Symmetrical angular thread ball screw mechanism

Abstract

A ball screw mechanism (1) comprises a screw (10) defining a reference axis (200), a nut (12) and at least two balls (2) positioned to roll on a screw thread (34) formed on the screw (10) and a nut thread (134) formed on the nut (12), the screw thread (34) and the nut thread (134) having a helix pitch P.In a section plane containing the reference axis (200) and passing through a center (C1) of a ball (2a), any segment (240) perpendicular to the reference axis (200), located at a distance x from the center (C1) of the first ball (2a), and having a first end which belongs to the screw thread (34) and a second end which belongs to the nut thread (134), has a center (C2) which, in an orthonormal reference frame (R) having an abscissa axis coincident with the reference axis (200) and an ordinate axis which passes through the center (C1) of the first ball (2a), has an abscissa equal to x and an ordinate y, defining a function which, when x varies between 0 and P, passes through a minimum Y0 reached for an abscissa X0 and through a maximum Y1 reached for an abscissa X1, Y1-Y0 being greater than 0.1 mm. The length L of the segment (240) is always greater than 0.25 mm. (Abstract figure: 2).

Description

Title of the invention: Ball screw mechanism with symmetrical angular threads TECHNICAL FIELD OF THE INVENTION

[0001] The invention relates to the field of ball screws, and more precisely to the threads of such a screw mechanism. STATE OF THE PRIOR ART

[0002] In document DE102007017214 a ball screw mechanism is disclosed, comprising a screw defining a reference axis, a nut and at least two balls rolling on a screw thread formed on the screw and a nut thread formed on the nut. This mechanism comprises threads whose flanks have different radii of curvature. When the mechanism is stressed with low amplitude forces in a given axial direction corresponding to normal operation, the balls are in contact with a flank of large radius of curvature of the screw thread and with a flank of large radius of curvature of the nut thread, in order to minimize friction.When the mechanism at rest is axially stressed in a direction opposite to the normal operating direction, the balls come to bear against a small radius of curvature flank of the screw thread and a small radius of curvature flank of the nut thread, so as to be able to take up large amplitude static forces, at the cost of greater friction. This mechanism is however not suitable for an application in which the forces exerted on the moving mechanism have a large amplitude and a constant axial direction, regardless of the direction of rotation of the mechanism. Statement of the invention

[0003] The invention aims to overcome the drawbacks of the state of the art and to propose a ball screw mechanism which can rotate without excessive friction in both directions of rotation, while being subjected to axial forces of high amplitude which are always applied in the same axial direction.

[0004] To do this, according to a first aspect of the invention, a ball screw mechanism is proposed, comprising a screw defining a reference axis, a nut and at least two balls of radius R positioned so as to roll on a screw thread formed on the screw and a nut thread formed on the nut, the screw thread and the nut thread having, in an active portion of the screw and the nut, a helix pitch P, characterized in that in a section plane containing the reference axis and passing through a center of a first ball among the at least two balls, the first ball being positioned in the active portion of the screw and the nut, any segment perpendicular to the reference axis, located at

[0005] a distance x from the center of the first ball, and having a first end which belongs to the screw thread and a second end which belongs to the nut thread, has a center which, in an orthonormal reference frame having an abscissa axis coincident with the reference axis and an ordinate axis which passes through the center of the first ball, has an abscissa equal to % and an ordinate y, defining a function xy = / (x) which, when x varies between 0 and P, passes through a minimum Y0 reached for an abscissa X0 and through a maximum Y1 reached for an abscissa XI, such that the following inequalities are respected: '-^R <X0<P-^R lu lu ±R <Xl<P-^R , n -ro> 0.10mm

[0006] Furthermore, any segment perpendicular to the reference axis, located at a distance x from the center of the first ball, and having a first end which belongs to the screw thread and a second end which belongs to the nut thread, has a length L defining a function x L = g(x) which, when the abscissa x of the center of the segment varies between 0 and the helix pitch P, is always greater than 0.25 mm, and preferably greater than 0.40 mm.

