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WO2012160149A1 - Concept pour un écrou de vis d'entraînement à roulements - Google Patents

Concept pour un écrou de vis d'entraînement à roulements Download PDF

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Publication number
WO2012160149A1
WO2012160149A1 PCT/EP2012/059738 EP2012059738W WO2012160149A1 WO 2012160149 A1 WO2012160149 A1 WO 2012160149A1 EP 2012059738 W EP2012059738 W EP 2012059738W WO 2012160149 A1 WO2012160149 A1 WO 2012160149A1
Authority
WO
WIPO (PCT)
Prior art keywords
thread
nut
spindle
rolling elements
return channel
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/EP2012/059738
Other languages
German (de)
English (en)
Inventor
Philipp Krebs
Ralph MEEUWENOORD
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SKF AB
Original Assignee
SKF AB
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 SKF AB filed Critical SKF AB
Priority to EP12724119.8A priority Critical patent/EP2715187A1/fr
Publication of WO2012160149A1 publication Critical patent/WO2012160149A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • F16H25/2204—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls
    • F16H25/2214—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls with elements for guiding the circulating balls

Definitions

  • the present invention is in the field of Wälzgewinderiose, in particular in the field of wear reduction of the components of Wälzgewinderiosen and their noise optimization.
  • Wälzgewindetriebe or Wälzschraubtriebe such as ball screws (KGT as a shortcut)
  • Wälzschraubtriebe such as ball screws (KGT as a shortcut)
  • Balls are used.
  • KGT are used in machine tools, such. As lathes on which workpiece or tool carrier must be positioned used. The component to be moved can be fastened to the nut and additionally supported by linear guides. KGT are also used for example in presses, injection molding machines and power steering systems.
  • a rolling screw drive comprises a spindle with a thread, a nut with threads and rolling elements, which are in the threads of the nut with the thread of the spindle engaged.
  • a motor can then drive the spindle either directly or via a gearbox.
  • rolling elements can be located between the spindle and nut in grooves or threads, for example, balls that change their axial position when turning the spindle. When the nut now moves a few turns, the balls reach the ends of the threads of the nut and would fall out at the end of the nut. Therefore, they will have one Return or a return channel again introduced elsewhere courses. The return channel in or on the spindle nut moves the balls back again, thus closing a circuit in which the balls circulate.
  • the Wälzgroper can also be cylindrical, barrel-shaped, conical, etc., the return channels are then adapted accordingly to the rolling elements.
  • the rolling elements are therefore loaded when introduced into the threads and relieved when exiting the threads again. After emerging from the threads, the rolling elements are no longer driven between the spindle and nut, but move partly by the entrained kinetic energy from the threads and partly by mutual pushing through the exiting from the threads rolling elements. Upon re-entry into the thread and thus in the loading area, the rolling elements are slightly compressed, which leads to a deformation at the contact points. The resulting forces can be particularly high when thread and return channel are not optimally aligned with each other. The necessary forces are then applied by the respectively following rolling element. As a result, there may be uncontrolled movements of the rolling elements in the return channel, which vibrations and corresponding audible noise may occur. When the rolling elements pass from the loaded to the unloaded state upon leaving the thread, they can bounce at high speed against the wall of the return channel or the rolling elements in the return channel. This can lead to vibrations and thus to a noise,
  • the vibrations also have the consequence that it can lead to increased wear of the rolling elements and the running surfaces in the thread and in the return channel. It is therefore the object of the present invention to provide an improved Wälzgewindetechnisch.
  • Embodiments of the present invention are based on the recognition that the vibration characteristics of a Wälzgewindetriebes can be influenced by the fact that the shape of the threads and the return channel are adjusted accordingly.
  • the guidance of the rolling elements can be influenced in such a way that the vibrations can be reduced.
  • Embodiments provide a nut or spindle for a rolling screw drive, characterized in that the nut or the spindle comprises a thread which is adapted to guide rolling elements along a thread of the spindle or the nut such that the rolling elements are engaged with the thread and a power transmission between the nut and the spindle is generated.
  • the thread is formed to supply the Wälzköper a return channel to receive the rolling elements from the return channel, and to relieve the rolling elements before returning to the return channel of the power transmission and / or to the rolling elements after receiving the return channel with the Load power transmission.
  • balls, rollers, ball rollers, cones, etc. may occur as rolling elements.
  • embodiments also include inverted ball screws, in which the nut is designed as a comparatively long pipe with internal thread and the spindle has only a few threads.
