• 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 present invention provides an actuating device (40) for a combustion engine, comprising a ball screw (10), the ball screw comprising: a nut (16), a screw (17) kinematically connected to the nut ( 16), balls (18) arranged to ensure relative movement of the nut (16) relative to the screw (17).
    公开号:FR3040746A1
    申请号:FR1558221
    申请日:2015-09-04
    公开日:2017-03-10
    发明作者:Frederic Ribera；Rudy Battistella；Gabriel Ridolfi；Nicolas Martin
    申请人:Valeo Systemes de Controle Moteur SAS；
    IPC主号:
    专利说明:

    Actuating device for a combustion engine
    The present invention relates to an actuating device for a combustion engine, comprising a ball screw.
    For example, US Pat. No. 8,862,369 discloses the principle of recirculating a part of the exhaust gases of a combustion engine to the intake. This technology, when applied to a supercharged positive ignition engine, improves engine efficiency and thus reduces fuel consumption. Applied to a diesel engine, it reduces emissions of pollutants, mainly nitrogen oxides. For these reasons, exhaust gas recirculation is a standard technology applied to combustion engines, including automotive engines. Exhaust gas recirculation is commonly referred to as EGR, the abbreviation of the English term "Exhaust Gas Recirculation". In order to optimize the operation of the engines, the amount of recirculated exhaust gas is adapted to the operating conditions, and is precisely controlled by an electric valve controlled by the electronic control unit of the engine of the vehicle. Such a valve is described in particular by patent FR 2 947 027. The flow of recirculated gas is managed by the position of a valve for partially or completely closing the conduit for the passage of recirculated gases. The rotational movement of an electric motor is converted into a translational movement of the valve by a motion transform mechanism.
    The changes made to the engines under development lead to an evolution of the performances expected for the recirculation valve.
    Thus, the tendency to reduce the engine displacement means that the pressure applied to the valve increases. The forces to be generated by the control mechanism of the valve must therefore increase. The reliability requirement of the valve is also increasing, so the wear of the mechanism over the life of the product must be minimized. In addition, the need to continuously reduce the cost price of products encourages the creation of products with a reduced number of components and easy to assemble. The size of the valve must also be minimized, because the space available for its implementation is increasingly reduced.
    The control of the flow of recirculated exhaust gas must also be more and more precise, in order to meet pollutant emission standards, which are ever more stringent with each new standard.
    The object of the invention is to propose a motion transformation mechanism having better performance on all of these criteria. For this purpose, the invention proposes an actuating device for a combustion engine, comprising a ball screw, the ball screw comprising: a nut, a screw kinematically connected to the nut, balls arranged to ensure relative movement. of the nut with respect to the screw.
    The balls are inserted between the nut and the screw, there is no direct contact between the nut and the screw.
    Preferably, the balls circulate in a helical path formed jointly on the nut and on the screw.
    When the nut and the screw have relative movement with respect to each other, the balls roll in the helical path. It can thus have a relative displacement of the screw relative to the nut with very little friction.
    Advantageously, the helical path is formed partially on an inner wall of the nut and on an outer wall of the screw.
    The helical path is formed of a portion of hollow circular section, scanning a helical profile. The balls are located between the inner wall of the nut and the outer wall of the screw and are thus guided and held in the helical path. By adapting the diameter of the balls to the space available between the inner wall of the nut and the outer wall of the screw, it is possible to obtain a very small clearance, or zero, in the mechanism.
    According to one embodiment of the device, the ball screw comprises a ball recovery path for receiving the balls from one end of the helical path and to transfer them to the other end of the helical path.
    The balls moving along the helical channel during the relative movement of the nut relative to the screw, the balls must be recirculated to allow a continuous movement of all the balls.
    Preferably, the recovery path of the balls is formed between an outer wall of the nut and an inner wall of the nut.
    The recovery path is thus formed by a cavity formed in the thickness of the wall of the ball nut. The size of the nut is not increased.
    Advantageously, the ball recovery path comprises a tube secured to the nut.
    In this case, the balls circulate inside the tube and are protected from any external contamination. The tube may not protrude from the outer surface of the nut.
    Alternatively, the tube protrudes from the outer surface of the nut. The radial size of the nut is then increased.
    According to another embodiment, the helical path comprises two distinct ends each arranged to form a stop on which a ball can bear.
