DE1458570C

DE1458570C - Resonance vibration device

Info

Publication number: DE1458570C
Application number: DE19631458570
Authority: DE
Inventors: Albert Barrington Thorn son Marvin G Prospect Heights 111 Musschoot (V St A )
Original assignee: General Kinematics Corp
Current assignee: General Kinematics Corp
Priority date: 1963-02-01
Filing date: 1963-02-01
Publication date: 1973-06-07

Description

F ig. 3 einen Schnitt gemäß der Linie 3-3 in Fig. 2,Fig. 3 shows a section along the line 3-3 in FIG. 2,

F i g. 4 einen Schnitt längs der Linie 4-4 in F ig. 2.F i g. 4 shows a section along the line 4-4 in FIG. 2.

Eine Rinne 10, die aus Seitenwänden 11 und 12, sowie einem Boden 13 besteht, ist an ihren Ecken mittels Federn 16, 17 auf einem ortsfesten Grundrahmen 15 gelagert. Die federnde Lagerung erlaubt eine Bewegung der Rinne 10 Richtung des Pfeiles A, d. h. in Arbeitsrichtung, in der die Antriebskraft des schwmgungserzeugenden Unwuchtantriebs eingeleitet wird. Der Unwuchtantrieb wird von einem Elektromotor 20 mit an beiden Wellenenden angeordneten, gleichsinnig wirkenden Exzentergewichten 21, 22 gebildet. Der Motor 20 steht über energiespeichernde Gummifederelemente 23, 24 mit der Rinne 10 in Verbindung. Das Resonanzschwingsystem besteht also aus den beiden gegeneinander schwingenden und durch die Gummifederelemente 23, 24 miteinander verbundenen Massen, d. h. der Masse des Motors 20 und der Masse der Rinne 10 einschließlich jeweils daran befestigter Teile.A channel 10, which consists of side walls 11 and 12 and a floor 13, is supported at its corners by means of springs 16, 17 on a stationary base frame 15. The resilient mounting allows the channel 10 to move in the direction of arrow A, ie in the working direction in which the drive force of the vibration-generating unbalance drive is initiated. The unbalance drive is formed by an electric motor 20 with eccentric weights 21, 22 arranged on both shaft ends and acting in the same direction. The motor 20 is connected to the channel 10 via energy-storing rubber spring elements 23, 24. The resonance oscillation system thus consists of the two masses oscillating against one another and connected to one another by the rubber spring elements 23, 24, ie the mass of the motor 20 and the mass of the channel 10 including parts attached to it.

Die Gummifederelemente 23, 24 sind toroidförmig ausgebildet. Vom Unwuchtantrieb werden über sie Scherkräfte in Arbeitsrichtung/4 übertragen, während die anders gerichteten Kräfte von ihnen aufgenommen werden, wobei sie auf Torsion beansprucht werden.The rubber spring elements 23, 24 are designed in the shape of a toroid. From the unbalance drive are over they transfer shear forces in the working direction / 4, while the differently directed forces are absorbed by them, whereby they are subjected to torsion will.

