CN110168303A - Constitute the hybrid component of the refrigerant assigned unit in the pipe for homogenizing heat exchanger - Google Patents

Abstract

The present invention relates to a kind of hybrid component (25), for being blended in the liquid and gas of the refrigerant to circulate in the collecting box of heat exchanger (FR).The hybrid component (25) includes at least one wall (30), wall (30) includes multiple mixed patterns (34a, 34b), and mixed pattern (34a, 34b) is arranged to guiding refrigerant (FR) into the periphery edge of hybrid component (25) into.The mixed pattern (34a, 34b) is along axis of elongation (A9) tandem sequence repeats.Mixed pattern (34a, 34b) extends between the first lip (35') and the second lip (36').The first lip (35') and the second lip (36') of identical mixed pattern (34a, 34b) are formed in the edge angle (δ) within the scope of 0 ° to 90 ° each other.

Description

Mixing constituting means for homogenizing the distribution of refrigerant in the tubes of heat exchangers member

technical field

The field of the invention is that of heat exchangers forming part of a refrigerant circuit with which a motor vehicle is equipped. The subject of the invention is a mixing member forming part of a device for homogenizing the distribution of refrigerant within the tubes of such a heat exchanger.

Background technique

Motor vehicles are often equipped with ventilation, heating and/or air conditioning units for thermally treating the air present in or fed into the interior of the motor vehicle. For this purpose, such a device is associated with a closed circuit in which the refrigerant circulates. The refrigerant circuit comprises in turn a compressor, a gas condenser or cooler, an expansion member and a heat exchanger. A heat exchanger is housed within the ventilation, heating and/or air conditioning unit to allow heat exchange between the refrigerant and the air flow circulating within said unit before the air flow is delivered to the interior of the vehicle.

According to one mode of operation of the refrigerant circuit, the heat exchanger acts as an evaporator to cool the air flow. In this case, the refrigerant is compressed in the compressor, then the refrigerant is cooled in the gas condenser or cooler, then the refrigerant undergoes expansion in the expansion member, and finally the refrigerant flows from the air in the heat exchanger obtain heat energy. When the refrigerant leaves the expansion member and enters the heat exchanger, the refrigerant is in a two-phase state and exists in a liquid and a gas phase.

The heat exchanger consists of a header tank and a return tank with a bundle of tubes interposed between them. During operation of the refrigerant circuit, refrigerant enters the heat exchanger through an inlet opening included in the header tank. The refrigerant then flows between the header tank and the return tank by using bundled tubes.

A common problem that arises is that it is difficult to supply the bundle tubes evenly with respect to the different phases of refrigerant (liquid and gas).

In particular, non-uniformity in the supply of refrigerant to the tube bundles results in non-uniformity in the temperature of the air flow through the heat exchanger. Such non-uniformity tends to create undue and undesirable temperature differences between regions within the vehicle interior, and this is detrimental.

Document US 2015/0121950 proposes a device housed inside the header tank for homogenizing the distribution of the refrigerant within the bundle tubes. The device includes a pipe provided with a plurality of orifices. The conduit has a first end connected to the first inlet opening for refrigerant to enter the heat exchanger. The conduits are arranged as a cylindrical tube defining an uninterrupted internal volume within which the refrigerant circulates. Liquid-phase refrigerant is sprayed in the form of droplets through orifices formed on the pipes.

This organization is not optimal from the point of view of homogenizing the refrigerant distribution within the heat exchanger. More specifically, the bundle of tubes furthest from the first end is generally undersupplied with refrigerant.

This results in non-uniformity in the temperature of the air stream leaving the heat exchanger, which is unsatisfactory.

Contents of the invention

An object of the present invention is to improve the uniformity of the distribution of the refrigerant within the heat exchanger so as to ultimately improve its efficiency and output to deliver an air flow of the desired temperature to the interior of the vehicle.

Another object of the invention is to improve the distribution of the refrigerant in the heat exchanger, including when the refrigerant is present in the heat exchanger in two different phases, liquid and gas, in variable relative proportions.

Another object is to design a hybrid element whose shape is easy to demould.

Another object is to propose a device for distributing refrigerant within a bundle of tubes that ensures an equal supply of refrigerant to the bundle of tubes, including the tube furthest from the first end of the tube that first receives the refrigerant.

Another object is to propose a device for distributing refrigerant designed to avoid accumulation of refrigerant in any one of its zones.

