is to definitively fix the elements together.
  • the portion 39 is based on the curvature 45 joining the deformations 25 and 27 at the ends of the tubes 9 and 13 respectively.
  • tenons 47 are provided facing each other projecting towards the inside of the opening 23.
  • the shape of the pins 47 is in accordance with the section of two blind grooves 49 formed externally on each of the tubes 9 and 13, in the vicinity of the end.
  • the pins 47 are thus adapted to slide inside the grooves 49 until reaching a final position in which the pins 47 rest on the bottom of the grooves 49.
  • the pins 47 are of trapezoidal section according to the section of the grooves 49. Any other form of pin 47 and groove 49 for a shape cooperation between the pins 47 and the grooves 49 may be used.
  • the section of the channels 15 is oval. More specifically, the section of a channel 12 here has two segments parallel to each other connected by semicircles. Sections of different shape can be used, for example round, rectangular or square.
  • the section of the channels 15 is advantageously provided identical to that of the channels 11 to obtain a symmetry in the heat exchange between the tubes 9 and 17 on the one hand and the tubes 17 and 13 on the other hand.
  • tubes 9 and 13 are identical, so that only one part model is to be manufactured. This reduces manufacturing costs.
  • the section of the channels 19 is not necessarily identical to that of the channels 11 and 15.
  • FIGS. 9 and 10 illustrate a second embodiment of the exchanger 1, in which the space 29 partially forms the second collector 7.
  • the fluid pressure forces applying against the tubes 9 and 13 at the level of deformations 25 and 27 internally (channels 11 and 15) and externally (space 29) tend to compensate, at least in part.
  • This entails the same advantages as those described above in the embodiment of FIGS. 2 to 4.
  • the elimination of the part 31 contributes to a still greater compactness of the exchanger 1.
  • the space 29 is closed on either side of the body 3 by a first plug 51 and a second plug 53, shown in detail in FIGS. 11 to 14.
  • the first cap 51 has an upper portion 55 whose inner contour is shaped to accommodate a lateral edge of each of the tubes 9 and 13, above the deformations 25 and 27.
  • the portion 55 is extended by a lower portion 57 whose contour is shaped to house a lateral edge of each of the tubes 9 and 13 at the deformations 25 and 27 and below them.
  • the plug 51 is traversed in the portion 57 by an orifice 59.
  • the plug 51 positioned at an upper corner of the tubes 9 and 13, the orifice 59 opens into the space 29.
  • the orifice 59 is bordered by a short centering 61 annular adapted to receive a junction tubing 63 visible in Figure 10.
  • the centering 61 is formed as a cylindrical portion of circular section.
  • the junction tubing 63 comprises a first junction portion 65 connected in fluid communication with the orifice 59 through the centering 61.
  • the portion 65 is formed as a straight cylindrical tube portion of circular section.
  • the tubing 63 further includes a second junction portion 67 connectable in fluid communication with the remainder of a second fluid circulation circuit.
  • the parts 65 and 67 are optionally connected by an intermediate portion 69, which is bent in this embodiment. It is understood that the configuration of the tubing 63 is a function of the constraints of arrangement of the exchanger in the motor vehicle and / or in the rest of fluid circulation circuits.
  • the plug 53 illustrated in FIGS. 13 and 14 is similar to the plug 51.
  • the plug 53 has an upper portion 71 similar to the portion 55 and a lower portion 73 similar to the portion 57.
  • the plug 53 has no orifice 59.
  • Each plug 51 and 53 has a portion 55 and 71 terminating at the top with a flat surface 75.
  • the collector 5 is supported on the surfaces 75 as shown in FIG. 15, so that it is both stopped in translation and positioned.
  • a third embodiment of the exchanger 1 is illustrated in Figures 16 and 17.
  • the tube 17 is longer than the tubes 9 and 13 so that it protrudes from their ends.
  • the tubes 9 and 13 are received in a first manifold 77.
  • the manifold 77 houses a second manifold 79 into which the tube 17 opens.
  • the manifold 77 is generally cylindrical in the form of a straight portion of circular section tube, while that the collector 79 is in the form of a straight portion of circular section tube of smaller diameter.
  • Collectors 77 and 79 of different shape may be used, for example parallelepipedal, provided that the collector 77 can be housed inside the collector 79.
  • a circular section is particularly suitable for high pressure fluids circulating cases.
  • the pressure forces applied internally to the collector 79 are at least partly compensated by the pressure forces due to the fluid contained in the manifold 77.
  • the collector 79 which is smaller in section, will therefore advantageously be devoted to a fluid at a higher pressure than the fluid of the collector 77.
