HELICAL TOOTHED CONTINUOUS SPEED CHANGE GEAR

Abstract: The continuous speed changer (100) which is the subject of this invention may be employed in all applications which demand a mechanical transmission requiring more thant one ratio between the number of revolutions of the conducting organ and the conducted organ (automobiles, motor-cycles, industrial equipment, machine tools, bikes, etc.). It is a simple, economic changer of robust construction. It essentially consists of a main shaft (400) with motor pinion, a satellite cog (441) capable of oscillating and of lateral movement while maintaining gear contact with the pinion, of a secondary shaft (500) with a cone of stepped cogs (513-519) for the various ratios. Its peculiarity rests in the capacity of the satellite cog (441) to pass to another of the wheels of the cone, to change ratio, with continuity as in a classic continuous changer. It has no limit of transmittable power, high yield in each ratio at all revolution regimes, it is by nature semi-automatic and can be automatised.

Description: ft, SOT? TFT I ON Helical toothed continuous speed change gear T. πhnlcnl FlRld The general architectural strtΛturp of the continuous speed changer consists or a Dinion which engages an idling toothed satellite cog, mounted on an arm capable of oscillating and or lateral movement while maintaining engagement with the pinion; the oscillations are centred on the rotation axis of the pinion and movements are parallel to the same axis. This satellite cog, thanks to its freedom of movement, can engage any one of the toothed cogs of a cone of dove tailed cogs on a short whose rotation axis is parallel to that or the pinion. The lenghts of the cone and that of the pinion, ta¬ ken parallel to their rotation axes, are eqaul. Thus there ore as many rotation ratios between the pinion shaft and the cogged cone as there are cogs on the cone. The originality or the invention rests in the -manner in which the idling satellite cog passes from one wheel to another changing ra¬ tio. This occurs .thanks to : toothed cogs with variable primitive radius interposed between those with constant primitive radius, destined to errect the working ratios of the changer, in such a manner as to joint the toothing with differing values ,or the primitive radius; - a command and guide mechanism for the idling satellite COR . Thus the passage is effected without disconnection; the satellite cog, in _conditions of cotinuous engagement, leaves the working ratio wheel with constant radius and moves late ¬ rally to engage the variable radius cog, in the sector in which the teeth are common. Having completed its jointing route,it effects a further lateral movement to leave the la_t ter and to joint, again in a sector where the teeth are com ¬ mon, on the successive sector of the working ratio cog at constant radius. In the current state of the art, it often occurs that motors are- incapable of erogating the power required- -by the operati ve machine at the various rotation speeds,.at which this must operate.There is therefore a requirement for more than one ro tation ratio between the motor source and the user; this is satisfied by various mechanisms, which may be grouped by functional principle,into the following fundamental classifi cation : - Continuous speed changers. mechanical type with clutch; variation of the transmis sion ratio may be manually controlled, semiautomatic or automatic. Principal advantages:- may have an -infinite number of intermediate ratios included between the extremes of construction; the variation between one ratio and another is continuos, with the possibility of limiting the peaks of acceleration of the masses in movement. Main disadvantages :- In construction terms, not the most simple, it is subject to strict limitations in the 5 transmittable torque, the yield decreases as the trans¬ mitted torque increases. Hydraulic type (torque converter); the variation of the transmission ratio is .automatic. Principal advantages :- permits an ideal coupling! bet- '° ween motor and operating machine; the possible ratios are infinite and mass accelerations gradual. Main disadvantages :- yield too low when the difference in the value of the rotation speed between the motor and the operating machine is too great. 15 Discontinuous speed changers. Mechanical type with ordinary toothed gears in fixed ratios; the variation of the transmission ratio may be manually controlled, semiautomatic or automatic. Principal advantages :- Of simple construction, any 0 power may be transmitted, has high yield at any ratio at all rotation speeds. Main disadvantages :- There is a defined number of ra tios, the operation of ratio change is complex requiring the disconnection of the transmission between the motor c and the changer and the synchronisation of the speeds __. k - of rotation of the elements to be coupled. Mechanical type with epicyclic toothed gears in fixed ratios; the variation of the transmission ratio may be manually controlled, semiautomatic or automatic. Principal advantages :- Occupies limited space,any po¬ wer may be transmitted, has high yield at any ratio at all rotation speeds. Main disadvantages :- Constructively complex if practi cal use is required, expensive, requires clutches and brakes generally controlled by a hydraulic plant to change ratio. Mixed speed changers (generally consisting of a combination of a torque converter or oleodynamic join -with a mechanical changer with epicyclic gears); the variation of the trans- mission ratio is generally controlled serai- or completely automatically. Principal advantages :- This type of function nears that of continuous changers with clutches without limitations in the transmittable torque. Main disadvantages :- Constructively complex, expensive, lower yield than mechanical type changers with ordinary or epicyclic gears. Disclosure of Invention In theory the mechanism, among those listed, which best re¬ solves the problems for which it was designed, is the con=- - 5 - tinuous speed changer, whether mechanical or hydraulic. In •practice however, as seen above, both types are subject to inconvenience which Limits their industrial usage. The present invention is designed to provide a continuous speed changer, of mechanical type, which is not subject to the limitations listed for that with a clutch nor the hydrau lie type. Its performance is mixed, not matching precisely that of any of the continuous or discontinuous changers existing today. The principal performance parameters are as 1Q follows: - The ratio is changed without disconnection of motoritrans mission, without interruption of the erogation of power, without the use of synchronisers, brakes or clutches. - It does not have an infinity of ratios between minimum and _. t - maximum. When it changes ratio it passes from one pre- established ratio to another by installation of the rela¬ tive gears. - Having established the maximum and minimum ratios, the ma¬ ximum number of ratios with which the changer may be con¬ structed is given by the difference between,the number of 0 teeth one the largest constant primitive radius cog, of the cone of toothed cogs, and that of the smallestconstant primitive radius cog, of the same cone, plus one unit. - The use of gears allows the eliminatiφn of the limitations 5 regarding the transmittable torque of continuous changers with clutch. - The yield is high -at-.all ratios and all rotation speeds, thanks to the limited number of geared cogs and bearings necessary, its value is higher than that of mechanical type discontinuous changers. - From time to time the working ratio may be made known and while functioning this is mathemacally unalterable(there is no slipping) . - It is fitted with original mechanical plant for a semi¬ automatic type changer which use the movement of the chan ger itself to take effect. - The automation of the changer requires onl .a decisional apparatus. - The changes of ratio may be effected singularly or in s . e ries, in increasing or reducing the ratio. - In comparison with mechanical changers with clutches, especially for the transmission of significant power, its construction is simpler and more robust. In the following paragraphs, the design, construction, and functioning of the new continuous speed changer with fixed ratio gears, are examine . Design To give formal consistency to the speed changer which is the subject of the present invention, ten design have been prepared. These permit identification of the constitutive elements, comprehension of the functional description and a representation;,- although indicative, of the construction. The evidente schematization of the whole and of the detail clarifies how themes not linked to the originality of the design have not been dealt with, these being strictly per¬ tinent to the execution phase. The system used for the pre sentation is that of orthogonal projection. All the tables, except No. 10 where details are presented, represent the complete changer, suitably sectioned to evidence thecompo nents which permit it to function. It was drawn in the con dition In which there is a ratio working, while all the parts destined to produce the ratio change~are at rest. To permit interpretative comparisons between the various dra- wings, the scale with respect to the hypothetical changer which they represent is' the same for each; with the excep¬ tion of the section 10A-10A presented in drawing No. 10 where there is an enlargement for reasons of clarity. These are in the order: - No. 1 :- Plan view of the changer along the section 1-1 indicated in the other drawings. - No.2 :- Side view of the changer along the section 2-2 indicated in the other drawings. - No. 3 :- Front view of the changer along the section3-3 indicated in the other drawings. - a - No. 4 :- Front view of the changer along the section 4-4 indicated in the other drawings. No. 5 :- External * front view of the changer from the motor entrance side as indicated by arrow No. 5 in the other drawings. No. 6 :- Longitudinal view of the changer along the section 6-6 on the secondary shεfft indicated in the other drawings. No. 7 :- Longitudinal view of the changer along the section 7-7 on the manoeuvre bar indicated in the other drawings. o. 8 :- Longitudinal view of the changer along the section 8-8 on the main shaft indicated in the other dra wings. In correspondence to arm " 43., the-section plane passes through the axis of wheel .41 and pin 435. o. 9 :- Plan view of the changer along the section 9-9 indicated in the other drawings. No.10 :- To the,left section 10A-10A enlarged, without axle 500, as indicated in drawing No. 3; to the right section 10B-10B as indicated in drawing No. 7 No.11 :- A partially enlarged overall view of one of the gear applications, with reference to the previous figures,particularly suitable for pedal powered vehicles. Number list of the components For clarity of interpretation, all those components, repre ¬ sented in the drawings which contribute to the functional solidity of the originality of this invention in its entire ty, are listed and numbered. 100 Changer box 101 Rest for tooth 433 (interaxis between wheels 441 and 516). 102 Rest for tooth 433 (interaxis between wheels 441 and 515). 103 Rest for tooth 433 (interaxis between wheels 441 and 514). 104 Rest for tooth 433 (interaxis between"wheels 441 and 513). 105 Mount on cas'ihg fdi. o_'dillatirig _trπi 700. 106 Mount on casing for oscillating arm 700. 107 Support mount on casing for spring 330. 108 Return guide for arm 322 at rest condition. 09 Return guide for arm 313 at rest condition. 10 Track at rest position of arms 313 and 322. 11 Movement channel for arms 312 and 321 when not active. 12 Platelet of guide 108 for mpvement of arm 322. 13 Platelet of guide 109 for movement of arm 313. 14 Disengagement vane for arm 321 when active. 15 Disengagement vane for arm 312 when active. 116 Reference direction for transversal movement. 117 Reference direction for transversal movement. 118 Reference direction for vertical movement. 119 Reference direction for vertical movement. 120 Reference direction for longitudinal movement. 121 Reference direction for longitudinal movement. 122 Reference direction for longitudinal rotation axis. 123 Reference direction for longitudinal rotation axis. 124 Reference direction for vertical rotation axis. 125 Reference direction for vertical rotation axis. 126 Imaginary plane of perpendicular reference for shaft 500. 127 Reference radius limiting sector of variable radius wheels. 128 Reference radius limiting sector of variable radius wheels. 29 Reference radius limiting sector of variable radius wheels. 30 Reference radius limiting sector of variable radius wheels. 31 Reference radius limiting sector of cams 507 and 508. 32 Reference radius limiting sector of cams 507 and 508. 33 Reference radius limiting sector of cams 507 and 508. 34 Reference radius limiting sector of cams 507 and 508. 35 Imaginary line of reference between axis of shaft ξLOO and wheel 441. 136 Excursion limit line for arms 312, 321 in direction 117 200 Stick to control changer ratio changes. 201 Lodging or extremity 806 of arm 805 • - 202 Lodging for arm 214. 203 Track plug to define movement of stick 200. 204 Definition lodging for track of stick 200. 205 Calibrated spacing.. . washer for track ofsprin g 206. 206 Position and return spring for stick 200. 