The mixing member of the present invention is a mixing member for mixing the liquid phase and the gas phase of the refrigerant flowing through the header tank of the heat exchanger. The mixing member includes at least one centrifugal wall including a plurality of mixing patterns arranged to direct refrigerant towards a peripheral edge of the mixing member. The mixed pattern repeats continuously along the axis of elongation. A mixed pattern extends between the first lip and the second lip. The first mixed pattern continues from the second mixed pattern along the axis of elongation.

According to the invention, the first lip and the second lip of the same mixed pattern form with each other a lip angle in the range of 0° and 90°, advantageously in the range of 0° and 20°.

Such a mixing member promotes mixing of the liquid and gas phases of the refrigerant passing therealong. Such hybrid members also include shapes with draft angles that allow easy demolding of the hybrid member.

The lip here is the area that defines the blend pattern. According to an example, the lip takes the form of a gradient inversion of the wall of the mixing member. The lip according to the invention does not necessarily comprise a solid intersection, but may be formed by a curved region of the wall.

One approach for measuring the lip angle includes extending a first line transverse to the axis of elongation and along a first lip of a mixed pattern, a second line transverse to the axis of elongation and along a second lip of the same mixed pattern. two straight lines, and then project the first and second straight lines onto a plane perpendicular to the elongated axis. Therefore, when the angle between these two projected straight lines is in the range of 0° and 90°, the hybrid component can be identified.

The mixing member advantageously comprises at least any one of the following features, alone or in combination:

- at least one of said lips is defined by crests and troughs extending between two adjacent blending patterns in a plane transverse to the axis of elongation.

- said walls are continuous from one mixed pattern to the other.

- said walls are designed to centrifugally move the refrigerant circulating along the mixing member.

- A first lip of a first mixed pattern coincides with a second lip of a second mixed pattern immediately adjacent to the first mixed pattern.

- said lip angle is between 0° and 10°.

- said lip angle is zero.

- said first mixed pattern and second mixed pattern are identical and arranged end to end one after the other along the axis of elongation.

- Each mixed pattern is arranged in a part of the spiral.

- said first mixed pattern is twisted in a clockwise direction about an axis of elongation and said second mixed pattern is twisted in a counterclockwise direction about an axis of elongation.

- A first lip of a first mixed pattern and a second lip of an adjacent second mixed pattern together form a pattern angle of zero degrees.

- Each mixing element extends between a first edge and a second edge forming a zero edge angle between them.

- A first edge of one mixing element forms a zero element angle with a second edge of an adjacent mixing element.

- said first mixing pattern and a second mixing pattern adjacent to the first mixing pattern together form mixing elements, for example identically repeating, along the axis of elongation.

The angles chosen above will be measured according to the measurement protocol described above, ie by projecting a straight line onto a plane perpendicular to the axis of elongation.

Another subject of the invention is a distribution homogenization device for homogenizing the distribution of refrigerant in the tubes of a heat exchanger, intended to be accommodated in the header tank of the heat exchanger, the distribution homogenization device Comprising a duct provided with at least one window through which refrigerant can enter the duct and at least one orifice through which refrigerant can exit the duct, said duct housing at least one such mixing member.

The means for homogenizing the distribution advantageously comprises at least any one of the following features, alone or in combination:

- The duct defines an inner volume in which the mixing member extends at least partially.

- the duct defines an internal cross section generally occupied by the mixing member, such internal cross section corresponding to a section perpendicular to the longitudinal axis of the duct in a part of the duct comprising a plurality of orifices.

- The mixing member occupies the entire internal volume.

-Mix components are centered inside the pipe.

The invention also relates to a header tank defining a first chamber housing at least one such distribution homogenizing device.

The invention also relates to a heat exchanger comprising such a header tank and a return tank, between which a bundle of tubes is interposed.

The invention also relates to a refrigerant circuit comprising at least one such heat exchanger.

The invention also relates to a method for obtaining such a mixing member from a mold comprising a first cavity and a second cavity which together form a molding space of the same shape as the mixing member.

The invention also relates to the use of such a heat exchanger as an evaporator accommodated in the housing of a ventilation, heating and/or air-conditioning device with which a motor vehicle is equipped.

