Patent Publication Number: US-6336597-B1

Title: Closed case oscillating sprinkler

Description:
This application is a division of application Ser. No. 08/863,739, filed May 27, 1997, now U.S. Pat. No. 6,109,545, which is a division of application Ser. No. 08/269,342, filed Jun. 30, 1994, now U.S. Pat. No. 5,653,390, which is a continuation-in-part of application Ser. No. 07/724,406, filed Jun. 28, 1991, now abandoned, which is a continuation-in-part of application Ser. No. 06/932,470 filed Nov. 18, 1986, now U.S. Pat. No. 5,417,370. 
    
    
     TECHNICAL FIELD 
     This invention relates to transmission devices having a rotary input shaft and oscillating output shaft, including a device to change the angle of oscillation, such as used in rotary sprinkler heads for irrigation where water causes the sprinkler to rotate in order to provide water precipitation over a desired area. 
     BACKGROUND ART 
     Oscillating transmission devices for rotatable sprinklers have been known in the prior art for use in irrigation. Patents setting forth a background for this invention are: U.S. Pat. Nos. 3,038,666; 3,107,056; 3,645,451; 3,713,584; 3,724,757; 3,854,664; 4,272,024; 4,353,507; 4,568,024; 4,624,412; 4,625,914; 4,634,052; 3,383,047; 3,526,363; and 5,115,977. 
     CROSS REFERENCE 
     Patent application Ser. No. 932,470, filed Nov. 18, 1986, now U.S. Pat. No. 5,417,370, for “A TRANSMISSION DEVICE HAVING AN ADJUSTABLE OSCILLATING OUTPUT”; patent application Ser. No. 037,704, filed Apr. 13, 1987, now U.S. Pat. No. 4,867,378, for a “SPRINKLER DEVICE”; patent application Ser. No. 183,071, filed Apr. 19, 1988, now U.S. Pat. No. 4,901,924, for a “SPRINKLER DEVICE WITH ANGULAR CONTROL”; patent application Ser. No. 245,126, now U.S. Pat. No. 4,955,542, for a “REVERSING TRANSMISSION FOR OSCILLATING SPRINKLERS”; and patent application Serial No. 626,993, filed Dec. 13, 1990, now U.S. Pat. No. 5,148,991, for a “GEAR DRIVEN TRANSMISSION FOR OSCILLATING SPRINKLER”, all filed by Carl L. C. Kah, Jr., are related to this divisional application of patent application Ser. No. 08/269,342. 
     BACKGROUND OF THE INVENTION 
     Patent application Ser. No. 932,470, now U.S. Pat. No. 5,417,370, discusses the need to maintain a continuous bias on the reversing transmission&#39;s gear cage which alternately shifts a pair of terminal gears carried on a gear cage assembly into and out of engagement with an output shaft ring gear during the period that a reversing toggle is being moved over its reversing overcenter position. Maintaining a bias on the driving terminal gear insures that it will not become disengaged during stopping or starting of the drive when the reversing toggle bias has been lifted off. 
     Also disclosed was a reversing gear drive configuration in which the driving pinion was always engaging the output gear with the reaction force on the driving terminal pinion gear tending to hold the driving gears in engagement with the driving input gear during driving in either direction and input shaft torque is not applied to the shiftable gear cage in a manner to cause the gear cage to be disengaged in either of its driving engagement positions. 
     In my U.S. Pat. No. 5,148,991, issued Sep. 22, 1992, several oscillating sprinkler drive configurations are shown having a shiftable gear cage bias means for continuously biasing the gear cage towards one driving engagement direction or the other up to the moment the gear cage is shifted overcenter. 
     DISCLOSURE OF INVENTION 
     An object of this invention is to have a transmission for alternately driving an output gear to oscillate it, by one driving gear and then another, with spring means being provided to prevent the transmission from being placed in an “off” position with neither driving gear positioned to drive the output gear upon starting. 
     Another object of this invention is to have an oscillating transmission with a pivoted gear cage having two drive gears, a first clockwise drive gear and a second counter-clockwise drive gear, for alternate driving engagement with an output gear to oscillate it, a first and second overcenter spring means act on said gear cage in one direction to place one drive gear into driving engagement within said output gear while placing said other drive gear out of driving engagement. To reverse the position of the drive gears, the first spring means has its biasing force removed from the gear cage to be placed in an overcenter position to bias the gear cage in the opposite direction so that the other drive gear can be placed in driving engagement with said output gear and the one drive gear can be placed out of driving engagement, said second spring means retaining the one drive gear in driving engagement until the first spring means is biasing the gear cage to the reverse posit;on and has overcome the second spring means to place it in an overcenter position; the second spring means thus acts together with the first spring means to pivot said gear cage to its reverse position. The second overcenter spring means insures that during the time that the pivoted gear cage is not being biased by the first overcenter spring means that it remains in one driving position or the other, and cannot be left in a “dead-center” position where neither of the two drive gears is in driving engagement with said output gear. 
     A further object of this invention is to provide an oscillating transmission which has an angular positioning member for directly setting the oscillating angle and a shaft with an adjusting, or setting, slot accessible on the top of an oscillating output cap. The slot has an arrowhead at one end indicating the position of an adjustable reversing actuator within the transmission, and an arrowhead is placed on the top of the output cap indicating the position of a fixed reversing actuator within the transmission. Indicia representing angles can be placed around the output cap to aid in positioning the setting slot at a desired angle. The ability to look at the adjustable angular selection dial and see at a glance what arc a particular unit is set for, provides an enhanced marketability for products using this drive, especially in the sprinkler field. When used as a sprinkler device, the sprinkler devices can be removed from a lawn location for cleaning or inspection and when it is desired to reinstall the sprinkler device, the desired angle of oscillation can easily be set by simply looking at the top of the device and if it is not already properly set, a rotatable member can be pointed at the desired angle position indicated on the top of the sprinkler device. 
     Another object of this invention is to provide for a driving connection between a rotating input shaft and an output gear for oscillating the output gear and providing for changing the angle of oscillation. The output gear has a fixed projection thereon to reverse rotation at one side of the angle and a cylindrical member mounted for rotation with said output gear has an adjustable projection to reverse rotation at the other side of this angle, relative rotation of said cylindrical member with said output gear changing said angle of oscillation. 
     A further object of this invention is to provide an oscillating transmission having a ring gear mounted for rotation with means for oscillating said ring gear; a toggle means reverses the rotation of said ring gear from one direction to the other, with contact means rotated by said ring gear engaging said toggle means to reverse rotation from one direction to the other, said contact means are two projecting members, with means mounting said two projecting members for relative movement to vary the angle at which said toggle means is actuated, said one projecting member being mounted on said ring gear while said other projecting member is mounted for rotation within said ring gear. Means connect said other projecting member to said ring gear for being driven thereby to contact said toggle means to reverse rotation of said ring gear, and means disconnect said other projecting member from said ring gear when said other projecting member is rotated to vary the angle between the projecting members. 
     An object of this invention is to provide a transmission having an oscillating output ring gear with a hollow shaft at the center thereof, said oscillating hollow shaft providing the output of the transmission such as by a gear attached thereto, a cylindrical member being mounted for rotation with said hollow shaft, an adjustable projection extending from said cylindrical member to serrations on the interior of said ring gear for contacting an actuating means to reverse transmission direction, said serrations connecting said adjustable projection to said ring gear for being driven thereby, said serrations providing for relative movement when said cylindrical member is rotated to vary the angle of rotation; said cylindrical member can be rotated directly through the hollow shaft. 
     Another object of this invention is to provide a torque-limiting member between said cylindrical member and said hollow shaft for providing for rotation of said cylindrical member without placing undue forces on any other operating parts. 
     Another object of this invention is to provide an oscillating transmission having an oscillating ring gear with a hollow shaft at the center thereof, said oscillating hollow shaft providing the output of the transmission, a nozzle head oscillated by said ring gear for receiving a flow of water through said transmission. 
     A further object of this invention is to provide an improved oscillating drive having a reversing gear cage and toggle device mounted on a base member for oscillation, said gear cage having two spaced driving gears always engaging an output gear with one spaced driving gear having an idler gear, either driving gear is driven by a spur gear on an input shaft located in the space between one driving gear and idler gear to drive the output gear, said input shaft extending through said space from said base member with a sleeve therearound with said gear cage having an elongated opening around said sleeve, the length of the elongated opening determining the engagement of the teeth of the spur gear with its cooperating driving gear or idler gear to prevent excessive or unnecessary interaction between the gears. 
     Another object of this invention is to provide an improved oscillating drive having a reversing gear cage wherein said gear cage is alternately biased by first biasing means in one or the other of two driving positions to provide for oscillating movement, second means being provided for biasing said gear cage in one of said directions to maintain a driving engagement when said first biasing means has been removed. 
     A further object of this invention is to provide an improved oscillating drive having a reversing gear cage with two spaced driving gears always engaging an output gear; either driving gear is driven by an input shaft, located in the space between the driving gears, to drive the output gear; the reaction force on the driving gear tends to hold the reversing gear cage and driving gear into engagement with the input shaft. 
     Another object of this invention is to provide an improved oscillating drive having a toggle device mounted on a base member for oscillation, stops are provided between said toggle device and base member for (1) limiting the biasing load on gears during operation; and (2) providing ease of spring insertion during assembly. 
     A further object of the invention is to apply the important concept of continuous gear cage engaging bias toward driving engagement for reversing transmissions used in oscillating sprinkler drives to ensure proper operation under all conditions of operation, setting, handling, and installation. 
     Another object of the invention is to provide a simplified shiftable pinion gear configurations in which, the shiftable gear cage which now is only a shiftable gear carrier for a single driving pinion gear and which remains in constant engagement with the output ring gear is shifted about the output ring gear center to engage one or the other of two counter rotating input shafts to achieve the reverse driving action. An overcenter driving engaging bias is provided which will insure the proper driving position of the driving pinion carrier until shifted to its reversed position by a shifting arm which has a lost motion connection to allow the shifting arm to be moved over it&#39;s overcenter biasing spring position before it engages the carrier to shift it out of driving engagement and carry it over its center so that the gear cage carrier&#39;s overcenter bias can then be applied in the reversed direction to carry the gear cage (carrier) into its full driving position in a reversed driving direction and maintain the driving pinion gear in proper reverse driving position until again shifted to provide driving engagement in the opposite direction. 
     Another transmission configuration is also shown where the reversing toggle&#39;s overcenter bias is a single spring and is also used to directly bias the gear cage assembly in its driving position in either direction. At the bias spring neutral center position of the reversing toggle, any gear cage movement towards premature disengagement of the driving terminal gear changes the overcenter relationship of the single overcenter reversing biasing spring, (acting on the single driving pinion gear cage (carrier)) to reverse the direction of its engaging bias and causes the driving pinion gear cage (carrier) to be shifted to its reversed driving position causing the desired reversing action while maintaining the driving engaging bias up to the moment of the reversing action occurring and then reapplying it in the reversed direction. 
