• 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 roller screw mechanism comprises a screw 12 comprising an external thread 14, a nut 16 disposed around and coaxially with said screw, said nut comprising an internal thread 18, and a plurality of rollers 20 arranged radially between the screw and the nut. and each provided with an external thread 22 in engagement with the outer and inner threads 14, 18 of said screw and said nut and of two external teeth 24, 26. The mechanism further comprises two synchronization teeth 44, 46 each engaged with one of the teeth 24, 26 of the rollers. The outer diameter of each toothing 24, 26 of each roll is smaller than the thread bottom diameter of the thread of said roll. Each tooth of said teeth 24, 26 of the rollers comprises plane faces cooperating with the teeth 44, 46 of synchronization.
    公开号:FR3026454A1
    申请号:FR1459199
    申请日:2014-09-29
    公开日:2016-04-01
    发明作者:Folly Abevi；Eric Allegri
    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 translational 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 having an external thread engaged with the external and internal threads of the thread. the screw and the nut. In a first type of roller screw mechanism, the threads of the rollers and the threading of the nut have helix angles that are identical to each other and different from that of the thread of the screw so that, when the screw rotates relative to at the nut, the rollers turn on themselves and roll around the screw without moving axially inside the nut. The rollers are guided in rotation parallel to the axis of the screw by means of rings reported in an unthreaded portion of the nut and comprising internal synchronizing teeth in engagement with external teeth of said rollers. Such a mechanism is called satellite roller screw. A second type of roller screw mechanism has a similar operating principle but is differentiated by an inverted arrangement. The helix angles of the threads of the rollers, the screw and the nut are chosen so that when the screw rotates relative to the nut, the rollers turn about themselves around the screw and move axially. in the nut. The rollers are guided in rotation by external synchronization teeth formed on the screw and cooperating with the teeth of said rollers. Such a mechanism is called inverse satellite roller screw. With the current design of these mechanisms, during the machining operations performed to form the external thread of each roll, the threading tool size the outer teeth machined beforehand at each end of said roll. The thread is therefore also present on the teeth of each of the rollers, generally in the useful area of the teeth provided for the transmission of forces and located between the head radius and the clearance radius of said teeth. During this transmission of forces, given the presence of these threads on the teeth of the rollers, the contact pressure exerted by said teeth on the synchronization teeth provided on the nut or on the screw, is relatively important in the useful area of the teeth of the rollers. This causes premature wear of the synchronization teeth. Moreover, given the involute profile of the teeth of each roller, these teeth are conventionally made by milling. This requires to provide axially between each toothing of the roller and the external thread a relatively large clearance area for the axial action mill. The axial dimension of each clearance zone is directly related to the radius of the cutter. For a given length of the roll, this zone of clearance formed at each end limits the length of the external thread that can be provided on the roll and therefore the load capacity as well as the radial and axial stiffnesses of the associated mechanism. In addition, with such a profile involute circle, sharp edges are present on the teeth of each roller. In operation, this also contributes to creating a significant contact pressure on the synchronization teeth provided on the nut, or on the screw, in the useful area of the teeth of the rollers. The present invention aims to remedy these disadvantages. More particularly, the present invention aims to provide a roller screw mechanism having an increased life and in which, for a given axial space, the load capacity is increased.
    [0002] The present invention further aims to provide a roller screw mechanism having a design adapted to a wide variety of steps of said mechanism. In one embodiment, the roller screw mechanism comprises a screw comprising an external thread, a nut disposed around and coaxially with said screw, said nut comprising an internal thread, and a plurality of rollers arranged radially between the screw and the screw. nut and each provided with an external thread engaged with the outer and inner threads of said screw and said nut and two outer teeth. The mechanism further comprises two synchronizing teeth each engaged with one of the teeth of the rollers. The outer diameter of each toothing of each roll is smaller than the thread bottom diameter of the thread of said roll. Each tooth of said teeth of the rollers comprises plane faces cooperating with the synchronization teeth. Advantageously, each tooth of the teeth of the rollers may comprise a connection radius between each flat face and an apex of said tooth.
