• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The heat exchanger (2) comprises: - a lower plate (4); an upper plate (6); a sheet (8) defining fins; the lower plate (4), the upper plate (6) and the sheet (8) forming a spirally wound three-layer structure, the lower plate (4) and the upper plate (6) defining between them a first passage (18); ) of the circulation of a first fluid. The heat exchanger (2) comprises a set (10) of spacers arranged in the first passage (18), these spacers being rods independent of the lower and upper plates (4). , 6).
    公开号:FR3020868A1
    申请号:FR1454146
    申请日:2014-05-07
    公开日:2015-11-13
    发明作者:Frederic Greber
    申请人:Faurecia Systemes dEchappement SAS；
    IPC主号:
    专利说明:

    [0001] Spiral heat exchanger and method of manufacturing the same The invention relates generally to heat exchangers. More specifically, the invention relates in a first aspect to a heat exchanger comprising: - a lower plate; - an upper sheet; a sheet defining fins; the lower sheet, the upper sheet and the sheet being superimposed and forming a three-layer structure spirally wound around a central axis and defining a winding, the first large faces vis-à-vis the lower sheet and the upper sheet defining between it a first flow passage of a first fluid, second large faces vis-à-vis the lower plate and the upper plate defining between them a second circulation passage of a second fluid in which is arranged the sheet. A heat exchanger of this type is known from WO 2005/017435. The lower and upper plates of this heat exchanger are stamped, so as to constitute the fluid inlet and outlet, and to maintain a constant spacing between the two sheets.
    [0002] The realization of a heat exchanger of this type is complex. In this context, the invention aims to provide a heat exchanger that is easier to manufacture. To this end, the invention relates to a heat exchanger of the aforementioned type, characterized in that the heat exchanger comprises a set of spacers disposed in the first passage, these spacers being independent rods of the lower and upper plates . Thus, it is possible to use for the realization of the heat exchanger flat sheets, not stamped. The spacers ensure the spacing between the lower plate and the upper plate, and thus allow to control the free section of the first pass.
    [0003] The heat exchanger may also include one or more of the following features, considered individually or in any technically feasible combination: - the spacer assembly includes a peripheral spacer, interposed between respective peripheral edges of the lower and upper laminations and sealing between said peripheral edges; the first passage has outer and inner circumferential ends located respectively radially further outside and radially further inside the heat exchanger, the spacer assembly comprising at least one central spacer extending circumferentially on the greater part of the length of the first passage and dividing the first passage into a forward leg and a return leg parallel to one another and communicating with each other at the inner end, preferably only at the inner end; the exchanger comprises a first fluid inlet communicating with the forward leg at the outer circumferential end and a first fluid outlet communicating with the return branch at the outer circumferential end; the exchanger comprises a cylindrical outer envelope in which the winding is inserted; the lower and upper laminations form a determined number of turns around the central axis, the sheet forming one more revolution than the lower and upper laminations, the said further lap being interposed between the upper plate and the outer casing; the exchanger comprises an inner tube around which the three-layer structure is wound, the inner tube being a rolled sheet with superposition of two axial edges of said rolled sheet, and / or the outer envelope being a rolled sheet with superposition of two axial edges of said rolled sheet; and - the sheet defining the fins is a folded sheet crenellated, said slots constituting the fins. According to a second aspect, the invention relates to a method of manufacturing a heat exchanger having the following characteristics: - formation of the three-layer structure by superimposing the lower sheet, the upper sheet and the sheet, with interposition the set of spacers in the first passage between the lower and upper plates; winding the three-layer structure in a spiral around the central axis. The method may also comprise one or more of the following characteristics, considered individually or in any technically possible combination: it comprises a step of pressurizing the first passage to press the upper sheet against the sheet, carried out after the step winding; - It comprises a step of fixing a first fluid inlet tube and a