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    • 专利摘要:
    The invention relates to a gearbox (1) having a cycloidal gear comprising an input shaft (2), rotatably mounted in a gearbox housing along an axis called "main axis" (ZZ '), an eccentric member (22). ) carried by the input shaft (2) and rotated by the latter, at least one cycloid disk (23) which is rotatably mounted on said eccentric member (22) and which is provided with a toothing cycloidal ring (23T), at least one ring (25) provided with a receiving toothing (25T) on which the cycloidal teeth (23T) of the cycloid disk meshes, and an output shaft (3), distinct from the shaft of inlet (2), which is arranged to be rotated by the cycloidal disc (23), the cycloidal toothing (23T) of the disc (23) and the corresponding toothing (25T) of the crown (25) being helical. .
    公开号:FR3050502A1
    申请号:FR1653631
    申请日:2016-04-25
    公开日:2017-10-27
    发明作者:Laurent Rey；Jean-Michel Saniez
    申请人:JTEKT Europe SAS；
    IPC主号:
    专利说明:

    Cycloidal helical gear reducer for power steering
    The present invention relates to the general field of gear reducers, and more particularly the field of cycloidal gear reducers (more simply called "cycloidal reducers"), which ensure a motion transmission between an input shaft and an output shaft, in order to reduce the speed of rotation in favor of an increase in the transmitted torque. The invention relates more specifically to the application of such gear units to a vehicle power steering system.
    It is known to provide, within a power steering system, a gear reducer which provides a transmission of movement between an assistance motor, generally electric, and a drive pinion which engages on a rack of direction, so as to cause said rack in translation to change the steering angle of the steering wheels of the vehicle.
    It is generally known to use for this purpose a gear wheel with tangent wheel and worm.
    This being the case, it has also been envisaged, in particular by the patent application EP-0 931714, to use for the same purpose a cycloidal gear reducer, in which the input shaft drives, by means of an element eccentric, such as a cam, a disc which is provided with a cycloidal toothing and which meshes with a series of teeth formed by meshing pins which are implanted in a circle in a ring forming a portion of a housing reducer. The output shaft, coaxial with the input shaft, is provided with a series of coupling fingers, each engaged in a circular hole in the disk, so that the rotation of the disk under the The combined effect of the cam and the cycloidal toothing makes it possible in turn to drive the output shaft in rotation.
    However, such an arrangement has certain drawbacks, which explain why the known cycloid gear reducers are in practice unsuitable, and in fact discarded, in a certain number of applications, especially when it is concretely desired to ensure a transmission of power and power. movement within a power steering system.
    Indeed, known cycloidal reducers first of all, because of the large number of parts that constitute them, among which include the multiple individual teeth (meshing pins) implanted in the ring as well as the multiple coupling fingers, a very complex structure, relatively heavy and bulky.
    This multiplicity of component parts also renders said cycloidal reducers particularly long and expensive to manufacture.
    Cycloidal gear reducers have, compared with conventional gearboxes, of the type of gearboxes with tangential wheel and worm gear, a low driving ratio ("contact ratio"), ie a small number of means of teeth that are simultaneously engaged during meshing.
    This low driving ratio tends to create certain irregularities during the transmission of movement, irregularities that can result in jerks, shocks and noise operation.
    Such irregularities are moreover likely to disturb the tactile feeling of the driver when the latter maneuvers the steering system, which can be detrimental to driving comfort, or even the safety of the vehicle and its occupants.
    In addition, the reduction ratio obtained by the cycloidal reducer described above, that is to say the ratio between input speed and output speed, is in practice relatively low.
    However, the increasing demands for lightness and compactness which are imposed on the power steering systems lead to privileging relatively low power assistance engines, capable certainly of producing a high speed of rotation but providing, on the other hand, little torque, and which must therefore be supported by a reduction gear having a high reduction ratio and good mechanical performance.
    The objects assigned to the invention therefore aim at overcoming the aforementioned drawbacks and at proposing a new type of simplified and compact cycloidal reducer, which provides an efficient, smooth and uniform transmission of motion, and which can be particularly suitable for training. a power steering mechanism.
    The objects assigned to the invention are achieved by means of a cycloidal gear reducer comprising an input shaft, rotatably mounted in a gearbox housing along an axis called "main axis" (ZZ '), an element of eccentric carried by the input shaft and rotated by the latter, at least one cycloidal disc which is rotatably mounted on said eccentric member and which is provided with a cycloidal toothing, at least one ring provided with a receiving toothing which meshes with the cycloidal toothing of the cycloidal disc, and an output shaft, distinct from the input shaft, which is arranged to be rotated by the cycloid disk, said gearbox being characterized in that the cycloidal toothing of the disc and the corresponding receiving toothing of the crown are helicoidal.
