• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The assembly (1) comprises: - a heat exchanger (7); a bypass duct (13) defining a passage path for the exhaust gases bypassing the heat exchanger (7); a valve (15) regulating quantities of exhaust gas flowing respectively through the heat exchanger (7) and through the bypass duct (13), the valve (15) having a shaft (23) of training. According to the invention, the assembly (1) comprises a fluid box (29), fluidly communicating with the heat transfer fluid circulation side (F) of the heat exchanger, arranged around the drive shaft ( 23) so as to cool said drive shaft (23).
    公开号:FR3063306A1
    申请号:FR1751588
    申请日:2017-02-27
    公开日:2018-08-31
    发明作者:Frederic Greber
    申请人:Faurecia Systemes dEchappement SAS；
    IPC主号:
    专利说明:

    © Publication no .: 3,063,306 (to be used only for reproduction orders)
    ©) National registration number: 17 51588 ® FRENCH REPUBLIC
    NATIONAL INSTITUTE OF INDUSTRIAL PROPERTY
    COURBEVOIE
    ©) Int Cl 8 : F01 N5 / 02 (2017.01), F 02 G 5/02
    A1 PATENT APPLICATION
    ©) Date of filing: 27.02.17. ©) Applicant (s): FAURECIA SYSTEES D'ECHAPPE- (30) Priority: MENT Simplified joint stock company - FR. ©) Inventor (s): GREBER FREDERIC. ©) Date of public availability of the request: 31.08.18 Bulletin 18/35. (56) List of documents cited in the report preliminary research: Refer to end of present booklet @) References to other national documents ©) Holder (s): FAURECIA SYSTEES D'ECHAPPE- related: MENT Simplified joint-stock company. ©) Extension request (s): ©) Agent (s): LAVOIX.
    154 / ASSEMBLY WITH A VALVE WITH COOLED DRIVE SHAFT FOR EXHAUST LINE.
    FR 3 063 306 - A1
    15/2 The set (1) includes:
    - a heat exchanger (7) ,;
    - a bypass duct (13), defining a passage path for the exhaust gases bypassing the heat exchanger (7);
    - a valve (15) regulating quantities of exhaust gas circulating respectively through the heat exchanger (7) and through the bypass duct (13), the valve (15) having a shaft (23) of training.
    According to the invention, the assembly (1) comprises a fluid box (29), communicating fluidically with the side (F) of circulation of the heat transfer fluid of the heat exchanger, arranged around the drive shaft ( 23) so as to cool said drive shaft (23).

    Assembly with a cooled drive shaft valve for exhaust line
    The invention generally relates to exhaust lines equipped with energy recovery system.
    More specifically, the invention relates, according to a first aspect, to an assembly for an exhaust line, of the type comprising:
    - A heat exchanger, having an exhaust gas circulation side having an exchanger inlet connected to the exhaust gas inlet and an exchanger outlet connected to the exhaust gas outlet, the heat exchanger further having a side for circulation of a heat transfer fluid having a heat transfer fluid inlet and a heat transfer fluid outlet;
    - a bypass duct, defining a passage path for the exhaust gases from the exhaust gas inlet to the exhaust gas outlet by bypassing the heat exchanger;
    a valve regulating the quantities of exhaust gas circulating respectively through the heat exchanger and through the bypass duct, the valve having a valve body internally traversed by the exhaust gases, a flap disposed at the inside the valve body and movable relative to the valve body, and a shutter drive shaft.
    Such an assembly is known for example from FR 2 966 873. In such an assembly, the drive shaft is brought to high temperature by the exhaust gases circulating in the bypass duct. For a gas temperature of 850 ° C, the temperature of the drive shaft at the end connected to the actuator reaches 550 to 600 ° C. The shaft guide bearing, the actuator and the kinematic chain coupling the actuator to the drive shaft must therefore withstand extremely high temperatures.
    This first of all means that the materials used for the bearing and the elements of the kinematic chain are chosen for their resistance to temperature, but have other defects. It is particularly difficult to eliminate the noises produced during the rotation of the flap. In addition, at high temperatures, significant clearance is created due to the expansion of the axis relative to the bearing. Gas also leaks along the shaft to the outside of the exhaust line.
    It is common to use an electric motor to drive the shutter. Such actuators typically include a plastic housing, as well as plastic gears. Thus, the engine and its electronics do not withstand temperatures above 120 or 140 ° C, depending on the case.
    As a result, it is generally necessary to move the actuator output shaft away from the drive shaft, so as to limit direct thermal conduction. It is also common to add heat shields between the actuator and the valve.
    In addition, the actuator is generally fixed to very hot parts of the assembly, by means of legs. These legs conduct heat to the actuator. To remedy this problem, it is possible to move the actuator away. However, this makes the assembly less compact and sensitive to vibrations.
    In this context, the invention aims to propose a set in which the problems mentioned below are eliminated or mitigated.
    To this end, the invention relates to an assembly for an exhaust line of the aforementioned type, characterized in that the assembly comprises a fluid box, communicating fluidically with the side of circulation of the heat transfer fluid, arranged around the shaft drive so as to cool said drive shaft.
