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WO2010076113A1 - Entraînement oscillant - Google Patents

Entraînement oscillant Download PDF

Info

Publication number
WO2010076113A1
WO2010076113A1 PCT/EP2009/066325 EP2009066325W WO2010076113A1 WO 2010076113 A1 WO2010076113 A1 WO 2010076113A1 EP 2009066325 W EP2009066325 W EP 2009066325W WO 2010076113 A1 WO2010076113 A1 WO 2010076113A1
Authority
WO
WIPO (PCT)
Prior art keywords
counterweight
drive
spring
vibration
output element
Prior art date
Application number
PCT/EP2009/066325
Other languages
German (de)
English (en)
Inventor
Vincent Rieger
Heiner Storck
Andre Meyer
Juergen Hilzinger
Original Assignee
Robert Bosch Gmbh
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 Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Priority to CN2009801577969A priority Critical patent/CN102341929A/zh
Publication of WO2010076113A1 publication Critical patent/WO2010076113A1/fr

Links

Classifications

    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02N—ELECTRIC MACHINES NOT OTHERWISE PROVIDED FOR
    • H02N2/00—Electric machines in general using piezoelectric effect, electrostriction or magnetostriction
    • H02N2/02—Electric machines in general using piezoelectric effect, electrostriction or magnetostriction producing linear motion, e.g. actuators; Linear positioners ; Linear motors
    • H02N2/026—Electric machines in general using piezoelectric effect, electrostriction or magnetostriction producing linear motion, e.g. actuators; Linear positioners ; Linear motors by pressing one or more vibrators against the driven body
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02N—ELECTRIC MACHINES NOT OTHERWISE PROVIDED FOR
    • H02N2/00—Electric machines in general using piezoelectric effect, electrostriction or magnetostriction
    • H02N2/0005—Electric machines in general using piezoelectric effect, electrostriction or magnetostriction producing non-specific motion; Details common to machines covered by H02N2/02 - H02N2/16
    • H02N2/001—Driving devices, e.g. vibrators
    • H02N2/002—Driving devices, e.g. vibrators using only longitudinal or radial modes
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02N—ELECTRIC MACHINES NOT OTHERWISE PROVIDED FOR
    • H02N2/00—Electric machines in general using piezoelectric effect, electrostriction or magnetostriction
    • H02N2/0005—Electric machines in general using piezoelectric effect, electrostriction or magnetostriction producing non-specific motion; Details common to machines covered by H02N2/02 - H02N2/16
    • H02N2/005—Mechanical details, e.g. housings
    • H02N2/0055—Supports for driving or driven bodies; Means for pressing driving body against driven body
    • H02N2/006—Elastic elements, e.g. springs

