WO2004087343A1 - Dispositif antivibratoire a masselottes rotatives - Google Patents
Dispositif antivibratoire a masselottes rotatives Download PDFInfo
- Publication number
- WO2004087343A1 WO2004087343A1 PCT/FR2004/000477 FR2004000477W WO2004087343A1 WO 2004087343 A1 WO2004087343 A1 WO 2004087343A1 FR 2004000477 W FR2004000477 W FR 2004000477W WO 2004087343 A1 WO2004087343 A1 WO 2004087343A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- rotors
- axis
- symmetry
- mobile equipment
- phase shift
- Prior art date
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B64—AIRCRAFT; AVIATION; COSMONAUTICS
- B64C—AEROPLANES; HELICOPTERS
- B64C27/00—Rotorcraft; Rotors peculiar thereto
- B64C27/001—Vibration damping devices
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
- B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
- B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
- B06B1/10—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy
- B06B1/16—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving rotary unbalanced masses
- B06B1/161—Adjustable systems, i.e. where amplitude or direction of frequency of vibration can be varied
- B06B1/166—Where the phase-angle of masses mounted on counter-rotating shafts can be varied, e.g. variation of the vibration phase
-
- 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
- F16F15/22—Compensation of inertia forces
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B64—AIRCRAFT; AVIATION; COSMONAUTICS
- B64C—AEROPLANES; HELICOPTERS
- B64C27/00—Rotorcraft; Rotors peculiar thereto
- B64C27/001—Vibration damping devices
- B64C2027/004—Vibration damping devices using actuators, e.g. active systems
Definitions
- the present invention relates to an anti-vibration device.
- the device according to the invention is intended to be mounted, in its preferred application, on board aircraft, especially in the cabin of a rotary wing aircraft such as the helicopter, but it could well understood to be used for any other application from the moment one wishes to reduce, or even eliminate, vibrations generated by a moving body.
- anti-vibration resonator devices which act by resonance at a predetermined frequency to reduce the vibrations exhibiting this frequency. Their effectiveness is nevertheless limited since they act only on vibrations having the predetermined frequency and not on other vibrations.
- the antivibration device of the controllable resonator type described in this prior patent makes it possible to treat vibrations at variable frequencies.
- the resonator is used as an actuator in a closed loop system and the measurements vibrations from sensors placed on the helicopter are analyzed by a control unit which delivers the control signal for each actuator, so as to minimize the vibration levels at the measurement points.
- this antivibration device has a certain number of drawbacks such as a high mass (ten kilograms for each resonator), which is always penalizing in the aeronautical field, and a significant energy consumption to effectively deal with the vibration levels encountered on helicopters.
- anti-vibration devices of another design have been developed and use the use of a rotating unbalance to create a force counteracting the vibrations to be reduced.
- American patents US-5,903,077 and European patent EP-O 337,040 teach such devices.
- the antivibration device or modular vibratory force generator described in this American patent consists of modules or assemblies each comprising a motor, driving by gear a pair of cooperating toothed rotors with respective eccentric masses, so that the center of gravity of each them is not located on its axis of rotation.
- the rotation of each rotor produces a rotating unbalance and, as they are arranged in the same plane, they produce identical unbalances but rotating in opposite directions. This results in a sinusoidal force in the direction perpendicular to the plane containing the axes of rotation of the rotors, because the components of the unbalances in this plane are opposite and therefore cancel each other out.
- the generator comprises two identical modules associated to obtain an adjustable resulting force whose amplitude depends on the phase shift between the modules and whose frequency is equal to the rotational speed of the rotors.
- a control unit controls and regulates the phase shift between the modules and the rotational speed of the rotors, so that vibrations of any frequency can be reduced.
- the anti-vibration device described in the above-mentioned European patent similarly comprises two identical sets of two rotors each, with respective eccentric weights, the two sets being arranged symmetrically with respect to an axis of symmetry and said rotors with eccentric weights, with axes parallel to each other and orthogonal to the axis of symmetry, are rotated by respective motors which are slaved to rotate at the same speed.
