Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
  • F28F9/02—Header boxes; End plates
  • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
  • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
  • F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes

Definitions

• the field of the present invention is that of the heat exchangers equipping the air conditioning installations for a vehicle, in particular an automobile.
• the invention relates more specifically to the distribution of a refrigerant fluid inside a manifold that includes such a heat exchanger.
• a vehicle is commonly equipped with an air conditioning unit for heat treating the air present or sent into the passenger compartment of the vehicle.
• an air conditioning unit for heat treating the air present or sent into the passenger compartment of the vehicle.
• Such an installation comprises a closed circuit inside which circulates a refrigerant fluid. Successively following the direction of circulation of the refrigerant fluid through it, the circuit essentially comprises a compressor, a condenser, a pressure reducer and at least one heat exchanger.
• the heat exchanger commonly comprises a bundle of tubes interposed between a header and a coolant return box.
• the refrigerant is admitted through an inlet mouth inside a manifold, flows along successive paths in the tubes of the bundle between the manifold and a return box, and is discharged out of the exchanger thermal through an outlet mouth.
• the outlet mouth is likely to be formed through the manifold or through the return box.
• the heat exchanger is for example an evaporator providing a heat exchange between the refrigerant and a flow of air therethrough.
• the refrigerant circulates inside the tubes of the bundle and the air flow circulates along the bundle tubes for cooling.
• This phenomenon generates a heterogeneity of the temperature of the air flow that has passed through the heat exchanger during operation. This heterogeneity complicates the thermal management of the apparatus that receives the heat exchanger and ultimately involves temperature differences between two areas of the passenger compartment, while the same airflow temperature is required.
• the present invention relates to a device for dispensing a refrigerant fluid inside a manifold of a heat exchanger.
• the subject of the invention is also a heat exchanger equipped with a device for dispensing a refrigerant fluid according to the invention.
• the heat exchanger is in particular designed to equip an air conditioning installation of a vehicle, in particular an automobile.
• An object of the invention is to perfect the homogeneity of the temperature of the heat exchanger during operation and finally to improve its efficiency.
• Another object of the invention is to perfect the distribution of the refrigerant fluid in the header collector in a homogeneous manner between its liquid phase and its gaseous phase. It is even more specifically targeted by the invention to provide a homogeneous supply of refrigerant fluid bundle tubes interposed between the manifold and the return box of the heat exchanger. Another object of the invention is to provide a refrigerant distribution device that can be obtained industrially at lower costs.
• Another object of the invention is to provide a refrigerant distribution device whose organization allows its easy adaptation and lower costs to heat exchangers of various structures.
• Such a diversity of structures of the heat exchangers is particularly to be appreciated with regard to the number of tubes of the bundle that they comprise, the modes of circulation of the refrigerant fluid inside the heat exchanger and / or relative positions between the mouth inlet and outlet mouth of the refrigerant fluid that includes the heat exchanger.
• the dispensing device of the invention comprises at least one first duct extended along a longitudinal axis defining the longitudinal direction of extension of the dispensing device.
• the first conduit comprises at a first of its longitudinal ends an inlet mouth for the refrigerant fluid admission inside the first conduit.
• the first conduit is closed at its second longitudinal end and comprises along at least a portion of its length a plurality of refrigerant discharge ports out of the first conduit.
• the coolant is intended to be admitted inside the first conduit at its first end having the inlet mouth, the first conduit being closed at its second end to force the passage of the refrigerant through the orifices.
• the dispensing device is mainly recognizable in that at least two orifices immediately adjacent to the longitudinal axis of the first duct are inclined towards the second end of the first duct, their outlet towards the interior of the first duct being closer to its first end than their outlet to the outside of the first conduit.
• all the orifices of the first conduit are inclined orifices.
• various variants can be implemented depending on the configuration of the heat exchanger and its performance obtained.
• the first conduit may comprise at least one group of orifices inclined in number greater than two.
• At least two groups of inclined orifices may be separated from each other by at least one intermediate orifice oriented differently with respect to the inclination of the inclined orifices.