Description of drawings

Other features, details and advantages of the invention will become apparent from reading the following detailed description given by way of illustration and with reference to the accompanying drawings, in which:

- Figure 1 is a schematic diagram of a refrigerant circuit comprising a heat exchanger according to the invention,

- Figure 2 is a schematic perspective view of a first alternative form of embodiment of the heat exchanger shown in Figure 1,

- Figure 3 is a schematic perspective view of a second alternative form of embodiment of the heat exchanger shown in Figure 1,

- Figure 4 is a perspective view with a cutaway of the device for homogenizing the distribution of refrigerant, with which the heat exchanger shown in Figure 2 or 3 is intended to be equipped,

- Figure 5 is a schematic perspective view of a mixing member forming part of the refrigerant distribution and homogenization device shown in Figure 4 .

Detailed ways

The drawings and their description illustrate the invention in detail and in terms of specific ways of carrying out the invention. Where appropriate, they can be used to better define the invention.

Figure 1 depicts a closed circuit 1 in which refrigerant FR circulates. In the exemplary embodiment shown, along the direction S1 in which the refrigerant FR circulates in the refrigerant circuit 1 , the refrigerant circuit 1 sequentially comprises a compressor 2 for compressing the refrigerant FR, a gas for cooling the refrigerant FR A condenser or cooler 3 , an expansion member 4 in which the refrigerant FR undergoes expansion, and a heat exchanger 5 . The heat exchanger 5 is accommodated in a housing 6 of a ventilation, heating and/or air-conditioning device 7 through which an air flow circulates. As shown in Figure 2, the heat exchanger 5 allows heat transfer between the refrigerant FR and the air flow FA in contact with and/or passing therethrough. According to the mode of operation of the refrigerant circuit 1 described above, when the air flow FA comes into contact with and/or passes through the heat exchanger 5, the heat exchanger 5 acts as an evaporator to cool the air flow FA.

In Figures 2 and 3, the heat exchanger 5 comprises a header tank 8 and a return tank 9, between which a bundle of tubes 10, 10a, 10b is interposed. Overall, the heat exchanger 5 extends parallel to a first plane P1 containing the header tank 8 , the tube bundles 10 , 10 a , 10 b and the return tank 9 . The header tank 8 is above the bundle tubes 10, 10a, 10b, which themselves are located above the return tank 9, in particular when the heat exchanger 5 installed in the housing 6 is in its position of use. In other words, in this position of use, the header tank 8 is the top tank of the heat exchanger 5 and the return tank 9 is the bottom tank of the heat exchanger 5 . The air flow FA flows through the heat exchanger 5 in a direction preferably orthogonal to the first plane P1.

The pipes 10, 10a, 10b are for example rectilinear and extend between the header tank 8 and the return tank 9 along a first overall extension axis A1. The header tank 8 extends along a second axis of overall extension A2 and the return tank 9 extends along a third axis of overall extension A3. Preferably, the second axis of overall extension A2 and the third axis of overall extension A3 are parallel to each other and they are orthogonal to the first axis of overall extension A1 .

The bundle tubes 10, 10a, 10b are provided with cooling fins 15 interposed between two consecutive tubes 10, 10a, 10b to facilitate the flow of air FA and the tubes 10, 10, For heat exchange between 10a, 10b, the airflow FA flows in a direction substantially perpendicular to the first plane P1.

The heat exchanger 5 comprises a first opening 16 through which the refrigerant FR enters the heat exchanger 5 . The first opening 16 constitutes an inflow opening allowing the refrigerant FR to enter the first chamber 13 defined in the header tank 8 . The heat exchanger 5 comprises a second opening 17 through which the refrigerant FR is removed from the heat exchanger 5 .

In FIG. 2 , the heat exchanger 5 is a heat exchanger in which the refrigerant FR flows along an I-shaped path. The tubes 10 are arranged parallel to each other and aligned in a first plane P1. The tube 10 extends between a first end 101 in fluid communication with the return tank 9 and a second end 102 in fluid communication with the header tank 8 . In other words, the return tank 9 forms the base of the "I", while the header tank 8 forms the top of the "I". According to this first alternative, the return box 9 is equipped with a second opening 17 .

During use of the refrigerant circuit 1 , the refrigerant FR enters the heat exchanger 5 through the first opening 16 comprised by the header tank 8 . The refrigerant FR is then distributed along the header tank 8 by the means 18 along the second extension axis A2 in order to homogenize the distribution. Next, the refrigerant FR flows between the header tank 8 and the return tank 9 using the pipe 10 . Finally, the refrigerant FR is discharged from the heat exchanger 5 through the second opening 17 of the return tank 9 .