- Such a device can thus adapt to fluctuations in amplitude, phase and frequency of the vibrations that it is desired to attenuate.
- the present invention aims to remedy these drawbacks.
- the anti-vibration device of the type comprising at least two sets of two identical rotors each, with respective eccentric weights, said sets being arranged symmetrically with respect to an axis of symmetry and the axes of rotation of said rotors being mutually parallel and orthogonal said axis of symmetry, a system for rotating said rotors, is remarkable, according to the invention:
- said drive system comprises a single motor for the rotation of said rotors, with an axis arranged perpendicular to said axis of symmetry, which causes an endless link passing around said rotors, so that the lengths of the strands of the link passing through said sets are equal.
- a stable vibratory force of determined amplitude and orientation can be generated by the device by simply moving along the axis of symmetry the mobile equipment carrying the single motor and which drives, via said link, the progressive phase shift of the rotors of each assembly to bring the eccentric weights to the desired position.
- the two symmetrical strands passing through the assemblies have identical displacement speeds and of the same module but of different meanings since, by symmetry, one of the strands passing through its assembly moves away from the single motor, while the other strand approaches it.
- the rotors all have the same rotation speed, imposed by the single motor.
- the resulting vibrational force is therefore very stable and perfectly controlled.
- the four rotors stop simultaneously, so that the vibration level of the structure will then rise to its initial value without any anti-vibration device but cannot exceed it, unlike the prior devices described previously.
- the final phase shift obtained after stopping the mobile equipment depends on the duration of movement of said equipment, that is to say on its effective movement along the axis of symmetry.
- the stroke of the linear displacement of said mobile equipment is delimited by two extreme positions, a first position for which the phase shift between the balance rotors of the first set and those of the second set is zero, and a second position for which the phase shift is equal to 180 °.
- the resulting vibrational force can thus vary by a maximum amplitude, when the phase shift between the balance rotors of the first set and those of the second set is zero, at zero amplitude, when the phase shift between them is 180 °, the frequency of said vibratory force being equal to the common rotation speed of the rotors driven by the single motor.
- the device preferably comprises at least one servomotor for controlling the position of said mobile equipment, a plurality of sensors measuring the position of said rotors to calculate the phase difference between said assemblies and a law for regulating and controlling the rotation of said motor. unique.
- said controllable equipment is a carriage sliding along said axis of symmetry and supporting said single motor.
- said endless link is a belt and is wound around pulleys, mounted coaxially on said rotors and on said single motor, contained in the same plane.
- said belt is notched and cooperates with corresponding teeth formed on said pulleys.
- controllable mobile equipment also comprises at least one roller for tensioning said endless link.
- the two sets of two rotors are carried by a frame that can be fixed to a vibrating structure, said controllable mobile equipment being slidably mounted on said frame along the axis of symmetry of the two sets.
- said anti-vibration device comprises, for each set of rotors, an intermediate rotary roller cooperating with said link to ensure the counter-rotating drive of the two rotors, the two rotary rollers being arranged on the frame and arranged respectively on both sides and d other of said axis of symmetry.
- Figure 1 shows, in perspective, an exemplary embodiment of the anti-vibration device according to the invention.
- Figures 2 to 6 schematically represent different positions that can be occupied by the anti-vibration device as a result of the action of the mobile equipment and the drive system, to reduce vibrations.
- the anti-vibration device 1 illustrated in FIG. 1 comprises two identical sets or modules 2, 3 of two rotors or rotary shafts each, respectively 4, 5 and 6, 7, with which respective weights 4A, 5A and 6A, 7A are associated which are offset relative to the axes of rotation of the rotors.
- the two assemblies 2, 3 are arranged in a common vertical plane and are separated from each other with respect to an axis of symmetry A, then horizontal.
- the axes of the rotors 4, 5, 6 and 7 are mutually parallel (horizontal in said example) and orthogonal to the axis of symmetry A of identical assemblies 2, 3 so that the rotors are opposite in pairs, the rotors 4 , 5 and 6, 7 being equidistant from an axis of symmetry B (vertical in FIGS. 2 to 8) orthogonal to the axis of symmetry A.
