US2250982A - Governor - Google Patents

Description

July 29, 1941.

H. ca. ADLER GOVERNOR 4 Sheets-Sheet 1 Filed Feb. 20, 1939 FIGZ.

INVENTOR.

, HERMAN GQADLER BY ATTORNEYS y 1941- H. G. ADLER 2,250,982

' GOVERNOR I Filed Feb. 20, 1939 4 Sheets-Sheet 2 FIGS.

INVENTOK HERMAN GADLER Arromvzg I July 29, 1941. AD 2,250,982

GOVERNOR l Filed Feb. 20, 1939 4 Sheets-Sheet 5 FIG.5. H69.

INVENTOR. HERMAN s. ADLER MMMQ ATTORNEYS July 29, 1941 H. G ADLER 0, 8

' GOVERNOR Filed Feb. 20, 1939 4 Sheets-Sheet 4- FIGJI. FIGJZ;

INVENTOR. HERMAN G.ADLER 29 Z i E v ATTORNEYS -to be adjusted .to operate with substantially the shown in Fig. .1;

ll, and if desired may cooperate therewith.

Patented July 29, 1941 UNITED STATES PATENT OFFICE Herman G. Adler, Detroit, Mich, assig'nor to Novi. Equipment Company, Novl, Mich., a corporation .of Michigan Application February 20, 1939, Serial No. 257,557 20 Claims. (01. ear-s) The present invention relates to a governor for internal combustion engines.

It is an 'object of the present invention to .provide an internal combustion engine governor which, while very compact, is exceedingly efllcient and can be manufactured economically and with a high degree of uniformity.

Another object of the present inventionis to provide a speed responsive device which is so I constructed as to besubstantially free from wear.

A further object of the invention is to provide an engine speed stable.

It is a further object of the present invention provide an engine speed governor which may governor which is inherently same efliciency over a large range of speeds. v It is a further object of the present invention to provide an engine speed governor which may be adjusted while in actual operation for different speeds.

Other objects of the invention will be apparentas this-description proceeds and whentaken in conjunction with the accompanying drawings, wherein 'Fig. 1 is aside elevation of my improved gov-' .ernor indicating its connection to the throttle of an internal combustion engine;

Fig. 2 is a vertical section "of the governor Fig. 7 is a vertical section showing a some what difi'erent embodiment of my invention;

Fig. 8 is an enlarged fragmentary detail of the device shown in Fig. 7;

Fig. 9 is a chart showing governor characteristics for a governor of the type shown in Fig.7;

' This The gear l3, which may be a straight spur gear or a helical gear, as desired, is keyed or otherwise secured to a shaft l4, suitably journaled in the housing It.

In order to reduce friction a ball bearing, generally indicated at i5, is provided, the inner race of which, I6, is secured to a disk II. The inner race it is mounted on a bushing I8 which is rotatable relative to the shaft [4. A second plate I9 is rotatably mounted on a bushing", which in turn is rotatably mounted on the shaft H. A washer 2| rotatably mounted on the bushing is formed with a circular; groove therein for the reception of balls 22, and a corresponding anhular groove is formed in the plate ltfThe outer circumference with a conically shaped a purpose which will presently be described.

Keyed or otherwise secured to the shaft is a driving member 24, shown in detail in Figure 4.

member is provided with a plurality of radially extending slots for the reception of relatively heavy governor balls. 26. Rotation of the shaft M, as will be readily apparent, rotates the driving member 24' and hence 'theballs 26. Du to centr' ugal action against the conical portion 23 of the plate IS, the balls tend to force Fig. 10 is a diagram illustrating why rolling motion of balls obtains; and Figs-11 to 13 are charts showing performance of my improved govemor.

Referring first to Figures 1 to 4, the governorcomprises a housing It attached to a base by suitable securing means, such as for example, screws l2. The governor is mounted adjacent the'eng'ine to be governed and is adapted to be in Figure 2 Lubrication may take place throughopenings a fan or centrifugal element driven by a gear mating with the gear l3 shown the plate It, together with the washer 2|, to the left, as seen in Figure 2.

The shaft l4 has'a stop thereby and abutting against a split ring, or the like, 28, received in a suitable groove in the shaft l4.