first fluid outlet tube on the upper plate, performed before the forming step and the winding step; and it comprises a step of inserting the winding into a cylindrical envelope. According to yet another aspect, the invention relates to an exhaust line comprising a heat exchanger having the above characteristics, the second circulation passage being fluidly connected to an exhaust gas circulation duct, and the first passage being interposed in a heat recovery circuit in which circulates a coolant. Other characteristics and advantages of the invention will emerge from the detailed description which is given below, by way of indication and in no way limitative, with reference to the appended figures, among which: FIG. 1 is a perspective view, exploded of certain elements of the heat exchanger of the invention, before winding; - Figure 2 is a side view of the sheets and the sheet defining the fins, after winding; - Figure 3 is a side view of the complete exchanger; FIG. 4 is a schematic view from above of the heat exchanger of FIG. 3; FIG. 5 is a step diagram of the manufacturing method of the invention; FIG. 6 is an enlarged view of a portion of FIG. 2, showing the deformation of the sheets after pressurization of the first passage; and FIG. 7 is a simplified schematic representation of an exhaust line comprising the exchanger of the invention. The heat evaporator shown in the figures is typically intended to be implanted in a vehicle exhaust line. The vehicle is for example a motor vehicle, typically a car or a truck. This heat exchanger is for example an evaporator for a Rankine type circuit. The exhaust gas flows from one side of the evaporator. A heat transfer fluid flows from a second side of the heat exchanger, the exhaust gas yielding a portion of their heat energy to the heat transfer fluid through the evaporator. The heat transfer fluid can be of any type: water, ethanol water mixture, refrigerant type R134 or R245FA, or any other type of organic fluid compatible with a Rankine cycle. This fluid enters the liquid form in the heat exchanger, and is evaporated by thermal contact with the exhaust gas. Alternatively, the heat exchanger is not an evaporator but a simple heat exchanger between two fluids. Each of these fluids can be in gaseous or liquid form.
    [0004] The heat exchanger can be used not only on an exhaust line, but at any other point of a motor vehicle, or even in any kind of industrial installation. As shown in Figure 1, the heat exchanger 2 comprises: - a lower plate 4; an upper plate 6; a sheet 8 defining fins; and a set of spacers interposed between the lower plate 4 and the upper plate 6.
    [0005] As can be seen in particular in FIGS. 2 and 3, the lower sheet 4, the upper sheet 6 and the sheet 8 are superimposed and form a three-layer structure wound in a spiral around a central axis X, thus forming a winding 12. first large faces 14, 16 vis-à-vis the lower plate 4 and the upper plate 6 define between them a first passage 18 for circulation of a first fluid. Second large faces 20, 22 opposite the lower plate 4 and the upper plate 6 define between them a second passage 24 for circulation of a second fluid, in which the sheet 8 is arranged. second large faces 14, 20 of the lower plate are opposite to each other. The first and second major faces 16, 22 of the upper plate are opposite to each other. The lower plate is for example stainless steel like 316L. Alternatively, it is in 1.4301 (austenitic steel) or 444 (ferritic steel). It has a thickness of between 0.1 and 0.4 mm, preferably between 0.15 and 0.3 mm, and is for example 0.2 mm. The upper plate 6 is typically made of the same material and has the same thickness as the lower plate 4. In the example shown, the lower and upper plates 4 and 4 each have, in the developed state, a rectangular shape. They are delimited each by two long sides respectively 26, 28, and by two small sides respectively 30, 32. Alternatively, the lower and upper plates 4, 6 do not have a rectangular shape but any other suitable form. The three-layer structure is wound so that the short sides 30, 32 are parallel to the central axis X, and the long sides 26, 28 are wound circumferentially about the X axis.
    [0006] As shown in the figures, the spacers are arranged in the first passage 18 and allow to maintain a predetermined spacing between the first major faces 14, 16 of the lower and upper plates. These spacers are independent of the lower and upper plates 4, 6. This means that the spacers are separate parts of the lower and upper plates 4, 6. They are not integral with the lower and upper plates 4, 6. They are not constituted by reliefs formed in the lower and upper plates 4, 6, for example by stamping of these sheets. The spacers are inserts between the lower and upper plates 4, 6.