    Thus, in the invention, the heat transfer fluid circulating in the heat exchanger is used to cool the drive shaft. This heat transfer fluid can be easily diverted to the fluid box, since the valve is located immediately near the heat exchanger.
    The maximum temperature of the heat transfer fluid is around 120 ° C. It is therefore significantly lower than the temperature of the drive shaft and can cool it very effectively. This keeps the actuator at an adequate temperature. This also makes it possible to maintain the kinematic chain and the guide bearing of the drive shaft at temperatures much lower than the temperatures known in the prior art. As a result, it is possible to use less expensive or more efficient materials, in particular more leaktight towards exhaust gases to limit leaks to the outside. This also reduces friction between the drive shaft and the bearing, and also makes the bearing more durable.
    The kinematic chain connecting the actuator to the drive shaft can be simplified, and above all the actuator can be brought closer to the drive shaft.
    This makes the whole more compact, and less sensitive to vibrations.
    The set may also have one or more of the characteristics below, considered individually or in all technically possible combinations:
    - the fluid box has at least first and second orifices, the first orifice being fluidly connected to one of the heat transfer fluid inlet or the heat transfer fluid outlet, the second orifice being intended to be connected to a circuit heat recovery;
    the fluid box has a third orifice communicating with the other of the heat transfer fluid inlet or the heat transfer fluid outlet, and has a fourth orifice communicating fluidly with the third orifice through the fluid box, the fourth orifice being designed to be connected to the heat recovery circuit;
    - The valve comprises at least one bearing for guiding the drive shaft, arranged in the fluid box;
    - the fluid box internally defines a circulation passage between the first orifice and the second orifice, forming a restriction at the level of the guide bearing;
    - The fluid box comprises a lower half-shell and an upper half-shell sealingly attached to the lower half-shell, preferably removably;
    - the lower half-shell is rigidly fixed to the guide bearing and to the heat exchanger;
    - The assembly includes an actuator and a kinematic chain by which the actuator drives the shutter drive shaft, the actuator being fixed to the fluid box, outside the fluid box;
    - The drive shaft protrudes out of the fluid box, the assembly comprising a skirt sealingly connecting the actuator to the fluid box around the drive shaft;
    - The actuator is an electric motor comprising an output shaft, the kinematic chain comprising a reduction gear coupling in rotation the output shaft and the drive shaft;
    - The reduction gear is arranged in a cavity delimited between the fluid box and a cover fixed in a sealed manner to the fluid box;
    - the cover has an opening through which the reduction gear is connected to the output shaft, the actuator being tightly connected to the cover around the opening;
    - The assembly comprises an actuator and a kinematic chain by which the actuator drives the shutter drive shaft, the actuator being placed inside the fluid box;
    - a seal is interposed between the drive shaft and the guide bearing;
    - The guide bearing has fins in contact with the heat transfer fluid;
    - the drive shaft is hollow.
    According to a second aspect, the invention relates to an exhaust line comprising an assembly having the characteristics below:
    Other characteristics and advantages of the invention will emerge from the detailed description which is given below, for information and in no way limitative, with reference to the appended figures among which:
    - Figure 1 is a simplified schematic representation of an exhaust line fitted with an assembly according to the invention;
    - Figure 2 is a perspective view of an assembly according to a first embodiment of the invention;
    - Figure 3 is a sectional view of the assembly of Figure 2, taken in a plane passing through the drive shaft;
    - Figure 4 is a view similar to that of Figure 2, some elements of the assembly having been removed to reveal the lower half-shell of the fluid box;
    - Figure 5 is a perspective view similar to Figure 4, part of the upper half-shell being shown;
    - Figure 6 is an exploded view of the assembly of Figure 7;
    - Figure 7 is a perspective view of the actuator of Figure 6, showing the skirt and the seal;
    - Figure 8 is a perspective view of a variant of the first embodiment of the invention;
    - Figures 9 and 10 are perspective views of the assembly of Figure 8, some elements having been removed to reveal the internal components of this assembly;
    - Figures 11 and 12 are perspective views of two variants of a second embodiment of the invention, the upper half-shell of the fluid box not being shown to reveal the components housed in the inside the fluid box; and
    - Figure 13 is a simplified schematic representation of an alternative embodiment of the invention.
    The assembly 1 is intended to be integrated into an exhaust line 2 of a vehicle, in particular of a motor vehicle such as a car or a truck, as shown in FIG. 1.
    The assembly 1 has at least one exhaust gas inlet 3 and an exhaust gas outlet 5.
    The exhaust gas inlet 3 is fluidly connected to a manifold C, collecting the exhaust gases leaving the combustion chambers of the vehicle engine M. Typically, other equipment such as a turbo-compressor and one or more pollution control devices are interposed between the manifold C and the exhaust gas inlet 3.
    The exhaust gas outlet 5 communicates fluidically with a cannula A through which the cleaned exhaust gases are released into the atmosphere. Typically, other equipment such as one or more silencers and one or more pollution control devices are interposed between the cannula A and the exhaust gas outlet 5.