• the intermediate orifice may for example be oriented perpendicular to the longitudinal axis of the first conduit.
• the intermediate orifice may be inclined towards the first end of the first conduit, its outlet into the first conduit being farther from its first end than its outlet outwardly of the first conduit.
• the velocity of the refrigerant fluid circulating inside the first conduit and discharged successively through the inclined orifices causes the refrigerant fluid, in particular the liquid phase thereof, towards the second end of the first conduit.
• the inclination of the inclined orifices thus promotes a homogeneous discharge of the refrigerant fluid therethrough between its liquid phase and its gaseous phase along the entire first conduit.
• the tubes of a bundle of tubes equipping a heat exchanger are typically sequentially arranged along the longitudinal axis of the first conduit to open on a manifold.
• the entrainment of the refrigerant fluid towards the second end of the first conduit thus makes it possible to homogenize the refrigerant supply of all the tubes of the bundle of tubes.
• the performance of the heat exchanger is increased.
• the temperature of the air passing through the heat exchanger is substantially balanced along all the tubes of the bundle of tubes.
• the temperature of a coolant flowing through a hydraulic cooling circuit extending at least partly along the heat exchanger is also considerably balanced during its passage along the entire tubes of the bundle of tubes.
• the inclination angles of the inclined orifices are less than 90 ° relative to the longitudinal axis of the first conduit, to cause a drive of the refrigerant, including its liquid phase, to the second end of the first conduit.
• the angle of inclination of the inclined orifices is measured between the longitudinal axis of the first duct and the direction of inclination of the orifices inclined towards the second end of the first duct.
• the inclination of the inclined orifices may vary in this angular range less than 90 °, for example as a function of the individual position of the orifices inclined with respect to the ends of the first duct, depending on their number and / or their position. along the first duct, and / or as a function of the longitudinal extension of the first duct, or even of its transverse extension.
• the number and position of inclined orifices are also likely to vary along and / or around the first conduit depending on the amount of coolant carried to the second end of the first conduit.
• the number and the position of orifices inclined along and / or around the first duct are adapted according to a specific configuration of a heat exchanger receiving the dispensing device, to evacuate the cooling fluid. homogeneously between its liquid phase and its gaseous phase along the first conduit.
• the inclination angles of the inclined orifices are between 30 ° and 60 ° with respect to the longitudinal axis of the first duct. Such a compromise is considered with regard to the performance obtained from the heat exchanger.
• An angle of inclination of the inclined orifices less than 30 ° tends to affect a projection of the refrigerant through the orifices inclined in a direction providing an optimized supply of refrigerant fluid of all tubes of the tube bundle of the exchanger.
• An angle of inclination of inclined orifices greater than 60 ° can make random a homogeneous supply of refrigerant fluid tubes of the beam.
• angles of inclination of at least two inclined orifices are different.
• the inclination angles of at least two inclined orifices vary progressively from the first end to the second end of the first conduit. More particularly, the inclination angles of at least two inclined orifices increase from the first end to the second end of the first conduit.
• the variation of the inclination angles of the inclined orifices is preferably carried out successively for each of the inclined orifices.
• the successive variation of the inclination angles of the inclined orifices is preferably carried out in a regular manner, in particular in the case where the inclined orifices are equidistant along the first duct.
• the variation of the inclination angles of the inclined orifices is successively carried out in groups of at least two inclined orifices.
• the inclination angles of the inclined orifices are identical.
• the angle of inclination of each of the inclined orifices is preferably 45 ° to promote a homogeneous flow of refrigerant to the second end of the first conduit. It is also avoided a suction effect of the refrigerant by the tubes of the bundle of tubes located closest to the first end of the first conduit. Such a suction effect can be induced due to a possible depression generated in this zone extending close to the first end of the first duct, especially in the case where a mouth of the refrigerant outlet out of the heat exchanger is located close to the entrance.
• the inclined orifices are aligned along a straight line parallel to the longitudinal axis of the first conduit.
