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Publication numberUS3263511 A
Publication typeGrant
Publication dateAug 2, 1966
Filing dateDec 2, 1963
Priority dateDec 2, 1963
Publication numberUS 3263511 A, US 3263511A, US-A-3263511, US3263511 A, US3263511A
InventorsWilliam Wellstein
Original AssigneeKerco Inc
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Variable speed linkage
US 3263511 A
Abstract  available in
Images(1)
Previous page
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Claims  available in
Description  (OCR text may contain errors)

Aug- 2, 1966 w. WELLSTEIN 3,263,511

VARIABLE SPEED vI INKAGE Filed Deo. 2, 1963 l L l-@ 57 1NVENTOR WILLIAM wELLsTEl United States Patent O "ice 3,263,511 VARIABLE SPEED LINKAGE William Wellstein, Fostoria, Ohio, assigner, by mesne assignments, to Kerco, Inc., a. corporation of Delaware Filed Dec. 2, 1963, Ser. No. 327,358 Claims. (Cl. 74--53) The present invention relates to improvements in a linkage for the operati-0n of various types of equipment at variable speeds froma single power source. As an example, the improved linkage may be employed to great advantage in controlling the travel of a tool or work carrying slide in reversing strokes under actuation by a single operating cam. More particularly, the control function is performed through the agency of novel dual type bell crank and lever linkage |provisions enabling a multiplication of lever `arm ratios through such linkage which can produce a vast and widely variable modification of the speed or power of an actuating stroke, applied by the linkage to a tool slide or the like, in relation to the stroke applied to the linkage by a cam or like pri mary actuator.

In general, it is an object of the invention to provide an improved, variable speed tool slide or equivalent actuating linkage driven from a single master power member, which is capable of providing a wide range of ratios of power cam throw, or stroke or throw of an equivalent operator, to slide stroke distance.

Another object is to provide an improved slide or equivalent unit operated by means of such improved linkage. The unit operated by t-he linkage might, for example, be a slide mounting a grinding, drilling or like head for variable speed movements, such as approach, working and retract travel componen-ts, relative to the work, or mou-nting a workpiece for variable movement in relation to a tool, or for a more general type of travel for whatever particular purpose Vmay be involved.

More specifically, the improved linkage comprises Ia primary actuator or medially pivoted bell crank and a coacting secondary actuator lever or arm member. In this arrangement, the bell crank, as directly engaged and operated at one of its arms by a master cam, affords a given ratio of the radial cam throw of that arm to the length of stroke of the slide, as the latter is directly engaged by the other arm of the bell crank. This may be employed, for example, `to afford a relatively fast initial advance and final subsequent retraction of a tool on the slide toward and away from a workpiece prior to and following Ian actual working phase.

The linkage combines with a bell crank -having this effect a medially pivoted secondary lever or arm member, one end of which :is engaged by an element of the bell crank on the side of the latters pivot opposite its slide engaging end. Thus the distance of this bell crank element from the bell crank pivot represents a further moment advantage anm of small length through which the medially pivoted lever or arm member is bell-crank actuated.

The product of the combination of crank and lever ratios represents la very high cam throw-slide str-oke ratio, indeed, so that with the opposite end of the medially pivoted lever directly engaged with the tool slide, like the bell crank but independently of the latter, there results a slow feed of the tool in the actual working phase of the equipment. In accordance with the invention, the last named product ratio is capable vof a wide range of change by an apt `selection of :bell crank and lever components and an adjustment of their points of engagement with one another.

It is of course to be kept in mind that the improved linkage is well adapted to applications other than tool 3,263,51 l Patented August 2, 1966 slide control; however, that application typically illustrates the advantages of the linkage, and will therefore be alone referred to in the following description.

Thus, with the bell crank and medially pivoted arm journaled on independent axes determining the length ratios of their respective arms, and with these members physically acting independently upon the tool slide, but co-ordinately in at least one of its travel phases, the slide may have a fast initial inward movement from -a fully retracted position to the point of engagement of the tool with the work, followed by retarded ensuing movement toward and into the workpiece, then by relatively slow and rapid retractions of vthe slide after the working phase.