- a drive system 8 also drives the rotors 4 to 7.
- a frame 9 consisting of an assembly of plates 9A and the base 9B of which can be fixed, by fixing members 10, to a vibrating structure of the helicopter, not shown.
- the device 1 comprises mobile equipment 1 1 carrying the drive system 8 and able to slide along the axis of symmetry A, the drive system 8 being common to all of the rotors, and the two rotors 4, 5 and 6, 7 of each assembly rotating in a counter-rotating manner relative to each other, so that the two rotors 4-6 symmetrically opposite rotate in the same direction and the other two rotors 5-7 in the opposite direction.
- the common drive system 8 is consists of a single motor 12 arranged between the two assemblies and whose axis of rotation of its output shaft 12A is parallel to the rotors 4, 5, 6, 7 and perpendicular to the axis of symmetry A.
- the single motor 12 causes an endless link 14 forming a closed loop and passing around the rotors for setting them in motion.
- the endless link 14 is constituted by a belt which is wound around pulleys 15 mounted coaxially on the rotors.
- the pulleys have an identical diameter so that, relative to the axis of symmetry of the device, the length of the strand 14A of the belt 14 passing through the assembly 2 is equal to the length of the strand 14B passing through the assembly 3 .
- the pulleys 15 are contained in the same vertical plane. To avoid the appearance of a sliding bearing, the belt 14 is notched and then cooperates with corresponding teeth 15A formed at the periphery of the pulleys 15. Alternatively, one could use a chain drive and sprockets.
- the toothed belt 14 is also wound around two intermediate rollers 16 such as free pulleys, identical to the previous ones, respectively arranged on either side of the axis of symmetry A.
- These two pulleys intermediaries 16 are thus located between the single motor 12 and the respective assemblies 2, 3 and are supported by the frame 9. And each of them, in connection with its assembly or module concerned, allows the two rotors 4,5-6, 7 of a set, via the associated pulleys, to rotate in opposite directions with respect to each other.
- the controllable mobile equipment 1 1 includes two rollers, or pulleys, identical tensioning 1 7 arranged symmetrically to each other relative to the axis of symmetry A, to allow adjustment of the tension of the belt 14.
- controllable mobile equipment 1 it is composed, in the illustrated embodiment, of a carriage 18 arranged between the two assemblies 2, 3 and capable of sliding, in the vertical plane of the device, along the axis of symmetry A.
- This carriage 18 is structurally linked in a sliding manner to the frame by a connection of the slide or similar type not shown, and carries the tensioning rollers 17 as well as the single motor 12 which drives the belt 14.
- the movement of the carriage along the axis of symmetry A is controlled by means of a servomotor 19 provided between the frame 9 and the carriage 18 and forming part of a device for controlling the frequency and the amplitude of the overall vibrational force generated by the anti-vibration device 1.
- This control device consists of the servomotor 19 controlling the position of the carriage 18 as a function of a first electrical signal for example to control the amplitude of the vibratory force generated by the device 1, of a plurality of sensors not shown measuring the angular position of the rotors of each assembly 2, 3 to calculate the phase shift to be produced between the assemblies according to the vibrations to be absorbed, and of a law regulating and controlling the rotation speed of the single motor 12 as a function of a second signal to control the frequency.
- phase shift between the rotors 4, 6, 5, 7 with eccentric weights 4A, 6A-5A, 7A of the two assemblies, symmetrically opposite with respect to the axis of symmetry A is
- ⁇ is the phase shift
- d corresponds to the linear displacement (stroke) of the carriage along the axis of symmetry
- r corresponds to the identical winding radius of the endless link around the center identical rotors.
- phase shift ⁇ between the rotors facing the assemblies is zero, the four eccentric counterweights 4A, 5A, 6A, 7A of the rotors being in the same angular position, and in this example, the carriage 18 then occupies one of its two limit position limit positions, on the right in Figure 2.