207 Calibrated spacing washer for track of spring 206. 208 Elastic track-ring for spring 206 (on stick 200). 209 Elastic track ring for spring 206 (on casing 100). 210 Inversion lever for direction of stick 20p. 211 Rotation pin' for lever 210. 212 Protuberance to control a_iιi 312. 213 Protuberance to control arm 321. 214 Connection arm with stick 200 of lever 210. 300 Manoeuvre bar. 301 Locking nut mount for spring 302. 302 Locking spring for ring nut 303. 303 Tracking ring nut spring 307 (on casing 100). 304 Tracking nut for spring 307 (on bar 300). 305 Safety locking cotter pin for nut 304. 306 Calibrated tracking spacing washer and guide for bar 300. 307 Positioning and longitudinalireturn spring for bar 300. 308 Calibrated tracking spacing washer and guide for bar 300. Arm of bar 300 for transport of trolley 423. Arm of car 300 for disengagement of tooth 703- Action lever for bar 300 in directions 122 and 121. Upper arm of action lever. 311. Side arm of action lever 311. Slide for arm 313- Beak for arm 313. Tracking return spring of lever 311- Slot of hub of lever 311 for lodging tooth 318. Reciprocal tracking tooth of bar 300 for levers 311, 320. Slot of hub of lever 320 for lodging tooth 318. Action lever for bar 300 in directions 122 and 120. Upper arm of action lever 320. Side arm of action lever 320. Slide for arm 322. Beak for arm 322. Tracking return spring of lever 320. Fileted tracking ring for hub of levers 311 and 320. Elastic locking plug for ring326. Positioning arni and rotation return for bar 300. Elastic retaining ring for hub of arm 328. Positioning and return spring for arm 328. Fluid filling tap; contrast rest for spring 332. Positioning and contrast spring for sphere 333- Flow control sphere in chamber 335 - Communication conduit between sphere valve and cylinder centre. - 13 - 335 Cylinder chamber. 336 Parafluid in the passage of the piston rod into chamber 335- 337 Longitudinal varikble section channelling into chamber 335. 338 Central connection conduit for the fluid. 339 Piston of the shock absorber ' lant. 340 Rod of the piston 339. 341 Calibrated perforations of the piston 339- 3.2 Cylinder chamber. 343Parafluid on the passage of the piston rod in chamber 342. 344 Longitudinal variable section channelling into chamber 342. 345 Fluid filling tap; contrast rest for spring 346. 346 Positioning and contrast spring for- sphere 347. 347 Flow control sphere in chamber 342. 348 Closure tap for the shock absorption plant cylinder. 3 9 Anchorage staff for piston rod on bar 300. 350 Longitudinal channeling for coupling bar 300 - arm 328. 400 Changer main shaft. 401 Shaft of reduction gear toothed wheel 403. 402 Fitting tongue of wheel 403 on shaft 401. 403 Cylindrical toothed wheel of shaft 401. 404 Blocking ring nut of wheel 403. - 1 _ - 405 Safety washer for ring nut 404. 406 Toothed wheel ori ' main shaft (Reduction gear). 407 Fitting tongue of wheel 406 on shaft 400. 408 Blocking ring nut of wheel 406. 409 Safety washer for ring nut 408. 410 Spacer washer between wheel 406 -and bearing 411. 411 Twin crown ball bearing for radial and axial thrust In both directions. 412 Fitting tongue of pinion 413 pn axis 400. 413 Main shaft pinion.' 414 Spacer washer between pinion 413 and bearing 415. 415 Crown ball bearing for radial thrust. -16 Blocking ring nut for pinion 413 and bearing 415. 417 Safety washer for ring nut 416. 418 Tubular support for shaft 400 and trolley 423. 19 Blocking ring nut for external thrust of bearing 411. 20 Safety washer for ring nut 419. 21 External longitudinal modular teeth of support 418. 22 Engagement slot between wheel 441 and pinion 413. 23 Running support trolley for wheel 441. 24 Internal longitudinal modular teeth of trolley 23; 25 Socket for arm 309 (movement of trolley 423). 26 Socket for arm 309 (movement of troliey 423) . 27 Socket for arm 309 (movement of trolley 423). 28 Socket for arm 309 (movement of trolley 423). 429 Socket for tooth 703 (blockage of. trolley 423). 430 Socket for tooth 703 (blockage of ' trolley 423). 431 Socket for tooth 703 (blockage of trolley 423). 432 Socket for tooth 703 (blockage of trolley 423). 433 Thrust tooth for interaxial calibration between wheel 441 and wheels 513,514, 515, 516. 434 Support arm for idling satellite wheel 441. 435 Pin of arm 434 to support wheel 441. 436 Twin crown ball bearing for radial and axial thrust in both directions< 437 Blocking ring nut for bearing 43 . 438 Safety washer for bearing 437. 39 Blocking washer for external thrust of bearing 436. 440 Blocking screws for washer 439. 441 Cylindrical toothed idling satellite wheel with helical teeth. 442 Cylindrical surface base of toothed vane of wheel 441. 00 Secondary shaft of the changer. 01 Blocking ring nut of the cam group. 02 Safety washer for nut 501. 03 Pressure washer for tightening cam group. 04 Support disc for cam group. 05 Spiral radial cam for oscillation control of lever 320. 06 Spiral radial cam for oscillation control of lever 311-. 07 Cylindrical cam for axial and radial control of lever 320. 508 Cylindrical cam for axial and radial control of lever 311 509 Fitting hub for cam group on shaft 500. 510 Fitting tongue for hub 509 on shaft 500. 511 Spacer between hub 509 and bearing 512. 512 Single crown ball bearing for radial_.lo_ld. 513 Cylindrical toothed wheel with helical teeth (constant radius) . 514 Cylindrical toothed wheel with helical teeth (constant radius) . 515 Cylindrical toothed wheel with helical teeth (constant radius) . 516 Cylindrical toothed wheel with helical teeth (constant radius) . 517 Cylindrical toothed wheel with helical teeth (varied radius) . 518 Cylindrical toothed wheel with helical teeth (varied radius) . 519 Cylindrical toothed wheel with helical teeth (varied radius) . 520 Peak of varied radius wheel teeth. 521 Fitting tongue for wheel cone on shaft 500. 522 Spacer between wheel 516 and bearing 523. 523 Twin crown ball bearing for radial and axial thrust in both directions. 524 Spacer between bearing 523 and joint 525. 525 Coupling joint of changer for motion output. 526 Blocking ring nut for wheel cone,: bearing 523 and joint 525. 527 Safety washer for nut 526. 5 528 Blocking washer for external thrust of bearing 523. 529 Blocking screws for washer 528. 600 Torsion spring bar. 601 Cylindrical toothed wheel with straight teeth. 602 Mount channelling for spring 600 on casing 100. 603 Elastic anti-running plug for spring 600 from casing 100. 604 Mount channelling for spring 600 on toothed wheel 601. 605 Elastic anti-running plug for spring 600 from wheel 601. 700 Oscillating arm to block. trolley 423. ' 701 Rotation pin for arm', 700. 702 Elastic anti-unwinding plug for pin 701 from mount 106. 703 Lower tooth of arm 700. 704 Thrust spring for arm 700. 800 safety cursor, Q 801 Calibrated tracking and running washer for cursor 800. 802 Calibrated tracking and running washer for cursor 800. 803 Elastic track ring for spring 804. 804 Position and longitudinal return spring for cursor 800. 805 Jointed security arm on support 418. 806 Taperod extremity of arm 805 • Operation With reference to drawings form No. 1 to No. 10. The drawings present a revolution reduction changer. Nothing would change however, with reference to this invention, if the changer were to be a revolution multiplier. In the foJL lowing description the operation of the changer is dealt with, above all with regard to its orig±riality. Many details such as elastic plugs, washers ring nuts, bearings, etc. listed among the components will not therefore be mentioned, as their fun- ction is clear and in any case easily deduced from the drawing. In the first part the elementary functions of- the primary com¬ ponents will be illustred, and, where necessary, certain for¬ mal characteristic linked_to the operation, where not clear from the drawings in sufficient emphasis; in the second part the general operation of the changer in its various hypothe¬ ses will be discussed. For clarity of illustration the chan¬ ger is divided into the following sectors : 1 - Changer casing (identified with its components in series 100 in the drawings) ; 2 - Control stick complex (as above series 200) . 3 - Manoeuvre bar complex (as above series 300) 4 - Main shaft complex (as above series 400) - Secondary shaft complex (as above series 500) - Torsion spring bar complex (as above serie 600) 7 - Trolley blocking complex (as above series 700) 8 - Safety devices (as above series 800) Elementary functions of the components 1 - Changers casing This Is the support lodging of the entire complex and is modelled in such a manner as to offer integrity for lubri. fication, protection from extraneous matter, attachments, seatings, tracks, lodgings, etc. In the proposed scheme only the components necessary to the illustration of the origina¬ lity of the operation of the present invention are represent ted. Beside the four' longitudinal walls, the two frontal clo sure plates and the intermediate support plate for the secon dary shaft 500, there are the components with specific fun¬ ctions mentioned in the description. 2 - Control stick complex This complex is required to transmit commands to change ra¬ tio to the manoeuvre bar complex. The control stick complex consists mainly of : Stick 200, spring 206, lever 210. The latter may not be necessary; see relativeexplanation in the sectionon the manoeuvre bar complex. Depending on the type of command to which the stick is subject, the changer may be defined as semi - or completely automatic: - Semi-automatic if the stick is directly controlled, ma¬ nually or through servo-mechanisms, by man; - Automatic if an intelligent control panel replaces man - 2D - which decides on the basis of pre-established parameters obtained from the plant. Stick 200 May only have axial translation movement. The entity of the excursion is defined by the lenght of the slot 204. The ope ration of the stick may be defined as having five phases: 1 - Rest phase; the stick is in a.condition of stasis and plug 203, integral to casing 100, is at the centre of slot 204. 2 - Outgoing longitudinal running phase; the stick moves in direction 116 bringing the extremity of slot 204 against plug 203. 3 - Return longitudinal running phase; the " stick moves in direction 117 to return to the restposition. 4 - Outgoing longitudinal running phase; the stick moves in direction 117 bringing the extremity of slot 204 against plug 203. 5 - Return longitudinal running phase; the stick moves in direction) 11.6 to return to the rest position. In the drawings the stick is presented in the rest position. Spring 206 This is preloaded and blocked in its lodging by elastic ring 209- Its operational phases coincide with those of the con¬ trol stick 200. They are : 1 - Rest phase; the spring is extended and exerts force on its tracks. It fixes the rest position of control stick 200. 2 - Compression phase for axial movement of control stick 200; The spring is compressed in direction 116. 3 - Extension phase for axial movement of control stick.200; the spring extends in direction 117 returning tooits rest position. 4 - Compression phase for axial movement of control stick 200; The spring is compressed in direction 117. 5 - Extension phase for axial movement of control stick 200; the spring extends in directionllδ returning to its rest position. In the drawings the- spring is presented in the rest position. Lever 210 This may have only one oscillation movement " around pin 211 in directions 124 and 125. Its operational phases coincide with those of the control stick 200. They are : 1 - Rest phase; the lever is stationary and neither of the two protuberances 212 and 213 exceeds line 136 in direction 116. 2 - Outgoing oscillatory phase; lever 210 rotates in direction 125 taking protuberance 213 beyond line 136 in direction 116. 3 - Return oscillatory phase; lever 210 rotates in direction 124 and return to the rest position. 4 - Outgoing oscillatory phase; lever 210 rotates in direction 124 taking protuberance 212 beyond line I36 in direction 116. 5 - Return oscillatory phase; lever 210 rotates in direction 125 and return to the rest position. In the drawings the lever is presented in the rest position. 