WO2009071502A1 - Guide linéaire avec amortisseur de vibrations - Google Patents

Guide linéaire avec amortisseur de vibrations Download PDF

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Publication number
WO2009071502A1
WO2009071502A1 PCT/EP2008/066505 EP2008066505W WO2009071502A1 WO 2009071502 A1 WO2009071502 A1 WO 2009071502A1 EP 2008066505 W EP2008066505 W EP 2008066505W WO 2009071502 A1 WO2009071502 A1 WO 2009071502A1
Authority
WO
WIPO (PCT)
Prior art keywords
carriage
guide
linear guide
pressure chamber
gap
Prior art date
Application number
PCT/EP2008/066505
Other languages
German (de)
English (en)
Inventor
Peter Lutz
Dietmar Rudy
Original Assignee
Schaeffler 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 Kg filed Critical Schaeffler Kg
Publication of WO2009071502A1 publication Critical patent/WO2009071502A1/fr

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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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C29/00—Bearings for parts moving only linearly
    • F16C29/002—Elastic or yielding linear bearings or bearing supports
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/005—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion using electro- or magnetostrictive actuation means
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
    • F16F15/0237—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means involving squeeze-film damping

Definitions

  • the present invention relates to linear guides, in which a carriage is arranged longitudinally displaceable on a guide rail.
  • a linear guide has become known according to the features of the preamble of claim 1.
  • the guide carriage has an upper and a lower carriage section, between which a gap is formed. Relative lateral displacements are possible between these two carriage sections in order to be able to compensate for positional tolerances, for example.
  • a lubricating film damper is formed in a further gap arranged between these two carriage sections.
  • the gap may typically be a few tens of microns in size.
  • a feed channel is connected to this gap, so that, for example, oil can be effortlessly and constantly transported into this gap to form the lubricating film damper.
  • Linear guides are predominantly used in production machines in the field of metal forming. In the continuous development of such linear guides whose power and dynamic limits are increasingly raised. As a result of this increase, the mass fractions to be moved must be significantly reduced. The omission of mass, however, causes an increased susceptibility to static deformations and, for example, regenerative chatter phenomena, which are due to vibrations that are due to the lighter components.
  • linear guides that are able to vibrate both statically and dynamically on the other hand, for example, to compensate for incorrect positioning by appropriate facilities on the linear guide.
  • the invention offers the advantage in that for an optionally required compensation of incorrect positioning on the one hand and a preferably dynamic vibration damping on the other hand is made possible by the same technical means.
  • the invention thus allows linear guides that are simple in construction, and where vibration damping and stroke adjustment are made possible by the same technical measures.
  • the gap may for example be filled with a hydraulic fluid, in which case the gap may be formed as a pressure chamber.
  • the pressure in the pressure chamber increases and the corresponding arrangement of the two carriage sections allows a stroke of the upper carriage portion relative to the lower carriage portion, for example by 70 microns.
  • a targeted vibration compensation can be generated via a suitable power unit with an appropriate control and regulation, so that in the pressure chamber targeted pressure oscillations are built up, which are opposite in an undesirable manner acting dynamic vibrations, so that a compensation is achieved, compared to a smooth running of the carriage allows the guide rail. Consequently, the described combinatorial effect of a stroke adjustment and a dynamic vibration damping can be achieved with simple means-for example hydraulic fluid-in the gap formed as a pressure chamber.
  • Alternative lifting devices of the invention provide for the use of piezoelectric materials disposed in the gap.
  • the directed deformation of a piezoelectric material forms microscopic dipoles within the unit cells; There is a shift in the charge centers.
  • the summation over all unit cells of the crystal leads to a macroscopically measurable electrical voltage.
