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
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B40/00—Subcoolers, desuperheaters or superheaters
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
  • F25B43/006—Accumulators
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
  • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
  • F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
  • F28D7/0025—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes
  • F28D7/0033—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes the conduits for one medium or the conduits for both media being bent
• • 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
  • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
  • F28D9/04—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being formed by spirally-wound plates or laminae
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2309/00—Gas cycle refrigeration machines
  • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
  • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2500/00—Problems to be solved
  • F25B2500/18—Optimization, e.g. high integration of refrigeration components
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
  • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
  • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Definitions

• the invention relates to a heat exchanger, in particular to an internal exchanger for an air conditioning circuit operating with a supercritical refrigerant fluid, such as carbon dioxide (CO2).
• a supercritical refrigerant fluid such as carbon dioxide (CO2).
• CO2 carbon dioxide
• the invention also relates to an integrated assembly intended for such a circuit. .
• the supercritical refrigerant fluid remains substantially in the gaseous state and under a very high pressure.
• Such a circuit generally comprises a compressor, a gas cooler, an internal exchanger, a pressure reducer, an evaporator and an accumulator.
• the compressor passes the refrigerant at high pressure before sending it to the gas cooler where it is cooled.
• the fluid then passes into a first part of the internal exchanger and is then expanded by the expander.
• the expanded low pressure fluid then passes through the evaporator, then passes through the accumulator before passing into a second portion of the internal exchanger.
• the fluid then returns to the compressor.
• the high pressure hot fluid of the first portion of the heat exchanger exchanges heat with the low pressure cold fluid of the second portion.
• the accumulator is provided at the outlet of the evaporator to store the excess liquid leaving the evaporator.
• the accumulator is generally in the form of a reservoir adapted to separate the liquid part of the fluid refrigerant of the gaseous part.
• the accumulator sends the gaseous portion of the refrigerant fluid at low temperature to the compressor after passing through the internal exchanger.
• JP 2003-121086 and JP2003-202197 use an extruded profiled tube in which are formed two rows of channels, one for the circulation of hot fluid, at high pressure, and the other for the circulation of the cold fluid, at low pressure.
• the manifolds are connected to the tubes by means of slots on one side of the tube. This solution generates a congestion that remains very important.
• Such an air conditioning circuit requires a large number of components and connections, which complicates its manufacture, increases its cost and its size. Furthermore, it is subject to risks of leakage, especially in view of the high pressure of the refrigerant fluid in the gaseous state.
• US Pat. No. 6,523,365 and US Pat. No. 2,005,752,419 disclose an integrated assembly comprising an accumulator and an internal exchanger arranged in a coaxial manner.
• the internal heat exchanger has a general spiral shape and is composed of two coiled tubes, one for the circulation of the hot fluid and the other for the circulation of the cold fluid.
• FR 2 752 921 Also known from FR 2 752 921 is an integrated assembly comprising a horizontal accumulator and an internal exchanger having a generally spiral shape. A gap is provided between the windings of the internal exchanger to allow the circulation of the cold fluid, while the hot fluid circulates inside the spirally wound tube.
• the integrated assembly comprises an outer cylinder and an inner cylinder arranged inside the outer cylinder, and an accumulator.
• the inner cylinder is in the form of a coiled flat tube provided with micro channels for the circulation of high pressure fluid.
• This solution has the disadvantage of generating a large longitudinal footprint.