3 - Manoeuyre bar complex This complex has the purpose of rendering operative the or¬ ders received from the control stick complex. It consists basically of : - the manoeuvre bar d'tself; with spring 307, arms 309 and 310 and arm 328 with spring 330, action lever 311 with arms 312 and 313 and spring 316; action lever 320 with arms 321 and 322 and spring 325; the shock absorption plant for the return of bar 300. It should be noted that in the drawings and in the description, for simplicity, this complex Is represented in a single bar solution which moves in both directions 120 and 121, with the task of moving trolley 423 (with wheel 441) in synchronicity with the ro¬ tation of the secondary shaft 500. Other solutions are pos_ sible; two are easily identified. The first is that with two bars, one for movement on direction 120, and the other in direction 121. -In this case each will require a spring type 307 for monodirectional longitudinal return, a type 309 arm to move trolley 423, a type 310 arm to unblock trolley 423, a type 328 arm to establish the rest position and for thecompression of the type 330 spring in oscillatory rota¬ tion, a type 330 spring for return from oscillatory rota¬ tion, a shock absorption plant to brake the return (If ne- cessary) . On one of the bars a type 311 action lever will be required with related arms type 312 and 313 and spring type 316, while the other will require a type 320 action lever with relative arms type 321 and 322 and spring type 325- The c two bars will be positioned in such a manner as to adequate¬ ly expedite their functions. The second may be defined as mixed. There is a bar which moves iζt direction 120 and di¬ rection 121. It has all the formal and functional characte¬ ristics of that illustrated in the drawings, with one excep- ° tion :- the type 320 and 311 action levers with their arms and springs are not mounted on the bar nut on two suitably positioned independent shafts; the action levers are join¬ ted to the shafts and these latter employ the " bar only when the respective lever is activated by the control: stick. In 5 these circumstances they transfer the rotational and transla tional movements transmitted by the cams to the bar. With reference to the direction of rotation of the cam group; arms 313 and 322 may be constructed to engage beaks 315 and 324,to cams 505 and 506, before or after the centre of oscil lation of the respective action lever. In the drawings the arms 313 and 322 are both illustrated as mounted before their centre of oscillation. There are three other possibilities: - both after, one before and one after, and again one before and one after but in the opposite sense to the preceding car se. When adopted the latter two cases permit the elimination of lever 210. Control stick 200 can command arms 312 and 321 directly, as the direction of their movements, to move levers 320 and 311, is the same as its own. Bar 300 This may have an axial translation movement and oscillate around Its own axis. Its operations may be divided into the following phases: 1 - Absolute rest phase; in this a longitudinal rest posi¬ tion and an oscillatory rest position are identified. 2 - Outgoing oscillatory rotation phase in direction 122. 3 - Returning oscillatory rotation phase in direction 123. 4 - Outgoing longitudinal slide movement in direction 120; may be effected in^ one or two phases (see general ope¬ ration) . 5 - Returning longitudinal slide movement in direction 121 6 - Outgoing longitudinal slide movement in direction 121; may be effected in one or two phases (see general ope¬ ration) . 7 - Returning longitudinal slide movement in direction 120. In the drawings the bar is presented in the absolute rest position. Spring 307 This is preloaded and blocked in its lodging by ring nut 303. It does not interfere with the oscillatory'- movements of bar 300, as it has only movements of axial sliding. Its operation may be established in the following phases : 1 - Rest phase; the ' spring is extended and exerts force on its tracks. It fixes the longitudinal rest position of bar 300. 2 - Compression phase for axial movement of bar 300 in direction 120. It follows the ippvements of bar 300 in the fourth phase. 3 - Extension phase for axial movement of bar 300 in direc- tion 121. It obliges the bar to effect its fifth phase. 4 - Compression phase for axial movement of bar 300 in di¬ rection 121. It ollows the movements of bar 300 in the sixth phase. 5 - Extension phase for axial movement of. bar 300 ini :di- rection 120. It obliges the bar to effect its seventh phase. In the drawings spring 307 is presented in the rest posi¬ tion. Arm 309 This is integral to bar 300. Its operational phases are those of bar 300. The following formal and functional cha¬ racteristics should be evidenced : - The section of the arm in the entry zone is tapered to faciliate its entry into lodgings 425, 4 6, 427, 428 on trolley 423. - The lateral faces of the section'::are perfectly parallel to - 2E - the perpendiculSr plane of the rotation axis of bar 300. - In the entry or exit phases of the arm into or from the lodgings of which above, trolley 423 is not moved in di¬ rections 120 and 121. The following is a list of its pha- ses : 1 - Absolute resti phase; in this a longitudinal rest posi- tion and an oscillatory rest position are identified. - Outgoing oscillatory rotation phase in direction 122 ; the arm enters one of the lodgings 425, 426, 427, 428. - Returning oscillatory rotation phase in direction 123; the arm exits one of the lodgings 425, 426, 427, 428, and returns to its oscillatory rest position. - Outgoing longitudinal slide movement in direction 120; may be effected in one or two phases (see general ope¬ ration) . The arm pushes the trolley 423 from one wheel 513, 514, 515, 516 to.-:another in direction 120. - Returning longitudinal slide movement in direction 121; the arm returns to its longitudinal rest position. - Outgoing longitudinal slide * movement in direction 121; may be effected in one or two phases (see general ope¬ ration) . The arm pushes the trolley 423 from one wheel 513, 514, 515, 516 to another in direction 121. - Returning longitudinal slide movement in direction 120; the arm returns to its longitudinal rest position. the drawings the arm is presented in the absolute rest position. Arm 310 This is integral to bar 300. Its operational phases are tho¬ se of bar 300. They are : 1 - Absolute rest phase; in this a longitudinal rest posi¬ tion and an oscillatory rest position are identified. 2 - Outgoing oscillatory rotation "phase in direction 122; the arm in its rotation causes arm 700 to rotate in di¬ rection 123 provoking the exit of tooth 703 from one of the lodgings 429, 430, 431, 432. 3 - Returning oscillatory rotation movement in direction 123; the arm returns to its oscillatory rest position. 4 - Outgoing longitudinal slide movement in direction 120; may be effected in one or two phases' (see general ope¬ ration) . The arm moves laterally in direction 120 and abandons arm 700 which rotates in direction 122 under the thrust of spring 704. 5 - Returning longitudinal slide movement in direction 121; the arm returns to its longitudinal rest position in correspondence to arm 700. 6 - Outgoing longitudinal slide movement in direction 121; may be effected in one or two phases (see general ope¬ ration) . The arm moves laterally in direction 121 and abandons arm 700 which rotates in direction 122 under • the thrust of spring 704. 7 - Returning longitudinal slide movement in direction 120; the arm returns to its longitudinal rest position in cor¬ respondence to arm 700. In the drawings the arm is presented in the absolute rest po- c sition. Action lever 311 This consists of the upper arm 31*2 and the lateral arm 313; it lodges on bar 300. It may have longitudinal translation movement together with bar 300 in directions 120 and 121,and 0 oscillate around the axis of bar 300 in directions 122 and 123. The oscillatory movement is, in part, effected freely and in part together with bar 300. Its operations may be di¬ vided into the following phases : 1 - Absolute rest phase; as with bar 300, in this longitu¬ 5 dinal rest position and an oscillatory rest position are identified. 2 - Outgoing oscillatory rotation phase; lever 311 rotates in direction 122, bar 300 is at rest. Beak 315 is brought 0 into contact with cam 506 for engagement. 3 - Outgoing oscillatory rotation phase in direction 122,bar 300 is at rest. Beak 315 firmly enters the channelling of cam 506. 4 - Outgoing oscillatory rotation phase; slot 317 strikes 5 tooth 318, lever 311 and bar 300 together in direction 122. Beak 315 completes run along cam 506. This phase coincides with the second phase o "bar 300. 5 - Returning oscillatory rotation phase; lever 311 rotates in direction 123 pushed by tooth 318. This phase coinci¬ des with the hird phase of bar 300 which returns to the oscillatory rest position. 6 - Returning oscillatory rotation phase; lever 311 continues to rotate in direction 123 pushed by spring 316 alone (tooth 318 is static), toward its oscillatory rest posi¬ tion. 7 - Outgoing longitudinal slide movement in direction 120; coincides with the fourth phase of bar 300. In this pha¬ se the lever is inactive. Arm 312 runs in channel 111. 8 - Returning longitudinal slide movement in"direction 121; coincides with the fifth phase of bar 300. In this phase the lever is inactive. Arm 312 runs in channel 111. 9 - Outgoing longitudinal slide movement in direction 121; coincides with the sixth phase of bar 300. 10- Returning longitudinal slide movement in direction 120; coincides with the seventh phase of bar 300. In the drawings the action lever is presented in the abso¬ lute rest position. Action lever 320 This consists of the upper arm 321 and the lateral arm 322; it lodges on bar 300. It may have longitudinal translation movement together with bar 300 in directions 120 and 121, and oscillate around the axis of bar 300 in directions 122 and 123. The oscillatory movement is, in part, effected 3D - freely and in part together with bar 300. Its operation may be divided into the following phases: 1 - Absolute rest phase; as with bar 300, in this a longitu¬ dinal rest position and an oscillatory rest position are identified. 2 - Outgoing oscillatory . rotation phase; lever 320 rotates in direction 122, bar 300 is at rest. Beak 324 is brought in¬ to contact with cam 505 for engagement. 3 - Outgoing oscillatory rotation phase in direction 122, bar 300 is at rest. Beak 324 firmly enters the channeling of cam 505 • 4 - Outgoing oscillatory rotation phase; slot 319 strikes tooth 318, lever 320 and bar 300 rotate together in di¬ rection 122. Beak 324 completes run along cam 505. This phase coincides with the second phase of bar 300. 5 - Returning oscillatory rotation phase; lever 320 rotates in direction 123 pushed by tooth 318. This phase coin¬ cides with the third phase of bar 300 which returns to the oscillatory rest position. 6 - Returning oscillatory rotation phase; lever 320 continues to rotate in direction 123 pushed by spring 325 alone (tooth 318 is static) towards its oscillatory rest po¬ sition. - Outgoing longitudinal slide movement in direction 120; coincides with the fourth phase of bar 300. 8 - Returning longitudinal slide movement in direction 121; coincides with the fifth phase of bar 300. 9 - Outgoing longitudinal slide movement in direction 121 ; coincides with the sixth phase of bar 300. In this phase the lever is inactive. Arm 321 runs in channel 111. 10- Returning longitudinal slide movement in direction 120; coincides with the seventh phase of bar 300. In this pha se the lever is inactive. Arm 321 runs in channel 111. In the drawings action lever 320 is presented in the absolu te rest position. Spring 316 This is lodged within the hub of action lever 311. The two extremities of the circular rod of which it consists are lodged respectively on bar 300 and the hub of action lever 311. It is torsion pre-loaded according to the axis of bar 300 and attempts to make lever 311 rotate.in direction 123. Its operational phases are : 1 - Rest phase; the spring holds the extremity of arm 3 3 pressed against track 110. - Outgoing oscillatory rotation phase in direction 122; the spring is compressed by torsion. Its extremity tou¬ ching lever 311 rotates in direction 122. It coincides with the second phase of lever 311 in which beak 315 comes into contact with cam 506. 3 - Outgoing oscillatory rotation phase in direction 122; the spring is further compressed by torsion. Its extre_ mity touching lever 311 rotates in direction 122 for a further excursion to that of the preceding phase. Coin- 5 cides with the third phase of lever 311 in which beak 315 is inserted in the channel of cam 506. 4 - Returning oscillatory rotation phase in direction 123; the spring is extended by torsion. Its extremity tou¬ ching lever 311 rotates in direction 123- Coincides with the sixth phase of lever 311 in which the latter returns to the oscillatory rest position. In the drawings spring 316 is presented in the rest position. Spring 325 This Is lodged within the hub of action lever 320. The two 5 extremities of the circular rod of which it consists are lodged respectively on bar 300 and the hub of action lever 320. It is torsion pre-loaded according to the axis of bar 300 and attempts to make lever 320 rotate in direction 123. Its operational phases are: o - Rest phase; the spring holds the extremity of arm 322 pressed against track 110. 2 - Outgoing oscillatory rotation phase in direction 122; the spring is compressed by torsion. Its extremity tou¬ ching lever 320 rotates in direction 122. It coincides with the second phase of lever 320 in which beak 324 5 comes into contact with cam 50 • 3 - Outgoing oscillatory rotation phase in direction 122; the spring is further compressed by torsion. Its extre mity touching lever 320 rotates in direction 122 for a further excursion to that of the preceding phase. Coin cides with the third phase of lever 320 in which beak 324 inserted in the channel of" cam 505. 4 - Returning oscillatory rotation phase in direction 123; the spring is extended by torsion. Its extremity tou- ching lever 320 rotates in direction 123- Coincides with the sixth phase of lever 320 in which the latter returns to the oscillatory rest position. In the drawings spring 325 is presented in the rest posi¬ tion. Arm 328 This may move in oscillation only, which it effects together with bar 300, to which it is coupled with longitudinal chan¬ nelling. Bar 300 can also slide freely in an axial direction within its hub. .Its operations phases are as follows: - Rest phase; the arm is at rest against casing 100 held by spring 330. It fixes the oscillatory rest position of bar 300. 