Infinitely variable gear box

FIELD: mechanical engineering.

SUBSTANCE: infinitely variable gear box comprises a number of velocity governors. Driving disk (34), driven disk, and cylindrical bearing member (18) are in contact with the first, second, and third points on each of the velocity governors. Disk (60) of the thrust bearing transmits rotation to the driving disk. At least two generators of axial loading are interposed between the driven and driving disks and disk of the thrust bearing and can apply the axial loading to the driven disk.

EFFECT: improved structure.

62 cl, 27 dwg

 

The scope of the invention

The field of invention relates in General to cartons transmission, and more particularly the invention relates to a continuously variable gear boxes.

The present invention relates to continuously variable transmissions and includes several new features and inventive aspects that are developed and are improvements over existing technology. To provide an infinitely variable transmission developed various gear with rollers, in which the power is transmitted through the drive rollers supported in the housing between the input and output disks of torque. In such transmissions drive rollers are mounted on supporting structures, which upon rotation causes engagement of the leading rollers with drive torque in circles of different diameters depending on the desired gear ratio.

However, the success of such traditional solutions limited. For example, one solution is disclosed a drive bushing for a vehicle with steplessly adjustable transmission ratio. This method considers the use of two iris plates, one on each side of leading rollers to tilt the axis of rotation of each roller. However, the use of iris plates can be very complicated is diversified due to the large number of parts, required to adjust the iris of the plates at the time of switching of the transmission. Another problem with this transfer is that it has a guide ring made with the possibility to be for the most part fixed relative to each roller. Since the guide ring is stationary, the offset of the axis of rotation of each of the top rollers is difficult.

One improvement over this earlier development includes a shaft, around which revolve the master element and the slave element. As a leading element and a driven element mounted on the shaft and in contact with a lot of power regulators, placed at equal distances around the circumference of the shaft. The power regulators are in frictional contact with both elements and transmit power from the driving element to the destination element. The supporting element located concentrically on the shaft and between the power regulators, applies a force to keep the separate power regulators to create frictional contact between the master element and the slave element. The limitation of this design is the lack of funds for adequate axial force to keep the master element and the slave element in sufficient frictional contact with the power regulators in the load torque of the PTO the NTA when changing gear. A further limitation of this design is the difficulty when shifting, which leads to situations with high torque and very low speed, and insufficient means for uncoupling the transmission and motion coasting.

Thus, there is a need for a continuously variable transmission with an improved mechanism for supporting the power regulators for the offset in the tool proper application of axial pressure to the master element and the slave element at different loads of torque and power and the means of uncoupling and re-coupling clutch for driving the reel.

The invention

Systems and methods have several features, none of which is solely responsible for the desired properties. More characteristics will be briefly discussed next, without limitation of amount, expressed in the following claims. After considering this discussion, and particularly after reading the section entitled "Detailed description of the preferred embodiments will become clear how the characteristics of the system and methods provide several advantages over conventional systems and methods.

In one aspect, disclosed a continuously variable transmission with the longitudinal axis and plenty of speed controllers. Each is th speed controller has an axis of rotation with adjustable tilt and is located radially outward from the longitudinal axis. Also includes a driving disk, which is able to rotate koltseobrazno around the longitudinal axis and also in contact with the first point on each of the speed controllers, and with the control element, which is also able to rotate koltseobrazno around the longitudinal axis. Provides a bearing disk, which is also able to rotate koltseobrazno around the longitudinal axis, and at least two axial force generator. These generators axial forces are located between the master disk and the bearing disk, and each of the axial force generator is configured to apply axial force to the drive disk.

In another aspect of the disclosed bearing disk can rotate koltseobrazno around the longitudinal axis, and mechanism of release. The tripping mechanism may be positioned between the bearing disk and the leading disk and adapted to make driving disk leading to uncouple the drive speed controllers.

