US634327A - Variable-power transmitter. - Google Patents

Description

' Patentqd Dot. 3, I899. L. M. DIETEBICH.

VARIABLE POWER TRANSMITTER.

(Application filed Apr. 26, 1899.)

- (No Model.) 3 Sheets-8heet l.

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THE no Patented Oct. 3, 1899.

' L. M. DIETERICH.

VARIABLE POWERIRANSMITTER.

(Applicatinn filed Apr. 26, 1899.}

3 Sheets-Sheet 2,

(No Model.)

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No. 634,327, Patented Oct. 3, I899. L. m. DIETERICH. VARIABLE POWER TRANSMITTER. I

(Application filed Apr. 26, 1899.)

3 Sheets-.-Sheet (No Model.)

"NrrE-D ST TES PATENT -F LUDW'IG M. DIETERICH, F HARTFORD, CONNECTICUT, ASSIGNOR TO THE DIETERIOH GEAR COMPANY, OF-NEWV YORK, N. Y.

VARIABLE-POWER TRANSMITTER.

SPECIFICATION forming part of Letters Patent No. 634,327, dated October 3, 1899.

Application filed April 26, 1899 $e1'ial No. 714,4:73. (No m'odel.) h

To all whom it may concern: tween the intermediate mechanism and the Be it known that I, LUDWIG M. DIEIERICH, driven mechanismwill cause the rotation of a subject of the Emperor of Austria-Hungary, the latter and will also tend to shift the axis residing in the city of Hartford, State of Con-' of the intermediate mechanism, but in a di- 5 necticut, have invented a new and useful rection opposite to thatin which the first set of 5 5 Power-Transmitter, of which the followingis transmitting; devices tends to move said axis. a specification. Consequently as long as the opposing recti- My invention relates to improvements in lineal resultants which are produced by the power transmitters, and particularly to a two sets of transmitting devices are equal no [0 power-transmitter which is intended to reshifting of the axis of the intermediate meeh- 6c. ceive power at a substantially uniform speed anism will occur; but when one of the rectiand force and deliver the same at a speed and lineal resultants is greater than the other the force which may vary with variations in the said axis of the intermediate mechanism will resistance to be overcome. be shifted with relation to the axes of the 5 The object of my invention isto provide a driving and driven mechanism until equilibdevice by means of which a source of uniform rium is established between the two opposing power may be advantageously used in operresultants, this equilibrium being brought ating mechanism whose resistance may vary about by changes in the conditions or posiowing to variations in the load upon it, the tions of the two sets of transmitting devices,

20 speed of the driven mechanism being reduced whereby one set of transmitting devices beupon an increase of its resistance or load and comes less effective in producing the rectiincreased upona reduction ofsuch resistance lineal resultant and the other set becomes or load at will or automatically. more elfective, the changes in the conditions With this general object in view an appa or positions of the transmitting devices be- 25 ratus embodyingthe preferred form of my ining due to the shifting of the axis of the invention comprises a revoluble driving mechtermediate mechanism. 7 anism, a revoluble driven mechanism, a revo- I have found that what may be called togluble mechanism intermediate the driving gle transmitting devices are particularly adand driven mechanisms and so arranged that vantageous in carrying out my invention, by

30 the axis about which it revolves may be which term I mean any mechanisms or deshifted with relation to the axes of revolution vices arranged to transmit motion from the of the driving and driven mechanism, and driving mechanism to theintermediate mechtwo sets of devices, one between the driving anism and from the latter to the driven mechmechanisn and the intermediate mechanism anism and which involve the fundamental 3 5 and the other between the latter and the principle of the well-known toggle-levers. driven mechanism, by means of which the My invention consists, furthermore, in the power from the driving mechanism is transfeatures, details of construction, and combimitted to the intermediate mechanism and nation of parts, which will first be described from the latter to the driven mechanism, said in connection with the accompanying draw- 0 transmitting devices being of such a nature ings and then particularly-pointed out in the that they resolve the rotary motion delivered to claims. them by the revoluble driving mechanisminto In the drawings, Figure l is an elevation of two resultants, one of which is rotary, while an apparatus embodying one part of my inthe other is rectilineal, whereby the set of vention. Fig. 2 is an end view, partly in sec- 5 transmitting devices between the driving tion, of the said apparatus; Fig. 3, a detail 5 mechanism and the intermediate mechanism elevation of a part of an apparatus embodywill cause the rotation of said intermediate ing all the features of my invention; Fig. 4, mechanism and at the same time tend to shift a side elevation of the same; Fig. 5, a transthe axis of said intermediate mechanism, verse sectional view of a bicycle driving-gear 50 while the other set of transmitting devices beprovided with my invention; Fig. 6, a detail I00 sectional view, partly in elevation, of the same; Figs. Tand 8, detail views to be referred to hereinafter.

Referring to Figs. land 2 of the drawings, 0 is a shaft revolved from anysuitable source of power. (Not shown.) This shaft is provided with a disk (I, fixed to it in any suit-able manner, the disk and shaft together being embraced within the term driving mechanism or power-supplying mechanism. Opposite to the said driving mechanism islocated a revoluble driven mechanism, in this case com prising a driven shaft and a disk (1, fixed thereon and suit-ably mounted to permit of rotation, the axis of revolution of said driven mechanism preferably being in a line with the axis of revolution of the driving mechanism.

ietween the driving mechanism and the driven mechanism above described is located a suitable revoluble intermediate mechanism comprising in the present instance a pair of rings R R fixed to opposite ends of a shaft 0, the axis of revolution of the said intermediate mechanism being movable or adjustable with relation to the axes of the driving and driven mechanism, which result may be obtained by arranging and constructing the intermediate mechanism so that its axis of revolution may be shifted with relation to the axes of the driving and driven mechanism as, for example, by mounting the shaft 0, which is in this case concentric with the axis of revolution of the intermediate mechanism, in a movable bearing Z), said bearing Z) being made movable by mounting it on arms F, which are longitudinally movable in supports G.