2 - Outgoing oscillatory rotation phase in direction 122; It coincides with the second phase of bar 300. 3 - Returning oscillatory rotation phase in direction 123; Coincides with the third phase of bar 300. In the drawings arm 328 is presented in the rest position. Spring 330 This is preloaded and lodged between support 107 and the extremity of arm 328. Its operation may be defined as fol¬ lows : 1 - Rest phase; the spring is exterfded and holds the arm against casing 100, fixingthe oscillatory rest posi¬ tion. 2 - Compressione phase; arm 328 rotating in direction 122 compresses the spring, further increasing its load. This coincides with the second phase of bar 300. 3 - Extension phase; arm 3 8 rotating in direction 123 permits extension of the spring which returns to a condition of rest. This coincides with the third phase of bar 300. The torque which spring 330 applies through arm 328 to bar 300, is decidedly superior to that applied in the opposite direction by springs 316 and 325 in all operating .condi¬ tions. In the drawings spring 330 is presented in the rest posi¬ tion. Shock absorption plant For functional purposes this consists of fixed elements, mobile ' elements and the luid which fills it. Without con sidering the two sphere valves which open and close automa tically, the sole element which determines its operational phases is piston 339. This is attached.via piston shaft 340 and mount 3 9 to bar 300. It only takes longitudinal move- _. ments from the bar so that its operational phases are: _ 1 - Rest phase; all quiet. Corresponds to the first rest phase of bar 300. 2 - Outgoing longitudinal slide movement in direction 120; coincides with the fourth phase of bar 300. 0 3 - Returning longitudinal slide movement in direction 121; coincides with the fifth phase of bar 300. 4 - Outgoing longitudinal slide movement in direction 121; coincides:-with the sixth phase of bar- 300. 5 - Returning longitudinal slide movement- in direction 120; 5 coincides with the seventh phase of bar 300. In the drawings the shock absorption plant is presented in the rest position. The shock absorption plant is used to avoid, during the 0 fifth and seventh phases of bar 300, because of the mass in play and the trust of spring 307, phenomena of axial vibra¬ tion with repeated extension and compression of spring 307 around the longitudinal rest point of bar 300. To analyse its operation, let us examine the working phases listed. 25 Since the plant is perfectly symmetrical, it is sufficient to consider the fourth and fifjfch phases : - 3G - - Phase 4; When piston 339 moves in direction 121, chamber 335 is reduced in volume while 3 2 increases in volume in the same measure. Piston 339 moves easily because the fluid can flow from 335 to 342 freely, both by lifting sphere 333, conduit 334, central conduit 338; and through channelling 337 and the calibrated perforations 341 in piston 339- The dimen sions of the passages must be sucj), that they do not create resistance to the movement of piston 339- - Phase 5; When piston 339 moves in direction 120 to return to its rest position, the movement reduces the volume of chamber 342 and increases in the same measure that of cham ber 335- The outflow towards 335 may not however be effected through sphere valve 333. This does not permit fluid to en ter chamber 335 in the same manner as it permitted exit. Out flow from 34 to 335 is effected only through the channelling 337 and the calibrated perforations 341. The possibility of varying the number and diameter of the perforations 341, and the section of channelling 337 point by point along the channel, permits adequate definition of the diagram of mo vement speed of bar 300 in the fifth return phase. Thus the eventuality of axial vibrations phenomena of bar 300 aroung the longitudinal rest point is eliminated. 4 - Main shaft complex This complex, receiving movement from outside the changer, transfers it to the secondary shaft. It basically consists of trolley 423, wheel 441, support 418, shaft 400 and pinion 413. Trolley 423 This presents on its surface the lodgings 425, 426, 427, 428 to retain arm 309, and lodgings 429, 430, 431, 432 to retain tooth 703. Their section relative to a longitudinal plain passing through the axis of the trolley requires that cer¬ tain formal characteristics of functional importance be pla- -ced in evidence : - The entrance is bevelled to facilitate engagement. - The lateral faces of the section are perfectly parallel to the perpendicular plane of the longitudinal rotational axis. - The circumferential extension of the lodgings in such that in the case of 425, 426, 427, 428 the trolley is permitted to rotate without interfering with arm 309; in the case of 429, 430, 431, 432 there is no interference with tooth 703 thus avoiding alteration to the interaxis between 441 and 513, 514, 515 and 516. Trolley 423 is animated by two movements; one of longitudinal translation along support 418 and one of oscillation together with this. The maximum excursion possible, in both cases, expects as many stages as there are working ratios in the changer; the stop take place in correspondence to the places where wheel 441 engages one of the wheels 513, 514, 515,516. Its phases may be defined as follows : 1 - Rest phase; the trolley is still. A working ratio is functioning between wheel 441 and one of the wheels 513, 514, 515, 516. 2 - Longitudinal slide movement in direction 120. Coincides with the fourth phase of manoeuvre bar 300. The excur ¬ sion is limited to two successive placings . It may occur in one or two stages (see general operation). 3 - Longitudinal slide movement in direction 121. Coincides with the sixth phase of manoeuvre bar 300. The excursion is limited to two successive placings. It may occur in one or two stages (see general operation) . 4 - Oscillatory rotation phase in direction 122; The excur- sion is limited to two successive placings. 5 - Oscillatory rotation phase in direction 123; The excur¬ sion is limited to two successive placings. In the drawings trolley 423 is depicted at rest in one of the two extreme position. Toothed cog 441.- This is a cylindrical toothed idling satellite wheel with helical teeth; the following should be considered characte¬ ristic of its functions : - Thickness; having to engage a cone of stepped cogs of differing diameters, in the definition of thickness (taken in the direction of its rotation axis) lateral play should be considered to avoid interference with the larger conti ¬ guous cogs in direction 121. - Surface base of toothed vane 442. This base belongs to a perfect cylindrical surface so that, during engagement with the variable radius cogs 517, 518,519 it permits support on the raised summit 520 of their teeth in order to guarantee instant by instant the desired interaxis. of the project. - Angle of inclination of the helical teeth (in common with the kinematic chain reproduced for the module) . The mini¬ mum value of inclination ofl'the teeth must be such that when cog 441 engages one of the variable radius cogs 517, 518, 519, the summit 520 of the teeth of this will always have support on the base 442 of the vane of* its teeth du¬ ring rotation, without a continuity solution. The value of the module of its teeth is in common with the wheels of the kinematic chain to which it belongs, that is 413, 441, 513, 515, 516, 517, 518, 519- Cog 441 is animated by a movement of rotation around its axis, one of oscillatory revolution around the axis of shaft 400 and one of longitudinal translation. Its operational phases are as follows : 1 - Absolute rest phase. There are no movements of any type, the changer is stopped. 2 - Rotation phase; the cog revolves around its own axis in the direction indicated by the arrows in the drawings. 0079 - .0 - 3 - Phase of revolution in direction 122; the entire system cog 441, trolley 423, support .18 rotates around the axis of shaft 400. This coincides with the fourth phase of the trolley 423. 4 - Phase of revolution in direction 123; the entire system etc. (see above). Coincides with the fifth phase of trolley 423. 5 - Phase of translation in direction 120; coincides with the second phase of trolley 423- 6 - Phase of translation in direction 121; coincides with the third phase of trolley 423• In the drawings the cog 441 is depicted engaged with cog 516. Support 418 This may move in oscillation only around its own axis. The maximum excursion possible expects as many stages as there are working ratios in the changer; the stops take place in correspondence to the places where wheel 441 engages one of the wheels 513, -514, 515, 516. Its operating are as:-follows: 1 - Rest phase; the support does not move. 2 - Oscillatory rotation phase in direction 122; The excur¬ sion is limited to two successive placings. 3 - Oscillatory rotation phase in direction 123; The excur¬ sion is limited to two successive placings. In the drawings support 418 is represented in one of the - .1 two extreme rest positions. Shaft 400 This may move in-rotation only around its own axis. Its ope_ rative phases are as follows : 1 - Rest phase; the shaft does not move. 2 - Rotation phase; the shaft rotates in the direction indi cated by the arrows in the drawings, feeding the move¬ ment of the changer. The movement may derive to the shaft from an external joint filleted to its extremity, or, as drawn, from a toothed cog ratio of type 403 and 406. These cogs may, as shown in the drawings, reduce the rotation speed of the shaft, or, if in verted, increase it. In the drawings shaft 400 is depicted in one of the many position assumed during rotation. Pinion 413 This is securely linked by filleting to shaft 400, with which it shares the operational phases. Its length, taken in the direction of its axis of rotation, is such that it permits cog 441 to maintain engagement, hen it passes from one to another of the extreme cogs of the stepped cone, that is 513 and 516. The value of the module of its teeth and the value in degrees of their inclination (see the explanations for cogs 441), are common to those of the other cogs of the kinematic chain, that is 413, 441, 513, 514, 515, 516, 517 518 , 519 - In the drawings pinion 413 is 'shown in one of the many posi tions assumed duriϊig rotation. 5 - Secondary shaft complex This complex, receiving movement from main shaft, via its toothed cogs, transfers it to the outside joint. It basical¬ ly consists of shaft ' 500, cylindrical toothed wheel with he¬ lical teeth (constant primitive radius) 513, 514, 515, 516, cylindrical toothed wheel with helical teeth (variable pri¬ mitive radius) 517, 518, 519, joint 525, rotating cam group 505, 506, 507, 508. Shaft 500 This may move in rotation only around its own axis . Its ope rative phases are indicated next : 1 - Rest phase; the shaft does not move. 2 - Rotation phase; the shaft rotates in the direction in¬ dicated by the arrows in the drawings. In the drawings shaft 500 is represented in one of the many positions assumed during rotation. Toothed cogs 513, 514, 515, 516. These are cylindrical cogs with helical teeth of constant primitive radius. They are the same as those used in con¬ struction. The value of the module of their teeth and the value in degrees of the inclination of the latter (see the explanations for cog 441), are common to those of the other cogs of the kinematic chain, that is ' 413, 441, 513, 514, 515, 516, 517, 518, 519. These cogs are filleted to shaft 500, with which they share the operational phases. In the drawings they are represented in ' one of the many positions assumed during rotation. Toothed cogs 517. 