    [0007] As shown in Figure 1, the spacers are rods. More specifically, the spacers are metal rods of flat section. Here is meant by rod a profile of elongate shape, preferably of solid section. This section is small in relation to the length of the profile. This section is preferably rectangular, but perhaps also slightly oval or have any other suitable form. For example, each spacer 10 has a substantially rectangular section, with a width of between 1 and 20 mm, preferably between 5 and 15 mm, and being for example 10 mm. Each spacer 10 has a section of thickness between 0.1 and 1 mm, preferably between 0.3 and 0.7 mm and still more preferably about 0.5 mm. The spacers 10 are typically in the same material as the lower and upper plates 4, 6. Alternatively, they are in a different material. The fact of using rods as spacers ensures the thickness of the first passage 18, without significantly increasing the heat transfer coefficient of the first fluid to the lower and upper plates 4 and 6. The rods do not hinder the winding of the three-layer structure because they have a reduced section and therefore a moderate rigidity. The spacer assembly includes a peripheral spacer 34 interposed between the respective peripheral edges of the lower and upper laminations 4, 6 and sealing between said peripheral edges. For example, the lower plate 4 and the upper plate 6 are sealingly welded to the peripheral spacer 34. In the example shown, the peripheral spacer 34 comprises two longitudinal rods 36 extending along the long edges 26, 28 of the lower and upper plates, and two transverse rods 38 extending along the small edges 30, 32 of the lower and upper plates.
    [0008] The peripheral spacer 34 constitutes a frame with a closed contour delimiting an empty central space. In the example shown, the rods 36, 38 are rigidly fixed to each other, for example by welding. Within the coil, the rods 38 are parallel to the X axis, and the rods 36 are circumferentially wound around the X axis. The spacer assembly 10 further comprises at least one central spacer 40 extending circumferentially over most of the length of the first passage 18, and dividing the first passage 18 into at least one forward leg 42 and a return leg 44 parallel to each other.
    [0009] Specifically, the first passageway 18 has outer and inner circumferential ends 46, 47 located respectively radially further outside and radially further inside the heat exchanger (see Figure 3). At the outer circumferential end, the central strut 40 extends to the peripheral strut 34 and thus isolates the forward leg 42 and the return leg 44 from each other. This is visible in particular in Figure 1, which is a developed view of the spacers. On the other hand, at the inner circumferential end of the first passage, the central spacer 40 does not extend to the peripheral spacer 34. Thus, the forward leg 42 and the return leg 44 communicate at the level of the inner circumferential end 47 through an opening 48. In the example shown, the opening 48 is delimited between one end 49 of the central spacer 40 and the peripheral spacer. Thus, there is arranged a U-shaped circulation for the first fluid within the first passage 18. Preferably, the passage section offered to the first fluid in the forward leg 42 is equal to the passage section in the return branch 44 and is equal to at the passage section at the opening 48. According to an alternative embodiment not shown, the assembly 10 comprises two central spacers parallel to each other, and placed head to tail. A first center spacer is disposed as illustrated in FIG. 1, so as to extend to the circumferential strut at the outer circumferential end 46. It provides an opening at the inner circumferential end 47 of the First passage. Another central spacer extends to the circumferential strut 34 at the inner circumferential end 47 of the first passage, but provides an opening at the outer circumferential end 46. Thus, it is created within the first passage a circulation in baffles for the first fluid.
    [0010] As can be seen in FIG. 1, the assembly 10 also comprises at least one intermediate spacer 50. The intermediate spacer (s) 50 are preferably regularly distributed in the space delimited internally by the peripheral spacer 34. They make it possible to guarantee the spacing between the lower plate 4 and the lower plate 6, in the areas of these sheets which are not located near the central spacer or the peripheral spacer. They also make the heat exchanger more rigid. In the example shown, the assembly 10 comprises a single intermediate spacer 50, having a shape of U. The spacer 50 comprises a first rod 52 extending in the center of the forward leg 42, over most of the circumferential length of the branch 42. It also comprises a second strip 54, extending substantially along and in the middle of the return branch 44, over most of the circumferential length of this branch 44. The intermediate spacer 50 comprises again an arcuate strip 56 which passes through the opening 48. The arcuate strip 56 extends from a circumferentially inner end 58 of the first strip 52 to the circumferentially inner end 60 of the second strip 54. Slight interruptions separate the rods 52, 54 and the arcuate strip 56 The intermediate spacer does not contribute to obtaining a U or S circulation, because it does not extend to the entrance peripheral height 34.
