US2398722A - Self-tuning polyharmonic damper - Google Patents

Description

P" 1946. s. A. RUBISSOW SELF-TUNING POLYHARMONIC DAMPER 3 Sheets-Sheet 1 Filed March 8, 1941 B A 2 M A 2 2 4 OJAJ 0 2 7% Z m z. a

L A. R}, 1 2

INVENTOR.

April 16, 1946. G. A. RUBISSOW ,7

, SELF-TUNING POLYHARMONIC DAMPER Filed March 8, 1941 :5 Sheets-Sheet 2 April 16, 1946.

G. A. RUBISSOW SELF-TUNING POLYHARMONIC DAMPER Filed March 8, 1941 3 sheets sheet 3 IN VENT OR.

Patented Apr. 16,1946

UNITED STATES PATENT OFFICE 2,398,722 SELF-TUNING roLYnAnMomc-nmm George Alexis Rubissow, New York, N. Y.

Application March 8, 1941, Serial No. 382,383

' 7 Claims. (01. 74-514) f This invention is particularly applicable to the polyharmonic dampers as described in the Salomon patent applications Nos. 333,561 and 335,081, in which the following formula is given for the tuningcondition calculation of a dynamic damper for a predetermined harmonic order n:

m.a.D.OK K

(theoretically for infinite inertia).

(theoretically for infinite inertia).

For obtaining fictive inertia, infinite and positive (in reference to harmonic n) R 1 m.a.D.OK Q I 2n Mp .d.l.02 For obtaining fictive inertia, infinite and negative in reference to harmonic n) For obtaining other values for the fictive inertia (nil, positive or negative) (often in line motors), it is necessary to give other values to (Rz-T) Figures 1 and 2 of this application show afront view and'a cross-sectional side view. when regarding the engine rotating in the direction of the arrow F. It is very important, in all calculations of this condition of direction, to place the restoring levers so that while they turn in the direction of the rotation of the driving shaft, the center of gravity of the restoring lever, when pivoting, approaches the axis 0 of this shaft.

The above and further objects and novel feaits of the invention.

Fig. 1 shows a schematic plan view with parts broken out, of one embodiment of a damper partly in cross-section.

Fig. 2 is a. cross-sectional view 2-2 of Figure 1.

Fig. 3 represents diagrammatic plan views partly in cross-section, with parts broken out, of a.

damper.

Fig. 4 is a diagrammatic side view. with parts broken out, of arresting means for the controlling weight controlling the position of the eccentric bushing-bearing member.

Figs. 5, 6 and 7 represent plan views, partly in cross-section, with parts broken out, of diflerent arrangements of eccentric bushing-bearing members. v

Figs. 8 and 9 represent plan views partly in cross-section with parts broken out of the lever provided with eccentric bushing-bearing members and additional weight, controlling the position of the center of gravity of the said lever.

Fig. 10 represents a cross-sectional side view, with parts broken out, of another embodiment of a part of a damper.

Figs. 11 and 12 represent, schematically, crosssectional side views of an eccentric bushing-bearing member mounted in a lever or the like.

Figs. 1 3 and 14 are schematic plan views partly in cross-section, and with parts broken out, of eccentric bushing-bearing member provided with weights for controlling their position.

Figure 1 shows a damper having a member S rigidly afiixed to the driven or driving shaft or to'any other rotatable part of any machine. This member S may have any shape or form. In Figures 1 and 2, the member S is represented in the form of a circular flywheel, for purposes of convenience. On the said member S is mounted an oscillating mass T which is able to freely move around the shaft on which the member S is tures will more fully appear from the following mounted. If desired, a bushing may be provided on the member S on which the oscillating mass T is mounted, preferably concentrically. This bushing is not shown on the drawings. If desired, a ball-bearing, needle-bearing, cylinderbearing, etc. may be employed. The mass T is shown mounted concentrically in relation to the center 0 on Figure 1, and in relation to the axis XX of Figure 2. However, the member S may be provided with an eccentric bushing in relation to the axis (not shown on the drawings, being self-explanatory), in which case the opening of the oscillating mass T may also be eccentric to the axis XX. 1

The restoring member or levers L may be one or two symmetrically placed levers as shown in Figures 1 and 2, or any number of levers. Each lever L is provided with an opening or 'arcuate runway 24. The oscillating mass T is provided with an opening or arcuate runway 26. The mem: her or lever L is operatlvely interconnected with the oscillating mass T through. the intermediary of a pin or roller 28. The member or lever L is further provided with a circular opening A25! in which a pivot axle 30 is mounted, so that the lever may rotate limitedly around it. The pivot axle 29 or A may be afilxed either rigidly or rotatably in the member S, for instance, by its ends 29--I and 29-2, as shown in Fig. 2.

