Abstract:
An arrangement of interlinking gear assemblies to define multiple motion control input, output and directional mechanisms capable of varied speed and directional output for constant or varied input sources. The gear assemblies utilize three basic gear elements, that of bevel gear, planetary and spur gear formats to achieve a phase angle control system. Different gear element assembly applications achieve a variety of multiple use and applications including differential, directional change, speed control, compressor use, P.T.O. cycle timer and transmissions of all types including bicycles. Manual and automatic control of transmissions adjustment is dependent on relative input speed to control respective output and selective feedback.

Description:
BACKGROUND OF THE INVENTION 
     1. Technical Field 
     This device relates to gear transmissions and the like that provide for adjustable output from a power input source for useful control and output by different relative gear ratios for varied use applications based on three variable elements. 
     2. Description of Prior Art 
     Prior art devices of this type have relied on a number of different gear configurations to impart increase or decrease output ratios from a fixed or variable input source, see for example U.S. Pat. Nos. 2,547,453, 4,077,278, 4,109,551, 4,802,376, 4,916,975, 4,961,719, 5,016,493, 5,103,352, 5,116,292, 5,169,359 and 5,937,701. Also see foreign patents, Canadian Patent 989,644, French 2,638,801 and 1,323,617. 
     In applicant&#39;s own prior art U.S. Pat. Nos. 5,116,292, 5,106,493, 5,308,293 and 6,068,570 illustrate the orbital path change to determine variable output. 
     In U.S. Pat. No. 4,961,719 a variable drive transmission is disclosed using a carrier member mounted on a rotatable crank shaft with a number of spaced pivotally mounted segments that can selectively engage a central sprocket with multiple chain engagement sprockets rotatably secured to each segment. 
     In U.S. Pat. No. 2,547,453 a variable speed transmission can be seen having a rotatable cage with multiple enclosed cranks. An annular cam is engaged by the cranks from which selective output can be determined. 
     U.S. Pat. No. 4,077,278 is directed towards dividing input rotation of force into two rotational components. An output differential combines the divided components rotational force. 
     In U.S. Pat. No. 4,916,975 a torque converter is illustrated with two different gears, input is transferred through each differential gear by planetary shafts which are aligned co-axially to one another. 
     In U.S. Pat. No. 5,937,701 a variable speed change gear device is illustrated wherein rotation of forces are transferred from an input shaft to an offset housing which in turn is transferred to variable rings so that angular velocities of the variable rings are periodically varied relative the angular velocity of the offset housing. 
     In French Patent 1,323,619 a gear arrangement having a pair of interconnected differential gear segments is shown. 
     In Canadian Patent 989,644 a rotary mesh translating device is shown that uses two differentials with a self-locking rotary coupler. 
     French Patent 2,638,801 is directed towards two different mechanical power converters wherein the cage of the first differential receives input from a motor, converts same to output via inner engaging gear to input shafts of the second differential with output from the cage of the second differential determined therefrom. 
     SUMMARY OF THE INVENTION 
     A variable output transmission system having direction, engine braking, and differential output sections for enabling infinitely variable output from constant or variable input source in multiple related venue applications. 
     A motion controlled system utilizing multiple gear and cam assemblies for speed control of variable or constant input with variable or constant output from single and multiple input and output sources. Control assemblies impart manual and automatic selective output control utilizing multiple application assemblies for transportation and motor input equipment with phase angle control element based on three variable elements. 
    
    
     DESCRIPTION OF THE DRAWINGS 
     FIG. 1 is a cross-sectional view of the principle spur gear elements of the invention; 
     FIG. 2 is a graphic illustration of the principle spur gear elements of the invention; 
     FIG. 3 is a cross-sectional view of combined spur gear elements of the invention; 
     FIG. 4 is a cross-sectional view of a beveled gear phase angle control assembly of the invention; 
     FIG. 5 is a cross-sectional view of a planetary gear phase angle control assembly of the invention; 
     FIG. 6 is a cross-sectional view of a spur gear phase angle control assembly of the invention; 
     FIG. 7 is a cross-sectional view of the speed control using spur gear assembly as seen in FIG. 6 with a cam control output interconnected thereto; 
     FIG. 8 is a full plan view of a cam follower illustrated in FIG. 7; 
     FIG. 9 is a cross-sectional view of the compressor using spur gear assembly of the invention with multiple controlled output cam assemblies; 
     FIG. 10 is a graphical illustration of effective cam orbital paths; 
     FIG. 11 is a partial front plan view of a cam follower as seen in FIG. 12 of the drawings; 
     FIG. 12 is a full cross-sectional view of a CVT manual using input control cam assembly and graphic illustration of a directional control manual adjustment; 
     FIG. 13 is a cross-sectional view of a bicycle using spur gear control cam assembly with alternate cam followers; 
     FIG. 14 is a graphic illustration of the cam follower assembly as seen in FIG. 13 of the drawings; 
     FIG. 15 is a cross-sectional view of a power take-off assembly using dual spur gear control cam assemblies of the invention; 
     FIG. 16 is a partial cross-section graphic view of an automatic control input assembly of the invention; 
     FIG. 17 is a graphic illustration of the automatic control input assembly illustrated in FIG. 16; 
     FIG. 18 is a graphic clock face illustration of a cycle timer using input and control assemblies of the invention; 
     FIG. 19 is a cross-sectional view of the cycle timer set forth in FIG. 18; and 
     FIG. 20 is a cross-sectional view of a variable input variable output automatic controlled multiple cam spur gear assembly of the invention. 
