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WO1988002076A1 - Systeme oscillatoire se couplant a un dispositif soumis a des oscillations d'excitation et destine a reduire les vibrations sur une bande large - Google Patents

Systeme oscillatoire se couplant a un dispositif soumis a des oscillations d'excitation et destine a reduire les vibrations sur une bande large Download PDF

Info

Publication number
WO1988002076A1
WO1988002076A1 PCT/DE1987/000374 DE8700374W WO8802076A1 WO 1988002076 A1 WO1988002076 A1 WO 1988002076A1 DE 8700374 W DE8700374 W DE 8700374W WO 8802076 A1 WO8802076 A1 WO 8802076A1
Authority
WO
WIPO (PCT)
Prior art keywords
vibration system
spring
vibration
couplable
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/DE1987/000374
Other languages
German (de)
English (en)
Inventor
Walter Elies
Harry Radel
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.)
Makita Engineering Germany GmbH
Original Assignee
Sachs Dolmar 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 Sachs Dolmar GmbH filed Critical Sachs Dolmar GmbH
Publication of WO1988002076A1 publication Critical patent/WO1988002076A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/24—Damping the reaction force
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
    • B23D47/00—Sawing machines or sawing devices working with circular saw blades, characterised only by constructional features of particular parts
    • B23D47/005—Vibration-damping
    • 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
    • F16F7/108—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted on plastics springs