    In other words, there is no recirculation path of the balls. The balls may abut at the end of the helical path. The construction of the ball screw is simplified, the less expensive part to manufacture. The invention relates to a valve for circulating a fluid, comprising: a body delimiting a fluid circulation duct, a shutter member adapted to be displaced between a closed position preventing the passage of fluid in the duct and a position opening for the passage of fluid in the conduit, an actuating device as described above, actuating the closure member. The shutter member for adjusting the flow rate of fluid passing through the valve is actuated by a device comprising a ball screw. The performance of the valve is improved. Among the advantages provided by the presence of the ball screw in the actuating mechanism of the valve, mention may be made of low friction, low wear, the almost total absence of parasitic play.
    According to a first embodiment of the valve, one of the assembly consisting of the screw and the nut is configured to be fixed in translation and free to rotate, the other element being configured to be free in translation and fixed in rotation.
    Several possibilities are available for converting a rotational movement into a translation movement. In this first embodiment, a locking in rotation and a locking in translation are distributed between two separate parts, the screw and the nut.
    According to a first example of implementation, the nut is fixed in translation and free in rotation, the screw being free in translation and fixed in rotation, the closure member being connected to the screw, the rotation of the nut ensuring a linear displacement of the screw. The nut can turn on itself but can not translate. The screw can translate, but can not rotate around its axis. Therefore, the rotation of the nut results in a translational movement of the screw. The direction of rotation of the nut determines the direction of movement of the screw.
    The shutter device of the valve being connected to the screw, the movement of the screw makes it possible to modify the position of the shutter device and thus to adjust the flow rate passing through the valve.
    According to a second example of implementation of this first embodiment, the screw is fixed in translation and free in rotation, the nut being free in translation and fixed in rotation, the closure member being connected to the nut. , the rotation of the screw ensuring a linear displacement of the nut.
    In this case, it is the nut that can translate, without being able to turn on itself. The closure member is connected to the nut. The screw can rotate about its axis, but can not translate, axial maintenance being assured. The rotation of the screw causes a translation of the nut, and thus allows to adjust the flow rate through the valve.
    According to a second embodiment of the invention, one of the assembly consisting of the screw and the nut is configured to be fixed in translation and fixed in rotation, the other element being configured to be free in translation and free in rotation.
    In this second embodiment, a locking in rotation and a locking in translation are assigned to the same part, which can be either the screw or the nut.
    According to a first example of implementation, the nut is fixed in translation and fixed in rotation, the screw being free in translation and free in rotation, the closure member being connected to the screw, the rotation of the screw ensuring simultaneously a linear displacement of the screw. The nut is here completely immobilized. The rotation of the screw simultaneously generates its axial displacement. The shutter member is connected to the screw, the rotation of the screw thus allows to adjust the flow rate through the valve.
    According to a second example of implementation of this second embodiment, the screw is fixed in translation and fixed in rotation, the nut being free in translation and free in rotation, the closure member being connected to the nut. , the rotation of the nut simultaneously providing a linear displacement of an axis of the nut.
    In this case, the screw is immobilized. The rotation of the nut causes its axial displacement. The shutter member is connected to the nut, the position of the shutter member is adjusted by the rotation of the nut.
    Advantageously, the valve comprises an electric motor arranged to drive in rotation either the screw or the nut. Control of the electric motor in a first direction of rotation makes it possible to increase the opening of the valve and thus to increase the flow rate therethrough. A control in the opposite direction of rotation makes it possible to decrease the opening of the valve and thus to reduce the flow rate.
    For example, the electric motor is of the DC type. This type of engine is economical, reliable and easy to control by the electronic control unit of the combustion engine.
    According to one embodiment, the axis of rotation of the motor is perpendicular to the axis of the screw.
    The valve then has an "L" shape. This shape can be more easily accommodated in the environment of the vehicle engine.
    According to another embodiment, the axis of rotation of the motor is parallel to the axis of the screw.
    This arrangement is adopted in embodiments where either the screw or the nut is immobilized.
    According to one aspect of the invention, the valve comprises a toothed wheel rotatably connected to the nut, the toothed wheel being driven by the electric motor. A toothed wheel is secured in rotation with the nut. The drive of the gear wheel by the electric motor thus ensures the rotation of the nut.
    Preferably, the toothed wheel comprises a hollow cylindrical portion in which the nut is inserted, the cylindrical portion and the nut being concentric. The nut is inserted into the toothed wheel to form an assembly.
    For example, the connection between the nut and the toothed wheel is provided by grooves formed on the outer periphery of the nut.