Definitions

  • the invention relates to a vibration drive, in particular for motor vehicle applications, preferably for adjusting a motor vehicle window, according to the preamble of claim 1.
  • the vibration drive designed as a ram drive comprises two piezoelectric actuators arranged at an angle to one another, with which a drive element (plunger) can be excited to oscillate in order to drive a rail (driven element) in translation.
  • the drive element is pressed by means of a spring in a pressing direction against the driven element in order to guarantee a sufficient force transmission by frictional engagement.
  • the invention has for its object to provide a vibration drive with improved efficiency.
  • the invention is based on the idea of assigning a countermass to the output element of at least one actuator, preferably a piezoactuator, that can be excited to oscillate in vibrations, and to store these resiliently in such a way that this force is applied to the driven element driven by the drive element in the direction of the output element.
  • a counterweight that can be excited to oscillate, preferably indirectly via the output element, is provided, which ensures that the output element is pressed against the drive element, that is, that contact forces act between the drive element and the driven element. If necessary, can be dispensed with a separate Federkraftbeetzschung of the drive element in the direction of the output element, as provided in the prior art.
  • An embodiment of the vibration drive in which the countermass to the drive element performs an opposite phase oscillation is very particularly preferred.
  • the at least one drive element and the at least one counterweight are arranged on two opposite sides of the driven element, so that the drive element, a second side facing away from the first side of the power take-off element and the counterweight.
  • the oscillating drive provided with the oscillating counterweight is designed as a linear drive, wherein in this case the output element is preferably designed as a rail with which an object to be driven translationally, preferably a motor vehicle window pane, is coupled.
  • the drive element engages an upper side of the rail and the counterweight on the underside of the rail.
  • counterweight and drive element are directly opposite, ie an imaginary, perpendicular to the output element axis intersects both the output element and the counterweight.
  • the counterweight spring-mounted spring is designed such that this in the normal direction relative to the driven element has a higher rigidity than in the tangential direction, i. as in the direction of movement of the output element. In this way it can be achieved that hardly tangential forces result on an optionally provided bearing, which will be explained later on, for rotatably supporting the counterweight, thereby avoiding tilting of the counterweight.
  • a plate spring is used for supporting the counterweight, which is further preferably provided with a plurality of radial slots distributed over the inner circumference.
  • the use of a disc spring makes it possible to realize a high level of normal rigidity in a simple manner.
  • the required (low) tangential rigidity can be realized by means of a guide of the actual bearing for rotatably supporting the countermass.
  • the assembly takes place in the untensioned state of the plate spring, wherein the bias voltage at the end of the assembly, for example, by tightening an adjusting screw (clamping screw) is adjusted.
  • the plate spring is designed such that a plateau, i. a horizontal one
  • Fine adjustment possible In this way, space can be saved and simplify the assembly or setting process.
  • the spring for resiliently supporting the countermass can be formed as an at least approximately C- or U-shaped contoured spring, in particular spring-loaded spring. With a thus formed spring a particularly high normal stiffness and at the same time a low tangential stiffness can be realized.
  • the contact pressure with which the counterweight presses against the driven element is adjustable.
  • This is preferably done by adjusting the spring force of the countermass bearing spring, which in turn very particularly preferably can be achieved via at least one spring clamping element, which in the case of execution of the spring as a plate spring, for example with a spring passing through the clamping screw can be achieved.
  • the two at least approximately parallel legs of the spring can be transversely to their longitudinal extent, i. towards each other, are stretched by means of a suitable spring tensioning element until the desired spring force and thus the desired contact pressure is set.
  • the counterweight is particularly preferred, but not mandatory, for the counterweight to be rotatably supported, particularly preferably by means of a roller bearing, for further optimization of the efficiency of the vibration drive. It is further preferred if the counterweight is formed as a hollow cylinder, which is penetrated by a corresponding bearing axis.
  • FIG. 1 shows a schematic representation of a first embodiment of a
  • C-shaped contoured band spring is provided, 2a and 2b show different views of an alternative embodiment of a vibration drive, wherein, in contrast to the embodiment shown in FIG. 1, a spring tensioning element for adjusting the
  • FIGS. 3a and 3b show different views of a further alternative exemplary embodiment of a vibration drive, wherein the resilient mounting of the
  • Fig. 6a to 6f an alternative vibration cycle with permanently on the output element adjacent counterweight.