In order to transmit motion from the driving mechanism to the'intermediate mechanism and from the latter to the driven mechanism, I employsuitable transmitting mechanisms, one mechanism between the driving mechanism and intermediate mechanism and the other between the latter and the driven mechanism.

In the preferred form of my invention each transmitting mechanism comprises a set of transmitting devices, each set consisting in the present instance of two transmitting devices connected to the intermediate mechanism in a manner to permit the adjustment or shifting of the axis of the intermediate mechanism with relation to the axis of the driving mechanism.

The transmitting devices shown in Figs. 1 and 2 consist of angularly-movable arms, as shown at L L each mounted for revolution about an axis concentric with the axis of revolution of the driving meehanismas, for example, by providing each arm with a hub or boss through which the shaft 0 passes loosely. The outer ends of the said arms L L are each provided with a slot, into each of which slots enters a pin I I, fixed in one of the rings R of the intermediate mechanism. Each transmitting device, furthermore, may be locked or connected to the driving mechanism by means of a suitable locking device, such as the frictional locking device shown in Figs. 1 and 2, which consists of a cam, as shown at 0 c pivotally connected to the respective arm, as indicated at t If. These cams are so arranged that when locked they bear against the periphery of the disk d and when unlocked they slide over or along said periphery.

The transmitting devices between the intermediate mechanism and the driven mechanism and the locking devices which look the said transmitting devices to the driven mechanism are similar to those just described, the only difference being that they are arranged in a reverse order.

The operation of the apparatus thus far described is as follows: \Vhen the shaft 0 is rotated by suitable means, its disk d is also rotated. If nowitbe assumed that the axis of the intermediate mechanism or, in other words, the axis of the shaft 0 is concentric with the axis of the shaft 0, the rotation of the disk d (which is supposed to be in the direction of the arrow, Fig. 2) will cause the cams c c to lock the arms L L respectively, to the disk (1, thus forcing said arms to revolve about the axis of the shaft 0, thereby also causing the ring R te be revolved about its axis, owing to the fact that the outer ends of the arms L L are connected to the said ring B. As the rings R and R are fixed to the shaft 0, the revolution of the ring R will cause the revolution of the ring The revolution of the latter will cause the arms L L" to be revolved about the axis of the driven shaft 70, and owing to the friction between the eams c and the periphery of the disk d the said cams will be locked to said disk, and hence the latter will be compelled to revolve with the arms L L and the intermediate mechanism. It will be plain, therefore, that when the axis of the intermediate mechanism is concentric with the axes of the driving and driven mechanisms the driving mechanism will drive the driven mechanism at the same rate as its own. If new the axis of revolution of the intermediate mechanism be shifted, so that instead of being concentric with the axes of the driving and driven mechanisms it is eccentric therewith, a different operation will occur.

In order to simplify the description of this operation, it becomes necessary for me to designate and define two imaginary planes of reference. These are as follows: The plane passing through the axis of the intermediate mechanism and through the axis of the driving mechanism I will call the major plane, the line in which it would cut Fig. 2 being indicated at 1 1 The plane coincident with the axis of the driving mechanism and at right angles to the major planeI will call the minor plane, its intersection with the plane of Fig. 2 being indicated by the line 00 as. Furthermore, in referring to these planes I will consider that side of the minor plane on which the axis of the intermediate mechanism is located as above said minor plane and the opposite side as below said plane, said terms being in accordance with the showing in Fig. 2. It is to be understood, however, that said terms are relative only and are to be considered in that sense, for if the axis of the driving mechanism is shifted to a vertical position the terms above and below would not apply if used in their usual sense. With this explanation I will now describe the operation of the mechanism shown in Figs. 1 and 2.

Referring to Fig. 2, which shows the axis of the intermediate mechanism eccentric to that of the driving mechanism, it will be found that the rotation of the disk 61 in the direction of the arrow, Fig. 2, will cause the cam 0 while above the minor plane to look its arm L to the said disk, and said arm would cause the periphery of the ring R to rotate with the disk d at a peripheral speed as much greater than the peripheral speed of the disk cl as the distance of the pin 1 from the axis of the shaft 0 is greater than the distance of the periphery of the disk 01 from the said axis of 0. As, however, all parts of the periphery of the ring R must revolve at the same peripheral speed, the pin I below the minor plane will be revolved about the axis of the shaft 0 at the same peripheral speed as the pin I and owing to its connection with the arm L will cause the latter also to revolve about the axis of the shaft 0; but owing to the eccentricity of the axis of the intermediate mechanism the distance of the pin I (when below the minor plane) from the axis of the arms L L" is less than the dis tance of the pin 1 (when above the minor plane) from said axis. Therefore, as is obvious, the cam c on the arm L will move as much faster than the cam c as the distance of the pin 1 from the axis of 0 is greater than the distance of the pin I from the same axis; but since the cam c is locked to the disk (Z, and therefore traveling at the same peripheral speed as the periphery of said disk, and since the cam c is traveling at a greater peripheral speed than that of the cam 0 therefore the cam 0 travels at a greater peripheral speed than the periphery of the disk cl. Hence the friction between the cam c and the disk cl will tend to keep said cam c unlocked, the cam merely slipping along the periphery of the disk d. As the arm L moves around its axis from a position above the minor plane (in which position it is shown in Fig. 2) to a position below the minor plane its effective lever-armthat is to say, the distance between its connection with the ring R and the axis of 0- becomes gradually less, while as the arm L moves from the position below the minor plane (in which position it appears in Fig. 2) to a position above the minor plane its effective lever-arm becomes greater. When the said arms L L lie with their respective points of connection to the ring R in the minor plane,