In FIG. 3 , the heat exchanger 5 is a heat exchanger in which the refrigerant FR flows along a U-shaped path. The tubes 10a, 10b are arranged parallel to each other, distributed in two layers 11, 12 comprising a first layer 11 of the first tube 10a and a second layer 12 of the second tube 10b. The first layer 11 and the second layer 12 are formed in respective planes parallel to each other and to the first plane P1.

The first tube 10 a of the first layer 11 extends between a first end 101 in fluid communication with the return tank 9 and a second end 102 in fluid communication with the first chamber 13 . The second tube 10b of the second layer 12 extends between a third end 103 in fluid communication with the return tank 9 and a fourth end 104 in fluid communication with the second chamber 14 also defined within the header tank 8 . The first chamber 13 and the second chamber 14 are adjacent and sealed relative to each other. The first chamber 13 extends along a fourth axis of overall extension A4 and the second chamber 14 extends along a fifth axis of overall extension A5. Preferably, the fourth axis of overall extension A4 and the fifth axis of overall extension A5 are parallel to each other and to the second axis of overall extension A2. The fourth axis of overall extension A4 and the fifth axis of overall extension A5 together define a second plane P2 which is preferably orthogonal to the first plane P1 . In other words, the return tank 9 forms the base of the U, while the first 11 and second 12 layers of tubes 10a, 10b form the branches of the U, and the first 13 and second 14 chambers form the ends of the U. According to this second alternative, the second chamber 14 of the header tank 8 is equipped with a second opening 17 .

During use of the refrigerant circuit 1, the refrigerant FR enters the heat exchanger 5 through the first opening 16 in the first chamber 13, through the means 18 for homogenizing the distribution along the second overall extension axis A2 along the header Box 8 dispensed. Then, the refrigerant FR flows between the first chamber 13 of the header tank 8 and the return tank 9 using the first tube 10 a of the first layer 11 . Then, the refrigerant FR flows between the return tank 9 and the second chamber 14 using the second tube 10 b of the second layer 12 . Finally, the refrigerant FR exits the heat exchanger 5 through the second opening 17 after circulating through the second chamber 14 .

Preferably, the first tubes 10a of the first layer 11 are aligned with the second tubes 10b of the second layer 12 in a third plane P3 perpendicular to the first plane P1 and parallel to the first axis of overall extension A1 .

Regardless of the embodiment variant of the heat exchanger 5 presented above, the header tank 8 houses means 18 for homogenizing the distribution of the refrigerant FR inside the tubes 10 , 10 a , 10 b. This means 18 for homogenizing the distribution is intended to distribute the refrigerant FR in a liquid-gas two-phase state evenly along the header tank 8 and eventually within the collection of tubes 10, 10a, 10b. This distribution homogenization means 18 more particularly seeks to distribute the refrigerant FR evenly within the heat exchanger 5, including when the refrigerant FR is present in the heat exchanger 5 in two different phases, liquid and gas, in variable corresponding proportions Inside time.

In FIG. 4, the distribution homogenizing device 18 comprises, for example, a duct 19 which extends between a first end 20 and a second end 21 of the duct 19 along a sixth overall extension axis A6 which is aligned with the The second axis of overall extension A2 and/or the fourth axis of overall extension A4 are parallel or even coincident.

It should be noted that any element extending along the sixth overall axis of extension A6 defined by the longest dimension of the duct 19 is said to be longitudinal. Any element extending in a transverse plane Pt orthogonal to the axis of overall extension A6 is said to be transverse.

The first end 20 is formed by one end of the duct 19 , while the second end 21 is formed by the other end of the duct 19 , which is longitudinally opposite the first end 20 .

According to an alternative form of embodiment, the first end 20 is intended to be in fluid communication with the first opening 16 of the heat exchanger 5 . According to another alternative form of embodiment, the first opening 16 pipes 19 , the first end 20 of which is placed in fluid communication with the pipe line of the refrigerant circuit 1 . According to both alternatives, the second end 21 is blind and forms a dead end with respect to the circulation of the refrigerant FR within the duct 19 .

The duct 19 is configured, for example, as a cylinder or a parallelepiped or any other shape with an axis of symmetry A7, which is preferably parallel or even coincident with the sixth axis of overall extension A6. The duct 19 comprises a peripheral shell 23 which is cylindrical in cross-section when the duct 19 is shaped as a cylinder or parallelepiped in cross-section when the duct 19 is parallelepiped. The peripheral casing 23 is a peripheral casing that gives the duct 19 an overall shape. In general, the peripheral shell 23 can be formed by a plurality of peripheral surfaces, which may or may not be separated relative to each other and which together form the peripheral shell 23 . In particular, the peripheral shell 23 can consist of a plurality of peripheral surfaces arranged in strips which may or may not be separated relative to each other.