Suitable means, which will subsequently be described -in detail, are provided for transmitting motion of the washer 21 to the engine-control means, and in addition for biasing the washer 2| and hence the plate I! toward the right in Figure 2. i

It is desired to point out certain important advantages of the construction as it is thus far described: The centrifugal element of this inventhe plate I! and the washer 2 I.

When the drive shaft I4 is rotated at a given portion 23 ford washer 21 carried assembled to the' freely therein,

' doing so, it would 2 speed, each ball develops a centrifugal force which is transmitted to the plate or race I9, and more particularly to the conically shaped portion 23 thereof. This tends to move plate l9 and the washer 2| to the left, as seen in Figure 2. The magnitude of this force upon the plate I1 is determined not only by the angular velocity of the drive shaft and radius of gyration of each ball,

but also by the cotangent of the angle formed by the conical portion 23 at the point of contact with the balls 26. 1

The advantages of the novel arrangement of the elements of this invention as thus far described can now be pointed out. Assume that the pressure upon the upper race l9 due to centrifugal force upon the balls is balanced by the resisting force of .this race due to the spring tension, subsequently to be described, in such a way that the balls are at some position intermediate to innermost and outermost positions. It is then evident that at a constant speed, each element of the unit, consisting of the drive shaft I4, plates l1 and IS, the driver 24, and the balls 26, are rotating at the same angular velocity. There will be no relative movement between any of these parts and consequently there will be no wear.

Now if the speed be, say, slightly increased, the centrifugal force upon the balls will increase. causing a small radial motion of the balls with a corresponding axial motion of the conical race l9. However, since the upper race l9 and .the lower race H are mounted freely upon the drive shaft, these plates, or races, during the period of acceleration will not rotate at the angular velocity of the drive shaft. Further, since the change in speed is accomplished during several revolutions of the drive shaft, each ball 25 will roll easily into its new position causing the upper and lower plates to rotate at such speeds as to automatically permit this free rolling motion. That during acceleration the balls actually roll into their new positions may best be shown by reference to Figure 10, wherein ABC is a section of a V-grooved track of infinite length containing ball P2. It will be noted thattheball races rotate faster than the driver. Since however, the driver is decelerating, this conditlon is present automatically, and pure rolling again is certain to take place.

It is therefore evident that in this combination of elements the balls can never skid. When the speed is constant, there is no relative motion between the balls, driver and races. When the speed changes, the balls freely move into new positions with pure rolling motion. I found that this ideal condition eliminates wear, and permits of extremely close regulation without 'lag, as shown by results of actual tests appended hereto.

It is evident from the above that while the balls move into new positions the speed of the upper and lower plates lags, or leads, the angular velocity of the drive shaft by but few revolutions per minute. Since this smalldifierence in speeds promotes the free radial motion ,of the balls, there is again no perceptible wear due to the motion on either the upper or lower plates.

In order to transmit motion of the washer 2| to the control in a manner to regulate the speed of the internal combustion engine, I provide the following associated mechanism: Suitably journaled in the casing l0 and having one end excontacts the inclined sides of the groove at points C1 and C2. If now a force F be applied to the center of the ball, the turning moment Fri thereby produced will cause the ball to roll along the track. The rotation will take place about axis PIPZ, which is always perpendicular to the bisector of angle ABC.

In the embodiments shown in Figures 2 and 7, this axis of rotation is therefore inclined'to lower plate Of course, there must always be a small difference in speedbetween the speed of the driver.

and the upp and lower races, before rolling motion can take place. Thus, referring to Figures 2 and 4, assume that the driver is accelerating while it rotates in a clockwise direction. In

would require that the speed of upper race 23 and lower race ll be somewhat less than the speed of tend to rotate each ball in an anticlockwise direction, and this latter rotation tending outside the casing, I provide a shaft 30. Keyed or otherwise secured to the shaft 30 is a bifurcated member 3| (see Figure 3) adapte'd to span the member l4 and having portions engaging the washer 2|. If desired, suitable bearings, such for example as needle bearings 32, may be provided, and in addition a suitable oil seal 33 may also be provided for the shaft 30. The casing I0 is provided with a circular projection 34 which is centrally apertured to receive the shaft 30. A lever 35 is keyed or otherwise secured to the projecting end of the shaft 30 and, as seen in Figure 1, is adapted to be connected bya link 36 with the throttle or other control 31 of the internal combustion engine. Journaled on the cylindrical portion 34 lever 38. This lever is therefore angularly adjustable about the axis of the shaft 30. A rod or other adjusting means 39 is connected to the lever 38 and the other end of the rod 39 may be conveniently accessible to the operator of the motor. J