    Alternatively, the toothed wheel is fixed to the nut including fitting, welding, brazing, gluing, screwing, clipping or crimping.
    The toothed wheel and the nut are thus secured without risk of inadvertent disassembly during the life of the product.
    According to one aspect of the invention, the screw passes through the gear wheel from one axial end of the gear wheel to the other axial end of the gear wheel.
    According to another aspect of the invention, the valve comprises a toothed wheel rotatably connected to the screw, the toothed wheel being driven by the electric motor.
    When it is the rotation of the screw which makes it possible to control the opening and closing of the closure member, the screw is rotatably connected to the toothed wheel. As before, the rotation of the electric motor makes it possible to modify the position of the shutter member.
    Advantageously, the toothed wheel comprises a hollow cylindrical portion in which the screw is inserted, the cylindrical portion and the screw being concentric. For example, the connection between the screw and the toothed wheel is provided by grooves formed on the outer periphery of the screw.
    Alternatively, the toothed wheel is fixed to the screw including fitting, welding, brazing, or crimping. As before, various methods of assembly are possible. The toothed wheel and the screw are thus secured without risk of inadvertent disassembly.
    According to an embodiment where the nut free rotation, the nut cooperates with a bearing inserted into a bore of the body, the nut being fixed relative to an inner ring of the bearing. The use of a bearing makes it possible to ensure the rotation of the nut with a minimum of friction. In addition, it is possible to simultaneously provide radial guidance and axial stop of the nut.
    Preferably, the screw comprises an anti-rotation device. The screw has a support zone off-center with respect to the axis of the screw. This bearing zone is brought into contact with a fixed element of the valve to prevent the rotation of the screw about its axis, while allowing its translation along its axis.
    For example, the anti-rotation device is arranged so that a projecting portion of the screw is inserted into a slot arranged in a part rigidly connected to the body of the valve, the axis of the slot extending in a manner direction parallel to the axis of translation of the screw. The insertion of a portion of the screw in the slot makes it possible to prevent the rotation of the screw about its axis, on the other hand allows a translation of the screw along its axis.
    Advantageously, the width of the slot is constant, the width extending in a direction perpendicular to the axis of translation of the screw. The portion connected to the valve body of the antirotation device is thus simple to perform.
    According to one embodiment, the projecting portion of the screw is an insert attached to the screw.
    The manufacture of the screw remains classic, an additional piece is then fixed on the screw.
    According to one embodiment of the valve, the closure member comprises a valve.
    Valve valves generally have low levels of leakage.
    According to a characteristic of the invention, the axis of the valve is parallel to the axis of the screw. The translation of the screw causes a translation of the valve of the valve.
    For example, the axis of the valve coincides with the axis of the screw. The valve and the screw are thus easily secured and the overall size of the assembly is reduced, particularly in a direction radial to the axis of the valve.
    The screw may also constitute the stem of the valve. The valve head is then attached to the screw. The invention will be better understood on reading the figures.
    FIG. 1 represents, schematically, a combustion engine equipped with an exhaust gas recirculation valve according to the invention,
    FIG. 2 is a perspective view of an exhaust gas recirculation valve fitted to the engine of FIG. 1,
    FIG. 3 is a perspective view of a part of the actuating device included in the valve of FIG. 2,
    FIG. 4 is a sectional view of the ball nut included in the actuating device of FIG. 3,
    FIG. 5 is a sectional view of the valve of FIG. 2.
    Figures 6a and 6b show schematically a valve according to another embodiment, for which the ball nut is fixed, the valve being in the closed position in Figure 6a and in the open position in Figure 6b.
    FIG. 1 shows a combustion engine 50.
    The motor 50 is supplied with combustion air by an intake circuit 51. By combustion air is meant a mixture comprising air, recirculated exhaust gas and fuel vapors from the tank. The fuel, pressurized and supplied to each of the combustion chambers of the engine 50, burns in each of the cylinders of the engine 50. This combustion generates the mechanical work provided by the engine. After combustion, the flue gases are discharged into the exhaust system 52.
    In the example shown, the engine 50 is supercharged, that is to say that the intake air pressure is raised to a value greater than the atmospheric pressure before admission into the engine 50. For this, a supercharging device 55 comprises a centrifugal compressor 56, driven in rotation by a turbine 57 which is traversed by the exhaust gas. The expansion of the exhaust gas in the turbine 57 provides the energy required for the compressor 56 to provide the work of compressing the intake air. The supercharging, well known to those skilled in the art, makes it possible to increase the performance of the engine with equal displacement, or to ensure the same performance with a smaller displacement.
