• 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:
    This roller screw mechanism comprises a screw, provided with an external thread, a nut disposed around and coaxially with the screw, the nut being provided with an internal thread (20), and a plurality of rollers (24). ) interposed between the screw and the nut and each comprising an external thread (26) engaged with the external thread of the screw and with the internal thread (20) of the nut. Each of the threads (20, 26) of the screw, the rollers (24) and the nut comprises first (200, 260) and second (202, 262) axially opposed flanks, respectively forming a first (a200, a260) and a second angle (a202, a262) with a plane (P) perpendicular to the central axis of the screw, the first and second flanks (260, 262) of each thread (26) of the rollers (24) respectively being in contact with the first and second flanks (200, 202) of the thread (20) of the nut and with the first and second flanks of the thread of the screw. The value of the first angle (a200, a260) is different from the value of the second angle (a202, a262). The sum of the respective values of the first angle (a200, a260) and the second angle (a202, a262) is 90 °.
    公开号:FR3036451A1
    申请号:FR1654417
    申请日:2016-05-18
    公开日:2016-11-25
    发明作者:Christian Boch；Folly Abevi
    申请人:SKF AB；
    IPC主号:
    专利说明:

    [0001] The present invention relates to the field of roller screw mechanisms for transforming a rotational movement into a linear translation movement and vice versa. Such a mechanism is provided with a screw comprising an external thread, a nut disposed around the screw and comprising an internal thread, and a plurality of longitudinal rollers comprising an external thread engaged with the external and internal threads of the thread. the screw and the nut respectively. Such a mechanism is in particular described in FR-A-2 984 443. The current roller screw mechanisms are not suitable for applications in which the axially applied load is greater in one direction of travel than in the other, as in This is the case for injection molding machines for example. Indeed, current roller screws have threads whose flanks are symmetrical, which means that the tolerable pressures are identical in both directions of translation of the mechanism. It is to these drawbacks that the invention more particularly intends to remedy, by proposing a new roller screw mechanism enabling the application to systems involving greater forces in one direction of translation than in the other. To this end, the invention relates to a roller screw mechanism comprising: - a screw provided with an external thread, - a nut disposed around and co-axially to the screw, the nut being provided with an internal thread, and a plurality of rollers interposed between the screw and the nut and each comprising an external thread engaged with the external thread of the screw and with the internal thread of the nut, each of the threads of the screw, the rollers and the the nut comprising axially opposed first and second flanks, respectively forming a first and a second angle with a plane perpendicular to the central axis of the screw, the first and second flanks of each thread of the rollers respectively being in contact with the first and second flanks of the thread of the nut and with the first and second flanks of the thread of the screw, the value of the first angle being different from the value of the second angle. This mechanism is characterized in that the sum of the respective values of the first angle and the second angle is 90 °.
    [0002] Thanks to the invention, the roller screw mechanism makes it possible to transmit a greater force in one direction of translation than in the other, which is advantageous for certain applications. According to advantageous but not obligatory aspects of the invention, such a roller screw mechanism may incorporate one or more of the following features, taken in any technically permissible combination: The difference between the value of the first angle and the value of the second angle is at least 15% of the value of the first angle. The difference between the value of the first angle and the value of the second angle is at most 40% of the value of the first angle. The first and / or second flanks of the threads of the rolls have a convex profile. The first and / or second flanks of the threads of the rollers have a straight profile.
    [0003] The flanks of the thread of the nut have a straight profile. The flanks of the thread of the nut have a concave profile. The flanks of the thread of the screw are concave, rectilinear or convex. The value of the first angle is 50 °, and the value of the second angle is 40 °. The flanks of the threads of the screw, the rollers and the nut whose angles with respect to the plane perpendicular to the central axis of the screw are the weakest, are adapted to transmit a greater axial force than the other flanks. . The invention will be better understood and other advantages thereof will appear more clearly in the light of the following description of a roller screw according to its principle, given by way of non-limiting example with reference to the attached drawings in which: - Figure 1 is a cross section of a roller screw mechanism according to the invention; FIG. 2 is a view on a larger scale of detail II in FIG. 1; FIG. 3 is a view similar to FIG. 2, of a thread of a nut belonging to a roller screw mechanism according to a first variant of the invention; - Figure 4 is a view similar to Figure 3, a thread of a nut belonging to a roller screw according to a second embodiment of the invention.
