INFINITELY VARIABLE POSITIVE MECHANICAL TRANSMISSION

Abstract: Disclosed herein are embodiments of transmissions. In a first embodiment, a transmission is provided in which the input shaft (16) and output shafts are mounted for rotation with respect to each other on a common shaft, and power is transmitted from the input shaft to the output shaft utilising the gear (20) on the output shaft meshed with an idler gear (44), the idler gear (44) being coupled to the input shaft through a wobble plate mounted on the input shaft and the connecting rod coupled between the wobble plate (78) and the idler gear. In one aspect of this embodiment, a plurality of idler gears (44) are meshed with the gear (20) on the output shaft and each of the idler gears is coupled to the wobble plate through a connecting rod (68) and a one-way gear or brake (132). In a second embodiment of the present invention, a transmission is provided which may transmit power from an input shaft to an output shaft in a direct manner or alternatively through a predetermined low gear ratio, or through the use of a unique variable hydraulic torque converter at gear ratios continuously variable between unity and the aforesaid low gear ratio. The torque converter of this embodiment utilises the interaction of variably extensible pawls with a static fluid to vary the torque responsive to the sensed output load as well as to the speed of rotation of the input shaft.

Description: The present invention relates generally to transmissions, and particularly, but not exclusively, to transmissions which may achieve a continuously variable output torque. In both industrial and consumer applications, it is often necessary to provide a transmission between a source of power and the load in order to provide an adjustable torque. Typical examples of such devices are automobiles and tractors. Conventional transmissions used in such devices employ selectable gears, or fluid clutches. In years gone by, arrangements of belts and pulleys were used to provide an adjustable torque. Selectable gears are efficient in transmitting power between the input shaft and the output shaft, but are considered by many to be somewhat inconvenient since it is necessary to remove the load from the shaft with a clutch to change gear ratios. Planetary gear arrangements have also been employed, and planetary gears in combination with fluid clutches have provided transmissions with reasonable efficiency, although complicated and expensive to construct. BE-A-572406 shows an infinitely variable transmission having a wobble plate rotatably driven by an input shaft with a one way gear mechanism driven by connecting rods from the wobble plate, the one way gear mechanism driving through helical gears to an output shaft. Although the torque transmitted may be continuously varied there is no provision for reversing under load or braking the output. It is an object of the invention to provide a transmission which is highly efficient and which provides the ability to vary the torque between the input and output shafts. In addition, it is an object of the present invention to provide such a transmission in which the torque may be continuously varied, even while maintaining the transmission under load. It is a further object of the present invention to provide such a transmission in a first embodiment which may be reversed, even while maintaining the transmission under load. It is a further object of the present invention to provide a second embodiment of a transmission which combines various aspects of positive drive and continuously variable torque output. Additionally, it is an object of the present invention to provide such a transmission which is simple to construct, relatively inexpensive, and durable. A transmission according to the present invention comprises in combination: an input shaft, an output shaft, means including a housing for mounting the input and output shafts on a common axis with each of said shafts rotatable with respect to each other and with respect to the housing, a wobble plate with an opening at its centre disposed about the input shaft, means operatively associated with the input shaft to wobble the wobble plate about a fixed position on the input shaft in unison with rotation of the input shaft, a first gear having a central axis, said first gear being mounted on the output shaft with its central axis coaxial with the output shaft for rotation with the output shaft, a third shaft mounted on the