    Advantageously, the implementation of a helical toothing, that is to say inclined at a predetermined helix angle with respect to the axis of rotation of the disk concerned (respectively relative to the axis of the crown concerned), makes it possible to obtain a more progressive and wider meshing of cycloidal teeth, and consequently a higher gear ratio and a better distribution of forces. The invention thus makes it possible to improve the smooth running of the cycloid gear, and more generally the smooth operation of the cycloidal gearbox, with respect to known gearboxes.
    It will be noted in this regard that, within the known cycloidal gearboxes, the manufacture of a toothing from individual meshing pins reported on the ring has until now required the use of straight cylindrical pins, identical to each other , and was therefore incompatible with a shaping and implantation of said pins in a helical geometry, which therefore required the implementation of a straight toothing, which suffers precisely the defects detailed above.
    Here, on the other hand, the helical cycloidal teeth of the gear unit according to the invention can be formed in one piece with the disk concerned, respectively with the ring concerned, for example by molding and / or cutting, which improves the robustness of said reducer. and greatly simplifies the assembly of said reducer.
    Moreover, the use of helical gears is perfectly suited to the production of a gearbox comprising several consecutive cycloidal reduction stages, typically of a reduction gearbox with two stages of reduction, which makes it possible to obtain very high reduction ratios , while maintaining a small footprint. Other objects, features and advantages of the invention will appear in more detail on reading the description which follows, and with the aid of the accompanying drawings, provided for purely illustrative and non-limiting purposes, among which:
    FIG. 1 illustrates, in a longitudinal sectional view along the main axis (ZZ '), an alternative embodiment of a two-stage cycloidal reducer according to the invention, and a possible implantation of said reducer within a power steering system.
    FIG. 2 illustrates, in the form of a kinematic diagram, the reducer of FIG. 1.
    Figure 3 illustrates, in an exploded perspective view, the reducer of Figures 1 and 2.
    FIG. 4 illustrates, in an exploded perspective view, the detail of the cycloid reduction stages of the gearbox of FIGS. 1 to 3.
    FIG. 5 illustrates, in a schematic perspective view, the operating principle of a cycloidal gear comprising a single reduction stage.
    Figures 6 and 7 illustrate, in perspective views with tearing material, the detail of a reduction subassembly comprising two reduction stages and usable within the reducer of Figures 1 to 4.
    FIGS. 8 and 9 show, in normal projection views to the main axis (ZZ '), the reduction subassembly of FIGS. 6 and 7 seen respectively from the first reduction stage (input) and from the second stage reduction (output).
    FIG. 10 illustrates a side view of the reduction subassembly, with severed material, of FIG. 7.
    FIG. 11 is a detailed perspective view of a helical cycloidal ring gear according to the invention, used in the gearbox of FIGS. 1 to 4 and 6 to 10.
    The present invention relates to a gearbox cycloidal gear 1, also called "cycloidal reducer" 1 (hereinafter "gearbox" 1).
    Such a gearbox 1 advantageously allows a transmission and a conversion of movement and / or effort, and therefore a transmission and a mechanical power conversion, between an input shaft 2, which receives the motive power to be transmitted, and a shaft 3, which transmits said driving power downstream of the gearbox 1.
    The term "reducer" 1 can here denote either a mechanism actually intended to reduce, that is to say, used to reduce the speed and increase the torque transmitted, the gearbox 1 then being arranged in a configuration called "configuration direct "so that the output shaft 3 rotates at an output rotational speed ω3 less than the input rotational speed ω2 of the input shaft 2 but developing an output torque T3 greater than the torque input T2 exerted on said input shaft 2, a multiplier mechanism, the gearbox 1 then being arranged in a configuration called "reverse configuration" so that the output shaft 3 rotates faster than the output shaft. input 2, but developing a torque T3 lower than that T2 supplied to the input shaft 2.
    Preferably, the gearbox 1 will be a reversible mechanism that can selectively adopt either the direct configuration or the inverse configuration simply by exchanging the roles of the input shaft 2 and the output shaft 3.
    By simple convenience of description, it will be considered in what follows that the gearbox 1 is in a direct configuration, and assumes a function of reducing the speed of rotation between the input shaft 2 and the output shaft 3.
    Moreover, the gearbox 1 is preferably in two directions of operation, in that it can transmit both a clockwise rotational movement and, conversely, a counterclockwise rotation movement.
    Of course, the gearbox 1 according to the invention may be coupled to any mechanical movement transmission system (and effort), and more particularly be used at the output of any type of rotating machine, such as engine, turbine, wind turbine or tidal turbine, or in combination with any type of rotary mechanism, motorized or manual, pedal-type, winch (including crank winch), watch movement (automatic winding), etc.
    However, according to a particularly preferred variant of application, the gearbox 1 according to the invention will be used within a power steering system 4, intended for a vehicle, preferably a motor vehicle, and will preferably be configured to provide a The invention therefore bears as such, as illustrated in FIG. 1, on a power steering system 4, which comprises an assistance motor 5, a steering mechanism 6 which makes it possible to modify the steering angle of one or more directional members 7, 8, such as one or more steered wheels 7, 8, said power steering system 4 comprising a cycloidal reducer 1 according to the any of the variants of the invention to ensure a mechanical transmission between said assist motor 5, here connected to the input shaft 2, and the steering mechanism 6, here connected to the output shaft 3.