     A third transmission configuration is shown where the overcenter carry action of a shifting arm is provided by the deflection of a spring member which carries the driving pinion gear cage (carrier) member overcenter once it has been driven out of driving engagement by the action of one of the arc control contact members being driven against the spring member shifting arm. 
     Because of the need to minimize the outside diameter of the gear drive assembly to reduce the sprinklers housing size and pressure surface and the central flow area needed to get water to the sprinklers oscillating nozzle a very compact and simple reversing gear arrangement is needed. Also the sprinkler mechanism needs to operate reliably for a long period of time in a very harsh environment of dirt and dirty water with no corrective attention. It is an object of this invention to provide improved and simplified reversing drive means for oscillation nozzle sprinklers for high reliability and more liberal manufacturing tolerances and ease of reliable product assembly. 
     Another object of this invention is to provide an improved oscillating drive reversing gear mechanism with two oppositely rotating input shafts spaced apart with a shiftable gear carrier (cage) for a single driving pinion gear which is shifted between engagement with one or the other of the counter rotating input shafts and the output drive gear to achieve the reversing drive of the output shaft. The reaction force of the driving gear on the driving pinion gear and shiftable gear cage carrier tends to hold the reversing gear cage and driving gear into engagement with the input gear in either of its driving positions. 
     Another object of the invention is to provide a reliable, simplified oscillation sprinkler transmission where the reversing gearing may be replaced by a friction rubber wheel drive to provide a friction driving connection between the input shaft and the output drive means. This can also provide the clutching action to prevent damage to the gear drive if the nozzle and output shaft is force rotated. The manufacturing tolerances would also be much less restrictive for a friction drive than a pure reversing gear drive and have substantially fewer parts than the slip clutch to output shaft arrangement described and shown for the pure gear drive. These features are a further object of the invention. 
    
    
     BRIEF DESCRIPTION OF INVENTION 
     FIG. 1 is an elevational view in section of a transmission device showing the input drive shaft and output cap, the reversing gear cage and reversing toggle being positioned as shown in FIG. 8, with the reversing gear cage spring means shown in full where it engages the base member; 
     FIG. 2 is a top view of the transmission device of FIG. 1 showing the output cap and oscillating angle selector; 
     FIG. 3 is a transverse sectional view of the transmission device taken along a plane represented by the line A—A of FIG. 1 showing the reversing gear cage and reversing toggle, each biased clockwise to one side with a driving gear of the reversing gear cage engaging the ring gear on the output member for counter-clockwise drive; 
     FIG. 4 is a transverse sectional view of the transmission device taken along a plane represented by the line A—A of FIG. 1 showing the reversing toggle forced counter-clockwise to a position where the reversing toggle has just passed over a center line reversing the biasing forces on said reversing toggle; 
     FIG. 5 is a transverse sectional view of the transmission device taken along a plane represented by the line A—A of FIG. 1 showing the reversing gear cage and reversing toggle, each biased counter-clockwise to the other side with an opposite driving gear of the reversing gear cage engaging the ring gear on the output member for clockwise drive; 
     FIG. 6 is a transverse sectional view of the transmission device taken along the line  6 — 6  of FIG. 1 showing the overcenter spring means for the reversing gear cage; 
     FIG. 7 is a view of the angular positioning member after its legs have become disengaged from grooves located in the cooperating cylindrical member; 
     FIG. 8 is a transverse sectional view of the transmission device taken along the line  8 — 8  of FIG. 1 with the seal removed between the cooperating cylindrical member and output member, the position of the reversing gear cage and reversing toggle being the same as shown in FIG.  1  and FIG. 4; 
     FIG. 9 is a fragmentary view of the right side of FIG. 3, with the toggle device removed and a portion of the ring gear broken away, to show the relation of the actuating post and downwardly projecting member of the reversing gear cage and gear cage overcenter spring means; 
     FIG. 10 is an enlarged view of the center part of FIG. 8, along with the angular adjustable radial projection, showing the connecting serrations; 
     FIG. 11 is an elevational view in section of a modification of the transmission device as shown in FIG. 1; 
     FIG. 12 is a top view of the modified transmission device of FIG. 11; 
     FIG. 13 is a view similar to FIG. 6 showing a modification of the spring means where the gear cage is only directly biased in one direction; 
     FIG. 14 is an elevational view in section of another modification of the transmission device as shown in FIGS. 1 and 11; 
     FIG. 15 is a transverse sectional view of the transmission device taken along a plane represented by line B—B of FIG. 14 with the ring gear and reversing gear cage removed, showing the reversing toggle device; 
     FIG. 16 is a transverse sectional view of the transmission device taken along a plane represented by line B—B of FIG. 14 showing the reversing gear cage and reversing toggle, each biased clockwise with a driving gear engaging the spur gear on the input shaft for driving the ring gear counter-clockwise; 
     FIG. 17 is a transverse sectional view of the transmission device taken along a plane represented by the line B—B of FIG. 14 showing the reversing toggle forced counter-clockwise to a position where the reversing toggle has just passed over a center line reversing the biasing forces on said reversing toggle; 
     FIG. 18 is a transverse sectional view of the transmission device taken along a plane represented by the line B—B of FIG. 14 showing the reversing gear cage and reversing toggle, each biased counter-clockwise with the other driving gear having its idler gear engaging the spur gear on the input shaft for driving the ring gear clockwise; the gear cage is cut away to show the spring means; 
     FIG. 19 is a transverse sectional view of another modification of the transmission devices shown in FIGS. 1-18 where a gear cage bias spring has been added to the reversing transmission described in detail for FIGS. 14 thru  18  where the driving pinions are continuously engaging the output gear; 
     FIG. 20 is a fragmentary side elevation view taken on line  20 — 20  of FIG. 21 of a sprinkler showing the upper rotating nozzle and reversing drive in section for the single shiftable driving gear between two counter rotating input shafts configuration; 
     FIG. 21 is a transverse sectional view taken on line  21 — 21  of FIG. 20 showing the gear cage assembly in its fully clockwise position for driving the output ring gear for counter-clockwise rotation. The reversing toggle device is shown in its fully clockwise position; 
     FIG. 22 is a sectional view taken on line  22 — 22  of FIG. 21 showing the driving relationship of the counter rotating input shafts; 
     FIG. 23 is a fragmentary side elevation view taken on line  23 — 23  of FIG. 24 of a sprinkler showing the upper rotating nozzle and reversing drive in section for a reversing configuration where the gear cage pivot has been moved off center and a single bias spring interacts directly between the gear cage and toggle action shifting arm; 
     FIG. 24 is a transverse sectional view taken on line  24 — 24  of FIG. 23 showing the gear cage(carrier) in its full counter-clockwise position for driving the output ring gear for counter-clockwise rotation. The reversing toggle is shown in its fully clockwise position; 
     FIG. 25 is a fragmentary side elevation view of a sprinkler showing the upper rotating nozzle and reversing drive in section for a reversing mechanism which has no toggle shifting arm and is shown with gear cage (carrier) with its bias spring seats aligned; 
     FIG. 26 is a transverse sectional view taken on line  26 — 26  of FIG. 25 showing the gear cage in its fully clockwise position for driving the output ring gear for counter-clockwise rotation. The shifting arm wire is shown in its vertical neutral position between its side bending limiting stiffening posts; 
     FIG. 27 is a partial side elevation view looking generally along line  27 — 27  of FIG. 25 with the output driving member and other parts removed, showing the reversing gear cage actuation arm wire and side stiffening posts extending upwardly from the top surface of the gear cage bottom plate as well as the position of the integral gear cage over-center biasing spring positioned below the gear cage bottom plate as shown in FIG. 25; 
     FIG. 28 is a partial transverse sectional view of the transmission device taken along line  28 — 28  of FIG. 25 showing an alternate configuration of gear cage biasing spring with shaped contact surface interacting on a camming post carried by the gear cage to provide a variable gear cage bias force. 
     FIG. 29 is taken on line  29 — 29  of FIG. 30; 
     FIG. 30 is taken on line  30 — 30  of FIG.  29 . 
    
    
     BEST MODE FOR CARRYING OUT THE INVENTION 
     Referring to FIG. 1 of the drawings, a sprinkler transmission device  1  is shown having a cylindrical housing  2  positioned over and fixed to a base member  4 . Cylindrical housing  2  has an integral cover  6  having a center outlet opening  8  for a purpose to be hereinafter described. The end of cylindrical housing  2  over base member  4  has a circumference of an increased inner diameter  52  forming an annular step  54 . Base member  4  is positioned in the increased diameter  52  of cylindrical housing  2  against the annular step  54  and an internal snap ring  56  is placed in an annular groove  58  in the circumference of increased inner diameter  52  formed at the bottom of base member  4  to fix it in place. Other holding means can be used. 
     Base member  4  has an opening  10  therethrough positioned to one side for receiving a rotary input shaft  12 . Rotary input shaft  12  can be driven by a fluid turbine. The upper part  14  of the opening  10  is enlarged to receive an annular flange  16  on the input shaft  12 . A reversing gear cage  18  is positioned within said cylindrical housing  2  adjacent said base member  4  and the reversing gear cage  18  is formed having a top plate  20  and a bottom plate  22  with cooperating center openings  21  and  23 , respectively. The bottom plate  22  has an opening  24  therein to receive the rotary input shaft  12 , the upper end of which is formed as a spur gear  26 . A cylindrical shaft  28  extends downwardly from the bottom of the bottom plate  22  around opening  24  and extends into the upper part  14  of the opening  10  to provide for pivotal movement of the reversing gear cage  18  while the cylindrical shaft  28  properly positions the input shaft  12  and sour gear  26  above the top of the bottom plate  22  by enclosing the annular flange  16 . An integral shaft  25  extends downwardly from the bottom of top plate  20  to engage a cylindrical opening  27  extending downwardly from the top of input shaft  12  through the centerline of the spur gear  26 . 
     As shown in FIGS. 3,  4  and  5 , three gears  30 ,  32  and  34  are mounted on integral shafts  36 ,  38  and  40  extending downwardly from top plate  20  of the reversing gear cage  18  and they extend in a counter-clockwise direction from the integral shaft  25 . Integral shaft  36  is positioned so that gear  30  will engage the spur gear. 26 ; shaft  38  is positioned so that gear  32  will engage gear  30 ; and shaft  40  is positioned so that gear  34  engages gear  32  and extends outwardly over the edges of top plate  20  and bottom plate  22  so that it can drivingly engage an output ring gear  50 , encircling the reversing gear cage  18  between the top plate  20  and bottom plate  22 . Output ring gear  50  is formed as a part of output member  49 . Output member  49  will be hereinafter discussed as to its structure and use. 
