EP3433560A1 - Échangeur de chaleur et son procédé de fabrication - Google Patents
Échangeur de chaleur et son procédé de fabricationInfo
- Publication number
- EP3433560A1 EP3433560A1 EP17715244.4A EP17715244A EP3433560A1 EP 3433560 A1 EP3433560 A1 EP 3433560A1 EP 17715244 A EP17715244 A EP 17715244A EP 3433560 A1 EP3433560 A1 EP 3433560A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- tubes
- fins
- heat exchanger
- axis
- angle
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000004519 manufacturing process Methods 0.000 title claims abstract description 30
- 238000000034 method Methods 0.000 title claims abstract description 13
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 13
- 239000002826 coolant Substances 0.000 claims description 5
- 238000003825 pressing Methods 0.000 claims 1
- 239000013529 heat transfer fluid Substances 0.000 abstract description 9
- 238000010586 diagram Methods 0.000 description 3
- 240000007817 Olea europaea Species 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000004888 barrier function Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
- 238000010008 shearing Methods 0.000 description 1
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
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/34—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
- F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
Definitions
- the invention relates to a heat exchanger and its method of manufacture. More particularly in the field of mechanical heat exchangers for an application in the automotive field.
- a mechanical heat exchanger 1, illustrated in FIG. 1, comprises:
- Tubes 3 parallel to each other and arranged in at least one row and in which a first coolant is able to circulate, and
- fins 4 evolving parallel to each other and through which a second heat transfer fluid 100 is able to flow, the fins 4 are disposed perpendicular to the plane of the row or rows of tubes 3 and they have orifices 40 in which the tubes 3 are inserted and fixed.
- Fixing the tubes 3 with the fins 4 is said to be mechanical, for example by widening said tubes 3. For this, an olive larger than that of the tubes 3 is inserted into the tubes 3 to enlarge said tubes 3, and then removed. The tubes 3 are then widened and attached to the fins 4.
- this type of mechanical heat exchanger 1 and in particular the connection between the tubes 3 and the fins 4 has a high thermal resistance which penalizes heat exchanges between the first and second heat transfer fluid. Indeed, at the level of orifices 40, there is no continuous contact especially when the fins 4 are hot and dilated. Indeed, when the fins 4 expand, the size of the orifices 40 increases which decreases the contact areas between the tubes 3 and the fins 4.
- An object of the present invention is therefore to at least partially overcome the disadvantages of the prior art and to provide an improved mechanical heat exchanger and its manufacturing process.
- the present invention therefore relates to a mechanical heat exchanger, comprising:
- the angle that the fins form with the perpendicular to the axis of the tubes induces shear stresses between the tubes and the fins.
- the heat exchanger comprises:
- said fins having orifices through which the tubes pass so as to form at least one group of tubes interconnected by the superposition of fins,
- the fins of the same group of tubes have a monotonous profile between two adjacent tubes.
- 20% of the tubes of the same group of tubes have the tangent to the surface of the fins halfway between two adjacent tubes which forms an angle greater than or equal to 0.5 ° and lower or equal to 10 ° with the perpendicular to the axis of the tubes.
- the angle between the tangent to the surface of the fins halfway between two adjacent tubes and the perpendicular to the axis of the tubes makes it possible to reduce the thermal resistance at the orifices, especially when the fins are expanded.
- the angle is greater than or equal to 0.5 ° and less than or equal to 5 °.
- the fins are flat. According to another aspect of the invention, the fins are curved.
- the fins have a sinusoidal profile, the orifices and tubes being placed at the level of ridges and hollows of said fins.
- the heat exchanger comprises a water box disposed at each end of the tubes and covers covering the space not occupied by the fins between the end fins of the same group of tubes. and said water boxes.
- the heat exchanger comprises a single group of tubes or at least two groups of separate tubes. The present invention also relates to a method for manufacturing a mechanical heat exchanger comprising
- said method comprising the following steps:
- the line connecting the ends of tubes of the same rank within the same group of tubes has an angle greater than or equal to 0.5 ° and less than or equal to 10 ° with the perpendicular to the axis of the tubes.
- the line connecting the ends of tubes of the same rank within the same group of tubes has an angle greater than or equal to 0.5 ° and less than or equal to 5 ° with the perpendicular to the axis of the tubes.
- the line connecting the ends of the tubes of the same group of tubes is a straight line.
- the line connecting the ends of the tubes of the same group of tubes is a curve.