    Part of the exhaust gas passes through the recirculation circuit 53 and is redirected to the intake circuit 51. The recirculated exhaust gas is taken from the exhaust circuit 52 upstream of a turbine 57 of a device the supercharger 55 of the engine 50 and are recirculated in the intake circuit 51 downstream of a compressor 56 of the supercharging device 55 of the engine 50.
    The valve 1 is arranged to circulate exhaust gas between an exhaust system 52 of a combustion engine 50 and an intake circuit 51 of combustion engine combustion engine 50. In other words, the valve 1 allows to adjust the flow of gas through the exhaust gas recirculation circuit 53. A heat exchanger 58 allows to cool the recirculated exhaust gas.
    This type of exhaust gas recirculation circuit corresponds to the architecture known as "high pressure", well known to those skilled in the art.
    A second recirculation circuit 54 of exhaust gas is also present. This second circuit corresponds to the so-called "low pressure" architecture. The exhaust gas is in fact taken from the exhaust circuit 52 downstream of the turbine 57 and downstream of the pollution control device 58. The pollution control device 58 converts most of the gaseous pollutants and traps the solid particles. Part of the exhaust gas is thus reintroduced into the intake circuit of the engine 50 after passing through the recirculation circuit 54. The recirculation circuit 54 is connected to the intake circuit 2 upstream of the compressor 56. A valve 60 allows the flow of gas passing through the recirculation circuit 54 to be regulated. A heat exchanger 59 makes it possible to cool the gases passing through the circuit.
    This type of exhaust gas recirculation circuit corresponds to the so-called "low pressure" architecture. The high pressure circuit and the low pressure circuit complement each other to obtain a very high EGR flow rate.
    Figure 2 describes the constitution of the valve 1 for recirculating exhaust gas.
    The valve 1 comprises: a body 2 delimiting a conduit 3 for circulating the fluid, a closure member 4 adapted to be displaced between a closed position preventing the passage of fluid in the conduit 3 and an open position allowing the passage fluid in the duct 3. The shutter member 4 is here a valve. The valve stem 11 slides linearly in the valve guide 12. The valve is shown in FIG. 2 in the closed position. The valve head 4a, secured to the valve stem 11, rests on the valve seat 13. In this position, the flow rate through the conduit 3 is zero.
    The valve 1 comprises an actuating device 40, not shown in FIG. 2, actuating the closure member 4.
    An electric motor 5, also not shown in this external view of the valve 1, makes it possible to control the position of the valve head 4a and to adjust the flow rate passing through the valve 1. The electric motor 5 is held by a housing 6 and a bonnet 7 closes the valve 1. The fastening clips 22 maintain the cover 7 on the body 2 of the valve.
    The valve 1 can be assembled on the combustion engine 50 by screwing, the fastening screws passing through the holes 9 made in the bosses 8.
    Figures 3 and 4 detail the constitution of the actuating mechanism 40 for moving the valve 4.
    The actuating device 40 for a combustion engine comprises a ball screw 10, the ball screw comprising: a nut 16, a screw 17 kinematically connected to the nut 16, balls 18 arranged to ensure a relative movement of the nut 16 with respect to the screw 17.
    The balls 18, visible in Figure 4, are interposed between the nut and the screw, there is no direct contact between the nut and the screw.
    The balls 18 circulate in a helical path 19 formed jointly on the nut 16 and on the screw 17. When the nut and the screw have a relative movement with respect to each other, the balls roll in the helical path 19.
    The helical path 19 is partially formed on an inner wall 16a of the nut and on an outer wall 17a of the screw. The helical path 19 is formed of a portion of hollow circular section, scanning a helical profile. The balls 18 are located between the inner wall 16a of the nut and the outer wall 17a of the screw. The balls roll inside the helical path 19 which guides the balls 18 while ensuring their maintenance. The radius of the profile of the helical path 19 is slightly greater than that of the balls 18, in order to minimize friction while ensuring a low clearance, particularly in the axial direction. Such a device has a low level of friction and very little clearance. The reliability of the valve is thus improved, as well as its mechanical efficiency.
    FIG. 4 details the ball nut 16. The ball screw 10 comprises a recovery path 20 of the balls 18 making it possible to receive the balls 18 coming from one end 23 of the helical path 19 and to transfer them towards the other end 24 of the helical path 19. The balls 18 moving during the relative movement of the nut 16 relative to the screw 17, the balls 18 must be recirculated to allow a continuous movement of the nut 16 relative to the screw 17.
