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WO1999061815A1 - Amortisseur de vibrations actif - Google Patents

Amortisseur de vibrations actif Download PDF

Info

Publication number
WO1999061815A1
WO1999061815A1 PCT/EP1999/002541 EP9902541W WO9961815A1 WO 1999061815 A1 WO1999061815 A1 WO 1999061815A1 EP 9902541 W EP9902541 W EP 9902541W WO 9961815 A1 WO9961815 A1 WO 9961815A1
Authority
WO
WIPO (PCT)
Prior art keywords
leaf springs
vibration damper
damper according
support
mass
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/EP1999/002541
Other languages
German (de)
English (en)
Inventor
Mathias Gugsch
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.)
Trelleborg Automotive Germany GmbH
Original Assignee
BTR AVS Technical Centre 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 BTR AVS Technical Centre GmbH filed Critical BTR AVS Technical Centre GmbH
Publication of WO1999061815A1 publication Critical patent/WO1999061815A1/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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/32—Belleville-type springs
    • F16F1/324—Belleville-type springs characterised by having tongues or arms directed in a generally radial direction, i.e. diaphragm-type springs
    • F16F1/326—Belleville-type springs characterised by having tongues or arms directed in a generally radial direction, i.e. diaphragm-type springs with a spiral-like appearance
    • 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
    • F16F7/00—Vibration-dampers; Shock-absorbers
    • F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
    • F16F7/1005—Vibration-dampers; Shock-absorbers using inertia effect characterised by active control of the mass
    • F16F7/1011—Vibration-dampers; Shock-absorbers using inertia effect characterised by active control of the mass by electromagnetic 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
    • F16F7/00—Vibration-dampers; Shock-absorbers
    • F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
    • F16F7/104—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted
    • F16F7/116—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted on metal springs