• the invention improves the situation by providing a heat exchanger for an air conditioning circuit, comprising at least one tube defining a path for the circulation of a first fluid and a second fluid, the tube being wound around an axis. so as to define successive windings.
• the successive windings of the tube are closely clamped together so as to define so-called secondary sealed channels for the circulation of the second fluid, said secondary channels being situated between projecting zones of said tube, and that said tube has so-called main channels at the projecting areas, to be traversed by the first fluid.
• the tube comprises a profile and the profile of the tube has on one of its faces ribs formed by the main channels and grooves between the main channels, while the other face is substantially flat, and each secondary channel for the second fluid is delimited by a groove between two adjacent ribs of a given winding and the flat face of the next winding.
• the profile of the tube comprises on its two faces ribs formed by the main channels and grooves between the main channels, each secondary channel for the second fluid then being delimited by a groove between two adjacent ribs of a given winding and the groove in look between the two adjacent ribs of the next winding.
• the ends of the main channels are received between a main inlet pipe adapted to receive the first fluid, and a main outlet pipe adapted to deliver the first fluid to the outside of the exchanger, while the ends of the secondary channels; are in fluid communication with a secondary inlet tubing adapted to receive the second fluid and a secondary outlet pipe clean to deliver the second fluid outside the exchanger.
• Each main pipe has a substantially cylindrical shape about an axis parallel to the axis of the heat exchanger and has an opening adapted to receive one end of the tube.
• Each secondary tubing has elongated apertures on a portion of its wall for fluid communication with the secondary channels.
• the exchanger comprises a connecting plate having a curved section of shape adapted to be housed between the penultimate outer winding of the tube and the last outer winding of the tube, while the main inlet pipe and the secondary tubing of output are integral with the connecting plate.
• the exchanger has an inner core of substantially cylindrical shape.
• the nucleus is monoblock.
• the core consists of several nested parts that provide power and distribution of the primary circuit and the secondary circuit and the winding of the tube or tubes.
• the core consists of two coaxial parts, the first part having a rigid structure provided with grooves on its periphery and the second part comprising a metal sheet wound around the first part so as to define the main outlet pipe and the secondary tubing input.
• the inlet and outlet secondary pipes comprise one or more elongate openings in the axis of the exchanger so as to be in fluid communication with the secondary channels.
• the openings are offset radially and in the axis of the exchanger relative to each other.
• the secondary inlet tubing has one or more openings and is divided into one or more input channels so that each input channel communicates with at least one of the openings.
• the tube is formed as a profiled piece in one or more elements.
• the tube is obtained by extrusion.
• the main channels of the tube have a substantially circular section.
• the invention also relates to the use of a heat exchanger, as defined above, as an internal exchanger, wherein the first fluid is a high pressure fluid and the second fluid is a low pressure fluid.
• the invention further provides an integrated assembly for an air conditioning circuit operating with a refrigerant fluid.
• the air conditioning circuit comprises an internal heat exchanger having one of the preceding characteristics and a housing in which is housed the internal heat exchanger, the housing delimiting a bottom.
• the housing comprises an auxiliary tubing arranged outside the windings of the tube, the auxiliary tubing being adapted to receive the second fluid and to convey it to the bottom of the casing so as to send only the part vaporized from the second fluid into the secondary inlet tubing.
• the invention also proposes an air conditioning circuit operating with a refrigerant fluid, comprising a compressor, a condenser, an expander, and an evaporator.
• the circuit comprises the integrated assembly defined above.
• the main inlet pipe is connected to the condenser, and the auxiliary pipe is connected to the compressor, while the main outlet pipe is connected to the lower part of an accumulator and receives the vaporized part of the fluid.
• FIG. 1 is a diagram of an air conditioning circuit according to the invention
• FIG. 2 is a perspective view showing a part of the internal exchanger according to a first embodiment of the invention
