• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
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    • 专利摘要:
    The invention relates to a heat exchange device (4), for condensing heat exchanger. This device is remarkable in that it comprises: at least two concentric bundles (5, 5 ') of tubes of thermally good conducting material, inside which a coolant is intended to circulate, each bundle of tubes (5, 5') , 5 ') comprising a series of circular arc-shaped tubes (50, 50'), the tubes of each bundle (5, 5 ') being arranged in parallel planes with a gap (53, 53') between two adjacent tubes (50, 50 '), - a single collector (6) of thermally good conductor material to which are connected the two ends (51, 51', 52, 52 ') of each tube (50, 50) of the different beams (5, 5 '), this manifold (6) being provided with inlet (61) and outlet (62) connections and comprising a plurality of partitions (63, 64, 66, 67) delimiting different channels (72, 73, 74) , which put in communication the different tubes, the channels being arranged to allow the passage of said fluid in the set of tubes (50, 50 ') since the ra inlet connection (61) to the outlet connection (62).
    公开号:FR3047063A1
    申请号:FR1650529
    申请日:2016-01-22
    公开日:2017-07-28
    发明作者:Mer Joseph Le
    申请人:SERMETA；
    IPC主号:
    专利说明:

    GENERAL TECHNICAL FIELD
    The present invention relates to a heat exchange device, and a condensing heat exchanger equipped with such a device.
    Such an exchanger is in particular intended to equip a gas or oil boiler for industrial or tertiary applications, for example to supply a central heating circuit or a sanitary water circuit.
    STATE OF THE ART
    Many exchangers are already known in the art for transferring energy from a fuel to a fluid to be heated.
    Heat exchangers operating according to two principles share most of the market for heating and hot water production. These are the tube heat exchangers and water tube exchangers, so called depending on the fluid flowing inside said tubes.
    The so-called "smoke tube" exchangers generally have a high water capacity. They are therefore bulky and very heavy. In addition, their design gives them a high inertia against the needs of rapid temperature and power variations that are required for the intended applications.
    The so-called "water tube" exchangers generally have a low water capacity. They are less bulky, less heavy and also allow a temperature and power variation faster. Finally, their manufacturing cost to obtain the same nominal power is generally lower than that of the tube heat exchangers.
    However, it remains desirable to further improve the existing condensing heat exchangers and water tubes on the market.
    PRESENTATION OF THE INVENTION The object of the invention is to propose a condensing heat exchanger which: - is of extremely modular design, so as to make it possible to obtain power ranges ranging from a few tens to several thousand kilowatts , while using a single burner whose power is adapted accordingly, can greatly limit the pressure drops inside the water circuit, has a reduced power / size / weight ratio and therefore a lower cost than the heat exchangers operating according to other concepts, allows to obtain condensing thermal efficiencies reaching the maximum in terms of physical laws, allows the assembly of the tubes by means other than brazing, thus providing a greater longevity to For this purpose, the invention relates to a heat exchange device, for a condensing heat exchanger.
    According to the invention, this device comprises: at least two bundles of tubes made of thermally good conducting material, inside which a heat transfer fluid, such as water, is intended to circulate, each bundle of tubes comprising a series of of tubes each of which is in the form of a circular arc and has a first end and a second end, the tubes of each bundle being arranged in parallel planes with a gap, preferably of constant width, between two adjacent tubes, the different tube bundles being arranged concentrically, - a single collector of thermally good conductor material to which are connected the first end and the second end of each tube of the different bundles, so that these different ends open inside said collector, manifold being provided with an inlet connection for supplying heat transfer fluid heating and an outlet fitting for evacuation of said fluid once heated and comprising a plurality of internal partitions defining different channels, each channel for communicating the first or second ends of at least one group of at least two at least one bundle, either with said inlet fitting, or with said outlet fitting, or with the first or second ends of at least one group of at least two tubes of the same bundle or one another beam, the channels being arranged to allow the passage of the fluid to be heated in all the tubes from the inlet fitting to the outlet fitting.
    Thanks to these characteristics of the invention, and in particular to the concentric arrangement of the bundles of tubes, the heat exchange device is particularly compact while allowing many heat exchanges. Circulating the fluid in parallel in all the tubes of the same group of tubes makes it possible to limit the pressure drops.
    Finally, the fact that the collector is thermally good conductor material further increases the heat exchange.
    According to other advantageous and non-limiting features of the invention, taken alone or in combination: the collector comprises a bottom, an outer wall, a rear wall, a front wall and two side walls through which the first and second ends of the tubes of the different bundles open into the collector and these lateral walls extend in radial planes of a cylinder whose longitudinal axis passes through the center of the circles of the different tubes in an arc of a circle, - the interstices between two adjacent tubes of the different bundles are calibrated by means of spacers, - preferably said spacers are bosses or corrugations, formed in the wall of a tube, facing the wall of an adjacent tube of the same bundle, the tubes have an oval cross-section flattened so that they comprise two plane lateral faces parallel to each other and perpendicular to the longitudinal axis joining the centers of the circles of the tubes in an arc of circle, - the partitions which constitute the different channels extend in the collector longitudinally, transversely and / or diagonally, - the partitions which constitute the different channels extend on part or all of the height, the width or the length of the collector, the bundles of tubes are of different lengths. The invention also relates to a condensing heat exchanger associated with supply means or means for producing hot gases.