- the line connecting the ends of the tubes of the same group of tubes is a sinusoid.
- said manufacturing method comprises, following the step of alignment under stress, a step of setting up water boxes on the ends of the tubes and of placing covers covering the space not occupied by the fins between the fins at the ends of the same group of tubes and said water boxes.
- the present invention also relates to a manufacturing device for implementing the manufacturing method as described above, said device comprising alignment shoes intended to press on the ends of the tubes so that the ends of said tubes pass through. a longitudinal position shifted to an aligned position where the ends of said tubes are aligned with the perpendicular to the axis of the tubes.
- FIG. 2 shows a schematic representation of a mechanical heat exchanger according to the invention
- FIGS. 3 to 6 show schematic representations of a mechanical heat exchanger according to the invention, according to different embodiments,
- FIG. 7 shows a schematic representation of the connection between the fins and the tubes
- FIG. 8 shows a diagram of the evolution of the electrical resistance as a function of the angle between the fins and the tubes
- FIG. 9 shows a flowchart of the various steps of the method of manufacturing a mechanical heat exchanger
- FIGS. 10a to 10c show schematic representations of a mechanical heat exchanger at different stages of its manufacturing process
- Figures 11 and 12 show schematic representations of a mechanical heat exchanger at different stages of its manufacturing process, according to different embodiments.
- an XYZ trihedron to show the angle of view of each of said figures relative to each other.
- the axes of this trihedron can also correspond to the different orientations of the motor vehicle.
- the axis X can thus correspond to the axis of the length of the vehicle, the axis Y to the axis of its width and the axis Z to that of its height.
- a mechanical heat exchanger 1 comprises tubes 3 parallel to each other and arranged in at least one row and in which a first heat transfer fluid is able to circulate.
- the refrigerant may come from a thermal management device such as air conditioning or the cooling circuit of a combustion engine of a motor vehicle.
- These tubes 3 extend in particular in the plane defined by the axes Y and Z.
- the heat exchanger 1 also comprises at least one superposition of fins 4 whose fins 4 evolve parallel to each other, in particular parallel to the plane defined by the axes Y and Z.
- the fins 4 are arranged perpendicularly to the plane of the row or rows of tubes 3.
- a second heat transfer fluid 100 is able to flow between the fins 4, for example air.
- the fins 4 have orifices 40 through which tubes 3 pass so as to form at least one group of tubes 3 interconnected by a superposition of fins 4.
- the heat exchanger 1 comprises:
- the fins 4 form with a perpendicular to the axis of the tubes 3, that is to say with a parallel to the Y axis of the triad XYZ, an angle different from 0 °.
- the tubes 3 are parallel to each other and arranged in at least one row and whose fins 4 evolve without intersecting.
- Said fins 4 comprise the openings 40 through which the tubes 3 pass so as to form at least one group of tubes 3 interconnected by the superposition of fins 4.
- the fins 4 of the same group of tubes 3 have a monotonous profile between two tubes 3 neighbors.
- at least 20% of the tubes 3 of the same group of tubes 3 have the tangent to the surface of the fins 4 midway between two neighboring tubes 3 which forms an angle ⁇ greater than or equal to 0.5 ° and less than or equal to 10 °, preferably less than or equal to 5 °, with the perpendicular to the axis of the tubes 3.
- the heat exchanger 1 may also comprise a water box 5 disposed at each end of the tubes 3. These water boxes 5 allow the collection and / or distribution of the first heat transfer fluid so that it can pass through the tubes 3.
- the fins 4 are flat and the heat exchanger 1 comprises a single group of tubes 3 gathering all the tubes 3 of said heat exchanger 1.
- the all of the tubes 3 has the tangent to the surface of the fins 4 at mid-distance between two adjacent tubes 3 which forms an angle a greater than or equal to 0.5 °, and less than or equal to 10 ° with the perpendicular to the tube axis 3.
- Figure 3 shows a second embodiment where the fins 4 are curved.
- the heat exchanger 1 also comprises a single group of tubes 3 gathering all the tubes 3 of said heat exchanger 1.
- all the tubes 3 do not have the tangent to the surface of the fins 4 halfway between two adjacent tubes 3 which forms an angle ⁇ greater than or equal to 0.5 ° and less than or equal to 10 ° with the perpendicular to the axis of the tubes 3 due to the curved profile of fins 4.