Definitions

  • the invention relates to an active vibration damper with a magnetically excitable damper mass which is fastened to a support by means of mutually parallel, spaced leaf springs, the damper mass being movable to and fro in a direction perpendicular to the leaf springs in such a way that movements of the support in this direction at least partially suppressed.
  • Such a vibration damper is used in particular in engine mounts for motor vehicles and suppresses vibrations emanating from the engine.
  • the vibration damper is usually attached to the body side.
  • a vibration damper of the type mentioned is known from JP-A 6-58368.
  • This publication describes an active vibration damper with a magnetically excitable door mass.
  • the absorber mass is fastened to a support designed as a housing by means of two leaf springs spaced apart from one another and can oscillate in a direction perpendicular to the leaf springs.
  • the absorber mass has a magnet and an air gap into which a moving coil attached to the support engages.
  • a magnetic field is generated by applying an electric current to the moving coil the magnet of the absorber mass acts. This sets the absorber mass in motion.
  • the movement of the absorber mass serves to at least partially suppress movements of the support in the same direction.
  • a disadvantage of this known vibration damper is that the absorber mass can only make small movements, since the deformable length of the leaf springs is only very small. In order to achieve satisfactory movements, the support surrounding the absorber mass must be made large so that the entire vibration damper has large dimensions.
  • Another active vibration damper is known from DE 43 01 845 C1.
  • This document describes an active vibration damper with a magnetically excitable damper mass, which is attached to a support by leaf springs spaced apart.
  • the absorber mass is provided with an additional guide opposite the support. This guide must be worked very precisely to ensure good mobility of the absorber mass and to prevent tilting.
  • the leaf springs have at least two spirally curved leaf spring arms which extend from an outer region to an inner region of the leaf springs.
  • the invention is based on the fact that the possibility of movement of the absorber mass is determined by the deformable length of the leaf springs. This deformable length is increased by the spiral design of the leaf spring arms without changing the overall dimensions of the vibration damper. At the same time, great rigidity in the radial direction is achieved. An additional guidance of the absorber mass in relation to the support is therefore not necessary.
  • the vibration damper according to the invention allows the use of one-piece leaf springs, so that the assembly effort can be minimized.
  • the leaf spring arms are involute-curved. In this way, a maximum length of the leaf spring arms is achieved, and the diameter of the leaf spring can be kept small.
  • the leaf springs preferably have three leaf spring arms which are bent in a spiral shape and distributed uniformly over the circumference. Very good radial guidance of the absorber mass is achieved by using three leaf spring arms.
  • the inner area of the leaf springs advantageously has an opening for attachment to the absorber mass.
  • clamping rings engage in these openings and can be fixed to the absorber mass.
  • Leaf springs and absorber mass are reliably held together and centered through the openings and the clamping rings.
  • the absorber mass has a central inner bore, which is penetrated by a screw for fastening the clamping rings, one clamping ring receiving the head of the screw and the other clamping ring having an internal thread into which the screw engages.
  • the clamping rings can thus be easily clamped against each other by the screw.
  • the damper mass has cylindrical, centrally arranged projections onto which spacers are attached.
  • the inner areas of the leaf springs are clamped between the spacers and the clamping rings.
  • the outer regions are clamped between a coil carrier and a cover, which are rigidly attached to the support.
  • the bobbin is used to attach a bobbin, while the lid provides protection against dirt, dust and moisture. Separate fastening elements are not required, so that the overall weight of the vibration damper according to the invention is reduced and assembly is made easier.
  • a spacer tube arranged between the leaf springs and on which the coil carrier rests is advantageously provided.
  • the distance between the supports on the leaf spring supports corresponds to the total length of the spacer tube and coil holder. This distance can be changed quickly and easily by changing the spacer tube.
  • the support has a jacket for receiving and guiding the leaf springs, the spacer tube, the bobbin and the cover. All of the components mentioned are accommodated in the jacket and are aligned and guided concentrically to one another by this. For assembly, the individual elements only have to be inserted into the jacket. The centering takes place automatically, so that the assembly is simplified. At the same time, the jacket serves as protection against dirt, dust and moisture.
  • the jacket has an extension on its inside as a stop for a first leaf spring. This approach ensures a defined position of the first leaf spring in relation to the support. The spacer tube, the bobbin, the second leaf spring and the cover are placed on the first leaf spring. All components are thus in a defined position in relation to the shoulder and thus to the support.
  • the absorber mass advantageously has a magnet and two masses which enclose the magnet between them. This configuration allows the use of a relatively small magnet, so that the costs for the absorber mass are reduced.
  • the absorber mass advantageously forms a gap into which a coil engages for the magical excitation of the absorber mass. Due to the very good radial guidance of the absorber mass, a particularly narrow air gap can be achieved, which is an advantage for a good energy yield.
  • Vibration absorber Figure 3 is a plan view of a leaf spring.
  • Figure 2 shows a section along the line II-II in Figure 1;
