Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
  • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
  • F28D7/04—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being spirally coiled
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F1/00—Tubular elements; Assemblies of tubular elements
  • F28F1/02—Tubular elements of cross-section which is non-circular
  • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings

Definitions

• Coiled heat exchanger and air conditioning device comprising such a heat exchanger.
• the invention is in the field of air conditioning loops cooperating with a ventilation system, heating and / or air conditioning of a motor vehicle. It relates to a coil heat exchanger which is constitutive of an air conditioning device comprising an air conditioning loop associated with a secondary loop. It also relates to such an air conditioning device.
• a motor vehicle is commonly equipped with a ventilation, heating and / or air conditioning system to modify the aerothermal parameters of the air contained inside the passenger compartment of the vehicle. Such a modification is obtained from the delivery inside the passenger compartment of at least one air flow.
• the installation consists mainly of a housing, made of a plastic material, which channels the circulation of said air flow and which houses means for heat treatment of the latter, such as at least one evaporator for cooling said flow of air. 'air.
• the installation cooperates with an air conditioning loop which comprises the evaporator and at least one compressor, a gas cooler, an internal heat exchanger, a detent and an accumulator inside which circulates a fluid.
• refrigerant such as a supercritical fluid, carbon dioxide known as R744.
• the refrigerant circulates from the compressor to the gas cooler, then to a "high pressure" branch of the internal heat exchanger, then to the expansion element, then to the evaporator, then to the accumulator, and finally to a branch "low pressure" of the internal heat exchanger, to return to the compressor.
• the compressor is intended to receive the refrigerant fluid in the gaseous state and to compress it to carry it at high pressure.
• the gas cooler is adapted to cool the compressed refrigerant at a relatively constant pressure, giving up heat to its environment.
• the expansion member is able to lower the pressure of the refrigerant at the outlet of the gas cooler by bringing it at least partly in the liquid state.
• the evaporator is itself capable of passing the coolant in the liquid state from the expansion element, at relatively constant pressure, to the gaseous state, by taking heat from said air flow which passes through the 'evaporator. The vaporized refrigerant is then sucked by the compressor.
• the air conditioning loop comprises a "high pressure" line extending from the compressor to the expansion member and a “low pressure” line extending from the expansion member to compressor, according to a flow direction of the refrigerant fluid inside the air conditioning loop.
• the air conditioning loop also includes a heat exchanger to allow heat transfer between the refrigerant circulating inside the air conditioning loop and a heat transfer fluid flowing inside a secondary loop.
• the heat exchanger is part of the air conditioning loop and the secondary loop.
• the air conditioning loop and the secondary loop together form an air conditioning device.
• WO2007 / 136379 discloses a heat exchanger comprising two flat tubes associated with each other and arranged in interleaved spirals one inside the other.
• the refrigerant circulates inside one of the flat tubes while the heat transfer fluid circulates inside the other flat tube, the flow of said fluids being effected inside the respective flat tubes against the current of one another.
• a first drawback to the use of such an exchanger lies in the fact that it is bulky.
• an exchanger of the aforementioned type has the disadvantage of being heavy.
• such an exchanger is complex to manufacture; the assembly of the flat tubes between them proving to be long and likely to generate damage to the flat tubes and finally the operation of the heat exchanger.
• such an air conditioning device comprising an exchanger as described above is likely to undergo substantial losses of loads affecting one and / or the other of the fluids, these pressure losses deserve to be minimized.
• such an air conditioning device provides thermal performance, including thermal power, thermal efficiency and hydraulic power, which deserve to be improved.
• a first object of the present invention is to provide a heat exchanger, intended to be traversed by a coolant and a coolant, which is compact, robust, lightweight, easy to manufacture and easy to install on a cooling device. relatively conformation.
• Another object of the present invention is to provide such a heat exchanger arranged to allow a heat transfer between the refrigerant and the heat transfer fluid which, according to various embodiments, is "co-current", “against the current "Or” cross flow ".
• Another object of the present invention is to provide such a heat exchanger which provides minimized pressure drops for one or the other of said fluids.