• the orifices may be distributed on either side of a straight line parallel to the longitudinal axis of the first conduit.
• the inclined orifices are nevertheless preferably formed along a half volume of the first pipe considered along its longitudinal axis.
• the inclined orifices are preferably arranged equidistant from one another along the first conduit.
• two adjacent groups of at least two inclined orifices may be placed along the first conduit at a separation distance from one another different from that separating one from the other at least two other groups adjacent to at least two inclined orifices.
• the dispensing device comprises at least a second longitudinally extended duct, advantageously closed at each of its longitudinal ends.
• the second duct houses the first duct along its longitudinal extension, leaving between them a channel surrounding the first duct.
• the second conduit is provided with passages for discharging refrigerant from the channel to the outside of the dispensing device.
• the second conduit forms an enclosure within which extends longitudinally the first conduit, a transverse gap being provided between the first conduit and the second conduit to form the channel.
• the refrigerant discharged through the orifices of the first conduit is able to circulate inside the channel at least partly around the first conduit prior to its evacuation out of the dispensing device through the passages.
• a first step of homogenizing the refrigerant between its liquid phase and its gaseous phase is performed during the evacuation of the refrigerant through the orifices to the channel.
• a second step of homogenizing the refrigerant between its liquid phase and its gaseous phase is then operated during its circulation inside the channel.
• the channel is adapted to accommodate at least one permeable body structured in a mixer to increase the mixing of the refrigerant between its liquid phase and its gas phase prior to its evacuation out of the dispensing device through the passages.
• a mixer is a member generating a disturbance of a linear flow of the refrigerant flowing therethrough.
• the mixer provides obstacles against the linear flow of refrigerant inside the channel. The homogenization of the refrigerant between its liquid phase and its gaseous phase during its circulation inside the channel is thus obtained efficiently.
• the configuration of the orifice through which the coolant is discharged out of the conduit can be advantageously differentiated from the configuration of the passage through which the coolant is dispensed from the dispensing device to the tubes of the bundle that includes the heat exchanger.
• the configuration, number and / or distribution of orifices along the first conduit can be determined independently of the configuration, number and / or distribution of passages along the second conduit.
• the orifices may be specifically configured to optimize the mixture obtained between the liquid phase and the gaseous phase of the refrigerant discharged through the first conduit.
• the passages can be specifically configured to make reliable and improve the homogenization of the distribution of the refrigerant fluid individually to each tube of a tube bundle of the heat exchanger.
• a combination between the specific characteristics of the orifices and the passages may be chosen to improve the obtaining of a homogeneous refrigerant supply of the tubes of the bundle, according to the specificity of the structural arrangement of the heat exchanger.
• the specificity of the structural arrangement of the heat exchanger is in particular to be considered with regard to the number and / or the configuration of the tubes of the bundle of tubes that includes the heat exchanger and / or the fluid circulation conditions between the box collector and the return box.
• the characteristics considered for such a combination are in particular relating to the transverse section, the number, the orientation and / or the positions of the orifices along the first conduit and those relating to the transverse section, the number, the orientation and or at the positions of the passages along the second conduit.
• the passages can be individually assigned to the tubes of the exchanger bundle, being placed in direct communication with their outlet on the manifold.
• the refrigerant fluid supply of the tubes of a bundle of tubes that comprises the heat exchanger can be performed:
• the first duct and the second duct may be mounted eccentrically relative to each other or to be mounted coaxially one inside the other along the longitudinal axis of the first duct.
• the first conduit and the second conduit have in particular an annular conformation centered on the longitudinal axis of the first conduit.
• the transverse sections of the first duct and the second duct may be differentiated with respect to each other, for example being individually of circular or oblong conformation.
• the passages are oriented perpendicular to the longitudinal axis of the first conduit. Homogenization of the quantities of refrigerant fluid successively discharged through the orifices along the first conduit, allows to direct the passages specifically towards the outlets on the manifold of the tubes of a bundle of tubes that includes a heat exchanger receiving the dispensing device.
