WO2007143974A1 - Amortisseurs de vibrations et de chocs - Google Patents

Amortisseurs de vibrations et de chocs Download PDF

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Publication number
WO2007143974A1
WO2007143974A1 PCT/DE2007/001024 DE2007001024W WO2007143974A1 WO 2007143974 A1 WO2007143974 A1 WO 2007143974A1 DE 2007001024 W DE2007001024 W DE 2007001024W WO 2007143974 A1 WO2007143974 A1 WO 2007143974A1
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WO
WIPO (PCT)
Prior art keywords
magnets
shock
magnet
spring
vibration damper
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/DE2007/001024
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German (de)
English (en)
Inventor
Gilbert Doko
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Individual
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Individual
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Filing date
Publication date
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=38616409&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=WO2007143974(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Individual filed Critical Individual
Publication of WO2007143974A1 publication Critical patent/WO2007143974A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F6/00—Magnetic springs; Fluid magnetic springs, i.e. magnetic spring combined with a fluid
    • A—HUMAN NECESSITIES
    • A43—FOOTWEAR
    • A43B—CHARACTERISTIC FEATURES OF FOOTWEAR; PARTS OF FOOTWEAR
    • A43B1/00—Footwear characterised by the material
    • A43B1/0054—Footwear characterised by the material provided with magnets, magnetic parts or magnetic substances
    • A—HUMAN NECESSITIES
    • A43—FOOTWEAR
    • A43B—CHARACTERISTIC FEATURES OF FOOTWEAR; PARTS OF FOOTWEAR
    • A43B13/00—Soles; Sole-and-heel integral units
    • A43B13/14—Soles; Sole-and-heel integral units characterised by the constructive form
    • A43B13/18—Resilient soles
    • A43B13/181—Resiliency achieved by the structure of the sole
    • 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
    • F16F2230/00—Purpose; Design features
    • F16F2230/0052—Physically guiding or influencing