• a final object of the present invention is to provide an air conditioning device comprising an air conditioning loop and a secondary loop on which is jointly installed said heat exchanger, the supercritical refrigerant fluid circulating inside the air conditioning loop, the fluid coolant circulating inside the secondary loop, such an air conditioning device offering a better compromise possible between an optimization of the heat transfer between said fluids, a minimization of pressure losses likely to affect the flow of one and / or either of said fluids and minimizing the external bulk. It is not understood that the heat exchanger according to the invention is installed at the intersection of the air conditioning loop and the secondary loop.
• the heat exchanger of the present invention is a heat exchanger comprising a casing which houses a flat tube wound on itself to form consecutive turns. Two consecutive turns vis-à-vis one another are separated by an interstitial space.
• the interstitial space (12) extends between two consecutive turns vis-à-vis one another a separation distance D which is between 0.5 mm and 5 mm.
• the separation distance D is preferably at least 2 mm.
• Such a heat exchanger provides a better compromise between low pressure losses that may affect the heat transfer fluid FC and optimized heat exchange between the refrigerant fluid FR and the heat transfer fluid FC.
• the flat tube advantageously accommodates a plurality of channels which each extend between a central rod equipping a central end of the flat tube and a peripheral rod equipping a peripheral end of the flat tube.
• Each channel preferably comprises a passage section (A1.A2), taken in a radial plane P of the heat exchanger comprising an axis winding ⁇ ⁇ of the flat tube on itself, which is between 0.2 mm 2 and
• Each channel advantageously comprises a wet perimeter Pe1, Pe2. taken in said radial plane P, which is between 1.6 mm and 1.9 mm.
• Each channel advantageously comprises a hydraulic diameter of between 0.4 mm and 0.9 mm.
• the channels are for example in a number between 75 and 85.
• the flat tube has a height H, taken parallel to the winding axis ⁇ ⁇ of the flat tube on itself between two opposite edges B1.E32 of the flat tube, which is between 75 mm and 80 mm.
• the flat tube comprises channels in a number equal to 81,
• the flat tube has a height H equal to 77.3 mm
• each channel has a passage section A1 which is shaped as a rectangle with a length L of 1 mm and a width I of 0.7 mm;
• each channel has a hydraulic diameter d equal to 0.86.
• the heat exchanger comprises the following characteristics:
• the flat tube comprises channels in a number equal to 77,
• the flat tube has a height H equal to 77.3 mm
• the flat tube has an extended length equal to 1400 mm
• each channel comprises a passage section A2 which is shaped in a circle of diameter çT equal to 0.6 mm,
• each channel has a hydraulic diameter d equal to 0.6.
• the heat exchanger comprises for example finally the following characteristics:
• the flat tube comprises channels in a number equal to 77,
• the flat tube has a height H equal to 77.3 mm, the flat tube has an extended length equal to 695 mm,
• each channel comprises a passage section A2 which is shaped in a circle of diameter çT equal to 0.6 mm,
• each channel has a hydraulic diameter d equal to 0.6.
• the casing preferably consists of a sleeve, a first end plate of a first end of the sleeve and a second end plate of a second end of the sleeve.
• the sleeve is generally cylindrical and extends along a general axis of extension ⁇ which is substantially orthogonal to planes P1 and P2 of general extension respectively of the first flange and the second flange.
• the flanges are for example reported on the sleeve indifferently by interlocking, by clipping or gluing.
• the envelope is preferably provided with an inlet port and an outlet port.
• any one of the inlet and outlet ports is formed through the first flange.
• the other outlet and inlet ports is for example formed through the sleeve.
• the other outlet and inlet ports is for example still formed through the second flange.
• the orifice, indifferently input or output, assigned to the first flange is advantageously formed in a central zone of the first flange.
• the central rod advantageously comprises a recess in relation to the channels which opens at a first end of the central rod and in that the peripheral rod has an orifice in relation to the channels which opens into a first end of the peripheral rod.