The operation of this device has been fully described in the said two Salomon applications, Polyharmonic dynamic dampers, Serial Nos. 333,561 and 335,081.

One aspect of this invention comprises providing the lever L with an eccentric member A2 having an interior circular opening 29A1 in which, or through which, the pivot axle 29 or A passes and which serves as a bushing or as a bearing for the said pivot axle. The outer circumference of the eccentric member A: is eccentric in respect to the center G of the pivot axle 29. The eccentric member A2 should preferably have its center of gravity GAz on the radius R5 passing through the centers and C. The centrifugal force will thus urge the eccentric member A: into such a p sition that its center of gravity GA: will lie on the radius R5. Should the eccentric member A2 for any reason be moved from the radius Rs, its center of gravity GAz will force it to return to its normal position. An arrangement such as this will permit the lever L to pivot around the pivot axle 29 or around the outer circumference of eccentric member AaE, or simultaneously around both, or first partly around pivot axle 29 and then around eccentric member AzE, or vice versa.

Owing to the fact that the harmonic order 11 also depends upon the distance d as per the formula herein given, any change in d either by way of being augmented or diminished, would change the harmonic order. This distance d is equal to WK1 as shown on Fig. 1 (assuming W on the perpendicular at K2 to 0K2).

It is evident that the action of the lever L will also depend on the possibility it has of rotating around the outer circumference AzE of the eccentric member A2, 1. e., around the axis passing through the center CA2, namely, rotate around another point W1 instead of CA2, thus augmenting the distance d in the arrangement as shown in Fig. 1, or diminishing the distance d if a suitable arrangement will be provided. This arrangement increases the polyharmonic tuning efficiency of the device herein described, and enables it to take care of several harmonics simultaneously. s a rule, in an engine with harmonic orders of 5 /2, /2, '7 or 8, for example, this invention will first take care of the harmonics for which it is designed by choosing the relation between the pivot axle 29, the pin 26 and the runways provided for the pin, and thereafter with the assistance of the eccentric member A2, will take care of additional harmonics as well.

This invention comprises valuable improvements on the subject of the before-mentioned applications, providing an automatic control for the position which adjusts the polyharmonic damper of the character referred to, tea. given order. Such automatic control utilizgsjhelallation-of the centrifugal force provided in the damper during its rotation at difierent speeds.

One of such improvements comprises means rigidly affixed to at least one of the eccentric bushing-bearing members, such means beinga weight rigidly attached to said bushing-bearing members at a sufllcient distance from their center of rotation, or mounted in said bushing-bearing members eccentric to their center of rotation, so that when the centrifugal force increases, the said bushing-bearing members will be urged by the centrifugal force created by the said weight. When the centrifugal force increases with the increase of the speed of rotation, it displaces the said weights and also turns the said eccentric bushing-bearingsfrom one position to another, changing thereby the tuning conditions controlling the movement of the lever relatively to the shaft and to the other components of the damper.

One of such arrangements is schematically illustrated in Fig- 3, wherein the lever L is pivoted on a pin I00 on whichthe eccentric bushing-bearing member IllI is mountedfeither rigidly or rotatably around it. 'An arm or pivot means I02 connects the eccentric member IIJI with the weight I03N1. The lever LN1 of such a polyharmonic damper is shown in dotted lines by LN in Fig. 3, in its non-operative position. Accordingly, in such a position the center IMN of the eccentric bushing-bearing member IUIi also shown in dotted lines, may be so chosen that prior to the rotation of the damper it takes the position as shown in Fig. 1, and as soon as the rotation of the damper begins, this center IMN respectively takes a new position, for example, the position lll lm (Fig. 3); because of the weight was (shown in dotted lines) being urged by the centrifugal force from its position I03N to the position I03N1. It is advisable to provide the arm or pivot means I02 with resilient means I06 attached to a support I01 which may be rigid with the flywheel mass S of Fig. 1 or may be rigid with the free oscillating mass T of Fig. 1, or may be rigid with the lever L itself, as shown in Fig. 14. Such resilient means may be a spring I06 or a rubber, or a mixture of spring and rubber, or may be a pneumatic arrangement such as I08 for instance, as shown in Fig. '7. Instead of one spring, several springs may be employed simultaneously, operating by pull or push, or both.