Definitions

  • the invention relates to a shock and vibration damper for a two masses and a spring existing vibration system, wherein the mass can be arbitrarily large and arbitrarily sluggish.
  • the invention avoids the disadvantages of the prior art. It is the object of the invention to provide a maintenance and wear-free long
  • the invention consists in that a magnet is attached to each of the two mutually oscillating masses, which exerts forces on the other magnet.
  • the forces can be attractive or repulsive forces, as a spring between the two masses is effective. Between the two masses a certain predetermined distance is specified in the idle state. In this state of rest, the magnets are adjusted to their zero position. As soon as by any external force, the mass is moved out of this rest state position, spring forces, but also magnetic forces are effective, both of which endeavor to return the moving body to its rest state position. While the spring, because of its elasticity, would like to cause the moving mass to oscillate about its rest point, the magnets exert forces that resist this oscillation. These are forces that are greater the greater the amplitude of the vibration. This results in an attenuation of the occurring vibration also and in particular in the case of resonance of the mass-spring system.
  • the magnets can be distributed over two mutually oscillating plates area, but the magnets can also be arranged in this shock and vibration on a holder at a distance from each other and the counter magnets according to a second holder. This one will use, where the shocks are to be intercepted initially strong and later weaker.
  • the distance between the magnets can be created by a non-magnetic component, on each of which rest on both sides of the magnets.
  • the shock and vibration damper may be made of one or more pairs of cooperating magnets, at least one of which has the shape of a cuboid or a circular disk and acts with its one surface on a corresponding surface of the other magnet.
  • the pair of interacting magnets may consist of an outer ring magnet and an inner ring magnet or disc-shaped magnet entering its inner annulus, having the geometry of the inner ring surface on its outer surface.
  • the shock and vibration damper can be accommodated for space saving reasons in the interior of a coil spring.
  • the magnets may be permanent magnets, whose magnetic forces are constant and therefore achieve a constant damping, or the magnets may be electromagnets, whereby an adjustable or controllable damping effect can be achieved.
  • the invention thus relates to a in its vibration behavior to be damped mass-spring system, ie a damper system, for the vibration-isolated storage of vibration generating systems (active vibration isolation of eg machinery, equipment, etc.) and of systems against the outside acting vibrations are to be protected (passive vibration isolation of eg systems, devices, components, etc.).
  • the damper element alone can also be used to reduce in connection with damper masses forced vibrations of elastic systems. It can be used wherever motion sequences need to be controlled or damped. It can be used where motion and vibration properties are to be influenced positively, ie as desired or in the required manner. State of the art in such spring-damper systems is a parallel arrangement of spring elements and damping elements.
  • spring elements are usually steel springs, rubber or other elastomer springs used with and without steel inserts or air springs.
  • the desired damping is usually achieved by flow around a piston moving in a viscous fluid, by friction elements, by the material damping (especially in the case of rubber or other elastomer springs) or by connected additional air volumes (with air springs).
  • the spring-damper system of the invention consists of a spring element (steel spring, rubber (elastomere) spring o. ⁇ .) And a parallel-connected magnetic damper element.
  • the magnets used are commercially available permanent magnets.
  • a spring element and a magnetic damper element are combined in a customized metal housing to form a compact system.
  • the spring-damper system designed in this way is independent of any supply equipment and it is maintenance-free.
  • compact spring-damper systems are manifold. For example, they can be arranged under each machine foot in a vibration-isolating machine. One or more machines can also be installed on a steel structure or a reinforced concrete slab which is mounted vibration-isolated on a sufficient number of compact spring-damper systems. The same applies to vibration-sensitive systems and devices. Individual building ceiling panels can be stored by means of such spring-damper systems vibration isolated from the rest of the building structure on the supporting walls and columns. In vehicle construction, on the one hand vehicle boxes, passenger compartments and the like can be protected against excessive vibrations by means of the spring-damper systems, and on the other hand vibration-generating drives can be installed so that they are vibration-insulated.
  • spring-damper systems can be used wherever the other spring-damper systems mentioned above have been used.
  • Magnetic damper elements without integrated springs can be used as shock absorbers and with damper masses as vibration dampers for elastic structures (eg for reducing torsional forces). vibrations in drive systems or bending vibrations).
  • the natural frequency of the spring-damper system is determined at a constant mass mainly by the stiffness of the built-in spring, and therefore it can also be varied by varying the spring (e.g., choosing a stiffer or softer spring).
  • the insulating effect of the system is determined on the one hand by the tuning ratio (exciter frequency by natural frequency) and on the other hand by the degree of attenuation. The latter can be changed in the magnetic damper element by changing the distance between each two interacting magnets.
  • Fig. 1 shows the structure of a spring-magnet damper system with two oppositely acting magnetic pairs in three sections.
  • Fig. 2 shows the structure of a spring-magnet damper system with a pair of magnets in three sections.
  • Fig. 4 shows the structure of a torsional vibration damper in two sections.
  • Fig. 5 shows the structure of a bending vibration damper in two sections.
  • Fig. 1 the construction of a spring-magnet damper system is shown with two oppositely acting magnetic pairs.
  • the steel housing is divided into two parts. It consists of a fixed lower part 1 and a movable upper part 2. Fixed to the upper part are welded in plan U-shaped steel plates 3. About this, the movable upper housing part is supported on a movably mounted in the lower housing part steel plate 4 from. The plate 4 is only vertically movable by laterally attached to a plate end wheels 5. The welded to the lower steel housing 1 webs 6 prevent horizontal movement of the plate 4. To secure the position of the loosely mounted upper housing part 2 and 3 4 webs 7 are welded to the plate. The plate 4 rests on a spring 8. If necessary, several springs can be arranged.
  • magnets 10 to 13 For vibration damping four permanent magnets 10 to 13 are installed in two oppositely acting pairs. Of these, the magnets 10 and 11 fixedly attached to the plate 4 (eg glued), while the magnets 12 and 13 are adjustable in height by means of screwing in the base blocks 14 and 15.
  • the base block 14 is welded to a steel plate 16, which in turn is fixedly connected to the lower steel housing part.
  • the base pad 15 is welded directly to the lower steel housing part.
  • the magnets 10 and 13 are to be installed so that they repel each other. The same applies to the magnets 11 and 12.
  • the magnets used for example to generate larger magnetic forces, from two or more magnetic pieces (eg discs, rings, etc.) may be composed, if the desired magnetic forces can not be achieved by individual magnets.
  • Fig. 2 the structure of a spring-magnet damper system is shown with a pair of magnets.
  • the steel housing is divided into two parts. It consists of a fixed lower part 1 and a movable upper part 2.
  • Part 2 rests on four springs 4 (if necessary, a different number of springs is possible).
  • To both housing parts 1 and 2 base blocks 5 are welded, in which the permanent magnets 6 and 7 are screwed height adjustable. Both magnets must be installed in such a way that they repel each other.
  • Fig. 3 the structure of a shock absorber is shown.
  • a piston guided in ball bearings moves 2.
  • a permanent magnet pair 3 and 4 Above the piston is a permanent magnet pair 3 and 4, wherein the magnet 3 is fixed on the piston and the magnet 4 on the housing.
  • a second pair of magnets 5 and 6 is arranged in the form of ring magnets, wherein magnet 5 is fixed to the piston and magnet 6 on the housing.
  • the magnets 3 and 4 are installed so that they repel each other.
  • the same applies to the magnets 5 and 6. 4 the structure of a torsional vibration damper is shown.
  • a drive plate 1 is fastened on the axis excited to torsional vibrations.
  • four permanent magnets 2 and 3 are attached (if necessary, another number is possible).
  • damper masses 6 and 7 Opposite to each other more four permanent magnets 4 and 5 are attached to two damper masses 6 and 7 in such a way that the opposite magnets 2 and 4 or 3 and 5 attract each other.
  • the damper masses 6 and 7 are mounted on ball bearings 8 and 9 on the drive plate 1 movable.
  • Four connecting pins 10 couple the two damper masses.
  • a bending vibration damper In Fig. 5, the construction of a bending vibration damper is shown. Between a top steel plate 1 and a bottom steel plate 2, which are interconnected by four bolts 3, a damper mass 4 is arranged. The bolts 3 are passed through holes in the damper mass 4, thereby they can not perform unwanted horizontal but only vertical movements. Above and below the damper mass are two permanent magnet pairs 5 and 6 or 7 and 8 installed. Of these, the magnets 5 and 7 are fixed to the damper mass, the magnet 6 to the lower steel plate 2 and the magnet 8 to the upper steel plate 1. The magnets 5 and 6 are mounted so as to repel each other. The same applies to the magnets 7 and 8.