    [0003] Preferably, each tooth of the synchronization teeth comprises flanks having in cross section a convex profile and cooperating with the flat faces of the teeth of the teeth of the rollers. Advantageously, the flat faces of each tooth of the teeth of the rollers are symmetrical with each other with respect to a median radial plane of said tooth passing through an axis of elongation of said roller. The flat faces vis-à-vis in the circumferential direction of adjacent teeth of the teeth of each roller may be interconnected by a concave bottom.
    [0004] In one embodiment, each roller comprises a groove located axially between the threading and each toothing. In one embodiment, the mechanism comprises crowns fixed on the nut and each comprising one of the synchronization teeth. Alternatively, the synchronization teeth can be formed on the nut. In another embodiment, the synchronization teeth are formed on the screw. Alternatively, the mechanism may comprise crowns fixed on the screw and each comprising one of the synchronization teeth. The invention also relates to an actuating cylinder comprising a rotation drive means and a roller screw mechanism as defined above, the screw of the mechanism being coupled to the drive means. The invention also relates to a method of manufacturing a roller screw mechanism roller comprising an external thread and two external teeth arranged axially on either side of said thread. The method comprises steps of removing material using at least one radial tool to form the outer teeth so that the outer diameter of each toothing is smaller than the thread diameter of the outer thread and that each tooth of said teeth comprises planar faces. In one embodiment, the material removal steps for forming the outer teeth of the roll are performed simultaneously with the material removal steps to form the outer thread of said roll. Advantageously, the steps of removing material to form the external teeth and / or to form the external thread are made by rolling.
    [0005] The present invention will be better understood on studying the detailed description of embodiments taken by way of non-limiting examples and illustrated by the appended drawings, in which: FIG. 1 is an axial sectional view of a mechanism Roller screw according to a first embodiment of the invention; FIG. 2 is an axial half-sectional view of a roller of the mechanism of FIG. 1; FIG. 3 is a sectional view according to FIG. Figure 4 is a detail view of Figure 3, Figure 5 is a detail view of a crown of the mechanism of Figure 1, and Figures 6 and 7 are views. in axial section of roller screw mechanisms according to second and third embodiments of the invention. In FIG. 1, the satellite roller screw mechanism, referenced 10 as a whole, comprises a screw 12, of axis 12a, provided with an external thread 14, a nut 16 mounted coaxially around the screw 12 and provided with an internal thread 18 whose inner diameter is greater than the outer diameter of the thread 14, and a plurality of longitudinal rollers 20 arranged radially between the screw and the nut. The screw 12 extends longitudinally through a cylindrical bore of the nut 16 on which the internal threading 18 is formed.
    [0006] The rollers 20 are identical to each other and regularly distributed around the screw 12. Each roll 20 extends along an axis 20a parallel to the axis 12a of the screw and comprises an external thread 22 engaged with the thread 14 of the screw. the screw and the thread 18 of the nut.