    [0004] In Figures 1 and 2, a roller screw mechanism referenced 10 as a whole, comprises a screw 12, centered on a central axis X-X ', provided with an external thread 14. A nut 16 is mounted coaxially around the screw 12 and is provided with an internal thread formed on a tubular portion 22 of the nut 16. The roller screw mechanism 10 also comprises a plurality of rollers 24 extending along respective central axes. X24 parallel to the axis XX 'and arranged radially between the screw 12 and the tubular portion 22 of the nut 16. The rollers 24 are identical to each other and regularly distributed around the screw 12. Each roller 24 comprises a thread 26 of the screw 12 and with the thread of the nut 16. The thread of the nut 16 comprises a first and a second flank 20 and a second flank 202 which are axially opposite and respectively form a first angle a200 and a seco nd angle a202 with a plane P perpendicular to the axis X-X '. The thread 26 of the rollers 24 comprises a first sidewall 260, which is in contact with the first sidewall 200 of the thread 20 and a second sidewall 262, which is in contact with the second sidewall 202 of the threading 20. The first and second sides 260 and 262 are axially opposed and respectively form a first angle α260 and a second angle a262 with the plane P. The thread 14 of the screw 12 has a geometry similar to that of the thread 20 and comprises first and second not shown flanks, which are axially opposite and are respectively in contact with the first flank 260 and the second flank 262. The flanks of the thread 14 form angles with respect to the plane P which have identical values to the angles a200 and a202. The flanks of the threading 14 may be concave, rectilinear or convex.
    [0005] The values of the angles a200, a202, a260 and a262 define the profile of the threads 14, 20 and 26. The values of the angles a200 and a260 are equal. The values of the angles a202 and a262 are equal. The rotation of the screw 12 about its axis X-X 'has the effect, according to the direction of rotation, to activate a translational movement along the axis X-X' of the nut 16, indicated by the arrows F1 and F2. Alternatively, the rotation of the nut 16 about its axis X-X 'has the effect, according to the direction of rotation, to activate a translational movement along the axis XX' of the screw 12. Certain applications in which roller screw mechanisms are used, especially plastic injection presses, require the application of greater forces in one direction of translation of the nut 16 than in the other.
    [0006] In particular, the effort to be transmitted is greater during the pressure phase of the press, while the effort to be transmitted is relatively low when the press returns to its starting position. For this purpose, the flanks of the threads 14, 20 and 26 are asymmetrical, i.e. the angular profiles of the flanks of the threads 14, 20 and 26 are different. Advantageously, the difference between the value of the angles a200 and a260 and the value of the angles a202 and a262 is at least 15%, preferably at most 40% of the value of the angles a200 and a260. In the example, the values of angles a200 and a260 are strictly greater than the values of angles a202 and a262, so that flanks 202 and 262 are more inclined relative to axis XX 'than flanks 200 and 260. As a result, the flanks 202 and 262 allow the transmission of a greater axial force than the flanks 200 and 260, which promote better sliding. The transmission of forces allowed by this geometry is greater in the direction of the arrow F1, because the flanks 202, that is to say the parts 15 of the nut 16 on which the displacement forces are exerted, are opposed along the axis XX 'in the direction of displacement. The thread 14 of the screw 12 having a geometry similar to that of the thread 20, the screw 12 is therefore capable of exerting greater torques in the direction of rotation corresponding to the displacement in the direction of the arrow F1.
    [0007] In order to maintain the same thread profile depth, the sum of the angles a200 and a202, or angles a260 and a262, is equal to 90 °. For example, the angles a200 and a260 may each be equal to 50 °, tandb that the angles a262 and a202 may each be equal to 40 °. In the example shown, the flanks 260 and 262 have a convex profile, while the flanks 200 and 202 have a rectilinear profile. For the flanks 260 and 262, the angles a260 and a262 are formed by the tangent T to the flanks 260 and 262 passing through the point of contact C between the flanks 260 and 200 or between the flanks 262 and 202. According to a variant of FIG. 3, in which only the thread 20 is shown, the flank 202 has a convex profile. In such a case, the flank 262 may have a convex or rectilinear profile. In variant not shown, each of the sidewalls 200 and 202 may be convex. According to another variant of the invention shown in Figure 4, in which only the thread 20 is shown, the sidewalls 200 and 202 have a concave profile. In such a case, the flanks 260 and 262 may have a convex profile.