housing, said third shaft having a central axis disposed normal to the central axis of the first gear, a second gear being a helical gear journalled on said third shaft and arranged to drive the first gear, the second gear being rotatable with respect to both the housing and the third shaft, a second plate pivotally mounted on the third shaft and extending outwardly from the first gear, a connecting rod disposed in a plane traversing the input and output shafts, said plane being perpendicular to the axis of the third shaft, the connecting rod being pivotally mounted at one end on the second plate, the other end of said rod being coupled to the periphery of the wobble plate, and a one-way gear mechanism mounted between the second plate and the second helical gear characterised in that said one-way gear mechanism is mounted to the second plate and comprises the second gear, a second rod mounted on the second plate outwardly of the second gear, the axis of the second rod being parallel to the axis of the third shaft, a casing mounted on the second rod and secured thereto, a pin mounted on the casing normal to the second rod and spaced from the second rod, said pin being disposed in the plane normal to the third shaft and centrally traversing the second gear, a third gear being a helical gear journalled on the pin and engaging the periphery of the second gear, and a pivot mechanism coupled to the casing to pivot the casing on the second rod. The present invention will be understood from the following specification and the accompanying drawings, in which: Figure 1 is a sectional view taken along the axis of the input or drive shaft of the first embodiment of the present invention; Figure 2 is a sectional view taken along the line 2-2 of Figure 1; Figure 3 is a sectional view taken along the line 3-3 of Figure 1; Figure 4 is a sectional view taken along the line 4-4 of Figure 1; Figure 5 is a sectional view taken along the line 5-5 of Figure 1; Figure 6 is a sectional view of another embodiment of the present invention taken along a line corresponding to Figure 2; and Figure 7 is a sectional view taken along the line 7-7 of Figure 6. As illustrated in Figures 1-5, the first transmission embodiment has a housing 10 with aligned apertures 12 and 14 on opposite sides thereof. A drive shaft, or input shaft, 16 is journalled within the aperture 12, and a driven shaft, or output shaft 18, is journalled within the aperture 14. The output shaft 18 carries a helical gear 20 at its inner end, the helical gear 20 being mounted with its central axis coaxial with the output shaft 18. The helical gear 20 is provided with a cylindrical cavity 22 which extends therein along the central axis thereof, and the cavity 22 accommodates a cylindrical stub 24 protruding coaxially from the end of the input shaft 16, the stub 24 being journalled in the cavity 22, thereby maintaining the drive shaft 16 and driven shaft 18 coaxial and rotatable with respect to each other. The aperture 14 in the housing extends through a wall at one side of the housing designated 26, and four partitions 28, 30, 32 and 34 extend inwardly from the wall 26 to confront different sides of the helical gear 20. Each of the partitions has two flat walls 36 and 38 disposed normal to each other and in planes parallel to the axes of the drive shaft 16 and driven shaft 18. The walls 36 of partitions 28 and 34 are disposed in the same plane, and this plane is parallel to a plane which contains the walls 36 of partitions 30 and 32. In like manner, the wall 38 of partition 34 is disposed in the same plane as the wall 38 of partition 32, and the walls 38 of partitions 28 and 30 are disposed parallel to said plane and in the same plane. The walls 36 of partitions 28 and 30 are provided with aligned apertures 40 which accommodate a pin 42. The pin 42 is journalled within the apertures 40, and carries a helical gear 44 which is mashed with the helical gear 20. The helical gear 44 is journalled for rotation on the pin 42, and a pair of side plates 46 and 48 of a housing 50 are also provided with apertures 52 and 54 which are journalled about the pin 42 for rotation with respect thereto. The housing 50 also has a second pair of side plates 56 and 58, the plate 56 being spaced from and adjacent to the plate 46 and the plate 58 being spaced from and adjacent to the plate 48. The plate 56 is maintained in position with respect to the plate 52 by means of a spacer 60 which is secured between the plates 