518, 519. These are cylindrical cogs with helical teeth; of variable primitive radius. The value of the .nodule of their teeth and the value in degrees of. the inclination of the latter (see the explanations for cog 441) , are common to those of the other cogs of the kinematic chain, that is 413, 441, 513, 514, 515, 516, 517, 518, 519. These cogs are filleted to shaft 500, with which they share the operational phases. The particular characteristics of these cogs is the raised summit of the teeth 520, their division into sectors as a function of the primitive radius and their thifckness taken in the direction of the rotational axis. - Raised summit. This serves to enable the realisation of the project interaxis between cog 441 and cogs 517, 518, 519, when the former engages one of the latter, through the support of the base of the tooth vane 442 and the external surface of the summit 520. The value of the sum mit with respect to the teeth of cogs 513, 514, 515, 516 is equivalent to the play between the peak of.the teeth of the cogs cited and the surface 442 of the base of the tooth vane of cog 441. In sectors 1 and 3 in which the teeth are in common with the constant radius cogs, the summit con ¬ tacts the summit of the teeth of the latter to facilitate the sliding of cog 441. The external surface of the summit belongs to a surface composed of generators parallel to the axis of rotation of the wheels; it must also be smooth. - Division into sectors. These cogs may be considered as djL vided into four sectors. The first is from radius 127 to 130, the second from 130 to 129, the third from"129 to 128, and the fourth from 128 to 127. In the first sector the pri mitive radius is constant and is equal to that of the adja¬ cent larger constant radius cog. Its teeth are a prolonga tion of those of the said adjacent cog. Irf the second se . c tor the primitive radius is varied. Its- law of variation and the number of teeth, besides kinematic and dynamic re quirements, should be chosen in such a mannner as to have the same pace and thus the same module of the teeth of the first and third sectors. In the third sector the primitive radius is constant and is equal to that of the smaller ad¬ jacent constant radius cog. Its teeth are a prolongation of the said adjacent cog. In the fourth sector the primitive radius is varied. Its law of variation and the number of teeth, besides kinematic and dynamic requirements, should be chosen in such a manner as to have the same pace and ' thus the same module of the teeth of the first and third - 45 sectors. The trajectory generated by the varied primitive radius in the second and fourth sectors, must give place to a form which renders the speed variation due to a chan ge of ratio gradual to a maximum,with reduced angular ac¬ celeration and thus low inertial moment in the rotating masses. - Thickness of the cog. This is linked to the behaviour of cams 507 and 508 for their longitudinal profile in their second sector. This behaviour together with that of the first and third give the law of movement according to which trolley 423 will move when the ratio changes. In the case depicted cams 507 and 508 in their second sector do not produce longitudinal movement, so the necessary and sufficient thickness of the cog is that of cog 441 plus the play necessary between 441 and that adjacent in di¬ rection 121 so that there shall be no friction. In the case in which in their second sectos cams 507 and 508 produce a longitudinal movement, the necessary and suf- ficient ' thickness of the cog is that stated, plus the entity or the longitudinal movement. These cogs are tied to shaft 500 with which they share the operational phases. In the drawings cogs 517,- 518, 519 are represented in one of the many positions assumed during rotation, in the phasing required with respect to the rotating cam group. - 4G Joint 525 This is coupling for the movement output by the changer. Shaft 500 may be extended also through ' he cam group to the outside, to accept a coupling joint. The movement output by the changer may thus be utilised at both extremes of shaft 500. These joints are tied to shaft with which they share the operational phases. In the drawings joint 525 is depicted in one of the many positions assumed during rotation. Rotating cam group 505, 506, 507, 508 This may be imagined divided in two by the plane of trace 126. Cams 505 and 507 on one side effect changes in dire.c tion 120 In increased ratios 506 and 508 on the other in direction 121 in reduced ratios. Cams 505 and 506 consist of a spiral channelling with a saw tooth section; the centre of the spiral is oncthe axis of shaft 500. The base of the section of the channelling lies on a plane perpendicular to the rotation axis, that is the axis of shaft 500. The pace of the spiral diminishes toward the outer side to disappearance at the point where there is initial contact between the cams and beaks 315 and 324. At these points the depth of the channelling is nil, as their summits belongs to conical surfaces. The profile coupled by beaks 315 and 324 is only the shoul der, in a radial sense, of the saw tooth section. A funda mental function of cams 505 and 506, besides the others described below, ' is that of engaging beaks 324 and 315 of levers 320 and 311, and bringing their slides 323 and 314 into contact with cams 507 and 508 at the beginning of their first sector. Cams 507 and 508 are fabricated from cylinders having a circular crown section and their axis coin ciding with that of shaft 500. The copied surfaces are tho se internal to the cylindr and that of the head of the crown in an axial direction; the first by beaks 32 and 325, the second by slides' 323 and 314. From a formal and functio nal point of view they may be considered as divided into four sectors: - Cam 507 The first sector from radius 134 to radius 133. The second sector from radius 133 to radius 132. The third sector from radius 132 to radius 131. The fourth sector from radius 131 to radius 134. - Cam 508 The first sector from radius 132 to radius 131. The second sector from radius 131 to radius 134. The third sector from radius 134 to radius 133. The fourth sector from radius 133 to radius 132. A fundamental function of cams 507 and 508, besides the others described below, is that of commanding the longi- tudinal movements in directions 120 and 121 of trolley 423, in phase with the sectors of the variable primitive radius cogs 517, 518, 51 ' 9 . The radial proflie.-, of cams 07" and 508 (in the fourth sector only) and above all longitudinal one, besides resolving geometric and kinematic requirements, it must take account to the highest degree of dynamic problems, due to the forces which come about, in function of the acce lerations impressed on the masses involved in linear and oscillatory movements for ratio changes. The rotating cam group 505, 506, 507, 508 is linked to shaft 500 with which it shares the functional phases. In the drawings the semi groups 505, 506, 507 and 508 are depicted in one of the many positions assumed during rota¬ tion with respect to the variable radius cogs 517, 518, 519. 6 - Torsion spring bar complex This has the scope of applying torque force to support 418 in direction 123 which must be, in all operational phases of the changer, superior to any opposing torque which might occur. The: applied torque has the purpose of maintaining cog 441 always pressed against the cogs of the stepped co ne on shaft 500, ith which it engages without there ever being variations in the values of the expected interaxis. Forces contrary to that applied, tending to separate 441 from the cogs of the stepped cone, may be caused by the transmitted driving torque. For example the relative posi - 49 - tion between the shaft 400 and 500, as a function of the rev volving arm of 441, of its diameter and its direction of ro tation, causes a torque which may act on support 418 in di¬ rection 123 or 122. For this'to be favourable the dimensions and the rotation directions of the cited elements should be suitably chosen. The complex basically consists of round spring bar 600,preloaded during assembly, and of the cylin drical toothed wheel with straight modular teeth 601. With regard to the operation, the component elements of the complex are tied to each other, so the common operational phases are indicated next : 1 - Rest phase; no motion animates the complex. 2 - Phase of oscillatory rotation in direction 122 of cog 601 and the extremity of round 600 filleted thereto. 3 - Phase of oscillatory rotation in direction 123 of cog 601 and the extremity of round 600 filleted thereto. In the drawings the torsion spring bar complex is illu¬ strated in the position which it assumes when 441 engages 16. Besides the solution described and illustrated in the dra wings, other are possible with analogous results. One is described with a helical spring acting in compression. To function the spring must rest one extremity on arm 43 where a support must be fitted; the other extremity must rest on the vertical wall of casing 100. Here a support must be fitted, which although linked to the casing, must be free to be dragged by the trolley, with a shaft which allows it to rotate, along a directrix parallel to that of the mo¬ vement of the same, that is the axis of shaft 400. This avoids unnecessary extension and compression of the spring due exclu sively to the disalignment of the supports of its extremities. The supports may be of an articulated type, in order to com pensate the alterations of parallelism of the bases due to the movements of arm 434. The spring is installed pre-loaded so that it provides the thrust necessary in all conditions. The operational phases of this type of spring are as follows : 1 - Rest phase; no movement animates the complex. 2 - Phase of oscillatory rotation in direction 123 of trol- ley 423- The spring extends by the increase in distance between arm 434 and the vertical wall of casing 100. 3 - Phase of oscillatory rotation in direction 122 of trol¬ ley 423. The spring is compressed by the decrease in d . i stance between arm 34 and the vertical wall of casing 100. 7 - Trolley blocking complex This has the purpose of blocking trolley 423 when cog 441 -has stable engagement with one of the cogs 513, 514, 515, 516. It essentially consists of arm 700 and spring 704. Arm 700 This may only have an oscillatory movement around pin 701. Its operational phases are as follows: 1 - Rest phase; the arm has no movement. Tooth 703 is sta tionary in one of the lodgings 429, 430, 431, 432. 2 - Phase of oscillatory rotation in direction 123; Tooth 703 exits completely from one of the lodgings 429, 430, 431, 432. 3 - Phase of oscillatory rotation in direction 122; inter¬ mediate return movement. Tooth»«703 rests on the exter¬ nal surface of trolley 423- 4- - Phase of oscillatory rotation in direction 122; defini tive return movement. Tooth 703 again is inserted into one of the lodgings 429, 430, 431, 432. In the drawings arm 700 is represented in its rest position. Spring 704 This is pre-loaded and lodges between the upper plate of casing and the extremity of arm 700. Its operational phases are as follows : 1 - Rest phase; there is no movement. 2 - Phase of compression in direction 118. 3 - Phase of partial extension In direction 119. 4 - Phase of complete extension in direction 119. In the drawings spring 704 is represented in a condition of rest. 8 - Safety devices These devices serve to impede incorrect commands from cau sing malfunction and damage to the changer. They essential ly consists of cursor 800 with spring 804 and arm 805. Cursor 800 This may be actived only by a movement of longitudinal translation in clrections 120 and 121. It serves to impede incorrect simultaneous activation of arms 312 and 321, which would cause the movement of levers 311 and 320, which would push trolley 423 in the opposite directions 120 and 121. This might occur in the time lapse in which one of the two beaks 315 or 324 runs along cam 506 or 505; during which,as there is no axial movement of bar 300, that of the two arms ° 312 or 321 not yet activated may so be, as they are not yet employed in channel 111. Cursor 800 must block that of the two arms 312 or 321 which is not yet active, before the beak 315 or 324 of that activated, is engaged ir_-the respective cam 506 or 505. Its operational phases are as follows : 5 1 - Rest phase; there are no movements. 2 - Phase of outgoing longitudinal sliding in direction 121. This block arm 312 when arm 321 is activated. 3 - Phase of return longitudinal sliding in direction 120. - Phase of outgoing longitudinal sliding in direction 120. This block'arm 321 when arm 312 is activated. 5 - Phase of return longitudinal sliding in direction 121. In the drawings cursor 800 is represented in its rest con¬ dition. Spring 804 This is pre-loaded and blocked in its lodging by elastic ring 803; supports with compression and extension along its axis the movements of cursor 800. Its operation may be de¬ fined as follows : 1 - Rest phase; the spring is extended and rests on its mounts. It fixes the rest position of cursor 800. 2 - Phase of compression in direction 121. This coincides with the second phase of cursor 800. 3 - Phase of extensio in direction 120. This coincides with the third phase of cursor 800. 4 - Phase of compression in direction 120. This coincides with the fourth phase of cursor 800. 5 - Phase of extension in direction 121. This coincides with the fifth phase of cursor 800. In the drawings spring 804 is represented inIts rest condition. Arm 805 This moves only in oscillation around the axis of support 418, to chich it is strictly linked. Its phases of opera tion coincide with those of support 418, to which refe¬ rence should be made. It serves to impede, when cog 441 engages wheels 513 and 516, that control stick 200 may command movement of trolley in an incorrect direction. Precisely, when 441 engages 516, it blocks control stick 200 in direction 117, to impede commands (via 210 and 312) to lever 311, which' would push the trolley in direction 121; when 441 engages 513, it blocks control stick 200 in direction 116, to impede commands (via 210 and 321) to lever 320, which would push the trolley in direction 120. Arm 805 acts through.its extremity 806 inserted into slot 201 of control stick 200, which- in the two cases in exami ς nation, comes into contact with the extremity of the slot. It should be noted that: - Arm 805 is placed in the two extreme position, in its > excursion in oscillation to effect its safety role, be¬ fore cog 441 engages cog 513 or 516, as the rotation of ° support 418 is commanded by 441 when this engages the variable radius cogs.517 or 519 in its rotation move¬ ment. This anticipation excludes all possibility of er_ ror. - The force with which arm 805 opposes the activation of control stick 200 in incorrect directions is : - In direction 117, when cog 441 engages 516, consisting of the opposition of rest 101 which contrasts tooth 433 of trolley 423. - In direction 116, when cog 441 engages 513, exercised by torsion spring bar which with cog 601 applies a grea¬ ter opposing torque to support 418. In the drawings it is presented in the position in which, as 441 engages 516, arm 805 has Its extremity resting in slot 201, to obstruct movement of control .stick 200 in di. rection 117. _ - 55 - General operation of the speed changer.: To render the description ordered, the general operation of the speed changer is considered divided into the fol¬ lowing hypotheses : - 1st hypothesis; the changer is in a static condition. - 2nd hypothesis; the changer is. in movement and is wor king on a fixed reduction ratio. - 3rd hypothesis; the changer is in movement and is ef¬ fecting a change in an increasing ratio. - 4th hypothesis; the changer is in movement and in ef¬ fecting a change in a decreasing ratio. - 5th hypothesis; particular manoeuvres of control stick 200. Reference is made to the elementary operational phases illustrated. 