WO2013127571A1 - Vis d'entraînement à roulement planétaire et procédé de fabrication d'une telle vis - Google Patents

Vis d'entraînement à roulement planétaire et procédé de fabrication d'une telle vis Download PDF

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Publication number
WO2013127571A1
WO2013127571A1 PCT/EP2013/051269 EP2013051269W WO2013127571A1 WO 2013127571 A1 WO2013127571 A1 WO 2013127571A1 EP 2013051269 W EP2013051269 W EP 2013051269W WO 2013127571 A1 WO2013127571 A1 WO 2013127571A1
Authority
WO
WIPO (PCT)
Prior art keywords
ring
nut
spindle
profile
planetenwälzgewindetrieb
Prior art date
Application number
PCT/EP2013/051269
Other languages
German (de)
English (en)
Inventor
Bernd EICHENHÜLLER
Matthias Dohr
Thomas Motz
Original Assignee
Schaeffler Technologies AG & Co. KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Priority to CN201380011459.5A priority Critical patent/CN104145138B/zh
Publication of WO2013127571A1 publication Critical patent/WO2013127571A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/22—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
    • F16H25/2247—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with rollers
    • F16H25/2252—Planetary rollers between nut and screw
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/22—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members

Definitions

  • the present invention relates to a Planetenskylzgewindetrieb that converts a relative rotation between a threaded spindle and a Spindelmuler arranged thereon in an axial relative displacement between the threaded spindle and the spindle nut.
  • a planetary roller screw drive has become known, with a spindle nut arranged on the threaded spindle » and with several planets distributed over the circumference of the spindle nut.
  • the spindle nut has a support body and disposed in the support body rings, which are respectively provided on the inner circumference with a nut-side groove profile for engagement of a planetary side groove profile of the planet
  • the multi-part construction of the spindle nut enables economical provision of the nut-side groove profile, which is often formed by a plurality of pitch-free grooves, which are arranged axially behind one another and parallel to each other.
  • the grooves are self-contained, so endless, and arranged transversely to the spindle nut axis.
  • the pitch - so the distance from groove to groove - and the groove depth can be designed differently depending on the size of the Planetenéelzgewindetriebes.
  • the object of the present invention was to provide a planetary roller screw, which is easy to assemble. According to the invention, this object has been achieved by the planetary screw drive according to claim 1. Characterized in that a wall thickness of the ring is less than four times and at least as large as 1, 5 times the profile height h of the nut side groove profile, the ring can be elastically and / or plastically deformed; this ability of - compared to known rings - thin-walled ring according to the invention allows its incorporation into the supporting body in spite of hardening distortion after a heat treatment. Depending on the hardness distortion can be experienced as a result of a pressing of the rings in addition to an elastic in addition to a plastic deformation and brought into its round shape. A hardening delay is accepted, a costly reworking of the hardened rings can be omitted.
  • the wall thickness corresponds to half the diameter difference of the
  • the support body may be provided at its ends in each case with a cylindrical bearing seat, wherein the ring is provided as a floating bearing or as a fixed bearing. If the ring is no longer round due to hardness distortion but somewhat deformed, for example oval, the ring provided as a fixed bearing is forced into its cylindrical bearing seat in its round shape during pressing, the thin-walled design of the ring - in the inventive ratio of wall thickness and profile height allows them Deformation.
  • the ring has a lower rigidity than the support body.
  • Rings with large outer diameters between 80 mm to 100 mm or larger can have a greater wall thickness in the upper region within the ranges according to the invention; Rings with small outside diameters between 15 mm and 40 mm can have a smaller wall thickness in the lower region within the regions according to the invention.
  • the wall thickness is according to the invention provide as "that in cases of an unwanted hardness delay a reverse deformation in the round shape is perfectly possible. All rings are common » that a small wall thickness is provided in relation to the profile height, which allows a deformation of a hardening distortion in the range according to the invention.
  • the ring may be arranged with sufficient play in the bearing seat. This game can be at one
  • the planets are distributed over the circumference. They are provided in their central region with so-called feed ribs, which are in rolling engagement with a thread of the threaded spindle.
  • the planets have at their two ends in each case so-called guide grooves, which are in rolling engagement with the nut-side grooves.
  • the planets run perfectly in the spindle nut on a circular path around the lockers! and around the spindle nut.
  • the rings are consequently shaped into their round shape.