52 and 56, and the plate 58 is maintained in position with respect to the plate 54 by means of a second spacer 62 secured thereto. A pin 64 extends between the plates 52 and 56 adjacent to the perimeter of the helical gear 44, and a second pin 66 extends between the plates 48 and 58 in alignment with the pin 64. One end of a connecting rod 68 is bifurcated into two parallel portions 70 and 72. The portion 70 has an aperture 74 which accommodates the pin 64, and the portion 72 has an aperture 76 which accommodates the pin 66. Hence, the portions 70 and 72 are journalled on the pins 64 and 66 and thus secured on the housing 50. The connecting rod 68 is disposed in a common plane with the drive shaft 16 and driven shaft 18 and is generally parallel to the axis of these shafts. The end of the connecting rod 68 opposite the housing 50 is mounted on a wobble plate 78 which is caused to wobble in synchronism with rotation of the drive shaft 16, as will be hereinafter described. As a result of wobbling of the wobble plate 78, the connecting rod 68 causes the housing 50 to oscillate back and forth on the shaft 42. The housing 50 is coupled to the helical gear 44 by means of a one-way gear 80 or one-way brake to be described hereinafter. The wobble plate 78 utilises a cylindrical disk 82 with a central aperture 84 which accommodates the input or drive shaft 16. A pin 86 extends centrally through the aperture 84 and through a bore 88 which extends through the central axis of the drive shaft 16, thereby securing the wobble plate 78 on the drive shaft. The aperture 84 in the disk 82 of the wobble plate 78 is shaped to permit the wobble plate to pivot with respect to the drive shaft 16. The disk 82 has a flat cylindrical periphery 90, and a pair of grooves 92 and 94 are disposed adjacent to the periphery 90 and form races for balls 96. A U-shaped cylindrical cap 98 is disposed about the perimeter of the disk 82, and the cap contains grooves 100 and 102 which form races for the balls 96. Hence the cap is free to rotate with respect to the disk 82. The cap is provided with an outwardly extending pin 104 which contains a substantially spherical body 106. The end of the connecting rod 68 opposite the housing 50 is journalled about the spherical body 106 by means of a mating opening 108 in an end hub 110 of the connecting rod 68. The connecting rod 68 is thus free to translate the wobbles from the wobble plate 78 to the housing 50. The angle of the wobble plate with respect to the drive shaft 60 is controlled by a lever 112 which is pivotally mounted by means of a pin 114, the pin being secured on a structural rib 116 mounted on the housing 10. A sleeve 118 is translatively disposed about the drive shaft 16. The sleeve 118 carries a collar 120 mounted in fixed position on the sleeve by means of a ball bearing assembly 122. The end of the lever 112 is mounted on the collar 120 by means of a pin 124 and a lever arm 126. The end of the sleeve 118 adjacent to the wobble plate 78 is connected to the wobble plate by means of an arm 126 which extends from the sleeve normal to the drive shaft 16 and a link 128 pivotally connected by means of pins 129A and 129B. The drawings illustrate a particular one-way brake 80 for coupling the connecting rods 68 to the helical gear 44, but it should be understood that other types of one-way clutches may also be employed. The particular one-way brake 80 illustrated is of particular advantage due to its simple construction, low cost and reversibility. The one-way brake 80 utilises a rod 130 which extends through the side plates 46 and 48 of the housing 50, and the rod is rotatable with respect to the side plates. A casing 132 is mounted on the rod 130 between the side plates 46 and 48, and is affixed to the rod and rotates with the rod. The casing 132 has a pair of side walls 134 and 136 which depend from the rod 130 and a pair of end walls 138 and 140 which extend between the side walls 134 and 136 to form a rectangular housing. A pin 142 extends centrally between the end walls 138 and 140, and a helical gear 144 is journalled on the pin 142. The helical gear 144 engages the perimeter of the helical gear 44. The rod 130 is connected to a mechanism for pivoting the casing 132 with respect to the axis normal to the drive shaft 16 and driven shaft 18, this mechanism being designated 146. If the pin 142 is disposed parallel to the tangent to the helical gear 44 at the point of contact of the helical gear 44 and the helical