  • Fig. 1 designed as a linear drive for adjusting a motor vehicle window not shown vibratory drive 1 is shown.
  • the vibration drive 1 is designed as a so-called ram drive and comprises a shock-shaped drive element 2, which by means of two, designed as piezoelectric actuators, actuators 3, 4 to a trained as a rail output element 5 (runner) driving vibration can be excited.
  • a rail output element 5 runner
  • the aforementioned motor vehicle window is set in a suitable manner.
  • the piezoelectric actuators 3, 4 are coupled to the drive element 2 via a metallic bridge part 7. If necessary, a drive element 2 or the drive means 8 formed by the actuators 3, 4, the bridge part 7 and the drive element 2 can be provided in the direction of the output element 5 spring-loading spring 12.
  • the drive element 2 is located on a first side 9 of the output element 5, so that the first side 9 is subjected to force by the drive element 2 in its oscillating motion, resulting in the translational adjustment of the output element 5 with object fixed thereto , here a motor vehicle window pane (not shown), results.
  • a swinging counterweight 1 1 is arranged on the side facing away from the first side 9 second side 10 of the output element 5, which runs parallel to the first side 9, a swinging counterweight 1 1 is arranged.
  • the counterweight 1 1 can oscillate horizontally to the surface extension or to the direction of movement of the output element 5, this is resiliently mounted - in the illustrated embodiment with a substantially U-shaped spring 12 in the region of the output member 5 facing apex 13 a bearing axis 14 receiving dent or indentation 15 has.
  • the bearing axis 14 passes through the hollow-cylindrical counterweight 1 1 transversely to the possible adjustment directions of the output element 5, which are indicated by the arrows 6, and serves to rotatably support the counterweight 1 1.
  • the spring 12 allows swinging of the counterweight
  • the counterweight 1 1 is located on this axis 16.
  • the counterweight 1 1 is mounted rotatably relative to the axis 16 by means of a rolling bearing, not shown.
  • the bearing of the counterweight 1 1 is designed such that the counterweight 1 1 in operation, ie during the operating frequency of the vibration drive 1, ge Duration of the drive means 8, in opposite phase to the drive means 8 and the drive element 2 oscillates, whereby the force balance on the output element 5 and the contact forces of the counterweight 1 1 - in comparison to the prior art - increases.
  • a vibration cycle of a first embodiment is shown, wherein the resilient mounting of the counterweight 1 1, which was not shown for reasons of clarity in Figs. 5a to 5f, is designed such that the counterweight in the normal direction of the driven element 5 and turn against it again.
  • the spring force for the counterweight 1 1 is set such that the counterweight in their vibration not, or only slightly, from the output element 5 lifts in the normal direction.
  • FIGS. 5 a to 6f pressure or contact forces are shown with hollow arrows 17 with which the drive element 2 and / or the counterweight 1 1 press against the output element 5.
  • a hollow circle 21 identifies the situations or oscillation states at which this force / forces is / are zero.
  • the full arrows 18 indicate the adjustment speed or the adjustment in which the drive element 2 and / or the counterweight 1 1 moves / move at the appropriate time.
  • the full circles 20 symbolize a zero adjustment speed.
  • On the output element 5 is a rectangular
  • Distance marking 19 shown to visualize the relative movement of the output element 5 relative to the drive element 2 to the counterweight 1 1.
  • the C-shaped spring 12 can be tensioned.
  • a spring tensioning element 22 is provided, with which the two at least approximately parallel legs 23, 24 to each other are kraftbeaufschlagbar, so as to adjust the spring force.
  • the spring tensioning element 22 comprises a screw 25 for adjusting the spring force and thus the contact pressure with which the counterweight 1 1, the output element 5 subjected to force.
  • a substantially U-shaped contoured profile frame 26 is shown, on which the actuators 3, 4 and the spring 12 are fixed.
  • FIGS. 3a and 3b A further alternative exemplary embodiment of a vibration drive 1 is shown in FIGS. 3a and 3b.
  • a C-shaped contoured band spring spring 12
  • the plate spring 12 is arranged such that the conically opening side of the plate spring 12 in the direction of rail-shaped output element 5 shows.
  • a bearing holder 28 is mounted, which carries the bearing axis 14 for rotatably supporting the counterweight 1 1.
  • Counterweight 1 1 is pressed against the output element 5, set by means of a screw 25 (clamping screw) comprehensive spring tensioning element 22, which passes through the spring 12 in the normal direction relative to the output element 5 and with the provided with an internal thread bearing bracket 28 in the direction of a screw head 27 of the screw 25 is movable, so as to tension the spring formed as a plate spring 12.
  • a screw 25 clamping screw
  • FIGS. 3a and 3b are also operable in the different operating modes, which are dependent on the spring tension and are shown in FIGS. 5a to 5f and FIGS. 6a to 6f.
  • Fig. 4 is a schematic diagram of a spring characteristic of a preferred, used for use spring 12 is shown. This comprises a (middle) plateau section 29, in which the spring force F F does not increase or increases only slightly with the spring travel s.