     Two gears  42  and  44  are mounted on integral shafts  46  and  48  extending downwardly from top plate  20  of the reversing gear cage  18  and they extend in a clockwise direction from the integral shaft  25 . Integral shaft  46  is positioned so that gear  42  will engage the spur gear  26  and shaft  48  is positioned so that gear  44  engages gear  42  and extends outwardly over the edges of top plate  20  and bottom plate  22  so that it can drivingly engage said output ring gear  50 . Integral shafts  36 ,  38 ,  40 ,  46  and  48  of top plate  20  extend into matched openings in bottom plate  22  and have a snap engagement at their ends with said openings to fix said top plate  20  and bottom plate  22  of the reversing gear cage  18  together. 
     A hollow actuating post  60  extends upwardly from the top of the bottom plate  22  at a point on the other side of the center opening  23  from the opening  24 , and on a radial line passing through the center of the opening  24 ; said arrangement permits arcuate movement of hollow actuating post  60  about the center of opening  24 , cylindrical shaft  28  and spur gear  26 , as reversing gear cage  18  is moved between its clockwise driving position and counter-clockwise driving position. A short integral shaft  62  extends downwardly from the bottom of top plate  20  to have snap engagement with the hollow actuating post  60 . 
     It can be seen that when the reversing gear cage  18  is positioned clockwise around input shaft  12 , as shown in FIG. 3, the gear  34  is engaging the ring gear  50 . With the rotary input shaft  12  being driven clockwise, the two idler gears  30  and  32  will rotate drive gear  34  counter-clockwise, imparting a counter-clockwise rotation to output ring gear  50 . When the reversing gear cage  18  is positioned counter-clockwise around input shaft  12 , as shown in FIG. 5, the gear  44  is engaging the ring gear  50 . With the rotary input shaft  12  being driven clockwise, the one idler gear  42  will rotate the drive gear  44  clockwise, imparting a clockwise rotation to output ring-gear  50 . 
     To bias the reversing gear cage  18  in a clockwise direction to have gear  34  engage ring gear  50 , or bias the reversing gear cage  18  in a counter-clockwise direction to have gear  44  engage ring gear  50  for oscillating movement of output ring gear  50 , a reversing toggle device  64  is positioned between the top plate  20  and bottom plate  22  of reversing gear cage  18 . The reversing toggle device  64  is formed having a C-shape with an arcuate inner surface  66  greater than 180 degrees for rotation about a cylindrical member  68 , extending through the center openings  21  and  23  of top plate  20  and bottom plate  22  of reversing gear cage  18 . Cylindrical member  68  will be hereinafter discussed as to its structure and use. 
     The C-shape of reversing toggle device  64  has two arms  70  and  72  with spring seat notches on their outer surface at  74  and  76 , respectively; said spring seat notches  74  and  76  being 180 degrees apart. Cooperating spring seat notches  78  and  80  are placed on projections  82  and  84 , extending upwardly from the top surface of base member  4 , adjacent the gear teeth of output ring gear  50 . The spring seat notches  78  and  80  are located on a diametrical line through the centerline of the cylindrical housing  2 , said diametrical line being 90 degrees to a line passing between the center of opening  24  of bottom plate  22  and the centerline of the cylindrical housing  2 . 
     An overcenter spring means  90  extends between spring seat notch  74  on reversing toggle device  64  and spring seat notch  78  on projection  82  of base member  4 , and a cooperating overcenter spring means  92  extends between spring seat notch  76  on reversing toggle device  64  and spring seat notch  80  on projection  84  of base member  4 . Spring means  90  and  92  bias reversing toggle device  64  in a clockwise direction as viewed in FIG. 3, and in a counter-clockwise direction as viewed in FIG.  5 . The action of these spring means  90  and  92  reverses when seat notches  74  and  76  pass on either side of a centerline passing through the spring seat notches  78  and  80 . 
     Reversing toggle device  64  has a relatively wide radial arm  86  extending outwardly from the center portion thereof between the arms  70  and  72 , to a location spaced inwardly from the gear teeth of ring gear  50 . An arcuate opening  88  is placed in said radial arm  86  at a radius to receive the hollow actuating post  60  of the reversing gear cage  18 . 
     Movement of toggle device  64  in either clockwise or counter-clockwise direction to just over its centerline position, reverses the biasing direction of each overcenter spring means  90  and  92 , changing the biased position of toggle device  64 . Toggle device  64  has an end of arcuate opening  88  which contacts hollow actuating post  60  to bias the reversing gear cage  18  in the same direction as the toggle device  64  changing the reversing gear cage  18  drive connection to output ring gear  50 . It can be seen that this movement of toggle device  64  controls movement of reversing gear cage  18  between clockwise and counter-clockwise movement. 
     The radial arm  86  of reversing toggle device  64  has an upstanding projection  94  for rotating said toggle device  64  in a counter-clockwise direction and an outwardly extending radial projection  96  for rotating said toggle device  64  in a clockwise direction to move it to the overcenter position where the overcenter spring means  90  and  92  take over and bias the toggle device  64  and, in turn, reversing gear cage  18  to its engaged position with output ring gear  50 . Upstanding projection  94  extends upwardly from the end of the top of radial arm  86  to a point above the teeth of the ring gear, and the outwardly extending radial projection  96  extends from the bottom of the radial arm  86  and under the output ring gear  50  adjacent its lower edge. Actuation of projection  94  and  96  will be hereinafter described. 
     To maintain a biasing force on reversing gear cage  18  at all times, to keep a driving gear  34  or  44  into engagement with ring gear  50 , a downwardly projecting member  31  is located on the bottom of bottom plate  22  of the reversing gear cage  18  and extends into a recess  33  formed in the top of base member  4 . Downwardly projecting member  31  is positioned below the actuating post  60  with a spring seat notch  35  facing outwardly along a radial line through the center of cylindrical shaft  28 . A cooperating spring seat notch  37  is positioned on the outer wall of recess  33  on a line passing through the center of cylindrical shaft  28  and the center of the cylindrical housing  2 . An overcenter spring means  39  extends between spring seat notch  35  on downwardly projecting member  31  and spring seat notch  37  on the outer wall of recess  33 . Overcenter spring means  39  (and spring means  90  and  92 ) are formed from ribbon-like spring material, for example, steel, and shaped with an intermediate arcuate portion and oppositely directed straight portions to engage spring seat notches. Each end of the straight portions have serrations  41  to grip the spring seat notches. Overcenter spring means of this type, and others, are shown in U.S. Pat. Nos. 3,713,584; 3,724,757; and 3,107,056. Other types of overcenter spring means can be used. The biasing force of overcenter spring means  39  is made less than the combined biasing force of overcenter spring means  90  and  92 , so that overcenter spring means  39  will only maintain the driving gear of reversing gear cage  18  in engagement until the overcenter spring means  90  and  92  actually go over center and force the toggle device  64  to the other side, the toggle device  64  contacting the actuating post  60  of the reversing gear cage  18  to carry the reversing gear cage  18  with it, breaking loose the driving gear from ring gear  50 , at which time spring means  90  and  92  overpower the spring means  39 , carrying the gear cage  18  overcenter to reverse the biasing force of spring means  39 , spring means  90 ,  92 , and  39 , biasing the opposite driving gear of gear cage  18  into engagement. This prevents the reversing gear cage  18  from becoming positioned with both drive gears  34  and  44  out of engagement with ring gear  50 . The reversing gear cage spring means  39  thus ensures that the drive gear of the reversing gear cage  18  remains engaged with ring gear  50  during stopping and starting torque changes through the range of rotational arcs where the gear cage  18  is not biased by the toggle device  64  loading against post  60  to hold the drive train in engagement. 
     Output ring gear  50  and cylindrical member  68  are mounted for rotation with each other in cylindrical housing  2  in either a clockwise or counter-clockwise direction. A fixed projection  100  extends downwardly from the bottom edge of output ring gear  50  to contact the outwardly extending radial projection  96  when ring gear  50  is being driven in a clockwise direction by gear  44  of reversing gear cage  18  (see FIG.  5 ). This movement of radial projection  96 , as described hereinbefore, moves toggle device  64  just over its centerline position and spring means  90  and  92  take over as the driving engagement of gear  44  is broken and spring means  90  and  92  overpower the reversing gear cage biasing spring means  39 , to bias toggle device  64  and reversing gear cage  18  to its opposite position to engage gear  34  and drive ring gear  50  in a counter-clockwise direction (see FIG.  3 ). 
     An angularly adjustable radial projection  200  extends radially from an annular flange  102  on top of cylindrical member  68  to contact the upstanding projection  94  of toggle device  64  when ring gear  50  and annular flange  102  are being driven in a counter-clockwise direction by gear  34  of reversing gear cage  18  (see FIG.  3 ). This movement of upstanding projection  94 , as described hereinbefore, moves toggle device  64  just over its centerline position and spring means  90  and  92  take over, as the driving engagement of gear  34  is broken and spring means  90  and  92  overpower the reversing gear cage biasing spring means  39 , to bias toggle device  64  and reversing gear cage  18  to its opposite position to engage gear  44  and drive ring gear  50  in a clockwise direction (see FIG. 8 where adjustable radial projection  200  is about to move the upstanding projection  94  over its centerline position). The cooperation between ring gear  50  and annular flange  102  will be hereinafter described. 
     Output member  49  includes a cylindrical shaft member  51  with a radial flange  53  extending outwardly from a midportion thereof. A cylindrical flange  55  extends downwardly from the end of the radial flange  53 , with output ring gear  50  being formed at the bottom thereof. Cylindrical shaft member  51  has an upper hollow output shaft portion  51 A extending upwardly through opening  8  to the exterior of the cover  6  and a lower cooperating cylindrical portion  51 B extending into cylindrical member  68 . 
     The upper hollow output shaft portion  51 A forms an annular groove  104  with the top of cover  6 . An annular resilient sealing member  106  is located in said groove  104 . An output cap  108  is placed over the end of upper hollow output shaft portion  51 A with its lower end enclosing the annular resilient sealing member  106 . The output cap  108  is fixed to the upper hollow output shaft portion  51 A by a pin  110 . Other desired fixing means can be used. 
     The upper surface of radial flange  53  of output member  49  has a raised portion adjacent said upper hollow output shaft portion  51 A on which a thrust washer  57  is placed to engage the inner surface of integral cover  6 . The lower surface of radial flange  53  has a cooperating contour with the top surface of annular flange  102  on the top of cylindrical member  68  to limit the angular movement between the mating flanges  53  and  102 . 
     An annular notch  69  is formed in the inner end of annular flange  102  facing the lower surface of radial flange  53  and upper part of cylindrical portion  58 B. An annular resilient sealing member  71  is positioned in annular notch  69  to seal the gear housing from pressure in the annular passage through the central shaft area. 
