DE2951526A1 - Vibration damper with spring - has fluid transmission with primary and secondary bellows of different cross=section accelerating swing mass - Google Patents

Vibration damper with spring - has fluid transmission with primary and secondary bellows of different cross=section accelerating swing mass

Info

Publication number
DE2951526A1
DE2951526A1 DE19792951526 DE2951526A DE2951526A1 DE 2951526 A1 DE2951526 A1 DE 2951526A1 DE 19792951526 DE19792951526 DE 19792951526 DE 2951526 A DE2951526 A DE 2951526A DE 2951526 A1 DE2951526 A1 DE 2951526A1
Authority
DE
Germany
Prior art keywords
fluid
space
spring
primary
bracket
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.)
Granted
Application number
DE19792951526
Other languages
German (de)
Other versions
DE2951526C2 (en
Inventor
Dipl.-Ing. Dr. Dieter 8011 Oberpframmern Braun
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.)
Airbus Helicopters Deutschland GmbH
Original Assignee
Messerschmitt Bolkow Blohm AG
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 Messerschmitt Bolkow Blohm AG filed Critical Messerschmitt Bolkow Blohm AG
Priority to DE19792951526 priority Critical patent/DE2951526A1/en
Priority to EP80100422A priority patent/EP0015378B1/en
Publication of DE2951526A1 publication Critical patent/DE2951526A1/en
Priority to US06/426,641 priority patent/US4781363A/en
Application granted granted Critical
Publication of DE2951526C2 publication Critical patent/DE2951526C2/de
Granted 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
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
    • 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
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic 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
    • 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
    • F16F2230/10—Enclosure elements, e.g. for protection

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Fluid-Damping Devices (AREA)
  • Combined Devices Of Dampers And Springs (AREA)

Abstract

The vibration damper comprises a spring between the vibrating part and the holder and a swing mass which moves inside a fluid transmission to suit the movement of the protected part. Fluid transmission is provided by a primary fluid space deforming in the vibration sense and a second space which also deforms in this direction, but is smaller in cross-section, and thus deforms mor strongly. This accelerates the serving mass so that inertia changes the pressure in the fluid and produces a dynamic force which compensates the dynamic component of the force transferred to the holder by the spring. The second fluid space may adjoin the first one with a low-leakage connection between, or the second one can be inside the first space and sealed to contain a compressible medium at over- or under pressure. The second space can be linked to atmosphere. The first space may have a deformable and a smaller fixed section, enclosing part of the second space and forming a fluid ring. A preset spring engages the mass and the holder to raise fluid pressure but without increasing fluid volume during operations.

Description

Beschreibungdescription

Die Erfindung betrifft einen Schwingungsisolator nach dem Oberbegriff des Patentanspruchs.The invention relates to a vibration isolator according to the preamble of the claim.

Ausgehend von der Patentanmeldung P 29 07 926.3-13 liegt der Erfindung die Aufgabe zugrunde, den Schwingungsisolator in seinem Aufbau weiter zu vereinfachen.The invention is based on patent application P 29 07 926.3-13 the underlying task is to further simplify the structure of the vibration isolator.

Diese Aufgabe wird durch das im Kennzeichen des Patentanspruchs angeführte Merkmal gelöst.This task is cited in the characterizing part of the claim Feature solved.

Die Erfindung hat den Vorteil, daß eine gesonderte Isolatorfeder entfallen kann, da deren Funktion im wesentlichen von dem primären Metallbalg übernommen wird.The invention has the advantage that there is no need for a separate isolator spring can, since their function is essentially taken over by the primary metal bellows.

Anhand der Zeichnung, in der im Axialschnitt eine Ausführungsform eines Schwingungsisolators gezeigt ist, wird die Erfindung näher erläutert.Based on the drawing, in the axial section, an embodiment a vibration isolator is shown, the invention will be explained in more detail.