  • FIG. 4 shows an enlargement of the detail X from FIG. 1;
  • FIG. 5 shows an enlargement of the detail Y from FIG. 1;
  • Figure 1 shows an active vibration damper 1 0 with a support 1 1, which has a jacket 1 2 with an inner shoulder 1 3.
  • the jacket 1 2 delimits an interior in which a damper mass is arranged which has a magnet 1 4 and two masses 1 5, 1 6 adjoining the magnet.
  • the absorber mass 1 4, 1 5, 1 6 forms a gap 1 7, in which a coil 1 8 engages.
  • the coil 1 8 is attached to a coil support 1 9.
  • Two mutually parallel spaced leaf springs 20, 21 are provided for fastening and guiding the damper mass 1 4, 1 5, 1 6.
  • the leaf springs 20, 21 are attached to the absorber mass 1 4, 1 5, 1 6 with an inner region 33 and to the support 1 1 with an outer region 32.
  • Spacers 23, 24 and a spacer tube 22 connected to the damper mass 1 4, 1 5, 1 6 are used to adjust the distance between the leaf springs 20, 21.
  • Clamping rings 25, 26 are provided for fastening the leaf springs 20, 21 to the absorber mass 1 4, 1 5, 1 6. These clamping rings 25, 26 pass through an opening 39 in the inner region 33 of the leaf springs 20, 21 (cf. FIG. 5). The inner regions 33 of the leaf springs 20, 21 are accommodated between the clamping rings 25, 26 and the associated spacers 23, 24.
  • a screw 27 is provided which passes through an inner bore 28 in the mass 1 5.
  • the upper clamping ring 26 receives the screw head, while the lower clamping ring 25 has an internal thread 42 into which the screw 27 is screwed. By tightening the screw 27, the clamping rings 25, 26 are braced against each other and thus press the inner regions 33 of the Leaf springs 20, 21 on the spacers 23, 24 and the spacers 23, 24 on the mass 1 5.
  • the spacers 23, 24 are seated on centrally arranged, cylindrical projections 40, 41 of mass 1 5 and are thus aligned concentrically with absorber mass 1 4, 1 5, 1 6.
  • the clamping rings 25 26 engage in inner recesses of the spacers 23, 24 and are thereby centered.
  • the centering of the leaf springs 20, 21 takes place by the inner region 33 abutting the clamping rings 25, 26.
  • the spacers 23, 24 can also be formed in one piece with the mass 1 5.
  • the coil carrier 1 9 with the coil 1 8 is first placed on the absorber mass 1 4, 1 5, 1 6.
  • the coil 1 8 engages in the gap 1 7.
  • the spacer tube 22 is slipped over the absorber mass 1 4, 1 5, 1 6, so that it bears against the coil carrier 1 9.
  • the assembly thus created is inserted from above into the casing 1 2 of the support 1 1 until the lower Leaf spring 20 rests on the neck 1 3.
  • the cover 29 is inserted and connected to the jacket 1 2 in a manner not shown.
  • the Til ⁇ germasse 14, 1 5, 1 6 is thus displaceable in the axial direction via the leaf springs 20, 21 relative to ⁇ over the support 1 1, but rigidly attached in the radial direction.
  • An opening, not shown, is provided for the energy supply, through which suitable supply lines (not shown) are passed.
  • the support 11 is provided with a plurality of bores 31. These bores can either be formed in a circumferential flange or, as shown in particular in FIG. 2, in an extension 30 of the support 11. The use of approaches 30 reduces the total weight of the vibration damper 10.
  • FIG. 3 shows a top view of a leaf spring 20, which is identical to the leaf spring 21.
  • the leaf spring 20 has an outer region 32 and an inner region 33 with the opening 39.
  • the outer region 32 and the inner region 33 are connected via three spirally curved leaf spring arms 35, which are separated from one another by recesses 34 which also run spirally.
  • the edges 36 of each leaf spring arm 35 are involute-curved, and the end regions 37, 38 of the recesses 34 are each rounded.
  • the leaf spring arms 35 extend spirally around the inner region 33 before they open into the latter. A displacement of the inner region 33 in the radial direction deforms all leaf spring arms 35 so that high restoring forces are achieved. At the same time, the length of the leaf spring arms 35 is increased.
  • FIG. 4 shows an enlarged illustration of the detail X from FIG. 1, in which the fastening of the outer region 32 of the leaf spring 21 is shown.
  • the outer diameter of the leaf spring 21 is matched to the inner diameter of the casing 1 2 such that the leaf spring 21 is received in the casing 1 2 essentially without play.
  • the outer region 32 is clamped in from below by the coil support 19 and from above by the cover 29 and is axially fixed in this way.
  • FIG. 5 shows an enlarged illustration of the detail Y from FIG. 1, in which the fastening of the inner region 33 of the leaf spring 21 is shown.
  • the clamping ring 26 has an essentially cylindrical section 43 which is provided at one end with an outwardly projecting flange 44 and at the other end with an inwardly projecting flange 45 with an opening 46 for the screw 27. The head of the screw 27 is received in the interior of section 43.
  • the outer diameter of the section 43 corresponds to the inner diameter of the opening 39 in the inner region 33 of the leaf spring 21 and the inner diameter of the spacer 24.
  • the leaf spring 21 is thus guided to the section 43 of the clamping ring 26 essentially without play.
  • the clamping ring 26 is in turn guided without play on the spacer 24, which in turn is guided without play on the shoulder 41 of the mass 15. Very good radial guidance is achieved in this way.
  • the inner region 33 of the leaf spring 21 is received between the spacer 24 and the flange 44 of the clamping ring 26.
  • the clamping ring 26 is clamped to the mass 15 by the flange 45 and the screw 27 with the opposite clamping ring 25.
  • the inner region 33 of the leaf spring 21 is axially immovably fastened to the absorber mass.
  • the opposite leaf spring 20 is attached analogously.
  • the absorber mass 1 4, 1 5, 1 6 is thus guided in a direction perpendicular to the leaf springs 20, 21 opposite the support 1 1.
  • An additional guide, for example between the spacer tube 22 and the absorber mass 14, 15, 16 is not necessary.
  • the length of the leaf spring arms 35 is significantly increased while the outer diameter of the leaf spring 20 remains the same. This will allow the total allowable movement of the absorber mass