    The assistance motor 5 is preferably an electric motor with a double direction of rotation, which is electronically controlled, according to predetermined assistance laws, by a computer 9 on board the vehicle.
    In a manner known per se, the steering mechanism 6 may comprise a rack 10, which is mounted in translation in a steering gear fixed to the chassis of the vehicle, and which is connected to the steering wheels 7, 8 by steering rods 11, 12. The output shaft 3 of the gearbox 1 can then advantageously be connected to a first drive gear 13 which meshes with said rack 10.
    The steering mechanism 6 preferably also includes a steering column 14 which carries a steering wheel 15 on which the driver acts to choose the steering angle, and thus the heading of the vehicle.
    According to a preferred embodiment, the steering mechanism 6 is a "double pinion" mechanism, in which the steering column 14 meshes with the rack 10 by means of a second drive pinion 16, distinct and remote from the first drive gear 13, as shown in FIG.
    According to the invention, and as shown in FIG. 1, the cycloidal gearbox 1 comprises an input shaft 2 which is rotatably mounted in a gearbox housing 20 along an axis referred to as the "main axis" (ZZ ') . For this purpose, the input shaft 2 is carried and guided in rotation by at least one input bearing 21, such as a ball bearing, housed in the gearbox housing 20.
    The gearbox 1 also comprises an eccentric member 22, such as a cam, which is carried by the input shaft 2 and driven in rotation by said input shaft 2. The eccentric member 22 can be formed by a separate piece, of the cam type, which is attached and fixed to the input shaft 2, or preferably, and as illustrated in FIGS. 1 and 4, said eccentric member 22 can be formed in one piece with the input shaft 2.
    The gearbox 1 further comprises at least one cycloid disk 23 which is rotatably mounted on the eccentric member 22, by means of an eccentric bearing 24, such as a ball bearing, said cycloid disk 23 being provided here, on its radially outer perimeter, a cycloidal toothing 23T.
    Note L23 the central axis of said cycloidal disk 23.
    Said central axis L23 is preferably parallel to the main axis (ZZ ').
    The cycloidal tooth 23T has, as its name suggests, substantially or even exactly a cycloid profile, said cycloid corresponding mathematically to the trajectory followed by a fictitious point situated on a fictitious generator circle which rolls without sliding on the radially outer periphery of the cycloid. a base circle centered on the central axis L23, said base circle corresponding here to the bottom of the tooth circle of the cycloid disk 23.
    In the present case, the lobes forming the toothing 23T of the disc 23 thus project radially in a direction centrifuged with respect to the central axis L23 and with respect to the bottom tooth circle of the disc 23.
    The gearbox 1 also comprises at least one ring 25 which is provided with a receiving toothing 25T on which meshes with the cycloidal gearing 23T of the cycloid disk 23.
    The receiving toothing 25T is advantageously also cycloidal, of shape conjugate to the toothing 23T of the disc 23, and has the same module (gear) as the toothing 23T of the disc 23, so as to allow meshing.
    Said receiving toothing 25 is generated on the radially inner circumference of the ring 25, radially projecting centripetal towards the central axis L25 of the ring gear. The central axis L25 of the ring 25 is preferably coincident with the main axis (ZZ '), so that the ring 25 is preferably coaxial with the input shaft 2.
    Of course, the parameters used to define, in the form of parameterized curves, the cycloidal profiles of the toothings 23T, 25T according to the invention, such as the diameter of the pitch circle, the eccentricity, or the diameter of the tooth's bottom circle. the crown can be adjusted freely to adapt said tooth profiles, with respect to a rigorously cycloidal theoretical profile, in order, for example, to minimize the stresses exerted on the teeth and to optimize the radial clearance allowing both easy assembly cycloidal gearing and smooth meshing.
    To ensure the necessary supports for the transmission of movement between the input shaft 2 and the cycloidal disk 23, the ring 25 is fixed in the gear housing 20, for example by fixing screws, so as to be locked at less in rotation about the main axis (ZZ '), and preferably so as to be totally integral with the gear housing 20 (all degrees of freedom between the ring gear 25 and the gearbox housing 20, in rotation and in translation , then deleted).
    Thus, rotation ω2 of the input shaft 2 causes a rotation of the disc 23, about its central axis L23 (which coincides at every moment with the axis of the eccentric member 22), under the combined action of the movement of the eccentric member 22, actuated by the rotation of the input shaft 2, and the cooperation between the cycloidal teeth 23T of said disk 23 and the receiving cycloidal teeth 25T conjugate of the ring 25, which causes and guides a rolling without sliding (or almost without sliding) of the cycloidal disc 23 on the ring 25.
    The gearbox 1 finally comprises an output shaft 3, distinct from the input shaft 2, and which is arranged to be rotated by the cycloid disk 23.