The peripheral shell 23 includes at least one aperture 22 , preferably a plurality of apertures 22 formed through the peripheral shell 23 of the conduit 19 . The apertures 22 are preferably aligned along an alignment axis A8 parallel to the sixth axis of overall extension A6 and/or the axis of symmetry A7.

According to an alternative, the orifices 22 are equidistant from each other. According to another alternative, the orifices 22 are separated from each other by a variable distance. The aperture 22 is, for example, an aperture of circular cross-section, but may be of any shape, in particular rectangular, oval, oblong.

The duct 19 constitutes a shell delimiting an inner space 24 around which the duct 19 is formed. In other words, the duct 19 is adjacent to the inner space 24 surrounded by the duct 19 . Depending on the shape of the duct 19 , the inner space 24 is, for example, cylindrical or parallelepiped or any other shape formed around the axis of symmetry A7 . The peripheral shell 23 of the duct 19 comprises an inner surface 23a adjoining and delimiting the inner space 24, the cross-section of the inner surface 23a is preferably circular.

The duct 19 houses a mixing member 25 extending within the interior space 24 . The mixing member 25 serves to promote mixing between the liquid phase and the gas phase of the refrigerant FR. The mixing member 25 is more particularly designed to direct the refrigerant FR towards the inner surface 23a of the tube 19 so that the refrigerant impinges on the tube, thereby increasing the mixing of the liquid and gas phases of the refrigerant.

It should be noted that the mixing member 25, in particular its mixing pattern 34a, 34b, is designed such that the deflection of the refrigerant alternates, as indicated by the arrows FR in FIG. 5 . The first mixing pattern 34a thus forces the refrigerant towards one peripheral edge 31 of the mixing member which is opposite with respect to the axis of elongation A9 of the mixing member 25 to the peripheral edge 31 defining the second mixing pattern 34b. Consider in a different frame of reference that the refrigerant impinges on a first angular sector of the inner wall 23a of the duct 19 which is on the opposite side of a second angular sector of the inner wall 23a with respect to the axis of elongation A9 of the mixing member 25 . At least one corner sector includes a plurality of apertures 22 .

The mixing member 25 is a member that causes a turbulent flow, particularly a centrifugal flow, of the refrigerant FR toward the inner surface 23 a of the pipe 19 . The mixing member 25 is also designed to avoid any accumulation of refrigerant FR in liquid state in the lower region of the duct 19 when the duct 19 is in the use position. The mixing member 25 is also designed to disrupt the laminar flow of the refrigerant FR inside the pipe 19 to mix the liquid and gas phases of the refrigerant FR. In other words, the mixing member 25 forms at least one baffle, preferably a plurality of baffles, hindering the laminar flow of refrigerant parallel to the sixth axis of overall extension A6 and/or the axis of symmetry A7. In general, the mixing member 25 acts as an obstacle to the laminar flow of the refrigerant FR within the internal space 24 .

Referring also to FIGS. 4 or 5 , the mixing member 25 extends longitudinally along an axis of elongation A9 , for example parallel to the sixth axis of overall extension A6 of the conduit 19 . The mixing member 25 is formed around this axis of elongation A9 which is preferably parallel or even coincident with the axis of symmetry A7 of the duct 19 when the mixing member 25 is located inside the duct 19 .

Seen in cross-section, the mixing member 25 occupies the entire inner cross-section of the duct 19, advantageously the longitudinal portion of the duct 19 including the orifices. Thus, one peripheral edge 31 of the mixing member is in contact with the inner surface 23 a delimiting the duct 19 .

The mixing member 25 extends within the interior space 24, occupying it in whole or in part. In other words, the mixing member 25 can fill the entire volume defined by the duct 19 . In other words, the mixing member 25 has a shape and/or geometry similar to that of the interior space 24 . According to the alternatives described above, the mixing member 25 can be cylindrical or parallelepiped or any other shape formed around the axis of symmetry A7. It will be appreciated that this shape is defined by the protrusion of the peripheral edge 31 of the mixing member 25 . The peripheral edge 31 of the mixing member 25 is formed by at least one surface of the mixing member 25 which is positioned facing the duct 19 . The peripheral edge 31 forms a series of Vs which abut together along the axis of elongation A9 of the mixing member 25 .