the effective leverages of the arms L L are equal and the cams c a will travel at the same peripheral speed, and hence at this moment both cams will be locked to the disk (1; but as the effective leverage of the arm L constantly grows less, even after it passes below the minor plane, its cam 0 will commence to travel faster than the periphery of the disk cl, and therefore will be unlockedthat is to say, will slip or slide over said periphery of the diskand, furthermore, since the effective leverage of the arm L will continue to increase after said arm has passed above the minor plane its cam 0 will no longer travel faster than the periphery of the disk (1, and hence the latter will maintain the said cam in its locked position, the said arm L thereby becoming the means for driving the ring R while the arm L then turns about the axis of the shaft 0 without doing any useful work until it has again passed above the minor plane. In this way the arms L L alternat-ely are locked to the driving mechanism and unlocked therefrom, thereby alternately acting to drive the ring R". In other words, when a transmitting device is above the minor plane it will be locked to the disk d and will drive the intermediate mechanism, whereas when below the minor plane it will be unlocked from the disk d and will be dragged around by the revolution of the intermediate mechanism until it is again brought to its position for operation. Itis to be understood, however, that when more than two transmitting devices are employed in each set of transmitting mechanisms-as, for example, three transmitting devices located at equal distances apart, as shown in Fig. 3 and as will be referred to hereinafter-only that transmitting device which is nearest the major plane and above the minor plane will be locked to the driving mechanism, while all of the remaining transmitting devices will be carried around by the revolution of the intermediate mechanism and will be unlocked from the driving mechanism.

When only two transmitting devices are employed in each set of transmit-ting mechanisms, as shown in Figs. 1 and 2, the intermediate mechanism is revolved at a variable speed, varying from a minimum to a maxi mum and then to a minimum again, the first minimum speed occurring when the transmittin g device lies with its point of connection to the intermediate mechanism in the minor plane and is moving in a direction to carry it above said minor plane. At this time the angular velocity of the intermediate mechanism isjust equal to that of the driving mechanism. As the said transmitting device rises above the minor plane its angular velocity remains the same, while the angular velocity of the intermediate mechanism gradually increases until the point of connection between the said transmitting device and the intermediate mechanism lies in the major plane and above the minor plane. At this time the angular velocity of the intermediate mechanism is a maximum and of course in excess of that of the driving mechanism.

Since the minimum angular velocity of the intermediate mechanism is equal to the angular velocity of the driving mechanism, which is constant, and since the minimum speed of the said intermediate mechanism only occurs at two instants, and since also between these two instants the said speed is greater than the minimum, therefore the average angular velocity of the intermediate mechanism is greater than that of the driving mechanism. \Vhen 110w more than two transmitting devices are employed in a set, the period during which one of the transmitting devices is operating the intermediate mechanism is reduced, this period depending upon the number of such transmitting devices in a set. In other words, only that transmitting device which is nearest the major plane and above the minor plane will drive the intermediate mechanism,and consequently when one transmit-ting device above the minor plane has passed the major plane the next following transmitting device above the minor plane will be approaching said major plane, and when the one which is approaching becomes closer to the said major plane than is the transmitting device which is receding the closer one is locked to the driving mechanism, and the other is thereby released or unlocked therefrom. In this manner the average angular velocity of the intermediate mechanism is kept much closer to the maximum with a number of transmitting devices than if only two were used, and the fluctuations in angular velocity of said intermediate mechanism become less in proportion to the increase in number of transmitting devices in a set.

Referring now to the method of transmit ting motion from the intermediate mechanism to the driven mechanism and considering only those transmitting devices which are between the intermediate mechanism and the driven mechanism, it will be found that the revolution of the said intermediate mechanismwill cause that transmitting device which is below the minor plane and nearest the major plane to become locked to the driven mechanism, thus causing the driven mechanism to be turned by the intermediate mechanism. The other transmitting device which is at that time above the minor plane will be carried around idly by the revolution of the intermediate mechanism, owing to the fact that its cam or locking device is being moved with a peripheral speed less than that of the periphery of the disk (1' of the driven mechanism. In other words, the angular velocity of the transmitting device which is below the minor plane and nearest the major plane will be greater than the angular velocity of any other transmitting device in the same set and the angular velocity of the driven mechanism is equal to that of the said transmitting device to which it is locked. Hence its angular velocity must be greater than that of any other transmitting device than the one to which it is locked, and consequently it will tend to keep unlocked the cams of all other transmitting devices than the one to which it is locked. It will be noted, moreover, that the angular velocity of each transmitting device below the minor plane is greater than that of the intermediate mechanism,whereby it results that the number of revolutions per unit of time of the driven mechanism is greater than that of the intermediate mechanism. Thus as there is an increase in the number of revolutions per unit of time between the driving mechanism and the intermediate mechanism and also between the latter and the driven mechanism the driven mechanism will run at a greater angular velocity than will the driving mechanism.

It is to be observed that when the axes of the intermediate mechanism and of the driving and driven mechanisms are concentric the driven mechanism is moved at the same angular velocity as the driving mechanism. Furthermore, when the axis of the intermediate mechanism is not concentric with the axes of the driving and driven mechanisms there is anincrease in speed of the driven mechanism over that of the driving mechanism, and it will be obvious that this increase of speed varies with the amount of eccentricity of the axis of the intermediate mechanism. Hence by shifting the journalbearing U, Fig. 1, of the intermediate mechanism in the construction shown in Figs. 1 and 2 the speed of the driven mechanism with relation to that of the driving mechanism may be varied.

In order to provide a simple automatic means for producing the desired adjustment of the axis of revolution of the intermediate mechanism with relation to the axis of the driving mechanism or driven mechanism, I employ a suitable motion-resolving mechanism as a transmitting mechanism, so that a part of the rotary motion of the driving mechanism is converted into a rectilineal result ant, tending to shift the axis of the intermediate mechanism in one direction. Two sets of such motion-resolving transmitting devices are employedone set between the driving mechanism and the intermediate mechanism and the other between the intermediate mechanism and the driven mechanism, these sets being arranged to produce rectilineal resultants which tend to act in opposite directions.