    Although it is not excluded that the output shaft 3 is inclined with respect to the input shaft 2, or even perpendicular to it, and thus forms a bevel gear, the output shaft 3 is preferably parallel, and more particularly coaxial, to the input shaft 2, as can be seen in FIGS. 1 and 2. The output shaft 3 will advantageously be supported, and guided in rotation, by at least one outlet bearing 26, such as a ball bearing, housed in the gear housing 20.
    In addition, preferably, the input shaft 2 will articulate in pivot connection, or even in ball joint connection, with the output shaft 3, by means of a connecting bearing 27, such as a ball bearing. here housed in the central hub of the output shaft 3, and coaxial with the input bearing 21, as shown in FIG. 1.
    Moreover, as is clearly visible in FIG. 4, the input shaft 2 may comprise one or more weights 28 arranged to compensate for the mass imbalance caused by the eccentric member 22 and the radial beating of the cycloidal disc 23 which is induced by the rotation of said eccentric member 22.
    With these weights 28, it will avoid generating vibrations or cause premature wear of the gearbox 1, and more particularly the bearings 21, 24, 26, 27.
    To facilitate the mounting of the gearbox 1, the gearbox housing 20 is preferably subdivided, in a joint plane PO transverse to the main axis (ZZ '), in at least a first housing portion 20A (upstream), here carrying the input bearing 21 and the input shaft 2, and a second housing portion 20B (downstream) carrying the output bearing 26 and the output shaft 3.
    According to the invention, and as is clearly visible in FIGS. 3, 4 and 6 to 11, the cycloidal teeth 23T of the disk 23, as well as the corresponding receiving teeth 25T of the ring 25, are helical.
    In other words, the lobes forming the teeth 23T, 25T of the cycloidal disk 23 and the ring 25 are geometrically generated from a base cross-section (considered section in a sectional plane perpendicular to the central axis L23 , L25), which here has a cycloid profile, and which sweeps a mean generatrix line which winds helically around the central axis L23, L25.
    The teeth 23T, 25T are thus inclined, in side projection, with a predetermined β30 helix angle with respect to the central axis L23, L25, as is clearly visible in FIGS. 6, 7, 10 and 11. .
    Advantageously, the use of a helical 23T, 25T toothing allows a progressive meshing and very spatially extended, which promotes the smooth operation of the gearbox 1 and eliminates jerks, shocks, and operating noises.
    According to an arrangement possibility corresponding to the variant embodiment illustrated in FIG. 5, the gearbox 1 could form a gearbox with a single cycloidal reduction stage 30, comprising a single cycloidal assembly within which a cycloidal disk 23 (optionally split into several cycloidal discs stacked axially against each other and fixed to one another) meshes with one and the same ring 25 (where appropriate common to the stack of disks 23).
    According to such a single-stage arrangement, the transmission of movement between the cycloid disk 23 (or the stack of cycloidal disks 23) and the output shaft 3 can be obtained, in a manner known per se, by providing on the output shaft 3 a plurality of rectilinear coupling fingers 31, parallel to the main axis (ZZ ') and arranged in a circle around the main axis (ZZ'), at regular intervals, said coupling fingers 31 cooperating each with a circular coupling hole 32 hollowed out in the cycloid disk 23.
    The coupling orifices 32, distributed in a circle and at a regular interval around the central axis L23 of the cycloid disk 23, have a diameter greater than that of the coupling fingers 31, so as to be able to absorb the radial deflection component of the disk 23 with respect to the output shaft 3 (that is, the component of movement perpendicular to the central axis (ZZ '), which is induced by the rotation of the eccentric member 22), while transmitting a rotation component ω3.
    Of course, alternatively, the coupling fingers 31 could be carried by the disk 23, and the coupling holes 32 by the output shaft.
    However, according to another possibility of particularly preferred arrangement, corresponding to the embodiment variant illustrated in Figures 1 to 4 and 6 to 10, the cycloidal reducer 1 comprises two reduction stages 30,130.
    Advantageously, the use of a double reduction stage makes it possible to obtain a very high reduction ratio R = ω2 / ω3, typically equal to or greater than 40, to 50 or even 100, while maintaining good compactness, and in particular a small axial space along the main axis (ZZ ') of the gearbox 1.
    In other words, the multiplication of the cycloid reduction stages makes it possible to increase the "density" of the gearbox 1, considerably increasing the reduction ratio while maintaining a light and compact gearbox.
    Such a double-stage gearbox 1 comprises, first of all, a first reduction stage 30, which comprises the eccentric member 22, a first cycloid disk 23, called an "input disk", mounted in rotation on said body eccentric 22 (itself driven in rotation by the input shaft 2) and which is provided with a first cycloidal teeth 23T, and a first ring 25, called "crown of entry", which is secured gearbox housing 20 and which is provided with a first cycloidal 25T receiving toothing on which meshes the first cycloidal gearing 23T of the input disk 23, as described above.