• the orifices are aligned along a first straight line parallel to the longitudinal axis of the first conduit and the passages are aligned along a second straight line parallel to the longitudinal axis of the first conduit or in other terms parallel to the first line.
• the invention also relates to a heat exchanger comprising at least one manifold provided with a dispensing device according to the invention. The manifold is extended in a longitudinal direction by providing a chamber housing the dispensing device extending longitudinally within the chamber along the longitudinal extension of the manifold.
• the chamber communicates with a plurality of tubes of a tube bundle of the heat exchanger successively arranged in the longitudinal direction of the header and interposed between the header and a fluid return box. refrigerant to the collection box.
• the orifices of the first duct are inclined towards the bottom of the header located opposite the inlet mouth in the longitudinal direction of the manifold.
• the internal volume of the header is at least partly placed in communication with the tube tubes of the heat exchanger tube via the chamber housing the dispensing device.
• the tubes are for example grouped into a first sheet of successively adjacent tubes along the longitudinal axis of extension of the manifold.
• the tubes extend between the header and the return box in a direction perpendicular to the longitudinal direction of extension of the manifold.
• the inclination of the orifices towards the bottom of the header box provides a homogeneous distribution of the coolant towards all the tubes of the bundle of tubes.
• the orifices open out of the first conduit opposite the opening of the tube bundle tubes on the chamber, to constrain a circulation of refrigerant fluid at least partly around the first conduit prior to feeding the tubes of the refrigerant fluid beam.
• a second conduit provided with passages opening on the chamber is interposed between the first conduit and a wall of the manifold defining the chamber.
• a channel is provided between the second conduit and the first conduit and a space is provided between the second conduit and the wall of the manifold defining the chamber.
• the coolant is discharged from the first conduit through the orifices inclined toward the channel, circulates within the channel at least in part around the first conduit, and is discharged out of the channel through the passages to said space.
• the refrigerant circulates inside the space prior to the supply of refrigerant fluid tubes of the bundle of tubes to increase the homogeneous mixture of the refrigerant between its liquid phase and its gas phase.
• the passages are in particular oriented perpendicularly to the longitudinal axis of the first conduit and parallel to a direction of extension of the tube bundle tubes between the header and the return box.
• the passages open on the chamber opposite the opening of the tube bundle tubes on the chamber and the openings open out of the first conduit on the side of the outlet of the beam tubes on the chamber.
• the coolant is discharged from the first conduit through the orifices inclined towards the channel in a first zone of the manifold disposed on the side of the tubes of the bundle.
• the coolant flows at least partly around the first conduit through the channel, out of which the coolant is discharged through the passageways to the space in a second zone of the manifold further away from the tubes of the bundle than the first zoned.
• the refrigerant fluid then circulates inside the space at least partially around the second conduit to the outlet of the tubes of the bundle in the manifold.
• the circulations of the refrigerant fluid on the one hand inside the channel at least partly around the first duct and on the other hand inside the space at least partly around the second duct are thus optimized to increase obtaining a homogeneous mixture of the refrigerant fluid between its liquid phase and its gaseous phase.
• the chamber is longitudinally compartmentalized by partitions in a plurality of cells each communicating with at least one tube of the tube bundle, and advantageously with a single tube of the bundle of tubes. It is therefore associated with a cell to a tube. At least one passage leads to each of the cells. Each of the cells is thus individually supplied with refrigerant fluid from its individual communication with at least one passage.
• the tubes of the bundle of tubes are individually supplied with refrigerant fluid from a cell assigned to them.
• the distribution of the refrigerant fluid to the tubes of the bundle of tubes is made reliable and is obtained efficiently.
• each of the cells is communicating with a single tube to promote the homogeneous supply of refrigerant fluid of all tubes of the tube bundle and enhance the performance of the homogeneous supply tube tubes refrigerant fluid tube.
• the partitions are advantageously formed by walls of the tubes forming between them eyelets participating in the formation of the wall of the collecting chamber defining the chamber.