It is clear that with the driving mechanism running at a constant speed and force any change in the load of or resistance to be overcome by the driven mechanism must be compensated for by a variation in the speed of said driven mechanism. For example, if the load on the driven mechanism is increased the speed of said driven mechanism must be correspondingly reduced, as otherwise a change of the power of the driving mechanism would be necessary. Furthermore, when the speed of the driven mechanism is to be reduced the axis of revolution of the intermediate mechanism must be shifted toward the axes of the driving and driven mechanism. Hence it follows that with an increase of the load on the driven mechanism the eccentricity of the intermediate mechanism should be reduced, while when the load on the driven mechanism is reduced the eccentricity of the intermediate mechanism should be increased. The motion-resolving transmitting devices employed for the production of oppositely-acting rectilineal resultants are therefore so arranged that an increase in the load on or of the resistance of the driven mechanism will cause an increase in that rectilineal resultant which tends to cause a shifting of the axis of the intermediate mechanism in the direction of reducing the eccentricity of said axis and that a reduction in said load or resistance will cause a reduction in said rectilineal resultant. As a consequence in the first instance the increase in the rectilineal resultant tending to reduce the eccentricity of the axis of the intermediate mechanism will enable it to overcome the other oppositely-acting rectiliueal resultant, and thereby shift the intermediate mechanism, so that its axis will be less eccentric than before. In the second instance-viz., when the rectilineal resultant tending to reduce the eccentricity of the axis of the intermediate mechanism is red u cedthen the oppositely-acting resultant is enabled to overcome the one which has been reduced and to shift the intermediate mechanism, so that its axis becomes more eccentric. It will be apparent, moreover, that the increase or decrease in the resultant which tends to reduce the eccentricity of the axis of the intermediate mechanism must not be permanent even tho ugh the increased load on the driven mechanism remains permanent, sinceif it were every increase in load, whether great or small,on the driven mechanism would move. the axis of the intermediate mechanism to its position of concentricity or, if actual concentricity be prevented, to its position of least eccentricity, thereby always producing the same speed ratio between the driving and driven mechanism .which would not be proper. Hence it is requisite that the motion-resolving transmitting devices be so arranged that upon a shifting of the axis of the intermediate mechanism a change in the ability of the transmitting devices to produce rectilineal resultants will take place, the movement of the axis of the intermediate mechanism to a position of less eccentricity causing that set of transmitting devices whose rectilineal resultant has produced such movement to assume a condition in which it cannot produce so great a rectilineal resultant as it did before the said movement, whereas the other set of transmitting devices assume a condition wherein they can produce a greater rectilineal resultant than they did before. By this arrangement the two oppositely-acting rectilineal resultants are bro u ghtinto equilibrium with each other, so that by a variation in the load on the driven mechanism the axis of the intermediate mechanism will be shifted to a position where the speed ratio between the driving and driven mechanisms will be proportioned to the total load on the driven meeh-- anism. In order to obtain all these results, I have found that transmitting mechanism consisting of two sets of oppositely-arranged toggle transmitting devices are especially suitable. The specific arrangement and construction of one form of my invention embodying such toggle transmitting devices will now-be described.

Referring to Fig. 3, R is a ring which forms part of the intermediate mechanism, similar to the ring R in the apparatus shown in Figs. 1 and 2. At 0 is shown the driving-shaft, on which is fixed the disk (1 the two forming a driving mechanism similar to that in Figs. 1 and 2. The transmitting devices each consists of toggle-arms m, pivoted to the ring R" at b and loosely mounted on the driving-shaft 0 these arms being provided with looking devices in the form of cams c.

The apparatus just described has all of the functions of that shown in Figs. 1 and 2 and the following in addition. When a transmitting device is above the minor plane and nearest the major plane, it is locked to the driving mechanism by its cam mechanism, and owing to its action as a toggle-arm will tend to force the ring R to a position where its axis will he more eccentric. The other toggle-arms not being locked to the driving mechanism will not resist this tendency to move the ring, and in case the said movement takes place will be bent back farther upon their central pivots. As will be obvious to those skilled in the art, that toggle device which is locked to the driving mecha ism if it be prevented from moving the ring R in a rectilineal direction will exert a pressure in such direction and at the same time by the rotation of the driving mechanism will cause a rotation of the ring R As the direction in which the operating toggle devices tend to move the ring R is a radial one, such direction is constantly changing with the revolution of the said transmitting device; ont owing to the fact that the axis of the intermediate mechanism is mounted for movement only in a fixed rectilineal direction the radial movement which the op erating transmitting device tends to cause is converted into a tendency to move the axis of the intermediate mechanism in said fixed rectilineal'direction.

The rectilineal resultant produced by the operating toggle transmitting device depends upon condition of the same thatis to say, upon the size of the acute angle included between longitudinal axes of the two parts of the toggle deviceaud is inversely proportional to such angle, the resultant becoming greater as the angle decreases and smaller as the angle increases. As a consequence the movement of the axes of the intermediate mechanism toward a position of greater eccentricity will cause the toggle transmitting devices to continuously assume conditions where the rectilineal resultant which it can produce with aconstant power on the driving mechanism grows constantly less. On the other hand, the ability of the said toggle transmitting device to produce a reel ilineal resultant grows constantly greater as the eccentricity of the intermediate mechanism becomes smaller.