    
    
     DESCRIPTION OF THE PREFERRED EMBODIMENT 
     Referring to FIGS. 1 and 2 of the drawings, basic elements of the invention can be seen utilizing a spur gear assembly  10  for a rotary motion control having a control bracket  11  with a pair of gears  12  and  13  rotatably positioned thereon. An input shaft  14  extends through the control bracket  11  having an output gear  15  thereon. The output gear  15  engages the respective spur gears  12  and  13  which are in turn engaged by pairs of respective transfer gears  16 A and  16 B that engage output gear  17  on the input shaft  14 . It will be seen that as input is applied to the control bracket  11  the drive transfer is achieved through the respective spur gears  12  and  13 . By rearranging input and control, the “basic elements” work as a differential. 
     Referring to FIG. 3 of the drawings, it will be seen that a pair of the gear assemblies  10  are combined to form a directional change clutch assembly  18  in which an output gear  15 ′ is connected to a secondary bracket  19  on which are rotatably positioned gears  19 A and  19 B. A corresponding output gear  20  and the bracket  19  become control input/output elements. Accordingly, with rotational input on a shaft  14 ′ while holding the bracket  19  (indicated by slash lines), output is achieved through output gear  20 . Conversely, by holding the input gear  11 ′ (indicated by slash lines) directional output is achieved by the bracket  19 . The gears and bracket elements  12 ′,  13 ′,  16 A′,  16 B′ and  11 ′ respectively defined matched ratios in their assembly wherein a one to one ratio is achieved between  14 ′ input and spur gear  12 ′ in same rotational direction while output gear  15 ′ and input shafts  14 ′ are a one to one ratio in the opposite direction. This arrangement achieves selective directional output change on output functionality. 
     Referring to FIG. 4 of the drawings, the phase angle control of the invention is illustrated in a bevel gear assembly  21  for continuity purposes. The bevel gear assembly  21  has multiple pairs of inner engaging gears  22  and  23  and control gear  24 . Each of said gear pairs  22  and  23  is defined as having oppositely disposed matching gears  22 A and  22 B in paired gear  22  and interengaging gears  23 A and  23 B in gear pair  23 . An input and support shaft  26  extends through gear  22 B and between said respective gears  23 A and  23 B and is integral with gear  22 A rotatably mounting gear  22 B and gear pair  23 . A transfer gear assembly  26  transfers output from a central support shaft  27  which is freely rotatable on the support shaft  26  to a control gear  28  rotatably positioned on the shaft  26  as illustrated by flow arrows. In this example multiple variable speed outputs via a gear  22 A and control gear  28  in the same direction as input on shaft  26  without interfering with input as indicated by arrows SP 1  and SP 2 . 
     Referring to FIG. 5 of the drawings, the phase angle control of the invention is illustrated in a planetary gear assembly  29 , in this example chosen for illustration, with input on a planetary shaft  29 A is transferred to respective planetary gears  30 A and  30 B on a support bracket  31  as illustrated by flow arrows. A gear control ring  32  controls relative rotation of the support bracket  31  and it&#39;s variable output via planetary gears  32 A and  32 B to output gear  33 . A second gear ring  34  is fixed to achieve output as hereinbefore described. Non-controlled output is achieved at output gear  29 B on the input shaft  29 A as indicated by output arrows SP 1  and SP 2 . 
     In FIG. 6 of the drawings, the phase angle control of the invention is illustrated in a gear assembly  35  is used to illustrate the phase angle control of the invention using a spur gear  37 A on an output control bracket  37  and a spur gear  38 A on a secondary control bracket  38 . Input on input shaft  36  can be constant or variable. Directional flow arrows are used to indicate motion transfer between gear elements in which variable or constant output is achieved at (SP 1 ) by rotational control of the control bracket  37  with a secondary control bracket  38  being fixed. Output at SP 2  is the same as input at shaft  36 . 