  • Directional deformation means that the applied pressure does not act on all sides of the sample, but only on opposite sides, for example.
  • an electrical voltage for example, a crystal (or the component made of piezoceramic) can be deformed.
  • piezoelectric bodies can perform mechanical oscillations. In piezoelectric materials, these vibrations can be electrically excited on the one hand, on the other hand cause again an electrical voltage.
  • the frequency of the oscillation is only from the speed of sound and the dimensions of the piezoelectric body, the sound velocity is a material constant.
  • piezoelectric components are also suitable for oscillators.
  • the most important material parameter for the inverse piezo effect and thus for actuators is the piezoelectric charge constant. It describes the functional relationship between the applied electric field strength and the strain generated thereby.
  • the characteristic sizes of a piezoelectric transducer are different for the different directions of action.
  • the piezoelectric transverse and longitudinal effects result in three different basic elements for piezoelectric actuators: the thickness oscillator, the transverse expansion element, the bimorph.
  • the bimorph is a combination of two transverse expansion elements.
  • An opposite control of the elements causes a bending of the actuator, which is why this receives a separate name
  • the above-mentioned thickness vibrator is suitable for the present invention.
  • the deformation when applying a voltage can be used in the thickness vibrator as an actuator, which can also be referred to as a piezo-positioner.
  • a plurality of piezo positioners can also be arranged in the gap and, depending on the type of application, in parallel or series connection.
  • piezo positioners allow precise movements which, in the present case, can be used in particular for dynamic vibration damping in linear guides according to the invention.
  • the two car sections are shifted relative to each other in the lifting directions under the action of the active piezoelectric actuator. This shift can then be static, or dynamic.
  • an electroactive polymer may be used that can change its shape when an electrical voltage is applied.
  • suitable vibration dampers can be used, which are also suitable as a lifting device.
  • this pressure chamber may be variable in volume. It is possible by means of dynamic loading of the pressure chamber to set certain stroke frequencies as well as certain lifting amplitudes of the upper carriage section relative to the lower carriage section. This targeted adjustability can superimpose unwanted vibrations such that a smooth sliding of the carriage is made possible, while ensuring a certain stroke position.
  • the two carriage sections can be integrally connected to each other.
  • remaining web portions which connect the two carriage sections to one another are expediently made so thin-walled and flexible that an enlargement of the gap-for example by means of pressurization-is possible.
  • elastically deflectable wall sections can connect the upper carriage section to the lower carriage section in one piece.
  • these deflectable wall sections limit the pressure chamber. This means that no separate seals are required to keep the pressure chamber pressure-tight.
  • the carriage is preferably formed in cross-section approximately U-shaped, wherein two legs of the carriage are connected to each other via a floor, wherein the carriage with his two legs, the guide rail engages, and wherein the bottom is provided with the pressure chamber, which is bounded on both its longitudinal sides by a longitudinal direction of the guide carriage longitudinal bore, and wherein between an outer boundary surface of the guide carriage and each of the two longitudinal bores elastically deflectable wall portion is formed.
  • the longitudinal bores can be easily created in the carriage known per se, so that elastically deflectable wall sections are produced in the desired manner, in order to allow an elastic enlargement of the gap.
  • a longitudinal groove parallel to the longitudinal bore and open to the surroundings of the guide carriage can be formed which, together with the longitudinal bore, delimits at least a portion of the elastically deflectable band section.
  • This longitudinal groove is thus positioned so that it provides a suitable elasticity of the wall sections together with the longitudinal bore.