[0007] The screw thread is radially projecting in the area located in the vicinity of the abscissa XI of the maximum, and in depression in an area located in the vicinity of the abscissa X0 of the minimum. Conversely, the nut thread is radially projecting in the area located in the vicinity of the abscissa X0 of the minimum, and in depression in an area located in the vicinity of the abscissa XI of the maximum. This allows, when a force is applied to the nut in a preferred axial direction of force going from the abscissa XI towards the abscissa X0, to benefit from a large contact area between the balls and the threads of the screw and the nut, which gives the mechanism a high capacity. In the opposite axial direction, the available contact areas are smaller, which is not a disadvantage as long as the expected forces remain low. The minimum distance L preserved between the screw thread and the nut thread ensures good lubrication of the mechanism. It also prevents any contact between the screw and the nut even under high loads and deformations.

[0008] Preferably:

[0009] Kl-KO > 0.20mm

[0010] According to one embodiment: • the screw thread forms a helical internal raceway turned radially away from the reference axis and delimited by two opposite flanks of the screw thread located on either side of a bottom of the screw thread, • the nut thread forms a helical external raceway turned ra- dially towards the reference axis and delimited by two opposite flanks of the nut thread located on either side of a bottom of the nut thread, • one extended flank among the two flanks of the nut thread is extended towards the reference axis relative to the other of the two flanks of the nut thread, • one extended flank among the two flanks of the screw thread is extended in a radial direction opposite the reference axis relative to the other of the two flanks of the screw thread, and • the extended flank of the nut thread lies radially opposite the other flank of the screw thread and the extended flank of the screw thread lies radially opposite the other flank of the nut thread, the extended flank of the nut thread and the extended flank of the screw thread being axially turned towards each other.

[0011] In a preferred axial direction of force corresponding to contact between the balls and the extended flanks of the screw thread and the nut thread, the contact ellipse can extend over a larger surface area of ​​the extended flanks of the two threads, including in the areas corresponding to the extensions of the flanks. This asymmetry makes it possible to increase the capacity of the mechanism in this direction, while preserving sufficient space between the screw and the nut, in the area located between two successive turns, for good lubrication of the mechanism. The asymmetry of the flanks has the consequence that the available surface area of ​​the non-extended flanks is less to constitute the contact interface with the balls, resulting in a lower capacity of the mechanism in the direction of forces opposite to the preferred direction, which is however not a problem since in the envisaged application, the forces in this direction are low, or even detrimental.

[0012] Preferably, the two flanks of the screw thread have, in a cutting plane perpendicular to the bottom of the screw thread, a radius of curvature at any point greater than the radius R of the balls. Similarly, the two flanks of the nut thread preferably have, in a cutting plane perpendicular to the bottom of the nut thread, a radius of curvature at any point greater than the radius R of the balls. This ensures good control of the contact interface, almost point-like, between the balls and the flanks of the screw thread and the nut thread.

[0013] Preferably, both flanks of the screw thread have a circular arc curvature in a cutting plane perpendicular to the bottom of the screw thread and both flanks of the nut thread have a circular arc curvature in a cutting plane perpendicular to the bottom of the nut thread. Preferably, one or more of the following conditions are met: • both sides of the screw thread have an identical radius of curvature; and / or • both sides of the nut thread have an identical radius of curvature; and / or • at least one of the two sides of the screw thread has a radius of curvature identical to at least one of the two flanks of the nut thread.

[0014] Thus, the coefficient of friction between balls and raceways is independent of the direction of application of the axial force (in the preferred direction or the opposite direction), for a given amplitude of the axial force resultant.

[0015] According to one embodiment, the values ​​X0 and XI verify the following inequalities:

[0016] tR <X0<P-R { et \r<xkp-r

[0017] According to one embodiment, the two extremes verify the following double inequality, where D is the distance D between the center of the first ball and the reference axis:

[0018] fo <z><fi

[0019] According to one embodiment, D - FO - s < Y1 - D < D - FO + s; e designating a distortion margin such that 0 < e < 0.05mm.

[0020] According to one embodiment, the function x -* y = f(x) is such that, for any value z between 0 and P ! 2 - R, where R is the radius of the at least two balls, we observe:

[0021] (2 / (|)-f:l < / (£+s)+ / (Ç--)<2 / (£)+£l with el< 0.05mm

[0022] These inequalities reflect an approximate symmetry of the function xy = f(x), with a distortion margin el, around and near a center of symmetry located at the abscissa P / 2.

[0023] According to one embodiment:

[0024] ) <D + £1

[0025] According to one embodiment:

[0026] = £

[0027] According to one embodiment, the function .xy = f(x) is continuous.

[0028] According to one embodiment, the function xy — f(x) is strictly increasing or strictly decreasing between X0 and XI.