• the first end of the central rod is advantageously provided with any one of an intake port or a discharge port while the first end of the peripheral rod is provided with the other port.
• the first end and the first end emerge for example through a same flange.
• the first end emerges through one of the flanges while the first end emerges through the other flanges.
• the central rod having a second end and the peripheral rod having a second end, the second end and the second end are preferably nested inside respectively of a central shaft and a peripheral shaft constituting said envelope.
• the orifice assigned to the first flange is preferably arranged in a crescent moon and partially covers the central shaft.
• the orifice assigned to the first flange is advantageously provided with a bent duct which is integral with a bottom of the peripheral drum.
• the flat tube is in particular made by extrusion of a thermally conductive material.
• the envelope as for it is in particular made from a plastic material.
• An air conditioning device of the present invention is mainly recognizable in that the air conditioning device comprises an air conditioning loop and a secondary loop on which is jointly installed at least one such heat exchanger.
• the heat exchangers are preferably in plurality and are installed in series on the air conditioning loop and the secondary loop.
• the air conditioning loop advantageously conveys a supercritical fluid FR in a first direction of circulation SJ . .
• the secondary loop advantageously conveys a refrigerant consisting of a mixture of water and glycol in a second flow direction S2.
• said first direction of flow SJ. is for example in the same sense as the second direction of circulation S2.
• said first direction of movement Sl is for example still in the opposite direction to said second direction of circulation S2.
• the first direction of circulation SJ is for example finally orthogonal to said second direction of circulation S2.
• the flat tube is advantageously constitutive of the air conditioning loop while the interstitial space is constitutive of the secondary loop.
• Said heat exchanger is for example installed on a line "low pressure" of the air conditioning loop.
• Said heat exchanger is for example still installed on a line "high pressure” of the air conditioning loop.
• FIG. 1 is a partial schematic illustration of an air conditioning device comprising a heat exchanger according to the present invention.
• Fig.2 and Fig.3 are schematic illustrations of respective embodiments of the air conditioning device shown in the previous figure.
• Fig.4 is a radial sectional view of a first embodiment of the heat exchanger shown schematically in the previous figures.
• Fig.4bis is a detailed view of the heat exchanger shown in the previous figure.
• FIG. 5 represents a curve illustrating a thermal power Rh of the heat exchanger illustrated in FIGS. 1 to 4 as a function of a separation distance D defining an interstitial space that comprises said exchanger.
• FIG. 6 represents a curve illustrating a thermal efficiency E of the heat exchanger illustrated in FIGS. 1 to 4 as a function of the separation distance D.
• FIG. 7 represents a curve illustrating pressure drops Pc capable of affecting a refrigerant circulating inside the heat exchanger illustrated in Fig.1 to Fig.4 according to the separation distance D.
• Fig.8 shows a curve illustrating a hydraulic power Ph of the heat exchanger illustrated in fig.1 to fig.4 according to the separation distance D.
• Fig.9 is a perspective view of the heat exchanger shown in Fig.1 to Fig.4.
• Fig.1O is a cross-sectional view of a turn of a flat tube constituting the heat exchanger shown in fig.2.
• Fig.11 is a cross-sectional view of a turn of a flat tube constituting the heat exchanger shown in Fig.3.
• FIGS. 1 to FIG. 4 are diagrammatic illustrations of relative circulation direction variations of a refrigerant and a heat transfer fluid circulating inside the heat exchanger shown in FIGS. 1 to FIG. 4, Fig.12a to Fig.12c being similar to Fig.4bis.
• Fig.13 is a partial perspective view of the heat exchanger shown in Fig.1 to Fig.4.
• Fig.14 is a longitudinal sectional view of a first embodiment of the heat exchanger illustrated in Fig.1 to Fig.4 and Fig.13.
• Fig.15 is a longitudinal sectional view of a second embodiment of the heat exchanger illustrated in Fig.1 to Fig.4 and Fig.13.
• FIG.16 is a longitudinal sectional view of an embodiment of the heat exchanger illustrated in Fig.1 to Fig.4 and Fig.14 to Fig.15.