    In the example of FIG. 4, the recovery path 20 of the balls 18 is formed between an outer wall 16b of the nut 16 and an inner wall 16a of the nut 16. More specifically, the recovery path 20 of the balls 18 comprises a tube secured to the nut 16. The tube is inserted into a cavity made in the thickness of the wall of the ball nut 16. The tube does not protrude from the surface of the nut 16.
    According to another embodiment not shown, the helical path has two distinct ends each arranged to form a stop on which a ball can bear. In other words, there is no ball recirculation tube. By rotating the nut relative to the screw in a first direction of rotation with a sufficiently high angular value, the ball closest to one end of the helical path abuts a first end of the helical path. By rotating the nut relative to the screw in the opposite direction, a sufficiently high angular value, it is the ball near the second end of the helical path which abuts on this second end. There is no continuous recirculation of the beads. This solution is simpler to manufacture, since it is not necessary to provide a ball recovery path. The friction in the mechanism is on the other hand higher once the balls are in abutment, since the rolling without sliding of the balls in the helical path is no longer possible. Since the valve 1 has a shutter member 4 with linear displacement, the actuating device 40 must convert a rotational movement of a workpiece into a translation movement of another workpiece.
    In a first embodiment, a locking in rotation and a locking in translation are distributed between two separate parts, which are the screw and the nut.
    For this, according to a first embodiment, one of the assembly consisting of the screw 17 and the nut 16 is configured to be fixed in translation and free in rotation, the other element being configured to be free in translation and fixed in rotation.
    According to a first example of implementation, corresponding to FIG. 5, the nut 16 is, relative to the valve body, fixed in translation and free in rotation, the screw 17 being free in translation and fixed in rotation. The shutter member 4 is connected to the screw 17, and the rotation of the nut 16 ensures a linear displacement of the screw 17. The nut 16 can turn on itself but can not translate. The screw 17 can translate, but can not turn on itself. Therefore, the rotation of the nut 16 results in a translational movement of the screw 17. The direction of rotation of the nut 16 determines the direction of movement of the screw 17. The axis of the valve 4 is parallel with the axis of the screw 17. More precisely, the axis of the valve 4 coincides with the axis of the screw 17. The valve 4 and the screw 17 are thus easily secured and the overall size of the assembly is reduced. , particularly in a direction radial to the axis of the valve.
    According to another embodiment, the screw and the valve stem constitute a single piece on which the valve head is attached.
    The valve 4 being secured to the screw 17, the displacement of the screw 17 makes it possible to modify the position of the valve 4 and thus to adjust the flow rate passing through the valve 1.
    The valve 1 comprises an electric motor 5 arranged to rotate the nut 16.
    The electric motor 5 is of the DC type. The electric motor 5 of the valve 1 is controlled by the electronic control unit of the combustion engine, not shown. Control of the electric motor 5 in a first direction of rotation makes it possible to increase the opening of the valve 1 and thus to increase the flow rate therethrough. A control in the opposite direction of rotation makes it possible to decrease the opening of the valve 1 and thus to reduce the flow rate.
    A position sensor, not shown, allows the electronic control unit to know the actual position of the valve and to ensure compliance with the position command. The opening of the valve 1 is continuously adjusted in order to adapt the flow rate to the operating flow rates of the combustion engine 50.
    When the electric motor 5 is not controlled, the return spring 29 makes it possible to return the toothed wheel 15 to its rest position and thus to return the valve 4 to the closed position. The return spring 29 is held in a groove 30 secured to the toothed wheel 15. Thus, the flow through the valve 1 is zero in the event of failure of the control system.
    Several turns of the nut 16 may be necessary in order to cover the entire opening stroke of the valve 4. It is therefore possible to have an important gear ratio. This makes it possible to have a force available to move the high valve, without using an electric motor having a high torque. A compact electric motor can be used.
    In the example of Figure 5, the axis of rotation of the motor 5 is perpendicular to the axis of the screw 17. The valve then has an L shape. The space under the housing 6 of the electric motor is free . This feature allows the valve to be more easily houseable in the environment of the vehicle engine.
    The motor 5 is pressed on the contact surface 28 of the body, and is held in place by the housing 6. The housing 6 is crimped on the cover 7, the two parts are thus secured.