• FIG. 3 is a sectional diagram of the tube of the internal exchanger according to the first embodiment of the invention.
• FIG. 4 is a sectional diagram of the internal exchanger showing two successive windings according to the first embodiment of the invention
• FIG. 5 is a perspective view of part of the internal exchanger according to a second embodiment of the invention.
• FIG. 6 is a sectional diagram of the tube of the internal heat exchanger according to the second embodiment of the invention
• FIG. 7 is a sectional diagram of the internal heat exchanger showing two successive windings according to the second embodiment of FIG. embodiment of the invention
• FIG. 8 is a partial perspective view of the internal exchanger according to the first embodiment of the invention
• FIG. 9 is a top view of the exchanger of FIG. 8,
• FIG. 10 is a perspective view of an inlet manifold for the high-pressure fluid according to the first embodiment of the invention.
• FIG. 11 represents an inlet pipe for the high-pressure fluid, according to the second embodiment of the invention.
• FIG. 12 is a view from above of an internal exchanger, comprising a three-part core,
• FIGS. 13 to 15 represent the elements of the core of the internal exchanger of FIG. 12,
• FIG. 16 is a view from above of an internal exchanger, comprising a monoblock core
• FIG. 17 shows the core of the internal heat exchanger of FIG. 16;
• FIG. 18 is a perspective view of an internal heat exchanger using a two-coaxial core,
• FIGS. 19 and 20 show the elements of the core of the internal heat exchanger of FIG. 18, and FIG. 21 is a partial perspective view showing a possible embodiment of the openings of the secondary outlet pipe.
• FIG. 1 shows an air conditioning circuit 10 operating with a refrigerant fluid, in particular a supercritical refrigerant fluid, for example carbon dioxide (CO 2 ).
• a refrigerant fluid in particular a supercritical refrigerant fluid, for example carbon dioxide (CO 2 ).
• CO 2 carbon dioxide
• the air conditioning circuit 10 can be installed in a motor vehicle to cool the air of the passenger compartment, according to the needs of the passengers.
• An air conditioning circuit operating in a supercritical refrigerant cycle essentially comprises a compressor 14, a gas cooler 11 associated with a fan 16, an internal heat exchanger 9, a pressure reducer 12, an evaporator 13, and an accumulator 17.
• the compressor 14 compresses the refrigerant fluid to a discharge pressure, called high pressure.
• the fluid then passes through the gas cooler where it undergoes a gas phase cooling under high pressure.
• the fluid is not condensed during cooling, unlike air conditioning circuits that use fluorinated compounds as a coolant.
• the fluid cooled by the gas cooler 11 then passes into a first portion 90 of the internal exchanger, called "hot" branch, to be further cooled.
• the fluid then passes into the regulator 12 which lowers its pressure, bringing it at least partly in the liquid state.
• the fluid then passes through the evaporator 13.
• the evaporator 13 passes the fluid in the gaseous state, at constant pressure.
• the exchange in the evaporator makes it possible to produce a flow of conditioned air which is sent towards the passenger compartment of the vehicle.
• the refrigerant flowing out of the evaporator 13 is not fully vaporized.
• the accumulator is provided at the outlet of the evaporator for storing the excess of liquid leaving the evaporator.
• the conventional accumulators are in the form of a reservoir adapted to separate the liquid portion of the refrigerant fluid from the gaseous portion.
• the accumulator 17 then sends the gaseous part of the refrigerant fluid at low temperature into a second part 92 of the internal exchanger 9, called the "cold" part, for a heat exchange with the "hot” part 90.
• FIG 2 shows a view of a portion of the internal exchanger, according to a first embodiment of the invention.
• the internal exchanger 9 comprises a flat tube 5 wound spirally around an axis
• the successive windings of the tube are closely clamped together so as to define so-called "secondary" channels 54 sealed for the circulation of the fluid at low pressure.
• the secondary channels 54 are situated between protruding zones or protuberances 53 of the tube 5.
• the tube 5 has so-called "main" channels 52 at the projecting areas, to be traversed by the fluid at high pressure.
• the tube 5 has salient main channels 52 for the circulation of the high-pressure fluid which circulates in the part 90 of the internal exchanger.
• the main channels extend over the entire length of the tube and therefore between the outer end of the spiral and the inner end of the spiral.