- the two strands of the belt 14 respectively upper 14A (above the axis of symmetry A) and lower 14B (below the axis of symmetry A) have speeds of the same module V but of opposite directions.
- each set 2, 3 The rotors 4-5, 6-7 of each set 2, 3 are driven at an identical speed and rotate as a whole in opposite directions from each other, but in identical directions for the pairs of rotors of the sets , arranged symmetrically with respect to the axis A, that is to say the pairs of rotors 4-6 and 5-7.
- a phase shift has of 45 ° provided by the sensors between the two pairs facing rotors
- the carriage 18 of the mobile equipment 1 1 moves at a speed v to the left under the action of the servomotor 19, as shown in FIG. 3, along the axis of symmetry A and prints its translational movement on the two strands 14A, 14B of the belt 14.
- Its tension remains constant, therefore identical, because the length of its path is unchanged (the displacement of the single motor compensates for that of the carriage).
- the speeds of the respective strands become, for the upper strand 14A, equal to Vv since it is pulled by the sliding of the carriage 18 and, for the lower strand 14B, equal to V + v since it is pushed by said carriage.
- FIGS. 4 to 6 show examples of remarkable phase shifts of the antivibration device 1 respectively equal to
- any resulting vibratory force (amplitude and orientation) can be delivered between the two extreme values of the phase shift (0 to 180 °) corresponding to the two limit strokes of the carriage, this is that is to say between a zero vibrational force when the influence of the eccentric weights is canceled and a maximum force when the influence of the four eccentric weights is added.
- control device can estimate the phase shift of the assemblies or modules from the effective position of the carriage (and not from the sensors associated with the rotors) since a position of the carriage along the axis A corresponds to a phase shift ⁇ .
- a prior calibration linking the carriage stroke to the phase shift of the assemblies is then necessary.
- servos described are of the electrical type, one could envisage, as a function of particular application constraints, servos of the mechanical, fluidic, optical or other type.
- the anti-vibration device is used alone with a predetermined level of vibration force, it is then possible to simplify the device for controlling the carriage by replacing the servomotor by a screw-nut type connection for adjusting the carriage along the axis. , and by a lock nut for blocking.
- the orientation of the elementary vibratory force of each set can be adjusted by shifting the position of the centers of gravity of the two eccentric flyweight rotors. If the elementary forces of the two sets have the same orientation, then the overall vibratory force resulting from the device with this orientation is an amplitude which will depend on the phase shift between the sets.
- Such an offset of the unbalances generated by the counterweights can be obtained manually by a predetermined adjustment of the position of the counterweights or automatically by a specific servo-control.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Aviation & Aerospace Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Apparatuses For Generation Of Mechanical Vibrations (AREA)
- Vibration Prevention Devices (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP04715923A EP1603686B1 (fr) | 2003-03-20 | 2004-03-01 | Dispositif antivibratoire a masselottes rotatives |
CN200480007561.9A CN1761536B (zh) | 2003-03-20 | 2004-03-01 | 具有旋转配重物的防振动设备 |