In another aspect of the disclosed output disk or rotary tubular casing with bearing disk can rotate koltseobrazno around the longitudinal axis of the transmission. Has a support element, is also able to rotate koltseobrazno around the longitudinal axis and adapted to move to any of the master disk and output disk, which rotates more slowly.

In olnamespace disclosed lever sub-node, with the hook, with the hook attached either to the master drive or bearing disk. There is also a lock that is attached either to the master drive or bearing disk.

In another aspect, disclosed many spindles with two ends, with one spindle is located in the bore hole of each of the speed controller, and there are many spindle supports with platform end and a spindle end. Each spindle support at work engages with one of the two ends of one of the spindles. Also, a plurality of spindle support wheels, and there is at least one spindle support wheel for each spindle bearings. There are annular first and second stationary supports, each of which has a first side facing the speed controller, and a second side directed from the speed controllers. Each of the first and second fixed support has a concave surface on the first side and the first fixed support located near the leading disk and the second fixed support located next to the slave disk.

Also disclosed continuously variable transmission having a helical spring, which is located between the bearing disk and the leading disk.

In another aspect, the mechanism of switching of the transmission containing the rod, the worm is hydrated screw with an external thread, bias tube with internal thread, whereby rotation of the bias of the tube causes a change in gear ratio, the coupling with internal thread and a split shaft having a threaded end.

In another aspect of the disclosed remote switching device transfer containing rotating the handle, the file with the first end and the second end, the first end engages with the arm and the other end engages with a bias tube. The handle is adapted to apply tension to the tether, and the tether is adapted to affect the bias of the tube during the application of tension.

These and other improvements will become more clear to a person skilled upon reading the following detailed description and viewing the attached drawings.

Brief description of drawings

Figure 1 is a side view in section of a variant of execution of the transfer.

Figure 2 is a partial view in cross section taken along the line II-II in figure 1.

Figure 3 is a view in perspective of a split shaft and two fixed bearings in the transmission of figure 1.

Figure 4 is a schematic side view in cross section of the transmission 1 is shifted to "low".

Figure 5 is a schematic side view in cross section of the transmission 1 is shifted to "high".

6 is a schematic side view of pitched bearing located between the two curved rays PE is Adachi of figure 1.

7 is a schematic side view of pitched bearing located between the two curved rays of the transmission of figure 1.

Fig is a schematic side view of pitched bearing located between the two curved rays of the transmission of figure 1.

Fig.9 is a view in perspective of a sub-node of the power regulator in the transmission of figure 1.

Figure 10 is a view in section and in perspective of the sub-node switch in the transmission of figure 1.

11 is a view in perspective of the fixed bearing in the transmission of figure 1.

Fig is a view in perspective of the screw and nut in the transmission of figure 1.

Fig is a schematic view in perspective of a farm in the transmission of figure 1.

Fig is a partial view in section and in perspective of the Central rays of the transmission of figure 1.

Fig is a view in perspective of the outer rays in the transmission of figure 1

Fig is a view in perspective lever sub-node in the transmission of figure 1.

Fig is a view in perspective of a sub-node of the tripping mechanism in the transmission of figure 1.

Fig is a view in perspective of the device of the shift lever in the transmission of figure 1

Fig is a side view in section of an alternative implementation of the transmission of figure 1.

Fig is a side view in section of another alternative implementation of the transmission of figure 1.

F. g is a view in perspective of the transmission Fig, depicting the tension link.

Fig is a view in perspective of an alternative mechanism of the coupler in the transmission of figure 1.

Fig is another view in perspective of an alternative mechanism for uncoupling the transmission Fig.

Fig is a form of sub-node of alternative execution generators axial forces in the transmission Fig.

Fig is a schematic view in cross section of the slots and grooves generators axial force on Fig.

Fig is a view in perspective of an alternative mechanism of the coupler in the transmission of figure 1.