    According to a second example of implementation of this first embodiment, not shown, the screw 17 is fixed in translation and free in rotation, the nut 16 being free in translation and fixed in rotation, the shutter member 4 being connected to the nut 16, the rotation of the screw 17 ensuring a linear displacement of the nut 16.
    In this case, it is the nut that can translate, without being able to turn on itself. The closure member is connected to the nut. The screw can rotate about its axis, but can not translate, axial maintenance being assured. The rotation of the screw causes a translation of the nut, and thus allows to adjust the flow rate through the valve.
    According to a second embodiment of the invention, one of the set consisting of the screw 17 and the nut 16 is configured to be fixed in translation and fixed in rotation, the other element being configured to be free in translation and free rotation. In other words, the locking in rotation and locking in translation are assigned to the same part, which can be either the screw or the nut.
    According to a first exemplary implementation, represented in FIGS. 6a and 6b, the nut 16 is fixed in translation and fixed in rotation, the screw 17 being free in translation and free in rotation, the closure member 4 being linked to the screw 17, the rotation of the screw 17 simultaneously ensuring a linear displacement of an axis of the screw 17. The nut 16 is in this case immobilized. The rotation of the screw 17 simultaneously generates its axial displacement. The shutter member 4a is connected to the screw 17, the rotation of the screw 17 thus makes it possible to adjust the flow rate passing through the valve.
    In this first example of implementation, the axis of rotation of the motor 5 is parallel to the axis of the screw 17. This configuration can limit the radial size of the valve 1. The screw 17 and the rod of valve 11 are coaxial.
    According to a second example of implementation of this second embodiment, not shown, the screw is fixed in translation and fixed in rotation, the nut being free in translation and free in rotation, the closure member being connected to the nut, the rotation of the nut simultaneously ensuring a linear displacement of an axis of the nut.
    In this case, the screw is immobilized. The rotation of the nut causes its axial displacement. The closure member is connected to the nut.
    It can be seen in FIG. 5 that the valve 1 comprises a toothed wheel 15 rotatably connected to the nut 16, the toothed wheel 15 being driven by the electric motor 5. More specifically, the motor shaft 5 comprises a pinion 14 meshing with the toothed wheel 15.
    The toothed wheel 15 comprises a hollow cylindrical portion 15a in which the nut 16 is inserted, the cylindrical portion 15a and the nut 16 being concentric. The adjustment between the toothed wheel 15 and the nut 16 is determined to obtain a tight fit of the nut 16 in the toothed wheel 15. The two parts are thus secured without risk of inadvertent disassembly.
    According to an embodiment not shown, the connection between the nut 16 and the toothed wheel 15 is provided by grooves formed on the outer periphery of the nut 16.
    The toothed wheel 15 can also be fixed to the nut 16, in particular by welding, brazing, gluing, screwing, clipping or crimping.
    The screw 17 passes through the toothed wheel 15 from one axial end of the toothed wheel 15 to the other axial end of the toothed wheel 15.
    According to an embodiment not shown, the valve comprises a toothed wheel rotatably connected to the screw, the toothed wheel being driven by the electric motor 5.
    When it is the rotation of the screw which makes it possible to control the opening and closing of the closure member, the screw is rotatably connected to the toothed wheel. As before, the rotation of the electric motor makes it possible to modify the position of the shutter member.
    As for the example described, the toothed wheel may comprise a hollow cylindrical portion in which the screw is inserted, the cylindrical portion and the screw being concentric.
    For example, the connection between the screw and the toothed wheel can be provided by splines formed on the outer periphery of the screw. As before, various methods of assembly are possible. Alternatively, the toothed wheel can be fixed to the screw including fitting, welding, brazing, crimping.
    According to the example of FIG. 5, the nut 16 cooperates with a bearing 21 inserted in a bore 25 of the body 2, the nut 16 being fixed with respect to an inner ring of the bearing 21.
    The outer ring of the bearing 21 is fitted into the bore 25, the bearing is blocked axially. The nut is fitted into the inner ring of the bearing 21. The bearing 21 thus simultaneously ensures the radial guide and the axial stop of the nut 16. In addition, the use of a bearing makes it possible to ensure the rotation of the nut with a minimum of friction. In the example of Figure 5, the screw 17 comprises an anti-rotation device.
    The screw has a support zone off-center with respect to the axis of the screw. This bearing zone is brought into contact with a fixed element 27 of the valve to prevent rotation of the screw 17 about its axis, while allowing its translation along its axis.