The inner surface 23a of the peripheral shell 23 is preferably smooth in order to allow easy insertion of the mixing member 25 into the duct 19, the peripheral edge 31 of the mixing member 25 abutting against the inner surface 23a.

The duct 19 is provided with two end walls 27 , 28 , which are a first end wall 27 equipped with the first end 20 and a second end wall 28 equipped with the second end 21 . The first end wall 27 and the second end wall 28 are for example planar and formed along a transverse plane Pt orthogonal to the sixth axis of overall extension A6 and/or the axis of symmetry A7. The first end wall 27 and the second end wall 28 emanate, for example, from a cover at least partially provided on the header tank 8 .

The first end wall 27 is equipped with at least one window 29 for allowing the refrigerant FR to enter the inner space 24 . In other words, the first end wall 27 of the duct 19 is equipped with a window 29 , for example fluidly connected with the first opening 16 to allow the refrigerant FR to enter the heat exchanger 5 via the duct 19 . In other words, the refrigerant FR enters the heat exchanger 5 via the pipe 19 provided with the orifice 22 from which the refrigerant FR can be discharged to circulate within the header tank of the heat exchanger.

As shown in FIG. 4 , the mixing member 25 includes a first longitudinal end 31 a that can be aligned with the first end wall 27 of the conduit 19 . The mixing member 25 includes a second longitudinal end 31b alignable with the second end wall 28 .

From these measures it follows that the refrigerant FR entering the heat exchanger 5 enters the inner space 24 of the duct 19 via a window 29 formed through the first end wall 27 . The refrigerant FR then diffuses in the internal space 24 and is mixed by the mixing member 25 . This leads in particular to a mixing of the liquid and gas phases of the refrigerant FR, thus being homogenized longitudinally along the duct 19 . The refrigerant FR then flows out of the duct 19 towards the first chamber 13 using the orifice 22 . Then, as described above, the refrigerant FR flows through the tube bundles 10 , 10 a , 10 b until returning to the tank 9 in order to be discharged from the heat exchanger 5 via the second opening 17 .

When the refrigerant FR passes through the pipe 19 thus equipped with the mixing member 25 , the refrigerant FR encounters obstacles which promote mixing between its liquid and gas phases. In addition, such ducts 19 promote homogenization of the distribution of the refrigerant FR within the tubes 10, 10a, 10b.

It should also be noted that the better the two phases of the refrigerant FR, liquid and gas, are mixed by the mixing member 25 in the inner space 24 of the conduit 19, the better and more uniformly this refrigerant FR will be sprayed when passing through the orifice 22, In order to be uniformly supplied to the bundle tubes 10, 10a, 10b afterwards. In other words, firstly, the mixing member 25 allows the longitudinal distribution of the refrigerant FR to be homogeneous along the axis of symmetry A7, after the refrigerant FR has been homogenized in the inner space 24, the injection of the refrigerant FR through the orifice 22 with The second phase takes place, which ensures a better uniform distribution of the refrigerant FR when it leaves the pipe 19 and subsequently inside the heat exchanger 5 .

In Fig. 5, the mixing member 25 comprises a wall 30 continuous between a first longitudinal end 31a and a second longitudinal end 31b. Such a wall 30 , hereinafter referred to as centrifugal wall 30 , is configured to guide the refrigerant in contact with it in a direction radial to the mixing member.

The centrifugal wall 30 is partially or fully twisted between the first longitudinal end 31a and the second longitudinal end 31b. The thickness of the centrifugal wall 30 is preferably constant between the first longitudinal end 31a and the second longitudinal end 31b. The centrifugal wall 30 is arranged, for example, in one layer in twisted form.

When the mixing member 25 is in its use position within the duct 19 , as shown in FIG. 4 , the mixing member 25 preferably extends longitudinally at the center C of the duct 19 along an axis of elongation A9 of the mixing member 25 . The center C of the duct 19 corresponds to its central area, for example cylindrical, in particular similar in shape to the duct 19 .

Continuity of the centrifugal wall 30 between the first longitudinal end 31a and the second longitudinal end 31b of the mixing member 25 means here that the mixing member 25 consists of a plurality of mixing elements 32 butted together. The mixing elements 32 are eg identical to each other and repeat iteratively along the axis of elongation A9. In other words, the mixing elements 32 are eg similar to each other and can be geometrically replaced with each other without changing the configuration of the mixing member 25 . Furthermore, the mixing elements 32 repeat one after another, identical to each other, eg within manufacturing tolerances, so that the mixing member 25 is geometrically constant from the first longitudinal end 31a to the second longitudinal end 31b.