• the successive windings of the tube 50 are closely clamped together so as to delimit between certain at least adjacent main channels 52 sealed secondary channels 54 for the circulation of low pressure fluid (part 92 of the internal exchanger).
• the secondary channels 54 are shown in FIG.
• the flat tube 5 is made in the form of a metal section monobloc having a particular section illustrated in Figure 3.
• the profile of the tube comprises on one of its faces ribs formed by the main channels 52 and grooves between the main channels 51.
• the other side of the tube is substantially flat.
• the ribs formed by the main channels 52 extend along the tubes and have a circular section.
• FIG. 4 is a sectional view showing two successive windings 50 n and 50 n + i.
• the successive windings 50 n and 50 n + i are tightly clamped against each other, so that a secondary channel 54 for the circulation low-pressure fluid is delimited by a groove 51 between two adjacent ribs 52 of a given winding 50 n and the flat face of the next winding 50 n + i-
• FIG. 5 shows a view of a portion of the internal exchanger, according to a second embodiment of the invention.
• the tube is still made in the form of a metal profile.
• the profile of the tube shown in more detail in Figure 6, has on both sides protruding ribs 520 formed by the main channels 52, and grooves 51 between these ribs.
• the tube 5 furthermore has a symmetry along an axis (AA) perpendicular to the axis of the main channels 52.
• FIG. 7 shows two successive windings 50 n and 50 n + 1 according to the second embodiment of the invention.
• each secondary channel 54 for the second fluid is delimited by a groove 51 between two adjacent ribs 52 of a given winding 50 n and the facing groove 51 n + i between two adjacent ribs 52 n + i of the winding following 50 n + i.
• the successive windings of the tube are again tightly clamped against each other so as to ensure the sealing of the secondary channels 54.
• the facing ribs 52 0 n and 520 n + 1 bear one against the other. 'other.
• the internal exchanger 9 can be brazed or glued. During the soldering or gluing process, the windings 50 are fixed together.
• the internal heat exchanger 9 of the invention thus has an alternation of hot main channels 52 and cold secondary channels 54 in the axis (XX) of the exchanger, which makes it possible to reduce the diametral size of the internal heat exchanger .
• the internal exchanger of the invention further ensures a sealed separation between the secondary channels 54 so that the risk of accumulation of liquid at the bottom of the internal exchanger is limited. Furthermore, the secondary channels 54 for the circulation of low pressure fluid have no direct contact with the two rows of neighboring main channels 52 where the high pressure fluid flows. Consequently, the risks of interference between the secondary channels 54 and the main channels 52 are extremely low.
• FIG. 8 represents a partial perspective view of the upper part of the internal exchanger, in the second embodiment of the invention.
• FIG. 9 which is a top view of the exchanger of FIG. 8
• the high-pressure fluid and the low-pressure fluid flow in opposite directions in their respective channels 52 and 54. More precisely in the embodiments shown in the drawings, the high pressure fluid flows in the main channels 52 from the outside of the spiral inward, while the low pressure fluid flows in the secondary channels 54 of the inside the spiral outward.
• the internal exchanger 9 comprises a main inlet pipe 6 connected to a high-pressure fluid inlet, a main pipe of outlet 32 connected to an outlet for the high pressure fluid, a secondary inlet pipe 30 connected to a low pressure fluid inlet, and a secondary outlet pipe 7 connected to an outlet for the low pressure fluid.
• the main inlet pipe 6 and the secondary outlet pipe 7 are arranged at the outer end of the pipe 5, while the main outlet pipe 32 and the secondary inlet pipe 30 are arranged at the level of the pipe. inner end of the tube 5.
• the main inlet pipe 6 receives the fluid from the gas cooler 11 (arrow Fl) and the main outlet pipe 32 delivers the fluid to the regulator 12 (arrow F3).
• the secondary inlet tubing 30 receives the low pressure fluid from the accumulator 17 (arrow F4) while the secondary outlet tubing 7 delivers the low pressure fluid to the compressor 14 (arrow F2).
• the main inlet tubing 6 according to the first embodiment of the invention is shown in FIG. 10. It has a generally cylindrical shape with an axis parallel to the axis (XX).
• the main tubing 6 further comprises an elongated opening 60 of shape conjugate to the profile of the tube 5 so as to receive the outer end of the tube 5.