One of the important aspects of this invention is the appropriate choice of the length of the arm I02, and of the value of the weight Hliim and of its shape and form.

From the aforementioned formula, the tuning order n.is directly proportional in certain relations to a and D, or only a or only D, and is in reverse proportion to d (i. e., if the 12 order is increased). Should all other symbols of the formula remain the same, then:

(1) When 11 increases, a decreases, or

(2) 12 increases and D increases, or

(3) 11. increases, a and D both increase, or

(4) 11, increases, d diminishes, or

(5) nincreases, It increases, and d diminishes,

(6) 1:. increases, D increases, and d diminishes.

In the case that n diminishes, vice versa relations will take place.

It may happen that, simultaneously, n will increase, a will slightly diminish, but D will au ment sufiici'ently to compensate for the diminishing of a; or, it may happen that d will diminish to compensate for the diminishing of a. Several of when rotating at certain such eventualities for tuning the n ordermay take place. and this invention provides means to automatically tune the lever L in a given damper according to the Order which has to be taken care 1 of, i. e., eliminated or substantially eliminated at corresponding speeds.

It is not feasible to describe all the movements of the components of the damper necessary for accomplishing these results, and by wayof ,example,'the most characteristic one will be given.

In Fig. 3, the lever LNI is shown in its operative position in dotted lines LN, in which position it is maintained when the center I04N1 of the eccentric bush-bearing member IOI lies on the radius RNi. The eccentric bushing member may, by way of example, be composed (as shown in Fig. 2) from'an axle 29-I, 29-2, on which the eccentricity making member 30 is mounted eccentricity making member 30. When 30 is rigid with the axle 20-I, 292, then the lever I02 may be mounted either on the member 30 or on g the axle 29-I, 29--2. When the member "30 is not rigid withthe axle 20 -I, 29-2, then the lever I02 should be mounted rigidly on the member 30.

In its non-operating position, and the lever I02 to which a weight I03N1 is attaohed occupy positions as shown in Fig. 3, such respective positions of lever LNl and lever I02 being controlled in particular by the position of the center of pivoting 504 of the eccentricity making member 30 around which the lever LNl is able to pivot. v

The corresponding position of 504, for instance, will lie on the radii RNl, when the lever I02 is in its lowest position as shown in Fig. 3.

The lever I02 may be provded with a weight |03N1 and resilient means I06 operatively interconnecting the lever I02 through the attachment II1 with the attachment I01 rigid with the member S mounted rigidly on the main shaft 505 as shown in Fig. 3.

When the damper rotates with various speeds, the position of the weight I03N1 will entirely depend on the resilience of the resilient means I05 the lever LN! he of any liind and nature and, for instanc resilient blade spring 501 or an arrangement a: shown in Fig. 4, comprising a support on which a lever H2 is mounted on a pivot I I3, the other end of said lever also having a pivot III on which is mounted another lever I I0. The pivots and 1evers may be so arranged that when the weight I03 N contacts the lever IIO, it will compress the spring II4 having a predetermined resiliency to correspond to the centrifugal force to which such weight I 03N will be subjected when it contacts the lever iln at predetermined R. P. M. of the damper. Thus, only after the resiliency of spring I I4 will be overcome could the weight I03N pivot the levers H0 and H2 and occupy the position I I03N2 for instance.

shown in Fig. 4 may be placed alongthe pathway 506 and may thus control more precisely the position of the lever I02, which will rest on such position-controlling means for as long as the corresponding R. P. M. of the damper will not exceed the predetermined ranges of value.