    According to the invention, this exchanger comprises at least one heat exchange device as mentioned above, in which a heat transfer fluid to be heated, such as water, is intended to circulate, said heat exchange device being disposed at adjacent said hot gas supply means or said hot gas generating means, in a position such that said hot gases pass into the interstices between the tubes of said heat exchange device.
    According to other advantageous and non-limiting features of the invention, taken alone or in combination: said heat exchange device is fixedly mounted inside a gas-tight envelope, this envelope having an evacuation sleeve gases, it comprises means for circulating said heat transfer fluid, and said supply means or said hot gas production means are arranged so that the hot gases pass radially at least a part of the length of the different bundles of tubes from inside to outside passing through the interstices formed between said tubes, before being evacuated outside the exchanger, via said exhaust duct; - The condensing heat exchanger comprises a thermal insulation disk, arranged perpendicularly to the longitudinal axis Χ1-ΧΊ passing through the center of the circles of the arcuate tubes, so as to close the center of the first beam, this disc having at its periphery a radial deflector ring gastightly inserted into the interstices between the tubes of the different bundles to the outermost tube bundle, so as to define a combustion chamber into which open or there are means for supplying or producing hot gases and a condensation chamber which extends between this baffle plate and the gas discharge sleeve, this heat exchanger being thus arranged that the hot gases pass radially through the inside outwards, first of all the part of the different concentric beams located upstream of the deflector plate, and this passed nt in the interstices formed between the tubes of said bundles, and then that they cross radially from the outside towards the inside, the part of the different concentric bundles located downstream of the baffle plate, passing through the interstices formed between the tubes said beams, before being discharged outside the exchanger, via said exhaust duct;
    In a preferred embodiment, the condensing heat exchanger comprises, opposite the combustion chamber, a number of tube bundles greater than the number of bundles of tubes located opposite the condensation chamber.
    Advantageously, the condensing heat exchanger is associated with means for producing hot gases which are a gas or oil burner.
    PRESENTATION OF THE FIGURES Other features and advantages of the invention will appear from the description which will now be made, with reference to the accompanying drawings, which show, by way of indication but not limitation, several possible embodiments.
    In these drawings: FIG. 1 is a longitudinal sectional view of a condensing heat exchanger according to a first embodiment of the invention taken along the sectional line 11 of FIG. 12, FIGS. are perspective views of a heat exchange device according to the invention, taken at two opposite angles of view, the rear end of the collector having been truncated in FIG. 3, FIG. 4 is a cross-sectional view. of the heat exchange device of FIG. 2 taken along a sectional plane represented by the line IV-IV in FIG. 2, FIG. 5 is a longitudinal sectional view of the heat exchange device of FIG. sectional plane P5, FIG. 6 is a cross-sectional view of the heat exchange device of FIG. 2 taken along a sectional plane represented by the line VI-VI, FIG. 7 is a plan view of the device of FIG. thermal exchanges of the fig 2, FIG. 8 is a perspective view of another embodiment of a heat exchange device according to the invention, FIGS. 9, 10 and 11 are longitudinal sectional views of various other modes of embodiment of condensation heat exchangers according to the invention, and Figures 12, 13 and 14 are perspective views of three condensing heat exchangers shown without the burner, which differ in the position of the inlet fittings and output.
    DETAILED DESCRIPTION
    Referring to Figure 1 attached, we can see a condensing heat exchanger 1. It comprises a gas-tight envelope 2, which delimits an enclosure inside which are mounted means 3 for producing hot gases or supplying hot gases and a heat exchange device 4 according to the invention. The casing 2 has approximately a generally cylindrical shape with a longitudinal axis XX ".
    This envelope 2 is closed at both ends by covers or facades. The term "front facade" refers to frontage 21 facing forward AV which is on the left in FIG. 1 and "rear facade", the opposite facade 22 which is at the rear rear of exchanger 1 The casing 2 has a bottom 23, with a mouth 24 for discharging the condensates. The casing 2 also includes a sleeve 25 for discharging the hot gases.
    In the exemplary embodiment shown in FIG. 1, this sleeve 25 is connected to the rear panel 22. However, this arrangement is not mandatory and in the embodiment of FIG. 9, it can be seen that the sleeve 25 can be connected to the upper wall 27 of the casing 2.
    The front panel 21 has an opening 210 adapted to receive a thermally insulated door 26 which supports a burner 3. The burner 3 is for example a gas or oil burner. It is preferably a cylindrical burner which extends along the longitudinal axis X-X '. This burner is a means of direct production of hot gases.