Fig is a view in perspective of an alternative mechanism for uncoupling the transmission Fig

A detailed description of the preferred option run

Embodiments of the invention will now be described with reference to the attached drawings, in which similar positions everywhere mean the same elements. Presented here is the terminology used in the description should not be interpreted in any limited or restrictive manner simply because it is used in conjunction with the detailed description of certain specific embodiments of the invention. Furthermore embodiments of the invention can include several new distinctive signs, none of which is fully answer the public for the desired properties, or which are necessary for the functioning of the inventions described here.

Described here gearboxes are the type that uses balls speed controllers with the axes of tilting as described in application for U.S. patent No. 09/695757, filed October 24, 2000. Presenter (input) drive and slave (output) disk are in contact with the balls speed controllers. As the balls lean on their axes, the point of rolling contact on one disk is moved in the direction of the pole or axis of the bowl where it is in contact with the ball on the circle of decreasing diameter, and the point of rolling contact on another disk moves in the direction of the equator of the ball, thereby contacting with the disk on a circle of increasing diameter. If the axis of the ball bends in the opposite direction, the disks are in the opposite situation. In this case, the ratio of the speed of rotation of the master disk to the rotational speed of the slave drive or gear ratio may vary within a wide range by a simple tilt of the axes of the balls speed controllers.

With regard to the longitudinal axis of the embodiment of the transmission, the driving disk and the driven disk can be located radially outward from the balls speed controllers, with an intermediate generally cylindrical support element located radiolover from the balls speed controllers, so each ball is in contact at three points with internal reference element and external drives. A driving disk, a driven disk and the support element can rotate around the same longitudinal axis. The master disk and the slave disk can be in the form of a simple disk, or may be concave, convex, cylindrical or any other shape depending on the configuration desired input and output. Surface rolling contact drives, where they are linked with the balls speed controllers, can be flat, concave, convex or have a different profile depending on torque and performance requirements of the application.

Figures 1 and 2 disclosed perform stepless box 100 transmission. Box 100 gear is concealed in the tubular casing 40, which functions as an output disk and desirable in various applications, including those in which the vehicle (such as a Bicycle or motorcycle) has a transmission enclosed within the driven wheel. Tubular casing 40 may, in certain embodiments perform to be closed tubular cap 67. In the middle of the box 100 transmission is many regulators 1 speed, which may be spherical in shape and are located on a circle more or less symmetrically about the center line or axis of rotation of the box 100 transmission. In the illustrated what ariante implementation uses eight regulators 1. However, it should be noted that there may be more or less regulators 1 speed depending on the use of the box 100 transmission. For example, the transmission may include 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, 13, 14, 15 or more speed controllers. The presence of more than 3, 4 or 5 speed controllers can provide certain advantages, including, for example, the wide distribution of effort the individual regulators 1 speed and to the points of their contact with other components of the box 100 transmission. Some options perform in applications with low torque but high gear ratio can use a bit of regulators 1 speed, but large regulators 1 speed, whereas some ways to run applications with high torque and high gear ratio can be used many regulators 1 speed and large knobs 1 speed. Others perform in applications with high torque and low gear ratio can be used many regulators 1 speed and small regulators 1 speed. Finally, some options perform in applications with low torque and low gear ratio can use a bit of regulators 1 speed and small regulators 1 speed.

The spindles 3 are inserted through holes that pass through the center of ka is the Treaty of regulators 1 speed, to set the axis of rotation for each of the controllers 1 speed. The spindles 3 in the General case are elongated shaft, around which revolve the regulators 1 speed, and have two ends that protrude outward from either end of the hole through the regulators 1 speed. Some ways to accomplish will be have the spindles 3 of cylindrical shape, although it may be used in any form. Regulators 1 speed is set so as to freely rotate around the spindle 3. In figure 1 the axis of rotation of regulators 1 speed shown approximately in the horizontal direction (i.e. parallel to the main axis of the box 100.