In order to provide means for counterbalancing the movement of the washer 2| due to the centrifuga1 action of the balls 25, I provide a spring 40 interconnecting levers 35 and 38 in a manner now to be described. Lever 35 has proiecting therefrom a short arm 4| which preferably is ofiset so as to be substantially aligned with a corresponding arm 42 projecting from the lever 33. As will be evident, tension of the spring 40 tends to rotate the lever 35 in a counter-clockwise direction as seen in Figure 1, and this force is transmitted through the bifurcated member 3| directly to the washer 2|. By adjusting the position of the lever 38, the initial position of the arm 42 may be predetermined. It is contemplated that the lever 38 may be set to desired position, at-which time the engine is governed at a desired speed.

Other means are provided for positively closing of the casing is a second greater rate of build up,

the engine would attain etc., that in order to obtain stable without undue loss in efiiciency, or

. creases.

are out. Curve 3 shows straight cone surface, the relation between movement of the cone and the force upon it is represented by a straightline, as shown by the line AB, Figure 5. In this figure the ordinates represent the axial force upon the upper race, and

the abscissae represents the movement of the race. The line AB is taken to represent the force on the upper race of 2000 R. P. M., while CD represents the force upon the upper race at 1900 R. P. M. Consequently, if the engine is to be governed so that at full load it will operate at 1900 R. P. M. and at no load at 2000 R. P. M., the spring resistance upon the upper race must be 9.4 lbs. at'1900 R. P. M. and 18 lbs. at 2000 R. P. M.

In Figure 5 the two speeds referred towere selected without regard to stability of performance, and it is possible that, if a-spring resistance as shown by the line CB were applied, the engine would hunt, at least at, or near, no load.

This condition of hunting can generally be remedied by the application of a spring of a that is, one having a resistance characteristic such as indicated by the line EB, for example, in Figure 5. However, this would result in inefficient performance, as now a considerably lower full load speed and the per cent regulation would thereby be increased.

It is generally found in tests on engines equipped with governors, that as the spring rate of a stable centrifugal governor is decreased, hunting takes place at, or near, no load, and then as the decrease in spring rate is continued, hunting may take place between no load and 10% load. A further decrease in spring rate may then cause the engine to hunt anywhere between no load and 30% load. A still further reduction in spring rate may cause hunting between no load and 50% load, etc.

It follows from the above, that since in the first case the engine is stable from 100% and in the second case from 100% to 30% load, and inthe third case from 100% to load, performance, undue increase to 10% load,

in per cent regulation, the eflective spring rate must increase as the load upon Referring again to Figure 5, .if a spring rate represented by the line EB is sufflcient to insure stability at no load, a spring resistance character istic shown by the curve CFB will provide stable performance at all loads, and still maintain the desired per cent regulation. a

In Figure 6 is shown the force developed by the balls upon the upper race at various speeds. Curve 1 shows the force developed when the balls are in. Curve 2 shows this force when the balls the effective spring rate the increase in spring if it were applied directly at-each speed, that is, load per inch deflection, to the upper race 11. u

The, geometry involved in properly designing a governor of the type disclosed is shown in Figure 1. In this figure T represents the radius of adjusting movement of arm '42 carried by manual lever 38. carried by the governing lever 35 is represented by x. In the position shown, a1 represents the the engine de- 0 can be established. A spring and the length of arms a1 and as are computed The radius of movement of arm 4| given or assumed setting, and a: represents the arm' of said spring when manual lever 38 is adjusted to control ata different speed. It is to be understood that movement of lever 38 to various positions causes the.governor to control the engine at various corresponding speeds. At any In the design of the governor, the dimensionm is selected, being the total travel of race l9 desired. Itslimiting positions correspond to full open and minimum throttle.