    Although this is not shown in the figures, it could however be replaced by means for supplying hot gases. These means make it possible to introduce hot gases through the door 26, inside the enclosure delimited by the envelope 2, these hot gases being produced outside the envelope 2.
    The heat exchange device 4 which will be described in more detail later also has a generally cylindrical shape of longitudinal axis Χ1-ΧΊ. It is mounted inside the casing 2 so that its axis X1-X 'is coaxial with the longitudinal axis X-X' of the casing 2.
    Finally, as can be seen in FIGS. 12 to 14, the casing 2 advantageously rests on a support 7.
    A first embodiment of a heat exchange device 4 according to the invention will now be described in relation to FIGS. 2 to 7.
    In this embodiment, the heat exchange device 4 comprises two bundles of tubes 5, 5 ', assembled together by means of a single manifold 6dit "mono-collector" 6.
    Each bundle of tubes 5, 5 'comprises a series of tubes 50, 50' respectively, of thermally good material, preferably of metal, for example stainless steel or aluminum.
    A coolant, for example water, is intended to circulate inside the tubes 50, 50 '.
    Each tube 50, 50 'has an arcuate shape whose center of the circle is located on the longitudinal axis Χ1-ΧΊ. These tubes are obtained for example by bending.
    Each tube 50 has a first end 51 and an opposite second end 52. Similarly, each tube 50 'has a first end 51' and a second end 52 '.
    The two bundles of tubes 5 and 5 'are arranged concentrically about the longitudinal axis Χ1-ΧΊ, the bundle 5, called "first bundle", being disposed inside the bundle 5 ", said" second bundle " In other words, the first beam 5 located inside has an outside diameter smaller than the inside diameter of the second beam 5 ".
    The two beams 5 and 5 'are thus spaced apart from one another by an interval E.
    This concentric arrangement makes it possible to maintain a central space inside which the burner 3 is housed.
    In each bundle 5, 5 ", the arcuate tubes 50, 50" respectively, are arranged in parallel planes, these different planes themselves being perpendicular to the axis Χ1-ΧΊ and two adjacent tubes 50, 50 respectively. are spaced apart from each other by a gap referenced 53, respectively 53. These interstices appear better in Figure 1, for example.
    Such interstices 53, 53 'are advantageously of constant width. They are defined using spacers consisting, for example by bosses or corrugations formed in the wall of a tube 50, respectively 50 'facing the wall of an adjacent tube 50, respectively 50'. These bosses 54, 54 'are for example formed by hydroforming.
    These bosses bear the reference 54 when they are on a tube 50 and the reference 54 'when they are on a tube 50 ".
    According to a first variant, the bundles of tubes 5, 5 'are arranged concentrically one inside the other so that their respective interstices 53, 53' are aligned in the same plane, as can be seen on Figures 1 and 9 to 11.
    According to another variant not shown in the figures, it is also possible to arrange the bundles of concentric tubes 5, 5 ', by shifting one of a half-step relative to the other, so that the tubes 50 beam 5 are facing the interstices 53 'formed between the tubes 50' of the beam 5 '.
    Advantageously, each tube 50, 50 'has an oval cross section flattened in the center, so that it has two plane parallel side faces and which extend in planes perpendicular to the longitudinal axis X1-ΧΊ of these tubes in an arc.
    Said planar side faces of the tubes 50, 50 'oriented rearward respectively bear the references 55, 55'. They are visible in FIG. 3. The opposite lateral plane faces of the tubes 50, 50 'facing forward AV respectively bear the references 56, 56'. They are visible in Figure 2.
    Advantageously, it will be noted that the bosses 54, 54 'are formed on only one of these lateral planar faces, for example the rear face 55, respectively 55' of the tubes 50, 50 '. They could, however, be formed on both sides 55, 56, 55 ', 56'.
    Also advantageously, these bosses 54, 54 'extend radially, that is to say along a radius of the circle of each of the tubes 50, 50' in an arc.
    Advantageously, the bosses 54, 54 'are uniformly distributed over the entire circumference of the arc.
    Finally, within each bundle of tubes 5, 5 'is designated "group of tubes", a group of at least two adjacent tubes within which the heat transfer fluid flows in parallel and in the same direction. In the embodiment shown in Figures 2 and 3, the first bundle of tubes 5 has two groups of tubes 50a, 50b, while the second bundle 5 'has two groups of tubes 50'a and 50'b referenced.
    As best seen in FIGS. 2, 12 and 13, collector tunnel 6 (or monocollector) is an element having substantially the shape of a parallelepiped, which comprises a bottom 600 oriented to Tax Χ1-ΧΊ, preferably plane, two walls. 601, 602, an outer wall 603 and two end walls, respectively a rear wall 604 and a front wall 605, so called because of their orientation relative to the front and back of the casing 2 when the device 4 is in this envelope.