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Vibration Prevention Devices (AREA)

Abstract

L'invention concerne un amortisseur de vibrations actif comprenant une matière d'amortissement (14, 15, 16), fixée sur un élément d'appui (11) par des ressorts à lame (20, 21) à distance les uns des autres. La matière d'amortissement (14, 15, 16) peut effectuer un mouvement de va-et-vient dans un sens perpendiculaire aux ressorts à lame (20, 21), de manière que les mouvements de l'éléments d'appui (11) soient supprimés au moins en parti dans ce sens. Les ressorts à lame (20, 21) présentent au moins deux branches (35) cintrées en spirale, qui s'étendent entre une zone extérieure (32) et une zone intérieure (33) des ressorts à lame (20, 21).
PCT/EP1999/002541 1998-05-27 1999-04-15 Amortisseur de vibrations actif Ceased WO1999061815A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1998123716 DE19823716A1 (de) 1998-05-27 1998-05-27 Aktiver Schwingungstilger
DE19823716.2 1998-05-27

Publications (1)

Publication Number Publication Date
WO1999061815A1 true WO1999061815A1 (fr) 1999-12-02

Family

ID=7869099

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1999/002541 Ceased WO1999061815A1 (fr) 1998-05-27 1999-04-15 Amortisseur de vibrations actif

Country Status (2)

Country Link
DE (1) DE19823716A1 (fr)
WO (1) WO1999061815A1 (fr)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7115112B2 (en) 2002-09-02 2006-10-03 Unomedical A/S Device for subcutaneous administration of a medicament to a patient and tubing for same
US7147623B2 (en) 2002-02-12 2006-12-12 Unomedical A/S Infusion device with needle shield
US7258680B2 (en) 2002-09-02 2007-08-21 Unomedical A/S Device for subcutaneous administration of a medicament to a patient
USD554253S1 (en) 2003-10-15 2007-10-30 Unomedical A/S Medical infusion device
USD576267S1 (en) 2003-10-15 2008-09-02 Unomedical A/S Medical infusion device
USD579541S1 (en) 2003-10-15 2008-10-28 Unomedical A/S Medical insertion device
US7481794B2 (en) 2003-02-12 2009-01-27 Unomedical A/S Cover
US7594909B2 (en) 2002-09-02 2009-09-29 Unomedical, A/S Apparatus and method for adjustment of the length of an infusion tubing
US7621395B2 (en) 2005-06-28 2009-11-24 Unomedical A/S Packing for infusion set and method of applying an infusion set
US7867200B2 (en) 2004-12-10 2011-01-11 Unomedical A/S Inserter
US8221355B2 (en) 2004-03-26 2012-07-17 Unomedical A/S Injection device for infusion set
US20170058984A1 (en) * 2015-08-30 2017-03-02 The Boeing Company Self-tuning tunable mass dampers
US10369277B2 (en) 2005-09-12 2019-08-06 Unomedical A/S Invisible needle

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL1017427C2 (nl) 2001-02-22 2002-08-23 Tno Bladveer en elektromagnetische actuator voorzien van een bladveer.
NL1017426C2 (nl) 2001-02-22 2002-08-23 Tno Werkwijze voor het vervaardigen van een elektromagnetische spoel, inrichting verkregen met de werkwijze alsmede actuator.
FR2825768B1 (fr) * 2001-06-06 2004-03-12 Vibrachoc Sa Dispositif d'amortissement de vibrations
DE10255019B4 (de) * 2002-11-25 2006-04-13 Sachsenring Zwickau Ag Schwingungstilger
DE20219398U1 (de) * 2002-12-13 2003-03-06 Gesellschaft zur Förderung angewandter Optik, Optoelektronik, Quantenelektronik und Spektroskopie e.V., 12489 Berlin Stellmotor für axiale Stellbewegungen
US7320455B2 (en) * 2003-10-24 2008-01-22 Newport Corporation Instrumented platform for vibration-sensitive equipment
DE102004001470B4 (de) * 2004-01-08 2005-11-03 Eurocopter Deutschland Gmbh Mechanischer Resonator
WO2010053933A1 (fr) * 2008-11-04 2010-05-14 Lord Corporation Générateur de force inertielle résonant à fréquence propre stable
FR2964579B1 (fr) * 2010-09-15 2012-09-28 Peugeot Citroen Automobiles Sa Batteur actif comportant une piece d'equilibrage et vehicule automobile equipe d'un tel batteur
KR101752645B1 (ko) 2011-02-04 2017-06-30 로오드 코포레이션 공진 관성형 액추에이터를 구비한 회전익 항공기 진동 제어 시스템
CN103883671B (zh) * 2012-12-21 2016-06-29 中国直升机设计研究所 一种撑杆内置吸振装置
DE102013011928A1 (de) 2013-06-26 2015-01-15 Aim Infrarot-Module Gmbh Ausgleichsschwingvorrichtung
GB2610822B (en) * 2021-09-15 2025-07-23 Bae Systems Plc Resonator, resonator array, vibration control system and method
WO2023041898A1 (fr) * 2021-09-15 2023-03-23 Bae Systems Plc Résonateur, réseau de résonateurs, système de régulation de vibrations et procédé
GB2612183B (en) * 2021-09-15 2024-06-19 Bae Systems Plc Resonator, resonator array, vibration control system and method
EP4151879A1 (fr) * 2021-09-15 2023-03-22 BAE SYSTEMS plc Résonateur, réseau de résonateurs, et système et procédé de contrôle de vibrations
US20250137512A1 (en) * 2023-10-30 2025-05-01 Cryo Tech Ltd. Tuned dynamic counter-balancer with magnetic spring