     A slight rounded projection  73  extends from the top of top plate  20  of reversing gear cage  18  over integral shaft  25  to properly space it from the bottom of annular flange  102 . 
     An annular groove  63  is placed in the top surface of annular flange  102 , with an integral stop member  65  being placed therein. Said integral stop member  65  is positioned in said annular groove  63  a few degrees counter-clockwise of the adjustable radial projection  200  (see FIG.  8 ). A cooperating stop projection  67  extends downwardly from the lower surface of radial flange  53  and projects into the annular groove  63 . It can be seen that flanges  102  and  53  have a relative angular movement of approximately  360  degrees, the arc of travel of stop projection  67  in annular groove  63  from one side of integral stop member  65  to the other. 
     A plurality of serrations  59  extend around the inner circumference of cylindrical flange  55  between the radial flange  53  of output member  49  and the internal teeth of ring gear  50 . Serrations  59  are positioned to engage an angular holding pointer  61  on the adjacent end of angularly adjustable radial projection  200 . 
     The lower part of cylindrical member  68  is formed having a smaller cylindrical section  68 A, said smaller cylindrical section  68 A forming an inner annular step  75  where it meets the upper larger portion of cylindrical member  68 , and an outer rounded step  77 . To receive the lower end of cylindrical member  68  and smaller cylindrical section  68 A, base member  4  has a second opening  79  therethrough axially aligned with outlet opening  8 . Second opening  79  has a small portion  81  of reduced diameter forming an annular step  83 , and a small end portion  85  of a further reduced diameter which is threaded forming an annular step  87 . 
     The upper part of cylindrical member  68  engages second opening  79  and smaller cylindrical section  68 A engages the reduced diameter of portion  81  with the bottom end of smaller cylindrical section  68 A engaging annular step  87 . This forms an annular chamber between annular step  83  and outer rounded step  77 . An annular resilient sealing member  89  is placed in said chamber against annular step  83 , and a seal retaining ring  91  is placed between said sealing member  89  and the rounded step  77 . This provides for proper positioning of cylindrical member  68  in cylindrical housing  2  and provides for sealing at that point. An adaptor  93  is threaded in opening  85  having an opening  95  therethrough for directing a liquid, such as water, into cylindrical section  68 A, if desired. 
     An angular positioning member  3  interconnects the lower cooperating cylindrical portion  51 B and cylindrical member  68  to set a desired angular position therebetween to control the oscillating angular movement of upper hollow output shaft portion  51 A. Said lower cooperating cylindrical portion  51 B extends into cylindrical member  68  approximately one-half of the distance to annular step  75 . The inner surface of the upper portion of cylindrical member  68  has four equally spaced longitudinal turning grooves  5  extending from the annular notch  69  to the inner annular step  75 . Angular positioning member  3  has a centerbody  7  with four equally spaced vane members  9  thereon. The lower portion of the vane members  9  extend into the cooperating grooves  5  from the bottom thereof up to approximately the lower end of lower cooperating cylindrical portion  51 B. The vane members  9  are integrally attached to centerbody  7  up to this point. The vane members  9  then taper inwardly and extend upwardly as four individual projections  11  into the lower cooperating cylindrical portion  51 B. This cylindrical portion  51 B has serrations  13  therearound for engagement by tapered, or pointed, outer ends  15  on projections  11  to connect angular positioning member  3  to cylindrical portion  51 B of output member  49 . 
     Centerbody  7  of angular positioning member  3  has crossed slots  112  aligned with vane members  9  to receive the flat paddle  114  of an angular positioning or setting shaft  116 . Angular positioning shaft  116  extends through output cap  108 , presenting a small adjusting, or setting, slot  118  to the top of the output cap  108 ; said small slot having an indicating arrowhead at one end indicating the position of the angularly adjustable radial projection  200 , while an indicating arrowhead on the output cap  108  indicates the position of the fixed projection  100 . An annular flange  121  on angular positioning shaft  116  prevents the flat paddle  114  from becoming accidentally disconnected. A seal  124  extends between the output cap  108  and angular positioning shaft  116 . 
     Gear teeth  120  are located around the output cap  103  to provide an external drive. An opening  122  is provided in output cap  108  to serve as a nozzle opening and it is aligned with the fixed projection  100 . Angular degree settings can be inscribed in the top surface of the output cap  108  to set a desired oscillating angle. 
     In driving operation, input shaft  12  turns clockwise driving output ring gear  50  in an oscillating motion through a predetermined angle set by adjusting slot  118 . This angle is shown as 180 degrees in the Figures. Starting from FIG. 3, drive gear  34  is engaged with and drives ring gear  50  counter-clockwise, bringing adjustable radial projection  200  into actuating contact with upstanding projection  94  of toggle device  64 , moving toggle device  64  against spring means  90 ,  92  past an overcenter position reversing the action of spring means  90 ,  92 . This biases toggle device  64  counter-clockwise for engagement with actuating post  60  of gear cage  18 . Further movement of ring gear  50  by drive gear  34  continues to move radial projection  200  against upstanding projection  94  which begins to pivot the gear cage  18  against the force of spring means  39 , disengaging the drive gear  34 . The reversed action of spring means  90 ,  92  now overcomes the force of spring means  39 , moving the spring means  39  past an overcenter position, reversing the action of spring means  39 . Spring means  39  and spring means  90 ,  92  now carry gear cage  18  to its new clockwise driving position (see FIG. 5) with drive gear  44  engaging and driving ring gear  50  clockwise; movement of ring gear  50  clockwise bringing fixed projection  100  into actuating contact with radial projection  96  of toggle device  64 , moving toggle device  64  against spring means  90 ,  92  past an overcenter position, reversing the action of spring means  90 ,  92 . This biases toggle device  64  clockwise for engagement with actuating post  60  of gear cage  18 . Further movement of ring gear  50  by drive gear  44  continues to move fixed projection  100  against radial projection  96  which begins to pivot the gear cage  18  against the force of spring means  39 , disengaging drive gear  44 . The reversed action of spring means  90 ,  92  now overcomes the force of spring means  39 , moving the spring means  39  past the overcenter position, reversing the spring means  39 . Spring means  39  and spring means  90 ,  92  now carry gear cage  18  back to its counter-clockwise position (see FIG. 3) with drive gear  34  engaging and driving ring gear  50  counter-clockwise. This oscillation continues as long as input shaft  12  is driven. 
     During the driving operation, fixed projection  100  is directly driven by ring gear  50  but angularly adjustable radial projection  200  is driven by ring gear  50  through serrations  59  and  13 . Output member  49  has an equal number of serrations  59  and  13  above ring gear  50  and in cylindrical portion  51 B, respectively. Angularly adjustable radial projection  200  has the angular holding pointer  61  on its outer end providing a direct driving connection with one serration of serrations  59 , so ring gear  50  can drive the angularly adjustable radial projection  200 . This angularly adjustable radial projection  200  has a special contour  204  on each side to mate with a contour  97  on upstanding projection  94 . As contour  204  is driven against contour  97 , the angular holding pointer  61  is held in its proper angle setting serration  59 . This action is obtained by an angled surface  206  on the end of angularly adjustable radial projection  200  which extends outwardly in the direction of movement of the ring gear  50  to engage a mating angled surface  98  on upstanding projection  94 . These angled surfaces  206  and  98  prevent the angular holding pointer  61  from bending in the direction the serrations  59  are moving and therefore preventing a serration  59  from being pulled over the angular holding pointer  61 . This action is employed to self-lock the output cap to its last set position in both clockwise and counter-clockwise directions of movement of ring gear  50 . 
     Angularly adjustable radial projection  200 , extending from annular flange  102 , has inner cylindrical member  68  providing an indirect driving connection with serrations  13  through which ring gear  50  can drive the annular flange  102  and angularly adjustable radial projection  200 . Angular positioning member  3  interconnects lower cooperating cylindrical portion  51 B to cylindrical member  68  through serrations  13  in lower cooperating cylindrical portion  51 B and cooperating grooves  5  in cylindrical member  68 . Tapered, or pointed, outer ends  15  on projections  11  extend into serrations  13  and the ends of vane members  9  extend into the cooperating grooves  5 . 
     Rotation of lower cooperating cylindrical portion  51 A turns serrations  13  which then rotate the ends  15  of projections  11  of angular positioning member  3 ; this rotates vane members  9  and cylindrical member  68  with its radial projection  200 . Rotation of cylindrical member  68  through serrations  13  provides for slippage prevention. As lower cooperating cylindrical portion  51 A rotates, or drives, angular positioning member  3 , the ends of vane members  9  in grooves  5  are dragged slightly rearwardly by cylindrical member  68 , placing a slight curve in the ends  15  of projections  11 . The serrations  13  push, or bite, into the ends  15  and tend to have a fixed relationship, and prevent slippage and overriding. This arrangement also aids in maintaining the preset angular setting indicated on the output cap  108 . 
     To set the angle between the fixed projection  100  and angularly adjustable radial projection  200 , the adjusting slot  118  is observed to note the indicated angular setting. If the new desired angular setting is larger than the indicated setting, the output cap  108  can be held and the slot  118  moved clockwise to the larger desired oscillating angle. In all but one case, the angular setting can be made larger by merely holding the output cap  108  and pointing the arrowhead of slot  118  at the larger angle position. In this one case, the angle is set as described below for a smaller angular setting. In FIG. 2, if a setting of 270 degrees is desired, since it is set at 180 degrees, the arrowhead of slot  118  would merely be positioned to point at 270 degrees. 
     Movement of slot  118  rotates setting shaft  116  and flat paddle  114  clockwise. Flat paddle  114  rotates angular positioning member  3  and in turn cylindrical member  68  through vane members  9  and cooperating grooves  5 . Tapered outer ends  15  on projections  11  are forced over the serrations  13 , aided by bending of vane members  9  by the drag on the ends of vane members  9  in grooves  5 , and angular holding pointer  61  on angularly adjustable radial projection  200  is forced over the serrations  59  to a new cooperating position with the serrations for the new angular setting. 
     If the new desired angular setting is smaller than the indicated setting, the output cap  108  is rotated clockwise as far as it will go with cooperating stop projection  67  engaging integral stop member  65 , if it will rotate clockwise at all; if the output cap  108  cannot be rotated clockwise, it is rotated counter-clockwise as far as it will go, to actuate toggle member  64 , and then rotated clockwise as far as it will go, as mentioned above. From this clockwise position the output cap  108  can be held and the slot  118  moved clockwise to the smaller desired oscillating angle. 
     Movement of slot  118  rotates shaft  116  and flat paddle  114  as before, to force the tapered outer ends  15  and angular holding pointer  61 , over the serrations  13  and  59 , respectively, to the new angular setting. 