1st operational hypothesis; the changer is in a static condition The case in which the rotational speed of main shaft 400 is zero is considered; zero is thus also the rotation speed of the other elements of the kinematic chain, that is of pionio 413, of the idling satellite cog 441, of the toothed cog cone 513, 514, 515, 516, 517, 518, 519, and thus of the secondary shaft 500. All the other elements of the speed changer involved in speed changes must be in their rest positions. Imagine that the stop has come about after the completion of a change of ratio. Control stick 200 may however be activated; in both di¬ rections 116 and 117, if arm ' 805, as a consequence of the position of cog 441, occupies an intermediate position, in only one of the two directions if cog 441 is engaged with cog 513 or 516 (in the case in the .drawings, 441 is enga ged with 516, arm 805 occupies an extreme position, thus movement of control stick 200 is obstructed in direction 117). If control stick 200 were to be' activated in direction 116, he following succession of phases would occur : - Control stick 200 phase 2, spring 206 phase 2,"lever 210 phase 2, action lever 320 phase 2, spring.325 phase 2, cursor 800 phase 2, spring 804 phase 2. Xhat happens with this succession of phases is explained in the third operational hypothesis. Here it is specified that given the force of spring 325, the static condition and the conformation of cam 505 , the engagement of the latter with beak 324 does not occur. As soon as the acti vation force in direction 116 is removed from control stick 200, the following succession of phases would oc¬ cur: - spring 206 phase 3, control stick 200 phase 3, le ver 210 phase 3, spring 325 phase 4, action lever 320 phase 6, spring 804 phase 3, cursor 800 phase 3. Here too for an explanation see the description of the third operationl hypothesis . Practically all the kinematic chain activated returns to the rest condition. If control stick 200 were to be activated-in direction 117 (when not obstructed by arm 805), the result would _> be the same (no engagement) . The kinematic chain which would be involved would be as follows : - To activate control stick 200 phase 4, spring 206 phase 4, lever 210 phase 4, action lever 311 phase 2, spring 316 pha 10 se 2, cursor 800 phase 4, spring 804 phase 4. For relea se control stick 200 phase 5, spring 206 phase 5, lever 210 phase 5, action lever 311 phase 6, spring 316 pha¬ se , cursor 800 phase 5 , spring 804 phase 5 • 2nd operational hypothesis; the changer is in movement 15 and is working on a fixed reduction ratio. This is the fundamental working condition of the changer, where it is to be found working for the majority of its time in almost all foreseeable applications. The motion 0 enters the changer through the preliminary reduction ra tio 403 , 406 or ' directly onto the main shaft 400 via an external joint. The rotation speed of shaft 400, in the direction indicated in the drawings, has thus a value differing from zero.The_.motion then passes from pinion _r 413 to the idling cog 441. This stably engages with one of the cogs 513, 514, 515, 516 wich establish the ratios of the changer. Shaft 500 transmits the reduced motion to . joint 525, which can transmit it to the successive kinema tisms. Cog 441 is" blocked in its movements of revolution and longitudinal translation. The blockage of revolutional c movement is linked to the realisation of the projected in teraxis between cog 441 and cogs 513, 514, 515, 516; this is obtained through ' the contrast between tooth 443 and the rests 101, 102, 103, 104. The force which maintains tooth and rests in contrast is exercised by torsion bar ° spring 600, through cog 601, support 418 and trolley 423. Tooth 703 of arm 700-blocks longitudinal translation mo¬ vement of cog 441 by inserting itself into lodgings 429, 430, 431, 432 on trolley 423- All the elemeflϊs involved in the change- of ratio are in their rest positions. The 5 direction of rotation of the axes of the changer may not be altered. The reduction (or multiplication) ratio is calculated with the usual criteria for toothed gearing. Note should be made of the high yield of a changer thus 0 constructed in these working conditions, due to the li¬ mited internal attrition, thanks to the limited number of engaging cogs and the reduced number of bearings pre sent. In this condition the changer may be stopped and restarted without causing problems. In the drawings cog -> 441 is illustrated engaged with cog 516. - 59 - 3rd operational hypothesis; the changer is in movement (see second hypothesis). An increase in ratio is effected. As initial condition, all the elements employed in changes of ratio are at rest, and -cbg 441 is blocked both in.revo- lution and in longitudinal translation as explained in the previous hypothesis. As was seen this is a fixed ratio chan ger, so to change ratio it is neces,s,ary to pass from one to another of the ratios inserted. The idling satellite cog 441, must, that is, pass from one cog of the set 513, 514, 515, 516 on the stepped cone to another. The analysis in this case is of a change of ratio- with trolley 423 which moves in direction 120; more precisely, since in the dra¬ wings cog 441 is illustrated engaged with cog~5l6, the ob servation is of the functioning of the changer when 441 is caused to engage cog 515- In the operative reality, to know which ratio is functioning, that is to say where cog 441 is engaged,the changer is easily fitted with an accessory of electrical or mechanical nature which, as a function of the position of trolley 423 or support .18, transfers this data in an explicit manner to the .outside. Commands are imparted only by means of control stick 200. This may be moved in two directions only, 116 and 117. Given the characteristics of the changer, 116 corresponds to a di- splace ent of trolley 423 in direction 120, that is to say the changer passes from minor ro major ratios; 117 cor- respondes to a displacement ot trolley' ' 423 in direction 121, that is to say the changer- asses from major to mi nor ratios. It should be noted that the position of troJL ley 423, at which cog 441 engages cog 516, is one of its extreme positions in oscillatory excursion which is com¬ mon to support 418 and arm 805; this latter in this posl. tion, with its extremity 806 in slot 201, inhibits con- trol stick 200 movement in direction 117, exercising its safety function to avoid incorrect movement of the con¬ trol stick. In addition, given the semi automatic natu¬ re of the changer, it effects alone the manoeuvres ne¬ cessary to a change of ratio. Outside commands need only manifest the desire to shift, distinguishingJoihether the order is for an increase or decrease in ratio. Control stick 200 is moved in direction 116 to the end of its run. The following succession of phases is started :- control stich phase 2, spring 206 phase 2, lever 210 phase 2, action lever 320 phase 2, spring 325 phase 2, cursor 800 phase 2, spring 804 phase 2. Practically the following happens : having moved control stick 200, le¬ ver 210 rotates in direction 125 pushing arm 321 in di¬ rection 116 with protuberance 213; -this causes action le ver 320 to rotate in direction 122 and beak 324 comes in to contact with cam 505; before beak 324 touches cam 505, cursor 800, pushed by arm 321, moves in direction 121 to block arm 312. Cam 505, being in rotation with shaft 500 according to the arrows ih the drawings, gently enga ges beak 324. This gentle engagement is due to :- the spi ral channelling of cam 505 *' at the external point of con- tact with beak 324, is practically parallel to the di¬ rection of the speed of rotation at that point; at the point of contact the height of the, channelling is zero and is increased extremely gradually; at the moment of engagement, before beak 324 stabilises itself in the channelling, this may have displacement in directions 120 and 121, permitted by bar 300 with the compression and extension of spring 307, which facilitate its inser_ tion. The pre-loaded force of spring 307 doe ' s not permit arm 321, pushed by spring 804 through cursor 800, to move bar 300. Once beak 324 has engaged, control stick 200 is released; its release starts the following phases : - spring 206 phase 3, control stick 200 phase 3, lever 210 phase 3. In synthesis control stick 200 and lever 210 return to their rest condition. In the meantime be_._ 324, engaged to cam 505, provokes the following succession of phases :- action lever 320 phase 3, spring 325 phase 3. In effect beak 324 runs along part of rhe channelling of cam 505, engaging itself in the saw tooth channelling to the extent that release becomes impossible. Beak 324 continues along the chan nelllng giving rise to the following succession of pha - 62 - ses : - action lever 320 phase 4, bar 300 phase 2, arm 309 phase 2, arm 310 phase 2, arm 328 phase 2, spring 330 pha se 2, arm 700 phase __ ■ , sυ-ring 704 phase 2. In this phase effectively beak 324 completss—its run along the spiral channelling of can 505 and presents itself at the begin¬ ning of the first sector of cam 507, indicated by radius 134, with slide 323- Slot 319 of action lever 320 arrives at rest on tooth 318, dragging bar 300.-in rotation in di rection 122. Tooth 313 does not interfere with lever 311 finding sufficient play for displacement in this direction in slot 317. Arm 310 raises arm 700 causing tooth 703 to exit lodgLng 429; before this operation is completed, arm 309 inserts itself into lodging 425, thus_.-not permit^ ting, thanks to the geometric forms of the elements in¬ volved, any movement to trolley 423 in direction 120 or 121 , Λ..Ϊ1328 compresses spring 330. In this situation trolley 423 is held in the longitudinal position by bar 300. The forces discharged on trolley 423 in direction 120.or 121 through cog 441, due to the heljL cal toothing and the torque transmitted, must be balanced by spring 30 thanks to its pre-loaded charge. This impe des bar 300 and thus trolley 423 with cog 441 from ungui ded movement in direction 120 or 121, which would be dan gerous to the integrity of the cogs. Before ' -contuining the functional description oV the chan ger it is necessary to clarify the link between the sec ¬ tors of cams 507 and 508, and ' those of. the variable ra¬ dius cogs 517, 518", 519; the first sector of cam 507 is equal in amplitude to the- " first of the variable radius cogs, the second to the second, the third and the fourth to the fourth, while the first' sector of ca 508 is equal in amplitude to the ' third of the variable radius cogs, the second to the fourth, the third to the first and the fourth to the second. In the specific case of the drawing as the sector of the variable radius cogs are all 90 * , all the sectors of cams 507 an ' 508 are also 90 ° ; thus the beginning of the first sector 507 is exactly 180 * out . of phase with the beginning of the first sector of 508, thus the separation rays of the sectors of the two cams are coincident. The phasing of the sectors of cams 507 and 508 with re¬ spect to the sectors of the variable radius cogs is as follows :- when radius 134 of the beginning of the first sector of cam 507 passes through the centre of beak 324 and slide 323, radius 127 of the beginning of the first sec. tor of the variable radius cogs coincides with the ad¬ joining 135, while when radius 132 of the beginning of the first sector of cam 508 passes through the centre of beak 315 and slide 314, radius 129 of the beginning of the third sector of the variable radius cogs coincides with the adjoining 135. Now beak 324 and slide 323 copy the first three sectors respectively of the radial profile and the longitudinal profile of cam 507 in rotation. The following succession of phases starts :- action lever 320 phase 7, bar 300 pha- - se 4, arm 309 phase 4, arm 310 phase 4, spring 307 phase 2, piston 339 phase 2,- arm 700 phase 3 and phase 4, spring 704 phases 3 and 4, cursor 800 phase 3, spring 804 phase 3, trolley 423 phases 2 and 5, cog 441 phases 4 and 5, support 418 phase 3, arm 805 phase 3, spring 600 phase 2. In effect, as there are no variations in radius in the ra dial profile of the first three sectors, beak 324 through arm 332 blocks the rotation of action lever 320 and bar 300; while the longitudinal profile for these three sec. tors provokes a movement of action lever 320, bar 300 etc. in direction 120 in the measure necessary to cause cog 441 to engage 515. Following slide 323 in copying sector by sector, cam 507 what happens is easily understood. The first sector commences when radius 134 passes in co£ respondence to the centre