gear 144, then the gear 144 tends to rotate with the helical gear 44. However, if the mechanism 146 pivots the pin 142 from the position described above, then the helical gear 144 will act as a latch to prevent rotation of the helical gear 44 in one direction, but will permit rotation in the reversed direction. The helical gear 144 acts as a latch with respect to helical gear 44 for rotation of the helical gear 44 toward the lower leading edge of the helical gear 144. Accordingly, wobbling of the wobble plate 78 causes the connecting rod 68 to reciprocate, thus driving the housing 50 in a periodic motion on the shaft 42. The one-way brake 80 will transmit the reciprocal motion of the connecting rod 68 to the helical gear 44 in either direction depending upon the angle at which the helical gear 144 is positioned by the pivot mechanism 146. Since the helical gear 44 drives the helical gear 20 and the driven shaft 18, the direction of rotation in response to a unidirectional drive on the drive shaft 16 may be controlled by the pivot mechanism 146. In the particular embodiment of the present invention, the pivot mechanism 146 utilises a spring steel member 148 which is attached to one end of the rod 130 and depends therefrom. The opposite end of the spring steel member engages a pawl 150 mounted on a flat surface of a bevel gear 152. The bevel gear 152 is secured on the pin 42, and the pin 42 extends to a control lever 154. In the present construction, it is not contemplated that the connecting rod 68 will rotate the helical gear 44 throughout 360° of rotation, and the present construction contemplates drive for the helical gear of no more than 90°. Accordingly, the transmission is provided with a plurality of helical gears identical to the helical gear 44 to drive the output shaft through a substantial portion of the 360° cycle. In the particular construction, these additional helical gears are designated 44A, 44B and 44C. The helical gear 44A is journalled on a pin 42A which is rotatably mounted between the walls 38 of the partition 28 and partition 34. In like manner, the helical gear 44B is journalled on a pin 42B which is rotatably mounted between the walls 36 of the partitions 34 and 32. Likewise, the helical gear 44C is journalled on a pin 42C rotatably mounted on the walls 38 of the partitions 32 and 30. Each of the helical gears 42A, 42B and 42C is coupled to a connecting rod 68A, 68B or 68C, respectively, and the connecting rods are coupled to the cap 98 of the wobble plate 78 in a manner identical to the connecting rod 78 at locations equally spaced about the perimeter of the cap 98. Also, each of the connecting rods 68A, 68B and 68C is coupled to the helical gear 44A, 44B and 44C by means of a one-way gear or brake 80A, 80B or 80C, respectively, the one-way gear being identical to the one-way gear 80. It is necessary for each of the one-way gears 80A, 80B and 80C to be provided with a pivot mechanism similar to the pivot mechanism 146 operable with the one-way gear 80. The one-way gear 80A has a depending spring steel member 148A, which engages a pawl 150A on the flat surface of a bevel gear 156. The bevel gear 156 meshes with the bevel gear 158 mounted on the end of the pin 42 opposite the bevel gear 152 to transmit rotational motion from the lever 154 to the bevel gear 156. The bevel gear 156 is mounted on one end of the pin 42A, and a bevel gear 160 is mounted on the opposite end of the shaft 42A. The bevel gear 160 is meshed with a bevel gear 162 mounted on the opposite end of the shaft 42B. The bevel gear 164 is meshed with the bevel gear 166 mounted on one end of the pin 42C, the opposite end of the pin 42C carrying a bevel gear 168 which is meshed with the bevel gear 152 on the pin 42. The one-way gear 80B is provided with a spring steel member 148B which engages a pawl 150B on the bevel gear 162 to provide actuation of the pivot mechanism 146B. In like manner, a spring steel member 148C of a pivot mechanism 146C for the one-way gear 80C extends to a pawl 150C on the back of bevel gear 166. In order to provide redundancy, the one-way gear 80 is provided with a second pivot mechanism 170 operating from the end of the rod 130 opposite the pivot mechanism 146, the pivot mechanism 170 being identical in construction to the pivot mechanism 146. In like manner, the one-way gear 80A is provided with a redundant pivot mechanism 170A, the one-way gear 80B is provided with a redundant pivot mechanism 170B, and the one-way gear 