Definitions

  • the vibration system according to the invention can be used wherever a vibration damper is supposed to wipe out vibrations in a larger frequency range.
  • vibration dampers For self or externally driven tools, devices, machines and the like. Mechanical vibrations often occur due to the drive or the working movements. For example, the machine drives act as vibration exciters, but the machining tools also transmit vibrations. Vibration dampers and vibration dampers in a wide variety of forms have already become known for reducing the interference caused by such vibrations.
  • the vibration dampers work in such a way that mechanical vibrations, for example by compression of an enclosed air cushion or by conversion of the kinetic energy as a vibrating mechanical part into flow energy and heat of a hydraulic fluid, work exist, are designed so that the vibration damper has a natural frequency that corresponds to the excitation frequency.
  • the device excited by the excitation frequency does not make any vibrations, but only the mass of the vibration absorber moves, with the result that the amplitudes of the vibrations of the mass of the vibration absorber are not too great.
  • the effectiveness of the vibration actuator is in each case essentially limited to the tuning frequency, and the vibration actuator has a vibration-enhancing rather than damping effect in other areas.
  • a broadband damping of vibrations over a range of excitation vibrations is not possible.
  • Vibration dampers are also not applicable, especially since the storage often becomes too soft, so that precise handling of the device is no longer possible.
  • the invention is intended to develop a vibration damper in such a way that, instead of a repetition frequency, it has a vibration elimination region in which vibrations of the device excited to vibrations are almost eliminated.
  • a system of the type mentioned at the outset in which it is provided that the spring has a spring rate which changes as a function of the excitation frequency.
  • the repayment frequency of the system which depends directly on the spring rate of the spring and the oscillating mass, is changed, so that ideally there is a repayment range, i.e. a range of excitation frequencies in which the vibration mass vibrates uniformly or to different degrees, while the device to which the vibration system is coupled remains at rest.
  • the spring consists of an elastic, open and closed cell foam plastic.
  • the spring By choosing the elasticity and by selecting the ratio of the number of open to the number of closed cells of the foam plastic, it is possible to obtain a spring behavior in the manner described above. At a low frequency, at which there is the possibility of emptying and refilling the open cells of the foam plastic, there is a softer spring rate, while with increasing frequency there is hardening. At the same time, there is the advantage that such a spring hardens even with increasing vibration amplitudes, so that vibration damping can also be achieved here.
  • Such springs can preferably consist of polyurethane rubber, polyurethane foam or an elastically cross-linked silicone rubber, preferably a homogeneous, approximately incompressible, elastic, cross-linked silicone rubber being selected.
  • the vibration system consists of a cylindrical solid body as a vibrating mass with an almost constant, high density and at least one ring body encompassing the cylinder body as a spring.
  • the system can be designed to be as small as it is effective, and the basic system can be optimally adapted to the various possible repayment areas, since the oscillating mass can be simply lengthened or shortened and a corresponding number of ring bodies can be arranged a suitable range can be selected without the system having to be subjected to fundamental changes.
  • the annular body has on its outer surface regularly arranged conical, cylindrical, cube-shaped or other suitable geometric shape supporting knobs or supporting ribs.
  • this results in an even better adaptability of the spring rate to the specified conditions, since the support knobs have a spring rate in a range other than the range of the spring rate of the ring body and by the selection of the size of the support knobs Size of the ring body the range selection for the described above Spring rate becomes particularly possible.
  • the support knobs also allow the system to be easily adapted to the various applications in such a way that the system can be coupled to the device loaded with the excitation vibrations without extensive prior vibration tests and by changing the spring behavior by simple means Cutting away, burning away or the like. the support knobs the spring rate can be changed, so that it can then be determined in which form of the spring the desired vibration elimination range occurs.
  • F i g. 1 shows a vibration system arranged in a machine part in the form of a tube in a vertical sectional view
  • F i g. 2 shows the vibration system according to FIG. 1 in a vertical sectional view according to line II-II in FIG. 1,
  • F i g. 3 shows a further embodiment of a ring body
  • F i g. 4 shows a further embodiment of the vibration system in a vertical sectional view
  • F i g. 5 shows the vibration system according to FIG. 4 in a vertical sectional view according to line VV in FIG. 4
  • F i g. 6 shows a further embodiment of a vibration system in a vertical sectional view
  • F i g. 9 shows a further embodiment of a vibration system in a vertical sectional view.
  • the oscillating mass 10 is designed as a cylindrical solid body 11, which has an almost constant, high density and can be made of lead, for example.
  • Ring bodies 30, which are approximately disc-shaped and have a rectangular cross section, are pushed onto the solid body 11 and are supported on the inner wall 41 of a machine part designed as a tubular body 40, as shown in FIG. 2.
  • the spring 20, which is designed as an annular body 30, forms the connection between the oscillating mass 10 and the tubular body 40, which via the excitation vibrations acting on the machine part. Spring 20 transferred to the oscillating mass 10.
  • FIG. 1 is designated by 100 and consists of an oscillating mass designated by 10 ? and a spring 20.
  • the oscillating mass 10 is designed as a cylindrical solid body 11, which has an almost constant, high density and can be made of lead, for example.
  • Ring bodies 30, which are approximately disc-shaped and have a rectangular cross section, are pushed onto the solid body 11 and are supported on the inner wall 41 of a machine part designed as a tubular body 40
  • FIG 3 shows a preferred embodiment of the ring body 130, which has an approximately rectangular cross section Q and in which the outer radius R decreases in the longitudinal direction L of the cylindrical solid body, not shown in the drawing.
  • the vibration system shown in FIGS. 4 and 5 shows two further design options for the spring 20.
  • the annular body 230 acting as a spring 20 is formed over the entire length of the solid body 10, which makes the vibration system 200 easier to handle and, on the other hand, is Provide the ring body 230 on its outer surface 231 with a triangular cross-section having support ribs 235, which result in the above-described, particularly good adaptability of the vibration system 200 to the particular vibration given by the excitation vibrations acting on the machine part 40 - and redemption terms.
  • FIGS. 6 and 7 show a further embodiment of the vibration system 300, in which the ring bodies 330 placed on the solid body 10 are disc-shaped in their basic form, with indentations in the ring bodies 331 are introduced. It follows from this that the ring body, which supports the solid body 10 on the machine part 40, has an approximately Maltese-shaped outer shape.
  • This embodiment has the particular advantage that it is possible to provide a controlled change in the spring rate via the excitation amplitude in addition to the change in the spring rate of the ring bodies 330 acting as spring 20 via the excitation frequency, since the Shaping results in a change in the spring rate with increasing or decreasing excitation amplitude.
  • a preferred field of application for the novel vibration system arises in the area of lawnmowers, free cutters and in particular in motor chain saws, since here the device body has a multiplicity of tubular machine parts.
  • the use of the vibration system is possible here without any problems, and it can preferably be provided that the vibration system is arranged in a container which is displaceable within the machine part, in order to avoid difficulties occurring at a certain point in a certain fre ⁇ to repay the quenz range optimally. 4
  • the vibration system 300 consisting of the solid body 10 and the ring bodies 330 is therefore arranged in a pot-shaped container 50, which can be closed by a cover part 51 and can be moved within the machine part 40 in the direction indicated by the arrow X.
  • this embodiment can be used particularly advantageously where vibrations occur in a finished system. Since here a subsequent optimization of the vibration attenuation or repayment is possible only with great effort, a container containing a vibration system of the type described above can now be moved within the device body without problems and then arranged firmly where the vibrations occur more intensely and are to be repaid.
  • the vibration systems described above and shown in the drawing have essentially annular springs.
  • the springs for example, rectangular or square, in order to create a system that works in the same way, e.g. to be arranged between two housing walls or in a tube piece with a square or rectangular cross section.
  • Other suitable geometric shapes are also conceivable, it being possible to provide or foam-fill spaces or cavities resulting in the machine housing with suitable properties and to arrange a vibrating mass of a suitable type therein.
  • the basic idea of the invention is realized, which consists in the fact that the spring rate of the spring changes as a function of the excitation frequency and / or of the excitation amplitude, and thus a vibration reduction or elimination is achieved in an excitation frequency range.
  • FIG. 8 therefore shows a further embodiment of the vibration system 400, in which the vibration mass 10 is designed as a solid body 111.
  • the solid body 111 is surrounded by a hollow spherical spring body 430, which acts as a spring.
  • Training the Vibrating mass 10 as a ball has the very essential advantage that the vibrating mass IT adjusts itself automatically in the direction predetermined by the vibration excitation. A vibration system has thus been created which has the desired properties uniformly in all directions and in which a specific setting is no longer necessary.
  • the vibration system 400 is arranged in a container 150 consisting of two hemispherical shells 151, 152, the vibration system 400 can be arranged within the device without any problems.
  • This vibration system also has the advantage that subsequent optimization can be carried out with little effort by displacing the container 150 containing the vibration system 400 within the device and arranging it firmly where the vibrations occur and are to be repaid.