  • the return channels are arranged on the spindle, that is, the rolling elements are then led away inwardly from the thread of the nut.
  • Embodiments include nuts in which the return channel is provided by a further part and also nuts with integrated exclusively by mechanical processing return channel. In other words, interiesbeam the mother and the return channel can also be integrally formed.
  • embodiments may also include spindles, which are adapted for inverse Wälzgewindetriebe, in which the return channel is provided by a further part and spindles with integrated exclusively by mechanical processing return channel.
  • the spindle and the return channel can also be integrally formed.
  • Embodiments may further be based on the recognition that the cross-section of a thread need not be constant in the course of the thread, but instead the depth or diameter of the thread may be increased away from the spindle toward the ends of the thread. In the case of an inverted Wälzge winch drove s, the depth or diameter of the thread can be increased to the axis of rotation towards the ends of the thread out.
  • the thread may have a depth indicating the extent of the thread in the radial direction, wherein the depth of the thread increases at least at one end of the thread.
  • the thread may widen towards its ends, ie its diameter or depth may increase. This can be the case at both ends of the thread, in embodiments may be an expansion of the thread on the input side and / or output side.
  • the thread may have an expanded entry region for the rolling elements and / or an expanded exit region for the rolling elements.
  • the depth of the thread can change abruptly or continuously. In some embodiments, the depth profile may be ramped, ie, linearly increasing falling between an inner (the power transmission enable outer (the power transmission not enabling) level run.
  • the power transmission between the nut and the spindle in the axial direction along the axis of rotation of the nut can take place.
  • Embodiments of the present invention are further based on the finding that the position at which the rolling elements are loaded or unloaded can be shifted into the thread in through the widening of the thread. Thus, the exact alignment between the return channel and the thread loses importance, because the transition from thread to return channel or vice versa can now be done in the unloaded area.
  • the thread can therefore be designed to guide the rolling element in a central region so that the force transmission between the nut and the spindle is formed. For example, this can be done by the rolling elements in the thread of the nut and in the thread of the spindle have one or more points of contact, then the force is transmitted.
  • the thread may be formed in an outer region in order to release the power transmission and to relieve the rolling elements or within the thread or load.
  • a cross section of the thread may be formed funnel-shaped at least at one of its ends, it being noted that the thread of the nut together with the thread of the spindle forms a channel with an at least approximately circular cross-section, if it is in the rolling elements to balls ,
  • the cross section of the thread of the nut or the spindle can be approximately semi-circular.
  • a funnel-shaped expansion or expansion is thus based on the cross-section of a thread of the nut, if this leads the rolling elements and on the thread of the spindle, when the spindle carries the rolling elements (inverted Wälzgewindetrieb).
  • the thread gang has an at least approximately semicircular cross-section whose radius increases towards at least one end.
  • embodiments may be based on the core idea that the application of the load to the rolling elements can be carried out gradually by a corresponding shaping of the thread.
  • the thread may have a tread that is farther from the axis of rotation or axis of symmetry of the nut at least at one end of the thread in the radial direction than at a central portion of the thread in the case of a regular pitch.
  • the thread of the spindle may have a running surface which is closer to at least one end of the thread in the radial direction at the axis of rotation or axis of symmetry of the spindle than in a central region of the thread.
  • the running surface can thus run in the form of a ramp and gradually move further away from the axis of rotation or approach the axis of rotation (inverted rolling screw drive).
  • rotation axis represents a definition of the axis of symmetry or the axis of rotational symmetry of those components which can rotate relative to each other.
  • the load on the rolling elements can be increased in a controlled manner when entering the thread or lowered controlled at the exit.
  • the load of the rolling elements can be slowly increased after they have entered the thread, and are slowly lowered before the rolling elements leave the thread in the direction of the return channel again.
  • Embodiments may also include a drive with a nut as described above.
  • Embodiments may thus also include a method for operating a Wälzgewindetriebs with a spindle, rolling elements and a nut, wherein the nut has a thread and a return channel for the rolling elements.
  • the method comprises introducing the rolling elements from the return channel into the thread and loading the rolling elements in the thread.