It can be shown that when a spring is applied externally its effective rate as applied to the race l9'varies directly as the square of its lever arm, i. e.

R=Rsa (1) where R=effective spring rate Rs=actual rate of spring, and a=spring arm From Formula 1, the spring arm which with I a given spring rate, will produce a desired effective rate, may be computed, i. e.

Referring again to Figure.6, it will be noted that the desirable effective spring rate decreases as the speed decreases. In order to maintain good performance over a long range of speeds, the spring rate must be changed so as to provide the proper eiTective rate for each speed.

However, there are manygovernor applications where the same engine is required to operate at various governed speeds. Thus, in the case of a tractor, plowing may be done 'at a certain'spee'd,

while when using the power take off another speed is desired, and when driving the tractor from one place to another, still another speed may be required. In order to avoid the troublesome necessity of actually changing springs, 'I have provided the structure described. The adjusting lever 38 is mounted so that it rotates concentrically with the lever 35. From the known operating requirements the maximum and minimum speeds are known, and from the chart shown in Figure 6 the corresponding spring rate rate is then selected from Formula 2 above. From this data the load upon the spring and the corresponding deflection may be readily computed and in this manner,

the values of L1 and L2 established. For this purpose; torques about pivot points are balanced, the arm of the force acting axially on the race being conveniently taken as one inch, whence Fg=FsJZ1 (5) where v F =a xial force on the race Fs=force of spring From the above Fs=Fg/a 1 arm of the spring 00 with the manual lever at a I w to the ball bearings which may be computed and L1 computed as Li=Lo+d (7) where L is the original length of spring, and.

d=the spring deflection, necessary to develop the force Fe aesopea principally in the substitution of a screw 50 for varying tension in the spring and in the substitution of a curved race 52 for the conical race 23, shown in Figure 'l. The bifurcated bell crank 53 is pivoted as at 54 within the housing 55, and

The point at which the graphs of these equations intersect establishes the value of :n, and since L2 is known, 1 may be determined graphically, or else computed by triangulation. This completes the computations and .the geometry of Figure 1 may now be laid out. Manual lever'33 and arm 42, and governing lever 35 and arm 4| may be drawn. It will be recognized that dimensions of these parts are kept within convenient limits by the selection of a suitable spring, but that the actual spring selected may have a rate between reasonably wide limits. After the actual spring rate is known, the foregoing method of design results in a governor which operates to govern engine speed with a very low per cent regulation, at various selected speeds, and with high stability.

Referring to Figure 1, it will be noted that when the adjusting lever 38 is adjusted so that the engine operates at the desired governed speed, the motion of the operating lever 35 from full load to no load increases'the spring arm from arto a1. Since the effective spring rate increases as the square of the length of this arm, the resistance applied to the upper race will have the characteristic shown by the curve CFB in Figure 5. It follows therefore that this simple and efficient combination of levers can be arranged not only to provide uniform regulation over a long range of speeds, but that because of the parabolic character of the spring resistance curve, close regulation may be obtained at' any speed without loss in stability.

As stated above, the rod 39 may be connected to an instrument board, or accelerator pedal. Thus the engine speed is controlled through the governor only. For example, in order'to idle the engine, the rod 39 is moved. to the right in Figure 1 until the speed is reduced to the desired idling speed. I

It will be noted that the axial thrust due to. the centrifugal force developed by the balls 26' and the spring tension of the spring 40 is applied l5 and not to the drive shaft l4.. The axial thrust upon the drive shaft is therefore nearly zero when a spur gear is used and is relatively small when the drive gear is spiral. This thrust is taken up by the bushing of driver 24 in one direction.

The operating lever 35 is acted on by the centrifugal means including balls 26, and by spring III. It connects directly to the throttle valve 31.