In further accordance with the invention, there is provided an adjustability as to the point of engagement of the bell crank with the medially pivoted, secondary lever or arm, thus permitting a `full range of intermediate ultimate ratios of cam throw to slide stroke. Let it be assumed, as -herein shown and described, that the bell crank engages the longer of two arm portions of the secondary lever at a relatively short distance from the bell crank pivot, and only a small fraction of the length of the cam-engaging bell crank anm. Then, for example, appropriate selection of the length of bell crank arms and pivoted arm portions will enable a full slide stroke of 0.003 inch when the ultimate ratio is 1:10, a stroke of 0.015 inch at 1:20 ratio, etc.; and an appropriate small adjustment at the point of operating engagement of the bell crank and lever arm will have the effect of selecting an intermediate ratio, such as 1:15.75 or thereabouts, A greater adjustment of the distance from the engagement point to the bell crank axis will result in a greater modification of the ratio, for example, halving or doubling it.

Thus the invention features simple linkage provisions enabling a wide range of control of the stroke of a movable tool slide or other variable stroke member, which were, for instance, -heretofore only -attained through resort to the use of multiple interchangeable cams or like time-consuming practice, such as is rendered unnecessary by the improved single cam-controlled linkage of the invention.

A general object of the invention is to provide a variable speed operating linkage fora slide or the like, characterized in that the linkage imparts successively to the slide an initial advance stroke in one direction under the sole control of the bell crank of the linkage, a short inward working component under the combined control 0f the bell crank and lever at a highly increased stroke speed reduction ratio, followed by a retract component in the opposite direction at increased speed, again under the control of the bell crank of the linkage; and in which the transisitions as between these speed components are accomplished smoothly and without 4any degree of jarring. The invention also contemplates adjustable provisions whereby the point of .take-over may be determined as desired for slide strokes of different speed characteristics.

The foregoing as well as other objects will become more apparent as this description proceeds, especially when considered in connection with the accompanying drawings illustrating the invention, wherein:

FIG. 1 is a fragmentary perspective and quite schematic view of a portion of typical tool slide equipment in which the linkage of the invention may be incorporated, other components of this equipment having been omitted as not germane to the invention;

FIG. 2 is a fragmentary view in vertical section through the slide and associated linkage of the machine, showing the dual bell crank and arm of the linkage as operated by a master cam;

FIG. 3 is an end view of components of the linkage alone, as viewed from the left of FIG. 2;

FIG. 4 is a fragmentary view, partially broken away and in horizontal section on line 4-4 of FIG. 3; and

FIG. 5 is a highly schematic diagram illustrating the nature of the advance, working and retract strokes imparted to the slide by the improved linkage.

Referring to FIG. 1, the generally known type of machine shown therein to which the improved linkage is applied may be considered to comprise an appropriate rigid base 11 having a horizontal top 12 upon which a mounting slide 13 is guided for longitudinal reversing movement. Each slide is adapted to have mounted thereon an appropriate tool head (not shown). F-urther reference to the nature of the slide 13 will be made. The improved linkage of the invention is generally designated by the reference numeral 30.

Referring now particularly to FIG. 2, the machine top 12 fxedly mounts a guide or Way member 32 for the slide 13, by which the latter is stably guided in its strokes to the right and left as viewed in FIG. 2. A small block 33 is xed to the bottom of slide 13 to depend within an elongated recess 34 of guide member 32; and an elongated adjusting stud or stem 35 is threaded through block 33, extending outwardly through guide member 32 and a depending end cover plate 36 on the slide. Stem 35 has a knurled handpiece 37 secured thereon outwardly of element 36, and the handpiece may be appropriately calibrated as shown in FIG. 1, to visually indicate the position of threaded adjustment of the stud or stern 35 longitudinally relative to the tool slide 13. The stem 35 is adapted to be actuated by a part of the linkage 30, as will be described.