  • a round shape in the sense of the invention makes it possible to roll the planets on the spindle nut along a circular path around the spindle nut axis.
  • a further advantage of the invention can be seen in the fact that weight savings are associated with planetary roller screw drives according to the invention; because the rings of the invention are thinner than the known rings. Especially in automotive applications, this is
  • the grooves provided on the rings can be rolled with great accuracy and tight tolerances .
  • the ring is arranged in a rolling gap of the tool and can be rolled with high accuracy in width, thickness and profiling. In particular, a constant thickness over the circumference is important for the functionality of the rings in Planetenskylzgewindetrieb.
  • the final contour of the ring is produced, ie the outside diameter and the pitch circle diameter for the planets.
  • the profile height h can be between 0.4 mm and 3 mm in planetary roller screw drives according to the invention, including these values.
  • rings according to the invention can have a wall thickness between about 2.2 mm and about 6 mm, depending on the outside diameter range ,
  • Planetary roller screw drives according to the invention have rings. their profile height
  • 0.6 mm may be for assemblies with a spindle diameter between 5 mm and 25 mm, wherein the pitch of the grooves can be 1, 03 mm in this case.
  • the profile height can be 0.8 mm, whereby the pitch of the grooves can be 1.35 mm.
  • the profile height can be 1, 2 mm , wherein the pitch of the grooves may be 2 mm.
  • the wall thicknesses for the mentioned assemblies are between about 1 mm and less than 5 mm , wherein the largest wall thicknesses is provided at the largest assembly.
  • the nut-side groove profile may have a plurality of annularly closed grooves arranged axially one behind the other and parallel to each other, wherein a groove is bounded by adjacent teeth of the ring, and wherein the teeth extend radially outward to a groove bottom and radially inward to a tooth tip , and wherein the profile height is given by the radial distance from the tooth tip to the groove bottom.
  • the pitch circle diameter is between the groove bottom diameter and the tooth tip diameter.
  • the tooth tip and the groove bottom may each have a radius of curvature of 0.1 mm to 0.5 mm inclusive, wherein the radius of curvature of the tooth tip is greater than the radius of curvature of the groove bottom.
  • the radius of curvature of the groove bottom is matched to the radius of curvature of the tooth tip of the engaging teeth. Rings with large outside diameters may have radii of curvature at the tooth tips and groove bottoms at the top of the specified range. The radius of curvature can be matched to the intended groove pitch.
  • the groove profile may have a plurality of endless grooves arranged axially one behind the other and parallel to one another, the pitch of which may be 0.8 mm to 4 mm.
  • the ring can have a width "which is at least three times the groove pitch of the groove profile and a maximum of eleven times the groove pitch.
  • a clear inner diameter of the ring may be between 14 mm and 150 mm, including these values.
  • the clear inner diameter may be limited by the tooth tips of the groove profile.
  • the support body can be seen in the direction of a spindle axis provided at its two axial ends with one of the rings, wherein the support body has a receptacle for each ring, and wherein the one ring as a fixed bearing and the other ring as a floating bearing in the receptacle of the support body is arranged.
  • the receptacle is preferably designed as a bore height (cylindrical, it can be provided on its end-facing side with an inlet chamfer for insertion of the ring.)
  • the other end of the receptacle may be limited by a shoulder.
  • An inventive Planetenxxlzgewindetrieb can be prepared according to the following steps: providing a ring blank with cylindrical surfaces, rolling the nut side groove profile to the inner circumference of
  • Ring blanks and subsequent hardening in a heat treatment process insertion of the rings in the support body. Further processing of the rings can unfold.
  • the rolling of the groove profile allows the production of rings, which advantageously in terms of friction reduction of the rolling engagement standing Wälzpartner are optimized: the rolled profiles spring back elastic, so that the tooth flanks have a slight Beautymaschine; this means that in the rolling contact a point contact with less friction is guaranteed.
  • Forming in the rolling process permits economical manufacture of the rings, their complex profile can be highly accurately shaped "wherein a more favorable for the use of the rings in a Planetenskylzgewtndetrieb fiber orientation is achieved in the ring.
  • the ring blank can be made by deep drawing from sheet metal or by means of cutting
  • a ring blank may also serve a pipe section which is divided out of a pipe.
  • the one provided as a fixed bearing ring can be in a vo r preferably hollow-cylindrical receptacle of the support body pressed in, and the other as a movable bearing provided ring can be inserted axially displaceable in the other receptacle of the supporting body.
  • the one ring can be elastically and / or plastically deformed by pressing into the receptacle and brought into its round shape.