    The input ring 25 may be fixed, for example by screwing, in the gear housing 20, and more particularly in a counterbore 33 of the upstream portion 20A thereof, which facilitates in particular the centering and the radial retention of said crown of entry 25.
    Said gearbox 1 also comprises a second reduction stage 130, which comprises a second cycloid disk 123, called "output disk", which is rotationally integral with the input disk 23, and preferably formed in one piece with said 2, and which is provided with a second cycloidal teeth 123T, said second reduction stage 130 also comprising a second ring 125, called "output ring", which is distinct from the input ring 25 (and axially distant from said input ring 25), which is integral in rotation with the output shaft 3 (so as to be able to rotate said output shaft 3, and / or be rotated by the latter), and which is provided with a second cycloidal receiving gear 125T on which meshes the second cycloidal teeth 123T of the output disk 123.
    By "integral in rotation", it is indicated that the output disc 123 is coupled, and more preferably fixed (for example by means of fixing screws, as can be seen in FIG. 6), to the input disc 23 of FIG. such that the rotation of the input disk 23, and more generally the movement of the input disk 23 (relative to the gearbox housing 20), is transmitted identically to the output disk 123, in the same movement. 'together.
    Note that the number Z23 of teeth (that is to say the number of cycloidal lobes) of the input disk 23 may be different from the number Z123 teeth of the output disk 123, and preferably strictly greater than the latter that is, we will have: Z23> Z123.
    Moreover, the number Z25, Z125 of teeth of a ring 25, 125 will be greater, preferably one unit (of a tooth), the number of teeth Z23, Z123 of the corresponding disc 23,123.
    We will thus have Z25 = Z23 + 1 and Z125 = Z123 + 1.
    Within the gearbox 1 with a double reduction stage, the reduction ratio R = ω2 / ω3 will be given by the formula: 1 / R = 1 - (Z25 x Z123) / (Z23 x Z125).
    The number of teeth of the various disks 23, 123 and crowns 25, 125 will advantageously be chosen according to the desired reduction ratio. By way of example, by choosing Z23 = 25 and Z123 = 18, and therefore Z25 = 26 and Z125 = 19, a reduction ratio R = 67.9 is substantially obtained.
    The output ring gear 125, rotatable about the main axis (ZZ ') relative to the gearbox housing 20, may be attached and fixed, for example by screwing, at one end of the output shaft 3, which may for this purpose form a support flange 34, preferably shouldered to facilitate the centering of said output ring 125, as shown in Figures 1 and 3.
    Within such a gearbox 1 with two reduction stages 30, 130, at least one of the two stages, and preferably each of the two stages, uses helical cycloidal toothing.
    In other words, and particularly preferably, the cycloidal teeth 23T, 25T, 123T, 125T of the input disk 23 and the input ring 25 on the one hand, the output disk 123 and the crown the output 125, on the other hand, are helical, and respectively have a helix angle called "inlet helix angle" β30 and a helix angle called "exit helix angle" β130, as is clearly visible in FIGS. 6 and 10.
    Said helix angles β30, β130 characterize the inclination of the teeth relative to the central axis L23, L25 of their disc 23, 123 or their respective ring 25, 125, and more generally with respect to the main axis ( ZZ ') to which said central axes are preferably parallel.
    Advantageously, all the cycloid reduction stages 30, 130 of the gear unit 1 thus have a smooth and quiet operation.
    Preferably, and as is clearly visible in FIGS. 6 and 10, the input helix angle β30 and the output helix angle β130 are oriented in the same direction with respect to the main axis (ZZ '), so that the first reduction stage 30 and the second reduction stage 130 are arranged in an arrangement with substantially parallel teeth 23T, 25T, respectively 123T, 125T.
    More particularly, the helix angle of the input disk 23 (by convention + β30) is of the same sign as the helix angle of the output disk 123 (by convention + β130), that is to say say is inclined in the same direction with respect to the main axis (ZZ '), or even substantially parallel to (and therefore at the same time of the same sign and of the same value as) the helix angle of the output disk 123, while, respectively, the helix angle of the input ring 25 (by convention -β30 because it is of the same value as the helix angle of the input disk 23, but of opposite sign by necessity of construction) is of the same sign as the helix angle of the output ring 125 (by convention -β130), or substantially parallel to said helix angle of the output ring 125.
    Advantageously, unlike a herringbone arrangement, a (substantially) parallel arrangement of the teeth, that is to say an arrangement according to which the helix angle β 30 of the first stage 30 and the angle β130 helix of the second stage 130 are of the same sign, that is to say have the same direction of inclination relative to the main axis (ZZ '), makes it possible to make bear by the gear 1 itself the efforts which are produced by the inclination of the helical teeth.
    Thus, it is possible to limit, or even substantially cancel, the resultant of axial force which is generated along the main axis (ZZ ') because of the use of helical teeth, which avoids having to bear such a component of axial force by bearings outside the gearbox 1.