Referring now to the set of toggle transmitting devices between the intermediate mechanism and the driven mechanism, it is to be observed that the points of connection of the said toggle transmitting devices to the intermediate mechanism are respectively in line with the points of connection of the corresponding toggle transmitting devices between the driving mechanism and the intermediate mechanism, as will be seen in Fig. 4;. Moreover, the acute angles formed between the longitudinal axes of the two parts of these transmitting devices are of opposite sign to those of the first set of transmitting devices, or, in other words, the central pivots of the first set of transmitting devices all lie to one side of the radii through their points of connection with the intermediate mechanism, while the central pivots of the second set of transmitting devices all lie on the opposite sides of their corresponding radii. It is to be noted thatin this construction, as in that illustrated in Figs. 1 and 2, the driven mechanism is revolved by means of that transmitting device which for the time is below the minor plane and nearest the major plane, the other transmitting devices of the same set being merely pulled around idly on their axis of revolution by the intermediate mechanism and comingintoaction only after they have respectively passed below the minor plane and one after the other come into a position which brings them nearest the major plane.

lVhen a transmitting device of the second set is locked by its cam or other locking device to the driven mechanism, it produces a rectilineal resultant which is opposite in di rection to that produced by the operating transmitting device of the first set. Therefore as the resultant produced by the operating transmitting device of the first set (and whichI will call the first resultant) tends to move the axis of the intermediate mechanism into a position of greater eccentricity and the resultant of the operating transmitting device of the second set (which I will call the second resultant) tends to move the said axis of the intermediate mechanism into a position of less eccentricity so it results either that no movement of the said axis occurs or it occurs in the direction of that resultant which is greater; but as the shifting of the axis of the intermediate mechanism causes a change in the ability of the operating toggle transmitting devices of the first and second set, respectively, to produce their respective rectilineal resultants, owing to a change in the angles made by the two parts of the toggle devices, and since, as will be observed from the drawings, an increase in the first resultant is accompanied by a decrease in the second resultant, and vice versa, the automatic shifting of the axis of the intermediate mech anism due to a preponderance of one rectilincal resultant over the other will bring about an equilibrium of the said resultants, and thereby stop the shifting of the said axis of the intermediate mechanism until suchtime as the said equilibrium of the rectilineal resultants is again destroyed. This destruction of the equilibrium of the two rectilineal resultants is brought about bya change in the load upon the driven mechanism. For example, if theload is suddenly increased its initial tendency would be to slow down the driving mechanism, thus tending to drag on the operating toggle transmitting device of the second set, and owing to the momentum of the intermediatemechanism the said operating toggle transmitting device endeavors to suddenly increase its acute anglcthat is to say, it tends to straighten out. At the same time said transmitting device tends to hold back the intermediate mechanism, and thus produces a tendency in the operating-toggle transmitting device of the first set to straighten out or increase its acute angle. It now the axis of the intermediate mechanism were concentric with the axes of the driving and driven mechanism, the opposite rectilineal resultants produced by the increase in load of the driven mechanism would be equal, and hence no movement of the axis of theintcrmediate mechanism would occur; but if the axis of the intermediate mechanism is eccentric the operating transmitting device of the second set will be in a somewhat more folded-up position than will that of the first set, and hence the second rectilineal resultant will be greater than the first rectilineal resultant and the axis of the intermediate mechanism will be shifted into a position of less eccentricity and until equilibrium of the two resultants is broughtabout, as hereinbefore explained.

In order to prevent the parts from ever assuming a position when the two operating transmitting devices of the first and second sets, respectively, will have the same acute angles, it is necessary to prevent the axis of the intermediate mechanism from at any time assuming a condition of concentricity with the axis of the driving and driven mechanisms. This may be done in any suitable way, as by limiting the movement of the sliding armsfor example, by the pin z-in the direction of concentricity.

Referring now to Figs. 5 and (5, which show the application of my invention to the driving-gear of a bicycle, II is a casing, and II a nut 11.

pedal-lever having a crank-shaft I1 preferably formed integral therewith and passing through the casing, the other end of the said shaft being provided with another pedal-lever H secured to said crank-shaft by a lock- Fastened to the shaft and pedals aforesaid by means of lugs t is a sleeve 1 adapted to turn with the shaft and-pedal-levers and mounted upon antifriction-rollers J, which rollers are supported upon and turn in bearings h of the casing H. To the sleeve 1 is secured, by means of screw connections, a collar Q, having cut-away portions Q, in which are located locking balls or rollers q. Around the collar are located three rings V V V each having an extension W, which is connected to a link W. These links W are mounted at their other ends upon pins to of 'a rotatable and bodily-movable ring U. In order to render the ringU rotatable, it is arranged to roll on antifrictioirbearings U of a ring U which is pivoted to and swings about a shaft or stud U the arrangement of all the parts being such that the axis of revolution of the ring U can never become concentric with the axis of revolution of the shaft H this being prevented by one edge of the ring U coming into contact with the casing. By this mechanism the ring U, as will be seen, is capable of movement from a position where it is only slightly eccentric to a position of greater eccentricity. Upon the opposite side of the ring U are corresponding rings V V V having links V similar to those previously described as pivotally con nected to pins w of the ring U.' AtY is shown a collar loosely mounted on the sleeve 1 This collar is fixed to the front sprocket Y by a screw connection, as shown. Antifriotion-rollers are provided to permit the rota tion of the said collar and its annexed parts in the frame H. The operation of this device is as followsi \Vhen power is applied to the pedal-lever, the crank-shaft is revolved andwith it the sleeve 1 the latter rolling upon the bearings J and causing the rotation of the collar Q. As the latter rotates the rings V V V will intermittingly and sert'atim become locked to the said collarQ by the locking balls or rollers q, thereby revolving the ring U through the medium of the respective links W. The said ring U will in turn revolve the respective links Wt, which will then rotate the respective rings V V V which through the instrumentality of the corresponding locking-rollers q, Fig. 6, will successively bind upon the collar Y, and thereby turn the sprocket-wheel, which drives the bicycle in the usual manner. Upon an increased resistance being offered to the progress of the bicycle, assuming the propelling power to remain unchanged, the ring U will be shifted to bring the axis of the ring U into a position of less eccentricity with reference to the axis of the driving or crank shaft H Thereupon the speed ratio of the driving and driven mechanism is so changed that the driven mechanismviz., the collar Y and its attached sprocket-will be turned at a reduced speed compared with what said driven mechanism had before the increased resistance to the progress of the wheel. Thus by this mechanism when a hill or a rough road is reached the cyclist will be enabled to pass the same without the expenditure of extra exertion, although of course at a slower speed. \Vhen, however, the resistance to the progress of the wheel is reduced, the ring U and with it the ring U, shifts to a position ofgreater eccentricity, thus giving a greater speed ratio between the driven and the driving mechanism,whereby the same amount of exertion of the rider as before will cause the vehicle to progress at a greater speed than when it was encountering more resistance to its progress. It will be seen that in this construction the shaft H sleeve I and collar Q, may be considered as the driving mechanism, the sprocket-wheel Y and collar Y as the driven mechanism, while the ring U is the intermediate mechanism, having a movable or adjustable axis of rotation, and the links W W and their rings V V V V V V form the toggle transmitting devices. Fnrthermore,the inclined openings shown at Q Fig. 6, together with the balls or rollers q, located therein, form the locking mechanism or cam-locking devices.