  • the support body is made significantly stiffer than the ring, so that the receptacle retains its cylindrical shape during the pressing.
  • the other ring can be brought into its round shape by conditioning the arranged on the spindle periphery planet on the inner circumference of the ring.
  • the planets are distributed equidistantly over the circumference of the threaded spindle and define points on the pitch circle.
  • the elastically deformable ring can be supported and receives its round shape, a circular shape,
  • FIG. 2 shows a detail enlargement from FIG. 1.
  • Figure 1 shows a Planetenskylzgewindetrieb invention in longitudinal section.
  • a spindle nut 2 is arranged on a threaded spindle 1.
  • a spindle nut 2 is arranged on a threaded spindle 1.
  • the planet 3 roll on the outer circumference of the threaded spindle 1 and on the inner circumference of the spindle nut 2 from.
  • the spindle nut 2 is designed in several parts.
  • two rings 5.6 aKialbeweglieh are arranged to each other.
  • One intended as a fixed bearing ring 5 can be pressed into a formed at one end of the support body 4 hollow cylindrical receptacle 7, and the other provided as floating bearing ring 6 can be inserted axially displaceable in a formed at the other end of the supporting body 4 receptacle 8 of the support body 4, wherein the other ring 6 is arranged with a transition fit in the other receptacle 8.
  • the ring 6 is axially sprung in this embodiment via a plate spring 9. This springing can be omitted in other Planetenannalzgewindetrieben invention.
  • the rings 5, 6 are provided on their inner circumference with a nut-side groove profile 10, 1 1, each having a plurality of axially successively and mutually parallel, annularly closed grooves 12, 13.
  • the grooves 12, 13 are arranged transversely to the spindle nut axis; they are stepless.
  • the grooves 12, 13 are bounded by adjacent teeth 14, 15 of the ring 5, 6.
  • the following description of the ring 10 also applies to the ring 1 1,
  • the teeth 14 extend radially outward as far as a groove bottom 16 and radially inward as far as a tooth tip 17.
  • the radial distance from the tooth tip 17 to the groove bottom 16 denotes the profile height "h" of the groove profile 10.
  • the tooth tip 17 has a radius of curvature of 0.2 mm and the groove bottom has a radius of curvature of 0.1 mm.
  • the radius of curvature of the tooth tip is larger than the radius of curvature of rings according to the invention Grooved floor » so that so-called head support can be avoided, in which the teeth are loaded unduly in the head area.
  • the distance from adjacent grooves 12 is in the exemplary embodiment 2 mm, wherein the distance from tooth tip 17 to tooth tip 17 is measured. This distance can also be referred to as groove pitch "t".
  • the ring 5 has a width "b" which is about 10 times the groove pitch
  • the ring 6 has a width "b" which is about three times the groove pitch "t"
  • the clear inner diameter of the rings 5, 6 is determined by the inner diameter "d.”
  • the outer diameter of the rings 5, 6 is denoted by “d a ".
  • the half of the difference of ".d a " and “df” denotes a wall thickness "s" of the rings 5. 6.
  • the wall thickness "s" is about 2 mm, the inside diameter "d,” about 55 mm Profile height “h” 0.8 mm, and the pitch "t" 1, 35 mm. These values have not been scaled in the figures for better representability.
  • the rings 5, 6 are made of a ring blank provided with cylindrical lateral surfaces. At the ring blank, the nut-side groove profile 10 is rolled in the ring rolling known per se. Due to the rolling material flows together at the tooth tip 17, so that a so-called Schf dirtfalte arises, which is a slight circumferential notch on the tooth tip 17. Subsequently, the rings 5, 6 are cured in a heat treatment process. As a result of curing, the rings 5, 6 undergo a hardening delay and are deformed from their round shape into an oval shape. When the rings 5, 6 are used in the planetary roller screw, the inventively designed rings 5, 6 again have their round shape.
  • the ring 5 is deformed by pressing into the hollow cylindrical receptacle 7 and brought into its round shape.
  • the support body 4 is compared to the rings 5, 6 significantly stiffer and is not deformed by the pressing.
  • the ring 5 can be deformed both elastically and plastically. However, in be ensured in each case that the groove profile 10 properly cooperates with the planet 3.
  • the other ring 6 is arranged with radial clearance in the hollow cylindrical receptacle 8.
  • the evenly distributed over the circumference arranged planet 3 are supported on the one hand radially on the threaded spindle 1 and on the other hand on the rings
  • the teeth 17 of the rings 5, 6 engage in guide grooves 18 of a planetary side groove profile 19 of the planet 3 a.
  • the thread of the threaded spindle 1 engages in feed grooves 20 planet-side groove profile 19 a. Since the threaded spindle 1 and the planet 3 are made with high precision » roll the planet 3 on a perfect circular path around the threaded spindle 3 from around.
  • the annular space between the ring 6 and the threaded spindle 1 is dimensioned so that the planet 3 have only a slight radial play.
  • the planet 3 force the brought by hardening distortion in a non-circular shape ring 6 consequently in its round shape.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)