    The outer wall 603 is not shown in Figure 2, in order to observe the interior of the collector 6 and also the front wall 605 appears in dotted lines.
    Advantageously, the collector 6 is also made of a thermally good conductive material, preferably metal, for example stainless steel or aluminum. The collector 6 being housed in the casing 2, this promotes heat exchange with the hot gases.
    Advantageously, the two side walls 601 and 602 are flared from the bottom 60 so that they extend, in radial planes P601, P602 of a cylinder of longitudinal axis Χ1-ΧΊ. The rear walls 604 and 605 before are substantially in the shape of isosceles trapezium, so as to adapt to the section of the collector 6.
    The side walls 601, 602 are pierced with a plurality of orifices 6010 and 6020, respectively, to which the first ends 51, 51 'of the tubes 50, 50' and the second ends 52, 52 'of the tubes 50, 50 are connected. . Thus the tubes 50, 50 'open into the manifold 6 and are in fluid communication therewith.
    Fixing the tubes on the walls 601, 602 of the collector is preferably performed by welding, or crimping or swaging depending on the thickness of the walls.
    The fact of having sidewalls 601, 602 which extend in radial planes of a cylinder of axis Χ1-ΧΊ makes it possible to use tubes 50, 50 'whose end sections 51, 52, 51' , 52 'are straight sections (ie perpendicular to the tube director). This simplifies the step of assembling the tubes on the walls 601, 602.
    However, the side walls 601 and 602 could also have a different orientation, for example being perpendicular to the bottom 600. The cutting plane of the ends 51, 52, 51 ', 52' would then be adapted accordingly.
    The collector 6 is provided with an inlet connector 61 which allows its supply of coolant (water) to be heated and an outlet connector 62 which allows the evacuation of said fluid once heated.
    In the exemplary embodiment shown in FIGS. 2 and 12, the inlet 61 and outlet 62 connections are disposed at the rear end of the manifold 6, the connection 61 opening into the manifold through the wall 601 and the connection 62 through the wall 602.
    However, other arrangements are possible. Thus, the inlet 61 and outlet 62 connections may be arranged at the rear end or front of the side walls 601 or 602, on the front face 605 or the rear face 604 or on the outer face 603.
    Moreover, the portion of the manifold 6 into which at least one of the connectors 61 and 62 opens may project out of the casing 2 (see FIGS. 12 and 13) or not (see FIG. 14).
    A plurality of partitions is further disposed within the manifold 6 so as to define a plurality of channels therein.
    These partitions are preferably made of the same material as the rest of the collector 6.Ce are advantageously thin sheets, welded together or to the walls of the collector. The embodiment shown in Figures 2 to 7 will now be described. In this case, the collector 6 comprises a horizontal longitudinal partition 63, called "median" because it extends between the two bundles of tubes 5 and 5 '. This partition 63 extends over the entire length of the collector 6 but only a portion of its width (about two-thirds) from the side wall 601.
    In the remainder of the description and the claims, the terms "horizontal" and "vertical" are to be considered in relation to the orientation of the device 4 in FIG.
    On the other hand, the collector 6 also comprises an upper vertical longitudinal partition 64, which extends over the entire length of the collector 6, over only a part of its height, namely the upper part from the partition 63 towards the outside (towards the upper wall 603).
    The collector 6 also comprises two vertical lower longitudinal partitions 65, 66. The partition 65 extends over only a portion of the length of the collector 6 from the rear AR to the half thereof; it is disposed substantially at one third of the width of the collector. The longitudinal partition 66 extends over the entire length of the collector, substantially at the second third of its width. The partitions 65, 66 extend between the bottom 600 and the partition 63, perpendicular to it.
    Finally, the collector 6 comprises a vertical transverse partition 67 which extends over the entire height of the collector 6, substantially in the middle of the length thereof, from the bottom 600 to the top wall 604 and over a part of the width of the collector (from the side wall 602 to the partitions 64 and 66).
    The collector 6 also comprises a second lower vertical transverse partition 68 which extends in the middle of the length of the collector, between the bottom 600 and the middle partition 63. This partition 68 joins the partition 65.
    The partitions 65, 63 and 68 form, with the bottom 600 and the side wall 601, a first channel 71 referenced. This channel 71 makes it possible to put in communication fluid the inlet connection 61 with the first ends 51 of the second group 50b of tubes 50 of the first beam 5.
    The partitions 64, 67 and 66 and part of the partition 63 delimit with the bottom 600, the upper wall 604 and the side wall 602, on the rear of the collector 6, a second channel 72. This second channel 72 puts in communication the second ends 52 of the second group 50b of tubes 50 of the first bundle 5 with the second ends 52 'of the second group 50'b of tubes 50' of the second bundle 5 '.
    The partitions 63 and 64 delimit with the upper wall 604 and the side wall 601, a third channel 73 which extends over the entire length of the collector 6. This third channel 73 makes it possible to connect the first ends 51 'of the second group 50' b tubes 50 'of the second beam 5' with the first ends 51 'of the first group 50'a of tubes 50' of the same beam.