• the heat exchanger is used in particular as an evaporator, in particular organized to equip an air conditioning installation of a vehicle.
• the heat exchanger can be used to cool an air flow therethrough or to cool a liquid dedicated to cooling an organ, such as at least one battery of a vehicle providing the energy required at least in part to his propulsion.
• the invention also relates to a refrigerant circuit comprising at least one compressor, a condenser or gas cooler, an expansion device, and a heat exchanger according to the invention, traversed by a refrigerant.
• the invention also relates to a ventilation, heating and / or air conditioning, or air conditioning installation, configured to equip a vehicle, including an automobile comprising at least one heat exchanger according to the invention.
• FIG. 1 is a schematic illustration of a refrigerant circulation circuit participating in an air conditioning installation of a vehicle.
• FIG. 2 is a schematic illustration of a heat exchanger that comprises the circuit shown diagrammatically in FIG.
• FIG. 3 is a partial illustration of a first participating conduit of a dispensing device according to the invention.
• FIG. 4 is a partial illustration of an embodiment of a heat exchanger according to the invention in the area of a manifold that it comprises.
• FIG. 5 is a partial illustration of another embodiment of a heat exchanger according to the invention in the area of a manifold that it comprises.
• FIG. 6 is a partial illustration of another embodiment of a heat exchanger according to the invention in the area of a manifold that it comprises.
• an air conditioning installation for a vehicle includes a closed circuit 1 inside which circulates a refrigerant fluid FR.
• the circuit 1 essentially comprises, successively in the direction SI of circulation of the refrigerant fluid FR, a compressor 2, a condenser 3 or gas cooler, an expansion member 4 and at least one heat exchanger 5 .
• the heat exchanger 5 is for example dedicated to the cooling of a flow of air FA passing therethrough, as illustrated in FIG. 2.
• a flow of air FA is notably used for heat treatment of the air of the vehicle interior or for example still to cool a body of the vehicle in operation.
• the heat exchanger 5 can be used for cooling a liquid used to cool a body of the vehicle in operation, such as one or more batteries supplying electrical energy to a propulsive electric engine of the vehicle.
• the heat exchanger 5 comprises a bundle 6 of tubes 12 interposed between a manifold 7 and a return box 8.
• the manifold 7 extends in a longitudinal direction D1 oriented perpendicular to a extension direction D3 tubes 12 of the bundle 6 of tubes 12 between the manifold 7 and the return box 8.
• the manifold 7 defines a chamber 9 supplied with refrigerant fluid FR through an inlet mouth 10.
• the refrigerant fluid FR circulates inside the heat exchanger 5 to cool at least the tubes 12 of the bundle 6 of tubes 12 and is discharged out of the heat exchanger 5 through an outlet mouth 11.
• the outlet mouth 11 is formed through the manifold 7, which implies that the heat exchanger 5 is a heat exchanger with "U" circulation.
• the outlet mouth 11 may be formed through the return box 8, which then implies that the heat exchanger 5 is an "I" circulation heat exchanger.
• the heat exchanger 5 is of the U-circulation type of the refrigerant fluid FR.
• the heat exchanger 5 is intended for cooling an air flow FA.
• the tubes 12 of the bundle 6 of tubes 12 typically comprise fins 13 promoting the heat exchange between the air flow FA and the tubes 12 of the bundle 6 of tubes 12.
• the flow of air FA passes through the bundle 6 of tubes 12 transversely to the general plane PI of the heat exchanger 5, flowing along the tubes 12.
• the refrigerant fluid FR flows from the manifold 7 to a first ply 12a of tubes 12 of the bundle 6 of tubes 12 dedicated to the supply of the return box 8 of refrigerant fluid FR. Then the refrigerant fluid FR flows from the gearbox 8 to the manifold 7 through a second ply 12b of tubes 12 of the bundle 6. The first ply 12a and the second ply 12b are superimposed according to the direction of flow of the flow. FA air through the heat exchanger 5.