     In the setting of the oscillating angle by turning the setting shaft  116 , if the motion of cylindrical member  68  is restricted and the setting shaft  116  turned with excessive force, the vane members  9  will bend out of grooves  5 , preventing any breakage by forcing setting shaft  116  (see FIG.  7 ). The material and thickness of the vanes  9  can be controlled to achieve a desired torque at which vanes  9  will be bent out of grooves  5  which will limit the torque placed on all other related operating parts. 
     The output cap  108  can have its oscillating motion connected to a device requiring an oscillating input by a gear meshing with gear teeth  120 . Other drive means can be used, such as pullies. 
     If it is desired to use the transmission device  1  as an oscillating sprinkler head, a liquid such as water, can drive a turbine connected to input shaft  12  and then be directed into opening  95 . From opening  95  the liquid will pass through the smaller cylindrical section  68 A where it enters the larger part of cylindrical member  68  between the four spaced vane members  9 . The liquid then flows past individual projections  11  around shaft  116  in the lower cooperating cylindrical portion  51 B of cylindrical shaft member  51  into the upper hollow output shaft portion  51 A and into the output cap  108 . The liquid is directed outwardly from the output cap  108  through the oscillating nozzle opening  122 . 
     The modified transmission device  1 A of FIG. 11 has the same rotary input shaft  12  and oscillating ring gear  50 , with intermediate oscillating drive, as shown in FIG.  1  and described above, as can be seen from a comparison of the Figures. The basic difference is the simplification of the mechanism to set the desired oscillating angle between fixed projection  100  and adjustable radial projection  200 . 
     In FIG. 11, the center upstanding cylindrical member  130  of base member  4 A physically replaces the cylindrical member  68  and  68 A and related annular seal ring  89  and seal retaining ring  91 , for supporting and sealing remaining annular flange  102 A. Removed along with cylindrical member  68  and  68 A, are the angular positioning member  3 , the lower cooperating cylindrical portion  51 B, the angular positioning shaft  116 , and the top of output cap  108  above the upper hollow output shaft portion  51 A, leaving member  108 A. The connection of pointer  61  of adjustable radial projection  200  to ring gear  50  remains the same. 
     Added to the modification is a cylindrical member  168 A extending into hollow output shaft portion  51 A and center cylindrical member  130  for connection to annular flange  102 A to mount it for rotation in output ring gear  50  and provide for rotating the flange  102 A and adjustable radial projection  200 . The connection of adjustable radial projection  200  on flange  102 A to ring gear  50  through pointer  61  and serrations  59  is as shown and described for FIG. 1. A top  132  can be placed on the cylindrical member  168 A for placing a small adjusting, or setting, slot  118 A thereon. If it is desired to use this modification as a sprinkler, the cylindrical member  168 A can extend externally of the upper hollow output shaft portion  51 A, and have a nozzle opening  122 A placed in the side thereof. 
     An annular groove  83 A is placed in the top of center cylindrical member  130  around cylindrical member  168 A for receiving a seal  89 A, and an annular groove  69 A is placed in the output member  49  around cylindrical member  168 A for receiving a seal  71 A. 
     It can be seen that this modification provides a simple mounting and setting arrangement for flange  102 A and adjustable radial projection  200 . To indicate the angular setting of the transmission, an indicating arrowhead is placed on the edge of member  108 A indicating the position of fixed projection  100 , while an arrowhead is placed on one end of slot  118 A indicating the position of angularly adjustable radial projection  200 . 
     The driving operation of this modification is the same as that of FIG. 1, with the angular setting of angularly adjustable radial projection  200  being made simpler, especially with the removal of the angular positioning member  3  and lower cooperating cylindrical portion  51 B, which did away with the serrations  13  and cooperating tapered ends  15  on projections  11 . Cylindrical member  168 A provides the setting function of setting shaft  116  of FIG.  1 . 
     As seen in FIG. 13, to provide for biasing of the gear cage  18  in only one direction, the recess  33 B is formed similar to recess  33  of FIG. 6, with spring seat notch  37  removed and the outer wall made straight. A spring member  39 B extends around a curved end of recess  33 B along the straight outer side and around approximately one-half of the other curved end where it extends into the recess  33 B with a straight portion  126  and a portion  127  angled towards the center of the straight inner side of the recess  33 B for engaging downwardly projecting member  31 B. 
     In this modification, the downwardly projecting member  31 B of the bottom plate  22  of the reversing gear cage  18 , is formed as approximately a one-half portion of the projecting member  31  of FIG.  6 . The downwardly projecting member  31 B has a flat surface  125  perpendicular to a line through the center of input shaft  12 , and an angled surface  35 B. When the portion  127  rests on the flat surface  125 , no biasing force is placed on the gear cage  18  (as shown in phantom in FIG.  13 ). A biasing force is only placed on the gear cage  18  in one direction when portion  127  contacts the angled surface  352 . 
     This requirement is to only move the reversing gear cage  18  in one direction back into engagement after the output shaft  51  has manually been turned clockwise externally forcing the teeth of driving gear  44  out of engagement and removing the biasing force through the toggle device  64 . This requirement is for a very small angle of gear cage  18  movement clockwise. Other positions of the gear cage  18 , outside of the small angle referred to, permit a gear,  34  or  44 , of the gear cage  18  to engage the ring gear  60 , by biased toggle device  64  or by torque applied by the spur gear  26  to the gear cage  18 . Those gear cage  18  locations are between a first position where radial projection  96  has been moved by fixed projection  100  to remove gear  44  from engaging ring gear  50  while removing the biasing toggle force, and a second position where the end of arcuate opening  88  first permits driving gear  34  to engage ring gear  50  for a driving action. 
     The cam action biasing configuration of FIG. 13 is attractive since it can be designed to be exactly responsive to the small angular biasing requirement with biasing removed when not needed. The bias is applied only during the movement range of  31 B that surface  127  is engaging surface  35 B. 
     Another advantage is that the biasing force of this configuration can be designed to remain relatively constant over the movement range that bias is applied. This configuration could, of course, be designed to also provide for bias in the other direction if needed, by putting an angled surface  35 B on the other end of downwardly projecting member  31 B. The arc through which the bias operates can be predetermined by the length of the angled surface  35 B. 
     The transmission device  13  of FIG. 14 is a modification of the transmission device  1 A of FIG.  11 . The drive means between the input shaft  12  and ring gear  50  is changed by (1) replacing the gear cage  18  with a new gear cage  18 A; (2) replacing the toggle device  64  with a new toggle device  64 A; (3) removing the spring means  39  and cooperating parts, downwardly projecting member  31  and recess  33 , for previously maintaining a direct biasing force an gear cage  18  at all times, and (4) placing a bearing sleeve  28 A around the top of input shaft  12 A. 
     The base member  4 B has the recess  33  removed and presents a flat surface  140  around center upstanding cylindrical member  130 , for the toggle member  64 A to be located on for oscillating movement around center cylindrical member  130 . A raised pad  142  on flat surface  140  is arcuate in shape and is positioned to provide a stop surface at either end, equally spaced from the center of spur gear  26 A and rotary input shaft  12 A, for toggle device  64 A, for a purpose to be hereinafter described. A bearing sleeve  28 A is press fitted into enlarged part  14 A of opening  10  over annular flange  16  and projects above the raised pad  142  and flat base plate  144  of toggle device  64 A to the bottom of the spur gear  26 A to provide a stop surface on two sides for gear cage  18 A for a purpose to be hereinafter described. 
     Toggle device  64 A comprises the base plate  144  which is substantially circular in shape having an outer cut-out portion  146  to encompass raised pad  142 , having cooperating end stop surfaces to have contact with the ends of raised pad  142  to provide a limiting movement between the reversing toggle device  64 A and the base member  4 B for operation and assembly. Base plate  144  has two opposed inner cut-out portions  148  and  150 , opening to the outer surface of cylindrical member  130 . The outer surface of cylindrical member  130  has diametrically opposed spring seat notches  152  and  154 ; spring seat notch  152  faces cut-out portion  148  and spring seat notch  154  faces cut-out portion  150 . The outer portion of cut-out portion  148  has a spring seat  156  and the outer portion of cut-out portion  150  has a spring seat  158 , said spring seats  156  and  158  being diametrically opposed and spaced equidistant from spring seats  152  and  154 , respectively. 
     An overcenter spring means  160  extends between spring seat notch  156  on reversing toggle device  64 A and spring seat notch  152  on base cylindrical member  130 , and a cooperating overcenter spring means  162  extends between spring seat notch  158  on reversing toggle device  64 A and spring seat notch  154  on base cylindrical member  130 . Spring means  160  and  162  bias reversing toggle device  64 A in a clockwise direction as viewed in FIGS. 15 and 16, and in a counter-clockwise direction as viewed in FIG.  18 . The action of these spring means  160  and  162  reverses when seat notches  156  and  158  pass on either side of a centerline passing through the spring seat notches  152  and  154 . 
     The base plate  144  has an upstanding projection  94 A for rotating said toggle device  64 A it a counter-clockwise direction when contacted by the angularly adjustable radial projection  200 , and an outwardly extending radial projection  96 A for rotating said toggle device  64 A in a clockwise direction when contacted by the fixed projection  100 . Another projection  170  extends upwardly from plate  144 , radially inward of projection  94 A and attached thereto, for a purpose to be hereinafter described. Gear cage  18 A is formed having a top plate  20 A and a bottom plate  22 A with cooperating concentric center openings  21 A and  23 A, respectively, for placing over base cylindrical member  130 . Bottom plate  22 A rests on the base plate  144  of toggle device  64 A. The bottom plate  22 A has an elongated opening  24 A to receive the rotary input shaft  12 A and bearing sleeve  28 A, to provide a limiting movement between the gear cage  18 A and the base member  4 B for operation; this limiting movement being determined by the length of the elongated opening  24 A. This distance could limit the travel of the gear teeth of gear  34 A or  42 A towards engagement with the gear teeth of spur gear  26 A. Spur gear  26 A extends upwardly from the top of bottom plate  22 A to the top plate  20 A. 
     As shown in FIGS. 16,  17 , and  18 , one gear  34 A is mounted on an integral shaft  40 A extending downwardly from top plate  20 A of reversing gear cage  18 A and it is in a counter-clockwise direction from the spur gear  26 A. Gear  34 A is mounted to extend over the edges of top plate  20 A and bottom plate  22 A so that it engages output ring gear  50 . 
     Two gears  42 A and  44 A are mounted on integral shafts  46 A and  48 A extending downwardly from top plate  20 A of the reversing gear cage  18 A and they extend in a clockwise direction from the spur gear  26 A. Gear  42 A is an idler gear and is spaced from gear  34 A to permit alternate engagement with spur gear  26 A therebetween. Gear  44 A is mounted to extend over the edges of top plate  20 A and bottom plate  22 A so that it engages output ring gear  50 . Integral shafts  40 A,  46 A, and  48 A of top plate  20 A extend into matched openings in bottom plate  22 A and have a snap engagement at their ends. 