Referring to the broad principles of my invention underlying the several embodiments hereinbefore described, it will be seen that in each there is a driving mechanism, a driven mechanism, and certain means connecting these two mechanisms, which means acts unyieldingly in transmitting motion from the driving mechanism to the driven mechanism and is consecutively adjustable.

I use the term unyieldingly-acting means as contradistinguished from means which acts yieldingly. The distinction intended by me will be made apparent by the following ex- IIO planation: In some devices for transmitting powerfor example, belt passing around two pulleys or two smooth friction-wheels in actual contact0nly a certain amount of power can be transmitted, because if the load becomes too great the belt will slip on the pulleys or the friction-Wheels will slip on'each otherthat is to say, the means for transmitting the power will yield to the excessive load and the driven mechanism cannot be operated from the driving mechanism. In another class of transmitting devices the only limitation to the power which can be transmitted is the strength of the various parts of the transmitting mechanism-as, for example, where cog-wheels are used to transmit power. In the latter case no matter what load may be placed on the driven mechanism there will be no yielding of the transmitting means, and unless the cog-wheels break the power applied by the driving mechanism will be transmitv ted. The latter sort of mechanism I term unyielding transmitting mechanism.

It will be seen that my device pariakes of l the nature of the last class of deviccsthat is to say, is an unyielding means for transl mitting powerbccause although in the construction described and shown the connecting devices which serve to lock the togglearms to the driving mechanism or driven mechanism, respectively, are frictional devices, yet when they have once looked a toggle-arm to its respective disk any additional load placed upon the driven mechanism will only act to lock said connecting devices more firmly and no yielding of thetransmitting means can occur.

By the term consecutively adjustable as employed by me I intend to indicate that feature of the construction which permits the unyieldingly acting means to pass through every intermediate adjustment from one extreme of adjustment to the other.

I am aware that it is old to transmit motion unyicldingly from a driving mechanism to a driven mechanism, and I am also aware that it is old to provide unyielding means for such transmission which can be adjusted to give certain fixed predetermined changes of speed ratio between the driving and driven mechanism. Furthermore, I know that it is old to transmit motion yieldingly (as opposed to unyieldingly) from a driving to a driven mechanism, the said yielding transmitting means being consecutively adjustable, so as to give any desired speed ratio between two extremes. Each of these said old constructions has certain advantages fully recognized by those skilled in the art. In the first construction the unyielding transmission of power is the important advantage and in the second construction the consecutive adjustability of the transmission mechanism the great advantage; but for many purposes both of said constructions are disadvantageous, the first because no way of consecutive adj nstment of the unyielding transmitting means has hitherto been produced and the second because under many conditions a yielding transmission of power is unsuitable. In my invention the advantages of both these old constructions are combined, so that I obtain an unyielding transmission of power from the driving to the driven mechanism and the possibility of obtaining any desired speed ratio between two extremes. Hence in the use of the term consecutively adjustable I employ the word consecutively in its mathematical sense, as will be understood by those skilled in the art.

I am aware also that it is old to provide a reciprocating transmitting means which acts nnyieldingly and is consecutively adjustable; but my invention differs from this in that the transmitting means does not reciprocate about a center, but moves continuously around its center in an orbital manner. Ilence I use the term orbitally movable as a distinction from such previous reciprocating devices.

llaving now Fully described n'iyinvention, what I claim, and desire to secure by Letters Patent, is-

l. The combination, with a revoluble driving mechanism, and a second revoluble mechanism, of a plurality of orbitally-movable transmitting devices connected to the said second revoluble mechanism, and detachable connecting devices between the transmitting devices and the driving mechanism.

2. The combination, with a. revoluble driving mechanism, and a second revoluble mech anism having their axes of revolution nonconcentric, of a plurality of transmitting devices connected to the said second revoluble mechanism, and detachable connecting devices between the transmitting devices and the driving mechanism.

3. The combination, with a revoluble driving mechanism, and a second revoluble mechanism, of a plurality of transmitting devices connected to the said second revoluble mechanism, detachable connections between the transmitting devices and the driving mechanism, and means for permitting the alteration of the relative positions of the axes of revolution of the driving mechanism and the said second revoluble mechanism.

4-. The combination, with a revoluble driving mechanism, and a second revoluble mechanism, of a plurality of transmitting devices connected to the said second revoluble mechanism, automatic detachable connections between the transmittingdevices and the driving mechanism, and means for permitting the alteration of the relative positions of the axes of revolution of the driving mechanism, and the said second revoluble mechanism.

5. The combination, with a revoluble driving mechanism, and a second revoluble mechanism, said mechanisms having their axes capable of eccentric location relative to each other, of a plurality of transmitting devices acting on the said second revoluble mechanism, and intermittingly-acting means for connecting each transmitting device to the driving mechanism during a portion of the revolution of the latter and then disconnecting it therefrom.

o. The combination, with a revoluble driving mechanism, and asecond revoluble mechanism, of a plurality of transmitting devices acting on the second revoluble mechanism, intermittingly-acting means for connecting each transmitting device to the driving mechanism during a portion of the revolution of the latter and then disconnecting it therefrom, and means for permitting the alteration of the relative positions of the axes of the driving mechanism and the said second revo luble mechanism.

7. The combination, with a revoinbledriving mechanism, and a second revoluble mechanism whose axis is capable of an eccentric location relative to that of the driving mechanism, of a plurality of transmitting devices acting on the said second revoluble mechanism, and cam devices for connecting each transmitting device to the driving mechanism during a portion of the revolution of the latter and then allowing it to be disconnected therefrom.