Abstract

L'invention concerne une vis d'entraînement à roulement planétaire, comportant une broche filetée (1) et un écrou (2) situé sur la broche filetée (1), et plusieurs engrenages planétaires (3) répartis sur la périphérie de l'écrou (2). L'écrou (2) comporte un corps de support (4) et une bague (5, 6) située dans le corps de support (4) et comportant, sur sa circonférence intérieure, un profilé rainuré (10, 11) situé côté écrou, pour venir en prise avec un profilé rainuré (19) des engrenages planétaires (3), l'épaisseur de paroi (s) de la bague (5, 6) étant inférieure à quatre fois celle de la hauteur (h) du profilé rainuré (10, 11) situé côté écrou et au moins aussi épaisse qu'une fois et demie cette hauteur.
PCT/EP2013/051269 2012-02-28 2013-01-24 Vis d'entraînement à roulement planétaire et procédé de fabrication d'une telle vis WO2013127571A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201380011459.5A CN104145138B (zh) 2012-02-28 2013-01-24 用于制造行星滚子螺纹传动装置的方法

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102012203040 2012-02-28
DE102012203040.9 2012-02-28
DE102012204038.2 2012-03-15
DE201210204038 DE102012204038A1 (de) 2012-02-28 2012-03-15 Planetenwälzgewindetrieb

Publications (1)

Publication Number Publication Date
WO2013127571A1 true WO2013127571A1 (fr) 2013-09-06

Family

ID=48950853

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2013/051269 WO2013127571A1 (fr) 2012-02-28 2013-01-24 Vis d'entraînement à roulement planétaire et procédé de fabrication d'une telle vis

Country Status (3)

Country Link
CN (1) CN104145138B (fr)
DE (1) DE102012204038A1 (fr)
WO (1) WO2013127571A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112032268B (zh) * 2020-08-24 2023-11-24 江西沃德成科技有限公司 一种行星滚柱丝杠用滚柱及其制造方法
CN113987717B (zh) * 2021-11-16 2024-03-26 重庆大学 一种行星滚柱丝杠公差优化设计方法

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR83127E (fr) * 1962-02-21 1964-06-19 Tech Integrale Dispositif de transformation d'un mouvement de rotation en mouvement de translation de très faible avance par tour
DE19646339A1 (de) * 1996-11-09 1998-05-14 Schaeffler Waelzlager Ohg Vorrichtung zur Umwandlung einer Drehbewegung in eine Axialbewegung
DE102010011820A1 (de) 2010-03-18 2011-09-22 Schaeffler Technologies Gmbh & Co. Kg Planetenwälzgewindetrieb

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2179289A5 (fr) * 1972-04-05 1973-11-16 Tech Integrale
EP0331761A1 (fr) * 1987-11-10 1989-09-13 Rollvis S.A. Mécanisme de taraud à rouleaux satellites
FR2699633B1 (fr) * 1992-12-17 1995-03-10 Aerospatiale Mécanisme de vis à rouleaux, notamment pour engin spatial, et actuateur linéaire comportant un tel mécanisme.
CN2628807Y (zh) * 2003-07-29 2004-07-28 西南交通大学 行星滚柱丝杆副

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR83127E (fr) * 1962-02-21 1964-06-19 Tech Integrale Dispositif de transformation d'un mouvement de rotation en mouvement de translation de très faible avance par tour
DE19646339A1 (de) * 1996-11-09 1998-05-14 Schaeffler Waelzlager Ohg Vorrichtung zur Umwandlung einer Drehbewegung in eine Axialbewegung
DE102010011820A1 (de) 2010-03-18 2011-09-22 Schaeffler Technologies Gmbh & Co. Kg Planetenwälzgewindetrieb

Also Published As

Publication number Publication date
DE102012204038A1 (de) 2013-08-29
CN104145138B (zh) 2018-08-10
CN104145138A (zh) 2014-11-12

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