    [0011] Furthermore, as can be seen in particular in FIG. 1, the heat exchanger comprises a first fluid inlet 62 communicating with the forward leg 42 at the outer circumferential end 46 of the first passage, and an outlet 64 of the first communicating fluid. with the return leg 44 at the outer circumferential end 46.
    [0012] To do this, the upper plate 6 has inlet and outlet ports 66, 68 opening respectively into the branches 42 and 44. The exchanger 2 further comprises input and output tubes 70, 72 welded sealed to the upper plate 6 and placed in register with the orifices 66 and 68. The orifices 66 and 68 are located near one of the edges 32 of the upper plate.
    [0013] The sheet 8 is typically a folded sheet so as to define a plurality of slots 74 constituting the fins, parallel to each other. As can be seen in FIG. 1, the sheet 8 has substantially the same width, taken along the X axis, as the lower and upper plates 4 and 6. The slots 74 all extend parallel to the axis X.
    [0014] As can be seen in FIG. 2, each slot 74 has a substantially U-shaped cross section, considered perpendicular to the X axis. Each slot 74 thus has a flat top 76, extended by two sidewalls 78. Two neighboring slots 74 are connected to one another. to the other by a substantially flat bottom 80. The bottom 80 connects to each other the flanks 78 vis-à-vis the two neighboring crenellations. The top 76 and the bottom 80 are of substantially circumferential orientation, and the flanks 78 have a substantially radial orientation with respect to the axis X. The sheet 8, before winding, is placed under the bottom plate, so that the vertices 76 slots are pressed against the lower plate 4. Thus, after winding, the funds 80 of the sheet are pressed against the upper plate 6. More specifically, for each tower of the three-layer structure, the peaks 76 of the slots are pressed against the lower plate 4 of the same turn, and the funds 80 are pressed against the upper plate 6 of the previous round, that is to say the turn radially immediately further inside. As seen in Figure 3, the sheet 8 circumferentially has a length greater than that of the lower and upper plates 4 and 6. It performs an additional turn. The sheet 8 is typically 316 type austenitic stainless steel. Alternatively, it is aluminum or 1.4301 (austenitic steel) or 444 (ferritic steel). It is made from a sheet of 0.2 mm thick. The slots have for example a height of between 2.5 and 10 mm, and being for example 3.7 mm.
    [0015] The slots are arranged circumferentially with a regular pitch, for example a pitch of between 1.5 and 5 mm, and typically being 3.2 mm. As can be seen in FIG. 3, the heat exchanger 2 comprises an inner tube 82 around which the winding of the three-layer structure is carried out. The inner tube 82 is substantially coaxial with the X axis.
    [0016] In an exemplary embodiment, the inner tube 82 is a rolled sheet, with a slight overlap of the two edges 84, 86 of said sheet. The edges 84 and 86 delimit the sheet parallel to the axis X and are rigidly fixed to each other. Advantageously, a shim 88 is interposed radially between the edges 84 and 86. Thus along the edge 86 is created a step of a height substantially corresponding to the cumulative thickness of the sheet 8, plates 4, 6 and the whole The upper sheet 6 has an excess length 90 which extends circumferentially slightly beyond the sheet 8, for example 10 millimeters (mm). This excess length 90 is rigidly fixed to the central tube 82, and more precisely to the edge 86. The sheet 8, the lower plate 4 and the spacer 34 abut against the edge 86 and against the shim 88.