Landscapes

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

Abstract

La présente invention concerne un amortisseur de vibrations et de chocs pour un système vibrant composé de deux masses et d'un ressort. Le but de la présente invention est de créer un amortisseur de vibrations et de chocs ne nécessitant pas d'entretien qui permet d'amortir efficacement et d'atténuer les vibrations apparaissant. La présente invention consiste en ce qu'un aimant (10-13) exerçant des forces sur les autres aimants soit fixé sur chacune des deux masses vibrant l'une contre l'autre. Les forces peuvent être des forces d'attraction ou de répulsion étant donné qu'un ressort (8) agit entre les deux masses. Un certain écart prédéfini est prescrit entre les deux masses au repos. Dans cet état, la position de repos des aimants est réglée. Dès que l'une des masses est déplacée de cette position de repos par une force extérieure quelconque, les forces du ressort, mais aussi les forces magnétiques, sont actives et visent toutes deux à ramener le corps déplacé dans sa position de repos. Alors qu'en raison de son élasticité le ressort pourrait commencer à faire vibrer la masse mobile autour de son point de repos, des forces s'opposant à cette vibration partent des aimants. Ces forces augmentent au fur et à mesure que l'amplitude de la vibration s'accentue. Il en résulte également un amortissement de la vibration apparaissant, notamment en cas de résonance du système masse/ressort.
PCT/DE2007/001024 2006-06-13 2007-06-12 Amortisseurs de vibrations et de chocs Ceased WO2007143974A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006027636.1 2006-06-13
DE200610027636 DE102006027636B4 (de) 2006-06-13 2006-06-13 Magnetischer Schwingungsdämpfer