    The gearbox 1 can thus advantageously be implanted within the power steering system 4 without it being necessary to modify or reinforce the steering mechanism 6.
    In absolute terms, it is possible to have strictly parallel helix angles between the first stage 30 and the second stage 30, that is to say that one has: β30 = β130 (thus + β30 = + β130 and -β30 = -β130).
    However, according to a preferred arrangement possibility, the value (amplitude) of the input helix angle β30 is different from the value (amplitude) of the output helix angle β130.
    More particularly, these two values of helix angle β30, β130 are preferably adjusted so as to obtain, especially with regard to the number of teeth Z23, Z123 and of the respective module m23, ml23 of each cycloidal disc 23, 123, a optimized compensation of axial forces.
    Indeed, for a helical helical angle gear β, of prime radius r (with r = 1/2 * m * Z, where m is the modulus and Z the number of teeth), the axial force component Fa generated is: Fa = T * 5ϊη (β) / r = 2 * T * sin ^) / (m * Z), where T represents the transmitted torque.
    By applying this formula to each reduction stage 30, 130, a relation can be expressed between the input helix angle β30 and the output helix angle β130 which allows each stage 30, 130 to neutralize the effort axial generated by the other stage 130, 30.
    More particularly, it will be possible to calculate the output helix angle β130 as follows: sin β130 = sin β30 * (ml23 * Z123) / (m23 * Z23) For example, an output disk 123 having an angle d helix β130 = 25.33 deg, a module ml23 = 4.5 mm and a number of teeth Z123 = 18, can compensate for the axial forces generated by an input disc 23 having a helix angle β30 of 25.00 deg, a module m23 = 3.2 mm and a number of teeth Z23 = 25.
    Furthermore, the majority of the teeth (cycloidal lobes), and preferably all of the teeth, which constitute the receiving toothing 25T, 125T of the crown (s) 25, 125 are preferably formed in one piece with their respective crown 25, 125 .
    Such a monolithic arrangement of the teeth 25T, 125T will make it possible, in comparison with the old teeth made by a set of individual pins, to increase the robustness of the crowns 25, 125 and, above all, to improve the precision of the (helical) shaping of the teeth and the precision of the positioning of said teeth relative to each other, which will improve the quality of the meshing while significantly reducing the manufacturing time required to assemble the gearbox 1.
    The shaping of the teeth 25T, 125T, and more generally crowns (in the form of closed rings, which surround the central axis L25 of the crown, and therefore the main axis (ZZ '), continuously over 360 degrees), can be made for example by molding and / or cutting.
    The material used to manufacture the rings 25, 125, and their respective teeth 25T, 125T, may be a steel, optionally treated (for example by heat treatment) to increase its surface hardness and / or reduce its coefficient of friction with respect to cycloidal disk 23.1123.
    Note that it will preferably be the same for each cycloidal disc 23, 123, the majority and preferably all of the teeth forming the toothing 23T, 123T will preferably be formed integrally, for example by molding and / or by cutting, with the disc 23,123 concerned.
    Furthermore, the input disk 23 and the output disk 123 will preferably be united to one another to form a disk subset 40, animated by the same overall movement (with respect to gearbox housing 20).
    According to one possible embodiment, the input disk 23 and the output disk 123 may be manufactured as separate parts, then be assembled to each other to form said subassembly, for example by screws. fixation, as shown in Figures 6 and 7.
    However, according to a preferred embodiment, the input disk 23 and the output disk 123, with their respective teeth 23T, 123T, may be formed in one piece with one another, so as to constitute a single subset 40, monolithic, each disc 23, 123 preferably forms an axial end, as shown in Figure 1.
    Preferably, there will be provided a groove 41 which will partially axially separate the input disk 23 from the output disk 123, at least over a range of radii (with respect to the central axis L23 common to the two disks) which covers the annular sector which corresponds to the height of the teeth 23T, 123T, as is clearly visible in FIGS. 1 and 4.
    Said groove 41 materializes the axial separation between the two reduction stages 30, 130 and advantageously makes it possible to prevent the input disk 23 from interfering with or meshing with the output ring 125, and conversely, that the disk output 123 does not interfere with or meshes with the input ring 25.
    In addition, such a groove 41 may form a tool clearance facilitating the cutting or grinding of teeth 23T, 123T disks 23,123.
    The subassembly 40 of discs will further preferably comprise a tubular central housing 42 adapted to receive, in an adjusted fit, the eccentric member 22 and the eccentric bearing 24.
    The disc or disks 23, 123, and therefore more generally the subassembly 40, may for example be formed of steel, which may optionally be treated (for example by heat treatment) to increase its surface hardness and / or reduce its coefficient of friction. .
    Of course, the invention also concerns as such the cycloidal "spare parts" with helical teeth making it possible to produce one and / or the other of the reduction stages 30, 130.