  • An alternative embodiment of the invention provides that the two car sections are formed by separate car parts, which are interconnected by means of expansion screws. In this case, these two car parts can limit the gap. Since, in this situation, the wall of the pressure chamber has a transition region from the lower carriage part to the upper carriage part, it may be expedient to provide a seal, in particular an O-ring, between the two carriage parts, which seals the pressure chamber to the surroundings of the guide carriage. Thus, the pressure chamber can be pressurized without this pressure undesirably enters the surroundings of the guide carriage.
  • a guide carriage which, seen in cross-section, is approximately U-shaped. is formed, wherein two legs of the carriage are connected to each other via a floor, wherein the guide carriage engages around the guide rail with its two legs, and wherein the bottom is provided with the pressure chamber, wherein the lower carriage part on its side facing the upper carriage part with a circumferential Is provided, and wherein the upper carriage member is provided with a flange for receiving the expansion bolts and with an engagement portion which engages in the bounded by the circumferential web receiving portion, wherein between the web and the engagement portion is a preferably endless O-ring for sealing the Pressure chamber is arranged opposite the surroundings of the carriage.
  • the pressure chamber is pressurized, takes place in the limited scope up to about 100 microns, a relative displacement of the two car parts to each other, this relative movement is made possible by an expansion of the expansion screws.
  • the expansion screws also offer the advantage of a high-precision guidance in the direction of the stroke, so that an undesirable tilting or jamming is excluded.
  • the screw axes of the expansion screws are preferably arranged parallel to the stroke direction of the upper carriage part with respect to the lower carriage part to allow the desired relative displacement between the two carriage parts by utilizing a desired elongation of the expansion screws.
  • FIG. 2 shows a representation as in FIG. 1, but with a modified carriage
  • FIG. 3 shows a representation as in FIGS. 1 and 2, but with a further guide carriage according to the invention
  • FIGS. 4 to 6 show different representations of a linear guide according to the invention, whose guide carriage is shown schematically in FIG. 1 and FIG
  • Figure 7 shows a schematic representation of a control circuit of the linear guide according to the invention.
  • FIGS. 4 to 6 illustrate a linear guide according to the invention with its essential components, while the special features according to the invention are specified in greater detail in FIGS. 1 to 3.
  • the linear guide according to the invention shown in FIGS. 4 to 6 has a guide carriage 1, which is mounted longitudinally displaceably on a guide rail 2. It can be seen from FIG. 5 that the guide jib 1 is roller-mounted on the guide rail 2 via rollers 3, these rollers 3 circulating in an endless manner in an endless roller channel 4.
  • FIG. 5 shows load sections 5 and return sections 6 of the endless roller channel 4. In the load section 5, the rollers 3 roll on raceways 7, 8 of the guide carriage 1 and the guide rail 2.
  • Figure 6 shows a perspective view of the carriage 1 without the guide rail.
  • FIG. 1 shows a schematic representation of a section through the guide carriage 1 along the line I - I of Figure 4.
  • the figure shows that the carriage 1 has an upper carriage section 9 and a lower carriage section 10, between which a gap 11 is formed is.
  • the gap 11 extends over at least the major part of the supporting structure of the guide carriage 1.
  • the lower carriage portion 10 is stiff and properly on the Guide rail guided without it may lead to undesirable relative displacements between the lower carriage portion 10 and the guide rail.
  • the upper carriage section 9 is also designed to be stiff and is not subject to any appreciable deformations during operation of such a linear guide.
  • the upper carriage section 9 is integrally connected by means of elastically deflectable wall sections 12 with the lower carriage section 10. These elastically deflectable wall sections 12 are bounded on the one hand by the outer contour of the guide carriage 1 and on the other hand by longitudinal bores 13 which are arranged in the longitudinal direction of the guide carriage in the edge region of the guide carriage 1.
  • the upper carriage section 9 is also provided on its longitudinal sides each with an outwardly open groove 14, so that the elastic wall portions 12 are limited by the longitudinal side of the carriage 1, and the groove 14 and further through the longitudinal bore 13.
  • the longitudinal bore 13 limited at the same time the gap 11 at its two longitudinal sides. The gap 11 thus opens into these longitudinal bores 13 a.