• the main inlet tubing 6 has a similar shape as 11, with the exception of the elongated opening 60. The high-pressure fluid thus enters the main inlet pipe from the gas cooler 11 and is transmitted to the main channels 54 through the opening 60.
• the main outlet pipe 32 for the high-pressure fluid has a general shape similar to that of the main pipe 6 and also has an elongate opening 320 of conjugate shape of the profile of the tube 5 so as to receive the inner end of the tube.
• the main pipes 6 and 32 both have a closed bottom, while their fluid connections are provided at the top of the pipes.
• the high-pressure fluid thus passes from the main channels 52 to the main inlet manifold, through the opening 320, then is conveyed outwards towards the expander 12.
• the secondary inlet tubing 30 shown partially in FIGS. 8 and 9 receives the low pressure fluid from bottom to top (arrow F4). It does not have a closed bottom. Apertures 34 elongate along the axis XX are provided on the part of the wall of the pipe 30 which is turned towards the outside of the internal exchanger so as to send the fluid into the secondary channels 54. Thus the fluid at low pressure arrives from the bottom of the tubing 30 before going up along it. The fluid then passes through the openings 34, as shown by the arrows indicated in the tubing 30, to spread in the secondary channels 54, at the beginning of the heat exchange.
• the secondary inlet tubing 30 may comprise a plurality of channels 300 elongate along the axis (XX), to promote a better distribution in the secondary channels 54.
• these channels are three in number. non-limiting example.
• the inlet channels 300 generate a good distribution of the refrigerant on the vertical plane.
• the openings 34 are arranged on the secondary inlet pipe 30 so as to optimize the distribution of the low-pressure fluid received in all the secondary channels 54.
• the openings 34 are elongated and arranged to occupy substantially the entire length of the tube.
• three openings 34 are provided for the fluid communication with each of the three channels 300 of the secondary inlet pipe 30.
• the three openings are furthermore slightly offset so as to come into communication with each one. 300 channels of the secondary inlet tubing 30.
• the secondary outlet tubing 7 extends along an axis parallel to the axis (XX) and has a closed bottom. Its fluidic connection is provided on its upper part. Furthermore one or more openings 37 elongate along the axis (XX) are provided on the part of its wall facing the center of the internal exchanger to receive the fluid exiting the secondary channels 54. An embodiment of the openings 37 is shown in Figure 21.
• the low-pressure fluid thus passes secondary channels 54 inside the secondary outlet pipe 7, at the end of the heat exchange, then goes back up the along the tubing before being sent to the compressor 14.
• the main inlet pipe 6 and the secondary outlet pipe 7 may be integral with a connecting plate 76 (see also Figure 21.
• the plate 76 has a curved section and a shape adapted to be housed between the penultimate outer winding of the tube and the last winding of the tube
• the secondary tubing 7 is arranged along the wall of the connecting plate under the last winding of the tube while the main pipe of the 6 is arranged at an edge of the connecting plate, at the outside of the windings
• the section of the secondary tubing 7 has a small radial width section to favor its insertion under the last winding of the tube.
• the heat exchanger also comprises an inner core of substantially cylindrical shape around which the tube 5 is wound. This core 3 makes it possible to stiffen the internal exchanger.
• the core may be in three nested parts 360, 38 and 32, the last part being constituted by the main outlet pipe while the secondary inlet pipe 30 is an integral part of the part 360.
• the assembly of the parts 360 and 38 delimits a recess adapted to house the main outlet pipe 32 for the outlet of the high-pressure fluid 32.
• the core 3 is integral and of generally cylindrical shape.
• the main outlet pipe 32 and the secondary inlet pipe 30 form an integral part of the core 3.
• a tubing 40 is also an integral part of the core 3 to define a passage for the realization of the spiral.
• the core may consist of two coaxial portions 31 and 33.
• the portion 33 is an internal rigid structure having recesses in the form of grooves on its periphery while the portion 31 is constituted a metal sheet surrounding the rigid structure 31 to define the main outlet pipe 32 and the secondary inlet pipe 30.
• the tube 5 according to the invention is produced as a profiled monobloc piece and can be obtained by extrusion.