     Referring now to FIG. 10 of the drawings, a graphic illustration of the orbital path change brought the basic repositioning of the cams within the respective cam assemblies  39 A and  50  of the invention is shown. A representative inner cam  145  and outer cam  146  shown in solid lines with repositioning control pins  147  in the outer cam  146 . By repositioning the outer cam  146  in relation to the inner cam  149 , 180 degrees as illustrated by the dotted lines at  148 , the effective orbital paths are indicated for P to P+1 is shown for axial center pivot point  147  illustrated by broken lines. 
     It will be evident that phase angle control of the invention as illustrated in the bevel gear arrangement in FIG. 4, the planetary gear arrangement of FIG.  5  and the spur gear phase angle control illustrated in FIG. 6 will produce the same results as that of the spur gear and cam assemblies illustrated hereinafter. 
     Referring now to FIGS. 7 and 8 of the drawings, a speed control using spur gear phase angle control as seen in FIG. 6 of the drawings is shown with the addition of cam assembly  39  and one-way clutch bearing output assembly  47 . Input on a drive shaft  40  is illustrated following flow arrows imparted to spur gears  41  on a control and support bracket  41 A for relative repositioning of cam assembly  39  by slotted control gear disk  42 . The cam assembly  39  is set forth in greater detail in applicant&#39;s U.S. Patent and is incorporated by reference herein. 
     Accordingly, the cam assembly  39  has an inner cam  43  with an outer cam  44  and a repositioning pin  45  extending therefrom. As noted, an eccentric cam path can be changed by repositioning input of the slotted control disk  42 . A cam follower bracket  46 , best seen in FIG. 8 of the drawings, transfers cam rotational output to the one-way clutch bearing assembly  47  providing controlled output at bearing shaft  48 . The one-way clutch bearing assembly  47  becomes the pivot point of the cam follower bracket  46  that oscillates as indicated by arrows  46 A. 
     Referring now to FIGS. 9 and 11 of the drawings, a phase angle control is illustrated for a compressor application. In this example, a motor  49  is indicated so as to provide constant input at M 1 . The spur gears and cam assemblies as shown in FIGS. 7 and 8 of the drawings have been modified for this application at  39 A for illustration purposes with a secondary cam assembly  50 . It will be seen that the slotted control disks  51 ,  52 , and  53  are interconnected by a transfer gear set  54  indicated by flow arrows. The eccentric cam motion is transferred to a gear transfer sets  57 A and  57 B and then to a pair of one-way clutch bearings  58  and  59  for output to a compressor pump indicated at  60 . The cam followers  55  and  56  both have a main frame  61  with a pivot point  61 A. An enlarged opening at  62  receives the outer cam of the respective cam assemblies  39 A and  50  as they oscillate as indicated by directional arrows  61 B. A geared surface  63  is engageable on a corresponding geared surface  64  of the one-way bearings  58  and  59 . It will be seen that by control input at  65  to a control bracket  66 , the effective reciprocation of the relative rotational position of the slotted control disks  51 ,  52  and  53  can be changed and thereby cam&#39;s path would vary the output of the rotational speed on the one-way clutch bearing assemblies  58  and  59  hereinbefore described. 
     Control input at  65  in this example corresponds with a thermostat (temperature) input generally illustrated at  67 . 
     Referring now to FIG. 12 of the drawings, the phase angle control of the invention is illustrated for a constantly variable transmission (CVT) assembly  68  application with directional control wherein only the cam assembly portion  69  and  70  are shown which are identical to that as the hereinbefore illustrated and described cam assemblies  39 A and  50  illustrated in FIG. 9 of the drawings. 
     A direct engagement of the cam followers  71  are shown here with a pair of one-way clutch bearing assemblies  72  connected for output to a drive shaft  73 . A manual directional change assembly  74  (MDCA) is graphically illustrated connected to the output drive shaft  73  for useable directional control. The MDCA  74  has a pair of interengaging outlet gears  75  and  76  that are selectively engaged by respective drive outlet gears  77  and  78  on an actuation arm  79 . The drive outlet gears  77  and  78  are in turn driven by a transfer gear assembly  80  in communication with the clutch bearing drive shaft  73  by gear  73 A. Worm gear  73 A is driving pinion gear  80 A to produce engine braking output. The actuation arm  79  is pivoted at  81  so as to selectively move the respective outlet gears  77  and  78  into engagement with respective drive outlet gears  75  and  76  imparting directional output control as illustrated by broken line arrows thereon. A neutral or idle position is illustrated in solid lines with the respective output position illustrated in broken lines at  77  and  78 . 