    Furthermore, the assembly 1 comprises a heat exchanger 7, having a side G for circulation of the exhaust gases and a side F for circulation of a heat transfer fluid (FIG. 1).
    The exhaust gases and the heat transfer fluid are in thermal contact with each other in the heat exchanger 7, the exhaust gases yielding part of their heat energy to the heat transfer fluid.
    The heat exchanger 7 is more clearly visible in FIGS. 4 and 5. It is of any suitable type: with tubes, plates, etc.
    The heat transfer fluid is of any suitable type. For example, the heat transfer fluid is water, possibly containing additives such as antifreeze products, in particular antifreeze products typically comprising glycol.
    The side G of the exhaust gas circulation has an exchanger inlet EG connected to the exhaust gas inlet 3 and an exchanger outlet SG connected to the exhaust gas outlet 5 (FIG. 1).
    The side F for circulation of the heat transfer fluid has a heat transfer fluid inlet 9 and a heat transfer fluid outlet 11 (FIGS. 1, 4 and 5). The alternative circulation is in the opposite direction.
    The assembly 1 also includes a bypass duct 13, defining a passage path for the exhaust gases from the exhaust gas inlet 3 to the exhaust gas outlet 5 by bypassing the heat exchanger. heat 7. By this is meant that the exhaust gases passing through the bypass duct 13 flow directly from the inlet 3 to the outlet 5 without passing through the heat exchanger 7.
    The assembly 1 also includes a valve 15 regulating the quantities of exhaust gas circulating respectively through the heat exchanger 7 and through the bypass duct 13 (Figures 1,2, 4 and 5).
    In the example shown, the valve 15 is placed at the outlet 5 of the exhaust gas.
    In this case, the assembly 1 typically includes a cone 17 fluidly connecting the exhaust gas inlet 3 to the exchanger inlet EG and to an upstream end of the bypass duct 13.
    Furthermore, the valve 15 comprises a valve body 19 internally traversed by the exhaust gases, a flap 21 disposed inside the valve body 19 and movable relative to the valve body 19, and a shaft 23 of flap drive 21.
    The valve body 19 fluidly connects the exhaust gas outlet 5 to the exchanger outlet SG and also to the downstream end of the bypass duct 13.
    As a variant, the valve 15 is placed at the level of the inlet 3.
    In this alternative embodiment, the positions of the cone 17 and of the valve body 19 are reversed.
    The assembly 1 also typically includes an actuator 25 and a kinematic chain 27 by which the actuator 25 drives the drive shaft 23 (Figures 2 and 3).
    The shutter 21 typically moves in rotation relative to the valve body 19.
    The valve 15 is for example a regulating valve. In this case, the flap 21 can be placed at a plurality of positions relative to the valve body 19. This makes it possible to vary the passage sections offered to the exhaust gas circulating respectively from the exchanger outlet SG to the exhaust gas outlet 5 and from the downstream end of the bypass duct 13 to the exhaust gas outlet 5.
    Alternatively, the valve 15 is an all or nothing valve. In this case, the flap 21 is capable of adopting either a heat exchange position in which the flap 21 prevents the circulation of exhaust gas in the bypass duct 13, or a bypass position in which the flap 21 prevents the circulation of exhaust gases in the heat exchanger 7.
    It should be noted that advantageously the drive shaft 23 is not located in the main flow of exhaust gases. It is arranged along a wall of the valve body 19, between the heat exchanger 7 and the bypass duct 13. Likewise, the flap is of the "door" type and not of the "butterfly" type. It is fixed by an edge on the drive shaft. In the bypass position, it is not in the main exhaust flow. The thermal transfers of the exhaust gases to the drive shaft 23 are thus limited.
    Advantageously, the assembly 1 comprises a fluid box 29, communicating fluidically with the side F of circulation of the heat transfer fluid, arranged around the drive shaft 23 so as to cool said drive shaft 23 (Figures 2 to 5 ). By fluid box is meant here a hollow volume, internally delimiting a passage traversed by the heat transfer fluid. The drive shaft 23 is in thermal contact with the heat transfer fluid passing through the fluid box, which makes it possible to cool this shaft.
    As can be seen in particular in FIG. 5, the fluid box 29 has first and second orifices 31.33.
    In a first alternative embodiment, the first orifice 31 is fluidly connected to the heat transfer fluid outlet 11. In this case, the second orifice 33 is designed to be connected to a heat recovery circuit not shown. The assembly 1 then typically comprises an inlet duct 35 fixed to the heat exchanger and communicating with the heat transfer fluid inlet 9 (FIG. 2). It also includes an outlet duct 37, fixed to the orifice 33 (Figure 2).
    The heat recovery circuit is intended to recover part of the heat energy from the exhaust gases and transfer it to another circuit or another component of the vehicle. For example, it transfers this heat energy to the heating circuit of the passenger compartment, or to the engine cooling fluid, etc.