US10/522,516 US7582032B2 (en) | 2003-03-20 | 2004-03-01 | Anti-vibratory device with rotary compensation weights |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR03/03412 | 2003-03-20 | ||
FR0303412A FR2852648B1 (fr) | 2003-03-20 | 2003-03-20 | Dispositif antivibratoire a masselottes rotatives |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2004087343A1 true WO2004087343A1 (fr) | 2004-10-14 |
Family
ID=32922311
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR2004/000477 WO2004087343A1 (fr) | 2003-03-20 | 2004-03-01 | Dispositif antivibratoire a masselottes rotatives |
Country Status (5)
Country | Link |
---|---|
US (1) | US7582032B2 (fr) |
EP (1) | EP1603686B1 (fr) |
CN (1) | CN1761536B (fr) |
FR (1) | FR2852648B1 (fr) |
WO (1) | WO2004087343A1 (fr) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1790421A1 (fr) * | 2005-11-28 | 2007-05-30 | Eurocopter | Dispositif d'asservissement pour un vibrateur à rotors déséquilibrés |
Families Citing this family (28)
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---|---|---|---|---|
CN101022994B (zh) | 2004-08-30 | 2012-07-04 | 洛德公司 | 直升飞机振动控制系统和消除振动的旋转力发生器 |
US7722322B2 (en) | 2004-08-30 | 2010-05-25 | Lord Corporation | Computer system and program product for controlling vibrations |
US8267652B2 (en) | 2004-08-30 | 2012-09-18 | Lord Corporation | Helicopter hub mounted vibration control and circular force generation systems for canceling vibrations |
US8162606B2 (en) | 2004-08-30 | 2012-04-24 | Lord Corporation | Helicopter hub mounted vibration control and circular force generation systems for canceling vibrations |
FR2882120B1 (fr) | 2005-02-17 | 2010-07-30 | Eurocopter France | Dispositif antivibratoire a masselottes rotatives a train epicycloidal |
FR2886176B1 (fr) | 2005-05-25 | 2007-07-06 | Eurocopter France | Generateur de vibrations par effet centrifuge a rotors contrarotatifs coaxiaux. |
US8382028B2 (en) | 2006-06-01 | 2013-02-26 | Lord Corporation | Rotary wing aircraft rotating machinery vibration control system |
DE102006059189B4 (de) * | 2006-12-15 | 2008-08-14 | Tutech Innovation Gmbh | Vorrichtung zur Schwingungskontrolle einer Konstruktion |
WO2009055007A2 (fr) | 2007-10-25 | 2009-04-30 | Lord Corporation | Systèmes répartis de contrôle actif des vibrations et aéronef à voilure tournante avec atténuation des vibrations |
US7980975B2 (en) * | 2007-11-16 | 2011-07-19 | Grossman Victor A | Drive configuration and method thereof |
US20110190083A1 (en) * | 2010-02-02 | 2011-08-04 | ALTe | Accessory drive system for a vehicle |
US9695744B2 (en) * | 2010-10-12 | 2017-07-04 | Ford Global Technologies, Llc | Engine drive system |
JP5535051B2 (ja) * | 2010-11-22 | 2014-07-02 | 株式会社マキタ | 動力工具 |
TW201338571A (zh) * | 2012-03-06 | 2013-09-16 | Askey Technology Jiangsu Ltd | 聲音品質檢測裝置 |
US10364865B2 (en) | 2013-08-29 | 2019-07-30 | Lord Corporation | Circular force generator (CFG) devices, systems, and methods having indirectly driven imbalanced rotors |
WO2016054209A1 (fr) | 2014-10-01 | 2016-04-07 | Sikorsky Aircraft Corporation | Aéronef à voilure tournante et à deux rotors |
WO2016053408A1 (fr) | 2014-10-01 | 2016-04-07 | Sikorsky Aircraft Corporation | Variation de signature acoustique d'aéronef mettant en oeuvre un embrayage |
US20170341739A1 (en) * | 2014-12-16 | 2017-11-30 | Sikorsky Aircraft Corporation | Variable amplitude force generator |
CN105652910B (zh) * | 2016-04-01 | 2017-12-29 | 中国船舶重工集团公司第七一九研究所 | 一种对偶旋转装置的振动控制方法 |
WO2018187178A1 (fr) * | 2017-04-04 | 2018-10-11 | Moog Inc. | Système de suppression de vibrations de masse rotative variable |