Landscapes

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

Abstract

Dans le système décrit comportant une masse oscillante et un ressort, le ressort (20) présente un taux d'élasticité (C) variant en fonction de la fréquence d'excitation OMEGA. Le système oscillatoire (100) comporte comme masse oscillante (10) un corps plein (11) cylindrique à densité élevée pratiquement constante, et comme ressort (20) au moins un corps annulaire (30) enveloppant le corps du cylindre.
PCT/DE1987/000374 1986-09-11 1987-08-21 Systeme oscillatoire se couplant a un dispositif soumis a des oscillations d'excitation et destine a reduire les vibrations sur une bande large Ceased WO1988002076A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19863630870 DE3630870A1 (de) 1986-09-11 1986-09-11 An eine erregerschwingungsbeaufschlagte vorrichtung zur breitbandigen schwingungsverringerung ankoppelbares schwingungssystem
DEP3630870.6 1986-09-11

Publications (1)

Publication Number Publication Date
WO1988002076A1 true WO1988002076A1 (fr) 1988-03-24

Family

ID=6309329

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE1987/000374 Ceased WO1988002076A1 (fr) 1986-09-11 1987-08-21 Systeme oscillatoire se couplant a un dispositif soumis a des oscillations d'excitation et destine a reduire les vibrations sur une bande large

Country Status (2)

Country Link
DE (1) DE3630870A1 (fr)
WO (1) WO1988002076A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0399615A3 (fr) * 1989-05-25 1991-02-27 Marinus Johannes Meijers Bicyclette
AT401965B (de) * 1994-10-27 1997-01-27 Pfeffer Peter Ernst Torsionsschwingungsisolator
EP1736283A3 (fr) * 2005-06-23 2008-05-14 Black & Decker, Inc. Mécanisme d'amortissement de vibrations pour un marteau perforateur
WO2009077228A1 (fr) * 2007-12-17 2009-06-25 Robert Bosch Gmbh Outil électrique à main, en particulier marteau perforateur et/ou burineur, avec une unité d'amortissement

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4207910C2 (de) * 1992-03-12 1994-06-01 Siemens Ag Resonanzvermindernde Ummantelung für einen Körperschallsensor
DE19821165A1 (de) 1998-05-12 1999-11-18 Volkswagen Ag Übertragungselement zur Kraft- und/oder Momentenübertragung, Schwingungstilger und Verfahren zur Dämpfung von Schwingungen
US7125048B2 (en) 2002-11-06 2006-10-24 Lear Corporation Dampener
DE10327770B4 (de) 2003-06-17 2022-04-07 Volkswagen Ag Anordnung eines Schwingungstilgers in Kraftfahrzeugsitzen
CN104791405B (zh) * 2015-04-27 2017-01-25 江苏欣捷诺环境工程技术有限公司 一种齿形减振器
DE102017106019B4 (de) * 2017-03-21 2021-12-23 WEGU GmbH Schwingungsdämpfung Schwingungstilger mit Auslenkungsbegrenzern für seine an zwei Enden elastisch gelagerte Tilgermasse
CN106870629A (zh) * 2017-03-31 2017-06-20 桂林电子科技大学 一种具有消除刚性壳体震动功能的震动消除装置及附加式实验分析装置