Thus, by way of example, at certain R. P. M., the pressure exercised by the weight I03N on the position-controlling means I09 may, for instance, be 140 pounds. Should we provide the resilient means of the blade spring 501, Fig. 3, or of the resilient means I I4 of Fig. 4 to be greater than 140 pounds, say for instance 155, then the weight I03N and also the lever I02 will rest on such spring until the R. P. M. will be so big that the and will take, for instance, the position I03Ni,

speed.

When non-rotating, the resilient means I06 will pull the lever I02 into the position I03N.

Thus, the center of pivoting 504 will respectively occupy the position from I04N1 to I04N2 to I04N, whereby the distance DN (i. e., the perpendicular from center 504 to the center of gravity GN of the lever LNi) DNl, displacing respectively, the center of gravity GN to the position GNI, GNz, and so on.

The difference between DN and DNl, and so on, may thus be controlled by the angular displacement of the weight I03N1 and of the lever I02 in regard to the center of pivoting 504 and thus, in order to provide a self-tuning damper, it will suffice to make such respective positions of the center of pivoting 504 and center of gravity GN correspond to the value 111 in the tuning equation, such as given herein.

On its way from the position I03N to the position I03N1 (i. e., from the position of rest of the damper to the position when it rotates at a certain speed) the lever I02 and the weight I03N will follow a predetermined pathway, for instance, 508 on Fig. 3. l

It will sufllce according to this invention, to provide means I09 as shown in Fig. 3, which may will change from DN to I centrifugal pressure will become equal to 155 pounds. This is extremely important to prevent the undesirable pivoting or the lever I02 durin the R. P. M. corresponding to the given centrifugal forces of -155, given purely for example only. It should be noted that such arresting position-controlling means as I09 and 501, Fig. 3, or as shown in Fig. 4, may be attached either to the member ,8 or to the member T of Fig. 3. This requires only a reasonable skill of engineering.

The eccentric bushing-bearing members 30, 29I, 292, may be provided as shown in Figs. 1, 2 and 3. In Figs. 5, 6 and '1 the ccentric I I8 may be mounted either around 28 or B,- or around the pin A (Fig. 2), or. around both of them simultaneously. Such an arrangement is shown by around Aas shown. However, the pin B may also be provided with one or two of such eccentries as shown in Figs. 11, 12, 13 and 14.

Instead of resilient means I06, a spring-blade or the like I23 (Fig. 8) may be used if affixed rigidly by attachment I24 to the lever (or to the flywheel mass S or to the oscillating mas T) and contacting by its free end I25 the attachment I26 rigidly affixed to the arm I02 to which the weight I03N1 is attached. Such type of spring I23 may also be employed with one end I21 (Fig. 11) attached directly to the pin A (or B) through suitable means I24-I, its free end I 25-I resting on attachment means I28 rigidly ailixed to the eccentric member A1 or B1.

The initial position of the eccentric bushingbearing member A1 or B1 as shown on Fig. 5,

may be so chosen that by movement of the weight I29: to a position I28m the center around which displacement; a displacement, for example, along the radius passing through the center (Fig. 3) of the rotation of the damper.

The eccentric members, as shown in Figs. 13 and 14, may also be employed if desired. In this case, the eccentric I33 cooperating with the pin B will be mountedin the lever L or flywheel mass or member S or oscillating mass T, and may be provided with arms or with weights I34 to control its positions. At the same time, the other eccentric members for the pin B may be either a simple opening I35 a shown in Fig. 9, or it may be an eccentric bushing-bearing member I36 (shown in Fig. 13), controlled by a special arm I39, together with the weight I31, if desired. Tuning of the lever may be controlled only by the weight I34 of the eccentric I33, in which case the arm I38 may be connected with the arm I39 through the intermediary of pivoted lever I48 or other articulated or flexible interconnection.

Still another embodiment of this invention is demonstrated in Figs. 11 and 12, wherein the eccentric members A1 or B1 are provided with arms MI and the lever L (or T or S respectively) are provided with a slot I42 through which the arm I4I may pass. Such arrangements are particularly advantageous for economy of space.

Another important feature of this invention is to provide operative interconnection between the arms which operate the bushing-bearing member of the same dampers. For instance, in Fig. 9, the weights I2I and I22 controlling the eccentrics A and B, are operatively interconnected through articulated means I64 which are pivoted on pivots I65, I66. Any number of such articulated interconnections may be used to coordinate relative displacements\ of one bushing-bearing in relation to others.