This lever 35 is therefore properly called an operating lever, or a governing lever, and both terms are applied to it herein. Lever 38 is referred to as a manual lever, since as shown it is manually adjustable, and it is also referred to, as an adjusting lever. It will be obvious that lever 33 need not be set literally by hand, i. e. manually, but can be otherwise positioned.

lncertoininstanceaitmaybeunnecessaryto the free end 56 thereof is adapted to be connected by means of a link or other suitable member with the control means for the internal combustion engine. The other arm 51 of the bell crank 53 is bifurcated and has a pair of opposed lugs, or the like, 58 adaptedto be received within a groove 59 in the member 60.

In this modification, as in that previously described, the race 52 is mounted for free rotation relative to the shaft 6|, as is also the straight race 62. The driver 63 may be substantially identical with that shown in Figure 4, and the balls 65 are of course the same.

In this modification as in that previously described, the races 52, 62, the driver 63, and the balls rotate at constant angular speed except during variations in speed. During variations in speed there is a relative angular movement.

between the races 52 and 62, and the balls 65 roll freely to their new position.

In the present embodiment the spring resistance, since it is applied directly to the race 52, is a straight linefunctlon. In order to provide stability combined with close regulation, it is therefore necessary to modify the movable race 52.

Referring to Figure 5, assume that the spring curve CFB is known to provide stability at all loads, that is, at all positions of the upper race. A tangent may now be drawn to this curve at the point C. This tangent then represents the characteristic of the spring 5| shown in Figure '7, and is indicated by the line CH in Figure 9. The derivative of the lines EB and AB, Figure 5, are then computed and the difference between them found. This difference, when added to the j derivative of the line CH, Figure 9, determines the derivative of the line JH.

Since when a curved race is used its axial movement becomes necessarily slightly greater than that of the straight cone, it becomes necessary to predetermine the amount of this movement before the chart of Figure 9 may be drawn. This new movement may be closely approximated from I A B SE t (5) where Sz=movement ofcu'rved race S1=movement of straight race a A, B, and H=force upon race at corresponding points as shown on chart From data thus established, the chart of Figure 9 may now be drawn as shown. Curve ANH is drawn so that it is tangent to AB at A, and to J H at H.

The valueof the actual angle of the cone at the outermost bal1 position corresponding to point H in Figure 9, may now be determined from the equation cot a= B I 1 regulation at 1600 R. P. M

lied to si-id .said shaft, an operating? lever where By the use of the above method, the initial angle, the final angle, and the movement, or lift, of the upper race 52 can thus be determined. A

spring means interconnecting said levers and v adapted to oppose said rotation of said shaft,

abutments carried by said levers and adapted to parabolic curve can then be selected so that it is tangent to initial and final angles of the upper race, thus establishing the locus of the center of 'the ball. The profile of the surface of the race 52 may then be determined graphically, as indicated at Figure 8. This is done by drawing a series of circles, such as 10, with a radius equal to the radius of the ball 65 and with centers located on the above established parabolic path of the ball. A curve tangent to all of the circles establishes the profile cf the upper race 52.

I found that in some cases acurved race is of great benefit even when used in connection with embodiment shown in Figure 2. Thus, referring to Figure 11, a 60 lbs,,rate spring was required in order to produce stability with a straight race, and this resulted in l regulation at 2000 R. P. M. When a curved race was substituted, it became possible to reduce the spring rate to 40 lbs. and still maintain good stability.

By reference to Figure. 12 it will be seen that the governor now regulated the engine much better and that 4% regulation was obtained at 2000 R. P. M.

The excellent was obtained by by reducing the spring arm a1. speed variation is not more than performance shown in chart 6 Here the total 30 R. P. M., or The foregoing detailed description of structure is given to enable those skilled in the ,art to practice the invention, the scope of whicllis indicated by the appended claims.

- What I'claim as my invention is:

l. A governor comprising a casing having a centrally apertured externally projecting stud, a shaft in said casing projecting from said stud, centrifugal means in said casing tending to rotate said shaft, an operating lever fixed on the projecting end of said shaft, a second lever pivoted to said stud concentrically witl'f'said shaft, spring meansinterconnecting said levers and adapted to oppose said rotation of said shaft.

2. A governor comprising a casing having a centrally apertured externally projecting stud, a shaft in said casing projecting from said stud, centrifugal means in said casing tending to rotate said shaft, an operating lever fixed on the projecting end of said shaft, a second lever pivstud concentrically with said shaft, said levers having arms projecting therefrom in adirection transverse to the axis of said'shaft, one of said arms being located substantially fur-.

ther from the axis of said shaft than said other arm, and a spring interconnecting said arms.