A tension coil spring 38 has one end secured to the end plate element 36 of slide 13 and the other end connected to frame 11, thus urging .the slide to the right, as viewed in FIG. 2, for its in-stroke.

The block 33 also receives another, set screw type adjusting stem 39 shown along with stem or stud 35 in dot-dash line in FIG. 3. The stem 39 serves as an actuator for another component of linkage 30, as will also appear later.

Now referring to FIGS. 2, 3 and 4, a bell crank member of the linkage 30 is generally designated 40, comprising an upright slide operating arm 41 and an inclined though generally horizontal operated aum 42. The arm 42 is provided at its end with a follower roller 43 engageable with a driven faster cam 44, against which it is urged by an appropriately anchored tension spring 42'; while the arm 41 is provided with -a side boss 45 apertured and receiving a bushing 46, at which the bell crank is pivoted on a horizontal pin 47 fixedly carried by a bracket 48 on the outer side of the machine frame 11. It is seen by reference to FIG. 2 that the bell crank 40 is thus pivoted on the frame 11 at a point slightly above the junction of bell crank arms 41 .and 42; and one of the moment arms of the lbell crank is established by this positional relationship, as will be described.

At its top end, the bell crank arm 41 is provided with an anti-friction roller 50 ladapted for engagement with the adjustable set screw 39 on slide block 33. Arm 41 also carries, adjacent the pivot bracket 48, a laterally projecting rectangular pad 52 which is provided with an elongated Iupright slot 53 for a purpose to be described. The arm 42 of bell crank 40 extends inwardly through an opening 54 of frame 11 for engagement with master cam 44.

While the cam 44 is shown as the primary power member for the input of energy to linkage 30, it will be understood that the invention contemplates as an equivalent any other suitable, identically repeating or cycling power unit which is capable of periodically imparting a predetermined throw to the bell crank arm 42, or equivalent member operated by such power unit, hence is capable of automatically repeating the variable speed operating strokes contemplated by the invention, `for a given setting of linkage 30.

The second component of the linkage 30 is a secondary actuator, arm member or rocker lever, generally designated 56, which is medially provided with a boss 56 at which it is pivoted by a pin 57 in a bracket 58 secured to and projecting from the exterior of frame 11, with a bushing 59 in the arm boss 56 receiving pin 57. A slide operating portion 60 of arm 56 above its pivot 57 is provided with an anti-friction roller 61, which is in side-byside -relation to the roller 50 atop the bell crank arm 41, as shown in FIGS. 3 and 4. The roller 61 is engageable in operation by the end of adjusting stud or stem 35.

The lower, operated portion `63 of the medially pivoted arm 56 is provided with a lateral extension piece 64; and in accordance with the invention, this extension 64 is engageable lby an actuator stud 65 which extends through the slot 53 of bell crank pad 52, being provided with lock nuts 66, l67 on opposite sides of the pad. This enables the stud 65 to be adjusted as desired up and down in the slot 53, then clamped to constitute a lever actuating element of the bell crank 40, the primary actuator of linkage 30. The position of stud 65 determines its distance from the pivotal axis of bell crank 40 at pin 47, which distance represents the moment arm (hereinafter referred to) about which the bell crank acts on the lever 56 at the latters extension 64.

Thus, reference being had to FIG. 3 of the drawings, it is seen that the distance x of actuator stud 65 from the bell crank pivot at -pin 47 represents a very short moment or lever arm of the bell crank 40, as compared with its long arm distance y from pivot 47 to follower 43. The ratio xzy of effective lengths may be, for example, 1:10 in a typical installation, and is a multiplier by which the ultimate combined, motion dropping ratio of linkage 30 is determined. The selection of a bell crank having, as between its pivot and its cam and slide ends, a different lever arm or moment ratio will of course vary the combined ratio, enabling it possibly, by choice of bell cranks, to provide an extremely wide range of slide stroke lengths.