    The heat transfer fluid circulates in a loop in the heat recovery circuit.
    Alternatively, the first port 31 is fluidly connected to the inlet 9 of the heat transfer fluid. In this case, the inlet duct 35 is connected to the second orifice 33, and the outlet duct 37 is fluidly connected to the outlet of heat transfer fluid 11.
    The valve 15 includes a bearing 39 for guiding the drive shaft 23 (Figures 3 and 4). Typically, this bearing 39 is rigidly fixed to the valve body 19, outside of it.
    Advantageously, the guide bearing 39 is arranged in the fluid box 29. Thus, the guide bearing 39 is in direct contact with the heat transfer fluid circulating inside the fluid box. The drive shaft 23 is engaged in the bearing 39. It is not in direct contact with the heat transfer fluid circulating in the fluid box 29. It is cooled by conduction through the bearing 39 (Figure 3).
    The fluid box 29 internally delimits a circulation passage 41 between the first orifice 31 and the second orifice 33, forming a restriction 43 at the level of the guide bearing 39 (FIG. 4). Thus, the heat transfer fluid is forced to circulate around the bearing 39. The passage section offered to the heat transfer fluid along the circulation passage 41 is smaller at the restriction 43 than in the rest of the passage 41.
    This also contributes to increasing the speed of circulation of the fluid in contact with the guide bearing 39, and therefore to improving the cooling of this bearing.
    Because the guide bearing 39 is kept at a moderate temperature, it is possible to use high-performance materials to make it.
    For example, the guide bearing 39 includes a metal support 45 and a ring 47 of metallic knit impregnated with graphite (FIG. 3).
    The support 45 has a cylindrical side wall 49 closed at one end by a bottom 51. The ring 47 is placed inside the cylindrical wall 49. The bottom 51 is sealed in an orifice 52 in the valve body 19 It has a central hole 53. The drive shaft 23 passes successively through the central hole 53 and inside the ring 47.
    The fluid box 29 advantageously comprises a lower half-shell 55 and an upper half-shell 57 attached in leaktight manner to the lower half-shell 55 (FIGS. 3 to 5).
    The lower and upper half-shells 55, 57 are, for example, tightly welded with each other. More specifically, the respective peripheral edges of the lower and upper half-shells 55, 57 are welded to each other in a sealed manner.
    Alternatively, the upper and lower half-shells 55, 57 are removably attached to each other. This opens the fluid box to exchange a part. Preferably, a seal is then interposed between the lower and upper half-shells. The upper half-shell can advantageously be made of a plastic material.
    The lower half-shell 55 is typically made of a metallic material.
    The lower half-shell 55 has for example the shape of a concave cup. It typically came from stamping.
    This makes it possible to conveniently produce reliefs such as the rib 59 delimiting the restriction 43 (FIG. 4).
    The lower half-shell 55 is rigidly fixed to the guide bearing 39 and to the heat exchanger 7.
    More specifically, it has a hole in which the bearing 39 is engaged with a tight fit, typically less than 0.1 mm in radius. The lower half-shell 55 is typically welded to the bearing 39, more precisely to the support 45.
    The first orifice 31 is advantageously formed in the lower half-shell 55. It is placed in coincidence with the outlet 11, or the inlet 9 if necessary. The lower half-shell 55 is welded tight to the outer casing of the heat exchanger 7, around the outlet 11 or the inlet 9.
    The upper half-shell 57 closes the fluid box 29.
    Typically, the second orifice 33 is formed in the lower half-shell 55. As a variant, the second orifice 33 is formed in the upper half-shell 57.
    According to a first embodiment, the actuator 25 is fixed to the fluid box 29, outside the fluid box 29.
    Typically, the actuator 25 is fixed only to the fluid box 29.
    The actuator 25 is fixed to the upper half-shell 57, for example by means of screws 61 welded to the half-shell 57, visible in FIGS. 2 and 6.
    Thus, the actuator 25 is fixed to a member cooled by the circulation of the heat transfer fluid. It can be fixed without interposing a heat shield, and close to the valve body. It is not necessary to move it away from the valve body, to limit heat transfer by conduction along the fasteners.
    The upper half-shell 57 has an opening 63, in which an upper end of the guide bearing 39 is engaged. The edge of the opening 63 is sealed on the bearing 39.
    One end 65 of the drive shaft 23 exits from the guide bearing 39 and projects outside the fluid box 29. The end 65 is connected to the actuator 25 by the kinematic chain 27.
    The actuator 25 and the kinematic chain 27 are of any suitable type.
    For example, the actuator 25 is an electric motor, provided with a rotary output shaft 67 (see FIG. 2). Alternatively, the actuator 25 is a wax actuator, or a shape memory spring.
    The kinematic chain 27 is of any suitable type. In the example shown, the kinematic chain comprises an Oldham seal, making it possible to transmit a torque from the output shaft 67 to the drive shaft 23 while thermally decoupling the two shafts from one another.
    Such a seal is described for example in patent application WO 2010/103249.