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GB763560A (en) * 1954-11-23 1956-12-12 Kelvin & Hughes Ltd Improvements in or relating to spring suspension devices
US4238845A (en) * 1979-04-10 1980-12-09 Mark Products, Incorporated Geophone springs
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US4922159A (en) * 1988-05-09 1990-05-01 Harris Corporation Linear precision actuator with accelerometer feedback
EP0547469A1 (fr) * 1991-12-17 1993-06-23 Metzeler Gimetall Ag Support élastique actif
FR2765647A1 (fr) * 1997-07-07 1999-01-08 Jacques Clausin Reducteur de vibrations monoaxe accorde a bande large et de grande legerete

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DE3807655A1 (de) * 1988-03-09 1989-09-28 Bosch Gmbh Robert Vorrichtung zur schwingungsdaempfung
JPH0658368A (ja) * 1992-08-10 1994-03-01 Hitachi Seiko Ltd 振動制御装置の吸振器

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GB763560A (en) * 1954-11-23 1956-12-12 Kelvin & Hughes Ltd Improvements in or relating to spring suspension devices
US4238845A (en) * 1979-04-10 1980-12-09 Mark Products, Incorporated Geophone springs
JPS5874931A (ja) * 1981-10-30 1983-05-06 Hitachi Ltd 慣性反力式加振機
US4710656A (en) * 1986-12-03 1987-12-01 Studer Philip A Spring neutralized magnetic vibration isolator
US4922159A (en) * 1988-05-09 1990-05-01 Harris Corporation Linear precision actuator with accelerometer feedback
EP0547469A1 (fr) * 1991-12-17 1993-06-23 Metzeler Gimetall Ag Support élastique actif
FR2765647A1 (fr) * 1997-07-07 1999-01-08 Jacques Clausin Reducteur de vibrations monoaxe accorde a bande large et de grande legerete

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Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7147623B2 (en) 2002-02-12 2006-12-12 Unomedical A/S Infusion device with needle shield
US7258680B2 (en) 2002-09-02 2007-08-21 Unomedical A/S Device for subcutaneous administration of a medicament to a patient
US7115112B2 (en) 2002-09-02 2006-10-03 Unomedical A/S Device for subcutaneous administration of a medicament to a patient and tubing for same
US7594909B2 (en) 2002-09-02 2009-09-29 Unomedical, A/S Apparatus and method for adjustment of the length of an infusion tubing
US7481794B2 (en) 2003-02-12 2009-01-27 Unomedical A/S Cover
USD554253S1 (en) 2003-10-15 2007-10-30 Unomedical A/S Medical infusion device
USD579541S1 (en) 2003-10-15 2008-10-28 Unomedical A/S Medical insertion device
USD576267S1 (en) 2003-10-15 2008-09-02 Unomedical A/S Medical infusion device
US8221355B2 (en) 2004-03-26 2012-07-17 Unomedical A/S Injection device for infusion set
US7867200B2 (en) 2004-12-10 2011-01-11 Unomedical A/S Inserter
US7621395B2 (en) 2005-06-28 2009-11-24 Unomedical A/S Packing for infusion set and method of applying an infusion set
US10369277B2 (en) 2005-09-12 2019-08-06 Unomedical A/S Invisible needle
US20170058984A1 (en) * 2015-08-30 2017-03-02 The Boeing Company Self-tuning tunable mass dampers
US9587699B1 (en) * 2015-08-30 2017-03-07 The Boeing Company Self-tuning tunable mass dampers

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