DE4011367A1 - Hybrid oscillation damping device - uses two parallel spring plates relatively adjusted via mechanical, electrical or hydraulic setting mechanism - Google Patents
Hybrid oscillation damping device - uses two parallel spring plates relatively adjusted via mechanical, electrical or hydraulic setting mechanismInfo
- Publication number
- DE4011367A1 DE4011367A1 DE19904011367 DE4011367A DE4011367A1 DE 4011367 A1 DE4011367 A1 DE 4011367A1 DE 19904011367 DE19904011367 DE 19904011367 DE 4011367 A DE4011367 A DE 4011367A DE 4011367 A1 DE4011367 A1 DE 4011367A1
- Authority
- DE
- Germany
- Prior art keywords
- spring
- spring constant
- vibration isolator
- electrical
- hybrid
- 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.)
- Withdrawn
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K5/00—Arrangement or mounting of internal-combustion or jet-propulsion units
- B60K5/12—Arrangement of engine supports
- B60K5/1283—Adjustable supports, e.g. the mounting or the characteristics being adjustable
-
- 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
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
- F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
- F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
-
- 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
- F16F15/08—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 with rubber springs ; with springs made of rubber and metal
- F16F15/085—Use of both rubber and metal springs
-
- 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
- F16F3/00—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic
-
- 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
- F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
- F16F2228/06—Stiffness
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Vibration Prevention Devices (AREA)
Abstract
Description
Gegenstand der Erfindung ist ein Schwingungsisolator zur Dämmung von Schwingungen.The invention relates to a vibration isolator for insulation of vibrations.
Solche Schwingungsisolatoren sind in den verschiedensten Aus führungsformen bekannt, beispielsweise als Federpakete, silent blocks, Gummipuffer, Gummimatten, Motorlager. Unabhängig von der Ausführungsform können diese Systeme durch ihre komplexe Feder konstante charakterisiert werden, wobei der Realteil die eigent liche Federkonstante und der Imaginärteil die Dämpfung be schreibt. Im allgemeinen Fall ist die Federkonstante unabhängig von der Vorlast und von der Anregungsfrequenz. Ein Isolatorele ment mit lastabhängiger Federkonstante ist die Tellerfeder. Da der Elastizitätsmodul von Gummi mit der Frequenz ansteigt, haben Schwingungsisolatoren aus Gummi eine mehr oder weniger frequenz progressive Federung. - Zum Stand der Technik zählen auch die aktiv elektronisch geregelten Isolatorsysteme, zu deren Betrieb aber ein Reglersystem mit Sensor und Aktuator notwendig ist.Such vibration isolators are in a variety of ways leadership forms known, for example as spring packs, silent blocks, rubber buffers, rubber mats, engine mounts. Independent of These systems can be embodied by their complex spring constant are characterized, whereby the real part is the actual spring constant and the imaginary part damping writes. In the general case, the spring constant is independent the preload and the excitation frequency. An isolator The disc spring is the element with the load-dependent spring constant. There the elastic modulus of rubber increases with frequency Vibration isolators made of rubber a more or less frequency progressive suspension. - The state of the art also includes actively electronically controlled isolator systems, for their operation but a control system with sensor and actuator is necessary.
Die passiven Schwingungsisolatoren sind einfache und bewährte Bauelemente. Ihr prinzipieller Nachteil läßt sich an dem Ausle gungskonflikt aufzeigen: Die Schwingungsdämmung (= Isolierung) ist umso größer, je kleiner die Federkonstante ist. Aus Stabi litätsgründen kann jedoch eine Mindestfederhärte nicht unter schritten werden. Je weicher die Federung, desto größer ist die statische Einfederung und desto mehr hebt und senkt sich das Höhenniveau einer Maschine bei Änderung der statischen Vorlast. Als weiterer Nachteil kommt hinzu, daß die Isolatorfeder zusam men mit der Maschinenmasse ein Schwingsystem bildet. Im Bereich der Schwingresonanz kommt es zu einer Verschlechterung der Iso lierwirkung.The passive vibration isolators are simple and proven Components. Their principal disadvantage can be seen in the Ausle Show conflict of interests: Vibration insulation (= insulation) the larger the smaller the spring constant. From stabilizer For reasons of quality, however, a minimum spring hardness cannot be below be paced. The softer the suspension, the bigger it is static deflection and the more it rises and falls Height level of a machine when the static preload changes. Another disadvantage is that the insulator spring together forms a vibration system with the machine mass. In the area the vibration resonance leads to a deterioration of the iso effect.