3. A govemcr comprising acasing having a externally projecting stud, a

centrifugal means in jecting end of said shaft, to saidstud concentrically with. said shaft,

- that its torque arm with lever increases substantially upon movement of an increase in speed, said -manual lever being adjustable and adapted to be increasing L1 (Figurel), thereconnecting said arms abut whereby said operating lever may be mechanically moved to and retained in one extreme position by said second lever.

4. In a centrifugal governor, an operating lever urged in one direction by centrifugal means, a manual lever concentric with said operating lever, and spring means interconnecting said .levers and adapted to resist movement of said operatng lever by said centrifugal means in such a way that the torque arm of said spring means with respect to said levers crease in speed.

5. In a centrifugal governor,'an operatinglever urged in one direction'by centrifugal means, a manually adjustable lever concentric with said operating lever, each of said levers having an arm projecting therefrom, said arms projecting from said levers in directions transverse to the axis of rotation of said levers, and spring means interconnecting said arms at their free ends, said spring means being connected to said levers so thatits torque arm with respect to said operating lever increases substantially upon movement of said lever in response to anincrease in speed.

6..In a centrifugal urged in one direction by centrifugal means, a manual lever concentric with said operating lever, each of said levers having an arm projecting therefrom in a direction rotation of said levers, and spring means interspring means being connected to said levers so said lever in response to set in adjusted position to vary the speed at which said governor controls.

, 7. In a centrifugal governor, an operating lever urged in one direction by centrifugal means. a manual lever concentric with said operating lever, each of said levers having an arm projecting therefrom, in a direction transverse to the axis of rotation of said levers, and spring means interconnectlng said arms at their free ends, the line of action of said spring being remote from the axis of rotation of said levers, said spring being connected to said levers so that the efl'ective torque arm of said spring crating lever increases substantially upon move- 65. ment of said operating lever inresponse to an in crease in speed.

8. In a centrifugal governor, an operating lever urged in. one direction by centrifugal means,- a

. abutting portions whereby manual lever concentric with said operating lever,

and spring means interconnecting said levers and adapted to resist movement of said operating lever by said centrifugal means, said levers having upon limiting movement of said manual lever, said operating lever ;may be moved to and retained in one extreme position by said manual lever.

9. A speed regulator comprising a casing, a drive shaft in said casing, a slotted ,driving member movable with said flat plate and a concavely h both pf'said plates being freely rotatable on saidsha'ft, .oneljof said 'a' second shaft in said casing perpendicular to said drive shaft, 9. bifurcated arm carried by said second at their free ends,- said respect 'to said operating increases upon an ingovernor, an operating lever transverse to the axis of with respect to said op-J shaft, ans in. said slots, a

formed plate abutting said balls from opposite sides,

shaft engaging said longitudinally movable plate, said second shaft projecting-from said casing, an operating lever carried by the projecting end of said shaft, a manually adjustable lever carried by said casing coaxial with said operating lever, and

a spring interconnecting said levers and adapted a manual lever mounted concentrically with said governing lever, a spring interconnecting said levers, the position of said spring at any predetermined speed being determined by determining a: from the following equations:

posing said force, comprising: a governing lever,

in which a1 and a: are the length of spring arm and L1 and L2 are lengths of spring respectively at upper and lower limits of speed range, where a: is the radial distance from the axis of the lever arms to the point of suspension of the spring to the governing lever, where L: is the length of said spring at said predetermined minimum speed-and L1 is the length of said spring at said predetermined maximum speed. V

11. A governor having a rotatable element adapted to apply a controlling force variable with the speed being governed, and regulating means opposing said force, comprising: a governing lever, a manual lever mounted concentrically with said governing lever, a spring interconnecting said levers, said spring having at a predetermined maximum speed a. length L1 and a spring arm 01, or being determined from the equation a1= /R/R5 in which R is the selected effective spring rate at said speed, and Rs is the actual rate of said selected spring, said spring being connected to said levers so that itstorque arm on said governing lever increases upon increases in speed.