The medially pivoted, secondary lever 56 of linkage 30 has a moment arm a from its pivot at 57 to its anti-friction roller 61 and a moment arm b from its pivot to its point of effective engagement by primary bell crank 40 at the actuator stud member 65. For example, the ratio a/b may be about 1/2 in a typical linkage, so if x/y equals about 1/10, the overall motion conversion ratio of the linkage 30 is about 1:20, i.e., a controlled working motion of the slide 13 where its adjustable stud 35 engages the anti-friction roller 60 of lever 56 amounting to one unit of length for 20 units of radial throw by master cam 44, the basic driver for the linkage. This affords a slow in and out feed of slide 13 in a working engagement of its tool (not shown) with a workpiece.

On the other hand, there is available a rapid speed advance and retract of slide 13, as effected only by and at the engagement of set screw stern 39 with the bell crank anti-friction roller 50, in a much greater ratio of, say, approximately 1:2, for rapid in and out initial and final strokes of a slide cycle, amounting to one length unit of slide travel to only about two radial throw units of cam 44.

As an instance of the adjustability of the linkage at the actuator stud 65, let it be assumed that the latter is set on pad 52 at a distance x of 1.3 inches from the bell crank pivot axis at pin 47, that the effective bell crank arm length from pivot to follower 43 is 13 inches, and that the lever arm lengths a and b are 2.6 inches and 5.2 inches respectively. Then, stated inversely, the combined ratio of linkage 30 is However, if actuator stud 65 is adjusted only one inch down on pad 52, the arm x becomes 2.3", the arm b becomes 6.2", and the combined ratio equals or 13.47z1. Thus in the first case there is, in a given range broadly determined by bell crank and lever design, a twenty-fold drop in slide travel, and in the other case a drop of approximately thirteen and a 'half to one.

A wide selection of slide operating ratios is available, along with a fine control in any general range, as determined by the adjustment of bell crank actuator stud 65. For instance, the adjustment may result in the multiplying or dividing of the moment arm length x to produce different orders of ultimate stroke ratio; and an intermediate fine adjustment may be had in any general order or range of adjustment. It is contemplated that the pad 52 of the bell crank may be calibrated adjacent the stud slot to assist in making the desired setting (FIG. 3). The invention contemplates a selection and adjustment of linkage 30, in regard to moment arm lengths of bell crank and/ or lever, such as will permit combined linkage ratios ranging from :1 (representing an overall slide stroke of, say, 0.003 inch) to :1 (or a 0.00375 inch stroke).

In operation, assuming that the tool slide 13 is in an extreme withdrawn initial position to the left in FIG. 2,

with the follower 43 of -bell crank 40 riding a high of master cam 44, the set screw actuator 39 on the slides block 33 will then be in engagement with the anti-friction roller of bell crank arm 41. As follower 43 rides onto a low (not shown) of cam 44, the bell crank 40 swings clockwise about its pivot pin 47, enabling bell crank roller 50 to fall inwardly, or to the right in FIG. 2; and the medially pivoted secondary lever 56 follows in the same direction. Thus a rapid instroke of slide 13 and its tool into initial engagement of the latter with a workpiece takes place under the urging of slide spring 38.

Upon the wheels assuming such workpiece engagement, with the extension 64 of lever arm 63 engaged by bell crank actuator stud 65, the motion of slide 13 cornes under the control of the combined linkage 30. The slide continues to be spring-urged inwardly for the working phase of its stroke, as variably controlled by the contour of master cam 44, but at one of the combined higher ratios discussed above, i.e., at a greatly diminished rate of travel.

As the slide completes this stroke phase, the follower 43 will be actuated by a cam high (not shown) for an outward throw, rocking bell crank 40 counterclockwise about its pivot pin 47. The resultant initial retraction of the slide and wheel from the work will first be at the slower rate, until the bell crank roller 50 moves to the rear away from lever roller 61, whereupon the slide 13 will be retracted at the bell cranks 2:1 throw ratio until slide 13 is fully withdrawn outwardly, the secondary lever 56 following at the slower ratio rate.