    According to an advantageous aspect of the invention, the assembly 1 comprises a skirt 69, sealingly connecting the actuator 25 to the fluid box 29 around the drive shaft 23 (Figures 2, 6 and 7).
    Such a skirt has two functions.
    First of all, it protects the kinematic chain 27 and the drive shaft 23 from external aggressions, for example dust, sand, gravel and all the materials which can be thrown during the running of the vehicle.
    The skirt 69 also makes it possible to avoid leakage of exhaust gases to the outside. Indeed, the exhaust gases possibly rising along the drive shaft 23, between the shaft 23 and the bearing 39, are confined in the space delimited by the skirt 69 between the actuator 25 and the box fluid 29.
    For example, the actuator 25 has an outer casing 71, the skirt 69 being integral with the casing 71. Typically, it came integrally with the casing 71.
    As can be seen in particular in FIGS. 6 and 7, the skirt 69 has a free edge with a closed contour 73 carrying a seal 75 also with a closed contour. The seal 75 is pinched between the free edge 73 and the fluid box 29, more precisely between the free edge 73 and the upper half-shell 57.
    Advantageously, the skirt 69 carries ears 77 cooperating with the screws 61 to fix the actuator 25 to the fluid box 29.
    The skirt 69 internally delimits a volume in which the kinematic chain 27 is housed.
    According to an advantageous alternative embodiment, the kinematic chain 27 comprises a reduction gear 79 coupling in rotation the output shaft 67 to the drive shaft 23. Such an alternative embodiment is illustrated in FIGS. 8 to 10.
    The reduction gear 79 typically comprises a pinion 81 fixed to the output shaft 67, and a toothed wheel 83 fixed to the drive shaft 23. The toothed wheel 83 directly meshes with the pinion 81, or as a variant is rotated by the pinion 81 by means of one or more other toothed wheels.
    The use of such a reducer 79 is made possible because of the low temperature to which the kinematic chain is exposed. At high temperatures, it is not possible to use a gear reducer and toothed wheel without risk of degradation due to temperature.
    Advantageously, the reduction gear 79 is disposed in a cavity 85 delimited between the fluid box 29 and a cover 87 fixed in leaktight manner to the fluid box 29.
    For example, the upper half-shell 57 has a hollow area 89 in which the reduction gear 79 is placed. The cover 87 is a stamped, concave part, closing the hollow area 89. In this case, the upper half-shell 57 is metallic, as is the cover 87. The cover 87 is then welded sealed by its peripheral edge to the upper half-shell 57.
    The cover 87 advantageously has an opening 91 through which the reduction gear 79 is connected to the output shaft 67 of the actuator (FIG. 10). The actuator is tightly connected to the cover 87 around the opening 91 (Figures 8 and 10). Typically, the outer casing 71 of the actuator carries a seal with a closed contour, surrounding the output shaft 67. The seal 93 is pinched between the outer casing 71 and the cover 87, and is placed around opening 91.
    It should be noted that in this case the cover 87 plays the same role as the skirt 69. It protects the kinematic chain from external aggressions, and prevents the escape of exhaust gas towards the outside of the assembly 1.
    The operation of assembly 1 will now be described.
    The actuator 25 drives the drive shaft 23 in rotation via the kinematic chain 27. This makes it possible to move the flap 21 relative to the valve body 19, and to adjust the quantities of circulating exhaust gas through the heat exchanger 7 and through the bypass duct 13.
    The heat transfer fluid circulates permanently inside the heat exchanger 7. Before entering the heat exchanger, or after leaving the heat exchanger, it passes through the fluid box 29. The shape of the passage circulation 41 forces the heat transfer fluid to circulate around the guide bearing 39.
    The exhaust gases circulating in the assembly 1 transfer part of their heat energy to the drive shaft 23. This heat energy rises by conduction along the drive shaft 23 and through the guide bearing 39. It is evacuated by the heat transfer fluid circulating inside the fluid box 29.
    Because the valve is of the door type, the flap clears and is not in full flow in the bypass position. The drive shaft is not in full flow either. Furthermore, the mass of the drive shaft is very limited, for example of the order of 7 grams.
    These different elements help to limit the amount of heat given off by exhaust gases to the drive shaft.
    In addition, the exchange density between the gas and the flap or the drive shaft is significantly lower than the exchange density between the heat transfer fluid and the bearing. The exchange density for the heat transfer fluid is 2000 W / m 2 . ° K against 400 W / rrf. ° K for exhaust gases.
    Furthermore, the thermal conductivity of the material constituting the guide bearing is much higher than the thermal conductivity of the drive shaft (40 W / m. ° K against 20 W / m. ° K).
    These various factors contribute to limiting the temperature of the drive shaft, which can be kept below 300 ° C., and typically of the order of 200 ° C.
    A second embodiment of the invention will now be described. Only the points by which this second embodiment differs from the first will be detailed below. Identical elements or ensuring the same function will be designated by the same references.
    In the second embodiment, the actuator 25 is placed inside the fluid box 29.
    The guide bearing 39 and the kinematic chain 27 are also placed inside the fluid box 29.