    The anti-rotation device is arranged so that a projecting portion 26 of the screw 17 is inserted into a slot 27 arranged in a part rigidly connected to the body 2 of the valve 1, the axis of the slot 27 is extending in a direction parallel to the axis of translation of the screw 17. The insertion of a portion of the screw into the slot makes it possible to prevent the rotation of the screw about its axis, on the other hand allows a translation of the screw along its axis.
    The width of the slot 17 is constant, the width extending in a direction perpendicular to the axis of translation of the screw 17. The portion connected to the valve body of the anti-rotation device is thus simple to achieve.
    According to one embodiment, the projecting portion 26 of the screw 17 is an insert attached to the screw 17.
    权利要求:
    Claims (13)
    [1" id="c-fr-0001]
    An actuating device (40) for a combustion engine, comprising a ball screw (10), the ball screw comprising: a nut (16), a screw (17) kinematically connected to the nut (16), balls (18) arranged to ensure relative movement of the nut (16) relative to the screw (17).
    [2" id="c-fr-0002]
    2. Device according to the preceding claim, wherein the balls (18) circulate in a helical path (19) formed jointly on the nut (16) and on the screw (17).
    [3" id="c-fr-0003]
    3. Valve (1) for circulating a fluid, comprising: a body (2) delimiting a conduit (3) for circulating the fluid, a closure member (4) able to be moved between a closed position preventing the passage of the fluid in the conduit (3) and an open position allowing the passage of fluid in the conduit (3), an actuating device (40) according to one of the preceding claims, actuating the closure member (4).
    [4" id="c-fr-0004]
    4. Valve (1) according to claim 3, wherein one of the assembly consisting of the screw (17) and the nut (16) is configured to be fixed in translation and free in rotation, the other element being configured to be free in translation and fixed in rotation.
    [5" id="c-fr-0005]
    5. Valve according to the preceding claim, wherein the nut (16) is fixed in translation and free in rotation, the screw (17) being free in translation and fixed in rotation, the closure member (4) being bonded. to the screw (17), the rotation of the nut (16) ensuring a linear displacement of the screw (17).
    [6" id="c-fr-0006]
    6. Valve (1) according to claim 3, wherein one of the assembly consisting of the screw (17) and the nut (16) is configured to be fixed in translation and fixed in rotation, the other element being configured to be free in translation and free in rotation.
    [7" id="c-fr-0007]
    7. Valve (1) according to the preceding claim, wherein the nut (16) is fixed in translation and fixed in rotation, the screw (17) being free in translation and free to rotate, the closure member (4). ) being connected to the screw (17), the rotation of the screw (17) simultaneously providing a linear displacement of an axis of the screw (17).
    [8" id="c-fr-0008]
    8. Valve (1) according to one of claims 3 to 7, comprising an electric motor (5) arranged to rotate in either the screw (17) or the nut (16).
    [9" id="c-fr-0009]
    9. Valve (1) according to claim 5, comprising a toothed wheel (15) rotatably connected to the nut (16), an electric motor (5), the electric motor (5) being arranged to drive in rotation the wheel toothed (15).
    [10" id="c-fr-0010]
    10. Valve (1) according to the preceding claim, wherein the toothed wheel (15) is fixed to the nut (16) in particular by fitting, welding, brazing, gluing, screwing, clipping or crimping.
    [11" id="c-fr-0011]
    11. Valve (1) according to one of claims 5,9,10, wherein the nut (16) cooperates with a bearing (21) inserted into a bore (25) of the body (2), the nut ( 16) being fixed with respect to an inner ring of the bearing (21).
    [12" id="c-fr-0012]
    12. Valve (1) according to one of claims 3 to 11, wherein the closure member (4) comprises a valve (4a).
    [13" id="c-fr-0013]
    13. Valve (1) according to one of claims 3 to 12, wherein the valve is arranged to circulate exhaust gas between an exhaust circuit (52) of a combustion engine (50) and a intake circuit (51) for combustion gas of the combustion engine (50).