- Figure 4 shows a heat exchanger 1 according to a third embodiment where the fins 4 have a sinusoidal profile.
- the orifices 40 of the fins 4 and the tubes 3 are here placed at the level of the peaks and valleys of the fins 4.
- the heat exchanger 1 also comprises a single group of tubes 3 gathering all the tubes 3 of said heat exchanger 1.
- the set of tubes 3 has the tangent to the surface of the fins 4 halfway between two neighboring tubes 3 which forms a angle a greater than or equal to 0.5 ° and less than or equal to 10 ° with the perpendicular to the axis of the tubes 3.
- FIGS. 5a and 5b show a heat exchanger 1 according to a fourth embodiment where heat exchanger 1 comprises at least two groups of tubes 3.
- the heat exchanger 1 has four groups. of tubes, each group of tubes 3 comprising two tubes 3.
- the tubes 3 are connected to each other by a superposition of fins 4.
- the tubes 3 have the tangent to the fin surface 4 at mid-distance between two adjacent tubes 3 which forms an angle ⁇ greater than or equal to 0.5 ° and less than or equal to 10 ° with the perpendicular to the axis of the tubes 3.
- the fins 4 are planar.
- the fins 4, within each group of tubes 3, have a curved profile or sinusoidal.
- the superpositions of fins 4 of each group of tubes 3 have an identical orientation.
- the superpositions of fins 4 of groups of tubes 3 successively have an inverted orientation, in the image of an inverted reflection in a mirror.
- angles a may differ from one group of tubes 3 to another, while remaining greater than or equal to at 0.5 ° and less than or equal to 10 °.
- the heat exchanger 1 may comprise covers 6 covering the space not occupied by the fins 4 between the end fins 4 of the same group of tubes 3 and said water boxes 5. These covers 6 act as a barrier for the second heat transfer fluid 100 so that it can not pass into this space not busy. The second heat transfer fluid 100 is then forced to circulate between the fins 4, which makes it possible not to deteriorate the heat exchange.
- FIG. 8 shows a diagram of the evolution of the electric resistance in ⁇ , as a function of an angle ⁇ between 0 and 5 ° at the orifices 40 forming the interface between the tubes 3 and the fins 4.
- the resistance electric is easy to measure and proportional to the thermal resistance.
- the diagram of FIG. 8 shows three curves 200, 201 and 202 corresponding to the variations of the electrical resistance for three samples of tubes 3 and fins 4 as a function of angle ⁇ .
- the three curves 200, 201 and 203 show that the greater the angle a increases, especially beyond 0.5 °, the lower the electrical resistance and therefore the thermal resistance.
- an angle ⁇ of 10 ° appears as a saturation limit of the decrease of the electrical resistance and therefore of the thermal resistance. By this it is meant that from this value, an increase in angle ⁇ would have little effect on the thermal resistance. As shown in Figure 8, an angle between 0.5 and 5 ° is optimal.
- the effect of the angle ⁇ on the electrical resistance and therefore on the thermal resistance is related to the shear stresses between the fins 4 and the tubes 3 exerted by the angle ⁇ . These shearing stresses make it possible to maintain good contact between the tubes 3 and the fins 4 at the orifices 40, even if the fins 4 are dilated.
- the present invention also relates to a method of manufacturing a heat exchanger 1 as described above.
- Figure 9 shows a flowchart of the different steps of said manufacturing process.
- the manufacturing process comprises the following steps:
- the tubes 3 of the same group of tubes 3 are arranged parallel to each other with a longitudinal positional offset.
- the imaginary line connecting the ends of the tubes 3 forms with a perpendicular to the axis of the tubes (3), that is to say with a parallel to the Y axis of the XYZ trihedron, an angle other than 0 °.
- the line connecting the ends of the tubes 3 of the same rank within the same group of tubes 3, has an angle a 'greater than 0.5 ° and less than or equal to 10 °, preferably lower or equal to 5 °, with the perpendicular to the axis of the tubes 3.
- the tubes 3 have a diameter smaller than that of the orifices 40 of the fins 4 so that they can be inserted therein.
- This second step 112 may be carried out by expansion of the tubes 3, that is to say by an increase in their diameter which is fixed in the orifices 40.
- This expansion of the tubes 3, can for example be performed by insertion into the tubes 3 of an olive of a diameter greater than that of the tubes 3.
- a third step 114 for stress-aligning the ends of the tubes 3 so that the ends of said tubes 3 are aligned with a perpendicular to the axis of the tubes 3, that is to say with a parallel to the Y axis of the XYZ trihedron.