    The partitions 64, 66, 67 and part of the partition 63 delimit with the upper wall 604 the bottom 600 and the side wall 602, forward AV of the collector 6, a fourth channel 74. This fourth channel 74 puts in communication the second ends 52 'of the first group 50'a of tubes 50' of the second bundle 5 'with the second ends 52 of the first group 50a of tubes 50 of the first inner bundle 5.
    Finally, the partitions 63, 66, 65 and 68 delimit with the bottom 600 and the front portion of the side wall 601, a fifth channel 75 which extends from one end to the other of the collector 6, presenting a further wide width forward and narrowing backward AR. This fifth channel 75 makes it possible to put the first ends 51 of the first group 50a of tubes 50 of the first inner bundle 5 into communication with the outlet fitting 62.
    The path of the gases will now be described in connection with FIG.
    In the exemplary embodiment shown in FIG. 1, a thermal insulation disk 30 is mounted inside the heat exchange device 4, perpendicular to its axis X1-ΧΊ.
    It extends facing the burner 3. It comprises at its periphery a radial deflector ring 31 which is inserted in a gas-tight manner in one of the interstices 53 of the first bundle 5 of tubes and in one of the interstices 53 ' of the second beam 5 ', while leaving a free annular space 28 between the outside of the second bundle 5' and the envelope 2, forcing the fumes to pass through the space 28.
    This thermal insulation disk 30 and the deflector 31 thus make it possible to separate the casing 2 of the exchanger 1 into a combustion chamber 11, inside which are the means for supplying or producing hot gases. 3 and a condensation chamber 12 extending between this thermal insulation disk 30 and the gas discharge sleeve 25, it being specified that according to the operating conditions, condensation can also occur in the combustion chamber.
    Such a provision is however not mandatory. It can thus be seen in FIG. 9 representing another embodiment, that the thermal insulation disc 30 can be placed close to the rear facade 22, the gas discharge sleeve 25 being then formed in the upper wall 27 of the casing 2. Such a heat exchanger then comprises only one chamber which acts as a combustion chamber 11.
    The hot gases escaping from the burner 3 pass radially from the inside to the outside first of all the interstices 53 between the tubes 50 of the first bundle 5 (arrows 11), then the interstices 53 'between the tubes 50'. the second beam 5 (arrows i2). They are thus guided because of the presence of the thermal insulation disk 30 and the deflector 31.
    The flow of very hot gases thus comes into contact with a relatively large surface of the wall of the tubes and by "licking" it thus ensures a very efficient heat exchange with the fluid to be heated circulating inside these tubes. The more the hot gases move radially outward and the more they cool, but they nevertheless contribute to a heat exchange with each bundle of tubes they pass through.
    When the hot gases reach the wall of the envelope 2 in the space 28, they are then guided backwards (arrows i3), reach the condensation chamber 12, and then cross radially, this time from the outside inwards, the interstices 53 'between the tubes 50' of the second bundle 5 '(arrows i4), then the gaps 53 between the tubes 50 of the first bundle 5 (arrows i5), before escaping through the gas discharge sleeve 25 (arrows i6).
    In the embodiment variant shown in FIG. 9, the hot gases escape only in one direction, namely radially from the inside towards the outside, in the direction of the casing and the gas discharge sleeve. 25.
    The flow of the fluid to be heated such as water will now be described in connection with Figures 2 to 7. The water is circulated using means such as a pump not shown. The cold water enters the inlet connection 61, passes through the first channel 71 (arrows j1), flows in the second group 50b of tubes of the first exchanger 5 and leaves at its other end in the channel 72 (arrows j2) . From there, the water returns to the second group 50'b of tubes of the second bundle 5 '(arrows j3) and spring at the first ends 51' thereof in the third channel 73. The water is thus preheated by crossing the cooled gases circulating in the interstices 53, 53 '. The water flows through the tubes of the first group 50'a located towards the front of the outer beam 5 '(arrows j4) flows through these tubes and leaves them in the fourth channel 74. In this, the water joins the first group 50a of the tubes 50 of the inner bundle 5 (arrows j5), then leaves to open into the channel 75 in the front part thereof. The water finally goes via the rear part of this channel to the outlet fitting 62 (arrows j6).
    It is thus understood that the fluid to be heated can flow between the inlet fitting 61 and the outlet fitting 62, having traversed all the tubes of the various bundles constituting the device 4.
    The hot gases circulate against the flow of the fluid to be heated, which allows a condensation operation.
    It is easy to understand that by using a number of different partitions, by arranging them over all or part of the length, height and width of the collector 6, it is thus possible to create different groups of tubes and to make channeling the fluid to be heated according to the desired path inside the bundles of tubes, this path being adjusted and adapted according to the power and the efficiency that one wishes to obtain with the heat exchange device 4, while having minimum pressure drop and avoiding any risk of overheating.