  • the carriage 1 is seen in cross-section approximately U-shaped. Two legs 15 of the guide carriage 1 are connected to one another via a base 16, wherein the guide carriage 1 engages around the guide rail with its two legs 15. The bottom 16 is presently provided with the gap 11 already described.
  • the gap 11 is formed as a pressure chamber 17, wherein in this pressure chamber 17 hydraulic fluid 18 is filled.
  • Control device 19 - which is merely indicated in the figure 1 - can
  • Hydraulic fluid 18 are pressurized in the pressure chamber 17.
  • the gap 11 widens, so that the upper carriage section 9 performs a lift relative to the lower carriage section 10, but away from the guide rail.
  • a lifting device 20 is provided by means of
  • Strokes are adjustable up to 100 ⁇ m.
  • Teen do it within the given limits desired stroke can be set as a fixed position of the upper carriage section 9 relative to the lower carriage section 10, wherein only a corresponding pressurization takes place.
  • FIGS filled with hydraulic fluid 18 pressure chamber 17 forms a damping device 22 which dampens vibrations.
  • This damping device 22 is suitable for substantially suppressing the transmission of vibrations between the upper carriage section 9 and the lower carriage section 10.
  • the linear guide according to the invention described here is particularly suitable for a dynamic vibration damping.
  • the power, control and regulation unit 19 for example in the presence of an undesired dynamic oscillation between the upper carriage section 9 and the lower carriage section 10, a targeted pulsating pressurization takes place in a frequency which superimposes the unwanted oscillation such that the upper one Carriage section 9 can run without vibrations.
  • the lifting device 20 forms with the power, control and regulating unit 19 an actuator 23. This actuator allows dynamic vibration damping in this invention Linear guide.
  • the carriage 1 can be modified to the effect that approximately in a longitudinal center plane of the carriage 1 a support element
  • the guide carriage according to the invention shown in FIG. 3 differs from that of FIG. 1 essentially in that the upper carriage section 9 and the lower carriage section 10 are formed by separate carriage parts 24, 25.
  • the associated design measures are explained in more detail below.
  • the under carriage part 25 is provided on its upper carriage part 24 facing side with a circumferential ridge 26.
  • This web 26 is provided with a plurality of threaded holes 27 for receiving expansion screws 28.
  • the inner wall of the web 26 serves as a sealing surface, as will be explained in more detail below.
  • the upper carriage part 24 is provided with a peripheral flange 29 which has a plurality of bores for receiving the expansion screws 28.
  • the flange 29 rests on the circumferential web 26.
  • the upper carriage member 24 is provided with an engaging portion 30 which in a bounded by the circumferential ridge 26 receiving portion of the lower carriage portion
  • the engagement portion 30 is provided with a circumferential groove 31 into which an O-ring 32 is inserted.
  • the O-ring 32 is applied to sealing surfaces of the circumferential ridge and the groove 31, so that the pressure chamber 17 is properly sealed to the environment of the carriage 1.
  • the gap 17 increases, the expansion screws 28 being stretched along their screw axes.
  • the seal described here can be sufficient by means of an O-ring, since this O-ring is predominantly subjected to only static loading. Of course, alternative seals are possible.
  • FIG. 7 shows a schematic illustration of the actuator 23, and in particular the power, control and regulating device 19.
  • a mass 33 is attached on the guide carriage 1.
  • a signal generator 34 is arranged, which transmits vibrations occurring at the mass 33 to a controller 35.
  • the controller 35 is connected to a hydraulic unit 36, via which the hydraulic fluid provided in the gap 11 of the guide carriage 1 can be pressurized.
  • the guide carriage 1 itself acts here as a damper, which introduces into the oscillating component-here the mass 33-a "counter-oscillation" phase-shifted by 90.degree ..
  • the oscillation of the mass 33 and the corresponding "counter-oscillation" cancel each other out.
  • This active damping device 22 can - in contrast to the passive dampers - compensate over a wide frequency range, while the known passive damper works optimally only for a specific frequency.
  • the integration of the dynamic damper in the carriage 1 allows a very space-saving design. LIST OF REFERENCE NUMBERS