80C is provided with a redundant pivot mechanism 170C. In order to provide lubrication for the various moving parts of the transmission set forth in the drawings, the housing 10 is made fluid tight, and a body of oil 172 is disposed in the housing, the oil being fragmentarily illustrated. Figures 6 and 7 illustrate another embodiment of the present invention. The transmission of the embodiment of Figures 6 and 7 contains the same housing 10, drive shaft 16, and wobble plate 78, but the helical gears 20 and 44, 44A, 44B and 44C have been replaced by bevel gears or miter gears, and in place of utilising four idler gears 44, 44A, 44B and 44C three such gears are employed. As illustrated in Figure 6, the input or drive shaft 16 is journalled on the axis of a bevel gear or miter gear 174 mounted coaxially at the end of the output or driven shaft 18 for rotation therewith. The bevel gear 174 corresponds in the embodiment of Figures 6 and 7 with the helical gear 20 of the embodiment of Figures 1 through 6. Three flat partitions 176, 178 and 180 extend inwardly from the end wall 26 of the housing and are disposed at equal distances from the common axis of the input shaft 16 and output shaft 18, and are further equally spaced about the output shaft 18. Each of the partitions 176, 178 and 180 is provided with an aperture 182, 184 and 186, respectively, the aperture being disposed in a common plane normal to the output shaft 18. A shaft 188 is mounted in the aperture 182 and locked in position with respect to the partition 176. A shaft 190 is disposed within the aperture 184 and locked in position with respect to the partition 178. A shaft 192 is disposed within the aperture 186 and locked in position with respect to the partition 180. Each of the shafts 188, 190 and 192 are threaded at their ends, and a locknut 194 is utilised to secure the shafts with respect to the partitions 176, 178 and 180, respectively. A sleeve 196 is rotatably journalled on the shaft 188, and a miter gear 198 is mounted on the end of the sleeve 196 opposite the partition 176 and meshed with the miter gear 174. An idler gear 200 is mounted on the sleeve 196 to rotate therewith and the idler gear 200 corresponds to the idler gear 44 of the first embodiment of the present invention. A housing 202 having parallel walls 204 and 206 disposed on opposite sides of the idler gear 200 is journalled on the sleeve 196 by means of apertures 208 and 210 in the walls 204 and 206, respectively. A casing 212 is pivotally mounted within the housing 202 by means of a pin 214, and corresponds to the casing 132 of the first embodiment. A one-way gear 216 is mounted in the casing on an axis normal to the axis of the idler gear 200. As in the first embodiment, the idler gear is a helical gear as is the one-way gear 216. Rings 218 and 220 are mounted on the walls 204 and 206, respectively, on the side thereof opposite the idler gear 200, and the rings 218 and 220 are journalled about the sleeve 196. A U-shaped bracket 222 has its ends mounted on the rings 218 and 220, respectively, and extends outwardly about the perimeter of the idler gear 200. A spiral spring 224 is mounted at one end on the bracket 222 and on the other end on the end of a pin 226 which extends through the one-way gear 216, the gear being rotatable thereon. In this manner, the spring 224 places a pivotal force on the one-way gear 216 to limit rotation of the idler gear 200 to the counter-clockwise direction as shown in Figure 7. As illustrated in Figure 6, three miter gears are illustrated, the miter gears 198A and 198B being identical to the miter gear 198 and disposed on shafts 190 and 192, respectively. Each of the miter gears 198A and 198B are mounted on the end of sleeves 196A and 196B, and each of the sleeves rotatably carries a housing 202A and 202B identical to the housing 202. Each of the housings 202A and 202B pivotally carries a casing 212A and 212B, respectively, and the casing 212A contains a one-way gear 216A and the casing 212B carries a one-way gear 216B, the gears 216A and 216B being identical to the gear 216. The housings 202, 202A and 202B are provided with an end plate 227, 227A and 227B, respectively, the end plates extending between the walls 204 and 206. The end plate 227 carries an outwardly extending pin 228, and the end plates 226A and 226B carry outwardly extending pins 228A and 228B. A connecting rod 230 is mounted at one end on the pin 228, and extends generally parallel to the axis of the