Zur Befestigung des schwingungserzeugenden Antriebs an der Rinne 10 dient eine an deren Unterseite angeordnete Rahmenkonstruktion 25, 26, 27, 28, von der aus sich ein Seitenplattenpaar 30, 31 in Arbeitsrichtung A nach unten erstreckt. Die Seitenplatten 30, 31 sind mittels eines L-förmigen Querträgers 32, der, wie später beschrieben, noch einem weiteren Zweck dient, gegeneinander versteift. Der Motor 20 ist mit Halterungen 35, 36 verstellbar an Flanschen 40 eines sich zwischen den Seitenplatten 30, 31 erstreckenden Rohres 37 befestigt. Die Verstellbarkeit zum Zwecke des Ausrichtens des Motors 20 in Arbeitsrichtung A ist durch Schlitzlöcher 41 in den Flanschen 40 gegeben, durch die sich Befestigungsschrauben 42 erstrecken. An jedem Ende des Rohres 37 ist eine Platte 45 angeschweißt, die als innere Anlagefläche für die toroidförmigen Gummifederelemente 23 bzw. 24 dient. Die Befestigung der Gummifederelemente ist auf beiden Seiten gleich, so daß hier nur auf eine Seite Bezug genommen wird. Die Seitenplatte 31 (siehe F i g. 4) ist mit einer kreisförmigen Öffnung 50 versehen, in die das Gummifederelement 24 hineinragt. Eine Abdeckplatte 51 ist mittels eines Bolzens 52, der sich koaxial durch das Rohr 37 erstreckt, und einer Mutter 53 gegen das Gummifederelement 24 gezogen. Die nach innen gerichtete Bewegung der Abdeckplatte 51 beim Anziehen der Mutter 53 wird durch eine Abstandshülse 54, die den Bolzen 52 umgibt, begrenzt.A frame structure 25, 26, 27, 28, arranged on its underside and from which a pair of side plates 30, 31 extends downward in the working direction A, is used to fasten the vibration-generating drive to the channel 10. The side plates 30, 31 are stiffened against one another by means of an L-shaped cross member 32 which, as described later, serves a further purpose. The motor 20 is adjustably attached to flanges 40 of a tube 37 extending between the side plates 30, 31 by means of brackets 35, 36. The adjustability for the purpose of aligning the motor 20 in the working direction A is provided by slotted holes 41 in the flanges 40 through which fastening screws 42 extend. A plate 45 is welded to each end of the tube 37 and serves as an inner contact surface for the toroidal rubber spring elements 23 and 24, respectively. The fastening of the rubber spring elements is the same on both sides, so that reference is only made to one side here. The side plate 31 (see FIG. 4) is provided with a circular opening 50 into which the rubber spring element 24 protrudes. A cover plate 51 is pulled against the rubber spring element 24 by means of a bolt 52, which extends coaxially through the tube 37, and a nut 53. The inward movement of the cover plate 51 when the nut 53 is tightened is limited by a spacer sleeve 54 which surrounds the bolt 52.

Zur Veränderung der Federkonstante des Gesamtsystems ist eine zusätzliche, in Arbeitsrichtung wirkende variable pneumatische Federung zwischen den erregten Massen vorgesehen. Luftfederbälge 60, 61, die sich an dem bereits erwähnten Querträger 32 abstützen, sind an einem U-Eisen 62 angeordnet, das mit Halterungen 63 und 64 verstellbar an den Flanschen 40 am Rohr 37 befestigt ist. Die Flansche 40 weisen Schlitzlöcher 65 auf, durch die Befestigungsschrauben 66 für die Halterungen 63, 64 geführt sind. Die pneumatischen Federn, d. h. die Luftfederbälge 60, 61, sind über Einlasse 69 bzw. 70 mit einer Leitung 68 verbunden, durch die Druckluft zugeführt werden kann. Sofern die Federbälge drucklos sind, wird die Federkonstante des Systems praktisch nicht beeinflußt. Mit Erhöhung des Luftdrucks wird der Arbeitshub der Förderrinne verringert.To change the spring constant of the overall system, an additional one acting in the working direction is required variable pneumatic suspension is provided between the excited masses. Air bags 60, 61, which are supported on the already mentioned cross member 32, are arranged on a U-iron 62, the is adjustably attached to the flanges 40 on the tube 37 with brackets 63 and 64. The flanges 40 have slotted holes 65 through which the fastening screws 66 for the brackets 63, 64 are guided are. The pneumatic springs, i.e. H. the air bags 60, 61, are via inlets 69 and 70, respectively, with a Line 68 connected through which compressed air can be supplied. If the bellows are depressurized, the spring constant of the system is practically not influenced. As the air pressure increases, the The working stroke of the conveyor trough is reduced.