[0029] Near the center of the balls, the function xy = f(x) is relatively constant. Thus, D designating the distance between the center of the first ball and the reference axis, and e designating a distortion margin such that 0 < e < 0.05mm, we observe: • for 0 <x<2^,D-e< f(x) < D + e • pourp_2g <x<p,D-f< / (x)<D+ e BRIEF DESCRIPTION OF THE FIGURES

[0030] Other characteristics and advantages of the invention will emerge on reading the description which follows, with reference to the appended figures which illustrate: • [Fig.l] [Fig.l], a ball screw mechanism in axial section, illustrating in particular balls circulating on raceways of a nut and a screw of the ball screw mechanism; • [Fig.2] [Fig.2] A detailed view of a nut thread and a screw thread with balls. • [Fig.3] [Fig.3] illustrates a curve showing the evolution of the radial distance between the middle of an imaginary segment separating the two threads of the ball screw mechanism and a reference axis, as well as a curve showing the evolution of the length of said imaginary segment, as a function of the axial distance from the center of a ball of the mechanism.

[0031] For clarity, identical or similar elements are identified by identical reference signs throughout the figures. DETAILED description of embodiments

[0032] In [Fig.l] is illustrated a ball screw mechanism 1 comprising two threaded components, namely a screw 10 and a nut 12, and balls 2. The screw 10 is preferably metallic, for example steel, and has a screw thread 34 which forms an inner helical raceway 14 around a reference axis 200 of the ball screw mechanism 1 defined by the screw 10, the inner helical raceway 14 being radially rotated away from the reference axis 200. The nut 12 is preferably metallic, for example steel, and has a nut thread 134 which forms an outer helical raceway 114 around the reference axis 200, and radially rotated towards the reference axis 200. One of the two threaded components, namely the screw 10 or the nut 12, forms in in addition to a recirculation channel, not shown in the figures, which preferably spans several turns of the raceways 14, 114 of the screw 10 and the nut 12.The balls 2 may for example be made of steel or ceramic, and are sized and positioned to circulate in a closed circuit between the outer helical raceway 114 of the nut 12 and the inner helical raceway 14 of the screw 10, as well as in the recirculation channel, preferably without separators between the balls 2.

[0033] The inner helical raceway 14 of the screw 10 has, on at least one active part, a helical envelope of constant pitch P around the reference axis 200, with a raceway bottom 16, as well as a first flank 18 and a second flank 20 facing each other on either side of the raceway bottom 16, the first flank 18 being turned in a first axial direction 210 of the reference axis 200, the second flank 20 being turned in a second axial direction 220 of the reference axis 200.

[0034] In the remainder of the description, we will refer to Figures 1 and 2 where the ball screw mechanism 1 is shown in a sectional view. The section of [Fig.2] is made in a sectional plane containing the reference axis 200 and passing by a center of one of the balls.

[0035] The flanks 18, 20 of the helical raceway 14 of the screw 10 preferably have a concave section, in any plane containing the reference axis 200. These concave sections have a non-constant radius of curvature in the plane of [Fig. 2]. However, observed in any section plane perpendicular to a tangent to the bottom of the raceway 16, therefore in a plane inclined by the value of the helix angle relative to the plane of [Fig. 2], the flanks 18, 20 are preferably in an arc of a circle, and preferably with equal radii of curvature for the two flanks, so as to form a ogive extending on either side of the bottom of the raceway 16, or a continuous arc of a circle. The helix angle is however sufficiently small so that, in the section plane of [Fig.2], the variations in the radius of curvature and the center of curvature of the flanks 18, 20 are small, for example less than 0.1 mm.

[0036] The first flank 18 has an end 38 opposite the path bottom 16. The second flank 20 has an end 40 opposite the path bottom 16.

[0037] The end 38 of the first flank 18 of the screw 10 is radially less distant from the reference axis 200 than the end 40 of the second flank 20 of the screw 10.

[0038] The helical raceway 14 of the screw 10 comprises several successive turns separated by connecting portions 36 projecting from the screw thread 34. Each connecting portion 36 connects the ends 38, 40 of the flanks 18, 20 of the screw 10. The connecting portion 36 forms a rectilinear curve 46 in the vicinity of the end 38 of the first flank 18 of the raceway 14 of the screw 10, the end 38 constituting an inflection point with two half-tangents forming an obtuse angle between them. The connecting portion 36 has a convex curvature 45 in the vicinity of the end 40 of the second flank 20 of the raceway 14 of the screw 10, this end 40 constituting an inflection point, the surface of the screw thread 34 crossing its tangent at this inflection point 40.