Schematic FIG. 5 conveniently illustrates the characteristics of the variable speed stroke imparted to slide 13 by the linkage. The bell crank 40 will, at the operating engagement of its roller 50 with the adjustment set screw 39, describe a stroke arc A extending equidistantly on opposite sides of an upright center line through the roller, the pivot axis at 57 for secondary lever 56 and the point of engagement of actuator stud with the lever extension 64. However, only the component of the stroke arm A which lies to the left of the center line is directly and alone effective on slide 13, producing its rapid initial inward component and its rapid final outward component.

As the bell crank arrives at the stroke center line, having effected a coarse slide control movement to approach a tool or the like thereon to close proximity to a workpiece, for example, the fine, high ratio control comes into effect, as exerted by the engagement of the roller 61 on lever 56 with the adjustment stud or stem 35. The Vduration of this is only to the slight extent of the stroke arc A which lies to the right of the center arm, both on the infeed and outfeed directions of slide movement. In this phase, a tool will -be in working engagement with the work.

When the lever 56 is returned to the upright center line, it loses control effect on the slide 13, which is taken up by the bell crank for the remainder of the retract stroke, on the left of the center line. All of these transitions are effected smoothly and without shock or jarring; and the point of cross-over from one phase to another may be varied by an appropriate adjustment of the adjustment stud 35.

It is seen that the invention affords a highly versatile slide control mechanism. A single, dual-type bell crank and lever linkage, which is highly compact, simple and inexpensive, and readily adaptable to various sorts of existing machinery, permits changeovers vas to slide stroke ratio in a moments time and without any change whatsoever in the equipment other than in making the adjustment as to bell crank moment arm distance. Such changeovers have heretofore been accomplished only by time-consuming modifications of the equipment. In so far as the matter of stroke accuracy is concerned, the present linkage, as actuated at all times from a single master power input member or cam, is of course at least the equivalent of any heretofore relied on procedure.

As indicated above, the master power source may be a driven cam or vany other equivalent agency capable of producing the bell crank throw. Furthermore, while the illustrated embodiment of the invention has its operating slide 13 spring-urged in one direction, and actuated in the other direction by the linkage 30, `it is to be understood that other operating means for the slide, acting in conjunction with the linkage, such as fluid pressure or mechanical operating means, are contemplated.

`What I claim as my invention is:

1. In apparatus of the type described, a support, a slide unit mounted for reversing sliding movement on said support, a linkage to operate said slide unit at varying speeds in different phases of said movement, said linkage comprising a primary actuator operatively engaging said unit, said actuator having a pivotal axis on said support and having a first portion to engage and operate said unit at a given speed in one of said phases, and a second operated portion to `be operated, a secondary actuator operatively engaging said slide unit and having a -pivotal axis on said support in parallel but transversely spaced relation to the pivotal axis of said primary actuator, said secondary actuator also having a portion to engage and operate said unit and a further portion providing an operating connection for actuation by said primary actuator, which further portion is transversely spaced from the pivotal axis of the primary actuator, the moment arm distance from said primary actuator axis to said further portion being substantially dilferent from the distance from said primary actuator axis to its said second operated portion, said actuators thus coacting in yoperating the slide unit at a different speed in another of said phases, and an automatically cycling drive device engaging said primary actuator at said second operated portion of the latter to provide repeated variable speed movement of the slide unit over the direction of the two phases.

2. A linkage to operate a unit at varying speed in different phases of its movement, said linkage comprising a primary actuator operatively engaging said unit, said actuator having a pivotal axis and having a first portion to engage ,and operate said unit at a given speed in one of said phases, and a second operated portion adapted to be operated by other means, a secondary actuator operatively engaging said unit and having a pivotal axis in parallel but transversely spaced relation to the pivotal axis of said primary actuator, said `secondary actuator having a portion to engage and operate said unit and a further portion lproviding an operating connection for actuation by said primary actuator, which further portion is transversely spaced from the pivotal axis of the primary actuator, the moment arm distance from said primary actuator axis to said further portion being substantially different from, and in a predetermined and fixed ratio to, the moment arm distance from said primary actuator axis to its said second operated portion, said actuators thus coacting in operating the unit at a different speed in another of said phases, and means to adjust the ratio of the lengths of said moment arm distances to one another.