Each mixing element 32 extends longitudinally between a first edge 35 and a second edge 36 . The first edge 35 and the second edge 36 are each formed by a peak 50 of the centrifugal wall 30 aligned with a valley 51 , both of which are substantially normal to the axis of elongation A9. Peak 50 forms a beveled inversion line in which the convex curvature of the twist is reversed. The valleys 51 form beveled inversion lines in which the concave curvature of the twist is reversed. In other words, on either side of peak 50 and valley 51 , centrifugal wall 30 changes meandering direction, from clockwise to counterclockwise or alternatively from counterclockwise to clockwise.

Each mixing element 32 has a first length L1 measured between the first edge 35 and the second edge 36 parallel to the axis of elongation A9. Two consecutive mixing elements 32 can be precisely superimposed on each other after a translational movement one towards the other along the axis of elongation A9 by a distance equal to the first length L1 .

According to this alternative, the first edge 35 and the second edge 36 are parallel to each other and orthogonal to the axis of elongation A9.

For another example, the first edge 35 of a mixing element 32 forms a zero angle with the second edge 36 of an adjacent mixing element 32 because the first edge 35 of one mixing element 32 forms the second edge 36 of an adjacent mixing element 32 or coincide with it.

Each mixing element 32 is formed within manufacturing tolerances by two mixing patterns 34a, 34b that are identical to each other and butted together end to end along the axis of elongation A9. An arrangement in which two mixed patterns 34a, 34b are butted together end to end is understood to be an arrangement in which the two mixed patterns 34a, 34b can be pivoted relative to each other by 180° in a fourth plane P4 containing the axis of elongation A9. Identical constructs stacked on top of each other.

Furthermore, the meandering direction of the first mixed pattern 34 a is opposite to that of the adjacent second mixed pattern 34 b, and these patterns constitute the same mixing element 32 . In other words, if two consecutive mixing patterns 34a, 34b are considered, the centrifugal wall 30 of one rotates in a clockwise direction and the centrifugal wall 30 of the other rotates in a counterclockwise direction. In other words, the curvature of the first mixed pattern 34a is the reciprocal of the curvature of the second mixed pattern 34b. Thus, it should be understood that when viewing the mixing member 25 along the axis of elongation A9, the first mixing pattern 34a twists in a clockwise direction and the next second mixing pattern 34b twists in a counterclockwise direction.

One mixing pattern of the mixing elements 32 shown in FIG. 5 , which may be the first pattern 34 a as well as the first pattern 34 b , is configured as part of a helix that meanders around the axis of elongation A9 . Each mixed pattern 34a, 34b extends longitudinally along the axis of elongation A9 between the first lip 35' and the second lip 36'. The first lip 35' and the second lip 36' are each formed by a peak 50 and a valley 51 of the centrifugal wall 30 in which the curvature of the wall is reversed.

The first lip 35 ′ and the second lip 36 ′ are connected together to ensure the continuity of the centrifugal wall 30 . The first lip 35' of the first mixing pattern 34a forms part of the same mixing element 32 as the second lip 36' of the adjacent second mixing pattern 34b, since the first lip 35' of the first mixing pattern 34a It abuts with the second lip 36' of the adjacent second mixed pattern 34b.

The first lip 35' and the second lip 36' of the same mixed pattern 34 form a lip angle δ between them. The lip angle δ is preferably in the range 0° and 90°, or even in the range 0° and 20°.

The first edge 35 and/or the second edge 36 defining the mixing element 32 and the first lip 35 ′ and/or the second lip 36 ′ defining the mixing pattern 34 a , 34 b are formed by peaks 50 and valleys 51 . In particular, the peaks and valleys each extend in complementary halves of the mixing member and are advantageously aligned. Thus, the peaks 50 extend along straight lines extending radially from the axis of elongation A9, whereas the valleys 51 extend along straight lines extending radially from the axis of elongation A9. These two straight lines can coincide.

In particular, the mixing member 25 is made by obtaining it by molding a polymer material. The mixing member 25 is designed to be obtained by molding without a back draft angle. The mixing member 25 is obtained, for example, using a mold comprising a first mold cavity and a second mold cavity which together form a molding space of the same shape as the mixing member 25 .

The mixing member 25 described above is in particular shaped and organized so as not to include a draft angle. This then makes it easier to demould the mixing component.

The mixing member 25 is a one-piece element that combines the mixing element 32 into a single piece that cannot be disassembled into multiple elements without destroying the mixing member 25 .