    Note that when there is a combustion chamber 11 and a condensation chamber 12, this insulation disc 30 may be facing the area between two adjacent groups of tubes or otherwise be opposite a given group of tubes, between two adjacent tubes of this group.
    A second embodiment of the invention will now be described with reference to FIG.
    On this, one can see a heat exchange device 4 'which differs from the device 4 described above in connection with Figures 2 to 7, in that it comprises three groups of tubes in each beam instead of two .
    The same elements as those described above bear the same numerical references. The three groups of tubes are referenced 50a, 50b and 50c for the first inner beam 5 and, respectively, 50'a, 50'b and 50'c for the second outer beam 5 '.
    In this figure, only two diagonal partitions 69, 69 'have been schematized by dotted lines and the other partitions present inside the collector 6 have not been shown for simplification purposes. However, the path of the fluid to be heated inside this manifold 6 will now be described.
    The fluid to be heated enters the inlet connection 61 from which it leaves to divide into two flows (arrows k1 and k6) which respectively supply the first ends 51 of the third group of tubes 50c of the bundle 5 and the first ends 51 of the third group of tubes 50'c of the second beam 5 '.
    The flows marked by the arrow k1 and k6 emerge from the tubes 50 respectively at the second ends 52 of the third group 50c of tubes and at the second ends 52 'of the third group 50'c of tubes and they are diagonally directed respectively towards the first ends 51 'of the second 50'b and the first group of tubes 50'a of the second beam 5' (arrows k2et k7) and emerge from their second ends 52 '.
    The flows that come out then penetrate both into the second ends 52 of the second group 50b of tubes of the inner beam 5 (arrows k3 and k8). The flow of liquid circulates inside the tubes 50 and leaves them from their first ends 51.
    The flow exiting from these first ends 51 is then directed diagonally towards the second ends 52 of the first group 50a of tubes of the first beam 5 (arrow k4). After circulating inside the tubes 50, the fluid leaves their first ends 51 and is then directed towards the outlet fitting 62 (arrow k5).
    It can thus be seen that, in this case, certain partitions may be diagonal, for example when it is a question of connecting the first ends of a given group of tubes, for example the first group of tubes at the second ends of the tube, second or third group of tubes. The diagonal partitions 69, 69 'are thus neither parallel to the longitudinal axis Χ1-ΧΊ, nor perpendicular to it.
    Moreover, it is observed that it is also possible to connect the first ends of a group of tubes from one of the beams to the second ends of a group of tubes of another beam. To do this, it is necessary to use inclined partitions, that is to say that are not parallel to the bottom 600.
    It is also possible to connect a group of tubes with several groups of tubes.
    Another embodiment of the invention will now be described with reference to FIG.
    This embodiment differs from the two previously described in that the heat exchange device 4 "comprises a third bundle 5" of tubes 50 "concentric with the other two and disposed outside the second bundle 5 '. third beams 5 ', 5 "are spaced apart from each other by an interval E1, which may be identical to or different from the gap E existing between the first and second beams, the interstices between the tubes 50" are referenced 53 ". 50 "tubes are not visible.
    Finally, the two embodiments shown in FIGS. 10 and 11 differ from the embodiment of FIG. 9, in that the bundles of tubes are not all of the same length. Thus, in the embodiment of FIG. 10, the third bundle 5 "of tubes is shorter than the other two bundles 5 and 5 ', so that there are three bundles of tubes facing the combustion chamber 11 and only two opposite the condensation chamber 12.
    Conversely, in the example shown in Figure 11, it is the first beam 5 which is shorter than the other beams 5 "and 5".
    It is easily understood that other embodiments are possible by varying the number of beams must be at least two, and using beams of the same or different lengths.
    Similarly, by varying the shape, length, height, width, arrangement and inclination of the various partitions positioned inside the collector 6, it is possible to form groups of tubes comprising more or less pipes, to make different paths between the inlet connection and the outlet connection and thus, to obtain heat exchange devices s having differences in power, compactness in length or in diameter, yield or losses load (pressure losses). In general, when it is desired to increase the power of the exchanger 1, it is possible to increase the number of tubes per beam, the dimensions of the section of the tubes, the diameter of the beams and / or the number of tubes. beams.
    To increase the yield, that is to say the ratio between the quantity of energy produced with respect to the quantity of energy supplied, it is possible for a given power to act on the aforementioned parameters and / or to increase the number of tubes in the condensation section.
    Furthermore, the monocollector 6 reduces the pressure losses with respect to a circulation in a helical tube, since it makes it possible to circulate the coolant in parallel in all the tubes of the same group. It also makes it possible to direct and share the heat transfer liquid flows between the beams in order to reduce the pressure drops and to avoid overheating.