3. In apparatus of the type described, a support, a slide unit mounted for reversing sliding movement on said support, and a linkage to operate said slide unit at varying speeds in different phases of said movement, said linkage comprising a primary actuator operatively engaging said unit, said actuator having a pivotal axis on said support and having a first portion to engage and operate said unit at a given speed in one of said phases, and a second operated portion adapted to be operated by other means, a secondary actuator operatively engaging said slide unit and having a pivotal axis on said support in parallel but transversely spaced relation to the pivotal axis of said primary actuator, said secondary actuator also having a portion to engage and operate said unit and a further portion providing an operating connection for actuation by said primary actuator, which further portion is transversely spaced from the pivotal axis of the primary actuator, the moment arm distance from said primary actuator axis to said further portion being substantially different from the distance from said primary actuator axis to its said second operated portion, said secondary actuator providing moment arms from the axis thereof which are of different lengths, respectively, to said further portion and to said first named unit operating portion of the secondary actuator, said actuator thus coacting in operating the slide unit at a different speed in another of said phases, said first actuator being a bell crank medially pivoted between said operating and operated portions thereof, said secondary actuator being a medially pivoted lever.

4. Apparatus in accordance with claim 3, in which said operating connection between said actuators is located on the same side of both of said pivotal axes and closer to the bell crank axis than to the lever axis, and means to adjust the moment arm distance from the axis of said lever to said further portion thereof.

5. A linkage to operate a unit as varying speeds in different phases of its movement, said linkage comprising a primary actuator operatively engaging said unit, said actuator having a pivotal axis and having a first portion to engage and operate said unit at a given speed in one of said phases, and a second operated portion adapted to be operated by other means, a secondary actuator operatively engaging said unit and having a pivotal axis in parallel but transversely spaced relation to the pivotal axis of said primary actuator, said secondary actuator having a portion to engage and operate said unit and a further portion providing an operating connection for actuation by said primary actuator, which further portion is transversely spaced from the pivotal axis of the primary actuator, the moment arm distance from said primary actuator axis to said further portion being substantially, different from, and in a predetermined and fixed ratio to, the distance from said primary actuator axis to its said second operated portion, said secondary actuator providing moment arms from the axis thereof which are of different lengths, respectively, to said further portion and to said first named unit operating portion of the secondary actuator, said actuators thus coacting in operating the unit at a different speed in another of said phases, said first actuator being a bell crank medially pivoted between said operating and -operated portions thereof, said secondary actuator being a medially pivoted lever.

6. A linkage in accordance with claim S, in which the distance from said operated portion to the bell crank axis greatly exceeds the moment arm distance from said bell crank axis to said operating connection, the distance from the medial axis of said pivoted lever to said further portion thereof substantially exceeding the distance from said medial axis to said first named unit operating portion of said lever.

7. A linkage in accordance with claim 5, and further comprising means to adjust said moment arm distance from the axis of said lever to said further portion thereof.

8. A linkage in accordance with claim 6, and further comprising means to adjust said moment arm distance from the axis of said lever to said further portion thereof.

9. A linkage in accordance with claim 8, in which said operating connection between said actuators is located on the same side of both of said pivotal axes.

10. In apparatus of the type described, a support, a slide unit mounted for reversing sliding movement on said support, a linkage to operate said slide unit at varying speeds in different phases of said movement, said linkage comprising a primary actuator operatively engaging said unit, said actuator having a pivotal axis on said support and having a first portion to engage and operate said unit at a given speed in one of said phases, and a second operated portion to be operated, a secondary actuator operatively engaging said slide unit and having a pivotal axis on said support in parallel but transversely spaced relation to the pivotal axis of said primary actuator, said secondary actuator also having a portion to engage and operate said unit and a further portion providing an operating connection for actuation by said primary actuator, which further portion is transversely spaced from the pivotal axis of the primary actuator, the moment arm distance from said primary actuator axis to said further portion being substantially different from the distance from said primary actuator axis to its said second operated portion, said secondary actuator providing moment arms from the axis thereof which are of different lengths, respectively, to said further portion and to said rst named unit operating portion of the secondary actuator, said actuators thus coacting in operating the slide unit at a different speed in another of said phases, and an automatically cycling drive device engaging said primary actuator at said second operated portion of the latter to provide repeated variable speed movement of the slide unit over the duration of the two phases.