Still another aspect of this invention is illustrated in Fig. 3A wherein the lever Lu is provided with a cutout I46 in which a mass I4! is mounted so that it can freely move along the said cutout. The lower surface of the cutout may follow a circumference I48 made with a radius from the center 0 or with any other suitable radius. The position of the mass I41 in the cutout I46 will vary the position of the center of gravity GN of the lever LN1. The mass I41 may be provided with means to control its position mechanically, hydraulically, pneumatically, electro-mechanically, or electro-magnetically, depending upon the speed of rotation of the device. These means may be operated voluntarily or automatically. Such automatic means consist of an arm I50 with a weight I49n affixed to a gear I5I mounted on a shaft I52, which is mounted on the lever Lm. When the weight I49: moves into the position I49m it moves the mass I41 from its original position (shown by dotted lines) to the position as shown in solid lines by I41 in Fig. 3

and corresponding to the position I49m of the lever I50. Resilient means I53 may be provided to control the displacement of the mass I41 and to push it back when the damper reduces the speed or stops. 6 In addition, resilient means I64 may also be provided to establish an opposing.

new position Gm, thus augmenting the distance Dm to the distance Dm from the pivot A1. The proper choice of augmentation or diminution of such distance will correspondingly influence the characteristics of the damper and thus take care of the harmonic or other disturbances corresponding, for instance, to the position of the center of gravity of Bus or any other intermediate positions between Du: or between Du.

The mass I41 may also have the form of a cylinder I5|, as depicted in Fig. 8, mounted in a cylindrical cutout I58 provided with resilient means I58. The inclination of the longitudinal axis of the cylinder I58 may be so chosen that there will be sufiicient forces provided to control the displacement of the weight I5'IN from its normal position I511: to its operating position 151m.

In Fig. 9, this cutout may be ,cylindrical or have any other shape, for instance, I60, and follow a circumference made by the radius I6I drawn from the center I62, eccentric to the center 0 of the rotation of the shaft. The choice of this eccentricity gives the desired sensitivity for the displacement of the weight, taking into consideration the resilient means I63, which may be spring, pneumatic, hydraulic, or electro-magnetic. 1

In the case of controlling the center of gravity of the lever L by means of the displacement of the masses and weights such as I41 and I49N (as shown in Fig. 3A), all desired predetermined positions of centers of gravity of the lever Ln may be predetermined accordingly and synchronized with predetermined speeds.-

Still another aspect of this invention consists of providing, in the damper described, the lever of the type described, with self-adjustable weight of the type described herein for Figs. 8, 9. The

arrangement such as the lever of Salomon provided with thefree mass of Rubissow consists of providing in the mass of such lever, a cutout having a cylindrical or a square cross-section for example, at a certain angle a in respect to the tangent to, which is perpendicular. to the radius r. The angle a may be very small and its choice dependent upon how much the chosen influence of the centrifugal force at certain speeds must displace the weight towards the part of the cutout which is at a further distance from the center of rotation of the damper than the former position of the weight in the same cutout. A spring I59 (Fig. 8) or I63 (Fig. 9) must be placed in the lower end of the cutout. During rotation of the damper, the spring is compressed by the weight to a predetermined degree, thereby controlling the position of the weight in the cutout at all speeds of rotation. The displacement of the position of the weight in the cutout permits the displacement of the dampers center of gravity from one position to another, and while this is accomplished automatically, as a function of the speed of the rotation of the damper, the automatic tuning capacity of the lever is thereb also controlled. Appropriate choice of the cross-section of the cutout, its length, the angle a, value of the weight and the force of the spring will be i r 2,898,722 necessary for proper control of the automatic tuning of the lever.

These arrangements may be employed without simultaneous use of the eccentric bushing-bearing member as described in thi application, The cutouts may be of any shape or form and their longitudinal symmetry axis may also follow a circumference of a radius I62 (Fig. 9), for instance, which is concentric to the radius r. The angle a between the circumference of the radius I62 and the circumference of the radius r may be considered similar to the angle a of Fig. 8.

The movement of the weight may be towards the free end of the leveras shown in Figs. 8 and 9, or towards the center of the gravity of the lever. If desired, several cutouts may be employed simultaneously with side of them.