8. The combination, with a revoluble driving mechanism, and a second revoluble mechanism whose axis is capable of eccentric location relative to that of the driving mechanism, of a plurality of transmitting devices acting on the second revoluble mechanism, and frictionally-controlled mechanism for detachably connecting each transmitting device to the, driving mechanism during a portion of the revolution of the latter.

9. The combination, with a driving mechanism, and a driven mechanism, of orbitallymovable means for transmitting power from the driving mechanism to the driven mechanism, and means for permitting the adjustmentof said transmitting means whereby the speed ratio between the driving and driven mechanism may be altered.

10. The combination, With a revoluble drivin g mechanism, and a revoluble intermediate mechanism, of a plurality of orbitally-movable transmitting devices connected to the said revoluble intermediate mechanism, detachable connecting devices between the transmitting devices and the driving mechanism, and a driven mechanism operated by the intermediate mechanism.

11. The combination, with a revoluble driving mechanism, and a revoluble intermediate mechanism having their axes of revolution non-concentric, of a plurality of transmitting devices connected to the said revoluble intermediate mechanism, detachable connecting devices between the transmitting devices and the driving mechanism and a driven mechanism operated by the intermediate mechanism.

12. The combination, with a revoluble drivin g mechanism, and a revoluble intermediate mechanism, of a plurality of transmitting devices connected to the said revoluble intermediate mechanism, detachable connections between the transmitting devices and the driving mechanism, means for permitting the alteration of the relative positions of the axes of revolution of the power-supplying mechanism and the intermediate mechanism, and a driven mechanism operated by the intermediate mechanism.

13. The combination, with a revoluble driving mechanism,and a revoluble intermediate mechanism, of a plurality of transmitting devices connected to the said revoluble intermediate mechanism, automatic detachable connections between the transmitting devices and the driving mechanism, means for changing the relative positions of the axes of revolution of the driving mechanism and intermediate mechanism, and a driven mechanism operated by the intermediate mechanism.

14. The combination, with arevoluble drivin g mechanism, and a revoluble intermediate mechanism, said mechanisms having their axes capable of eccentric location relative to each other, of a plurality of transmitting devices acting on the revoluble intermediate mechanism, intermittiugly-acting means for connecting each transmitting device to the driving mechanism during a portion of the revolution of the latter and then disconnecting it therefrom, and a driven mechanism operated by the intermediate mechanism.

15. The combination, with a revoluble driving mechanism, and a revoluble intermediate mechanism, of a plurality of transmitting devices acting on the revoluble intermediate mechanism, intermittingly-acting means for connecting each transmitting device to the driving mechanism during a portion of the revolution of the=latter and then disconnecting it therefrom, means for permitting the alteration of the relative positions of the axes of the power-supplying mechanism andthe intermediate mechanism, and a driven mechanism operated by the intermediate mechanism.

16. The combination, with a revoluble driving mechanism, and a revoluble intermediate mechanism whose axis is capable of an eccentric location relative to that of the driving mechanism, of a plurality of transmitting devices acting on the revoluble intermediate device, cam devices for connecting each transmitting device to the driving mechanism during a portion of the revolution of the-latter and then allowingit to be disconnected therefrom and a driven mechanism operated by the intermediate mechanism.

17. The combination, with a revol uble drivin g mechanism, and a revoluble intermediate mechanism Whose axis is capable of an eccentric location relative to that of the driving mechanism, of a plurality of transmitting devices acting on the revoluble intermediate mechanism, frictionallycontrolled mechanism for detachably connecting each transmitting device to the driving mechanism during a portion of the revolution of the latter, and a driven mechanism operated by the interme diate mechanism.

18. The combination, with a revoluble driving mechanism, a revoluble driven mechanism,and a revoluble intermediate mechanism, of two sets of transmitting devices, the first set between the driving mechanism and the intermediate mechanism, the second set between the intermediate mechanism and the driven mechanism, and means for permitting ism, and locking devices arranged to lock the second set of transmitting devices to the driven mechanism.

20. The combination with a revoluble driving mechanism, a revoluble driven mechanism,and a revoluble intermediate mechanism, of two sets of transmitting devices, both connected to the intermediate mechanism, frictional locking devices intermediate the first set of transmitting devices and the driving mechanism and frictional locking devices intermediate the second set .of transmitting devices and the driven mechanism.

21. The combination,with a revoluble driving mechanism, a revoluble driven mechanism,and a revoluble intermediate mechanism, of two sets of transmitting devices, both connected to the intermediate mechanism, frictional locking devices between the two sets of transmitting devices and the driving and driven mechanisms respectively, and means for permitting the adjustment of the axis of revolution of the intermediate mechanism.

22. The combination,with a driving mechanism, and a driven mechanism, of unyielding transmitting meansintermediate the driving and driven mechanism and adjustable by the resistance of the driven mechanism, wherebya constant power is transmitted with varying ratios of speed and force, from the driving mechanism to the driven mechanism in an unyielding manner.

23. The combinatiomwith a revoluble driving mechanism, and a revoluble driven mechanism, of a revoluble intermediate mechanism,transmitting devices connecting the driving mechanism and the intermediate mechanism and tending to shiftin one direction the axis of the said intermediate mechanism, and transmitting devices connecting the intermediate mechanism and driven mechanism and tending to shift in an opposite direction the said axis of the intermediate mechanism.

24. The combination,with a revoluble driving mechanism, a revoluble driven mechanism, and revoluble intermediate mechanism, of two sets of transmitting devices arranged to transmit power, the first set from the driving mechanism to the revoluble intermediate mechanism, and the second set from the intermediate mechanism to the driven mechanism, both sets of transmitting mechanism bein g so arranged as to resolve apart of the motion of revolution into a rectilineal motion,the rectilineal resultant produced by the first set being opposite-in direction to that produced by the second set, whereby the axes of revolution of the revoluble intermediate mechanism and of the driving and driven mechanism will be automatically varied by a variation in load on the driven mechanism.