    [0017] At the first turn of the three-layer structure, that is to say the radially innermost turn, the bottoms 80 bear against the inner tube 82. The central tube 82 has an average diameter which is for example 40 mm. As also shown in Figure 3, the exchanger 2 comprises a cylindrical outer casing 92 in which is enclosed the winding 12. The outer casing 92 is coaxial with the axis X. In the embodiment of Figure 3 this envelope is made from a sheet rolled around the axis X. It thus has two edges parallel to the X axis 94, 96, which overlap and which are rigidly fixed to one another. In the example shown, the edge 94 is folded towards the inside of the exchanger. Edge 96 is bent outward. The edge 94 is placed above the edge 96, that is to say radially outwardly with respect to the edge 96. Thus, along the edge 96, a step whose height corresponds to three times the thickness sheet metal. This step is of height substantially corresponding to the cumulative thickness of the sheet 8, the upper and lower plates 4 and 6 and spacers. It should be noted that, along the last turn of the sheet 8, that is to say of the turn located radially the outermost of the winding, the flat tops 76 are in abutment against the inner surface of The casing 92. The arrangement shown in FIG. 3 has the advantage that it is possible to spirally wind the three-layer structure with a substantially uniform pressure at any point of the winding. In the absence of a step at the inner tube and the outer shell, the two circumferential ends of the three-layer structure would experience greater compression and deformation. This deformation could lead to the appearance of hot spots when using the heat exchanger. The deformation could irreversibly damage the sheets, which would create leaks. As can be seen in FIG. 4, the outer envelope 92 advantageously comprises two cylindrical portions 98, 100. The portions 98, 100 are in contact with one another by their respective slices, the contact plane being substantially perpendicular to the X axis. The cylindrical portions 98 and 100 are sealed to one another. Each of the two cylindrical portions 98, 100 is delimited towards the other cylindrical portion by a circumferential edge in which is provided a notch, respectively 102, 104. The inlet and outlet tubes 70, 72 come out of the outer casing 92 respectively by the notch 102 and the notch 104. The space between the tubes 70, 72 edges of notches 102, 104 is closed and sealed by any suitable means.
    [0018] The manufacturing process of the heat exchanger will now be detailed, with reference to FIGS. 5 and 6. The method comprises at least the following steps: - preferably welding the inlet and outlet tubes 70, 72 on the sheet upper 6 (step 110); - Overlay the lower plate 4, the set of spacers 10 and the upper plate 6 (step 112); - Preferably weld the lower and upper plates 4 and 6 to the spacers (step 114); - superimpose the sheet 8 to the lower and upper plates 4 and 6 (step 116); winding the spiral three-layer structure around the central axis X (step 118); preferably placing the winding in the cylindrical outer envelope 92 (step 120); pressurizing the first passage to press the upper plate against the sheet 8 (step 122); - Close preferably the central tube (step 124). Typically, the orifices 66 and 68 are already made in the upper plate, before the start of step 110.
    [0019] In step 114, the lower and upper plates 4 and 6 are each welded to all the spacers. The weld makes it possible to seal between the lower and upper plates 4 and 6 and the peripheral spacer 34. The central spacer 40 is first locked in position on the plate 4 by welding spots. Then, once the sheet 6 is laid, the sheets 4 and 6 and the central spacer 40 are welded together tightly. The spacer 50 is welded in the same way, except that it is not necessary to weld it continuously over its entire length. It is possible to obtain the sheet 8 with the fins already formed. Alternatively, the method comprises a step of forming the fins, including crenellations 74, from a flat sheet.
    [0020] In step 116, the sheet 8 is pressed against the bottom plate 4, and is rigidly attached thereto. More specifically, an end 126 of the sheet 8, intended to be placed radially the innermost inside the heat exchanger, is fixed by a few soldering points on one end of the bottom plate 4 located opposite the inlet and output 62, 64. The end 126 of the sheet 8 is slightly shifted towards the inlet and outlet 62 and 64 so as to create the excess length 90, along which the lower sheet 4 is not covered by the sheet 8.
    [0021] In a variant, the sheet 8 is not rigidly fixed to the sheet 4. In order to carry out the winding step 118, the inner tube 82 is first obtained and the length 90 is fixed to the internal tube 82. The structure three-layer is then wrapped circumferentially around the inner tube.
    [0022] In step 120, the two cylindrical portions 98, 100 of the outer casing are placed around the winding. They are put in place by axially sliding each of the parts around the winding 12. The portions 98, 100 are oriented angularly about the axis X so that the tubes 70, 72 engage in the notches 102 , 104.
    [0023] Alternatively, the outer shell 92 is rolled around the coil 12 and the edges 94, 96 are then welded to each other. In this case, the envelope 92 does not consist of two parts 98, 100 but is in one piece. During the winding step 118, there is a deformation of the lower and upper plates 4 and 6.