The resilient means, instead of being as shown in Fig. 8 and Fig. 9, may also be on both sides of the weight, one working as compressor and the other as a depressor. Only compressor or only depressor resilient means may be employed. Resilient means may be replaced by pneumatic piston-cylinder arrangement.

Another aspect of this invention provides a combined use of the described eccentric bushingbearing member with or without arms, or with several weights placed inr tion. A synchronized speed-control device may talsii be employed if desired, for automatic con- This invention is particularly important, inasmuch as it permits the tuning of this particular damper to any desired order or disturbing force of any nature. This latter aspect, as shown in Fig. 15, may be applied directly to the bushingbearing members A or B or A1, A: etc., or B1, B2 etc., or directly to the arms or means which control the position of the center of gravity of the lever. lhis means mayalso be applied in combination with automatic controlling means for the eccentric bushing-bearing members as herein described, in which latter case, their au v tomatism will be controlled manually or by a synarms and weights, by operatively interconnecting such eccentric bushing-bearing members with the aforesaid weights of the character of weights or masses I41, I51N. This may be effected particularly by means of rigid interconnections, such as I64, Fig, 9, interconnected through the pivots I65 and I66, to the Weights I44 (or directly to the eccentrics A and B, not shown on the drawings), or through pulley and flexible connections, gears, chains, caterpillar and the like.

Still another embodiment is illustrated in Fig. 14, having, in addition to the eccentric bushingbearing member B, a cylindical bearing I61 which is mounted in a bushing I68 provided in the lever- L. Such cylindrical bearing I61 will permit the pin B4 to rotate while it'is urged left or right, thus diminishing tangential frictional effort be tween the contacting surfaces of displacing parts.

Another, and one of the most important aspects of this invention provides voluntary consimultaneous use of the eccentric bushing-beartrol of the position of the eccentric bushing-bearing members. This is accomplished by an arrangement of levers, flexible interconnections, ar-

ticulated means, pneumatic cylinder-piston devices, electro-mechanical or electro-magnetic means, with a collar-like member mounted on a shaft in such a way that when Pushed to and fro longitudinally along the shaft, the position of the said bushing-bearing members is controlled. This voluntary control enables the operator of the engine to tune the damper at a given speed to a given sensitivity in advance, thus eliminating the undesirable torques or vibrations. This is extreme- 1y important and applicable to all engines where chronized controlling device. This aspect permits the varying of the tuning of a resonance damper of the type described herein during the operation of the engine itself.

Fig. 15 represents the mass S (which may also be the free oscillating mass T or the lever L itself) in which the pin 463 rigid with the eccentric bushing-member 464 is mounted. A rigid arm 465 and a small axle 466 are rigidly affixed to the pin 463 or may be directly affixed to the eccentric 464 itself. A rigid connection in the form of a wire, bar, arm, chain or flexible cable 461 operatively interconnects the axle 466 with the pivot lever 468 which may be of any shape or form. Such interconnection is establishedby means of a pivot 469 or other suitable equivalent means, and by means of a pivot I16 on which the lever 468 pivots. The pivot I16 is mounted rigidly in respect to the shaft I1I by means of a girdl I12 rigidly attached to the said shaft.- When the device rotates, the centrifugal force urges the arm 461 in the direction of the arrow I13. A controlling non-rotatable device I14 comprising a, preferably, well-polished plate or disk is'mounted on a girdle or collar I15, provided on shaft HI and able to slide to and fro thereon, guide means I16, one or more, may be provided in the frame, I11, which is rigid with the foundation or the ground or the chassis. When the controlling device "4 i pushed to and fro, it contacts the lever 468 in the surface I18 which surfac itself i in constant contact with the disk I14 because of the rotation of the lever 468 with the shaft HI and because of absence of rotation of the disk I14. By pushing the disk to and fro, the arm I61 of the lever 6I8,control s the position of the eccentric I64 to the desired value,

thus controlling. as herein described, the characteristics of the damper and it tuning to the ap tary control by the operator, of the position of the eccentricmembers A1 and/or B1, and/or of the position of the center of gravity of the lever or levers.

3. Dampers which consist of automatic control of the position of the eccentric member A: and/or B1 bymean of automatic synchronized speed-controlling or speed regulating devices, such as described herein.