  • the method further comprises relieving the rolling elements in the thread and applying the relieved rolling elements from the thread in the return channel.
  • Embodiments may therefore be based, in particular, on the knowledge that the gradual unloading of the rolling elements in the relief zone can prevent the rolling elements from being ejected out of the loading region. As a result, it can also be avoided in the sequence that the rolling elements shoot out of the load area into the return channel, and thus shocks and pulse transmissions, which are decisive for the vibrations, can be avoided. Embodiments can reduce the force required to enter the rolling elements in the thread, and thus reduce the formation of shocks and pulse transmissions in the inlet area.
  • Embodiments can thus provide a rolling screw, in the noise and vibration development, due to the unloaded entry of the rolling elements in the thread and due to the non-sudden reduction of the load, are reduced. As a result, a reduced wear on the rolling elements, the thread and the return channel can be adjusted.
  • the manufacturing costs of the Wälzge can wind s drive can reduce, after the accuracy requirements can be reduced to the entry and exit area of the thread.
  • the tolerance limits can be increased during assembly, as can be dispensed with a highly accurate tuning of the thread with the return channel.
  • FIG. 1 a is a depth diagram of an exemplary embodiment
  • Figure lb an embodiment of a nut with a funnel-shaped thread
  • Figure 3 is a comparison of simulation results of an embodiment with the prior art.
  • the figure la shows a depth diagram of a thread of a nut or a spindle for a ball screw. It is assumed that the balls in the thread once completely rotate the spindle, ie that they pass through an angular range of 360 ° in the thread around the spindle. As a result, the thread itself also extends over this angular range.
  • the angle of revolution is plotted on the abscissa in degrees about the spindle, which covers a range of 0-360 °. covers.
  • a depth difference in ⁇ is assumed contracted that the depth of zero corresponds to the distance within the thread, ie the distance from the axis of rotation of the spindle, in which the power transmission from the spindle to the mother takes place.
  • the depth ie the distance to the axis of rotation becomes larger.
  • the balls would be led inwards and as a result the distance to the axis of rotation would decrease accordingly.
  • the distance to the axis of rotation of the spindle by about 50 ⁇ larger (smaller for the case of the inverted ball screw).
  • This increase in the distance or the depth causes the power transmission in the inlet region and in the outlet region to decrease, so that the balls are relieved even before they are transferred to the return channel, or only charged after they return from the return channel in the thread were led.
  • the power transmission between the nut and the spindle can be effected in the axial direction along the axis of rotation of the nut and by means of or via the rolling elements.
  • the thread may have a tread which is at at least one end of the thread in the radial direction further away from the axis of rotation of the nut than in a central region of the thread.
  • the thread may have a depth which indicates the extent of the thread in the radial direction away from the axis of rotation of the nut, wherein the depth of the thread increases at least at one end of the thread. In the case of an inverted ball screw, the tread or its depth changes in the other direction.
  • FIG lb an embodiment of a nut with a funnel-shaped thread 1 10 is shown, wherein the figure lb the thread 1 10, the rolling body 120 and the thread gang 130 of the spindle shows.
  • the Gew is adapted to guide rolling elements 120 along a thread of a spindle such that the Wälzköper 120 are in engagement with the thread of the spindle and a power transmission between the nut and the spindle is generated.
  • the thread 1 10 is formed to supply the Wälzköper 120 a return channel and to receive the rolling elements 120 from the return channel.
  • the thread 1 10 relieves the rolling elements 120 before returning to the return channel of the power transmission and / or loaded the rolling elements 120 only after receiving the return channel with the power transmission.
  • the figure lb shows in the upper part of an inlet or outlet region of the thread 1 10 of an embodiment.
  • Figure lb illustrated in the upper region of the rolling elements 120, wherein only one rolling element is provided with a reference numeral, which enter the thread or a 10 10.
  • the thread in the sense of a tunnel, results only in an interaction of the thread 1 10 on the nut and a counterpart of a thread 130 on the spindle.
  • the figure lb shows in the lower part of a principle sketch, in which the semicircular threads 1 10, 130 of the nut and the spindle are shown.
  • the thread 1 10 of the nut expands, insofar forms a funnel-shaped, semi-circular cross-section.
  • a rolling element 120 will initially have a clearance when entering, before it is then transferred along the tapered thread 1 10 into the frictional connection.
  • the conditions reverse accordingly and the cross section of the thread of the spindle changes in a funnel shape.
  • the thread 1 10, or in the thread of the spindle in the inverted ball screw also have a "Gothic Arc" profile, as occurs for example in four-point bearings.