- the angle a 'between the line connecting the ends of the tubes 3 and the perpendicular to the axis of the tubes 3, because the fins 4 and the tubes 3 are fixed together is reported in the angle ⁇ between the tangent to the surface of the fins 4 at mid-distance between two adjacent tubes 3 and perpendicular to the axis of the tubes 3.
- the connection between the tubes 3 and the fins 4 will then be under shear stresses improving thermal exchanges.
- This third step 114 may for example be achieved by the fact that the manufacturing device for implementing the manufacturing method comprises alignment shoes. These alignment shoes are intended to press on the ends of the tubes 3 so that the ends of said tubes 3 pass from their offset longitudinal position, illustrated in FIG. 10b, to an aligned position where the ends of said tubes 3 are aligned with the perpendicular to the axis of the tubes 3, as shown in Figure 10c.
- the shape of the line connecting the ends of the tubes 3 of the same rank within the same group of tubes 3 made in the first step 110 determines the profile of the fins 4 of the heat exchanger 1. Thus, if this line is a straight line as shown in Figure 10a, the fins 4 will be flat at the end of the manufacturing process. If this line is a curve as shown in Figure 11, the fins 4 will also be curved at the end of the manufacturing process.
- this line is a sinusoid as shown in Figure 12, the fins 4 will have a sinusoidal profile at the end of the manufacturing process.
- the manufacturing method may also include, following the third step of alignment for stress alignment, a fourth step 116 of installation of water boxes 5 on the ends of the tubes 3 and of setting up covers 6 covering the space not occupied by the fins 4 between the fins 4 at the ends of the same group of tubes 3 and said water boxes 5.
Landscapes
- Physics & Mathematics (AREA)
- Engineering & Computer Science (AREA)
- Geometry (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR1652424A FR3049048B1 (fr) | 2016-03-21 | 2016-03-21 | Echangeur de chaleur et son procede de fabrication. |
PCT/FR2017/050629 WO2017162966A1 (fr) | 2016-03-21 | 2017-03-17 | Échangeur de chaleur et son procédé de fabrication |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3433560A1 true EP3433560A1 (fr) | 2019-01-30 |
EP3433560B1 EP3433560B1 (fr) | 2020-04-15 |
Family
ID=56943594
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP17715244.4A Active EP3433560B1 (fr) | 2016-03-21 | 2017-03-17 | Échangeur de chaleur et son procédé de fabrication |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP3433560B1 (fr) |
CN (1) | CN109477700B (fr) |
FR (1) | FR3049048B1 (fr) |
WO (1) | WO2017162966A1 (fr) |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1440217A (en) * | 1920-09-23 | 1922-12-26 | James D Flood | Radiator |
US1837905A (en) * | 1928-01-03 | 1931-12-22 | Hart & Hutchinson Company | Radiator |
GB9616956D0 (en) * | 1996-08-13 | 1996-09-25 | Caradon Ideal Ltd | Heat exchangers |
US6249968B1 (en) * | 1999-08-25 | 2001-06-26 | Visteon Global Technologies, Inc. | Method of making a robust gosper fin heat exchanger |
CN2896189Y (zh) * | 2006-03-17 | 2007-05-02 | 张德地 | 一种列管换热器 |
CN203115975U (zh) * | 2013-03-08 | 2013-08-07 | 河南永兴锅炉集团有限公司 | 铸铁斜片式省煤器 |
CN103591832B (zh) * | 2013-11-22 | 2016-04-20 | 茂名重力石化机械制造有限公司 | 一种斜翅片管换热器 |
-
2016
- 2016-03-21 FR FR1652424A patent/FR3049048B1/fr not_active Expired - Fee Related
-
2017
- 2017-03-17 EP EP17715244.4A patent/EP3433560B1/fr active Active
- 2017-03-17 WO PCT/FR2017/050629 patent/WO2017162966A1/fr active Application Filing
- 2017-03-17 CN CN201780031527.2A patent/CN109477700B/zh not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
EP3433560B1 (fr) | 2020-04-15 |
FR3049048A1 (fr) | 2017-09-22 |
CN109477700A (zh) | 2019-03-15 |
FR3049048B1 (fr) | 2019-04-19 |
CN109477700B (zh) | 2021-05-11 |
WO2017162966A1 (fr) | 2017-09-28 |
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