    [0024] The radial spacing between the second large faces 20, 22 is maintained during the winding, due to the rigidity of the sheet 8. The free section of the second passage 24 is thus retained. The lower plate 4 bears on the sheet 8, in particular on the crenellations 74, and therefore adopts a regular spiral shape. This is however not true for the upper plate 6. Some areas of the upper plate 6 are supported on the spacers, and will adopt a spiral shape. On the other hand, the areas of the upper plate 6 which are not resting on a spacer will bear against the lower plate 4. This is due in particular to the fact that the sheets are thin. The step 122 of overpressure of the first passage allows the final establishment of the upper plate 4, against the fins of the next turn. To do this, the first pass is maintained at a relatively high internal pressure of several tens of bars. For example, for lower and upper plates of 0.2 mm thick, the pressure is of the order of 35 bars. This pressure has the effect of taking off the upper plate 6 of the lower plate 4 and to press the upper plate 6 against the fins immediately above. This also has the effect of soliciting the lower plate strongly against the fins of the same turn. As shown in Figure 6, some areas 128 of the upper plate 6 then come into contact with the funds 80 connecting the slots 74 between them.
    [0025] Other zones 130 of the upper plate 6 are situated at the right of the crenellations 74, between the flanges 78. The zones 130 will adopt a concave shape, penetrating slightly into the internal volume of the crenellations 74. A similar deformation is observed at the level of the crenellations 74. the lower plate 4. Some zones 132 are urged during the pressurization against the peaks 76 of the crenellations. Other zones 134, situated between two vertices 76 will adopt a concave shape, and penetrate slightly in the free space separating two crenellations 74. In other words, there is deformation of the lower and upper plates 4 and 6 of such so that the upper sheet marries the base of the crenellations, and that the lower plate marries the summit of the battlements. These deformations make it possible to block the fins in position, and to prevent any sliding of the fins relative to the lower and upper plates. In step 124, the central tube 82 is closed internally. This makes it possible to force the second fluid to flow axially between the fins in the second passage.
    [0026] The heat exchanger 2 is for example used in an exhaust line, as illustrated in FIG. 7. The second circulation passage is fluidly connected to an exhaust gas circulation duct. The first passage is interposed in a heat recovery circuit in which circulates a heat transfer fluid. The heat exchanger 2 operates as an evaporator.
    [0027] A divergent 136 connects the outer casing 92 to a conduit 138 for supplying exhaust gas. This duct 138 is connected to a not shown manifold, which captures the exhaust gas leaving the combustion chambers of the engine. A convergent 140 connects the outer casing 92 to an exhaust gas discharge conduit 142. The conduit 142 is connected to an exhaust gas release cannula in the atmosphere (not shown), with the interposition of one or more exhaust gas purification members. The heat exchanger 2 is delimited radially outwards by the outer envelope, and is defined axially by two large faces 144, 146, substantially perpendicular to the axis X. The second passage 24 is open at the two major 144, 146. The divergent 136 covers the face 144, and distributes the exhaust gas arriving from the duct 138 over the entire large face 144. Conversely, the convergent 140 covers the large face 146 and captures the exhaust gas exiting second passage 24. The exhaust gas flows axially through the heat exchanger, into the different channels created by the fins. The exhaust gases give a first part of their thermal energy to the first fluid through the lower plate and the upper plate, and a second part to the fins defined by the sheet 8. The fins transfer this second part to the lower and upper plates 4 and 6 by conduction. The exchanger 2 is also connected to a circuit 148 for heat recovery. This circuit comprises a circulation member, such as a pump 150, which forces the first fluid towards the inlet 62. It also comprises an expansion member 151, for example a turbine, in which the steam leaving the exchanger heat 2 through the outlet 64 is expanded to a low pressure. The circuit 148 further comprises a condenser 152, interposed between the outlet of the expansion member 151 and the suction of the pump 150.