of beak 324 and slide 323; it finishes when radius 133 passes there. The displacement of the action lever 320 etc., is equal to that necessary to bring cog 441 from engagement with 516 to engagement with 519- In this longitudinal displacement in direction 120 spring 307 is compressed. Arm 321, moving in direction 120 in channel 114, permits spring 804 to extend ahd press cursor 800 in the same direction toward its rest position. Simultaneously arm 312 which moves in the same direction, before cursor 800 frees it,-6 " ήters channel 111 which again precludes it from possible activation by lever 210. Piston 339 invades chamber 342 without-encountering resistance (see shock absorption plant operation). Arm 310 abandons arm 700 (phase 3) which pushed by spring 704 (phase 3) bring tooth 703 into contact with the surface of trolley 423 in movement, where it slides. Arm 309 drags trolley 423 (phase 2) with cog 441 (phase.5) and tooth 433. Given the phasing between cam 507 and the variable radius cogs, when radius 13 passes through the centre of=beak 324 and slide 323, and radius 127 (initial radius.of the first sec. tor of the variable radius cogs) passes on the adjoining 135, cog 141 begins to move in direction 120 on cog 519. The displacement provoked by the first sector of cam 507 causes cog 441 to completely engage 519. The transfer is completed with the passage of radius 130 (final radius of the first sector of the variable radius cogs) on the adjoining 135. This movement is made possible because in the first sector variable radius cog 519 has its teeth and primitive radius in common with the constant radius cog 516. There is no problem with regard to the movement between 441 and pinion 413. With regard to tooth 433, this abandons rest 101; before this activity is completed, the interaxis between 441 and 519 is entrusted to the sup ¬ port between vane 442 of the teeth of cog 441 and raised summit 520 of the teeth of cog 519. This superelevation 520 is tapered at the beginning towards 516 throughout the first sector to avoid hiccups in entering movement. The second sector of cam 507 commences when radius 133 passes in correspondence to the centre of beak 324 and slide 323; it finishes when radius 132 passes here. This may or may not produce longitudinal movement In direction 120; it depend on the' speed and' acceleration diagram re¬ quired for the masses involved in linear displacements in the changing of ratios. In the case of the " drawing it does not produce movement so the thickness of 519 is that represented. In the case where movement is produced, the thickness of the variable radius cogs 517, 518, 519 must be greater as indicated in the chapter on the function of the components at the entry which refers thereto. On the other hand all the other elements involved in this variation would proportionally change their longitudinal dimensions. In any case while slide 3 3 runs along the second sector of cam 507, cog 441 engages only the se¬ cond sector of cog 519; the sector from 130 to 129 pas_ ses on 135- As the second sector of cog 519 is of varia¬ ble radius, in this case decreasing, cog 441 (phase 4) has 123 as its direction of movement, which causes both trolley 423 (phase 5), support '418 and arm 805 to rotate in direction 123. The latter, moving, restores liberty of movement in direction 117 to'the control stick 200. Tooth 703 again drags on the outside of trolley 423. Arm 309 does not interfere with the rotation of trolley 423, as lodging 425 (and 426,' 427, 428) is constructed with the play necessary there to. The interaxis between 441 and 519 in this sector is assured by the support of vane 442 of the teeh of cog 441 on summit 520 of the teeth of 519- The contact is always guaranteed by bar spring 600 which, through wheel 601, applies the required torque to sup¬ port 418 (also during its rotation) and thus -to trolley 423 which causes cog 441 to press with the required for¬ ce against 519 (during the revolution movement of cog 441). When radius 129 passes on the adjoining 135, tooth . 433 in its rotation reaches and touches rest 102, on which it settles to provide the new interaxis between cogs 441 and 515. If cam 507 in its second sector produces a di¬ splacement in direction 120, this, through slide 323 and arm 322 of action lever 320, is added to that of the first sector being transmitted to the arm 321, to spring 307, to arm 312, to piston 339,to arm 310, to arm 309, to trolley 423, to cog 441 and tooth 433- The latter three effect.the movement in direction 120 simultaneously to the rotation in direction 123. Naturally, as stated above, this movement regards, besides cam 507 in its second sec ¬ tor, all the other " elements involved altering their dimen sions, changer casing box included. The third sector starts when radius 132 passes in correspondence to the centre of beak 324 and slide 323; it finis ' hes when radius 131 passes there. The displacement of action lever 320 etc., is equal to that necessary to move cog 441 from engagement with cog 519 into engagement with cog 515, completing phase 4 of bar 300. In this longitudinal displacement in direction 120 spring 307 (end phase 2) finishes -its compression, arm 312 (end phase 7) finishes running along channel 111 without reaching the rest condition position occuped " by arm 321. Piston 339 (end phase 2) reaches the end of its run into chamber 342, arm 310 (end phase 4) reaches the end of its run, arm 309 (end phase 4) drags trolley 423 (end phase 2) to the end of its run with cog 441 (end phase 5) and tooth 33; tooth 703 of arm 700 (phase 4), pushed by spring 704 (phase 4) enters lodging 430. Given the phasing between cam 507 and the variableradius cogs, when radius 132 pas. ses through the centre of beak 324 and slide 323, and ra dius 129 (initial radius of the third sector of the varia. ble radius cogs) passes the adjoining 135, cog 441 begins to engage cog 515 moving in direction 120. The displace¬ ment provoked by the third sector of cam 507 causes cog 441 to completely engage cog 516. The transfer is completed by the passage of radius 128 (end radius of the third sector of the variable radius cogs) on the adjoining 135- This move ent is rendered possible because in the third sector varia 5 ble radius cog 519 has its teeth and primitive radius in common with the adjacent constant radius cog 15 • There is no problem with regard to the movement between cog 441 and pinion 413. With regard to tooth 433, it has already been stated that already at the end of the second sector it has 10 established contact with rest 102, installing the interaxis between 441 and 515; in the third sector it maintains this interaxis running on rest 102, while the base 442 of the hollow of the teeth of 441 abandon the support, of superele vation 520 of 519- In this sector too superelevation 520 15 of the teeth of 519 is tapered at the contact with the teeth of 515; this is required when 441 passes from 515 to 519 to pass on to 516. At this point beak 324 and slide 323 are following the fourth sector of cam 507, the former in ra¬ dial profile and the latter in longitudinal profile. The 2o following succession of phases initiates: - action lever 320 phases 5, 6, 8, bar 300 phases 3 and 5, arm 309 phases 3 and 5, arm 310 phases 3 and 5, spring 307 phase 3, spring 325 phase 4, arm 328 phase 3, spring 330 phase 3, piston 339 phase 3- In practice the following occurs. Cam 507 oc- oc . cupies the fourth sector only partially with an appendix 25 whose radial profile has radius in incr en , while its Ion gitudinal profile produces no movement of slide 323 in di¬ rections 120 or 121-.- Thus beak 324 provokes of action lever 320 (phase 5) in direction 123, pushed by spring 330, through arm 328, bar 300 (phase 3), tooth 318. The extremity of arm 5 322, before beak 324 terminates-its copy of the appendix of cam 507, rises onto plane 112. As soon as the appendix of cam 507 terminates, spring 330, through etc. (as above), further pushes arm 322 to run along plane 112, instantly 0 bringing beak 324 and slide 323 out of reach of cam 507. To here this rotation in direction 123 of action lever 320 (phase 5) with its arms 321 and 322 is effected together with bar 300 (phase 3), its arms 310 (phase 3_ and 309 (phase 3), where the latter has exited lodging 425, its arm 5 328 which has returned to placing; bar 300, arm 310, arm 309, arm 328 and spring 330 have returned to their oscil¬ latory rest condition. No longer retained by plane 112 which has been completely passed over, arm 322 permits o spring 307 to extend pushing bar 300 (phase 5) in direc_ tion 121; the same may be effected by spring 325 which causes action lever 320 (phase 6) to firther rotate in direction 123 causing it to bring arm 322 to rest against 110. These movements come about simultaneously so spring 307 carries bar 300 back to the longitudinal rest cond.i tion, thus arm 310 (phase 5) returns under arm 700, arm 309 (phase 5) comes in front of lodging 426, piston 339 (see separate section on functioning) returns to the cen tral position, action lever 320 (phase 8) returns to the initial rest condition.. In-this return journey in direction 121 arm 322 is controlled by guides 108 and 110, to ascer tain that arm 321 is correctly positioned an .that beak 324 does not interfere with cam 505 •• Arm 312 once again runs in channel 111 in direction 121 returning to its rest position; this tie has the dual function of impeding in- correct activation of lever 311, and of blocking, in the effected excursions in directions 120 and 121, interferen ce between arm 313 (together with beak 315 and slide 314) and disk 504, of the cam complex, even in cases of imper feet functioning of spring 316. All the elements involved in the change of ratio have returned to their initial rest condition, ready for a new operation.A changer stop and thus the interruption of change operations would cause no ' functional problem; the operation is completed when the changer is restarted. The duration of the ratio change operation is linked to the speed of rotation of shaft 500; it will thus be greater for the minor ratios and lesser for the major ratios. The entrance ratio (cogs 403 and 406, as drawn, or inverted) among other factors would permit alteration of this duration. 4th operational hypothesis; the changer is in movement. A change is effected in a decreasing ratio. It is desired that the idling satellite wheel 441 should pass from engagement with 515 to engagement with 516; trol. ley 423 must move in'direction 121. The complete succession of phase required to obtain..this aim is listed. It is con- sidered unproductive to add as in the third hypothesis an explanation of the phases. Comprehension may be facilited by utilising the explanations of the third hypothesis as a format, and, naturally, the drawings for reference. The initial condition is as explained in the third hypothesis. Control stick is caused to run in direction 117 to its term! nus. The following succession of hases starts :- Control stick 200 phase 4, spring 206 phase 4, lever 210 phase 4, action lever 311 phase 2, spring 316 phase 2, -eursor 800 phase 4; spring 804 phase 4. Cam 506 gently . engages beak 315- Control stick 200 is released and starts the follo¬ wing phases :- spring 206 phase 5, control stick 200 pha. se 5, lever 210 phase 5. Meanwhile beak 315, engaged to cam 506, provokes the following succession of phases:- action lever 311 phase 3, spring 316 phase 3. Beak 315 continues to run in the channelling causi__g_the follo¬ wing succession of phases: - action lever 311 phase 4, bar 300 phase 2, arm 309 phase 2, arm 310 phase 2, arm 328 phase 2, spring 330 phase 2, arm 700 phase 2, spring 704 phase 2. Now beak 315 and slide 314 copy the first three sectors respectively in radial and longitudinal - 73 - profile of cam 508 in rotation. The following succession of phases commences :- action lever 311 phase 9, bar 300 phase 6, arms 309 and 310 phase 6, spring 307 phase 4, pjL ston 339 phase 4, arm 700 phases 3 and 4, spring 704 pha ses 3 and 4, cursor 800 phase 5 , spring 804 phase 5 , trojL ley 423 phases 3 and 4, cog 441 phases 3 and 6, support 418 phase 2, arm 805 phase 2, spring 600 phase 3- Note that when tooth 433 regains the support of rest 101, mo¬ ving in direction 121, it has already achieved the posi¬ tion which it will have on the rest thanks to cog 441 etc. To avoid blockages, the entrance to rest 101 (and the others 102, 103, 104) is tapered. At this point beak 315 and slide 31 are employed in following the fourth sector of cam 508, the former in the radial profile and the lat¬ ter in the longitudinal profile. The following sequence of phases commences :-action lever 311 phases 5, 6 and 10, bar 300 phases 3 and 7, arm 310 phases 3 and 7, arm 309 phases 3 and 7, spring 307 phase 5, spring 316 phase 4, arm 328 phase 3, .spring 330 phase 3, piston 339 phase 5. The change of ratio has been effected, so cog 441 is engaged to cog 516,all the elements which control the change of ratio have returned to their initial condition of rest, ready for a new operation.A changer stop and thus the in terruption of change operations would cause no functional problem; as in the third hypothesis, the operation is com pleted when the changer is restarted. 