[0039] The outer helical raceway 114 of the nut 12 has, on at least one active part, a helical envelope of constant pitch P around the reference axis 200, with a raceway bottom 116, as well as a first flank 118 and a second flank 120 facing each other on either side of the raceway bottom 116, the first flank 118 being turned in the second axial direction 220 of the reference axis 200, axially facing the first flank 18 of the raceway 14 of the screw 10 and radially facing the second flank 20 of the raceway 14 of the screw 10, the second flank 120 being turned in a first axial direction 210 of the reference axis 200, axially facing the second flank 20 of the raceway 14 of the screw 10 and radially facing the first flank 18 of the bearing race 14 of the screw 10.

[0040] The flanks 118, 120 of the helical raceway 114 of the nut 12 have preferably a concave section in any plane containing the reference axis 200. These concave sections have a non-constant radius of curvature in the plane of [Fig.2]. However, observed in any cutting plane perpendicular to a tangent to the path bottom 116, therefore in a plane inclined by the value of the helix angle relative to the plane of [Fig.2], the flanks 118, 120 are preferably in an arc of a circle, and preferably with equal radii of curvature for the two flanks, so as to form an ogive extending on either side of the path bottom 116, or a continuous arc of a circle. The helix angle is however sufficiently small so that, in the cutting plane of [Fig.2], the variations in the radius of curvature and the center of curvature of the flanks 118, 120 are small, for example less than 0.1 mm.

[0041] The first flank 118 has an end 138 opposite the bottom of the race 116. The second flank 120 has an end 140 opposite the bottom of the race 116. The end 138 of the first flank 118 of the nut 12 is radially further from the reference axis 200 than the end 140 of the second flank 120 of the nut 12. The helical raceway 114 of the nut 12 comprises several successive turns separated by projecting connecting portions 136 of the nut thread 134. Each connecting portion 136 connects the ends 138, 140 of the flanks 118, 120 of the nut 12. The connecting portion 136 forms a rectilinear curve 146 in the vicinity of the end 138 of the first flank 18 of the raceway 114 of the nut 12, the end 138 constituting an inflection point with two half-tangents making an obtuse angle between them.The connecting portion 136 has a convex curvature 145 in the vicinity of the end 140 of the second flank 120 of the raceway 114 of the nut 12, this end 140 constituting an inflection point, the surface of the nut thread 134 crossing its tangent at this inflection point 140.

[0042] Thus, the second flank 120 of the nut thread 134 is extended towards the reference axis 200 relative to the first flank 118 of the nut thread 134. Similarly, the second flank 20 of the screw thread 34 is extended in the radial direction opposite the reference axis 200 relative to the first flank 18 of the screw thread 34. The extended flank 120 of the nut thread 134 is radially opposite the non-extended flank 18 of the screw thread 34 and, similarly, the extended flank 20 of the screw thread 34 is radially opposite the non-extended flank 118 of the nut thread 134. The extended flanks 120 and 20 are opposite each other on either side of the ball center 2.

[0043] To describe the volume delimited by the screw thread 34 and the nut thread 134 in the plane of [Fig.l] and [Fig.2], an orthonormal reference frame R is defined having an abscissa axis coincident with the reference axis 200 and an ordinate axis which passes through the center Cl of the first ball 2a. It is then possible to observe any imaginary segment 240 perpendicular to the reference axis 200 located at a distance x from a center Cl of a first ball 2a, the distance x varying from 0 to P, P being the value of the helix pitch of the screw thread 34 and the nut thread 134. The segment 240 has a first end belonging to the screw thread 34 as well as a second end belonging to the nut thread 134.

[0044] The segment 240 has a center C2 which has coordinates x on the abscissa and y on the ordinate, defining a function x -* y = / (x) whose curve F is illustrated schematically in superposition on [Fig.3], and with reference to the left scale on the graph of [Fig.3], the abscissa axis being graduated by units each corresponding to 1 / 5th of P. The numerical values ​​proposed are of a purely illustrative nature. In practice,

[0045] The function x -* y = f(x) passes through a minimum Y0 reached for an abscissa X0 as well as through a maximum Y1 reached for an abscissa XI, where the values ​​X0 and XI are each greater than the radius of the balls 2. The function xy = f(x) is continuously increasing or continuously decreasing between X0 and XI, and is more generally continuous over the entire length of the screw 10.