• Such a configuration of the heat exchanger 5 makes it particularly useful obtaining a homogeneous distribution of the refrigerating fluid FR between its liquid phase and its gaseous phase and a homogeneous distribution of the refrigerant fluid FR along the manifold 7 to each of the tubes 12 of the first ply 12a of the bundle 6 of tubes 12.
• the described example of the architecture of the heat exchanger 5 and the circulation of the refrigerant FR between the manifold 7 and the return box 8, are given for information and are not restrictive as to the scope of the invention.
• the chamber 9 accommodates a dispensing device 18 extending in a longitudinal direction D2 parallel to the longitudinal extension direction D 1 of the manifold 7.
• the dispensing device 18 comprises a first conduit 14 extending along a longitudinal axis A1 between a first end 15 and a second end 16 of the first conduit 14.
• the first conduit 14 is intended in particular to provide a homogenization of the refrigerant fluid FR between its liquid phase and its gaseous phase during its evacuation out of the first conduit 14.
• the longitudinal axis A1 of the first duct 14 is oriented parallel to the extension direction D1 of the manifold 7 and defines the longitudinal extension direction D2 of the dispensing device 18.
• the dispensing device 18 is potentially centered at the inside the manifold 7 as illustrated in Figure 1. Alternatively, it can be eccentric inside the manifold 7 with respect to a central longitudinal axis A2 of extension of the manifold 7, such as illustrated in Figure 2.
• a first longitudinal end of the first duct 14 comprises the inlet mouth 10 for the supply of refrigerant FR of the dispensing device 18 via the first duct 14.
• the inlet mouth 10 is capable of receiving the refrigerant fluid FR since the outside of the distribution device 18 is directly or via a connecting member of the heat exchanger 5 with the fluid circuit 1 illustrated in Figure 1.
• the second end 16 of the first conduit 14 is closed by a shutter formed for example d a bottom wall 16 'incorporated in the first conduit 14 as illustrated in FIG. 3. It will be noted that the bottom wall can also be part of the manifold 7.
• At least one orifice 17 is formed through the first conduit 14 for the discharge of the refrigerant fluid FR from the first conduit 14 to the chamber 9.
• the first conduit preferably comprises a plurality of orifices 17 formed on at least a portion of its length to promote the homogenization of the refrigerant discharged along the first conduit 14 between its liquid phase and its gaseous phase.
• FIGs 3 to 6 various embodiments of a dispensing device 18 according to the invention are illustrated.
• the dispensing devices 18 illustrated in Figures 3 to 6 are arranged to be housed in the manifold 7 from which the tubes 12 of the first web 12a that includes the heat exchanger 5 are supplied with refrigerant fluid FR.
• the dispensing devices 18 comprise at least the first conduit 14 provided with a plurality of orifices 17 through which the refrigerant fluid FR admitted inside the first conduit 14 is discharged.
• the first duct 14 has orifices 17 which are in their entirety inclined towards its second end 16. As referenced in FIG. 3, the inclination of the orifices 17 is such that their outlet 17a towards the interior of the first conduit 14 is closer to its first end 15 than its outlet 17b towards the outside of the first conduit 14.
• At least two adjacent orifices 17 are inclined.
• the adjacency between two inclined orifices 17 is a disposition immediately side by side of the two inclined orifices 17, in particular in the longitudinal direction D2 of the dispensing device.
• the velocity of the refrigerant fluid FR flowing through the first conduit 14 from its first end 15 to its second end 16 is used to promote a drive of the refrigerant fluid FR, including its liquid phase, to the second end 16 of the first conduit 14 .
• the FR refrigerant jets discharged out of the inclined orifices 17 generate a displacement of the vapor phase and the liquid phase of the refrigerant fluid FR outside the first conduit 14 towards the second end 16 of the first conduit 14.
• the refrigerant supply FR, homogeneous between its liquid phase and its vapor phase, of each of the tubes 12 of the bundle 6 that comprises the heat exchanger 5 is obtained efficiently, which thus promotes the homogenization of the temperature of the airflow FA on an exit surface of the heat exchanger 5.