  • the tubes 9 and 13 are flat; elongated and parallelogram-shaped, that is, their lower and upper edges are not perpendicular to the side edges. All channels 15 and 19, respectively, are of identical length but result in different heights in the collectors. Thus a corner of the end of the tubes 9 and 13 and on the other hand 17 abuts against the inside of the manifolds 77 and secondly 79. The translation stop mentioned above is thus achieved.
  • Other shapes of the tubes 9, 13 and 17 are conceivable. A symmetry between the lower and upper ends of these tubes is advantageous: it is then possible to obtain these tubes by cutting extruded strips with minimized material losses.
  • the manifolds 77 and 79 are closed by a common plug 81 on one side and by a connection box 83 on the other.
  • the connection box 83 is able to be connected to the remainder of circulation circuits of first and second fluids.
  • the heat exchanger 1 is, in all the embodiments described above, able to withstand high pressures.
  • the exchanger 1 is therefore particularly adapted to be integrated in an air conditioning circuit operating with a refrigerant fluid according to a supercritical cycle.
  • a refrigerant such as for example carbon dioxide
  • Such a circuit operates with a natural refrigerant, such as for example carbon dioxide, present in a single phase, namely a gas phase.
  • the operating conditions are such that the circuit generally exceeds the critical temperature of carbon dioxide (31.1 ° C) in most cases.
  • FIG. 18 illustrates such an air conditioning circuit, in particular for a motor vehicle, in which the heat exchanger 1 of the preceding figures can be integrated.
  • the circuit of FIG. 18 essentially comprises a compressor 85.
  • a refrigerant, for example carbon dioxide CO2 sent by the compressor 85 then passes through a gas cooler 87, from which it comes out in a state of high pressure and high temperature.
  • the fluid passes through the exchanger 1 through the channels 19 and is then expanded in a pressure reducer 89.
  • the fluid thus expanded is then conveyed to an evaporator 91 and to a battery 93, before joining the exchanger 1 in a state of low pressure and low temperature, through which it passes through the channels 11 and 15.
  • the exchanger 1 is traversed by the same fluid in different states. It is then generally referred to as the internal heat exchanger.
  • the value of the high pressure of the coolant influences the cooling performance, and this value can be very high, which imposes components and an assembly of these components capable of withstanding this pressure.
  • the fluid pressure can reach values of the order of 130 bar (high pressure).
  • FIG 19 partially illustrates another heat exchanger according to the invention in another embodiment.
  • the tubes 9 and 13 are made straight.
  • the tube 17 is made longer so that its ends protrude from the ends of the tubes 9 and 13.
  • the tubes 9, 13 and 17 are received in a general collector 95 made in the form of a single piece.
  • the collector 95 has an opening 101 shaped to allow the passage of the tubes 9, 13 and 17.
  • an additional opening 103 is provided between the recesses 97 and 99.
  • the opening 103 is shaped to ensure the passage of the tube 17.
  • the tubes 9 and 13 open into the recess 97, which thus forms a first collector 5.
  • the tube 17 enters the collector 95 through the opening 101, passes through the recess 97, and then opens into the recess 99 through the intermediate of the opening 105.
  • the recess 99 thus forms a second collector 7.
  • the recess 99 is here in the form of a cylindrical hole of circular section. This form gives it good resistance to pressure as explained above.
  • a part of the recess 97, in particular in the vicinity of the opening 105, is made to fit a part of the periphery of the recess 99. On this part, the forces due to a high pressure in the recess 99 can advantageously be compensated, at least in part, by the forces generated by a low pressure in the recess 97.
  • the collector 95 can be made in the form of a molded part in which the recesses 97 and 99 are machined. Connection means (not shown) to the remainder of fluid circulation circuits are provided. These connection means may comprise circular openings formed at the ends of the collector 95 and shaped to receive connecting tubes.
  • FIG. 20 partially illustrates a configuration of a tube 105 that can be used as tube 17 in particular.
  • the tube 105 is similar to the tube 17 described more.
  • the end of the tube 105 has a shoulder 107 made in the form of a section reduction.
  • the shoulder 107 borders an end section 109 in which there are fluid circulation channels, for example the channels 19.
  • the tube 105 is of rectangular section. It is the same for section 109.
  • Other configurations are possible, however, in which the section of section 109 and the section of tube 105 may be of identical shapes (oval section / oval section) or different (oval section / rectangular section).
  • the end of the tube 105 thus configured may be received in a manifold (not shown) having an aperture adapted to conform to the section 109, the shoulder 107 abutting against said collector.
  • This configuration of the tube 105 may be adapted for use in the exchanger of Figures 16 and 17 or Figures 2 and 3, in particular.