[0046] Inside the raceways 14, 114, the center of the segment 240 remains at a distance from the reference axis which is close to the value D, which can be expressed as a function of an e designating a distortion margin such that 0 < e < 0.05 mm, by: • for Q <y<^£,£> -£< f(x) < D + e • for P - — < x< P^D~e< < D + e

[0047] The center Cl of the first ball 2a is distant from the reference axis 200 by a distance D which corresponds to half a primitive diameter of the mechanism. The minimum Y0 is less than the distance D, while Y1 is greater than the distance D. The minimum Y0 is reached for an abscissa X0 such that

[0048] R <X0<P-R

[0049] The maximum Y1 is reached for an abscissa XI such that:

[0050] R <X1<P-R

[0051] The ball screw mechanism 1 preferably has an approximate symmetry in the section plane of Figures 1 and 2, such that

[0052] D-Y0-8 <Yl-D<D-Y0 + e -,

[0053] e denoting a distortion margin such that 0 < e < 0.05mm.

[0054] More generally, the central symmetry that the ball mechanism 1 presents at the center of symmetry located at the abscissa XS=(Xl+X0) / 2 or XS=P / 2, and at the ordinate YS=D, can be written

[0055] <2 / (Ç)+£l

[0056] el designating a distortion margin such that 0 < wire < 0.05mm.

[0057] In these inequalities, e and el account for the inclination of the helical threads relative to the axial section plane of figures 1 and 2, therefore of the helix angle and the 2D primitive diameter of the mechanism.

[0058] The distortion margins e and el are related to the inclination of the helical threads relative to the axial cutting plane of Figures 1 and 2, and are a function of the helix angle and the 2D pitch diameter of the mechanism. The values ​​of e and el are less than D / 10, and preferably D / 50.

[0059] In practice, the difference El - FO is significant, and respects the following inequality:

[0060] Y1 - Y0 > 0.10mm

[0061] Preferably:

[0062] El-F0 > 0.20mm

[0063] Furthermore, the length L of the segment 240 varies as a function of the abscissa x of the segment 240, defining a function xg(x) = L, the curve G of which is illustrated on the graph of Figure 3, with reference to the right-hand scale for the ordinates. The function x -* L = Xx), passes through a minimum value Lmin, itself greater than or equal to 0.25mm, preferably greater than 0.40mm, for example greater than 0.45mm or 0.50mm, on the one hand to guarantee satisfactory circulation of grease between the turns of the raceways and on the other hand to avoid impacts between the threads of the screw and the nut under heavy loads and heavy deformations, in particular in the zone corresponding to the connecting portions 36,136 where this minimum value is possibly reached.

[0064] The axial direction 210 is a preferred direction for the forces applied by the nut 12 to the balls 2 and for the forces applied by the balls 2 and by the screw 10: when the nut applies to the balls 2 a force whose resultant has an axial component in the axial direction 210, the contact ellipse between each ball 2 and the raceway 114 of the nut 12 is formed on the second flank 120, and can extend over a large surface of the second flank, including in the zone corresponding to the extension of this second flank 120. Similarly, the contact ellipse between each ball 2 and the raceway 14 of the screw 10 is formed on the second flank 20, and can extend over a large surface of the second flank 20, including in the zone corresponding to the extension of this second flank 20.

[0065] This asymmetry makes it possible to increase the capacity of the mechanism in this direction, while preserving sufficient space between the screw and the nut, in the zone located radially between the connecting portions 36, 136, for good lubrication of the mechanism.

[0066] The asymmetry of the flanks also has the consequence that the surface available at the level of the non-extended flanks 18, 118 is less to constitute a contact interface with the balls, so that the capacity of the mechanism in the direction of forces 220 opposite to the preferred direction 210, is substantially less than the capacity in the preferred direction 210, which is however not a problem since in the application envisaged, the axial forces are unidirectional or essentially unidirectional.< / z>