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    同族专利:
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    CN108350837A|2018-07-31|
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    WO2017037065A1|2017-03-09|
    引用文献:
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    WO1984000592A1|1982-08-03|1984-02-16|Martin Marietta Corp|Magnetically actuated valve|
    US6802488B1|2002-08-30|2004-10-12|The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration|Electro-mechanical coaxial valve|
    JP2007211698A|2006-02-09|2007-08-23|Yanmar Co Ltd|Egr device|
    US20120012766A1|2007-08-10|2012-01-19|Astrium Gmbh|Coaxial valve with an electric drive|
    KR20110028878A|2009-09-14|2011-03-22|한국델파이주식회사|Exhaust gas recirculation valve for vehicles|
    JP2015152069A|2014-02-13|2015-08-24|富士重工業株式会社|flow control valve|FR3067779A1|2017-06-14|2018-12-21|Valeo Systemes De Controle Moteur|ACTUATING DEVICE FOR MOTOR CONTROL ACTUATOR INCLUDING A CAGE SCREW SCREW MECHANISM|
    FR3067778A1|2017-06-14|2018-12-21|Valeo Systemes De Controle Moteur|ACTUATING DEVICE FOR MOTOR CONTROL ACTUATOR INCLUDING BALL SCREW MECHANISM WITH RING|
    DE102018131236A1|2017-12-18|2019-06-19|Valeo Systemes De Controle Moteur|Actuator for engine control valve|DE19961756C1|1999-12-21|2001-04-19|Siebe Automotive Deutschland Gmbh|Exhaust gas feedback valve for automobile engine has valve element rotated about its axis at least during inital part of its linear movement|
    CN101157427B|2007-09-30|2010-05-26|西子联合控股有限公司|Manual-automatic integral lifting gear|
    DE102007061996A1|2007-12-21|2009-06-25|Continental Automotive Gmbh|Actuator for actuating a valve flap in a valve seat|
    DE502008002568D1|2008-10-06|2011-03-24|Cooper standard automotive deutschland gmbh|Exhaust gas recirculation valve|
    CN101850435A|2009-04-01|2010-10-06|德阳嘉龙机械制造有限公司|X-shaft ball screw nut transmission mechanism of numerical control floor type boring and milling machine|
    CN102482998B|2009-06-17|2017-03-22|法雷奥电机控制系统公司|Valve comprising a movement transformation device|
    FR2947027B1|2009-06-17|2011-07-15|Valeo Sys Controle Moteur Sas|MOVEMENT TRANSFORMATION DEVICE AND VALVE HAVING SUCH A DEVICE|
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    CN102155525A|2011-04-26|2011-08-17|池州市邦鼐机电科技有限公司|Inversion-free ball screw assembly|FR3065507B1|2017-04-21|2019-06-28|Valeo Systemes De Controle Moteur|ROTATION DRIVE DEVICE, IN PARTICULAR FOR A VALVE, COMPRISING A GEAR AND SKIRT AGAINST THE PROPAGATION OF WEAR PARTICLES OF THE GEAR|
    FR3071883B1|2017-10-04|2020-03-20|Valeo Systemes De Controle Moteur|OPERATING DEVICE FOR INTEGRATED INTO A VALVE FOR A HEAT ENGINE|
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    DE102017130323B3|2017-12-18|2019-05-02|Pierburg Gmbh|Valve device for an internal combustion engine|
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    IT201800007766A1|2018-08-02|2020-02-02|Magneti Marelli Spa|FLEXIBLE LINEAR ELECTRIC ACTUATOR FOR AUTOMOTIVE APPLICATIONS|
    法律状态:
    2016-09-28| PLFP| Fee payment|Year of fee payment: 2 |
    2017-03-10| PLSC| Search report ready|Effective date: 20170310 |
    2017-09-29| PLFP| Fee payment|Year of fee payment: 3 |
    2018-09-28| PLFP| Fee payment|Year of fee payment: 4 |
    2019-09-30| PLFP| Fee payment|Year of fee payment: 5 |
    2020-09-30| PLFP| Fee payment|Year of fee payment: 6 |
    2021-09-30| PLFP| Fee payment|Year of fee payment: 7 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1558221A|FR3040746B1|2015-09-04|2015-09-04|ACTUATING DEVICE FOR COMBUSTION ENGINE|
    FR1558221|2015-09-04|FR1558221A| FR3040746B1|2015-09-04|2015-09-04|ACTUATING DEVICE FOR COMBUSTION ENGINE|
    EP16766238.6A| EP3344866A1|2015-09-04|2016-08-30|Actuation device for internal combustion engine|
    CN201680062246.9A| CN108350837A|2015-09-04|2016-08-30|Actuation means for combustion engine|
    PCT/EP2016/070422| WO2017037065A1|2015-09-04|2016-08-30|Actuation device for internal combustion engine|
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