    [0028] The first fluid injected into the heat exchanger through the inlet 62 traverses the forward leg 42 circumferentially from the outer circumferential end 46 to the inner circumferential end 47, passes through the opening 48 and travels through the return leg 44. reverse direction, circumferentially from the inner circumferential end 47 to the outer circumferential end 46. It leaves the heat exchanger through the outlet 64. Due to the presence of the fins in the second passage 24, the coefficient of The exchange between the exhaust gases and the lower and upper plates is considerably increased. In the absence of fin, it is of the order of 150 Watts / m2 Kelvin. On the other hand, on the side of the first fluid, this exchange coefficient is of the order of 1000 Watts / m2 Kelvin when the fluid is in the liquid state, 10,000 to 15,000 Watts / m2 Kelvin during the evaporation of the first fluid. fluid, and about 400 Watts / m2 Kelvin for superheated steam at 35 bar (case of a mixture of water, ethanol 70 -30%). The presence of fins makes it possible to bring the exchange coefficient on the exhaust gas side closer to the exchange coefficient on the fluid side. Thus, the efficiency of the heat exchanger is much greater, especially when it operates as an evaporator. Moreover, the manufacture of this heat exchanger is facilitated. In particular, the lower and upper plates are not stamped. The assembly of the various elements of the heat exchanger is simple, in particular because the fins are not brazed on the lower plate 4 or the upper plate 6.
    [0029] Finally, the exchanger essentially comprises thin sheets, and is therefore particularly light. It has a low thermal inertia. In a variant, the fins are brazed to the lower and upper plates 4 and 6. For this purpose, by any appropriate means, strips of filler metal are placed between the peaks 76 of the crenellations and the bottom plate, and between the bottoms 80 and the upper plate.
    [0030] After the pressurization step 122, the heat exchanger is placed in an oven, the first passage being kept under pressure by an inert gas (for example nitrogen, or any other inert gas). This gas is under sufficient pressure to press the plates 4 and 6 on the fins during brazing operations. The brazing used is based on nickel with a melting temperature of about 1100 ° C.
    权利要求:
    Claims (12)
    [0001]
    CLAIMS1.- Heat exchanger (2) comprising: - a lower plate (4); an upper plate (6); a sheet (8) defining fins; the lower sheet (4), the upper sheet (6) and the sheet (8) being superimposed and forming a three-layer structure spirally wound around a central axis (X) and defining a winding (12), first large faces (14, 16) vis-à-vis the lower plate (4) and the upper plate (6) defining between them a first passage (18) for circulation of a first fluid, second large faces ( 20, 22) facing the lower plate (4) and the upper plate (6) defining between them a second passage (24) for circulation of a second fluid in which the sheet is disposed ( 8); characterized in that the heat exchanger (2) comprises a set (10) of spacers arranged in the first passage (18), these spacers being rods independent of the lower and upper plates (4, 6).
    [0002]
    2. Exchanger according to claim 1, characterized in that the assembly (10) of spacers comprises a peripheral spacer (34) interposed between respective peripheral edges (34) of the lower plate (4) and upper (6) and sealing between said peripheral edges.
    [0003]
    3. Exchanger according to claim 1 or 2, characterized in that the first passage (18) has outer and inner circumferential ends (46, 48) located respectively radially further outside and radially further inside the heat exchanger (2), the spacer assembly (10) comprising at least one central spacer (40) extending circumferentially over most of the length of the first passage (18) and dividing the first passage ( 18) into a forward leg (42) and a return leg (44) parallel to one another and communicating with each other at the inner end (48), preferably only at the the inner end (48).
    [0004]
    4. Exchanger according to claim 3, characterized in that the exchanger comprises a first fluid inlet (62) communicating with the forward leg (42) at the outer circumferential end (46) and an outlet (64). first fluid communicating with the return leg (44) at the outer circumferential end (46).
    [0005]
    5.- exchanger according to any one of the preceding claims, characterized in that the exchanger (2) comprises a cylindrical outer casing (92) in which is inserted the winding (12).
    [0006]
    6. Exchanger according to claim 5, characterized in that the lower and upper plates (4, 6) form a determined number of turns around the central axis (X), the sheet (8) forming a tower more than the lower and upper plates (4, 6), said further tower being interposed between the upper plate (6) and the outer casing (92).