12. In a governor, a casing having a centrally 'apertured externally projecting stud, a rotatable shaft in said casing projecting through said apertured stud, centrifugal means in said casing tending to rotate said shaft, an operating lever fixed on the projecting end of said shaft, an adjusting lever pivoted to said stud concentrically with said shaft, a laterally projecting arm on one of said levers, a laterally projecting arm on the other of said levers, said arms extending generally in the same direction, a spring interconnecting said arms, one of said arms being offset so that said spring is substantially perpendicular to the axis of said shaft.

13. In a governor, a casing having acentrally apertured externally projecting stud, a rotatable shaft in said casing projecting through said apertured stud, centrifugal means in said casing tending to rotate said shaft, an operating lever fixed on the projecting end of said shaft, an adlusting lever pivoted to said stud concentrically with said shaft, a laterally projecting arm on one of said levers, a laterally projecting arm on the otherof said levers, said arms extending generally in the same direction, a spring interconnecting said arms, one of said arms being offset so that said spring is substantially perpendicular to the axis of said shaft, the offset portion. of said one lever serving as an abutment whereby extreme movement of said control lever mechanically positions said operating lever in one extreme positionr 14. A governor adapted to control motor speed at any speed within a wide range, comprising a rotatable shaft, a slotted member keyed to said shaft, a pair of plates mounted on said shaft for free rotation thereon, one of said plates being axially movable on said shaft, said plates'deflning an outwardly restricted annular chamber, balls in the slots of said slotted member, means resisting relative axial movement of said plates comprising a shaft, a lever carried by said shaft engaging said axially movable plate, an operating lever rigidly carried by said shaft, a manually adjustable lever mounted for relative movement to said shaft about an axis concentric therewith, and a spring interconnecting said operating lever and said manually adjustable lever, said parts being constructed and arranged to 'employ substantially full movement of said balls to govern speed at any position of adjustment of said manual lever.

15. A governor comprising a rotatable shaft, a

slotted driving member rotatable with said shaft,

-- balls in said slots, a pair of plates mounted on said shaft, fabutting said balls at opposite sides thereof and defining between said plates an outwardly restricted chamber, means urging said plates toward said balls, said plates being rotatable on said shaft, one of said plates being axially movable on said shaft, and an abutment carried by said shaft limiting axial movement of said last plate on said shaft.

16. In a centrifugal governor, a governing lever urged in one direction by centrifugal means, a manual lever adjustable concentric with the governing lever and extending generally in the same direction, spring means interconnecting said levers having its line of action generally parallel to said levers but offset therefrom so as to have a substantial torque arm when said levers are strictly parallel.

17. In a centrifugal governor, a governing lever urged in one direction by centrifugal means, a manual lever adjustable concentric with the governing lever and extending generally in the same direction, spring means interconnecting said levers having its line of action generally parallel to said levers but offset therefromso as to have a substantial torque arm when said levers are strictly parallel, said spring being located such that its torque arm with respect to said governing lever increases upon movement of said governing lever in response to a speed increase.-

18. In a centrifugal governor, centrifugal means, an operating lever urged in one direction by said centrifugal'means, an adjusting lever pivoted concentrically with said operating lever, a governor spring interconnecting said levers and adapted to resist movement of said operating lever by said centrifugal means, the connections of opposite ends of said spring to said levers being at widely different radial distances from the common pivot axis of said levers. I

19. In a centrifugal governor, centrifugal means, an operating lever urged in one direction by said centrifugal means, an adjusting lever pivoted concentrically with said operating lever, a governor spring interconnecting said levers and adapted to resist movement of said operating lever by said centrifugal means, the connections of opposite ends of said spring to said levers being at widely different radial distances from the common pivot axis of said levers, the connection to said adjusting lever being furthest from said pivot 20. A'governor comprising a casing having a centrally apertured externally projecting stud, a

shaft in said casing, projecting from said stud.- v centrifugal ineans in said casing tending to rotate said shaft, an operating lever fixedon the projecting end of said shaft, a second lever pivoted to said stud concentrically with said shalt,v

tain saidsecond lever on said stud.

' HERMAN G ADLER.

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