  • This profile allows a support of the rolling elements at four points during lying two each in the thread gangway 1 10 of the nut and the C of the spindle.
  • the cross-section of this profile results from two overlapping circular arcs, the centers of which can be at a distance from one another and which can have the same radii. The distance causes the two circular arcs do not complement each other to a semicircle, to which a rolling element could fit snugly, but rather that two defined contact points arise.
  • the thread 1 10 may thus be designed to guide the rolling elements 120 in a central region so that the force transmission between the nut and the spindle is formed.
  • the thread 1 10 may be formed in at least one outer region to release the power transmission and to relieve the rolling elements 120 still within the thread 1 10 or to burden.
  • the cross section of the thread 1 10 may be formed at least at one of its ends substantially semi-circular, funnel-shaped, or semi-funnel-shaped.
  • Embodiments may also include a ball screw with a nut or spindle as described above.
  • embodiments may also include a method of operating a ball screw with a spindle, rolling elements 120 and a nut, wherein the nut or the spindle has a thread 1 10 and a return channel for the rolling elements 120 include.
  • the method may include a step of inserting the rolling elements 120 from the return channel into the thread 1 10 and a step of loading the rolling elements 120 in the thread 1 10.
  • the method may include relieving the rolling elements 120 in the thread 1 10 and applying the relieved rolling elements 120 from the thread 1 10 in the return channel.
  • the figure lc illustrates two three-dimensional representations of a game of a Wälzgewindetriebs, wherein in the figure lc each of the thread 1 10 and the recess for the return channel 1 15 are shown.
  • the arrows illustrate the path or the path that the Wälzgroper describe.
  • the rolling elements can be assumed here again as balls, for the sake of clarity, the rolling elements are not shown in the figure lc.
  • the two representations of Figure lc show at the transition points between thread 1 10 and return channel, as the thread 1 10 slightly widened and so the rolling elements are relieved before entering the return channel. It should be noted that the widening of the thread has been greatly exaggerated here for clarity and in embodiments, the expansion can also be far less.
  • the thread in the area of the expansion, can expand by 0.1%, 0.5%, 1%, 5%, or 10% compared to the area of the transmission.
  • the entry of Wälzköper in the thread 1 10 can take place in the same manner. This is also clarified by the figure lc when the rolling elements move in the opposite direction of the arrow. Here, the rolling elements then enter first in the expanded portion of the thread 1 10, before the thread tapers 1 10 and the rolling elements are loaded.
  • FIG. 2 shows three time profiles, wherein different quantities are shown over the same time axes.
  • the radial distance of the rolling elements 120 from the axis of rotation of the spindle is shown.
  • the sinusoidal curves show that the rolling elements 120 are brought to the spindle, remain there and then again be guided over the return channel of the spindle path.
  • the highlighted in Figure 2 areas 201, 202 and 203 mark those places where the rolling elements in the thread gang 1 10 of the mother enter, or exit.
  • the entry and exit points 201, 202 and 203, the radial accelerations are compared in the middle of the time in Figure 2, which experience the balls 120 at these points.
  • the points 21 1, 212 and 213 are highlighted, where it can be seen that just in the Entry and exit areas the accelerations are particularly high s jump-like accelerations arise, which can cause vibrations.
  • FIG. 3 shows a comparison of simulation results of an embodiment with the prior art.
  • FIG. 3 shows on the left side those courses which were simulated with the conventional technique, on the right side
  • FIG. 3 shows the diagrams which were simulated with an exemplary embodiment.
  • the upper two diagrams and the middle diagram illustrate again the distance of the balls 120 to the axis of rotation of the spindle.
  • the rolling bodies are guided one after the other away from the spindle and then back to the spindle. This happens when exiting from the thread 1 10 of the mother and when entering the return channel, or when exiting the return channel back into the thread 1 10 of the mother.
  • the accelerations measured for the individual rolling elements 120 are shown. As already explained with reference to FIG. 2, these arise mainly on entry and exit into the thread 1 10.
  • a comparison of the comparison in FIG. 3 shows that, with the exemplary embodiment, the accelerations acting on the rolling elements 120 are less than that was possible with conventional technology.
  • the bottom line of Figure 3 are already shown on the basis of the figure accelerations, which act on the mother in total. Again, it can be seen that the forces acting on the mother accelerations, so that the vibrations and ultimately the wear can be reduced with embodiments.
  • the average accelerations 231 are again indicated for the simulation results for the conventional technique and also for the simulation results for the exemplary embodiment. This also shows that they can be significantly reduced with embodiments.