    权利要求:
    Claims (13)
    [1" id="c-fr-0001]
    1. Heat exchange device (4, 4 ', 4 ") for a condensing heat exchanger, characterized in that it comprises: at least two bundles (5, 5', 5") of tubes of material thermally good conductor, within which a coolant, such as water, is intended to flow, each bundle of tubes (5, 5 ', 5 ") comprising a series of tubes (50, 50', 50 ") Each of which is in the form of an arc and has a first end (51, 51 ') and a second end (52, 52'), the tubes (50, 50 ', 50") of each beam (5 , 5 ', 5 ") being arranged in parallel planes with an interstice (53, 53', 53"), preferably of constant width, between two adjacent tubes (50, 50 ', 50 "), the different beams of tubes (5, 5 ', 5 ") being arranged concentrically, - a single collector (6) made of thermally good conducting material to which the first end (51, 51') is connected and the second end (52, 52 ') of each tube (50, 50', 50 ") of the different bundles (5, 5 ', 5"), so that these different ends open into said manifold, this manifold (6) being provided with an inlet fitting (61) for supplying heat transfer fluid for heating and an outlet fitting (62) for evacuation of said fluid once heated and comprising a plurality of internal partitions (63, 64, 65, 66, 67, 68, 69, 69 ') delimiting different channels (71, 72, 73, 74, 75), each channel making it possible to put in communication the first (51, 51') or the second ends (52, 52 ') of at least one group (50a, 50b, 50c, 50'a, 50'b, 50'c) of at least two tubes (50, 50', 50 ") of at least one beam (5, 5 ', 5 "), either with said inlet fitting (61) or with said outlet fitting (62), or with the first (51, 51') or second ends (52) , 52 ') of at least one group (50a, 50b , 50c, 50'a, 50'b, 50'c) of at least two tubes (50, 50 ') of this same bundle (5, 5', 5 ") or of another bundle (5, 5 ') ', 5' '), the channels being arranged to allow the passage of the fluid to be heated in all of the tubes (50, 50', 50 ") from the inlet fitting (61) to the outlet fitting (62). ).
    [2" id="c-fr-0002]
    2. heat exchange device (4, 4 ', 4 ") according to claim 1, characterized in that the collector (6) comprises a bottom (600), an outer wall (603), a rear wall (604). , a front wall (605) and two side walls (601, 602) through which the first and second ends (51, 51 ', 52, 52') of the tubes of the different beams (5, 5 ', 5 ") open into the collector (6) and that these side walls (601, 602) extend in radial planes of a cylinder whose longitudinal axis (X1-ΧΊ) passes through the center of the circles of the different tubes (50, 50 ', 50 ") in an arc.
    [3" id="c-fr-0003]
    3. Heat exchange device (4, 4 ', 4 ") according to claim 1 or 2, characterized in that the interstices (53, 53', 53") between two adjacent tubes (50, 50 ', 50 " ) of the different beams (5, 5 ', 5 ") are calibrated by means of spacers.
    [4" id="c-fr-0004]
    4. heat exchange device (4, 4 ', 4 ") according to claim 1 or 2, characterized in that said spacers are bosses or corrugations (54, 54'), formed in the wall of a tube ( 50, 50 ', 50 ") facing the wall of an adjacent tube (50, 50', 50") of the same bundle.
    [5" id="c-fr-0005]
    5. heat exchange device (4, 4 ', 4 ") according to one of the preceding claims, characterized in that the tubes (50, 50', 50") have an oval cross section flattened so that they comprise two plane lateral faces (55, 55 ', 56, 56') parallel to each other and perpendicular to the longitudinal axis (Χ1-ΧΊ) joining the centers of the circles of the tubes (50, 50 ', 50 ") circle.
    [6" id="c-fr-0006]
    6. Heat exchange device (4, 4 ', 4 ") according to one of the preceding claims, characterized in that the partitions (63, 64, 65, 66, 67, 68, 69, 69') which constitute the different channels (71, 72, 73, 74, 75) extend into the collector (6) longitudinally, transversely and / or diagonally.
    [7" id="c-fr-0007]
    7. Heat exchange device (4, 4 ', 4 ") according to one of the preceding claims, characterized in that the partitions (63, 64, 65, 66, 67, 68, 69, 69') which constitute the different channels (71, 72, 73, 74, 75) extend over part or all of the height, width or length of the collector (6).
    [8" id="c-fr-0008]
    8. Heat exchange device according to one of the preceding claims, characterized in that the bundles (5, 5 ', 5 ") of tubes are of different lengths.
    [9" id="c-fr-0009]
    9. Condensation heat exchanger (1), associated with supply means or means for producing hot gases (3), characterized in that it comprises at least one heat exchange device (4, 4). ', 4' ') according to one of claims 1 to 8, wherein a heat transfer fluid to be heated such as water, is intended to circulate, said heat exchange device (4, 4', 4 ") being disposed in the vicinity of said hot gas supply means or said hot gas generating means (3), in a position such that said hot gases pass into the interstices (53, 53 ', 53 ") separating the tubes (50, 50 ', 50 ") of said heat exchange device (4, 4', 4").