input shaft 16 and output shaft 18 to the wobble plate, not shown, which is identical to the wobble plate 78. In like manner, a connecting rod 230A extends from the pin 228A to the wobble plate, and a connecting rod 230B extends from the pin 228B to the wobble plate. The connecting rods 230A and 230B are also disposed generally parallel to the axis of the input shaft 16 and output shaft 18 and are translatable with movement of the periphery of the wobble plate in the manner illustrated above in connection with the embodiment of Figures 1 through 6. The embodiment of Figures 6 and 7 functions in substantially the same manner as the embodiment of Figures 1 through 6, except power is transmitted through each of the bevel gears 198 throughout approximately 120 o of its rotation. Further, the embodiment of Figures 6 and 7 does not permit reversal of the driven shaft 18 with respect to the drive shaft 16, since the springs 224, 224A and 224B maintain tension on the casing 212, 212A or 212B in the same rotational direction at all times.

Claims: A transmission comprising, in combination: an input shaft (16), an output shaft (18), means including a housing (10) for mounting the input and output shafts on a common axis with each of said shafts rotatable with respect to each other and with respect to the housing, a wobble plate (78) with an opening (84) at its centre disposed about the input shaft, means (118,126,128) operatively associated with the input shaft to wobble the wobble plate about a fixed position (88) on the input shaft in unison with rotation of the input shaft, a first gear (20,174) having a central axis, said first gear being mounted on the output shaft with its central axis coaxial with the output shaft for rotation with the output shaft, a third shaft (42,188,190,192) mounted on the housing, said third shaft having a central axis disposed normal to the central axis of the first gear, a second (44,200) gear being a helical gear journalled on said third shaft and arranged to drive the first gear, the second gear being rotatable with respect to both the housing and the third shaft, a second plate (46,48,204,206) pivotally mounted on the third shaft and extending outwardly from the first gear, a connecting rod (68,230) disposed in a plane traversing the input and output shafts, said plane being perpendicular to the axis of the third shaft, the connecting rod being pivotally mounted at one end on the second plate, the other end of said rod being coupled to the periphery of the wobble plate, and a one-way gear mechanism (80,216) mounted between the second plate and the second helical gear characterised in that said one-way gear (80,216) mechanism is mounted to the second plate (46,48,204,206) and comprises the second gear (44,200), a second rod (130,214) mounted on the second plate outwardly of the second gear, the axis of the second rod being parallel to the axis of the third shaft, a casing (132,212) mounted on the second rod and secured thereto, a pin (142,226) mounted on the casing normal to the second rod and spaced from the second rod, said pin being disposed in the plane normal to the third shaft and centrally traversing the second gear, a third gear (144,216) being a helical gear journalled on the pin and engaging the periphery of the second gear, and a pivot mechanism (146,170) coupled to the casing to pivot the casing on the second rod. A transmission as claimed in claim 1 wherein the pivot mechanism (146) comprises a flat strip (148) of spring material mounted at one end on the second rod (130), and a wheel (152) mounted on the third shaft (42) for rotation with the third shaft and carrying a pawl (150), said strip extending from the second rod in a plane perpendicular to the second rod and traversing the pawl, said pawl engaging one side of the flat strip responsive to rotation of the wheel in one direction and the side opposite the one side of the strip responsive to rotation of the wheel in the direction opposite the one direction, whereby rotation of the third shaft (42) pivots the third gear (144) withrespect to the second gear (44). A transmission as claimed in claim 1 or 2 wherein the one-way gear mechanism is provided with a control member (154) having a first position preventing clockwise movement of the second plate (46,48) with respect to the second gear (44), a second position preventing counter-clockwise movement of the second plate (46,48) with respect to the second gear (44) and a third and neutral