• FIGS. 17 to 20 are perspective views of respective choices for connecting the heat exchanger shown in FIGS. 13 and 14 to the air conditioning device illustrated in FIG.
• Fig.21 is a perspective view of a heat exchanger shown in Fig.1 to Fig.4 and Fig.14 to Fig.15.
• Fig.22 is a side view of the heat exchanger shown in the previous figure.
• a motor vehicle is equipped with a ventilation, heating and / or air conditioning system to modify the aerothermal parameters of the air contained inside the passenger compartment. Such a modification is obtained from the delivery of at least one air flow F inside the passenger compartment.
• the installation consists mainly of a plastic housing arranged under a dashboard of the vehicle. The housing is intended to channel the flow of air flow F prior to the delivery of the latter F inside the passenger compartment.
• the installation houses means for heat treatment of the air flow F to cool and / or heat the latter F.
• the installation cooperates with an air conditioning device 1 comprising an air conditioning loop 2 inside which circulates a refrigerant fluid FR, preferably supercritical, such as carbon dioxide referenced R 744, for example.
• the air conditioning loop 2 comprises at least one heat exchanger 3 arranged to allow a heat transfer between the refrigerant fluid FJR and a heat transfer fluid FC flowing inside a secondary loop 4.
• the heat transfer fluid F ⁇ is preferably constituted by a mixture of water and glycol.
• the heat exchanger 3 is constitutive or integrated at the intersection of the air conditioning loop 2 and the secondary loop 4 and is traversed by the refrigerant fluid FR and the heat transfer fluid F ⁇ _ according to separate circuits. Note that this exchanger 3 does not exchange with air, that is to say that it is not crossed by a flow of air.
• the heat exchanger 3 comprises an inlet 5 for the refrigerant fluid FJR which communicates with a discharge orifice 6 of the refrigerant fluid FR via a first circulation path 7 of the refrigerant fluid FR inside. of said heat exchanger 3.
• the refrigerant fluid FR circulates in a first direction of flow Sl.
• the heat exchanger 3 comprises an orifice of inlet 8 of the heat transfer fluid F ⁇ which communicates with an outlet orifice 9 of the second heat transfer fluid F ⁇ through a second circulation path 10 of the heat transfer fluid FC inside said exchanger 3.
• the heat transfer fluid F ⁇ circulates in a second direction of circulation S_2.
• the air conditioning device 1 comprises two heat exchangers 3 arranged in series on the air conditioning loop 2 and the secondary loop 4.
• the first paths 7 of each exchanger 3 are placed one after the other so that the refrigerant circulates both in the other and the first of the first paths 7.
• the discharge port 6 of a first heat exchanger 3 is in relation with the inlet orifice 5 of a second heat exchanger 3 while the outlet orifice 9 of the first heat exchanger 3 is in relation with the inlet orifice 8 of the second heat exchanger 3.
• the air conditioning loop 2 further comprises a compressor 100, a gas cooler 101, an internal heat exchanger
• the air conditioning loop 2 comprises a "high pressure" line 106 extending from the outlet of the compressor 100 to the inlet of the expansion member 103 and a "low pressure” line 107 extending from the outlet of the expansion member
• the heat exchanger 3 is installed on the "low pressure" branch 107 of the air conditioning loop 2. More particularly, the heat exchanger 3 is interposed between the outlet of the expansion device 103 and the inlet of the internal heat exchanger 102, according to the flow direction Sl of the refrigerant FR inside the air conditioning loop 2.
• the heat exchanger 3 behaves thermally as an evaporator , in that it is able to cool the heat transfer fluid F ⁇ which circulates therethrough, by giving away refrigerants to the coolant FC.
• An air cooler / heat transfer fluid 120 is integrated on the secondary loop 4 whose function is to transfer the frigories carried by the heat transfer fluid to an air F which enters the passenger compartment of the motor vehicle to condition the latter.