     To provide for the “lost motion” connection of toggle device  64 A with respect to rotation of gear cage  18 A, an arcuate cut-out  172  is placed on bottom plate  22 A to encompass projection  170 ; the ends of cut-out  172  providing the limits of rotative movement of projection  170 , and therefore, relative movement of toggle device  64 A with gear cage  18 A. Actuating post  60  and arcuate opening  88  provide this “lost motion” connection in the transmission device  1  of FIG. 1, and transmission device  1 A of FIG.  11 . 
     In driving operation, input shaft  12 A turns clockwise driving output ring gear  50  in an oscillating motion through a predetermined angle set by adjusting slot  118 A. This angle is shown as 180 degrees in the Figures. Starting from FIG. 16, drive gear  34 A engages spur gear  26 A of shaft  12 A and drives ring gear  50  counter-clockwise, bringing adjustable radial projection  200  into actuating contact with upstanding projection  94 A of toggle device  64 A, moving toggle device  64 A against spring means  160 ,  162  past an overcenter position reversing the action of spring means  160 ,  162 . This biases toggle device  64 A counter-clockwise for engagement of projection  170  with an end of cut-out  172  of gear cage  18 A. Further movement of ring gear  50  by drive gear  34 A continues to move radial projection  200  against upstanding projection  94 A which begins to pivot the gear cage  18 A for disengaging the drive gear  34 A. The reversed action of spring means  160 ,  162  then carries gear cage  18 A to its new clockwise driving position (see FIG. 18) where idler gear  42 A engages spur gear  26 A of shaft  12 A which drives drive gear  44 A, driving ring gear  50  clockwise; movement of ring gear  50  clockwise bringing fixed projection  100  into actuating contact with radial projection  96 A of toggle device  64 A, moving toggle device  64 A against spring means  160 ,  162  past an overcenter position, reversing the action of spring means  160 ,  162 . This biases toggle device  64 A clockwise for engagement of projection  170  with an end of cut-out  172  of gear cage  18 A. Further movement of ring gear  50  by drive gear  44 A continues to move fixed projection  100  against radial projection  96 A which begins to pivot the gear cage  18 A for disengaging drive gear  44 A. The reversed action of spring means  160 ,  162  then carries gear cage  18 A back to its counter-clockwise position (see FIG. 16) with drive gear  34 A engaging spur gear  26 A and driving ring gear  50  counter-clockwise. This oscillation continues as long as input shaft  12 A is driven. 
     FIG. 19 shows a modification of the configuration shown in FIG. 16 to include a separate reversing gear cage biasing spring  39 C. 
     The shiftable gear cage of FIGS. 1-13 will not stay engaged reliably with the transmission output drive shaft ring gear without the help of the gear cage terminal driving gears having at least some biting engagement relationship with the output ring gear when engaged on the side where the driving torque of the input shaft  12  wants to rotate the gear cage  18  out of driving engagement. As shown in FIGS. 1 through 5 the input shaft  12  is rotating clockwise, and frictional and driving torque on gear cage  18  pinion gears  30 ,  32 ,  34 ,  44  and  46  want to cause the gear cage  18  to be rotated clockwise as previously discussed, and move it out of driving engagement of driving terminal gear  46  with output ring gear  50  unless the gear cage is biased into engagement by shifting toggle device  64  or a separate second gear cage bias that is maintained up until the gear cage is shifted. Previous sprinkler reversing gear cages relied on the teeth of the gear cage terminal gear wanting to bite into the teeth of the output ring gear  50  to maintain driving engagement when the reversing toggle bias was removed. 
     With the shifting gear cage arrangement of FIGS. 14-19, there is no rotational input shaft torque applied to the gear cage  18 A or  18 B. This allows using much finer teeth for the shiftable gearing and smaller annular rotation of the gear cage and shifting mechanism. 
     In FIG. 19 the lower gear cage plate  22 B has been modified to include an inner cut out portion  33 B opening to the outer surface of cylindrical member  130  of base member  4 . Another spring seat notch  35 B has been added to cylindrical member  130  within the area of inner cut out portion  33 B of the lower gear cage plate  22 B. 
     The outer portion of cut out portion  33 B of lower gear cage  22 B also has a cooperating spring seat notch  37 B. An overcenter gear cage bias spring  39 B extends between spring seat notch  35 B on the cylindrical member  130  and spring seat notch  37 B on lower plate  22 B of the gear cage  18 B. Spring  39 B now biases the gear cage  18 B of this configuration in a clockwise or counter-clockwise driving position until positively shifted by the action of the overcenter toggle shifting arm  64 A as previously discussed for the reversing configuration of FIGS. 14 through 18. 
     The gear cage bias incorporated in this manner provides the same advantage for this gear cage as desired and previously described for the toggle device of FIGS. 1 through 14 and an objective of this invention. The fact that the inner end of the biasing spring  393  is fixed and the outer end acts at a greater radius on the gear cage, provides more torque to move the gear cage as was explained for the overcenter shifting toggle device  64 A of the configurations of FIGS. 14 through 18. 
     As previously explained for the camming surface gear cage biasing spring discussions, once the engaging bias of the reversing toggle device  64  has been removed and not carried over center to be reapplied, if there is no secondary engaging biasing force on the gear cage  18 , rotation of the nozzle and output shaft  51  rotates the output gear carrying the driving pinion  34  or  44  of the gear cage out of driving engagement and the drive will not start itself again if left in a neutral position. 
     The primary reason to have the gear cage bias for this configuration is to allow the sprinkler nozzle to be manually rotated back and forth during installation and arc of oscillation adjustment to verify the ground coverage of the oscillation of the sprinkler. This would be especially true for sprinklers that did not incorporate the feature disclosed in the patent application Ser. No. 932,470, filed Nov. 18, 1986, where the arc of oscillation set is indicated on the top of the sprinkler. As the sprinkler nozzle is manually rotated back and forth the gear cage biasing spring keeps the gear cage driving pinion gear  34 C from being carried overcenter and prematurely engaging the other input shaft spur gear  27 C stopping the manual rotation of the nozzle turret before it correctly indicates the operating arc of sprinkler coverage which it is needed to know when the sprinkler is being installed. 
     Another benefit of the gear cage bias spring is that it can carry the gear cage further overcenter into engagement and allow the rotational travel of the shifting arm toggling device to be less than might be required if it were also required to bias the gear cage all the way into full driving engagement of the gearing. The toggle device now functions only as an overcenter carry mechanism for the gear cage bias once the gear cage has been driven out of driving engagement. This additional engagement travel is illustrated in FIG.  19 . It can be seen that tho added gear cage bias spring has carried the gear cage further clockwise opening a gap between the notch  172 D end  173 B and the toggle  64 A projection  170 B . 
     The widened cut-out opening  172 B which provides the lost motion connection between the shifting toggle device  64 B and the gear cage  18 B then allows the toggle to be further overcenter in the shifting direction for greater overcenter rotational torque by the toggle device  641  produced by its overcenter bias springs  160 B and  162 B before it again engages the other end  174 B of cutout opening  172 B to drive the gear cage out of driving engagement counter-clockwise and then over power the remaining bias of the gear cage bias spring  39 B to carry it overcenter and achieve the reversing action. 
     The gear cage  18 B is shown being biased fully clockwise with its driving terminal gear  34 B engaging input shaft  26 B and output shaft ring gear  50 B for driving the output shaft in a counter-clockwise direction. 
     The gear cage  18 B biasing spring  39 B exerts an engaging bias clockwise as shown against spring notch  37 B on the inside surface of cut-out  33 B which has been added to the now enlarged gear cage lower plate  22 B diameter in this area. The other end of spring  39 B is secured in an additional notch  35 B in the outside surface of cylindrical member  130 . 
     The pitch diameter of the gear teeth has been increased to have a larger number of smaller teeth in the driving terminal gears and input shaft spur gear and output shaft ring gear. 
     Gears are shown without teeth in some Figures, showing only the pitch circles and outside diameters for illustration of each of the gears. 
     The smaller gear teeth allow shifting from driving engagement in a clockwise direction through neutral to a driving direction counter-clockwise to be accomplished with a smaller annular rotation of the gear cage and smaller rotational travel of the shifting toggle. 
     Larger gear teeth are not required for biting engagement to hold the gear cage in driving engagement as the driving reaction force of the output ring  50 B gear through the driving terminal gear  34 B center shaft  40 B to the shiftable gear cage  18 B forces the gear cage in a backward rotational direction toward engagement with the input shaft  26 B. 
     Referring to FIG. 20 of the drawings, a sprinkler device  1 C is shown having a cylindrical housing  2 C positioned over and fixed to a base member  4 C. Cylindrical housing  2 C has an integral mid-flange  6 C having a center opening  8 C for a purpose to be hereinafter described. The end of cylindrical housing  2 C over base member  4 C has a circumference of an increased inner diameter  52 C forming an annular step  54 C. Base member  4 C is positioned in the increased diameter  52 C of cylindrical housing  2 C against the annular step  54 C. 
     Water passes up through the center of the base member  4 C through hole  17 C in cylindrical member  130 C and up through the hollow center of output shaft  51 C into the rotating nozzle assembly  3  for ejection out of the nozzle opening  122 C. 
     Base member  4 C has an upstanding cylindrical member  130 C. There is an annular groove around the inner top surface of upstanding cylindrical member  130 C in which a resilient seal  89 C is placed to separate the water from direct access to the gear box. Another seal  69 C is placed between annular flanges  102 C and  53 C to prevent dirty water from entering the gear box area. 
     Base member  4 C has two openings  10 C and  11 C therethrough positioned to one side and circumferentially separated from each other for receiving rotary input shafts  12 C and  14 C. 
     Below the surface  140 C of base member  4 C are two cavities  16 C and  17 C which intersect to allow gears  13 C and  15 C on input shafts  12 C and  14 C to interact and cause input shaft  14 C to be driven in a reverse direction to that of input shaft  12 C which is connected though its lower shaft  12 C to a source of rotational power such as a water turbine enclosed in the lower part of housing  2 C. The upper end of each of the counter rotating input shafts  12 C and  14 C are formed as spur gears  26 C and  27 C respectively. These spur gears are shown without teeth in FIG. 21 showing only the pitch circles and outside diameter for illustration. 
     The single shiftable driving gear  34 C is carried on the gear cage  18 C (shifting carrier) of this invention. 
     As shown in FIGS. 20 and 21 this driving gear  34 C is mounted on a shaft  40 C extending downwardly from the gear cage top plate  20 C of reversing gear cage  18 C. Driving gear  34 C is mounted to extend over the edge of the rib  30 C of the lower gear cage plate  22 C so that it can be shifted to engage either of the input shaft spur gears  26 C or  27 C. 
     The shiftable driving gear  34 C is also mounted to extend over the outer edge of lower gear cage  18 C rib  30 C to engage the output ring gear  50 C so that it may drive the output ring gear  50 C in a clock wise or counter clockwise direction when it is shifted by gear cage  18 C to engage input shaft spur gear  26 C or  27 C. 