• the orifices 17 inclined in their entirety are aligned along a first straight line L1 parallel to the longitudinal axis A1 of the first duct 14.
• the inclined orifices 17 are arranged equidistant from one another and are inclined, in particular an angle of 45 ° with respect to the longitudinal axis A1 of the first duct 14.
• the inclined orifices 17 may, however, be distributed differently along and / or around the first duct 14.
• the inclined orifices 17 may be distributed as aligned along at least two straight lines parallel to the longitudinal axis A1 of the first duct 14.
• the inclined orifices 17 may be arranged in staggered rows along the first duct 14.
• the inclined orifices 17 may be distributed along at least two ducts. a helical portion extending along the longitudinal axis A1 of the first duct 14.
• the number of orifices 17 inclined of the same group of orifices 17 inclined may vary, being greater than two inclined orifices 17,
• the number of groups of orifices 17 inclined may vary.
• a group of inclined orifices 17 is identifiable in the case where at least one intermediate orifice is interposed between at least two groups of inclined orifices 17.
• Such an intermediate orifice is for example oriented perpendicularly with respect to the longitudinal axis A1 of the first conduit 14 or more generally is oriented differently with respect to the orientation of the orifices inclined towards the second end 16 of the first conduit 14,
• An angle of inclination B individual two inclined orifices 17 may vary within an angular range of less than 90 °.
• the inclination angle B 1 of the inclined orifices 17 is measured between the longitudinal axis Al of the first duct 14 and the inclination slope of the inclined orifices 17 seen from the second end 16 of the first conduit 14,
• the angle of inclination B individual inclined holes 17 may vary gradually from the first end 15 to the second end of the first conduit 16. More particularly, the angle of inclination of individual B holes 17 is likely to increase progressively from the first end 15 towards the second end of the first conduit 16,
• a separation distance D4 between two orifices 17 immediately adjacent to all the orifices 17 of the first conduit 14 may vary along the length of the first conduit 14.
• the separation distance D4 between two orifices 17 immediately adjacent may increase progressively from the first end 15 of the first conduit 14 to the second end 16 of the first conduit 14.
• Such variation in distance can be achieved between two adjacent orifices 17, that at least one of the two adjacent orifices 17 is inclined or be a intermediate orifice oriented differently from the orientation of the inclined orifices, such as for example perpendicular to the longitudinal axis A1 of the first duct 14,
• the orifices 17, inclined or not, of all the orifices 17 of the first conduit 14 may be variously distributed along the first conduit 14, being aligned or being variously distributed around the first conduit 14, such as for example staggered or along a portion of helix wound at least partly around the first conduit 14.
• the inclined orifices 17 are formed along the same longitudinal portion of the first conduit 14, the trans-shaped profile of which is shaped in half-section of the first conduit 14.
• the longitudinal portion of the first conduit 14 having the orifices 17 has a cross section shaped in a semicircle.
• a dispensing device 18 comprising a first conduit 14 of the invention is housed inside the chamber 9 formed inside the manifold 7.
• the chamber 9 is delimited by a wall 7a of the manifold 7 formed by eyelets 25 successively abutted in the direction D1 of extension of the manifold 7.
• the eyelets 25 are formed in extension of the tubes 12 of the bundle 6 of the heat exchanger 5.
• the first conduit 14 is preferably mounted on the manifold 7 while being centered inside the chamber 9 along the longitudinal axis A2 of the manifold 7.
• the first conduit 14 may be mounted on the manifold 7 eccentrically relative to the chamber 9 along the axis longitudinal A2 of the manifold 7.
• a transverse direction DT is considered to be the longitudinal axis A1 of the first duct 14, parallel to the extension direction D3 of the tubes 12 of the bundle 6 of tubes 12 between the manifold 7 and the return box. 8.
• the inclined orifices 17 open on the chamber 9 opposite the outlet 24 of the tubes 12 on the chamber 9 for supplying the tubes 12 with refrigerant fluid FR.