position. A transmission as claimed in any one of claims 1 to 3 wherein said first gear (20) is a helical gear and wherein a plurality of third shafts (42,42A,42B,42C) mounted on the housing, each third shaft being disposed on an axis disposed in a plane common to the axes of the other third shafts, the axis of each third shaft intersecting the axes of two other third shafts at the same angle, a said second helical gear (44,44A,44B,44C) journalled on each of said third shafts, each of the second helical gears being of the same diameter and meshing with the first helical gear (20), a said second plate (46,48) pivotally mounted on each of the third shafts and extending outwardly from the first helical gear, a plurality of said connecting rods (68,68A,68B,68C), each connecting rod being disposed in a plane perpendicular to the axis of the third shaft, and traversing the input and output shafts, each connecting rod being pivotally mounted at one end on one of the second plates, the other end of each rod being coupled to the periphery of the wobble plate (78), the rods being coupled to the wobble plate at locations equally spaced about the perimeter of the wobble plate, and a plurality of said oneway gear mechanisms (80,80A,80B,80C), each one-way gear mechanism being mounted between one of the second plates and the adjacent second helical gear, each one-way gear mechanism being provided with a control mechanism (152,158,156,160,162,164,166,168) having a first position preventing clockwise movement of the second plate with respect to the second helical gear and a second position preventing counter-clockwise movement of the second plate with respect to the second helical gear, and third and neutral position. A transmission as claimed in claim 4 when dependent on claim 2 wherein the control mechanisms comprise each third shaft (42,42A,42B,42C) of said transmission being rotatably mounted and carrying a bevel gear (152,158,156,160,162,164, 166,168), at both respective ends thereof, the bevel gears of adjacent third shafts being inter-meshed, each of the bevel gears carrying a said pawl (150,150A,150B,150C) on the surface thereof adjacent to the second helical gear, a said flat strip (148,148A,148B,148C) of spring material mounted at one end on each of the second rods (130), each strip extending from said second rod in a plane normal to the third shaft and toward the third shaft, the end of each of the strips of spring material being positioned to engage one of the pawls, whereby rotation of the third shaft causes the pawls to engage the flat strips and thus pivots each third gear with respect to the adjacent second gear. A transmission as claimed in any one of claims 1 to 3 wherein said first gear (20) is a helical gear and meshes with one or more said second helical gears. A transmission as claimed in any one of claims 1 to 3 wherein said first gear (174) is a bevel gear and meshes with one or more further bevel gears drivably connected with a respective said second gear. A transmission as claimed in claim 1 wherein the one-way gear mechanism (80) comprises a) a brake housing (50,202); b) the third shaft (42,188) mounted in said brake housing rotatably supporting the second gear therein; c) the second rod (130,214) mounted in said brake housing substantially parallel to said third shaft; d) the casing (132,212) mounted on said second rod for pivotal movement thereon; e) actuating means attached to said casing for controllably pivoting said casing about said second rod whereby when said casing is pivoted to a position wherein the teeth of said helical second and third gears are substantially aligned with one another, said second gear is free to rotate in either direction and, further, when said casing is pivoted to a position wherein the teeth of said helical gears are misaligned with respect to one another, said second gear is constrained to rotate in one direction only. A transmission according to claim 8, further including biasing means (224) in said housing for biasing said carrier cage means in one direction of the pivoting, said actuating means acting against said biasing means in one direction of actuation thereof. A transmission brake according to claim 8 or 9, wherein said third shaft (42,188) is keyed to said second gear, whereby rotation of said third shaft causes rotation of said second gear.

Inventors: BLAKEMORE, JOHN H.
Applicants: BLAKEMORE, JOHN H.
Application year: 1988
Main classification: F16H29
IPC codes: F16H47, F16H29