Aufgabe der Erfindung ist ein Schwingungsisolator, der unabhän gig von seiner Vorlast eine geringe Federsteifigkeit und damit hohe Isolierwirkung aufweist und doch statisch stabil ist.The object of the invention is a vibration isolator that is independent due to its preload a low spring stiffness and therefore has a high insulating effect and is still statically stable.
- 1) Nach dem Hauptmerkmal der Erfindung werden 2 Federplat ten, eine mit positivem und eine mit negativem Bereich der Federsteifigkeit hintereinander geschaltet und deren gegensei tige Verspannung lastabhängig über einen Verstellmechanismus gesteuert. Gleichzeitig wird damit auch eine lastunabhängige Höhennivellierung und damit statische Stabilität erreicht.1) According to the main feature of the invention, 2 spring plates ten, one with positive and one with negative range of Spring stiffness connected in series and their opposite dependent tensioning via an adjustment mechanism controlled. At the same time, it also becomes load-independent Height leveling and thus static stability achieved.
- 2) Es gibt Situationen, wo es nur zwei oder eine begrenzte Anzahl von Vorbelastungen gibt. In diesem Fall sind nach einem weiteren Erfindungsmerkmal nur ebensoviele Verspannungsniveaus fest einprogrammiert und werden je nach Lastfall eingeschaltet.2) There are situations where there are only two or a limited one Number of preloads there. In this case, after one another feature of the invention only as many levels of tension permanently programmed and are switched on depending on the load.
- 3) Nach einem weiteren Merkmal der Erfindung treiben die Schwingbewegungen einen Stromgenerator an, dessen abgegebene, elektrische Leistung in einem Akku gespeichert wird, um damit die zwischen den beiden Tellerfedern wirkende Verspannung einzu stellen.3) According to a further feature of the invention, the Vibrating movements to a power generator, the emitted, electrical power is stored in a battery in order to do so the tension acting between the two disc springs put.
- 4) Nach einem weiteren Erfindungsmerkmal wird parallel zum Verstellmechanismus eine Feder geschaltet, die einen großen Teil der Verstellkräfte aufnehmen kann. Ein ebenfalls im Parallel kreis befindlicher Dämpfer reduziert im besonderen die hochfre quenten Kraftspitzen.4) According to another feature of the invention, parallel to Adjustment mechanism switched a spring that a large part which can absorb adjusting forces. One also in parallel damper located in the circle in particular reduces the high fre quent force peaks.
Der Erfindungsgegenstand ist anhand mehrerer Ausführungsbei spiele dargestellt. Es zeigenThe subject matter of the invention is based on several examples games shown. Show it
Fig. 1 Grundaufbau eines hybriden Schwingungsisolators. Fig. 1 basic structure of a hybrid vibration isolator.
Fig. 2 Verstellmechanismus mit Schraubengelenk. Fig. 2 adjustment mechanism with screw joint.
Fig. 3 Verstellmechanismus mit Schraubengewinde. Fig. 3 adjustment mechanism with screw thread.
Fig. 4 Verstellmechanismus mit elektro- bzw. magnetostriktiven Translatoren. Fig. 4 adjustment mechanism with electro- or magnetostrictive translators.
Fig. 5 Hybrider Schwingungsisolator mit Hydraulik-Verstellung. Fig. 5 Hybrid vibration isolator with hydraulic adjustment.