    [0007]
    7.- exchanger according to claim 5 or 6, characterized in that the exchanger (2) comprises an inner tube (82) around which is wound the three-layer structure, the inner tube (82) being a rolled sheet with superposition two axial edges (84, 86) of said rolled sheet, and / or the outer envelope (92) being a rolled sheet with superposition of two axial edges (94, 96) of said rolled sheet.
    [0008]
    8.- exchanger according to any one of the preceding claims, characterized in that the sheet (8) defining the fins is a folded sheet crenellated (74), said slots constituting the fins.
    [0009]
    9. A method of manufacturing a heat exchanger according to any one of the preceding claims, the method comprising the following steps: - formation of the three-layer structure by superimposing the lower plate (4), the upper plate (6 ) and the sheet (8), with interposition of the assembly (10) of spacers in the first passage (18) between the lower and upper plates (4, 6); winding the spiral three-layer structure around the central axis (X).
    [0010]
    10. A method according to claim 9, characterized in that it comprises a step of pressurizing the first passage (18) to press the upper plate (6) against the sheet (8), performed after the step of winding.
    [0011]
    11. A process according to claim 9 or 10, characterized in that it comprises a step of fixing an inlet tube (70) of first fluid and an outlet tube (72) of first fluid on the upper plate (6), performed before the forming step and the winding step.
    [0012]
    12. A method according to any one of claims 9 to 11, characterized in that it comprises a step of insertion of the winding (12) in a cylindrical envelope (92).
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    EP0798527B1|1997-10-08|Spiral heat exchanger
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    同族专利:
    公开号 | 公开日
    US20150323260A1|2015-11-12|
    KR20150127552A|2015-11-17|
    DE102015106985A1|2015-11-12|
    CN105091642A|2015-11-25|
    FR3020868B1|2016-06-24|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    EP0380419A1|1989-01-25|1990-08-01|SPIREC, Société à Responsabilité Limitée|Heat exchanger having spirally wound elements, and process for its manufacture|
    US6233824B1|1999-10-08|2001-05-22|Carrier Corporation|Cylindrical heat exchanger|
    WO2002063231A1|2001-02-05|2002-08-15|Pursuit Dynamics Plc|Spiral flow heat exchanger|
    DE1914588U|1965-01-16|1965-04-22|Losenhausenwerk Duesseldorfer|SOIL COMPACTORS.|
    JP2001215097A|2000-02-01|2001-08-10|Shinwa Corp|Heat exchange element with added harmful gas elimination function|
    US6989134B2|2002-11-27|2006-01-24|Velocys Inc.|Microchannel apparatus, methods of making microchannel apparatus, and processes of conducting unit operations|
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    US10365048B2|2015-08-06|2019-07-30|Sanoh Industrial Co., Ltd.|Multiply-wound tube, method of manufacturing multiply-wound tube, and device for manufacturing multiply-wound tube|
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    法律状态:
    2015-05-19| PLFP| Fee payment|Year of fee payment: 2 |
    2015-11-13| PLSC| Search report ready|Effective date: 20151113 |
    2016-05-30| PLFP| Fee payment|Year of fee payment: 3 |
    2018-03-02| ST| Notification of lapse|Effective date: 20180131 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1454146A|FR3020868B1|2014-05-07|2014-05-07|SPIRAL HEAT EXCHANGER AND METHOD FOR MANUFACTURING THE SAME|FR1454146A| FR3020868B1|2014-05-07|2014-05-07|SPIRAL HEAT EXCHANGER AND METHOD FOR MANUFACTURING THE SAME|
    DE102015106985.7A| DE102015106985A1|2014-05-07|2015-05-05|Spiral-shaped heat exchanger and corresponding manufacturing process|
    US14/703,937| US20150323260A1|2014-05-07|2015-05-05|Spiral Heat Exchanger and Corresponding Manufacturing Method|
    CN201510230667.5A| CN105091642A|2014-05-07|2015-05-07|Spiral heat exchanger and corresponding manufacturing method|
    KR1020150063579A| KR20150127552A|2014-05-07|2015-05-07|Spiral heat exchanger and corresponding manufacturing method|
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