Landscapes

  • General Electrical Machinery Utilizing Piezoelectricity, Electrostriction Or Magnetostriction (AREA)

Abstract

L'invention concerne un entraînement oscillant (1), en particulier pour applications automobiles, comprenant un élément d'entraînement (2) qui peut être mis en oscillation par au moins un actionneur (3, 4) et qui est configuré et agencé pour entraîner l'élément mené (5). Selon l'invention, il est prévu un contrepoids (11) monté élastiquement qui exerce une force sur l'élément mené (5) dans la direction de l'élément d'entraînement (2).
PCT/EP2009/066325 2009-01-05 2009-12-03 Entraînement oscillant WO2010076113A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN2009801577969A CN102341929A (zh) 2009-01-05 2009-12-03 摆动驱动装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009000017A DE102009000017A1 (de) 2009-01-05 2009-01-05 Schwingungsantrieb
DE102009000017.8 2009-01-05

Publications (1)

Publication Number Publication Date
WO2010076113A1 true WO2010076113A1 (fr) 2010-07-08

Family

ID=42062440

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2009/066325 WO2010076113A1 (fr) 2009-01-05 2009-12-03 Entraînement oscillant

Country Status (3)

Country Link
CN (1) CN102341929A (fr)
DE (1) DE102009000017A1 (fr)
WO (1) WO2010076113A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013204026A1 (de) * 2013-03-08 2014-09-11 Physik Instrumente (Pi) Gmbh & Co. Kg Aktoranordnung für einen Ultraschallmotor
WO2018005225A1 (fr) 2016-06-30 2018-01-04 Danisco Us Inc Protéases aspartiques
WO2018118815A1 (fr) 2016-12-21 2018-06-28 Dupont Nutrition Biosciences Aps Procédés d'utilisation de sérine-protéases thermostables
WO2018169750A1 (fr) 2017-03-15 2018-09-20 Danisco Us Inc Sérine protéases de type trypsine et leurs utilisations
WO2018169784A1 (fr) 2017-03-15 2018-09-20 Dupont Nutrition Biosciences Aps Sérine protéases de type trypsine et leurs utilisations en référence croisée à une application associée
EP2753859B2 (fr) † 2011-09-06 2025-01-22 Nicoventures Trading Limited Isolation

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103758430B (zh) * 2014-01-28 2016-04-06 哈尔滨工业大学 压电超声振子驱动型汽车电动车窗

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4997177A (en) * 1987-10-23 1991-03-05 Hitachi, Ltd. Method of and apparatus for conveying object by utilizing vibration
US6262514B1 (en) * 1996-08-14 2001-07-17 Intelligent Manufacturing Systems Limited Bearings and supports
US6617759B1 (en) * 1997-12-15 2003-09-09 Nanomotion Ltd. Conveying means and method

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4613782A (en) 1984-03-23 1986-09-23 Hitachi, Ltd. Actuator
CN100361790C (zh) * 2006-01-26 2008-01-16 沈阳建筑大学 具有自锁功能的叉式机械手

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4997177A (en) * 1987-10-23 1991-03-05 Hitachi, Ltd. Method of and apparatus for conveying object by utilizing vibration
US6262514B1 (en) * 1996-08-14 2001-07-17 Intelligent Manufacturing Systems Limited Bearings and supports
US6617759B1 (en) * 1997-12-15 2003-09-09 Nanomotion Ltd. Conveying means and method

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2753859B2 (fr) † 2011-09-06 2025-01-22 Nicoventures Trading Limited Isolation
DE102013204026A1 (de) * 2013-03-08 2014-09-11 Physik Instrumente (Pi) Gmbh & Co. Kg Aktoranordnung für einen Ultraschallmotor
EP2973980B1 (fr) * 2013-03-08 2017-05-10 Physik Instrumente (PI) GmbH & Co. Kg Dispositif pour moteur à ultrasons
DE102013204026B4 (de) 2013-03-08 2019-08-08 Physik Instrumente (Pi) Gmbh & Co. Kg Aktoranordnung für einen Ultraschallmotor
WO2018005225A1 (fr) 2016-06-30 2018-01-04 Danisco Us Inc Protéases aspartiques
EP3825399A1 (fr) 2016-06-30 2021-05-26 Danisco US Inc. Protéases aspartiques
WO2018118815A1 (fr) 2016-12-21 2018-06-28 Dupont Nutrition Biosciences Aps Procédés d'utilisation de sérine-protéases thermostables
WO2018169750A1 (fr) 2017-03-15 2018-09-20 Danisco Us Inc Sérine protéases de type trypsine et leurs utilisations
WO2018169784A1 (fr) 2017-03-15 2018-09-20 Dupont Nutrition Biosciences Aps Sérine protéases de type trypsine et leurs utilisations en référence croisée à une application associée

Also Published As

Publication number Publication date
CN102341929A (zh) 2012-02-01
DE102009000017A1 (de) 2010-07-08

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