Publications (1)

Publication Number Publication Date
WO2007143974A1 true WO2007143974A1 (fr) 2007-12-21

Family

ID=38616409

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2007/001024 Ceased WO2007143974A1 (fr) 2006-06-13 2007-06-12 Amortisseurs de vibrations et de chocs

Country Status (2)

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DE (1) DE102006027636B4 (fr)
WO (1) WO2007143974A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010128822A3 (fr) * 2009-05-08 2011-03-24 웰니스힐스주식회사 Appareil de vibration magnétique utilisant la pression externe et sabot présentant ledit appareil installé à l'intérieur
KR101073499B1 (ko) 2009-05-08 2011-10-17 웰니스힐스 주식회사 압력을 이용한 자석 진동장치
US8474156B2 (en) 2009-09-21 2013-07-02 Sang Gu Kim Vibration generating shoe and vibration device thereof
CN104257004A (zh) * 2014-09-22 2015-01-07 温州碧戈之都鞋业有限公司 缓冲式磁力登山鞋
CN108571550A (zh) * 2018-06-11 2018-09-25 珠海格力电器股份有限公司 钢丝绳减震器及空调设备

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITRM20100586A1 (it) * 2010-11-05 2012-05-06 Drusian Gabriele Permanent magnetic shock-absorber ammortizzatore magnetico perenne
FR2986842B1 (fr) * 2012-02-06 2015-05-29 Jacques Clausin Dispositif de reduction des vibrations actif peu couteux constitue de plots elastiques
AT512747A1 (de) * 2012-03-29 2013-10-15 Leitner Vorrichtung zum federnden Abstützen von Gegenständen
AT513832B1 (de) 2013-09-06 2014-08-15 Ever Loyal Global Co Ltd Vibrationsvorrichtung
US9341224B2 (en) * 2014-05-13 2016-05-17 Google Inc. Systems for absorbing an impact force
DE202014102645U1 (de) 2014-06-06 2015-09-11 Kendrion (Markdorf) Gmbh Drehschwingungsdämpfer sowie Drehschwingungsdämpfersystem
CN105757155B (zh) * 2016-05-06 2018-04-24 哈尔滨工程大学 一种质量可调式半主动吸振装置
DE102020119406A1 (de) 2020-07-22 2022-01-27 Klaus W. Scheibe Hybrider Einrohr-Stossdämpfer
EP4644724A1 (fr) * 2024-05-03 2025-11-05 Solid Tech AB Isolateur de vibrations pour équipement audio
DE102024003283A1 (de) * 2024-10-08 2026-04-09 Joris Paul Iba Stabilisierte Halterung für Getränkebecher an Rollstühlen und Rollatoren