• the heat exchanger 3 is installed on the "high pressure" branch 106 of the air conditioning loop 2. More particularly, the heat exchanger 3 is interposed between the output of the compressor 100 and the exchanger of internal heat 102, according to the direction of circulation SJ. in this configuration, the heat exchanger 3 behaves thermally like a gas cooler, in that it is able to cool the refrigerating fluid FR which circulates at the same time. through, giving up heat to the FC heat transfer fluid.
• the secondary loop 4 comprises a fluid cooler capor / air 121 which is placed in the front of the vehicle so as to exchanger with the air outside the vehicle and thus cool the coolant FC.
• said first path 7 consists of a flat tube wound on itself to form a spiral consisting of successive turns 11, preferably concentric.
• Said second path 10 consists at least partially of an interstitial space 12 formed between two consecutive turns 11 of the winding of the flat tube 7.
• the interstitial space 12 is defined by a separation distance D between two consecutive turns 11 which is between 0.5 mm and 5 mm.
• the separation distance D is measured between two consecutive turns 11 arranged facing each other.
• the separation distance D is equivalent to a spacing formed between two consecutive turns 11 directly vis-à-vis one another.
• the separation distance D is measured between an outer face 108 of an outer wall 109 of a first turn 11a and an inner face 110 of an inner wall 111 of a second turn 11b, the second turn 11b being disposed vis-à-vis the first turn 11a.
• An outer face of a wall of a turn is further away from a winding axis ⁇ ⁇ of the flat tube 7 on itself than an inner face of the same wall of the same turn.
• the interstitial space 12, forming at least partially the second circulation path 10 extends from a first turn 11a to a second turn 11b, or more precisely from an outer wall 109 of the first turn 11a to the internal wall 111 of the second turn 11b, without any other wall channeling the flow of heat transfer fluid FC.
• the thermal power Rh corresponds to the energy yielded by the hottest fluid (namely respectively the coolant F F according to the configuration of the air conditioning device 1 illustrated in FIG. 2 and the refrigerant fluid FR according to the configuration of the air conditioning device. 1 illustrated in FIG. 3) to the coldest fluid (namely respectively the refrigerant fluid FR according to the configuration of the air conditioning device 1 illustrated in FIG. 2 and the heat transfer fluid FC according to the configuration of the air conditioning device 1 illustrated in FIG. fig.3).
• the thermal power Rh corresponds to the energy yielded by the hottest fluid (namely respectively the coolant F F according to the configuration of the air conditioning device 1 illustrated in FIG. 2 and the refrigerant fluid FR according to the configuration of the air conditioning device. 1 illustrated in FIG. 3) to the coldest fluid (namely respectively the refrigerant fluid FR according to the configuration of the air conditioning device 1 illustrated in FIG. 2 and the heat transfer fluid FC according to the configuration of the air conditioning device 1 illustrated in FIG. fig.3).
• the thermal power Rh decreases linearly from a power Pth1 to a power Pth2, when the separation distance D changes from 0.5 mm to 5 mm. More particularly, between these two values of the separation distance D, a ratio Pth2 / Pth1 equals 40% for a separation distance D of 5 mm and a ratio Pth3 / Pth1 is equivalent to 25% for a separation distance D of 3 mm.
• a thermal efficiency E of the heat exchanger 3 also decreases linearly between an efficiency EJ. up to an efficiency E2, when the separation distance D changes from 0.5 mm to 5 mm, as shown in fig.6. More particularly, between these two values of the separation distance D, we obtain a ratio E2 / El. Which equals 40% for a separation distance D of 5 mm and a ratio E3 / EJ. which equals 25% for a separation distance D of 3 mm.
• a hydraulic power Ph procured by such a heat exchanger 3 decreases linearly between a hydraulic power Ph1 to a hydraulic power Ph2, when the separation distance D changes from 0.5 mm to 2 mm, then remains stable when the separation distance D changes from 2 mm to 5 mm, as illustrated in fig.8. More particularly, it has been observed that the hydraulic power Ph2 is ten times less than the hydraulic power Ph1.
• the hydraulic power Ph is defined as the product of a flow rate of the refrigerant fluid FR by a pressure difference between an inlet pressure of the refrigerant fluid FR inside the flat tube 7 and an outlet pressure. FR refrigerant out of the flat tube 7.