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB764507A (en) * 1954-12-09 1956-12-28 Blackburn & Gen Aircraft Ltd Improvements in or relating to vibration dampers
US2838137A (en) * 1955-01-17 1958-06-10 Lord Mfg Co Self tuning vibration absorber
US3075406A (en) * 1961-07-13 1963-01-29 Gen Motors Corp Propeller shaft damper
DE1800960A1 (de) * 1967-10-12 1969-06-19 Cincinnati Milling Machine Co Schwingungsdaempfer fuer Werkzeugmaschinen
FR2149919A5 (fr) * 1971-08-05 1973-03-30 Stihl Andreas Maschinen
DE2302732A1 (de) * 1972-01-21 1973-07-26 Trondhjems Nagle Spigerfab Einstellbare daempfungsvorrichtung
DE2440364A1 (de) * 1974-08-23 1976-03-04 Maschf Augsburg Nuernberg Ag Einrichtung zum daempfen von drehschwingungen bei mehrzylinder-hubkolbenmaschinen
US4050665A (en) * 1976-02-11 1977-09-27 Newport Research Corporation Vibration damping apparatus
FR2468036A1 (fr) * 1979-10-23 1981-04-30 Knoll Fritz Dispositif pour l'absorption d'energie cinetique
US4282938A (en) * 1978-03-25 1981-08-11 Yokosuka Boat Kabushiki Kaisha Vibration insulation device for handle of vibratory machine
GB2100832A (en) * 1981-07-01 1983-01-06 Porsche Ag Vibration absorber in motor vehicle transmission

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB764507A (en) * 1954-12-09 1956-12-28 Blackburn & Gen Aircraft Ltd Improvements in or relating to vibration dampers
US2838137A (en) * 1955-01-17 1958-06-10 Lord Mfg Co Self tuning vibration absorber
US3075406A (en) * 1961-07-13 1963-01-29 Gen Motors Corp Propeller shaft damper
DE1800960A1 (de) * 1967-10-12 1969-06-19 Cincinnati Milling Machine Co Schwingungsdaempfer fuer Werkzeugmaschinen
FR2149919A5 (fr) * 1971-08-05 1973-03-30 Stihl Andreas Maschinen
DE2302732A1 (de) * 1972-01-21 1973-07-26 Trondhjems Nagle Spigerfab Einstellbare daempfungsvorrichtung
DE2440364A1 (de) * 1974-08-23 1976-03-04 Maschf Augsburg Nuernberg Ag Einrichtung zum daempfen von drehschwingungen bei mehrzylinder-hubkolbenmaschinen
US4050665A (en) * 1976-02-11 1977-09-27 Newport Research Corporation Vibration damping apparatus
US4282938A (en) * 1978-03-25 1981-08-11 Yokosuka Boat Kabushiki Kaisha Vibration insulation device for handle of vibratory machine
FR2468036A1 (fr) * 1979-10-23 1981-04-30 Knoll Fritz Dispositif pour l'absorption d'energie cinetique
GB2100832A (en) * 1981-07-01 1983-01-06 Porsche Ag Vibration absorber in motor vehicle transmission

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0399615A3 (fr) * 1989-05-25 1991-02-27 Marinus Johannes Meijers Bicyclette
AT401965B (de) * 1994-10-27 1997-01-27 Pfeffer Peter Ernst Torsionsschwingungsisolator
EP1736283A3 (fr) * 2005-06-23 2008-05-14 Black & Decker, Inc. Mécanisme d'amortissement de vibrations pour un marteau perforateur
US7451833B2 (en) 2005-06-23 2008-11-18 Black & Decker Inc. Vibration dampening mechanism
EP2017040A1 (fr) * 2005-06-23 2009-01-21 Black & Decker, Inc. Mécanisme d'amortissement de vibrations pour un marteau perforateur
WO2009077228A1 (fr) * 2007-12-17 2009-06-25 Robert Bosch Gmbh Outil électrique à main, en particulier marteau perforateur et/ou burineur, avec une unité d'amortissement
RU2499662C2 (ru) * 2007-12-17 2013-11-27 Роберт Бош Гмбх Ручная электрическая машина, прежде всего перфоратор и/или отбойный молоток, с динамическим виброгасителем
US8783377B2 (en) 2007-12-17 2014-07-22 Robert Bosch Gmbh Hand-held power tool, particularly a rotary and/or chisel hammer, having a vibration absorbing unit

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Publication number Publication date
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