WO2019005250A1 (fr) | 2017-06-27 | 2019-01-03 | Moog Inc. | Système de suppression des vibrations de masse à rotation variable supporté radialement |
US11472540B2 (en) * | 2017-06-27 | 2022-10-18 | Moog Inc. | Variable rotary pendulous mass vibration suppression system |
CN107756411A (zh) * | 2017-09-15 | 2018-03-06 | 南京轩世琪源软件科技有限公司 | 一种基于电磁波测距的室内定位系统 |
TWI632985B (zh) * | 2017-09-27 | 2018-08-21 | 國立臺灣師範大學 | 一種雙偏心軸異相位驅動機構 |
CN107745332B (zh) * | 2017-11-13 | 2024-02-02 | 常州机电职业技术学院 | 一种减轻或消除磨削振痕的装置 |
EP3766778B1 (fr) * | 2019-07-19 | 2021-11-24 | LEONARDO S.p.A. | Rotor pour un avion capable de vol stationnaire |
CN112859589B (zh) * | 2021-01-14 | 2022-04-15 | 南京航空航天大学 | 旋翼变转速直升机振动主动控制的混合控制方法 |
CN116273812A (zh) * | 2023-02-24 | 2023-06-23 | 歌尔股份有限公司 | 激励器和电子设备 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0400510A1 (fr) * | 1989-06-02 | 1990-12-05 | M.A.B. | Installation à table vibrante pour la fabrication de produits en béton |
WO1996006290A1 (fr) * | 1994-08-24 | 1996-02-29 | F.L. Smidth & Co. A/S | Dispositif de compensation de vibrations |
US5903077A (en) * | 1995-09-21 | 1999-05-11 | Moog Inc. | Modular vibratory force generator, and method of operating same |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5584375A (en) * | 1994-12-21 | 1996-12-17 | Food Engineering Corporation | Single drive vibrational conveyor with vibrational motion altering phase control and method of determining optimal conveyance speeds therewith |
US5825663A (en) * | 1996-11-04 | 1998-10-20 | Gec-Marconi Aerospace Inc. | Vibration control system |
FR2770825B1 (fr) * | 1997-11-13 | 1999-12-31 | Eurocopter France | Dispositif pour reduire les vibrations dans la cabine d'un aeronef a voilure tournante, notamment un helicoptere |
CN2413805Y (zh) * | 1999-12-03 | 2001-01-10 | 西安建筑科技大学 | 变向激振器 |
JP4634565B2 (ja) * | 2000-03-09 | 2011-02-16 | 東北リコー株式会社 | 印刷装置 |
-
2003
- 2003-03-20 FR FR0303412A patent/FR2852648B1/fr not_active Expired - Fee Related
-
2004
- 2004-03-01 US US10/522,516 patent/US7582032B2/en active Active
- 2004-03-01 WO PCT/FR2004/000477 patent/WO2004087343A1/fr active Application Filing
- 2004-03-01 CN CN200480007561.9A patent/CN1761536B/zh not_active Expired - Fee Related
- 2004-03-01 EP EP04715923A patent/EP1603686B1/fr not_active Expired - Lifetime
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0400510A1 (fr) * | 1989-06-02 | 1990-12-05 | M.A.B. | Installation à table vibrante pour la fabrication de produits en béton |
WO1996006290A1 (fr) * | 1994-08-24 | 1996-02-29 | F.L. Smidth & Co. A/S | Dispositif de compensation de vibrations |
US5903077A (en) * | 1995-09-21 | 1999-05-11 | Moog Inc. | Modular vibratory force generator, and method of operating same |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1790421A1 (fr) * | 2005-11-28 | 2007-05-30 | Eurocopter | Dispositif d'asservissement pour un vibrateur à rotors déséquilibrés |
FR2894040A1 (fr) * | 2005-11-28 | 2007-06-01 | Eurocopter France | Dispositif d'asservissement pour un vibrateur a rotors desequilibres. |
US7471057B2 (en) | 2005-11-28 | 2008-12-30 | Eurocopter | Servo-control system for an unbalanced rotor vibrator |
Also Published As
Publication number | Publication date |
---|---|
EP1603686A1 (fr) | 2005-12-14 |
US7582032B2 (en) | 2009-09-01 |
FR2852648B1 (fr) | 2006-06-30 |
CN1761536B (zh) | 2010-08-11 |
FR2852648A1 (fr) | 2004-09-24 |
CN1761536A (zh) | 2006-04-19 |
EP1603686B1 (fr) | 2009-05-13 |
US20060135302A1 (en) | 2006-06-22 |
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