• the flat tube 7 is housed inside an envelope 13 constituted by a sleeve 14 whose ends 15, 16 are respectively closed by a first flange 17 and a second flange 18. It is therefore understood that the envelope 9 is tight vis vis the external environment.
• the flat tube 7 is immersed in the coolant FC that fills the casing 13.
• the fact that the flat tube 7 is immersed in a heat transfer fluid bath FC facilitates the heat exchange between the heat transfer fluid FC and the refrigerant fluid FR.
• the casing 13 is provided with a plurality of fingers 119, otherwise called grooves, for holding the flat tube 7 in position inside the casing 13.
• Said fingers 119 come into contact with the outermost turn 11 of the winding of the flat tube 7 on itself. This results in rigidity and optimized strength of the heat exchanger 3, the fingers 119 being formed and shaped so as not to interfere with a circulation of the heat transfer fluid FC between the casing 13 and the outermost turn 11.
• the sleeve 14 is generally cylindrical and extends along a general axis of extension ⁇ which is substantially orthogonal to the planes PJ . and P2 of general extension respectively of the first flange 17 and the second flange 18. These flanges 17, 18 are attached to the corresponding ends 15 and 16 of the sleeve 14 by interlocking, or by any other similar assembly technique, such as the clipage or collage in particular.
• the flat tube 7 is made in particular from the extrusion of a thermally conductive and mechanically resistant material, aluminum, for example, to tolerate the circulation of the refrigerant fluid FR at a pressure greater than atmospheric pressure.
• the heat exchanger 3 of the present invention is sized to allow a reliable and secure circulation of the refrigerant fluid FR at a pressure between 20 bar and 120 bar.
• the envelope 13 is for its part made for example by molding a lightweight plastic material and sufficiently resistant to channel the circulation of coolant F F at atmospheric pressure. These provisions are such that the heat exchanger 3 has a mass as small as possible.
• FIG. 10 which represents a section of a flat tube 7 installed on the "low pressure" line 107 of the air conditioning loop 2
• the flat tube 7 houses a plurality of channels 112, preferably 81 in number. adjacent channels 112 are spaced from each other by a space e which is constant, of the order of 0.25 mm.
• the channels 112 are formed in respective general extension planes P which are parallel to each other and orthogonal to said general extension axis ⁇ .
• the flat tube 7 has a height H taken parallel to the general extension axis ⁇ of an edge B1 at the opposite edge B2 of the flat tube 7, which is between 75 mm and 80 mm, preferably of the order of 77 mm. mm, and preferentially still equivalent to 77.3 mm.
• a flat tube 7 has a hydraulic diameter d, defined as being the result of four times a passage section Al of the refrigerant FR divided by a wet perimeter Pe 1 of the passage section A1, which is between 0, 8 and 0.9, preferably equivalent to 0.86.
• the passage section Al of the refrigerant FR is of rectangular conformation.
• Said section A1 is in particular of length L, taken parallel to said plane P, which is of the order of 1 mm, and of a width I 1 taken orthogonally to said plane P, which is of the order of 0.7 mm.
• FIG. 11 which represents a section of a flat tube 7 installed on the "high pressure" line 106 of the air conditioning loop 2
• the flat tube 7 houses a plurality of channels 112, preferably 77 in number. adjacent channels 112 are spaced from each other by a space e which is constant, of the order of 0.4 mm.
• the channels 112 are formed in respective general extension planes P which are parallel to each other and orthogonal to said general extension axis ⁇ .
• the flat tube 7 has a height H, taken parallel to the general extension axis ⁇ of the edge B1 at the opposite edge B2 of the flat tube 7, which is between 75 mm and 80 mm, preferably of the order of 77 mm. , and preferably still equivalent to 77.3 mm.
• a flat tube 7 has a hydraulic diameter d, defined as being the result of four times a passage section A2 of the refrigerant FR divided by a wet perimeter Pe2 of the passage section A2, which is between 0.4 and 0.65, preferably equivalent to 0.6.