    [10" id="c-fr-0010]
    10. Condensation heat exchanger (1) according to claim 9, characterized in that said heat exchange device (4, 4 ', 4 ") is fixedly mounted inside a casing (2) sealed to gas, said envelope (2) having a gas evacuation sleeve (25), in that it comprises means for circulating said coolant, and in that said means for supplying or said gas generating means 3) are arranged in such a way that the hot gases pass radially at least a part of the length of the different bundles (5, 5 ', 5 ") of tubes (50, 50', 50") from the inside to the outside passing through the interstices (53, 53 ', 53 ") formed between said tubes (50, 50', 50"), before being evacuated outside the exchanger (1), via said sleeve evacuation (25).
    [11" id="c-fr-0011]
    11. condensing heat exchanger (1) according to claim 10, characterized in that it comprises a thermal insulation disk (30), arranged perpendicularly to the longitudinal axis) Χ1-ΧΊ) passing through the center of the circles tubes in an arc of a circle so as to close the center of the first bundle (5), this disk (30) having at its periphery a radial deflector ring (31) inserted in a gastight manner in the interstices (53, 53 '). , 53 "), existing between the tubes of the different bundles to the outermost tube bundle, so as to define a combustion chamber (11) into which the supply or production means of hot gases (3) and a condensing chamber (12) extending between this deflector plate (30) and the gas discharge sleeve (25), this heat exchanger being arranged so that the hot gases pass radially. from the inside to the outside, everything first the part of the different concentric beams (5, 5 ', 5 ") located upstream of the deflector plate (30), and this passing through the interstices (53, 53', 53") formed between the tubes of said beams (5, 5 ', 5 "), and then cross radially from the outside to the inside, the part of the different concentric beams (5, 5', 5") located downstream of the baffle plate ( 30), passing through the interstices (53, 53 ', 53 ") formed between the tubes of said bundles (5, 5', 5"), before being evacuated outside the exchanger, via said sleeve evacuation (25).
    [12" id="c-fr-0012]
    12. Condensation heat exchanger according to claim 11, characterized in that it comprises, opposite the combustion chamber (11), a number of beams (5, 5 ', 5 ") of tubes greater than the number of bundles (5, 5 ', 5 ") of tubes located opposite the condensation chamber (12).
    [13" id="c-fr-0013]
    13. Condensation heat exchanger according to one of claims 9 to 12, characterized in that it is associated with means for producing hot gases (3) which are a gas burner or fuel oil.
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    同族专利:
    公开号 | 公开日
    CN108474588A|2018-08-31|
    KR20180108694A|2018-10-04|
    CN108474588B|2021-05-18|
    EP3405723A1|2018-11-28|
    RU2018130211A3|2020-03-05|
    CA3011196A1|2017-07-27|
    US20190024942A1|2019-01-24|
    US11079137B2|2021-08-03|
    RU2717732C2|2020-03-25|
    RU2018130211A|2020-02-25|
    FR3047063B1|2018-11-30|
    WO2017125361A1|2017-07-27|
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    法律状态:
    2017-01-12| PLFP| Fee payment|Year of fee payment: 2 |
    2017-07-28| PLSC| Publication of the preliminary search report|Effective date: 20170728 |
    2018-01-12| PLFP| Fee payment|Year of fee payment: 3 |
    2020-01-10| PLFP| Fee payment|Year of fee payment: 5 |
    2021-01-13| PLFP| Fee payment|Year of fee payment: 6 |
    2021-12-10| PLFP| Fee payment|Year of fee payment: 7 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1650529A|FR3047063B1|2016-01-22|2016-01-22|THERMAL EXCHANGING DEVICE FOR CONDENSED HEAT EXCHANGER|
    FR1650529|2016-01-22|FR1650529A| FR3047063B1|2016-01-22|2016-01-22|THERMAL EXCHANGING DEVICE FOR CONDENSED HEAT EXCHANGER|
    PCT/EP2017/050833| WO2017125361A1|2016-01-22|2017-01-16|Condensation heat exchanger provided with a heat exchange device|
    CA3011196A| CA3011196A1|2016-01-22|2017-01-16|Condensation heat exchanger provided with a heat exchange device|
    EP17700814.1A| EP3405723A1|2016-01-22|2017-01-16|Condensation heat exchanger provided with a heat exchange device|
    KR1020187024248A| KR20180108694A|2016-01-22|2017-01-16|A condensing heat exchanger having a heat exchanger|
    US16/071,479| US11079137B2|2016-01-22|2017-01-16|Condensation heat exchanger provided with a heat exchange device|
    CN201780007328.8A| CN108474588B|2016-01-22|2017-01-16|Condensation heat exchanger provided with heat exchange device|
    RU2018130211A| RU2717732C2|2016-01-22|2017-01-16|Condensing heat exchanger equipped with heat exchanging device|
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