     A reversing gear cage assembly, or shiftable drive assembly,  18 C is positioned within said cylindrical housing  2 C adjacent said base member  4 C and the reversing gear cage assembly  18 C is formed having a top plate  20 C and bottom plate  22 C with cooperating center openings  21 C and  23 C, respectively. 
     The gear cage  18 C (shifting gear carrier) of this invention needs only one shiftable connecting pinion gear  34 C that is shifted between engagement with one or the other of the counter rotation input shafts spur gears  26 C or  27 C to connect oscillating driving power to the output ring gear  50 C. 
     The single shiftable connecting pinion gear  34 C is mounted on shaft  40 C extending downwardly from the top plate  20 C. Posts  46 C and  48 C also extend down from top plate  20 C and the stepped reduced diameter lower ends ( 38 C for shaft  40 C) respectively extend into matched openings in the bottom plate  22 C and have a snap engagement at their ends with said openings to fix said top plate  20 C and bottom plate  22 C of the reversing gear cage (carrier) assembly  18 C together. 
     As shown in FIG. 21 a notched area  172 C extends across the opposite side of the center opening  23 C of the lower gear cage plate  22 C from where the single shiftable connecting pinion gear  34 C is mounted. The shiftable driving connecting pinion  34 C is mounted on its rotational center shaft  40 C on an arm  30 C which extends out from the center opening  23 C of the lower gear cage plate  22 C in between the input shaft spur gear  26 C and  27 C. 
     A reversing toggle shifting arm device  64 C is positioned just above the reversing lower gear cage plate  22 C and is also positioned around the cylindrical member  130 C of base member  4 C. The reversing toggle device  64 C has a center opening  66 C fitted around cylindrical member  130 C at the inner end of a radial arm  86 C and positioned for partial rotation around cylindrical member  130 C. An actuation arm  94 C extends upwardly from the radial arm  86 C of toggle device  64 C for contact by radial contact member  100 C and  200 C rotated by ring gear  50 C to rotate reversing toggle device  64 C in a clockwise or counter clockwise direction respectively. 
     On either side of the shifting arm  86 C are overcenter biasing spring notches on the outer side surfaces at  74 C and  76 C being 180 degrees apart. Cooperating spring seat notches  78 C and  80 C are placed on projections  82 C and  84 C, extending upwardly from the top surface of base member  4 C, adjacent the gear teeth of output ring gear  50 C. The spring seat notches  78 C and  80 C are located on a diametrical line through the center line of the cylindrical housing  2 , said diametrical line being 90 degrees to a line passing between the center of the cylindrical housing and bias spring notch  37 C on the outside wall of cavity  33 C below the top surface  140 C of base member  4 C. 
     An overcenter spring means  162 C extends between spring seat notch  74 C on reversing toggle device  64 C and spring seat notch  78 C on projection  82 C of base member  4 C, and a cooperating overcenter spring means  160 C extends between spring seat notch  76 C on the reversing toggle device  64 C and spring notch  80 C on projection  84 C of base member  4 C. Spring means  160 C and  162 C bias reversing toggle device  64 C in a clockwise direction as viewed in FIG.  21  and in a counter clockwise direction when carried overcenter by the action of arc control contact member  100 C or  200 C action against the reversing toggle device  64 C actuation arm  94 C. 
     To maintain a biasing force on reversing gear cage  18 C at all times, to keep the shiftable driving pinion gear  34 C into driving engagement with the ring gear  50 C and one of the input shafts spur gear  26 C or  27 C, a downwardly projecting member  31 C is located on the bottom of gear cage bottom plate  22 C of the reversing gear cage  18 C and extends into recess  33 C formed in the top of base member  4 C. Downwardly projecting member  31 C is located on the plate  220  below the shifting area  172 C with a spring seat notch  35 C facing outwardly along a radial line through the center of cylindrical member  130 C. A cooperating spring notch  37 C is positioned on the outer wall of recess  33 C on a line passing through the center of cylindrical member  130 C. 
     Overcenter spring  39 C (and spring means  160 C and  162 C) are formed from ribbon-like spring material, for example steel, and shaped with an intermediate arcuate portion and oppositely directed straight portions to engage the spring seat notches. 
     The biasing force of overcenter spring means  29 C is made less than the combined biasing force of overcenter spring means  160 C and  162 C at the rotation position of disengagement, so that overcenter spring means  39 C will only maintain the driving gear of reversing gear cage  18 C in engagement until the overcenter spring means  160 C and  162 C actually go overcenter and force the toggle device  64 C to its overcenter other side, the toggle device  64 C lower extension arm  90 C then contacting the end surface  173 C or  174 C of the gear cage notch area  172 C which constitutes a mechanical lost motion connection between reversing toggle means  64 C and shiftable gear cage (carrier)  18 C. 
     For this configuration, as shown in FIG. 20, arc control contact member  100 C has been relocated from the lower left under edge of output ring gear  50 C, as shown in FIG. 14, to a cylindrical flange area  53 C of output drive means  49 C. The location of the arc control contact members is not significant to the function of the invention. Arc of oscillation extremes contact control means only needs to cause the shifting lever device (toggle)  64 C to be moved to cause the reversing action to be initiated at the appropriate arc of rotation positions. For example the desired arc extremes could be established by a second annularly displaced actuation arm such as  94 C also mounted or connected to the toggle device  64 C and then only one actuation member would rotate with the nozzle and output drive means  49 C between the two toggle connected arc control contact means to achieve the same reversing result at a desired arc of coverage. 
     The rotational driving action of arc control contact member  100 C or  200 C as shown which do rotate with the nozzle and output drive means are moved against the actuation arm  94 C of reversing toggle  64 C rotationally driving the reversing toggle overcenter of its biasing springs  160 C and  162 C and now causing the gear cage to be rotated by the action of lower extension arm  90 C contacting the end surface  173 C or  174 C of the gear cage notch. The gear cage  18 C is now move out of driving engagement over its bias means  39 C center reversing its biasing direction to now cause the connecting gear driving pinion gear  34 C to be moved to engage the other counter rotating input shaft spur gear  26 C or  27 C and causing the output ring gear  50 C to be driven in the opposite direction. 
     In all of the configurations disclosed in this continuation in-part application, the reaction force on the driving connecting pinion gear reversing gear cage and output gear are to hold engagement with the input shaft spur gear during driving, however a gear cage biasing spring is still provided to further ensure that as previously discussed in patent applications Ser. No. 932,470, filed Nov. 18, 1986, that should the sprinkler nozzle output shaft be turned manually from the outside during handling installation or adjustment that it not be left with the reversing toggle positioned sufficiently off of engagement with the reversing gear cage so that the gear cage driving pinion gear teeth will not be touching the teeth of one of the input shaft spur gear  26 C or  27 C which would then not allow it to walk the gear cage back into the full engagement position either clock-wise or counter clockwise and drive the output ring gear. 
     It should be noted that if the reversing toggle is not holding the gear cage driving pinion  34 C into engagement with one of the input shaft spur gears  26 C or  27 C and there is no gear cage bias provided when the output shaft ring gear, as shown in FIG. 21, is manually rotated counter-clockwise, the driving direction, it carries the driving pinion gear  34 C and gear cage counter-clockwise disengaging the driving pinion  34 C from the input shaft spur gear  26 C. If the nozzle and output drive gear are further manually rotated counter-clockwise driving pinion gear  34 C will be carried over to engagement with input gear  27 C. The reversing toggle  64 C will have been lifted off of contact with the gear cage  18 C and carried short of its overcenter reversing position. When the water is again turned on to the sprinkler and the input shafts start to turn the sprinkler will turn slightly in the reversed direction and stop remaining in this disengage dead center position. This is only a very small arc and the action must have been created by manual external handling. 
     Also the gear cage biasing spring as previously discussed can be used to provide additional rotational travel for the gear cage over that provided by the reversing toggle overcenter springs which for the configuration of springs shown the springs tend to jump out of their end notches  74 C or  76 C if the rotation of the reversing toggle device  64 C exceeds more than 30 degrees on either side of center. Since it is desired to have a lost motion connection between the reversing toggle device  64 C and the gear cage  18 C where the reversing toggle springs are sufficiently overcenter before the toggle engages the reversing gear cage on the other side of center to over power the gear cage biasing spring before or as it is driving the gear cage out of engagement, a substantial amount of this available 30 degrees is consumed prior to the gear cage being contacted to move it. 
     The addition of the overcenter biasing spring to the gear cage thus also reduces the sensitivity of the reversing mechanism to manufacturing tolerances ensuring reliable operation under all conditions. 
     In the configuration shown in FIG. 23, output ring gear  50 D of output driving member  49 D is mounted for concentric rotation and driving engagement with output shafts  51 D and  251 . Driving engagement between output driving member  49 D and the outer output shaft  51 D is achieved by a lightly serrated frictional area  167 D formed between radial flange  102 D and under surface of radial flange member  53 D. This arrangement provides a torque limiting clutch action. 
     Concentric output shafts  251  and  51 D pass through the center hole  61 D in the output driving member  49 D, through a thrust bearing washer  57 , out of cylindrical housing  20  through its center opening  8 D and are locked together in a nozzle assembly  3 D or may be a single piece. Means can be provided to change the angular relation of shafts  251  and  51 D and respective contact members  100 D and  101 D, if desired. 
     The inner concentric output shaft  251  also has a radial annular flange  104 D. Both radial flange  102 D of output shaft  51 D and radial flange  104 D of output shaft  251  have radial contact members  101 D and  100 D which are arcuately positioned as desired to achieve the desired oscillation arc control by their action when contacting the actuation arm  94 D of the reversing mechanism. 
     In the reversing mechanism configuration shown in FIG. 22 and 23 the shiftable gear cage has only one shiftable connecting pinion gear which is alternately shifted between driving engagement with one or the other of two counter rotating input shafts as for the configuration shown in FIG. 20 and 21, however the shiftable gear cage  18 D pivotal center has been moved to the outside circumference of the housing  2  and no longer has cooperating center openings for rotation about the central cylindrical member  130  of base member  4 D. 
     The gear cage  18 D now takes the form of a shiftable yoke  22 D which surrounds the cylindrical member  130 D and has clearance areas  23 D and  24 D to avoid shifting interference with counter rotating input shaft spur gear  26 D and  27 D. 