4. Dampers using a pneumatic control of the position of the eccentric members A1 and/or Bl or of the weights I41.

trically to the axis of the latter, a lever mounted.

. for oscillation about said pivot means eccentri- Having now ascertained and described the" nature of the said invention and the manner in which it is to be performed, I declare that what I claim is the following:

1. A vibration or oscillation damper for a machine shaft comprising a first member rigidly mounted on said shaft, a second member mounted for movement about the axis of said shaft and said first member, at least one pivot means oscillatably mounted on said first member eccentrically to the axis of the latter, a lever mounted for oscillation about said pivot means eccentrically to the axis of said pivot means and the center of gravity of said lever, a. first arcuate runway in said lever, a second arcuate runway in said second member, a pin of a radius smaller than the radius of curvature of either of said runways operatively connecting said lever with said second member, a solid weight eccentrically secured to said pivot means, resilient means adapted to resist movement of said-weight in response to centrifugal force, said Divot means, weight, and re-.

silient means cooperating to shift or adjust the ivot point of said lever relative to the center of gravity of the lever in response to centrifugal force, thereby tuning said damper to various orders of vibration.

2.v A vibration or oscillation damper for a machine shaft comprising a first member rigidly mounted on said shaft, a second member mounted for movement about the axis of said shaft and said first member, at least one pivot means oscillatably mounted on said first member eccentrically to the axi of the latter, a lever mounted for oscillation about said pivot means eccentrically to the axis of said pivot means and the cenresilient means cooperating to shift or adjust th pivot point of said lever relative to the center of gravity of the lever in response to centrifugal force, said damper further comprising means for supplementing or increasing resistance to movement of said weight in response to centrifugal 'force, said supplemental or increased resistance being applied at a certain point or at certain points in the path of movement of said weight,

thereby tuning said damper to various or ders' ofvibration.

3. A vibration or oscillation damper for a machine shaft comprising a first member rigidly mounted on said shaft, a second member mounted for movement about the axis of said shaft and said first member, at least one pivot means oscillatably mounted on said second member eccencally to the axis of said pivot means and the center of gravity of said lever, a first arcuate runway in said lever, a second arcuate runway in said second member, a pin-of a radius smaller than the radius of curvature of either of said runways operatively connecting said lever with said second member, a solid weight eccentrically secured to said pivot means, resilient means adapted to resist movement of said weight in response to centrifugal force, said pivot means, weight, and resilient means cooperating to shift or adjust the pivot point of said lever relative to the center of gravity of the lever in response to centrifugal force, thereby tuning said damper to various orders of vibration.

4. A' vibration or oscillation damper for a machine shaft comprising a first member rigidly mounted on said shaft, *a second member mounted for movement about the axis of said shaft and said first member, at least one pivot means oscillatably mounted on said second member eccentrically to the axis of the latter, a lever mounted for oscillation about said pivot means eccentrically to the axis of said pivot means and the center of gravity of said lever, a first arcuate runway in said lever, a second arcuate runway in said second member, a pin of a radius smaller than the radius of curvature of either of said runways operatively connecting said lever with said second member, a solid weight eccentrically secured to said pivot means, resilient means adapted to resist movement of said weight in response to centrifugal. force, said pivot means, weight, said resilient means cooperating to shift or adjust the pivot point of said lever relative to the center of gravity of the lever in response to centrifugal force, said damper further comprising means for supplementing or increasing resistance to movement of said weight in response to centrifugal force, said supplemental or increased resistance being applied at a certain point or at certain points in the path of movement of said weight.

5. A damper as set forth in claim 1 wherein said pivot means comprises a pivot-axle and an arm attached rigidly thereto, clearance means being provided in said second member around said pivot-axle to permit the movement of said second member around the axis of said shaft.

6. A damper'as set forth in claim 3 wherein clearance means are provided in said first member around said pivot-axle to permit the movement of the said second member and said pivotaxle around the axis of said shaft.

7. A damper as set forth in claim 2 wherein said means for supplementing or increasing resistance to the movement of said weight in response to centrifugal force comprises at least one articulate member having resilient opposing means and mounted in the path of movement of a contact member rigidly attached to said weight to resist the movement of said weight as it pivots around said pivot means in response to said centrifugal force.

GEORGE A. RUBISSOW.

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