Claims

Claims

1. Ball screw mechanism (1), comprising a screw (10) defining a reference axis (200), a nut (12) and at least two balls (2) of radius R positioned so as to roll on a screw thread (34) formed on the screw (10) and a nut thread (134) formed on the nut (12), the screw thread (34) and the nut thread (134) having, in an active portion of the screw and the nut, a helix pitch P, characterized in that in a section plane containing the reference axis (200) and passing through a center (Cl) of a first ball (2a) among the at least two balls (2), the first ball being positioned in the active portion of the screw and the nut, any segment (240) perpendicular to the reference axis (200), located at a distance x from the center (Cl) of the first ball (2a), and having a first end which belongs to the screw thread (34) and a second end which belongs to the nut thread (134), has: - a center (C2) which, in an orthonormal reference frame having an abscissa axis coincident with the reference axis (200) and an ordinate axis which passes through the center (Cl) of the first ball (2a), has an abscissa equal to x and an ordinate y, defining a function y — f(x) which, when x varies between 0 and P, passes through a minimum Y0 reached for an abscissa X0 and through a maximum Y1 reached for an abscissa XI, such that the following inequalities are respected: l^R <XQ<P-^R lu w , Fl -F0> 0.1 0mm and - a length L defining a function x~* L = g(x) which, when the abscissa x of the center of the segment (C2) varies between 0 and the helix pitch P, is always greater than 0.25 mm, and preferably greater than 0.40 mm.

2. Ball screw mechanism (1) according to claim 1, characterized in that the screw thread (34) forms an inner raceway (14) helical rotated radially opposite the reference axis (200) and delimited by two opposite flanks (18, 20) of the screw thread (34) located on either side of a bottom (16) of the screw thread (34), - the nut thread (134) forms a helical outer raceway (114) facing radially towards the reference axis (200) and delimited by two opposite flanks (118, 120) of the nut thread (134) located on either side of a bottom (116) of the nut thread (134), - one extended flank (120) among the two flanks of the nut thread (134) is extended towards the reference axis (200) relative to the other of the two flanks (118) of the nut thread (134), - one extended flank (20) among the two flanks of the screw thread (34) is extended in a radial direction opposite to the reference axis (200) relative to the other of the two flanks (18) of the screw thread (34), - the extended flank (120) of the nut thread (134) is radially opposite the other flank (18) of the screw thread (34) and the extended flank (20) of the screw thread (34) is radially opposite the other flank (118) of the nut thread (134), the extended flank (120) of the nut thread (134) and the extended flank (20) of the screw thread (34) being axially turned towards each other.

3. Ball screw mechanism (1) according to claim 2, characterized in that the two flanks (18, 20) of the screw thread (34) have a circular arc curvature in a cutting plane perpendicular to the bottom (16) of the screw thread (34) and the two flanks (118, 120) of the nut thread (134) have a circular arc curvature in a cutting plane perpendicular to the bottom (118) of the nut thread (134), and, preferably, - the two flanks (18, 20) of the screw thread (34) have an identical radius of curvature; and / or - the two flanks (118, 120) of the nut thread (134) have an identical radius of curvature; and / or - at least one of the two flanks (18, 20) of the screw thread (12) has a radius of curvature identical to at least one of the two flanks (118, 120) of the nut thread (134).

4.

5.

6.

7.

8.

9.

10. Ball screw mechanism (1) according to any one of the preceding claims, characterized in that / ) - Y 0 - s < Y1 - D < D - YO + e; D designating the distance between the center of the first ball (2a) and the reference axis (200), e designating a distortion margin such that 0 < s < 0.05mm. Ball screw mechanism (1) according to any one of the preceding claims, characterized in that the function xy = f(x) is such that, for any value z between 0 and P / 2 - R, where R is the radius of the at least two balls (2): 2 / (4 ) -if < / (| +;)+ / (£-;) < 2 / (£ ) +£1 avec el < 0,05mm Ball screw mechanism (1) according to any one of the preceding claims, characterized in that 2 “2 Ball screw mechanism (1) according to any one of the preceding claims, characterized in that the function xy = f(x) is continuous. Ball screw mechanism (1) according to any one of the preceding claims, characterized in that the function xy = f(x) is strictly increasing or strictly decreasing between X0 and XI. Ball screw mechanism (1) according to any one of the preceding claims, characterized in that: 71-70 > 0.20mm Ball screw mechanism (1) according to any one of the preceding claims, characterized in that: for0 <x<-^^D-e< / W<D + e pourp__lp<x<p,£> -s <!--(x)<D + e<br--> D designating the distance between the center of the first ball (2a) and the reference axis (200), e designating a distortion margin such that 0 < e < 0.05mm.

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