    The actuator 25 is of any suitable type.
    According to an alternative embodiment, the actuator 25 comprises a shape memory spring 95 (FIG. 11).
    Such a shape memory spring is described for example in patent application FR 1660130.
    Typically, such an actuator comprises a rod 97 on which is threaded a ring 99 free to slide along the rod. The shape memory spring 95 is a helical spring, which has a first end fixed to the rod 97 and a second end fixed to the ring 99.
    Below a predetermined temperature, the shape memory spring 95 is rigid. Beyond the predetermined temperature, the shape memory spring 95 becomes elastic, its length varying according to the temperature.
    The kinematic chain 27 comprises a lever 103, having a first end 105 rigidly fixed to the transmission shaft 23, and a second end 105 linked to the ring 99 by a pivoting connection. The movement of the ring 99 along the rod 97 under the effect of temperature variations causes the lever 103 to rotate relative to the valve body 19.
    Advantageously, a seal 107 is interposed between the drive shaft 23 and the guide bearing 39. This seal makes it possible to separate the exhaust gases from the heat transfer fluid. In particular, it makes it possible to prevent the exhaust gases from going up along the drive shaft 23 and from penetrating inside the fluid box 29.
    The seal 107 is a seal with a closed contour, for example an O-ring. It is in an elastic material such as rubber, EPDM, silicone or any other suitable material.
    In order to guarantee that the temperature of the seal remains below its maximum operating temperature, the guide bearing 39 has fins 109 in contact with the heat transfer fluid.
    The bearing 39 preferably comprises a cylindrical central part 111, one lower end of which is engaged in the orifice 52 of the valve body. This end is sealed to the valve body. The drive shaft 23 is engaged inside the cylindrical central part 111.
    The seal 107 is placed in a groove formed at the periphery of the drive shaft 23, and bears against a radially internal surface of the central cylindrical part 111. The fins 109 are formed on the radially external surface of the central cylindrical part 111.
    The height of the bearing 39, the dimensions of the fins 109, and the number of fins 109, are chosen as a function of the quantity of heat transferred by the exhaust gases to the drive shaft 23, this quantity having to be transferred with heat transfer fluid.
    Furthermore, in order to reduce the amount of heat transferred by conduction, the drive shaft 23 is hollow. It has a hollow cylindrical central part 113, closed at its two opposite ends by solid parts 115. The groove for receiving the seal 107 is hollowed out in one of the end parts 115.
    In FIG. 11, the bypass duct 13 and the heat exchanger 7 have shapes different from those of the duct 13 and the heat exchanger 7 of FIGS. 2 to
    10. Alternatively, they have the same shapes.
    According to a variant of the second embodiment, the actuator 25 is a wax actuator (Figure 12).
    Such an actuator is known and will not be described here in detail.
    This actuator 25 comprises a wax cartridge, not visible. The volume of the wax changes depending on the temperature. The actuator 25 also includes a lever 121, moved longitudinally under the effect of variations in the volume of the wax. The lever 121 is connected by a link 123 to the end of the drive shaft 23.
    A return spring 125 recalls the lever 121 in a longitudinal direction, towards a rest position.
    The drive shaft 23 and the guide bearing 39 are as described above with reference to FIG. 11.
    In this alternative embodiment, the lower and upper half-shells 55, 57 are advantageously fixed to each other in a removable manner, to allow replacement or maintenance of the actuator 25.
    They are for example fixed to each other by bolts, with the interposition of a gasket 127.
    The upper half-shell is preferably made of a plastic material.
    According to an alternative embodiment shown diagrammatically in FIG. 13, the fluid box 29 has third and fourth orifices 151, 153. If the first orifice 31 communicates with the heat transfer fluid outlet 11, then the third orifice 151 is in fluid communication with the heat transfer fluid inlet 9.
    The fourth orifice 153 communicates fluidly with the third orifice 151 through the fluid box 29. The fourth orifice 153 is then connected to the heat recovery circuit, by the inlet duct 35.
    Conversely, if the first orifice 31 communicates with the heat transfer fluid inlet 9, then the third orifice 151 communicates with the heat transfer fluid outlet 11. The fourth orifice 153 is connected to the heat recovery circuit by the outlet duct 37.
    The fluid box 29 is therefore designed to internally delimit two circulation passages, a circulation passage between the first and second orifices 31, 33, and another circulation passage between the third and fourth orifices 151, 153.
    This embodiment is particularly advantageous when the heat exchanger 7 is small. In this case, the fluid box 29 will cover practically the entire surface of the heat exchanger 7. The tubes 35 and 37 are no longer welded directly to the heat exchanger 7 but to the fluid box 29, which is much more accessible.
    It should be noted that the drive shaft 23 could not be cooled by the heat transfer fluid through the guide bearing, but be directly in contact with the heat transfer fluid.
    The invention has multiple advantages.
    It completely protects the kinematic chain 27 and the drive shaft 23 against external aggressions. It also makes it possible to seal the valve 15, and to prevent leakage of exhaust gases to the outside, thus preventing oxygen from the air from entering the exhaust channel, which could be harmful to the operation of certain pollution control devices.