5th hypothesis; particular manoeuyres of control stick 200. Since control stick ' 200 may be activated at any time in ei. ther direction 116 or 117 (with ' the exclusion of direction lie when cog 441 engages 516, and of 116 when 441 engages 513), besides the classic cases' escribed above, in which the command is imparted when:-all the § -lements of bar 300 are in their respective absolute rest positions, it may be that an attempt is made to initiate a change of ratio when a change phase, which has started, has not been completed. The following cases are given :- - Control stick 200 continues to be pressed rafter a com mand in direction 116 or 117, or is pressed"again in the same direction and so maintained before the change ratio phase is completed. That is to say that it is desired to effect more than one change in the same direction, in in¬ crement or diminution of the ratio. Arm 321 or . 312, rela¬ tive to protuberance 213 or 212 of arm 210 which has re- mained at or has passed beyond line 136, is no longer in position having already initiated the commanded chan ge of ratio. As illustrated, action levers 311 and 320, in their 6th phase, return to their oscillatory rotation rest position and with phases 8 and 10 return to their longitudinal rest positions; these two phases occur si¬ multaneously. Because springs 316 and 325 and guides 108, 109 and 110 acting on arms 313 and 322, action levers 311 and 320 are obliged to recuperate their oscillatory rest positions, before reaching the relative longitudinal rest po sitions. Thus their arms...321 " and 312 are subject to line 136 in direction 121 or 120 before reaching the position occu¬ pied by the activated protuberance 212 or 213- The contrast between arms 313 or' 322 and guides 109 or 108 does not per¬ mit arm 312 or 321 to move away from line 136, until the longitudinal position has not been perfectly regained. Given the wedge shape, the subject protuberance is thus pushed in direction 11 obliging lever 210 and control stick 200 to re turn to their rest positions. If the pressure on control stick 200 has been maintained, with all the elements in their rest conditions a new change operation is started as described in the third and fourth hypotheses. - Control stick 200 is pushed in direction 116 or 117 imme¬ diately after having been pushed in the opposite direction to obtain a change of ratio. If this command is activated before arm 312 or 321, the first in the command chain, is in rotation for phases 3 and 4 of action levers 311 or 320 on or with bar 300, the other arm 321 or 312 is still to be found in the longitudinal rest position and in the oscil. latory rotation rest position. To impede the activation by protuberances 212 or 213 of lever 210, cursor 800 operates as explained in its description above. If the command is - 76 - activated when arm 312 or 321, the first in this command chain has just begun the translation required in phases 7 and 9 of action levers 311 or 320, the other 321 or 312 may not be moved in direction -116 by protuberance 212 or 213 of lever 210 because it has already been inserted into channel 111 dragged in turn by phases 7 or 9 of action levers 311 or 320 to which it -belongs, which permits it only to transla te. If again the command is imparted when arm 312 or 321, first in the command chain, is no longer stable in its Ion . gitudinal rest position, nor can the other be struck by the protuberance 212 or 213 involved." If control stick 200 re¬ mains pressed, protuberance 212 or 213 will remain active beyond line 136. At the point at which arm 312 or 321, which is in channel 111 for phase 8 or 10 of its respective action lever 311 or 320, it will return to its longitudinal rest position, not being able to rotate in direction 122 before this is reached, it will push protuberance 212 or 213, given its wedge shape, in direction 117 to return be- hind line 136, in -.the rest condition of lever 210. Control stick 200 will be obliged to return to its central rest p. sition. Here too, if the pressure on control stick 200 has been maintained, wi ; :h all the elements in their rest con¬ ditions, e new change operation is started as described in the third and ourth hypotheses. According- to a possible variant, the speed variator descri. - 77 - bed herein has been made suitable for pedal powered vehi cles such as bicycles. Said variator is illustrated in Fig. 11. Essentially, it consists of a gear wheel cone 90, an -J_:ϊi.._ ^-ear wheel 901 and ' a pinion 902. In this case the gear wheel cone lacks wheels of varying radius since the difference in the number of- teeth of the gear wheels is a maximum of two the passage is made directly from one to the other in the sector in which the teeth almost coin cide. The idle wheel may be engaged by both the gear wheels and the pinion (which is as long- as the gear wheels) and in order to do so it is capable of oscillating and transla ting, the oscillatory movement occurring around the axis of the pinion, while the translation is parallel to the axis of the pinion and of the gear wheels, since they are all parallel the one to the other. The wheel 901 changes ■ the gear through the aforementioned two movements. With regard to the application on bycicles, the pedals will be splined to the axis tif the gear wheel cone 903, while the output of the movement for the chain ring will occur along the axis of the pinion 90 . In order to change gear it is necessary to pull the lever 905 which, by means of its shaft 906 and arm with a pin 907, enables the sle , eve 908 to slide axially. The arms 909 and 910, with their relative pins, are integral with the sleeve. The movement of the sleeve allows one of the pins to enter the bracing cross of one of the wheels 911 or 912. By engaging one or the other of these Wheels, with sleeve movements in one da. rection of the other, it is possible to achieve the rota¬ tion of the same for a certain angle. The movement of wheels 911 and " 9i2 is communicated to wheel 913 by engagement and, therefore, because they are integral with the cam wheel 914 and the other gear wheel 915- The cam wheel 914 moves the device 916, which, in turn, pulls the slide 917, leaving It free to rotate and, subsequently, the idle- wheel 901-, to which it is tied by means of the support 918, to translate. The gear wheel 915 engages the gear wheel 919-~containing the cam wheel 920, it houses the pin of arm 921 which then controls the oscillation of the sleeve 922, of the slide 917, of the support 918 of the idle wheel 901 in its oscil latory movement. Given the manner in which the gear works, three safety devices have been devised. The first one prevents the idle wheel 901 from being pushed towards the outside when it engages with the first and last wheel of the gear wheel cone, when the device 916 brings the idle wheel 901 in the extreme positions its tooth 923 strikes the teeth 924 and 925, thus displacing the bar 926, such a displa cement,, by means of teeth 927 and 928 and of the arm 929, provided with a pin, causes the lever to return to the neutral position, thus preventing that the entire mecha nism be forced. The second device prevents the functioning of the sleeve 908 when the arms-with pins 909 and 910 are not yet in the right position, it mak.esvsure that the movement is completed before the pins of arms 909 and 910 enter the » bracing crosses of wheels.911 and 912 and that during the entrance the movement becomes irreversible. This is achieved by sectors 930 and 931; with the blade fixed to the frame 932. The thir.d device establishes that standstill position of the elements enabling the change of gears, this is taken care of by the small sliding cy¬ linder 933, interlocked with a pressure spring which en ters the holes 93 of the gear wheel 911 with its cone- shaped point. Construction of the speed changer The originality of the continuous fixed ratio speed chan ger which is the subject of the present invention, rests essentially on its architecture and its functional cha¬ racteristics.It was not therefore considered necessary to treat in the description all those problems which are the subject of a specific executive project. This is be. cause the solution from time to time of the problems which will arise in the executive planning for the most varied applications, will not condition the possibility of constructing the speed changer as invented, in relation to. its architecture and functionality. Thus, as mentioned else, where in this document, the drawings, while remaining plau sible, are intentionally schematic. The forms do not result from structural, constructional, ' or aesthetic, analyses, etc., these are all problems which must be faced in real construe, tion and are part and parcel of normal professional expe¬ rience. Thus the problems of machining the parts, material 0 type and quality, assembly and disassembly, maintenance, lubrification, equilibration of static and dynamic masses, etc., have all been Ignored. Naturally the form and the construction details may vary depending on the requirements of the practical application, 5 without however leaving the environment of this invention. Q 5

Claims: - - C L A I M S 1. A fixed ratio stepless speed change gear consisting of: the cylindrical varying cone distance gear ωheels 517 518, 519, interposed between the cylindrical fixed cone distance gear uiheels 513, 514, 515, 516, in the stepped cone, in order to alloω the idle satellite gear ωheel 441 to pass from one to the other of the latter wheels 513, 514, 515, 516 in conditions of coπtϊπuous engagement. 2. A fixed ratio stepless speed change gear,according to the foregoing claim, characterized by the fact that the bottom of the teeth space 442 and the angle of incli¬ nation of the teeth of the idle satellite gear ωheel 441 are of particular significance, in order to achieve the design value αf the axle-base between the idle satellite gear ωheel 441 and the varying cone distance gear ωheels 517,518 and 519. 3. A fixed ratio stepless speed change gear, according to the foregoing claims, consisting αf: tωo radial drive oam ωheels 505 and 506, for the hααkiπg, insertion, rotation and timing of the drive levers 311, 32D (by means of the relative arms 313, 322 ) . 4. A fixed ratio stepless speed change gear, according to the foregoing claims, consisting αf : tωo radial and longi¬ tudinal drive can ωheels 507, 508, for the longitudinal shifting and the rotation of the drive levers 311, 320 (by means of the relative arms 313, 322 ). 5. A fixed ratio stepless speed change gear, according tD the foregoing claims, consisting of: an elastic unit 600-605, capable of pressing the idle satellite gear wheel 441 against the stepped cone of gear wheels 513- 519, ωith the necessary strength . 6. A fixed ratio stepless speed change gear, according to the foregoing claims, consisting of : a lacking unit 700-704 for the longitudinal displacement of the carriage 423 . 7. A fixed ratio stepless speed change gear, according to the foregoing claims, consisting of: a safety device 800-804 preventing the contemporary working of the tωα drive levers 311, 320 . 8. A fixed ratio stepless speed change gear, according to the foregoing claims, consisting of: a safety device 805, 806, preventing the idle satellite gear wheel 441 from moving beyond the first 513 and the last 516 wheels of the fixed cone distance gear uheels 513-519 . 9. A fixed ratio stepless speed change.gear, according to the foregoing claims, consisting of : a control rod unit 200 — 214, for communicating gear change commands . 10. A fixed ratio stepless speed change gear, according to the foregoing claims, consisting of: one (or two) pushing bars 300, the task πf which is to disengage the car¬ riage 423 and to push it in the right direction for the re¬ quired movement, in synchrony with the rotation of the stepped cone of gear wheels 513 - 519 . 11. A fixed ratio stepless speed change gear,according to the foregoing claims, consisting of: two drive levers 311, 320, one for each of the carriage's 423 directions of the movement., so that, after having received the gear change command from the control rod unit 200 - 214, they may cπpy the profile of the cam wheels 505, 506, 507, 508 and may operate the pushing bar (s) 300 . 12. A fixed ratio stepless speed change gear, according to the foregoing claims, consisting of: a dampening system 331 - 349 for adequately braking the return run of the pushing bar(s) 300, when required by the size of its mass. 13. A fixed ratio stepless speed change gear, according to the foregoing claims, consisting of: a pawl 433 on the carriage 423 and fixed pawls 101, 102, 1037 104 for each of the speed change gears, on the box, in order to achieve the wheel-base value between the idle satellite gear ωheel 441 and the fixed cone distance gear wheels 513, 514, 515, 516 of the stepped cone of gear wheels 513 - 519 . 14. A fixed ratio stepless speed change gear,according to the foregoing claims, consisting of: fixed catches and guides located DΠ the box 108 - 115 for the ' arms 312, 313, 321, 322 of the drive levers 311, 320 . 15. A fixed ratio stepless speed change gear, according to the foregoing claims, consisting of: elements of the right shape, postion and amount 425, 426, 427, 428, located on the carriage , gripping the arm(s) 309 of the pushing bar(s) 300 and of the arm 7D3 of the locking unit 429, 430, 431, 432. All substantially as described and illustrated and for the specified purposes .

Inventors: CELANI LUIGI, CELANI, LUIGI
Applicants: CELANI LUIGI, CELANI, LUIGI
Application year: 1992
Main classification: F16H3
IPC codes: F16H3