Hierzu 1 Blatt Zeichnungen1 sheet of drawings

Claims

1 21 2

the freely oscillating mass of the electromagnetic

Patent claims: vibration exciter not only in the direction of utility

swing axis can swing, but also in ir-

I. Resonance oscillating device with two opposite directions transversely thereto.

oscillating against each other, by an oscillating 5 From the German patent specification 976 405 is a generating drive excited masses, the unbalance vibrator with a in a metallic support energy-storing rubber spring elements, pendulum bearings and elastically tied ones transmit the shear forces in the working direction, known vibration generator. For elastic fetters together are connected, as a result, a coaxial next to the support bearing is used to denote that, in a per se known io, to the pendulum shaft attached to this, only in a gate manner as a vibration generator, a rubber body subject to an imbalance anion, which is located on the outside of the drive is provided, which is attached to an electric motor vibration generator. The Pendulum (20) with arranged at both shaft ends, tion causes such unbalance vibrators that the eccentric weights (21) acting in the same direction, centrifugal forces occurring on the unbalance shaft 22) is formed, and further that the rubber spring 15 are divided into two components, of which the elements (23, 24) formed toroidally and in a directional oscillation via the self-aligning bearing in relation to the vibration generator comes into effect, while the one perpendicular to it are arranged so that they the excitation forces in Ar component a pendulum swing of the Schwinarbeitsrichtung Oppose greater stiffness than caused by the generator and remain ineffective. at in all other directions. 20 to which the German patent specification 976 405

2. The resonance vibration device after the unbalance vibrator has become known is for recording claim 1, characterized in that an ineffective force component for reasons of additional, variable, simpler structure acting in the direction of work, less wear and tear pneumatic suspension (60, 61) between the er and the smaller manufacturing effort instead of one excited masses is provided. 25 otherwise usual spring shackles an elastic shackle

treatment by means of which are only subjected to torsion

Rubber body provided.

Based on the prior art described here, the invention is based on the object

The invention relates to a resonance vibration device 30 a resonance vibration device of the opening report to create with two written ways swinging against each other, one by going through a vibration generating drive energized circular drive force generated into a linear one th mass, which is converted by energy-storing rubber, without the addition of the energy spring elements, transferring the shear forces in the working direction to the rubber spring elements that store cast, are connected to each other. 35 liable bearings or management and intermediate links

In such resonance vibration devices for the vibration-generating drive is required are the kinetic energy at the motion deceleration.

until the turning point is reached This object is achieved according to the invention by

added to the storage springs and after being released, that in a manner known per se as Schwinlauf of the reversal point is released again and an unbalance drive is provided for 4 ° generation generator, used to accelerate the masses. The sinks from an electric motor with both wave generators The drive only provides useful ends arranged in the same direction as Ex- and to overcome the energy losses necessary is formed, and further that the Gumliche Work. It is the aim of the designer to have a toroidal design and in having a linear driving force available. 45 with respect to the vibration generator so arranged The resonance vibrating devices mentioned at the beginning are that they correspond to the excitation forces in working guidelines Oppose type with electromagnetic oscillation greater rigidity than in all excitation generators, as in the German patent specification, their directions.

861478 known, the driving force is essentially in a further embodiment of the invention is for loading

chen linear. The situation is different with resonance 5 ° influence of the spring constant of the Schwinguhgssyschwingvorrichtungen, where the pathogen is an unstems an additional one acting in the direction of work balancing drive is provided. There must be the circular variable pneumatic suspension between the excitatory driving force be converted into a linear, so th masses provided.

that additional intermediate links, for example Len- The advantages achieved by the invention exist

ker, between the drive and the driven 55 in particular that a structurally simple Utility device are required (German interpretation document Resonanzschwingvorrichtüng with an imbalance 1 097 728). Through the German Auslegeschrift was created, which as a result of the simultaneous 1 052 723 is the provision of an intermediate link tig as a storage for the drive serving between energy an electromagnetic vibration-storing rubber spring element practically exciter and a utility device known. There is 60 is maintenance-free and also has a compact structure the intermediate member made of sheet metal or flat iron.

that is kink and flexurally rigid in the useful oscillation axis, An embodiment of the invention is in the

across it, however, is pliable. Shown with this training drawing and will be explained in more detail below The aim is to achieve that coupling vibrations are described. It shows

and the associated risk of the occurrence of 65 F i g. 1 shows a side view of the resonance oscillating coupling interference resonances between the utility device and device, which is designed as a conveyor trough,
an associated via handlebar Leitträger un- F i g. 2 is a sectional view taken along line 2-2 in FIG

which are caused by the fact that Fig. 1,