• the refrigerant fluid FR admitted into the first conduit 14 is successively discharged to the chamber 9 through the inclined orifices 17 in substantially homogeneous fractions between the liquid phase and the vapor phase of the refrigerant fluid FR.
• the refrigerant fluid FR then circulates inside the chamber 9 at least partly around the first conduit 14 to the tubes 12 of the bundle 6 of tubes 12 for their individual supply of refrigerant fluid FR.
• the first duct 14 is surrounded by a second duct 19 interposed between the first duct 14 and the wall 7a of the manifold 7 delimiting the chamber 9.
• the second duct 19 surrounds at a distance first conduit 14 by providing between them a channel 22 for circulating the refrigerant fluid FR discharged from the orifices 17.
• the second conduit 19 has passages 20 for the discharge of the refrigerant fluid FR from the dispensing device 18 from the channel 22 to the tubes 12 of the bundle 6 of tubes 12.
• the second duct 19 is centered inside the chamber 9 and / or centered with respect to the first duct 4.
• the second duct is mounted on the manifold 7 by passing longitudinally through the eyelets 25 forming the wall 7a. of the manifold 7 delimiting the chamber 9.
• the second duct 19 is placed at a transverse distance from the wall 7a of the manifold 7 delimiting the chamber 9, leaving between them a space El on which the passages 20 open out.
• the space E 1 forms a circulation space for the refrigerating fluid FR inside the chamber 9 at least partly around the second conduit 19 towards the outlets 24 of the tubes 12 of the bundle 6 of tubes 12 on the chamber 9.
• the passages 20 are oriented perpendicular to the longitudinal axis A1 of the first duct 14 being aligned along a line L2 parallel to the first line L1.
• the first line L1 and the second line L2 extend parallel on either side of the longitudinal axis A1 of the first duct 14.
• the orifices 17 are formed along a longitudinal portion of the first duct 14 situated on the side of the outlets 24 of the tubes 12 of the bundle 6 of tubes on the chamber 9.
• the passages 20 are formed through a longitudinal portion of the second conduit 19 located opposite the opening of the tubes 12 of the bundle 6 of tubes 12 on the chamber 9 with respect to the longitudinal axis A1 of the first conduit 14.
• the refrigerating fluid FR is admitted inside the first duct 14 and is discharged from the first duct 14 to the duct 22 through the orifices 17. Then the refrigerant FR is evacuated out of the duct 22 through the passages 20 to the space E1 and then circulates in the space E1 at least partly around the second duct 19 to the outlets 24 of the tubes 12 of the bundle 6 of tubes 12 for their supply of refrigerant FR.
• the chamber 9 is partitioned by transverse partitions 23 into a plurality of cells E2 successively adjacent in the longitudinal direction D1 of the header box 7. At least one passage 20 opens on each of the E2 cells .
• the partitions 23 are formed by walls of the eyelets 25 extending the tubes 12 of the bundle 6 of tubes 12. Each of the cells E2 is in communication with one of the tubes 12 of the bundle 6 of tubes 12. The partitions 23 are in contact with each other. the peripheral wall of the second conduit 19.
• the refrigerant fluid FR is admitted inside the first conduit 14 and is discharged from the first conduit 14 through the orifices 17 to the channel 22.
• each cell may be associated, that is to say in fluidic relation, to a single outlet 24 of tube 12 of the bundle of tubes.
• a cell may be associated with a plurality of outlets 24 of tubes 12, provided that this number of outlets is less than the total number of outlets 24 of the tube bundle 12.
• the invention promotes the liquid-gas mixture of the refrigerant while optimizing the supply of refrigerant thus mixed tubes farthest from the inlet mouth for the refrigerant admission inside the first conduit.

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• Engineering & Computer Science (AREA)
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• Thermal Sciences (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
• Details Of Heat-Exchange And Heat-Transfer (AREA)

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• 2016
  • 2016-11-30 FR FR1661735A patent/FR3059404B1/fr active Active
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