These measures allow the refrigerant FR entering the distribution homogenization device 18 to be evenly distributed to all tubes 10, 10a, 10b, even those supplied by the orifice 22 closest to the second end 21 and even beyond the refrigerant FR. A case where two phases, namely a liquid phase and a gaseous phase, exist within the heat exchanger 5 .

Furthermore, the presence of such a mixing member 25 avoids any accumulation of the liquid phase of the refrigerant FR in the lower region of the conduit 19 when the conduit 19 is in the use position.

Claims (15)

1. a kind of hybrid component (25), for being blended in the liquid of the refrigerant (FR) to circulate in the header (8) of heat exchanger (5) Mutually and gas phase, the hybrid component (25) include multiple mixed patterns (34a, 34b), mixed pattern (the 34a, 34b) arrangement At the periphery edge (31) that refrigerant (FR) is guided into hybrid component (25), the mixed pattern (34a, 34b) is along the axis of elongation Line (A9) continuously repeats, and mixed pattern (34a, 34b) is along axis of elongation (A9) in the first lip (35') and the second lip Extend between (36'), wherein the first lip (35') and the second lip (36') of the same mixed pattern (34a, 34b) shape each other At the labial angle (δ) within the scope of 0 ° and 90 °.

2. hybrid component (25) as described in claim 1, wherein at least one of described lip (35', 36') is by peak (50) it is limited with paddy (51), the peak (50) and paddy (51) mix in the plane transverse to axis of elongation (A9) two adjacent It closes and extends between pattern (34a, 34b).

3. described in any item hybrid components (25) as in claims 1 and 2, wherein the wall (30) is from a mixed pattern It is continuous to another mixed pattern.

4. hybrid component (25) as described in any one of the preceding claims, wherein each mixed pattern (34a, 34b) arrangement In a part of spiral.

5. hybrid component (25) according to any one of claims 1 to 4, wherein the first lip of the first mixed pattern (34a) Portion (35') is overlapped with the second lip (36') of the second mixed pattern (34b) close to first mixed pattern (34a).

6. hybrid component (25) as claimed in claim 5, wherein first mixed pattern (34a) and the second mixed pattern (34b) is identical, and head and the tail are positioned opposite one by one along axis of elongation (A9).

7. the hybrid component (25) as described in any one of claim 5 and 6, wherein first mixed pattern (34a) surrounds Axis of elongation (A9) distorts along clockwise direction, and second mixed pattern (34b) surrounds axis of elongation (A9) along counterclockwise Direction distortion.

8. the hybrid component (25) as described in any one of claim 5 to 7, wherein first mixed pattern (34a) and with Adjacent the second mixed pattern (34b) of first mixed pattern (34a) is formed together duplicate mixed along the axis of elongation (A9) It closes element (32).

9. evenly distributedization of refrigerant (FR) distribution in pipe (10,10a, 10b) of the one kind for homogenizing heat exchanger (5) Device (18), it includes being provided at least one window (29) and at least one that (18) are set in the evenly distributed makeup for homogenizing distribution The pipeline (19) of a aperture (22), refrigerant (FR) can enter pipeline (19) by the window (29), and refrigerant (FR) can It is left pipeline (19) by the aperture (22), the pipeline (19) accommodates at least one as described in any one of the preceding claims Hybrid component (25).

10. (18) are set in evenly distributed makeup as claimed in claim 9, wherein the pipeline (19) limits by hybrid component (25) inner section (24) integrally occupied.

11. (18) are set in the evenly distributed makeup as described in any one of claim 9 and 10, wherein the hybrid component (25) It is placed in the middle in the pipeline (19).

12. a kind of header (8), limit the first room (13), first room (13) accommodate at least one as claim 9 to (18) are set in evenly distributed makeup described in any one of 11.

13. a kind of heat exchanger (5) comprising header (8) as claimed in claim 12 and return case (9), a beam tube (10,10a, 10b) are between the header (8) and return between case (9).

14. a kind of method obtained using mold such as hybrid component described in any item of the claim 1 to 8 (25), the mould Tool includes the first die cavity and the second die cavity, and first die cavity and the second die cavity are collectively formed and the hybrid component (25) shape Identical molding space.

15. a kind of purposes of heat exchanger as claimed in claim 13 (5) as evaporator, the evaporator is contained in motor-driven Vehicle equipped with ventilation, heating and/or air-conditioning device (7) shell (6) in.