    [0007] As illustrated more clearly in FIG. 2, each roller 20 comprises, at each end, an external toothing 24, 26 and a cylindrical pin 28 extending axially outwardly from the toothing. The teeth 24, 26 are arranged axially on either side of the external thread 22. The teeth 24, 26 are identical to each other. Each roll 20 further comprises an annular outer groove 32, 34 formed axially between the thread 22 and each toothing 24, 26. The threading 22 is located axially between the grooves 32, 34. Each toothing 24, 26 is delimited axially by the groove 32, 34 associated and the pin 28, 30 corresponding. As will be described in more detail below, the outer diameter of each toothing 24, 26 of each roll is smaller than the thread bottom diameter D of the thread 22. Referring again to FIG. 1, the mechanism 10 comprises also two rings 40, 42 annular each fixed in an unthreaded portion of the bore of the nut 16 and each comprising an internal toothing 44, 46 respectively engaged with the toothing 24, 26 of the rollers for synchronization. Each ring 40, 42 is mounted axially in abutment against a radial shoulder of the nut 16 formed between the internal thread 18 and the associated non-threaded portion of the bore of said nut. The rings 40, 42 are identical to each other. The mechanism 10 further comprises two rings 48, 50 annular each mounted radially between the thread 14 of the screw and the crown 40, 42 associated. Each ring 48, 50 is mounted axially in the bore (not referenced) of the ring 40, 42 associated with being mounted free in the circumferential direction relative to said ring. Each ring 48, 50 comprises a plurality of cylindrical recesses (not referenced) through which are regularly distributed in the circumferential direction and inside which are housed the pins 28, 30 of the rollers. The rings 48, 50 carry the rollers 20 and maintain their regular circumferential spacing. The mechanism 10 also comprises rods 52, 54 each mounted in a groove (not referenced) formed in the bore of the ring 40, 42 associated and provided to maintain axially the corresponding ring 48, 50. Referring again to Figure 2, the teeth 24, 26 of each roller each comprise a plurality of teeth 60, 62 radial identical to each other and spaced relative to each other evenly in the circumferential direction. The teeth 60, 62 extend axially. Since the teeth of each roller 20 are identical, only the toothing 24 will be described here. As illustrated more clearly in FIG. 3, each tooth 60 of the toothing 24 comprises two opposing flanks or faces 60a, 60b of opposite planes and a top 60c. connecting the ends of large diameter of said faces. In the exemplary embodiment illustrated, the top 60c of each tooth is flat. The faces 60a, 60b delimit in the circumferential direction the associated tooth. The faces 60a, 60b of each tooth has in cross section or straight a straight profile. The faces 60a, 60b of each tooth are inclined with respect to a median plane P of said tooth passing through the axis 20a of the roller in two opposite directions. In the exemplary embodiment illustrated, the faces 60a, 60b of each tooth are symmetrical with each other by considering the median plane P. Each tooth 60 has a trapezoidal profile in cross section. The face 60a of a tooth is vis-à-vis in the circumferential direction with the face 60b of the immediately adjacent tooth, said faces being interconnected by a concave bottom 60d. In the exemplary embodiment illustrated, the number of teeth 60 is equal to ten. Alternatively, another number of even or odd teeth could be provided. As illustrated more clearly in FIG. 4, each tooth 60 of the toothing 24 comprises a connection radius 60e provided between each face 60a, 60b and the associated vertex 60c. Each connecting radius 60e is convex. The design of the faces 60a, 60b each having a planar shape allows to provide a connection radius 60e between each of said faces and the top 60c of the tooth. This avoids the presence of sharp edges on the teeth 60. This avoids premature wear of the teeth 44, 46 crown synchronization. Referring again to Figure 3, the outer diameter da of the toothing 24 corresponds to the circle passing through the tops 60c of the teeth. We also speak of head diameter. As indicated above, this outer diameter da of the toothing 24 of each roll is smaller than the diameter D (FIG. 2) of the thread bottom of the thread 22. With such a ratio between the outside diameter da of each toothing 24, 26 of each roll and the thread bottom diameter D of the thread 22 of said roll, no thread is formed on each of these teeth during the material removal operations performed to machine the thread 22. This makes it possible to avoid premature wear of the teeth. 44, 46 of synchronization of the crowns. In addition, the design of the teeth 60, 62 of the teeth 24, 26 of each roller having opposite planar faces makes it possible to form these teeth by deformation in the radial direction of the material using a tool with radial action, considering the axis 20a of the roll. The teeth 24, 26 may advantageously be formed by rolling. The use of a tool with radial action to form the teeth 24, 26 of each roller is particularly advantageous insofar as it is not necessary to provide between each toothing 24, 26 of the roller and the threading 22 associated with a zone axial clearance for the tool. For each roll 20, the axial distance separating each toothing 24, 26 of the associated thread 22 can therefore be reduced. For a given length of the roll 20, the length of the thread 22 can thus be increased. This makes it possible to increase the load capacity as well as the axial and radial rigidity of the mechanism 10 for a given axial space requirement.