11. In apparatus of the type described, a support, a slide mounted for reversing movement on said support, and a linkage to operate said slide at widely varying speeds in different phases of said movement, said linkage comprising a primary actuator pivoted on an axis on said support and having operated and operating arms respectively engaging and operated by a driving member and engaging and directly operating said slide in one phase of its movement, a secondary actuator having a pivot axis on said support in parallel but transversely spaced relation to the pivot axis of said primary actuator on the support, said secondary actuator having direct operating engagement with said slide to operate the latter in a different phase of its movement and being provided with means for an operating connection for actuation by said primary actuator at a point transversely spaced from the pivot axis of the latter, the moment arm distance from said primary actuator pivot axis to said operating connection being substantially different from that from said actuator axis to the point of engagement of said operated arm of the primary actuator with said driving member, said secondary actuator providing moment arms which are of different lengths, respectively, to said operating connection and to the point of operating engagement of said secondary actuator with said slide, the slide being thereby operable by the linkage in said dif-ferent phase of a stroke of said slide at a speed determined by the product of the respective moment arm ratios of said actuators.

12. In apparatus of the type described, a support, a slide mounted for reversing movement on said support, and a linkage to operate said slide at widely varying speeds in different phases of said movement, said linkage comprising a primary actuator pivoted on an axis on said support and having operated and operating arms respectively engaging and operated by a driving member and engaging and directly operating said slide in one phase of its movement, a secondary actuator having a pivot axis on said support in parallel but transversely spaced relation to the pivot axis of said primary actuator on the support, said secondary actuator having direct operating engagement with said slide to operate the latter in a different phase of its movement and being provided with means for an operating connection for actuation by said primary .actuator at a point transversely spaced from the pivot axis of the latter, the moment arm distance from said primary actuator pivot axis to said operating connection being substantially different from that from said actuator axis to the point of engagement of said operated arm of the primary actuator With said driving member, said secondary actuator providing moment arms Which are of different lengths, respectively, to said operating connection and to the point of operating engagement of said secondary actuator with said slide, the slide being thereby operable by the linkage in said dilerent phase of a stroke of said slide at a speed determined by the product of the respective moment arm ratios of said actuators, and means to adjust said operating connection toward and away from said pivot axis of said primary actuator.

13. In apparatus of the type described, a support, a slide mounted for reversing movement on said support, and a linkage to operate said slide at Widely varying speeds in different phases of said movement, said linkage comprising a bell crank medially pivoted on an axis on said support and having operated and operating arms respectviely engaging and operated by a driving member and engaging and directly operating said slide in one phase of its movement, the length of the operated arm being greater in the degree of a substantial multiple of that of the operating arm, a lever having a pivot axis intermediate its length on said support in parallel but transversely `spaced relation to the pivot axis of said bell crank on the support, said lever having direct operating engagement at one end with said slide to operate the latter in a different phase of its movement and being provided adjacent its other end With an operating connection for actuation by said bell crank at a point transversely spaced from the pivot axis of the latter, said other end of said lever being at a side of said bell crank axis remote from the lever axis, the moment arm distance from said bell crank axis to said operating connection being substantially less than that from said bell crank axis to the point of engagement of said operated arm of the bell crank to said driving member, said lever providing moment arms on opposite sidesof its pivot axis which are of greater and lesser lengths, respectively, to said operating connection and to the point of lever operating engagement with said slide, the slide being thereby operable by the linkage in said dierent phase of a stroke of said slide at a speed determined by the product of the respective moment arm ratios of `said bell crank and lever.