Der in der Zeichnung gezeigte Antiresonanzkraftisolator hat einen Teil 1 für das Einleiten der Schwingung, das beispielsweise der getriebeseitige Befestigungspunkt des Isolators bei einem Hubschrauber sein kann. Das schwingende Teil 1 ist über einen Metallbalg 3 mit einer Halterung 4 verbunden, bei der es sich beim Anbringen in einem Hubschrauber um einen zellenseitigen Befestigungspunkt handelt. Selbstverständlich können die Schwingungen auch über die Halterung 4 eingeleitet werden. In diesem Fall übernimmt dann Teil 1 die Funktion der Halterung.The anti-resonance force isolator shown in the drawing has a Part 1 for initiating the oscillation, for example the transmission-side Can be the attachment point of the isolator in a helicopter. The swinging one Part 1 is connected via a metal bellows 3 to a bracket 4, which is when mounted in a helicopter is a cell-side attachment point. Of course, the vibrations can also be introduced via the holder 4 will. In this case, part 1 then takes over the function of the bracket.

Die Eigensteifigkeit des Metallbalges 3 ist so gewählt, daß der Metallbalg 3 die Funktion der Feder zwischen dem schwingenden Teil 1 und der Halterung 4 erfüllt, so daß eine Isolatorfeder, wie sie bei der Patentanmeldung P 29 07 926.3-13 vorgesehen ist, entfallen kann, wodurch der Gesamtaufbau des Antiresonanzkraftisolators erheblich vereinfacht wird. Der Metallbalg 3 umschließt den primären Fluidraum, in dem ein sekundärer Balg 5 aus Metall angeordnet ist, dessen Querschnitt kleiner ist als der des Metallbalgs 3. An der Stirnseite des sekundären Balgs 5,die sich in dem vom primären Metallbalg umschlossenen Fluidraum befindet, greift eine als Verbindungselement dienende Stange 6 an, die in reibungsarmen Lagern 8 axial verschiebbar geführt ist, die in einer von der Halterung 4 aus im Inneren des sekundären Balgs 5 hochstehenden Büchse 4a angeordnet sind. Der Innenraum des sekundären Balgs 5 ist an seiner halterungsseitigen Stirnseite mit der Atmosphäre verbunden.The inherent rigidity of the metal bellows 3 is chosen so that the metal bellows 3 fulfills the function of the spring between the oscillating part 1 and the holder 4, so that an isolator spring, as provided in patent application P 29 07 926.3-13 is, can be omitted, whereby the overall structure of the anti-resonance force isolator is considerable is simplified. The metal bellows 3 encloses the primary fluid space, in which a secondary bellows 5 made of metal is arranged, the cross section of which is smaller is than that of the metal bellows 3. On the face of the secondary bellows 5, which is is located in the fluid space enclosed by the primary metal bellows, acts as a Connecting element serving rod 6, which is axially displaceable in low-friction bearings 8 is guided in one of the bracket 4 from inside the secondary bellows 5 upstanding sleeve 4a are arranged. The interior of the secondary bellows 5 is connected to the atmosphere at its end face on the bracket side.

An der Stange 6 hängt außerhalb des sekundären Balgs 5 eine Pendelmasse 9. An der Stirnseite der Pendelmasse 9, die vom sekundären Balg 5 abgewandt ist, greift eine Feder 7 an, die sich an der hülsenförmig erweiterten Halterung 4 abstützt und die Pendelmasse 9 in Richtung des sekundären Balgs 5 drückt.A pendulum mass hangs on the rod 6 outside the secondary bellows 5 9. On the face of the pendulum mass 9, which faces away from the secondary bellows 5, a spring 7 engages, which is supported on the holder 4 which is expanded in the form of a sleeve and pushes the pendulum mass 9 in the direction of the secondary bellows 5.

Der Antiresonanzkraftisolator arbeitet folgendermaßen: Wenn der die Funktion der Isolatorfeder erfüllende, ausreichend eigensteife primäre Metallbalg 3 zusammengedrückt wird, verringert sich sein Volumen. Gleichzeitig wird der sekundäre Balg.The anti-resonance force isolator works as follows: When the the Sufficient inherently rigid primary metal bellows fulfilling the function of the isolator spring 3 is compressed, its volume is reduced. At the same time becomes the secondary Bellows.