     Referring now to FIGS. 13 and 14 of the drawings, a further application of the phase angle control of the invention is illustrated by applying same to a bicycle drive assembly  82 . An input shaft  83  drives a cam assembly  84  as indicated by the flow arrows through spur gears generally indicated by  85 . Cam assembly  84  has in this application has four pairs of oppositely disposed cam follower assemblies  86 , best seen in FIG. 14 of the drawings that transfer the eccentric cam motion directly to respective one-way clutch bearing assembly  87 A for selective output at to the bicycle wheel  88 . 
     The cam follower assemblies  86  are pivotally connected to respective link arms  89  that extend from respective one-way bearing shafts  90  and  91  which outputs (indicated by arrow  92 ) to the bicycle wheel indicated generally in this illustration as at  88 . 
     As set forth previously, control of the cam assembly  84  is achieved by the repositioning of an inner cam  88 A in relation to an outer cam  88 B by slotted control gear  88 C and its associated gear assembly  88 D as indicated by flow arrows as hereinbefore described. 
     Referring now to FIG. 15 of the drawings, a different application can be seen wherein multiple elements of the invention are used in parallel allowing for use in a variety of different environments and venues. The application illustrates the use as a power take-off (PTO) with a single input at  93  can have a pair of independently controlled outputs at  94  and  95 . Essentially, the main input and control cam arrangement of the invention as hereinbefore described is duplicated at assemblies  96  and  97  with the single input shaft  93  having multiple cam assemblies  98 ,  99 ,  100  and  101  thereon. As noted, variable output (speed) is regulated by cam relationship output through cam followers  102 - 105  to one-way clutch bearing pairs  106  for each of the outputs  94  and  95  as indicated by respective flow and control arrows in the drawings. Such constant input with multiple constantly variable outputs (CVO) arrangements can be used in a variety of practical application systems that require multiple independent operations that can now be achieved with one input as illustrated. 
     Another example of the multiple use of the basic control system of the invention can be seen in FIGS. 18 and 19 of the drawings wherein system elements arranged in parallel are used to function as a cycle timer  111 . Referring to FIG. 18 of the drawings, a preset “ON” time at  112  and “OFF” time at  113  are illustrated on a clock representation face  114 . Referring correspondingly to FIG. 19 of the drawings, the input (time drive) via a time drive shaft  115  “on” time controls at gear  116  which by following the flow arrows repositions a control bracket  117 . Accordingly, an “OFF” time control input indicated at  118  repositions a control bracket  1   19 . Electric circuit (not shown) activation and de-activation is illustrated by respective interengaging gear assemblies  120  and  121  with output circuit switch (not shown) is achieved at cam  122  for “ON” and cam  123  for “OFF” as will be well understood by those skilled in the art given the above detailed description. The same interdependency and basic gear elements hereinbefore illustrated of the invention are used in an alternate cycle time parallel arrangement. 
     Output can be of an automated or of a manual nature wherein changes of input velocity (i.e. variable input) will be used to effect control by use of a spring loaded weight control assembly  107  (illustrated as an example, but not limited thereto) in FIGS. 16 and 17 of the drawings. 
     In this example, a control element output  107 A shall be determined based on the divergency i.e. the degree of separation between a spring interconnected mass element  108  which is attached to bracket  107 A and rotational force of an input shaft  109  connecting fitting  110  indicated by the respective arrows in FIG. 17 of the drawings. As the rotational input varies the degree of separation will change accordingly, thus varying the control of the output in proportional relationship thereto. 
     Referring to FIG. 20 of the drawings, a further variation of the gear elements of the invention can be seen wherein a variable input, variable output automatic control assembly  130  is illustrated. An automatic control assembly  131  is interconnected to a variable input shaft  132 . A pair of automatic cam assemblies  133  and  134  on the variable input shaft  132  are identical to the hereinbefore-described cam assemblies  69  and  70  shown in FIG. 12 of the drawings. The repositioning of the respective cams is controlled by the automatic control assembly  131  having a differential weight  131 A engaging a control gear  135  on a support bracket  136 . A transfer gear  137  is engaged by a control gear  135 A on a control bracket assembly  138 . A second control gear  139  on the control bracket  138  is correspondingly engaged by a variable input gear  140  on the variable input shaft  132  as indicated by the flow arrows in the drawings. The differential ratio between the variable input on the variable input shaft  132  and connected weight  131 A of the automatic control assembly  131  will reposition selective control disks  140 A and  141  of the respective assemblies. The automatic cam assemblies  133  &amp;  134  output to one-way clutch bearings  142  and  143  as indicated by flow arrows to deliver variable output on the one-way bearing output shafts  144 . 
     It will thus be seen that a variable speed transmission and variable speed gear assembly in multiple forms has been illustrated and described and it will be apparent to those skilled in the art that various changes and modifications may be made thereto without departing from the spirit of the invention.