14. In apparatus of the type described, a support, a slide mounted for reversing movement on said support, and a linkage to operate said slide at Widely varying speeds in different phases of said movement, said linkage comprising a bell crank medially pivoted on an axis on said support and having operated and operating arms respectively engaging and operated by a driving member and engaging and directly operating said slide in one phase of its movement, the length of the operated arm being greater in the degree of a substantial multiple of that of the operating arm, a lever having a pivot axis intermediate its length on said support in paralllel but transversely spaced relation to the pivot axis of said bell crank on the support, said lever having direct operating engagement at one end with said slide to operate the latter in a different phase of its movement and being provided adjacent its other end with an operating connection for actuation by said bell crank at a point transversely spaced from the pivot axis of the latter, said other end of said lever being at a side of said bell crank axis remote from the lever axis, the moment arm distance from said bell crank axis to said operating connection being substantially less than that from said bell crank axis to the point of engagement of said operated arm of the bell crank to said driving member, said lever providing moment arms on opposite sides of its pivot axis which are of greater and lesser lengths, respectively, to said operating connection and to the point of lever operating engagement With said slide, the slide being thereby operable by the linkage in said dilerent phase of a stroke of said slide at a speed determined by the product of the respective moment arm ratios of said bell crank and lever, and means to adjust said operating connection toward and away from the bell crank axis.

15. A linkage to operate a unit at varying speeds in different phases of its movement, said linkage comprising a primary actuator operatively engaging said unit, said actuator having a pivotal axis and having a lirst portion to engage and operate said unit at a given speed in one of said phases, and a second operated portion adapted to be operated by other means, a secondary actuator operatively engaging said unit and having a pivotal axis in parallel but transversely spaced relation to the pivotal axis of said primary actuator, said secondary actuator having a portion to engage and operate said unit and a further portion providing an operating connection for actuation by said primary actuator, which further portion is transversely spaced from the pivotal axis of the primary actuator, the moment arm distance from said primary actuator axis to said further portion being substantially different from, and in a predetermined and fixed ratio to, the moment arm distance from said primary actuator axis to its said second operated portion, said secondary actuator providing moment arms from the axis thereof which are of different lengths, respectively, to said further portion and to said first named, unit operating portion of the secondary actuator, said actuators thus coacting in operating the unit at a different speed in another of said phases, and means to adjust the ratio of the lengths of said moment arm distances to one another.

References Cited by the Examiner UNITED STATES PATENTS 1,117,661 11/1914 Gourlay 74-101 1,853,495 4/ 1932 Bertrand 74--518 1,934,456 11/1933 Taylor 74-516 2,005,019 6/1935 Bertrand 74-518 2,43 6,897 3/1948 Nutt 74-5l6 2,690,321 9/1954 Luna et al 74-516 X 2,809,725 l0/ 1957 Ayers 74-516 X 2,909,936 10/1959 Huthsing et al 74-102 MILTON KAUFMAN, Primary Examiner.

BROUGl-ITON G. DURHAM, D. H. THIEL,

Assistant Examiners.

UNITED STATES PATENT OFFICE CERTIFICATE OF CQRRECTION Patent No. 3 263 ,Sll August Z 1966 William Wellstein It is hereby certified that error appears in the above numbered patent requiring Correction and that the said Letters Patent should read as corrected below.

In the heading to the printed specification, lines 3 and 4, for "assignor, bly mesne assignments, to Kerco, Inc. a Corporation df Delaware" read assigner, by mesne assignment to Kerr Manufacturing Company) a Corporation of Delaware Signed and sealed this lst day of August 1967.

(SEAL) Attest:

Edward M. Fletcher, J r.

EDWARD J. BRENNER Attesting Officer Commissioner of Patents

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Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US3888339 *Mar 1, 1974Jun 10, 1975Triumph Werke Nuernberg AgImpression control mechanism for a typewriter or similar machine
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US8042403 *Oct 7, 2008Oct 25, 2011Raytheon CompanyApparatus to control a linearly decreasing force
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Classifications
U.S. Classification74/53, 74/102, 74/516, 74/101
International ClassificationF16H25/10, F16H25/00
Cooperative ClassificationF16H25/10
European ClassificationF16H25/10