    [0008] In the exemplary embodiment illustrated, the groove 32, 34 located axially between the thread 22 and each toothing 24, 26 is provided to allow a discharge of material during the steps of removal of material by the radial action tool. Each groove 32, 34 may have another shape or may have a reduced axial dimension so as to further increase the length of the thread 22. Advantageously, the steps of removing material to form the two teeth 24, 26 of each roll may be carried out simultaneously, by two separate tools or even a single tool. It is also possible to provide these steps simultaneously to the machining operations provided for obtaining the threading 22 which can also be made by radial rolling. In addition, the flat shape of the faces of the teeth 60, 62 makes it possible to obtain on each of the rollers teeth 24, 26 adapted to a wide variety of steps, even at relatively large steps.
    [0009] With this flat shape of the faces of the teeth 60 and 62, it is possible to maintain an outer diameter da for the teeth 24, 26 of the roller lower than the diameter D of the thread bottom of the thread 22 independently of the value of the pitch of the roll. This is not feasible with the conventional profile of involute roll gear teeth for all possible steps. As indicated above, the teeth 44, 46 for synchronizing the rings 40, 42 are identical to each other. Only the toothing 44 will be described in detail later. As illustrated in FIG. 5, the synchronization toothing 44 comprises a plurality of radial teeth 64 which are identical to one another and spaced relative to one another in a regular manner in the circumferential direction. The teeth 64 extend axially and are directed radially inwards.
    [0010] Each tooth 64 comprises two opposite convex flanks 64a, 64b and a vertex 64c connecting the large diameter ends of said flanks. In the exemplary embodiment illustrated, the vertex 64c of each tooth is in the form of a radius. The flanks 64a, 64b delimit in the circumferential direction the associated tooth. The flanks 64a, 64b of each tooth each have a convex profile in cross section. Two successive teeth 64 are interconnected in the circumferential direction by a bottom 64d. In the exemplary embodiment illustrated, each side 64a has a convex profile in cross section formed by a first hypocycloid and each side 64b has a convex profile formed by a second hypocycloid. The first and second hypocycloids are symmetrical to each other by considering a median plane of each tooth 64 passing through the axis of the crown. Alternatively, it may be possible to provide for the ring 40 teeth 64 each having in cross section a convex profile formed by two symmetrical circular arcs considering a median plane of said tooth. In operation, the lateral flanks 64a, 64b of the teeth of the synchronization toothing 44 of the ring 40 cooperate by contact with the lateral faces 60a, 60b of the teeth of the toothing 24 of the rollers. Similarly, the convexly shaped flanks of the teeth of the toothing 46 of the ring 42 abut against the flat faces of the teeth of the toothing 26 of the rollers in the circumferential direction el.