    The invention makes it possible to protect the bearing 39 from heat, and therefore to use materials with lower cost or more efficient materials for the constitution of this guide bearing.
    It also makes it possible to protect the kinematic chain 27 from heat.
    The invention also makes it possible to construct all of the dimension chains from the position of the guide bearing and of the drive shaft. This avoids having complex constructions in order to respect the dimension chains.
    The invention further simplifies the welding of the inlet and / or outlet ducts on the exchanger, since the outlet tube and / or the inlet tube are offset at the level of the fluid box.
    The invention makes it possible to protect the electronic components and the motor from heat, in the case where the actuator is an electric motor.
    The overall size of the assembly is reduced.
    权利要求:
    Claims (16)
    [1" id="c-fr-0001]
    1, - Exhaust line assembly, the assembly (1) having at least one exhaust gas inlet (3) and one exhaust gas outlet (5), the assembly (1) comprising:
    - a heat exchanger (7), having an exhaust gas circulation side (G) having an exchanger inlet (EG) connected to the exhaust gas inlet (3) and an outlet (SG) heat exchanger connected to the outlet (5) of exhaust gas, the heat exchanger (7) further having a side (F) for circulation of a heat transfer fluid having a heat transfer fluid inlet (9) and a heat transfer fluid outlet (11);
    - a bypass duct (13), defining a passage path for the exhaust gases from the inlet (3) of exhaust gas to the outlet (5) of exhaust gas by bypassing the heat exchanger (7);
    - a valve (15) regulating quantities of exhaust gas flowing respectively through the heat exchanger (7) and through the bypass duct (13), the valve (15) having a valve body (19) internally traversed by the exhaust gases, a flap (21) disposed inside the valve body (19) and movable relative to the valve body (19), and a shaft (23) for driving the flap ( 21);
    characterized in that the assembly (1) comprises a fluid box (29), communicating fluidically with the side (F) of circulation of the heat transfer fluid, arranged around the drive shaft (23) so as to cool said drive shaft (23).
    [2" id="c-fr-0002]
    2, - assembly according to claim 1, characterized in that the fluid box (29) has at least first and second orifices (31, 33), the first orifice (31) being fluidly connected to one of the heat transfer fluid inlet (9) or heat transfer fluid outlet (11), the second orifice (33) being adapted to be connected to a heat recovery circuit.
    [3" id="c-fr-0003]
    3, - An assembly according to claim 2, characterized in that the fluid box (29) has a third orifice (151) communicating with the other of the heat transfer fluid inlet (9) or the heat transfer fluid outlet ( 11), and has a fourth orifice (153) communicating fluidically with the third orifice through the fluid box (29), the fourth orifice (153) being provided to be connected to the heat recovery circuit.
    [4" id="c-fr-0004]
    4, - Assembly according to any one of the preceding claims, characterized in that the valve (15) comprises at least one bearing (39) for guiding the drive shaft (23), disposed in the fluid box ( 29).
    [5" id="c-fr-0005]
    5. - assembly according to claim 4, characterized in that the fluid box (29) internally delimits a circulation passage (41) between the first orifice (31) and the second orifice (33), forming a restriction (43) at the guide bearing (39).
    [6" id="c-fr-0006]
    6. - Assembly according to any one of the preceding claims, characterized in that the fluid box (29) comprises a lower half-shell (55) and an upper half-shell (57) attached in leaktight manner to the lower half-shell (55), preferably removably.
    [7" id="c-fr-0007]
    7. - An assembly according to claim 6 combined with claim 4, characterized in that the lower half-shell (55) is rigidly fixed to the guide bearing (39) and to the heat exchanger (7).
    [8" id="c-fr-0008]
    8. - Assembly according to any one of the preceding claims, characterized in that the assembly (1) comprises an actuator (25) and a kinematic chain (27) by which the actuator (25) drives the shaft drive (23) of the flap (21), the actuator (25) being fixed to the fluid box (29), outside the fluid box (29).
    [9" id="c-fr-0009]
    9. - assembly according to claim 8, characterized in that the drive shaft (23) protrudes from the fluid box (29), the assembly (1) comprising a skirt (69) sealingly connecting the actuator (25) to the fluid box (29) around the drive shaft (23).
    [10" id="c-fr-0010]
    10. - An assembly according to claim 8 or 9, characterized in that the actuator (25) is an electric motor comprising an output shaft (67), the kinematic chain (27) comprising a reduction gear (79) coupling in rotation l 'output shaft (67) and the drive shaft (23).
    [11" id="c-fr-0011]
    11. - assembly according to claim 10, characterized in that the reduction gear (79) is disposed in a cavity (85) delimited between the fluid box (29) and a cover (87) fixed in leaktight manner to the fluid box (29).
    [12" id="c-fr-0012]
    12. - An assembly according to claim 11, characterized in that the cover (87) has an opening (91) through which the reduction gear (79) is connected to the output shaft (67), the actuator (25) being tightly connected to the cover (87) around the opening (91).