In Fig. 1 ist der Grundaufbau eines hybriden Schwingungsisola tors 10 dargestellt. Wesentlicher Bestandteil sind 2 Feder platten 11 und 12 , die nach den Vorschriften einer Teller feder bzw. eines Silators eine Vorwölbung und damit eine geo metrisch nichtlineare Federkennlinie besitzen. Im besonderen hat die Federplatte 12 einen Bereich mit negativer Federsteifig keit. Die Federsteifigkeit der Federplatte 11 dagegen ist in diesem Bereich positiv, so daß die Parallelschaltung beider Fe derplatten 11 und 12 eine minimale, aber positive Gesamt federsteifigkeit besitzt. Ändert sich die Vorlast, so daß der Arbeitspunkt aus dem Federminimum herauswandert, so werden die beiden Federplatten 11 und 12 durch einen Verstellme chanismus, hier durch einen Hubmagneten 13 gegeneinander wieder in das Federminimum verschoben. Gesteuert wird der Hub magnet 13 durch einen Wegmesser 14. Um die Kräfte am Hub magneten 13 zu verkleinern, befindet sich parallel zu ihm eine Feder 16, die die Hauptkräfte aufbringt. Um die Bela stung im Hubmagneten 13 weiter zu senken, befindet sich zwi schen den beiden Federplatten 11 und 12 ein zusätzlicher Dämpfer 17. Schließlich sind die Federplatten 11 und 12 durch ringförmige Gummischeiben 18 gegeneinander fixiert. Die abzudämmende Maschine sitzt auf dem Auflager 15. Der Name "hybrider Schwingungsisolator′ erklärt sich aus dem Wirkungs prinzip. Die Schwingungsdämmung resultiert passiv aus der mini malen Gesamtfederung. Ein Regelmechanismus, bestehend aus Weg geber 14 und Verstellmechanismus 13 hat aktiv nur den Arbeitspunkt mit Federminimum nachzuregeln.In Fig. 1, the basic structure of a hybrid vibration isolator 10 is shown. An essential part are 2 spring plates 11 and 12 , which have a protrusion according to the specifications of a plate spring or a silator and thus have a non-linear spring characteristic. In particular, the spring plate 12 has an area with negative spring stiffness. The spring stiffness of the spring plate 11, however, is positive in this area, so that the parallel connection of both Fe derplatten 11 and 12 has a minimal but positive overall spring stiffness. Changes the preload, so that the operating point migrates out of the spring minimum, the two spring plates 11 and 12 by a mechanism Verstellme, here by a solenoid 13 against each other again in the spring minimum. The stroke magnet 13 is controlled by a travel meter 14 . In order to reduce the forces on the stroke magnet 13 , there is a spring 16 parallel to it, which applies the main forces. In order to further reduce the load in the lifting magnet 13 , there is an additional damper 17 between the two spring plates 11 and 12 . Finally, the spring plates 11 and 12 are fixed against each other by annular rubber washers 18 . The machine to be insulated sits on the support 15 . The name "hybrid vibration isolator 'is explained by the principle of operation. The vibration insulation results passively from the minimal overall suspension. A control mechanism, consisting of encoder 14 and adjustment mechanism 13 , only has to actively adjust the working point with a spring minimum.
Anstelle des Hubmagneten 14 zur Änderung der Vorspannung zwischen den beiden Federplatten 11 und 12 gibt es ver schiedene, in den Fig. 2 bis 4 dargestellte Realisierungen. In Fig. 2 ist ein Schraubengelenk 24 zur Verstellung der beiden Federplatten 21 und 22. Diese haben dieselben Eigenschaf ten wie die Federplatten 11 und 12. Auch in den übrigen Komponenten stimmen die Ausführungsbeispiele von Fig. 1 mit denen von Fig. 2 bis 4 überein. In Fig. 3 werden die Federplat ten 31 und 32 durch ein Schraubengewinde 34 gegeneinan der verstellt. In Fig. 4 erfolgt die Verstellung der Federplat ten 41 und 42 durch einen elektro- bzw. magnetostriktiven Translator 44.Instead of the solenoid 14 for changing the bias between the two spring plates 11 and 12, there are different implementations shown in FIGS . 2 to 4. In FIG. 2 is a screw joint 24 for adjusting the two spring plates 21 and 22. These have the same properties as the spring plates 11 and 12 . The exemplary embodiments in FIG. 1 also correspond to those in FIGS. 2 to 4 in the other components. In Fig. 3, the Federplat th 31 and 32 are adjusted by a screw thread 34 against each other. In Fig. 4, the adjustment of Federplat th 41 and 42 is carried out by an electro- or magnetostrictive translator 44th
Im Ausführungsbeispiel nach Fig. 5 schließlich befindet sich zwischen den beiden Federplatten 51 und 52 eine Flüssig keit 59, z. B. Öl. Über einen Hydraulikkolben 54 kann der Plattenabstand verstellt werden.In the embodiment of Fig. 5, finally, is located between the two spring plates 51 and 52, a liquid ness 59, z. B. Oil. The plate distance can be adjusted via a hydraulic piston 54 .
Um die Tragfähigkeit zu vergrößern, ist es zweckmäßig, die Fe derplatten (11-51 und 12-52) aus zwei oder mehreren Einzelfederplatten zusammenzusetzen. Durch Einbringung eines viskosen Dämpfungsstoffes zwischen den einzelnen Lagen der Federplatten läßt sich damit auch eine Dämpfung realisieren.In order to increase the load capacity, it is advisable to assemble the spring plates ( 11-51 and 12-52 ) from two or more individual spring plates . By introducing a viscous damping material between the individual layers of the spring plates, damping can also be achieved.