    [0011] During the transmission of forces, the flat faces of the teeth of the teeth 24, 26 of the rollers tend to locally deform at the points of contact with the convex flanks of the teeth of the teeth 44, 46 for synchronizing the rings. Under load, the tooth faces of the teeth 24, 26 of the rollers may thus present locally in cross section a slightly concave profile. During such deformation under load, a conjugate profile is obtained between the teeth 24, 26 of the rollers and the teeth 44, 46 for synchronizing the crowns. This increases the contact surfaces between the teeth of the rollers 20 and crowns 40, 42 and reduce slippage and wear. In addition, the prediction of the connecting radii on each tooth of the toothing 24, 26 of the rollers makes it possible to further reduce the wear at the end of the engagement of each of the teeth 60, 62 of the rollers with the tooth engaged with the crown 40, 42 associated. In the first exemplary embodiment illustrated, each synchronization toothing 44, 46 is formed on the associated ring 40, 42 which is itself attached and fixed on the nut 16. The embodiment illustrated in FIG. which identical elements bear the same references, differs from this first example only in that the synchronization teeth 44, 46 are formed directly on the nut 16. The mechanism 10 is devoid of rings fixed on the nut 16. In the First two examples illustrated, the present invention has been illustrated on the basis of a satellite roller screw mechanism. The exemplary embodiment illustrated in FIG. 7, in which the identical elements bear the same references, differs only in that the mechanism 10 is of the type of inverse satellite roller screw. The design of the rollers 20 is strictly identical to that described above. The screw 12 comprises two external timing teeth 70, 72 formed on the outer surface of said screw. The teeth 70, 72 are identical to each other and arranged axially on either side of the thread 14. The toothing 70, 72 is respectively engaged with the toothing 24, 26 of the rollers for their synchronization. Each toothing 70, 72 comprises a plurality of teeth 74, 76 radial identical to each other and spaced relative to each other regularly in the circumferential direction. The teeth 74, 76 extend axially and are directed radially outwardly. Each tooth 74, 76 comprises two opposite convex support flanks and a vertex connecting the large diameter ends of said flanks. The flanks of each tooth each have a convex profile in cross section. One of the flanks of each tooth may have a convex profile in cross section formed by a first epicycloid and the other sidewall may have a convex profile formed by a second epicycloid, the first and second epicycloids being symmetrical to each other by considering a median plane of said tooth. Alternatively, it may be possible to provide teeth 74, 76 each having in cross section a convex profile formed by two symmetrical circular arcs considering a median plane of said tooth. The rings 48, 50 are each mounted here radially between a non-threaded portion of the outer surface of the screw 12 and the thread 18 of the nut. The rods 52, 54 here have a reduced radial dimension and are each mounted in a groove (not referenced) formed on the associated non-threaded portion of the screw 12. In this embodiment, the outer teeth 70, 72 of synchronization are formed directly on the screw. Alternatively, it may be possible to provide rings attached to the outer surface of the screw and each comprising one of these synchronization teeth.
    权利要求:
    Claims (14)
    [0001]
    REVENDICATIONS1. A roller screw mechanism comprising a screw (12) comprising an external thread (14), a nut (16) disposed around and coaxially with said screw, said nut comprising an internal thread (18), and a plurality of rollers (20) arranged radially between the screw and the nut and each provided with an external thread (22) engaged with the external and internal threads (14, 18) of said screw and of said nut and of two external teeth (24, 26), the mechanism further comprising two timing toothings (44, 46; 70, 72) each engaged with one of the teeth (24, 26) of the rollers, characterized in that the outer diameter (da) of each toothing (24) , 26) of each roll is smaller than the bottom diameter (D) of the thread of the thread (22) of said roll, each tooth of said set of rolls having flat faces (60a, 60b) cooperating with the teeth (44, 46; , 72) of synchronization.
    [0002]
    2. Mechanism according to claim 1, wherein each tooth of the teeth (24, 26) of the rollers comprises a connecting radius (60e) between each face (60a, 60b) plane and a top (60c) of said tooth.
    [0003]
    3. Mechanism according to claim 1 or 2, wherein each tooth of the synchronous toothings (44, 46; 70, 72) comprises flanks (64a, 64b) having in cross section a convex profile and cooperating with the faces (60a, 60b) planes of the teeth of the teeth (24, 26) of the rollers.
    [0004]
    4. Mechanism according to any one of the preceding claims, wherein the faces (60a, 60b) planes of each tooth of the teeth (24, 26) of the rollers are symmetrical to each other with respect to a median radial plane of said tooth passing through an axis (20a) of elongation of said roller.
    [0005]
    5. Mechanism according to any one of the preceding claims, wherein the faces (60a, 60b) planes vis-à-vis in the circumferential direction of adjacent teeth of the teeth (24, 26) of each roller are interconnected by a concave bottom (60d).
    [0006]
    6. Mechanism according to any one of the preceding claims, wherein each roller (20) comprises a groove (32, 34) located axially between the thread (22) and each toothing (24, 26).
    [0007]
    7. Mechanism according to any one of the preceding claims, comprising rings (40, 42) fixed on the nut (16) and each comprising one of the teeth (44, 46) of synchronization.