• the tube 5 is made of aluminum alloy, but other materials are possible.
• the invention makes it possible to obtain a reduced diametral bulk for the internal exchanger, thanks to the alternation of hot main channels 52 and cold secondary channels 54.
• the sealed separation between, on the one hand, the secondary channels 54, and on the other hand, between the secondary channels 54 and the neighboring main channels 52 makes it possible to limit the risks of accumulation of liquid at the bottom of the exchanger and the risks of thermal interference.
• the structure of the internal exchanger according to the invention further ensures good thermal insulation between the main channels 52 and the secondary channels 54, without it is necessary to interpose insulation sheets.
• the invention therefore reduces the number of components in the exchanger, which simplifies the manufacturing process of the exchanger and reduces its costs.
• the profile of the tube or tubes is defined in such a way that the channels formed by winding thereof do not comprise convex shapes in order to avoid any filling of the form previously mentioned with oil and therefore to increase the surface area. exchange.
• the invention also relates to the use of a heat exchanger, as defined above, as an internal exchanger, in which the first fluid is a high-pressure fluid and the second fluid is a low-pressure fluid. .
• the invention further provides an integrated assembly comprising an accumulator and the internal exchanger 9 described above.
• FIG. 1 schematically shows an air conditioning circuit incorporating such an integrated assembly 100.
• the integrated assembly comprises an outer casing 115 in which the internal exchanger 9 and an accumulator 17 are arranged.
• the casing 115 is delimited by a bottom and is closed by a cover, not shown, in order to form a sealed internal chamber.
• the lid and the housing can be fixed together by soldering.
• the lid and the housing may be formed of any suitable material.
• the integrated assembly also comprises an auxiliary tubing 4 designed to receive the low-pressure fluid from the evaporator and convey it towards the bottom of the casing, as shown in FIGS. 8 and 9.
• the auxiliary tubing 4 has a shape General cylindrical and is arranged outside the windings of the tube as shown in Figure 9.
• the fluid that arrives in the pipe 4 is received in the bottom of the housing 115, so that the liquid portion of the refrigerant fluid at low pressure remains at bottom of the housing, while only the vaporized portion of the fluid passes into the secondary inlet pipe 30 whose bottom is open.
• the low pressure fluid is then sent into the secondary channels 54 through the openings 34.
• the main external tubing 6 receives the high pressure fluid that is sent into the main channels 52 to flow in the opposite direction to that of the low pressure fluid. pressure in the secondary channels 54.
• the fluids exchange heat before exiting through their respective outlet pipes 32 and 7.
• the number of main channels 52 may vary depending on the heat exchange to be performed.
• the various components of the integrated assembly 100 are advantageously made of an aluminum alloy and are then brazed by means of solder plating.
• the assembly can be brazed at one time by passing through a brazing furnace. The assembly being thus realized, it is then sufficient to connect it to the branches of the circuit as indicated above.
• Such an integrated assembly reduces the overall size of the air conditioning circuit while providing satisfactory cooling performance.
• the invention applies in particular to air conditioning circuits of motor vehicles.

Landscapes

• Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Thermal Sciences (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Analytical Chemistry (AREA)
• Power Engineering (AREA)
• Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
• Details Of Heat-Exchange And Heat-Transfer (AREA)
• Washing And Drying Of Tableware (AREA)

Priority Applications (3)

Applications Claiming Priority (2)

Publications (1)

Family

ID=38658144

Family Applications (1)

Country Status (6)

Cited By (6)

Families Citing this family (8)

Citations (3)

• 2007
  • 2007-03-12 FR FR0701758A patent/FR2913764B1/fr not_active Expired - Fee Related
• 2008
  • 2008-03-11 ES ES08717605T patent/ES2363053T3/es active Active
  • 2008-03-11 WO PCT/EP2008/052858 patent/WO2008113714A1/fr active Application Filing
  • 2008-03-11 DE DE602008006034T patent/DE602008006034D1/de active Active
  • 2008-03-11 EP EP08717605A patent/EP2118608B1/fr active Active
  • 2008-03-11 AT AT08717605T patent/ATE504793T1/de not_active IP Right Cessation

Patent Citations (3)

Also Published As

Similar Documents

Legal Events