    Thus, the invention also relates to a cycloidal disk 23, 123 for a cycloidal gear reducer 1, according to any one of the variants of the invention, said cycloid disk 23, 123 comprising on its periphery, preferably in a single piece (and all around said disc, 360 degrees about its central axis L23), helical cycloidal toothing 23T, 123T. The invention more particularly relates to a subassembly 40 of a two-stage, preferably one-piece, cycloidal disc 30, 130 comprising, preferably in one piece, a first cycloidal disc 23, having a first helical cycloidal gearing 23T, and a second cycloidal disk 123, having a second helical cycloidal gear 123T, axially stacked, said first and second disks 23 preferably being partially separated from one another by a groove 41, and their teeth preferably having angular angles; β30, β130 helix of the same sign, or even parallel.
    Similarly, the invention also relates to a cycloidal ring 25, 125 for cycloidal gear reducer 1, according to any one of the variants of the invention, said ring 25, 125 comprising an annular rim 25A, 125A on the inner periphery. of which is formed, preferably in one piece, a helical cycloidal toothing 25T, 125T, as illustrated in particular in Figure 11.
    Preferably, said ring 25,125 is formed in a "slice" of material of constant (axial) thickness E25, E125, whose extremal faces are substantially normal to the central axis L25.
    Preferably, said ring 25, 125, and more particularly its annular rim 25A, 125A, is pierced with fixing holes 43 allowing attachment, for example by screwing, of the (input) ring 25 on the gearbox housing 20, respectively of the (output) ring 125 on the output shaft 3.
    Of course, the invention is in no way limited to the variants of embodiment described in the foregoing, the person skilled in the art being able in particular to isolate or combine freely between them one or the other of the aforementioned characteristics, or substitute equivalents for them.
    权利要求:
    Claims (8)
    [1" id="c-fr-0001]
    Cycloidal gear unit (1) comprising an input shaft (2) rotatably mounted in a gear housing (20) along an axis referred to as the "main axis" (ZZ '), an eccentric member (22) ) carried by the input shaft (2) and rotated by the latter, at least one cycloid disk (23) which is rotatably mounted on said eccentric member (22) and which is provided with a toothing cycloidal ring (23T), at least one ring (25) provided with a receiving toothing (25T) on which the cycloidal teeth (23T) of the cycloid disk meshes, and an output shaft (3), distinct from the shaft of inlet (2), which is arranged to be rotated by the cycloid disk (23), said gear (1) being characterized in that the cycloidal teeth (23T) of the disk (23) and the toothing (25T) ) corresponding to the ring (25) are helical.
    [2" id="c-fr-0002]
    2. Gear unit according to claim 1 characterized in that it comprises two reduction stages (30, 130), including a first reduction stage (30), which comprises the eccentric member (22), a first cycloid disk (23), said "input disk", which is rotatably mounted on said eccentric member and which is provided with a first cycloidal toothing (23T), and a first ring (25), called "crown "input" which is integral with the gear housing (20) and which is provided with a first cycloidal receiving tooth (25T) on which meshes the first cycloidal gear (23T) of the input disk (23), and a second reduction stage (130), which comprises a second cycloid disk (123), called "output disk", which is rotatably connected to the input disk (23), and preferably formed in one piece with said an input disk, and which is provided with a second cycloidal toothing (123T), said second reduction stage comprises also a second ring (125), called "output ring", which is distinct from the input ring (25), which is integral in rotation with the output shaft (3), and which is provided with a second cycloidal receiving tooth (125T) on which meshes the second cycloidal teeth (123T) of the output disk, and that the cycloidal teeth (23T, 25T, 123T, 125T) of the input disk (23) and the the input ring (25) on the one hand and the output disk (123) and the output ring (125) on the other hand are helical and, in this respect, respectively have an inlet helix angle. (β30) and an output helix angle (β130).
    [3" id="c-fr-0003]
    3. Gear unit according to claim 2 characterized in that the input helix angle (β30) and the output helix angle (β130) are oriented in the same direction relative to the main axis (ZZ '), so that the first and second reduction stages (30,130) are arranged in substantially parallel tooth arrangement (23T, 25T, 123T, 125T).
    [4" id="c-fr-0004]
    4. Reducer according to claim 2 or 3 characterized in that the value of the input helix angle (β30) is different from the value of the output helix angle (β130).
    [5" id="c-fr-0005]
    5. Gear unit according to any one of the preceding claims characterized in that the majority of the teeth, and preferably all of the teeth, which constitute the receiving toothing (25T, 125T) of the crown or rings (25, 125) are formed in one piece with their respective crown.
    [6" id="c-fr-0006]
    Cycloid disk (23, 123) for a cycloidal gear reducer comprising on its periphery, preferably in one piece, a cycloidal toothing (23T, 123T) helical.
    [7" id="c-fr-0007]
    Cycloid ring (25, 125) for a cycloid gearbox comprising an annular rim (25A, 125A) on the inner periphery of which a helical cycloidal toothing (25T, 125T) is preferably formed in one piece.