• the passage section A2 of the refrigerant fluid FR is of circular conformation.
• Said section A2 is in particular of a diameter çT which is of the order of 0.6 mm.
• the heat exchanger 3 has the advantageous characteristic of allowing a heat transfer between the refrigerant fluid FR and the coolant FC that is "to co-current ", or” against the current ", or” cross current ", as respectively illustrated in Fig.12a to Fig.12c. It follows that such a heat exchanger 3 offers various operating possibilities relating to said heat transfer, from the same flat tube 7 and from an interchangeability of the envelope 13, which is obtained at lower cost , and from a connection choice of the heat exchanger 3 on the air conditioning loop 2 and the secondary loop 4.
• said flow directions SJ. and S2 within the heat exchanger 3 are rotational directions both of which are clockwise positive.
• said flow directions SJ . and S2 within the heat exchanger 3 are directions of rotation which are both trigonometric.
• said flow directions SJ . and S2 are said to be "parallel" and of the same meaning.
• Such a heat exchanger 3 is called "co-current”.
• said flow direction SJ. is clockwise positive direction while said flow direction S2 is trigonometric positive direction.
• said flow direction Sl is trigonometric positive sense while said flow direction S2 is clockwise positive direction.
• said SJ circulation directions . and S2 are said to be "parallel" and of opposite direction.
• Such a heat exchanger 3 is said to be "against the current”.
• said flow direction SJ. is clockwise positive direction while said flow direction S2 is perpendicular to the plane of Fig.12c oriented from the front to the rear of the plane of Fig.12c.
• said flow direction S2 is oriented from the rear towards the front of the plane of fig.12c.
• said direction of movement Si is trigonometric positive direction while said direction of flow S2 is still perpendicular to the plane of Fig.12c, indifferently oriented from the front to the rear of the plane of Fig.12c, or from the back to the front of the latter.
• Such a heat exchanger 3 is called "cross flow".
• the flat tube 7 extends between a central end 21 and a peripheral end 22 of its winding, the central end 21 being positioned at the heart of the winding of the tube 7 while the peripheral end 22 is disposed at the outer edge of said winding.
• the central end 21 is equipped with a central rod 23 which extends along a first axis ⁇ l while the peripheral end 22 is provided with a peripheral rod 24 which extends along a second axis ⁇ 2.
• the first axis ⁇ l, the second axis ⁇ 2 and the axis of general extension ⁇ of the sleeve 14 are parallel to each other and also parallel to the winding axis ⁇ ⁇ of the flat tube 7 on itself.
• the said axes ⁇ and ⁇ ⁇ are preferably parallel or even merged.
• the peripheral rod 24 abuts against an abutment 31 formed inside the sleeve 14 to prevent a passage of the coolant FC on either side of the peripheral rod 24.
• the stop 31 against which relies the peripheral rod 24 is formed upstream of the inlet port 8 of the heat transfer fluid FC inside the heat exchanger 3 according to said first direction of circulation SJ . to facilitate a fluid and homogeneous circulation of the coolant F F inside the heat exchanger 3.
• the central rod 23 is provided with a recess 25 which opens at a first end 26 of the central rod 23.
• the peripheral rod 24 is provided with a orifice 28 which opens at a first end 29 of the peripheral rod 24.
• the recess 25 and the orifice 28 are connected to each other via said channels 112.
• the recess 25 is in relation with the inlet orifice 5 and the orifice 28 is in relation with the discharge orifice 6, ie the recess 25 is in relation with the discharge orifice 6 and the orifice 28 is in relation with the inlet orifice 5.
• the first end 26 of the central rod 23 and the first end 29 of the peripheral rod 24 emerge from the casing 13 through the second flange 18 for connection to the air conditioning loop 2.
• the rod central 23 and the peripheral rod 24 respectively comprise a second end 27 and a second end 30 which are nested inside respective drums 33,32 formed on the first flange 17.
• the first end 26 of the central rod 23 emerges from the casing 13 through the first flange 17 and the first end 29 of the peripheral rod 24 emerges from the casing 13 through the second flange 18 for their connection to the air-conditioning loop 2.