    [13" id="c-fr-0013]
    13. - assembly according to any one of claims 1 to 7, characterized in that the assembly (1) comprises an actuator (25) and a kinematic chain (27) by which the actuator (25) drives the shaft drive (23) of the flap (21), the actuator (25) being placed inside the fluid box (29).
    [14" id="c-fr-0014]
    14. - Assembly according to claim 13 combined with claim 4, characterized in that a seal (107) is interposed between the drive shaft (23) and the guide bearing (39).
    [15" id="c-fr-0015]
    15. - Assembly according to claim 14, characterized in that the guide bearing (39) has fins (109) in contact with the heat transfer fluid.
    [16" id="c-fr-0016]
    16. - Assembly according to any one of claims 13 to 15, characterized in that the drive shaft (23) is hollow.
    1/8
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    同族专利:
    公开号 | 公开日
    US20190120111A1|2019-04-25|
    JP6825117B2|2021-02-03|
    FR3063306B1|2019-04-12|
    KR20180099515A|2018-09-05|
    CN108518264A|2018-09-11|
    KR102201907B1|2021-01-11|
    JP2020506328A|2020-02-27|
    CN108518264B|2020-07-07|
    WO2018153500A1|2018-08-30|
    US10605145B2|2020-03-31|
    DE102018103720A1|2018-08-30|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US20100146954A1|2008-12-12|2010-06-17|Wescast Industries, Inc.|Liquid-Cooled Exhaust Valve Assembly|
    EP2378092A2|2010-04-13|2011-10-19|Pierburg GmbH|Pre-cooler|
    US20110302910A1|2010-06-11|2011-12-15|Burgers John G|Annular Heat Exchanger|
    CN100427733C|2006-03-09|2008-10-22|金安桐|Tailed gas heat recovering and utilizing device of IC engine|
    FR2943114B1|2009-03-13|2013-05-31|Faurecia Sys Echappement|VALVE FOR EXHAUST LINE|
    FR2966873B1|2010-10-27|2012-12-21|Faurecia Sys Echappement|HEAT RECOVERY DEVICE FOR EXHAUST LINE|
    KR101451158B1|2013-11-05|2014-10-15|현대자동차주식회사|Rotary type apparatus for exhaust heat recovery|
    CN204187113U|2014-10-24|2015-03-04|浙江伟光泵阀制造有限公司|A kind of high temperature regulation and control butterfly valve|
    FR3033383A1|2015-03-06|2016-09-09|Faurecia Systemes D'echappement|DEVICE FOR DRIVING A VALVE SHUTTER, VALVE EQUIPPED WITH SUCH A DEVICE, METHOD OF OPERATING THE SAME|US11208934B2|2019-02-25|2021-12-28|Cummins Emission Solutions Inc.|Systems and methods for mixing exhaust gas and reductant|
    DE102020200556B3|2020-01-17|2021-02-25|Robert Bosch Gesellschaft mit beschränkter Haftung|Assembly for a motor vehicle|
    DE102020200555B3|2020-01-17|2021-02-25|Robert Bosch Gesellschaft mit beschränkter Haftung|Assembly for a motor vehicle|
    DE102020007418A1|2020-01-17|2021-07-22|Robert Bosch Gesellschaft mit beschränkter Haftung|Assembly for a motor vehicle|
    法律状态:
    2018-02-27| PLFP| Fee payment|Year of fee payment: 2 |
    2018-08-31| PLSC| Publication of the preliminary search report|Effective date: 20180831 |
    2020-02-25| PLFP| Fee payment|Year of fee payment: 4 |
    2021-02-23| PLFP| Fee payment|Year of fee payment: 5 |
    2022-01-20| PLFP| Fee payment|Year of fee payment: 6 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1751588A|FR3063306B1|2017-02-27|2017-02-27|ASSEMBLY WITH A COOLING DRIVE SHAFT VALVE FOR EXHAUST LINE|
    FR1751588|2017-02-27|FR1751588A| FR3063306B1|2017-02-27|2017-02-27|ASSEMBLY WITH A COOLING DRIVE SHAFT VALVE FOR EXHAUST LINE|
    PCT/EP2017/056168| WO2018153500A1|2017-02-27|2017-03-15|Assembly with a valve having a cooled drive shaft for exhaust line|
    JP2019542450A| JP6825117B2|2017-02-27|2017-03-15|Assembly with valve with cooled drive shaft for drain piping|
    DE102018103720.1A| DE102018103720A1|2017-02-27|2018-02-20|Assembly with a valve with cooled drive shaft for an exhaust line|
    US15/903,141| US10605145B2|2017-02-27|2018-02-23|Assembly with a valve having a cooled driving shaft for an exhaust line|
    KR1020180022644A| KR102201907B1|2017-02-27|2018-02-26|Assembly with a valve having a cooled driving shaft for an exhaust line|
    CN201810164029.1A| CN108518264B|2017-02-27|2018-02-27|Assembly for an exhaust line having a valve with a cooled drive shaft|
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