    [0008]
    8. Mechanism according to any one of claims 1 to 6, wherein the teeth (44, 46) of synchronization are formed on the nut (16).
    [0009]
    9. Mechanism according to any one of claims 1 to 6, wherein the teeth (70, 72) of synchronization are formed on the screw (12).
    [0010]
    10.Mechanism according to any one of claims 1 to 6, comprising crowns fixed on the screw (12) and each comprising one of the teeth (70, 72) of synchronization.
    [0011]
    An actuating actuator comprising a rotary drive means and a roller screw mechanism according to any one of the preceding claims, the mechanism screw being coupled to the driving means.
    [0012]
    12. A method of manufacturing a roller screw mechanism roller comprising an external thread and two external teeth arranged axially on either side of said threading, characterized in that it comprises steps of removing material from the thread. using at least one radial action tool to form the outer teeth so that the outer diameter of each toothing is smaller than the thread root diameter of the outer thread and each tooth of said toothing comprises planar faces.
    [0013]
    The method of claim 12, wherein the steps of removing material to form the outer teeth of the roll are performed simultaneously with the material removal steps to form the outer thread of said roll.
    [0014]
    14.Procédé according to claim 12 or 13, wherein the steps of removing material to form the external teeth and / or to form the external thread are made by rolling.
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    CN105465314B|2020-02-07|
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    引用文献:
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    EP1918612A1|2005-08-23|2008-05-07|Toyota Jidosha Kabushiki Kaisha|Planetary device for conversion between rotary motion and linear motion|
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    CN103939552B|2014-05-08|2016-05-18|黄溧震|The helical pitch controlled planetary roller screw that moves|EA020935B1|2012-05-11|2015-02-27|Зао "Диаконт"|Electromechanical driving actuator with damping device|
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    CN106270823A|2016-09-30|2017-01-04|东莞市健旺五金制品科技有限公司|A kind of screw rod Rapid milling device|
    JP6531748B2|2016-11-18|2019-06-19|トヨタ自動車株式会社|Motion conversion mechanism and electric brake actuator using the same|
    CN107524772A|2017-08-21|2017-12-29|北京精密机电控制设备研究所|A kind of big stroke planetary roller screw pair|
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    CN111015157B|2019-12-18|2021-05-11|浙江辛子精工机械有限公司|Assembling method of closed roller screw mechanism|
    法律状态:
    2015-09-30| PLFP| Fee payment|Year of fee payment: 2 |
    2016-04-01| PLSC| Search report ready|Effective date: 20160401 |
    2016-09-28| PLFP| Fee payment|Year of fee payment: 3 |
    2017-10-02| PLFP| Fee payment|Year of fee payment: 4 |
    2018-09-28| PLFP| Fee payment|Year of fee payment: 5 |
    2019-09-23| PLFP| Fee payment|Year of fee payment: 6 |
    2020-09-21| PLFP| Fee payment|Year of fee payment: 7 |
    2021-09-27| PLFP| Fee payment|Year of fee payment: 8 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1459199A|FR3026454B1|2014-09-29|2014-09-29|ROLLER SCREW MECHANISM AND METHOD OF MANUFACTURING THE SAME|FR1459199A| FR3026454B1|2014-09-29|2014-09-29|ROLLER SCREW MECHANISM AND METHOD OF MANUFACTURING THE SAME|
    CN201510611547.XA| CN105465314B|2014-09-29|2015-09-23|Roller screw mechanism and related manufacturing method|
    ITUB2015A003824A| ITUB20153824A1|2014-09-29|2015-09-23|ROLLER SCREW MECHANISM AND ASSOCIATED MANUFACTURING PROCEDURE|
    US14/864,933| US10018257B2|2014-09-29|2015-09-25|Roller screw mechanism and associated manufacturing method|
    DE102015218621.0A| DE102015218621A1|2014-09-29|2015-09-28|Thread rolling mechanism and associated manufacturing process|
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