• the second end 27 of the central rod 23 is fitted inside a peripheral shaft 32 formed on the second flange 18 and the second end 30 of the peripheral rod 24 is nested. inside a central shaft 33 formed on the first flange 17.
• the heat exchanger 3 shown is indifferently "co-current” or "against the current", as respectively illustrated in Fig.14a and Fig.14b.
• the first flange 17 is provided with the outlet orifice 9 of the coolant F 1 - while the second flange 18 is provided with the inlet orifice 8 of the coolant FC.
• These provisions are such that the heat exchanger 3 is "cross flow". Indeed, the flat tube 7 being indifferently arranged as described in FIG. 14 or in FIG. 15, the fact that the inlet orifice 8 and the outlet orifice 9 are formed on flanges 17, 18 different, as shown in Fig.16, allows the coolant FC to cross the heat exchanger 3 from the first flange 17 to the second flange 18 in a second flow direction S2 punctually perpendicular to the first direction SJ circulation. FR refrigerant inside the flat tube 7, as shown in Fig.12c. These provisions minimize the pressure losses Pc that may affect the heat transfer fluid FC.
• a first shim 113 is interposed between the edges JH of the flat tube 7 and the first flange 17 while a second shim 114 is interposed between the edges B2 of the flat tube 7 and the second flange .
• the first shim 113 is interposed between the edges Bl of the flat tube 7 and the barrels 32,33 formed on the first flange 17 while the second shim 114 is interposed between the edges B2 of the flat tube 7 and two elementary sleeves 115,116 associated with the second flange 18.
• the first shim 113 is interposed between the edges BJ . of the flat tube 7 and on the one hand the peripheral barrel 32 and secondly a central elementary sleeve 115 which are formed on the first flange 17.
• the second shim 114 as for it is interposed between the edges B2 of the flat tube 7 and on the one hand the central shaft 33 and on the other hand a peripheral elementary sleeve 116 which are formed on the second flange 18.
• the first shim 113 and / or the second shim 114 are for example arranged in a cross.
• the peripheral rod 24 is provided with the inlet port 5 while the central rod
• the sleeve 14 is provided with the inlet orifice 8 while the first flange 17 is provided with the outlet orifice 9.
• the latter 9 is positioned in a central zone 19 of the first flange 17, said central zone 19 being more particularly visible in Fig.21.
• the sleeve 14 is provided with the outlet orifice 9 while the first flange 17 is provided with the inlet orifice 8.
• the latter 8 is positioned in the central zone 19 of the first flange 17.
• the peripheral rod 24 is provided with the discharge port 6 while the central rod 23 is provided with the inlet port 5.
• the sleeve 14 is provided with the inlet orifice 8 while the first flange 17 is provided with the outlet orifice 9.
• the latter 9 is positioned in the central zone 19 of the first flange 17.
• the peripheral rod 24 is provided with the discharge port 6 while the central rod 23 is provided with the inlet port 5.
• the sleeve 14 is provided with the outlet orifice 9 while the first flange 17 is provided with the inlet port 8.
• the latter 8 is positioned in the central zone 19 of the first flange 17.
• the orifice 8,9 assigned to the first flange 17 is provided with an angled duct 117 which is integral with a bottom 118 of the peripheral barrel 32. These provisions are intended to optimize a mechanical cohesion of the elbow duct 117 with the first flange 17 and strengthens the solidity of the latter 17.

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• Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
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• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Geometry (AREA)
• Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
• Air-Conditioning For Vehicles (AREA)

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• 2008
  • 2008-12-01 FR FR0806737A patent/FR2939187B1/fr not_active Expired - Fee Related
• 2009
  • 2009-11-30 WO PCT/FR2009/001360 patent/WO2010063897A1/fr active Application Filing
  • 2009-11-30 EP EP09784354A patent/EP2366087A1/de not_active Withdrawn
  • 2009-11-30 JP JP2011538020A patent/JP2012510600A/ja active Pending

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