Claims (5)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19904011367 DE4011367A1 (en) | 1990-04-07 | 1990-04-07 | Hybrid oscillation damping device - uses two parallel spring plates relatively adjusted via mechanical, electrical or hydraulic setting mechanism |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19904011367 DE4011367A1 (en) | 1990-04-07 | 1990-04-07 | Hybrid oscillation damping device - uses two parallel spring plates relatively adjusted via mechanical, electrical or hydraulic setting mechanism |
Publications (1)
Publication Number | Publication Date |
---|---|
DE4011367A1 true DE4011367A1 (en) | 1991-10-17 |
Family
ID=6404015
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
DE19904011367 Withdrawn DE4011367A1 (en) | 1990-04-07 | 1990-04-07 | Hybrid oscillation damping device - uses two parallel spring plates relatively adjusted via mechanical, electrical or hydraulic setting mechanism |
Country Status (1)
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DE (1) | DE4011367A1 (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19509485C1 (en) * | 1995-03-16 | 1996-05-15 | Daimler Benz Ag | Vibration insulator with coupled positive and negative spring constants |
US5558191A (en) * | 1994-04-18 | 1996-09-24 | Minnesota Mining And Manufacturing Company | Tuned mass damper |
US5564536A (en) * | 1994-04-18 | 1996-10-15 | Minnesota Mining And Manufacturing Company | Tuned mass damper |
US5915508A (en) * | 1994-04-18 | 1999-06-29 | Minnesota Mining And Manufacturing Company | Tuned mass damper |
DE10326625A1 (en) * | 2003-06-13 | 2005-01-05 | Contitech Vibration Control Gmbh | Active spring damper mechanism for damping mechanical vibration e.g. for automobile engine mounting, has setting device for active control of support spring effect |
DE102009043588A1 (en) * | 2009-09-30 | 2011-03-31 | Ust Umweltsensortechnik Gmbh | Device for use in ultrasonic drill head for protecting components against vibrations, has permanent magnet/electric coil provided in housing so that vibrations of component are controlled and electricity is produced depending on vibrations |
WO2015054673A1 (en) * | 2013-10-10 | 2015-04-16 | Firestone Industrial Products Company, Llc | Mounting assemblies and systems including same |
-
1990
- 1990-04-07 DE DE19904011367 patent/DE4011367A1/en not_active Withdrawn
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5558191A (en) * | 1994-04-18 | 1996-09-24 | Minnesota Mining And Manufacturing Company | Tuned mass damper |
US5564536A (en) * | 1994-04-18 | 1996-10-15 | Minnesota Mining And Manufacturing Company | Tuned mass damper |
US5915508A (en) * | 1994-04-18 | 1999-06-29 | Minnesota Mining And Manufacturing Company | Tuned mass damper |
DE19509485C1 (en) * | 1995-03-16 | 1996-05-15 | Daimler Benz Ag | Vibration insulator with coupled positive and negative spring constants |
DE10326625A1 (en) * | 2003-06-13 | 2005-01-05 | Contitech Vibration Control Gmbh | Active spring damper mechanism for damping mechanical vibration e.g. for automobile engine mounting, has setting device for active control of support spring effect |
DE10326625B4 (en) * | 2003-06-13 | 2012-04-26 | Contitech Vibration Control Gmbh | Actuator-equipped spring-damper mechanism |
DE102009043588A1 (en) * | 2009-09-30 | 2011-03-31 | Ust Umweltsensortechnik Gmbh | Device for use in ultrasonic drill head for protecting components against vibrations, has permanent magnet/electric coil provided in housing so that vibrations of component are controlled and electricity is produced depending on vibrations |
DE102009043588B4 (en) * | 2009-09-30 | 2012-08-02 | Ust Umweltsensortechnik Gmbh | Device and method for protecting components against vibrations |
WO2015054673A1 (en) * | 2013-10-10 | 2015-04-16 | Firestone Industrial Products Company, Llc | Mounting assemblies and systems including same |
US20160245363A1 (en) * | 2013-10-10 | 2016-08-25 | Firestone Industrial Products Company, Llc | Mounting assemblies and systems including same |
US10295009B2 (en) | 2013-10-10 | 2019-05-21 | Firestone Industrial Products Company, Llc | Mounting assemblies and systems including same |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
8141 | Disposal/no request for examination |