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Bearings For Parts Moving Linearly (AREA)
  • Vibration Prevention Devices (AREA)
  • Machine Tool Units (AREA)

Abstract

Guide linéaire, avec un chariot de guidage (1) qui est disposé à translation longitudinale sur un rail de guidage (2) et qui présente un raccord (21) pour monter un organe de machine, par exemple un porte-outil ou une table de machine, et au moins une surface d'appui, disposée à distance du raccord (21), pour le montage du chariot de guidage (1) sur le rail de guidage (2), sachant que le chariot de guidage (1) présente une partie supérieure de chariot (9) présentant le raccord (21) ainsi qu'une partie inférieure de chariot (10) présentant la ou les surfaces d'appui, qu'un interstice (11) est prévu entre la partie supérieure de chariot (9) et la partie inférieure de chariot (10), et qu'il est prévu des translations relatives limitées entre les deux parties de chariot (9, 10) sans translations relatives entre la partie inférieure de chariot (10) et le rail de guidage (2) ; et avec un amortisseur de vibrations disposé pour agir entre les deux parties de chariot (9, 10) afin d'amortir les vibrations, sachant qu'un dispositif de levage (20) est prévu dans l'interstice (11) pour un levage variable de la partie supérieure de chariot (9) par rapport à la partie inférieure de chariot (10), le dispositif de levage (20) étant utilisé comme amortisseur de vibrations (22).
PCT/EP2008/066505 2007-12-06 2008-12-01 Guide linéaire avec amortisseur de vibrations WO2009071502A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007059156.1 2007-12-06
DE102007059156.1A DE102007059156B4 (de) 2007-12-06 2007-12-06 Linearführung mit Schwingungsdämpfer

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Publication Number Publication Date
WO2009071502A1 true WO2009071502A1 (fr) 2009-06-11

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PCT/EP2008/066505 WO2009071502A1 (fr) 2007-12-06 2008-12-01 Guide linéaire avec amortisseur de vibrations

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DE (1) DE102007059156B4 (fr)
WO (1) WO2009071502A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140137776A1 (en) * 2011-07-12 2014-05-22 Micro-Controle-Spectra Physics Device for the translational guidance of a load and method of creating such a device

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010020032A1 (de) * 2010-05-11 2011-11-17 J. Eberspächer GmbH & Co. KG Schwingungstilger
DE102012205762A1 (de) 2012-04-10 2013-10-10 Schaeffler Technologies AG & Co. KG Linearführung mit einem Schwingungsdämpfer
DE102013225328A1 (de) * 2013-12-10 2015-06-11 Aktiebolaget Skf Linearlager mit Schwingungsdämpfung
CN104006081B (zh) * 2014-06-11 2016-06-01 上海雄联精密机械配件有限公司 一种直线导轨副的高防尘性能结构
DE102019111000A1 (de) * 2019-04-29 2020-10-29 Airbus Operations Gmbh Luftfahrzeugsitzbefestigungsbaugruppe, damit versehene Sitzanordnung und Luftfahrzeugkabine sowie Luftfahrzeug

Citations (2)

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Publication number Priority date Publication date Assignee Title
DE4304950A1 (de) * 1993-02-18 1994-08-25 Schaeffler Waelzlager Kg Führungswagen für eine Linearführung
CH684434A5 (de) * 1991-03-06 1994-09-15 Schneeberger Ag Maschf Dämpfungsvorrichtung für gegenseitig geführt bewegbare Maschinenteile.

Family Cites Families (1)

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Publication number Priority date Publication date Assignee Title
JPH0560133A (ja) * 1991-08-23 1993-03-09 Nippon Thompson Co Ltd 防振性を有する直動案内摺動ユニツト

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH684434A5 (de) * 1991-03-06 1994-09-15 Schneeberger Ag Maschf Dämpfungsvorrichtung für gegenseitig geführt bewegbare Maschinenteile.
DE4304950A1 (de) * 1993-02-18 1994-08-25 Schaeffler Waelzlager Kg Führungswagen für eine Linearführung

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140137776A1 (en) * 2011-07-12 2014-05-22 Micro-Controle-Spectra Physics Device for the translational guidance of a load and method of creating such a device
US9080717B2 (en) * 2011-07-12 2015-07-14 Micro-Controle-Spectra Physics Device for the translational guidance of a load and method of creating such a device

Also Published As

Publication number Publication date
DE102007059156A1 (de) 2009-06-10
DE102007059156B4 (de) 2015-11-26

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