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

Abstract

L'invention concerne un concept pour un écrou ou une broche pour vis d'entraînement à roulements, caractérisé en ce que ledit écrou ou ladite broche présente un pas de filet (110) conçu pour guider des corps de roulement (120) le long d'un filet de telle sorte que les corps de roulement (120) sont en prise avec le filetage de la broche ou de l'écrou et qu'il se produit une transmission de force entre l'écrou et la broche. Le pas de filet (110) est conçu pour amener les corps de roulement (120) dans un canal de retour et pour les faire sortir de ce canal. Le pas de filet (110) est également conçu pour que les corps de roulement (120) soient déchargés de la transmission de force avant leur retour dans le canal de retour et/ou pour que les corps de roulement (120) assurent la transmission de force seulement après leur sortie du canal de retour.
PCT/EP2012/059738 2011-05-25 2012-05-24 Concept pour un écrou de vis d'entraînement à roulements Ceased WO2012160149A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP12724119.8A EP2715187A1 (fr) 2011-05-25 2012-05-24 Concept pour un écrou de vis d'entraînement à roulements

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011076438.0A DE102011076438B4 (de) 2011-05-25 2011-05-25 Konzept für eine Mutter oder Spindel eines Wälzgewindetriebs
DE102011076438.0 2011-05-25

Publications (1)

Publication Number Publication Date
WO2012160149A1 true WO2012160149A1 (fr) 2012-11-29

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2012/059738 Ceased WO2012160149A1 (fr) 2011-05-25 2012-05-24 Concept pour un écrou de vis d'entraînement à roulements

Country Status (3)

Country Link
EP (1) EP2715187A1 (fr)
DE (1) DE102011076438B4 (fr)
WO (1) WO2012160149A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014006152A1 (fr) * 2012-07-06 2014-01-09 Schaeffler Technologies AG & Co. KG Vis d'entraînement à billes

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2946445T3 (es) 2020-09-22 2023-07-18 SFS Group International AG Mecanismo lineal de tipo bola y tuerca de husillo para ello

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11351350A (ja) * 1998-06-10 1999-12-24 Thk Co Ltd ボールねじ
JP2004162848A (ja) * 2002-11-14 2004-06-10 Nsk Ltd ボールねじ
US20050076733A1 (en) * 2003-10-14 2005-04-14 Favess Co., Ltd. Ball screw mechanism, machining method for joint between nut and ball circulation piece, and electric power steering device
US20050235766A1 (en) * 2001-08-03 2005-10-27 Nsk Ltd. Ball screw
DE102006011940A1 (de) * 2006-03-15 2007-09-27 Hiwin Technologies Corp. Rücklaufelement für eine Kugelumlaufspindel

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004025683A1 (de) * 2004-05-26 2005-12-15 Ina-Schaeffler Kg Spindelmutter für einen Kugelgewindetrieb

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11351350A (ja) * 1998-06-10 1999-12-24 Thk Co Ltd ボールねじ
US20050235766A1 (en) * 2001-08-03 2005-10-27 Nsk Ltd. Ball screw
JP2004162848A (ja) * 2002-11-14 2004-06-10 Nsk Ltd ボールねじ
US20050076733A1 (en) * 2003-10-14 2005-04-14 Favess Co., Ltd. Ball screw mechanism, machining method for joint between nut and ball circulation piece, and electric power steering device
DE102006011940A1 (de) * 2006-03-15 2007-09-27 Hiwin Technologies Corp. Rücklaufelement für eine Kugelumlaufspindel

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014006152A1 (fr) * 2012-07-06 2014-01-09 Schaeffler Technologies AG & Co. KG Vis d'entraînement à billes
US9746059B2 (en) 2012-07-06 2017-08-29 Schaeffler Technologies AG & Co. KG Ball screw drive

Also Published As

Publication number Publication date
DE102011076438A1 (de) 2012-11-29
EP2715187A1 (fr) 2014-04-09
DE102011076438B4 (de) 2020-03-12

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