25. The combination,with a revoluble driving mechanism, a revoluble driven mechanism,and a revoluble intermediate mechanism, of two sets of motion-resolving means, one set arranged to transmit rotary motion from the driving mechanism to the intermediate mechanism and also to produce a rcctilineal resultant in one direction, the other set being arranged to transmit rotary motion from the intermediate mechanism to the driven shaft and to produce a rectilineal resultant opposite in direct-ion to that of the first set.

26. The combinatiomwith a revoluble driving mechanism, a revoluble driven mechanism,and a revoluble intermediate mechanism, the axes of the intermediate mechanism and of the driving and driven mechanism being relatively movable, of two sets of motion-resolving means, one set arranged to transmit rotary motion from the driving mechanism to the intermediate mechanism and also to produce a rectilineal resultant in one direction, the other set being arranged to transmit r0- tary motion from the intermediate mechanism to the driven shaft and to produce a rectilineal resultant opposite in direction to that of the first set.

27. The combination, with a revoluble driving mechanism, a revoluble driven mechanism and revoluble intermediate mechanism, of two sets of toggle transmitting devices, one set connecting the driving mechanism and the intermediate mechanism, the other set connecting the intermediate mechanism and the driven mechanism.

28. The combination, with a revoluble driving mechanism, a revoluble driven mechanism, and a revoluble intermediate mechanism the axes of the intermediate mechanism and of the driving and driven mechanism being relatively movable, of two sets of toggle transmitting devices, one set connecting the driving mechanism and the intermediate mechanism, the other set connecting the intermediate mechanism and the driven mechanism.

29. The combination, with a revoluble driving mechanism, a revoluble driven mechanism,and a revoluble intermediate mechanism of two sets of oppositely-acting toggle transmitting devices, one set connecting the driving mechanism to the intermediate mecham ism and the other set connecting the intermediate mechanism to the driven mechanism.

30. The combination, with a revoluble driving mechanism, a revoluble driven mechanism,and a revoluble intermediate mechanism, the axes of the intermediate mechanism and of the driving and driven mechanism being relatively movable, of two sets of oppositelyacting toggle transmitting devices, one set connecting the driving mechanism to the intermediate mechanism, the other set connecting the intermediate mechanism to the driven mechanism.

31. The combination, with a revoluble drivin g mechanism, and a revoluble driven mech anism having their axes in line with each other, of a revoluble intermediate mechanism having its axis of revolution movable with relation to the axis of the driving and driven mechanism, and two sets of toggle transmitting devices, one set acting in a direction op posite to the other, one set connecting the driving mechanism to the intermediate mechanism, the other set connecting the intermediate mechanism to the driven mechanism.

32. The combination, with a revoluble driving mechanism, a revoluble driven mechanism, and a revoluble intermediate mechanism having its axis adjustable with relation to the ax es of the driving and driven mechanism, of two sets of toggle transmitting devices, connected to the intermediate mechanism, means for intermittingly locking the driving mech-. anism to and unlocking it from one set of transmitting devices, and means for intermittingly locking the driven mechanism to and unlocking it from the other set of transmitting devices. I

33. The combination, with a revoluble driving mechanism, a revoluble driven mechanism, and a revoluble intermediate mechanism havingits axis adjustable with relation to that of the driving and driven mechanism, of two sets of oppositely-acting toggle transmitting devices, connected to the intermediate mechanism, means for intermittingly locking the driving mechanism to one set of transmitting devices and unlocking it therefrom,and means for lockin g the driven mechanism to the other set of transmitting devices and unlocking it therefrom.

34. The combination,with a revoluble driving mechanism, a revoluble driven mechanism ,and a revoluble intermediate mechanism, of two sets of transmitting devices connected to the intermediate mechanism, each set comprising a plurality of toggle devices, means for locking the toggle devices of one set, serictit'm to the driving mechanism and unlocking them therefrom, and means for locking the toggle devices of the other set, seriatim to the driven mechanism, and unlocking them therefrom.

35. The combination,with a revoluble driving mechanism, a revoluble driven mechanism, and a revoluble intermediate mechanism having its axis of revolution adjustable with relation to the axes of the driving and driven mechanism, of two sets of oppositely acting toggle transmitting devices connected to the intermediate mechanism, frictionally-actuated locking devices between the driving mechanism and one set of transmitting devices, and frictionally-actuated locking devices between the driven mechanism and the other set of transmitting devices.

36. The combination,with a revoluble driving mechanism, a revoluble driven mechanism,and a revoluble intermediate mechanism, having a movable axis, of two sets of transmitting devices connected to the intermediate mechanism, each set comprising a plurality of toggle devices, one set arranged to act in a direction opposite to the other, cam mech anism between the.driving mechanism and one set of transmitting devices, and cam mechanism between the driven mechanism and the other set of transmitting devices.

37. The combination with a driving mech anism and a revoluble mechanism, said mechanisms having their axes relatively adjustable, of means for transmitting motion from one mechanism to the other,whereby the speed ratio of the two mechanisms may be varied to any desired extent between two extremes and an unyielding transmission of power is obtained.

38. In a power-transmitter, the combina tion, with a driving mechanism, a driven mechanism, and an intermediate rotatable and bodily-movable ring, of two sets of rings, links connectingeach ring of each set to the intermediate ring and cam locking devices for locking the corresponding sets of rings, individually, to the driving and driven mechanism respectively.

39. In a power-transmitter, the combination, with a drivingshaft, a collar driven thereby, a driven mechanism provided with a collar, and two sets of rings, one set loosely mounted on each collar, respectively, of cam devices for locking the rings individually to their respective collars, an intermediate rotatable ring, links connecting the rings of each set to the intermediate ring, and a bodily-movable supporting device for said intermediate ring.

LUDWVIG M. DIETERIOH.

Witnesses:

HERBERT KNIGHT, PETER F. SoUNoK.

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