     The shiftable yoke  22 D is stepped downwardly at  28 D on each side connecting across on the bias spring side to allow clearance for the single biasing spring coils to pass between the toggle arm  86 D and the top of the shiftable yoke  22 D along the portion of the yoke. Again a single connecting pinion gear  34 D is shifted from driving engagement between the output ring gear  50 D and one of the counter rotating input spur gears  26 D or  27 D for driving the output ring gear  50 D in one direction or the other. The shifting arm reversing toggle device  64 D is however still rotated through its clockwise and counter clockwise shifting positions about cylindrical member  130 D. However the overcenter bias is now not provided by two individual springs on either side of the toggle arm. Instead a single biasing spring  500  is provided which simultaneously biases the gear cage  18 D and reversing toggle device  64 D. This is now possible to have a single spring directly act on both the overcenter gear cage  18 D and overcenter reversing shifting toggle arm  64 D since the reversing gear cage pivot has been located to the outside of the shaft axis of the gear cage connecting driving pinion gear  34 D and achieves correct driving engagement for reaction force biting engagement when it is moved in the opposite direction to that of the shifting arm toggle device  64 D which must be shifted in the direction of rotation of the output shaft  51 D to achieve the reversing action when contacted by arc control contact members  100 D or  101 D which are rotatable with the nozzle and output shafts. 
     A multiple coil wire gear cage biasing spring  500  is shown with one end  501  being bent down and inserted into a hole  502  in the yoke  22 D at its outside center edge away from the gear cage pivot shaft  19 D. The other end  503  of the wire spring  500  is bent upward and is placed through a hole  504  towards the end of the toggle shifting arm  86 D away from the rotation center for the toggle device around cylindrical member  130 D. This hole  504  is out-board of the hole  502  for the spring end through the shifting yoke  22 D of gear cage  18 D so that as the shifting arm  64 D is rotated by the arc control contact means  100 D or  101 D contacting the upper end of the biasing spring wire end  503 , which extends upward to also serve as the actuation arm  94 D for the reversing toggle means  64 D, the biasing spring end hole  502  in the gear cage  18 D will pass hole  504  in the toggle  64 D at an outside radius so that the coil  506  and legs  507  and  508  of the single biasing spring  500  will be rotated to the inside where there is adequate clearance for it to be reversed toward the inside the opposite of what is shown in FIG. 23 with the gear cage now moved fully clockwise and the reversing toggle device moved fully counter clockwise for clockwise driving of the output ring gear  50 D. 
     Stops  510  and  512  are provided to limit the rotational travel of the reversing toggle  64 D so that the connecting biasing spring  500  can now force the gear cage  18 D overcenter to the other shifting position and the toggle  64 D to its other overcenter reversed position. 
     The advantage here is the simplicity of a single biasing spring for production assembly and the simultaneous reversal of the shifting toggle arm device  64 D and gear cage  18 D engagement bias. The gear cage is biased into engagement up to the moment of shifting, whether the transmission is driving itself or the output shaft and ring gear are being manually positioned as may sometimes be done during installation. There is no need for the shifting toggle springs to have to overpower the gear cage bias spring. 
     To now describe the gear cage  18 D in more detail, it consists of an upper plate  20 D and a lower plate  22 D or yoke. The single driving pinion gear is mounted on a shaft  40 D extending downwardly from the upper plate  20 D through the center of shiftable connecting driving pinion gear  34 D and into a mating hole on an arm portion  30 D of the lower gear cage plate  22 D which extends toward the center of the housing  2 D from the gear cage pivot  193 . The shiftable connecting driving pinion gear  34 D overhangs the sides of arm portion  30 D so as to have clearance to engage input shaft spur gear  26 D or  27 D. 
     A portion of the lower gear cage plate  22 D yoke is stepped downwardly at  28 D and  29 D and connected with plate surface  21 D to form a completely hooped yoke around cylindrical member  130 D. The stepped surface at  28 D and  29 D can serve as an angular (rotational) stop for the gear cage to control the engagement pressure of the driving pinion gear against the input shaft spur gears  26 D and  27 D. Lower connecting surface  21 D of the lower gear cage plate  22 D or yoke provides vertical clearance space for the legs  507  and  508  and coil  506  of the biasing wire spring  500  to pass over each other during toggling. 
     The shiftable connecting pinion gear  34 D maybe replaced by a rubber wheel if so desired which is only a friction drive providing a clutching action if the nozzle and output drive shaft are force rotated past the normal reversing stops where gear engagement in a reversed driving direction would normally have stopped further rotation in that direction instead of providing the slip clutch between the output shaft  51 D and the output driving member  49 D, shown for FIG.  23 . 
     The upper end of the biasing spring wire  500  which is extending upwardly through the reversing toggle device arm  64 D now serves as the toggle device actuation arm  94 D which when contacted by the arc control contact member  100 D or  101 D carries the toggle shift device over its bias center in the direction of rotation of the driving ring gear  50 D of output driving member  49 D. 
     This wire shifting actuation arm  94 D can be bent out of the way of the arc control contact members also acting as a clutch to prevent damage to the reversing mechanism during forced rotation of the sprinkler nozzle outside of the reversing limits of the transmissions. 
     The reversing transmission shown in FIG. 25 has the same shifting gear cage arrangement of FIG. 20 with a shiftable connecting pinion gear  34 E shiftable between counter rotating input shaft spur gears  26 E and  27 E. There is however for the reversing transmission configuration shown in FIG. 25 no shifting arm toggle device. Instead the overcenter carry action required once the shiftable connecting driving pinion gear  34 E has been driven out of engagement by the action of the arc control contact members  100 E or  101 E being driven against the actuation wire  94 E. The actuation wire  94 E is directly mounted on the lower gear cage plate  22 E and is deflected an arcuate distance sufficient to carry the gear cage and its biasing spring  39 E the remaining overcenter distance after disengagement occurs between the drive pinion  34 E and input shaft sour gear  26 E or  27 E by the now stiffened actuation wire  94 E when loaded against post  95 E or  96 E which also are shown extending upwardly from the lower gear cage plate  22 E in FIG.  26 . More complete details of a reversing transmission operation with this type of action is the subject matter of referenced U.S. Pat. No. 5,143,991, issued Sep. 22, 1992, and should be included into this continuation-in-part application as if fully disclosed herein. 
     Detail of the actuation wires stiffening posts configuration is shown in FIG. 27 where the upper arc control contact member  101 E is being rotated towards the right and is shown about to contact the action wire arm  94 E to deflect it to the right to contact stiffening post  95 E. 
     To have this work properly the overcenter biasing force necessary to carry the gear cage overcenter must become less than the force necessary to disengage the shiftable driving gear as the deflection force for carry over must be accumulated against any driving reaction force on the gear cage and the gear cage biasing spring force. Once the gear cage overcenter carry action begins, the bendable actuation wire  94 E force continues to diminish as it is returned to its neutral upright position while producing the overcenter carry action for the reversing gear cage. 
     FIG. 28 shows a shaped cam action gear cage bias spring configuration where downwardly extending leg  31 F of the gear cage configuration shown in FIG. 26 has been modified to be a triangular shaped piece  31 F now interacting with the surfaces on a leaf spring  39 F which enters from a cavity  401  to one side of the cavity  33 F with the leaf spring position secured by its other end which encompasses a post  400  in cavity  401  of base member  4 F. 
     The shaped end of gear cage biasing leaf spring  39 F has two different slopes as shown at  402  and  403  and  404  and  405  on either side of its center positions. The gear cage shifting arcuate movement for this configuration is totally balanced with full engagement of the connecting driving pinion gear  34 E occurring at the same angular displacement of the gear cage on either side of its overcenter position. 
     The force necessary to over power the gear cage biasing spring is greater when the gear cage camming leg  31 F is engaging the steeper surface  402  or  405  of the biasing leaf spring  39 F than when the spring is deflected and it is being forced over its more gradually sloped surface  403  or  404  surfaces. This is the action desired to enhance the action of the overcenter carry wire configuration of FIG. 26 which eliminated the need for an overcenter shifting toggle device part. Shaft camming surfaces for changing the biasing force on the gear cage were previously discussed for FIG. 13 of application Ser. No. 932,470, filed Nov. 18, 1986, the original parent application. 
     FIGS. 29 and 30 show a modification of FIGS. 20 and 21 to further clarify that the gear cage with the single driving gear for engaging two separate driving counter rotating input gears can be pivoted to move side to side about the axis of the output shaft with the gear cage pivot displaced off of the center axis of the output drive shaft but still inside of the radial location of the two counter rotating input shafts. Displacing the pivotal center of the shiftable gear cage increases the shifting mechanical advantage making it easier for the shifting arm toggle to move the shiftable gear cage driving terminal gear out of driving engagement. The driving reaction force is trying to keep the shiftable driving terminal gear in driving engagement until disengaged and shifted to its alternate reversed driving position. 
     FIG. 29 of the drawings is a cross sectional side elevation of the sprinkler device as shown in FIG. 20 modified by the addition of a different shaped gear cage  18 G and a gear cage pivot shaft  700  which is displaced off of the center A of the output shafts  51 C and  168 A on a radius between the output shafts&#39; center A and the centers of the counter rotating input shafts  12 C and  14 C (see FIG.  22 ). The upper ends of each of the counter rotating input shafts  12 C and  14 C are formed as spur gears  26 C and  27 C, respectively. 
     The shape of the shiftable gear cage  18 G is changed from that shown in FIG. 21 to provide additional clearance in the center area  710  for the shiftable gear cage  18 G to shift from side to side about the cylindrical member  130 C (see FIG. 30) on pivot shaft  700 , and to extend around the counter rotating input shafts  12 C and  14 C. The remainder of the gear cage  18 G is formed and functions as the gear cage  18 C of FIGS. 20 and 21. 
     The gear cage pivot shaft  700  pivots in a hole  702  through surface  140 C in base member  4 C. The pivot shaft  700  extends upward out of surface  140 C and is fixed in hole  704  in an inwardly extending rib  30 G of the lower gear cage plate  22 G of the shiftable gear cage  18 G. Driving gear  34 G, carried by a shaft  40 G mounted between top plate  20 G and lower plate  22 G of gear cage  18 G, extends over the side edges of the rib  30 G so that the driving gear  34 G can be shifted around pivot shaft  700  to engage either of the spur gears  26 C or  27 C of counter rotating input shafts  12 C and  14 C. Shaft  40 G has a reduced diameter lower end  38 G which has a fixed snap engagement with a matched opening in the lower gear cage plate  22 G. Other posts  46 G and  48 G extend between top plate  20 G and lower gear cage plate  22 G to fix said top plate  20 G and lower plate  22 G together. 
     The shaft hole  712  in driving gear  34 G is slightly enlarged for a loose fit on the shiftable gear cage shaft  40 G to accommodate the slight change in radius from the shaft  40 G to the output ring gear  50 C as the gear cage  18 G rotates. 
     The operation of this modification of the reversing gear drive shown in FIGS. 29 and 30 is the same as described for the gear drive configuration of FIGS. 20,  21 , and  22 . 
     Thus, while I have illustrated and described my invention by means of specific embodiments, it is to be understood that numerous changes and modifications may be made therein without departing from the spirit and scope of the invention as defined in the claims.