5 zusammengeschoben. Dabei bewegt sich die Pendelmasse 9, die über die Stange 6 mit dem oberen Ende des sekundären Balges 5 verbunden ist, nach unten. Je näher die Pendelmasse 9 dem unteren toten Punkt des periodischen Bewegungsablaufes kommt, desto stärker wird die Pendelmasse 9 abgebremst, d.h. desto größer wird die nach unten gerichtete, auf die Masse wirkende Trägheitskraft. Diese Trägheitskraft ruft innerhalb des Balgsystents eine Druckabsenkung hervor. Daraus resultiert eine nach oben gerichtete Kraft auf die Halterung 4. Der dynamische Anteil der Kraft, die der federnd elastische Metallbalg 3 auf die Halterung 4 ausübt, ist zu diesem Zeitpunkt nach unten gerichtet. Bei geeigneter Isolatorabstimmung ist für eine bestimmte Erregerfrequenz, die Antiresonszfrequenz, die Summe der an der Halterung 4 angreifenden dynamischen Kräfte gleich Null, d.h. die Halterung 4 bleibt gegenüber dem schwingenden Teil 1 in Ruhe. Die Vorspannung der Feder 7 ist so gewählt, daß in der betrachteten Phase des Bewegungsablaufs keine Vergrößerung des Gesamtvolumens des Balgsystems erzeugt wird.5 pushed together. The pendulum mass 9 moves over the rod 6 is connected to the upper end of the secondary bellows 5, downwards. The closer the pendulum mass 9 to the lower dead point of the periodic motion sequence comes, the more the pendulum mass 9 is braked, i.e. the greater the downward inertial force acting on the mass. This inertial force causes a pressure drop within the bellows system. This results in a upward force on the bracket 4. The dynamic component of the force, which the resilient metal bellows 3 exerts on the holder 4 is related to this Point in time directed downwards. With a suitable isolator tuning is for a certain Excitation frequency, the anti-resonance frequency, the sum of those acting on the holder 4 dynamic forces equal to zero, i.e. the bracket 4 remains opposite to the oscillating Part 1 in peace. The bias of the spring 7 is chosen so that in the considered Phase of the movement sequence no increase in the total volume of the bellows system is produced.

Claims (1)

Schwingungsisolator, insbesondere Antiresonanzkraftisolator Zusatz zu Patentanmeldung P 29 07 926.3-13 Patentanspruch Schwingungsisolator zum Reduzieren der Schwingungsübertragung von einem periodisch schwingenden Teil auf eine mit diesem Teil verbundene Halterung, wobei im Antiresonanzfall im wesentlichen keine Schwingungen mehr auf die Halterung übertragen werden, mit wenigstens einer zwischen dem schwingenden Teil und der Halterung wirksamen Feder und mit einer Pendelmasse, die ansprechend auf die Bewegung des schwingenden Teils unter Zwischenschaltung einer Fluidübertragung bewegbar ist, wobei die Fluidübertragung aus wenigstens einem primären, in Bewegungsrichtung der Schwingungen verformbaren Fluidraum und aus wenigstens einem sekundären, ebenfalls in Bewegungsrichtung der Schwingungen verformbaren Raum besteht, dessen wirdsamer Querschnitt kleiner als der des primären Fluidraums ist, so daß der sekundäre Raum durch das bei der Verformung des primären Fluidraums verdrängte Fluid entsprechend stärker verformt wird, wodurch die ihm zugeordnete Pendelmasse beschleunigt wird und die daraus resultierende Trägheitskraft im Fluid eine Druckänderung bewirkt, die als dynamische Kraft den dynamischen Anteil der von der Feder auf die Halterung übertragenen Federkraft kompensiert, und wenigstens der primäre Fluidraum von einem zylindrischen, in seine Axialrichtung reibungsarm verformbaren gewellten Metallbalg umschlossen ist, nach Patentanmeldung P 29 07 926.3-13, dadurch g e k e n n -z e i c h n e t, daß die zwischen dem schwingenden Teil (1) und der Halterung (4) wirksame Feder von dem mit der erforderlichen Eigensteifigkeit versehenen Metallbalg (3) gebildet wird. Vibration isolator, especially anti-resonance force isolator add-on to patent application P 29 07 926.3-13 patent claim vibration isolator to reduce the transmission of vibrations from a periodically vibrating part to one with it Part connected bracket, with essentially no vibrations in the case of anti-resonance more to be transferred to the bracket, with at least one between the oscillating Part and the bracket effective spring and with a pendulum mass that is appealing to the movement of the vibrating part with the interposition of a fluid transfer is movable, the fluid transfer from at least one primary, in the direction of movement of the vibrations deformable fluid space and from at least one secondary, likewise deformable space exists in the direction of movement of the vibrations, its becomes more Cross section is smaller than that of the primary fluid space, so that the secondary space correspondingly by the fluid displaced during the deformation of the primary fluid space is more strongly deformed, whereby the pendulum mass assigned to it is accelerated and the resulting inertial force im Fluid a change in pressure causes the dynamic force as the dynamic portion of the spring on the Bracket transmitted spring force compensated, and at least the primary fluid space of a cylindrical, corrugated, deformable with little friction in its axial direction Metal bellows is enclosed, according to patent application P 29 07 926.3-13, thereby g e k e n n -z e i c h n e t that between the vibrating part (1) and the bracket (4) Effective spring from the metal bellows provided with the required inherent rigidity (3) is formed.
DE19792951526 1979-03-01 1979-12-20 Vibration damper with spring - has fluid transmission with primary and secondary bellows of different cross=section accelerating swing mass Granted DE2951526A1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE19792951526 DE2951526A1 (en) 1979-12-20 1979-12-20 Vibration damper with spring - has fluid transmission with primary and secondary bellows of different cross=section accelerating swing mass
EP80100422A EP0015378B1 (en) 1979-03-01 1980-01-28 Vibration insulator
US06/426,641 US4781363A (en) 1979-03-01 1982-09-29 Vibration isolator particularly of the antiresonance force type