    [0008] In a variant not shown, the flanks 260 and 262 of the thread 26 of the rollers 24 may have a convex or rectilinear profile. The features of the embodiments and variants described above may be combined to provide novel embodiments of the invention. 5
    权利要求:
    Claims (10)
    [0001]
    REVENDICATIONS1. A roller screw mechanism (10) comprising: a screw (12) provided with an external thread (14), a nut (16) disposed around and coaxially with the screw (12), the nut (16) being provided with an internal thread (20), and - a plurality of rollers (24) interposed between the screw (12) and the nut (16) and each comprising an external thread (26) engaged with the external thread (14). ) of the screw (12) and with the internal thread (20) of the nut (16), each of the threads (14, 20, 26) of the screw (12), the rollers (24) and the nut (16) comprising first (200, 260) and second (202, 262) axially opposite flanks, respectively forming a first (a200, a260) and a second angle (a202, a262) with a plane (P) perpendicular to the central axis (X-X ') of the screw (12), the first and second sidewalls (260, 262) of each thread (26) of the rollers (24) being respectively in contact with the first and second sidewalls (200, 202 ) of the thread (20) of the nut (16) and with the first ier and second flanks of the thread (14) of the screw (12), the value of the first angle (a200, a260) being different from the value of the second angle (a202, a262), the mechanism (10) being characterized in that the sum of the respective values of the first angle (a200, a260) and the second angle (a202, a262) is equal to 90 °.
    [0002]
    Mechanism according to claim 1, characterized in that the difference between the value of the first angle (a200, a260) and the value of the second angle (a202, a262) is at least 15% of the value of the first angle ( a200, a260).
    [0003]
    Mechanism according to claim 2, characterized in that the difference between the value of the first angle (a200, a260) and the value of the second angle (a202, a262) is at most 40% of the value of the first angle ( a200, a260).
    [0004]
    4. Mechanism according to one of the preceding claims, characterized in that the first and / or second flanks (260, 262) of the thread (26) of the rollers (24) have a convex profile.
    [0005]
    5. Mechanism according to one of claims 1 to 3, characterized in that the first and / or second flanks (260, 262) of the thread (26) of the rollers (24) have a straight profile. 3036451 7
    [0006]
    6. Mechanism according to one of the preceding claims, characterized in that the flanks (200, 202) of the thread (20) of the nut (16) have a straight profile. 5
    [0007]
    7. Mechanism according to one of claims 1 to 5, characterized in that the flanks (200, 202) of the thread (20) of the nut (16) have a concave profile.
    [0008]
    8. Mechanism according to one of claims 1 to 5, characterized in that the flanks of the thread (14) of the screw (12) are concave, rectilinear or convex. 10
    [0009]
    9. Mechanism according to one of the preceding claims, characterized in that the value of the first angle (a200, a260) is 50 °, and the value of the second angle (a202, a262) is 40 °. 15
    [0010]
    10. Mechanism according to one of the preceding claims, characterized in that the flanks (142, 202, 262) of the threads (14, 20, 26) of the screw (12), the rollers (24) and the nut. (16) whose angles (a202, a262) relative to the plane (P) perpendicular to the central axis (X-X ') of the screw (12) are the weakest, are adapted to transmit a larger axial force than the other flanks (200, 140, 260). 20
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    同族专利:
    公开号 | 公开日
    CN105387161A|2016-03-09|
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    DE102015215431A1|2016-02-25|
    US9759298B2|2017-09-12|
    FR3025011A1|2016-02-26|
    FR3025011B1|2018-01-05|
    CN105387161B|2019-11-12|
    ITUB20153197A1|2017-02-21|
    FR3036451B1|2017-06-16|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
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    EP3406936B1|2017-05-22|2020-08-26|Goodrich Actuation Systems SAS|Improved planetary screw mechanism|
    TWI659168B|2017-09-22|2019-05-11|洪子晴|Roller screw structure and mechanism thereof|
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    法律状态:
    2016-08-30| PLFP| Fee payment|Year of fee payment: 3 |
    2016-12-23| PLSC| Search report ready|Effective date: 20161223 |
    2017-08-28| PLFP| Fee payment|Year of fee payment: 4 |
    2018-08-29| PLFP| Fee payment|Year of fee payment: 5 |
    2019-08-22| PLFP| Fee payment|Year of fee payment: 6 |
    2021-05-07| ST| Notification of lapse|Effective date: 20210405 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1457921A|FR3025011B1|2014-08-21|2014-08-21|ROLLER SCREW MECHANISM|
    FR1654417A|FR3036451B1|2014-08-21|2016-05-18|ROLLER SCREW MECHANISM|FR1654417A| FR3036451B1|2014-08-21|2016-05-18|ROLLER SCREW MECHANISM|
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