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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)
EP06013318A 2005-06-29 2006-06-28 Wärmetauscher mit erhöhter Kompaktheit und Druckfestigkeit Withdrawn EP1739375A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR0506622A FR2887971B1 (fr) 2005-06-29 2005-06-29 Echangeur de chaleur a compacite et resistance a la pression ameliorees

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EP1739375A1 true EP1739375A1 (de) 2007-01-03

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010091251A (ja) * 2008-09-11 2010-04-22 Daikin Ind Ltd 冷凍装置
CH700886A1 (de) * 2009-04-17 2010-10-29 M & M En Forschung Anstalt Flachwärmetauscher, sowie Verfahren zu dessen Herstellung.
FR2946132A1 (fr) * 2009-06-02 2010-12-03 Valeo Systemes Thermiques Unite d'echange thermique et echangeur thermique correspondant, procede de realisation d'une unite d'echange thermique.
DE102013217287A1 (de) * 2012-09-03 2014-03-06 Behr Gmbh & Co. Kg Innerer Wärmeübertrager für einen Kältemittelkreislauf, insbesondere für eine Klimaanlage eines Kraftfahrzeuges, und einen Kältemittelkreislauf mit einem Verdampfer
CN107796246A (zh) * 2017-10-23 2018-03-13 杭州三花研究院有限公司 换热系统及其换热器
EP3819579A1 (de) * 2019-11-07 2021-05-12 Valeo Systemes Thermiques-THS Wärmetauscher
EP4283236A4 (de) * 2020-08-26 2024-07-17 Gd Midea Heating & Ventilating Equipment Co Ltd Wärmetauscher, elektrischer steuerkasten und klimatisierungssystem

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Publication number Priority date Publication date Assignee Title
JP6596660B2 (ja) * 2015-10-30 2019-10-30 パナソニックＩｐマネジメント株式会社 熱交換器およびそれを備えた冷凍サイクル装置、ヒートポンプ給湯装置
CN110793353B (zh) * 2018-08-01 2021-03-30 杭州三花研究院有限公司 一种换热器及其加工方法

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JP2000346584A (ja) * 1999-06-02 2000-12-15 Denso Corp 熱交換器
US20030178188A1 (en) * 2002-03-22 2003-09-25 Coleman John W. Micro-channel heat exchanger
JP2004177006A (ja) * 2002-11-27 2004-06-24 Japan Climate Systems Corp 内部熱交換器
FR2850743A1 (fr) * 2003-01-30 2004-08-06 Visteon Global Tech Inc Unite de raccordement pour echangeur de chaleur a canaux multiples et echangeur de chaleur correspondant
DE10346141A1 (de) * 2003-10-01 2005-05-19 Eaton Fluid Power Gmbh Wärmetauschereinheit

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JP2010091251A (ja) * 2008-09-11 2010-04-22 Daikin Ind Ltd 冷凍装置
CH700886A1 (de) * 2009-04-17 2010-10-29 M & M En Forschung Anstalt Flachwärmetauscher, sowie Verfahren zu dessen Herstellung.
FR2946132A1 (fr) * 2009-06-02 2010-12-03 Valeo Systemes Thermiques Unite d'echange thermique et echangeur thermique correspondant, procede de realisation d'une unite d'echange thermique.
EP2273224A1 (de) * 2009-06-02 2011-01-12 Valeo Systèmes Thermiques Wärmeaustauscheinheit und entsprechender Wärmetauscher sowie Umsetzungsverfahren einer Wärmeaustauscheinheit
US9103604B2 (en) 2009-06-02 2015-08-11 Valeo Systemes Thermiques Heat exchange unit and corresponding heat exchanger, method of manufacturing a heat exchange unit
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CN107796246A (zh) * 2017-10-23 2018-03-13 杭州三花研究院有限公司 换热系统及其换热器
EP3819579A1 (de) * 2019-11-07 2021-05-12 Valeo Systemes Thermiques-THS Wärmetauscher
EP4283236A4 (de) * 2020-08-26 2024-07-17 Gd Midea Heating & Ventilating Equipment Co Ltd Wärmetauscher, elektrischer steuerkasten und klimatisierungssystem

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FR2887971B1 (fr) 2009-11-20

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