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19792951526 DE2951526A1 (en) 1979-12-20 1979-12-20 Vibration damper with spring - has fluid transmission with primary and secondary bellows of different cross=section accelerating swing mass

Publications (2)

Publication Number Publication Date
DE2951526A1 true DE2951526A1 (en) 1981-07-23
DE2951526C2 DE2951526C2 (en) 1989-02-23

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Family Applications (1)

Application Number Title Priority Date Filing Date
DE19792951526 Granted DE2951526A1 (en) 1979-03-01 1979-12-20 Vibration damper with spring - has fluid transmission with primary and secondary bellows of different cross=section accelerating swing mass

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Country Link
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2761438A1 (en) * 1997-03-21 1998-10-02 Eurocopter Deutschland MECHANICAL SHOCK ABSORBER

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19711845C2 (en) * 1997-03-21 1999-01-14 Eurocopter Deutschland Mechanical vibration damper

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3322379A (en) * 1964-11-03 1967-05-30 Kaman Aircraft Corp Dynamic antiresonant vibration isolator
CA781817A (en) * 1965-08-25 1968-04-02 Kaman Aircraft Corporation Dynamic antiresonant vibration isolator
DE1600402B2 (en) * 1967-05-23 1970-12-17 Messerschmitt-Bölkow-Blonm GmbH, 8OOO München Pre-tension accumulator for generating a pump pre-pressure in a closed hydraulic system
DE2452221A1 (en) * 1974-11-04 1976-05-13 Josef Nemetz Hydrodynamic working cylinder - incorporates sealing sleeve for working piston with gap between sleeve and cylinder

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3322379A (en) * 1964-11-03 1967-05-30 Kaman Aircraft Corp Dynamic antiresonant vibration isolator
CA781817A (en) * 1965-08-25 1968-04-02 Kaman Aircraft Corporation Dynamic antiresonant vibration isolator
DE1600402B2 (en) * 1967-05-23 1970-12-17 Messerschmitt-Bölkow-Blonm GmbH, 8OOO München Pre-tension accumulator for generating a pump pre-pressure in a closed hydraulic system
DE2452221A1 (en) * 1974-11-04 1976-05-13 Josef Nemetz Hydrodynamic working cylinder - incorporates sealing sleeve for working piston with gap between sleeve and cylinder

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2761438A1 (en) * 1997-03-21 1998-10-02 Eurocopter Deutschland MECHANICAL SHOCK ABSORBER

Also Published As

Publication number Publication date
DE2951526C2 (en) 1989-02-23

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