    [8" id="c-fr-0008]
    8. A power steering system (4) comprising an assist motor (5), a steering mechanism (6) for changing the steering angle of one or more directional members (7, 8), such as one or more steering wheels, said power steering system (4) being characterized in that it comprises a cycloidal gear (1) according to one of claims 1 to 5 to ensure a mechanical transmission between the assistance motor (5). ) and the steering mechanism (6).
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    同族专利:
    公开号 | 公开日
    CN109154363A|2019-01-04|
    EP3449157A1|2019-03-06|
    WO2017187056A1|2017-11-02|
    US10704650B2|2020-07-07|
    CN109154363B|2021-10-15|
    FR3050502B1|2020-02-14|
    JP2019518908A|2019-07-04|
    US20190136946A1|2019-05-09|
    BR112018071905A2|2019-03-06|
    引用文献:
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    FR1351031A|1962-03-10|1964-01-31|Fichtel & Sachs Ag|Eccentric gear|
    EP0286760A1|1985-08-24|1988-10-19|Shen Peiji|Cycloidal equidistant curved gear transmission mechanism and its device|
    EP0931714A1|1998-01-23|1999-07-28|Trw Inc.|Electric steering system with speed reducer|
    CN104633062A|2013-11-07|2015-05-20|吕文杰|Double-cycloidal speed reducer|
    EP2960546A1|2014-06-27|2015-12-30|Robotyka.com|Eccentric gearbox|
    WO2007020999A1|2005-08-18|2007-02-22|Ntn Corporation|Power transmission device|
    WO2009008767A1|2007-07-09|2009-01-15|Stanovskoy Viktor Vladimirovic|Toothed wheel gearing and a planetary toothed mechanism based thereon |
    CN101949429B|2010-08-18|2013-02-06|吴声震|Single-stage cycloidal speed reducer of industrial robot|
    WO2017022062A1|2015-08-03|2017-02-09|株式会社ハーモニック・ドライブ・システムズ|Strain wave gearing device|
    WO2017022061A1|2015-08-03|2017-02-09|株式会社ハーモニック・ドライブ・システムズ|Wave gear device|
    FR3050504B1|2016-04-25|2020-02-14|Jtekt Europe|CYCLOIDAL REDUCER WITH AUTOMATIC GAME RETRIEVAL AND POWER STEERING SYSTEM PROVIDED WITH SUCH A REDUCER|
    FR3050502B1|2016-04-25|2020-02-14|Jtekt Europe|CYCLOIDAL REDUCER WITH HELICAL TOOTHING FOR POWER STEERING|FR3050502B1|2016-04-25|2020-02-14|Jtekt Europe|CYCLOIDAL REDUCER WITH HELICAL TOOTHING FOR POWER STEERING|
    US11168763B2|2017-05-03|2021-11-09|Delta Electronics, Inc.|Cycloid speed reducer|
    CN108620691B|2018-03-21|2019-10-11|湖北工业大学|A kind of Cycloid tooth profile correction method and Cycloidal Wheel, RV retarder|
    KR102098051B1|2018-09-14|2020-04-07|주식회사 만도|Reducer of Electric Power Steering Apparatus|
    KR102167914B1|2019-05-14|2020-10-20|주식회사 만도|Steering Apparatus for Vehicle|
    US11125301B1|2020-03-31|2021-09-21|Circular Wave Drive Partners Inc.|Circular wave drive|
    法律状态:
    2017-03-09| PLFP| Fee payment|Year of fee payment: 2 |
    2017-10-27| PLSC| Search report ready|Effective date: 20171027 |
    2018-03-16| PLFP| Fee payment|Year of fee payment: 3 |
    2019-03-08| PLFP| Fee payment|Year of fee payment: 4 |
    2020-02-28| PLFP| Fee payment|Year of fee payment: 5 |
    2021-03-25| PLFP| Fee payment|Year of fee payment: 6 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1653631A|FR3050502B1|2016-04-25|2016-04-25|CYCLOIDAL REDUCER WITH HELICAL TOOTHING FOR POWER STEERING|
    FR1653631|2016-04-25|FR1653631A| FR3050502B1|2016-04-25|2016-04-25|CYCLOIDAL REDUCER WITH HELICAL TOOTHING FOR POWER STEERING|
    BR112018071905-6A| BR112018071905A2|2016-04-25|2017-04-21|power steering, gearbox and crown gearbox|
    CN201780025477.7A| CN109154363B|2016-04-25|2017-04-21|Cycloid speed reducer with spiral teeth for power steering|
    PCT/FR2017/050944| WO2017187056A1|2016-04-25|2017-04-21|Cycloidal reducer with helical toothing for power steering|
    US16/096,633| US10704650B2|2016-04-25|2017-04-21|Cycloidal reducer with helical toothing for power steering|
    JP2018555961A| JP7036737B2|2016-04-25|2017-04-21|Cycloid reducer with spiral teeth for power steering|
    EP17725659.1A| EP3449157A1|2016-04-25|2017-04-21|Cycloidal reducer with helical toothing for power steering|
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