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1805789A1 (de) * 1968-10-29 1970-05-21 Breitbach Dipl Ing Elmar Nichtlineares Federsystem unter Verwendung von Permanentmagneten
DE3202641A1 (de) * 1982-01-28 1983-08-04 Hans-Günter Bieber Daempfung-, federung und pufferung auf gleichpoliger magnet-basis
SU1455084A1 (ru) * 1986-04-22 1989-01-30 Донецкий политехнический институт Виброизол тор
RU1825903C (ru) * 1991-01-26 1993-07-07 Научно-производственный центр "Информационные и транспортные системы" Устройство дл гашени колебаний
GB2264547A (en) * 1992-02-29 1993-09-01 Jaguar Cars Mountings
WO1999017034A1 (fr) * 1997-09-26 1999-04-08 Technische Universiteit Delft Systeme de support magnetique
DE19840244A1 (de) * 1998-09-03 2000-03-30 Burgmann Dichtungswerk Feodor Stoß- und Schwingungsdämpfer, insbesondere zur Aufhängung von Abgasanlagen von Kraftfahrzeugen
EP1030076A1 (fr) * 1999-02-17 2000-08-23 Delta Tooling Co., Ltd. Unité de suspension comprenant un ressort magnétique
EP1172581A2 (fr) * 2000-07-11 2002-01-16 Delta Tooling Co., Ltd. Appareil pour l'amortissement des vibrations utilisant un circuit magnétique
US20030234476A1 (en) * 2000-06-02 2003-12-25 Delta Tooling Co., Ltd. Vibration damping apparatus containing magnetic spring device

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3807655A1 (de) * 1988-03-09 1989-09-28 Bosch Gmbh Robert Vorrichtung zur schwingungsdaempfung
DE3911131A1 (de) * 1989-04-06 1990-10-11 Bosch Gmbh Robert Federungssystem fuer fahrzeuge

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1805789A1 (de) * 1968-10-29 1970-05-21 Breitbach Dipl Ing Elmar Nichtlineares Federsystem unter Verwendung von Permanentmagneten
DE3202641A1 (de) * 1982-01-28 1983-08-04 Hans-Günter Bieber Daempfung-, federung und pufferung auf gleichpoliger magnet-basis
SU1455084A1 (ru) * 1986-04-22 1989-01-30 Донецкий политехнический институт Виброизол тор
RU1825903C (ru) * 1991-01-26 1993-07-07 Научно-производственный центр "Информационные и транспортные системы" Устройство дл гашени колебаний
GB2264547A (en) * 1992-02-29 1993-09-01 Jaguar Cars Mountings
WO1999017034A1 (fr) * 1997-09-26 1999-04-08 Technische Universiteit Delft Systeme de support magnetique
DE19840244A1 (de) * 1998-09-03 2000-03-30 Burgmann Dichtungswerk Feodor Stoß- und Schwingungsdämpfer, insbesondere zur Aufhängung von Abgasanlagen von Kraftfahrzeugen
EP1030076A1 (fr) * 1999-02-17 2000-08-23 Delta Tooling Co., Ltd. Unité de suspension comprenant un ressort magnétique
US20030234476A1 (en) * 2000-06-02 2003-12-25 Delta Tooling Co., Ltd. Vibration damping apparatus containing magnetic spring device
EP1172581A2 (fr) * 2000-07-11 2002-01-16 Delta Tooling Co., Ltd. Appareil pour l'amortissement des vibrations utilisant un circuit magnétique

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010128822A3 (fr) * 2009-05-08 2011-03-24 웰니스힐스주식회사 Appareil de vibration magnétique utilisant la pression externe et sabot présentant ledit appareil installé à l'intérieur
KR101073499B1 (ko) 2009-05-08 2011-10-17 웰니스힐스 주식회사 압력을 이용한 자석 진동장치
CN102413805A (zh) * 2009-05-08 2012-04-11 威尔尼斯希尔公司 利用外压的磁石震动装置及安装该震动装置的鞋
US8474156B2 (en) 2009-09-21 2013-07-02 Sang Gu Kim Vibration generating shoe and vibration device thereof
CN104257004A (zh) * 2014-09-22 2015-01-07 温州碧戈之都鞋业有限公司 缓冲式磁力登山鞋
CN108571550A (zh) * 2018-06-11 2018-09-25 珠海格力电器股份有限公司 钢丝绳减震器及空调设备

Also Published As

Publication number Publication date
DE102006027636A1 (de) 2007-12-20
DE102006027636B4 (de) 2014-03-27

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