1, 4 and 5 can be used to describe how the axis controllers 1 speed can bend when working to switch box 100 transmission. Figure 4 shows a box of 100 gear, switched to low gear ratio, or low gear, while figure 5 shows a box of 100 gear, switched at a high gear ratio or gear. In figures 9 and 10 multiple spindle poles 2 are attached to the spindles 3 near each of the ends of the spindles 3, which protrude from the holes made in the regulators 1 speed, and act in the radial direction inside of these points of attachment to the axis of the box 100 transmission. In one embodiment, each of the spindle supports 2 them is no through hole, which receives one end of one of the spindles 3. The spindles 3 are preferably protrude through the spindle support 2 beyond them, so that they have an open end. In the illustrated versions of the spindles 3 at the same time have the spindle rollers 4, located coaxially with and sliding over the open ends of the spindles 3. Spindle rollers 4 in the General case are cylindrical wheels, mounted on the axis of the spindle 3 from the outside and the outside spindle bearings 2, and freely rotate around the spindle 3. Figure 11 spindle rollers 4 and the ends of the spindles 3 are located in the grooves 6, which are embedded in a pair of stationary supports 5A and 5b.

Figs.4, 5 and 11 of the stationary supports 5A and 5b have in General the form of parallel disks located koltseobrazno around the axis of the gearbox on each side of regulators 1 speed. When the axis of rotation of regulators 1 speed changed by moving the spindle bearings 2 in the radial direction from the axis of the box 100 transmission to reject the spindles 3, each spindle roller 4 is in the groove 6 and follows it in one of the stationary supports 5 a and 5b. Any radial force, not rotary, but a clamping force that regulators 1 speed can be attached to the spindle 3, is absorbed by the spindle 3, the spindle rollers 4 and the sides 81 of the grooves 6 in the stationary supports 5A and 5b. The stationary is e pillars 5 a and 5b mounted on a pair of split shafts 98, 99, along the axis of the box 100 transmission. Split shafts 98, 99 are generally elongated cylinders that define a significant portion of the axial length of the box 100 of the transmission and can be used for the connection box 100 transmission with objects that use it. Each of the split shafts 98, 99 has an inner end near the middle of the box 100 gear and the outer end of which protrudes from the inner shell of the box 100 transmission. Split shafts 98, 99, preferably hollow to contain inside other optional elements that may be embodied. Each of the stationary supports 5A and 5b has a hole 82 through which the split shafts 98, 99 are inserted and rigidly fixed to prevent any relative movement between the split shafts 98, 99 and stationary supports 5A and 5b. The stationary supports 5A and 5b are preferably rigidly attached to the ends of the split shafts 98, 99 near the centre of the box 100 transmission. Nut 90 fixed points can be screwed on split shaft 99 and is secured to the fixed bearing 5b in the corresponding thread of the stationary supports 5A and 5b. Grooves 6 in the stationary supports 5A and 5b, above, are from the inner circumference of the stationary supports 5A and 5b in the radial direction inside of the split shafts 98, 99. In most embodiments of the sides 81 of the grooves 6 are practically parallel, the button to allow the spindle rollers 4 to ride on the sides of the grooves 81 up and down, when the box is 100 transmission switches. In some embodiments, performing the depth of the grooves 6 is practically constant on the circle 9 stationary supports 5A and 5b, but the depth of the grooves 6 becomes smaller at points closer to 7 split shafts 98, 99, to conform to the arc described by the ends of the spindles 3, when they are rejected, and to increase the strength of the stationary supports 5A and 5b. As box 100 transmission is switched to a smaller or greater transmission number by changing the axes of rotation of regulators 1 speed, each of the pairs of spindle rollers 4, which are located at opposite ends of a single spindle 3, is moved in opposite directions along their respective grooves 6.

In figures 9 and 11, the rollers 30 of the fixed bearing can be attached to the spindle support 2 pins 31 fixed bearing rollers or in any other way. The rollers 30 of the fixed bearing coaxially and mounted to slide on the pins 31 fixed bearing rollers and secured with conventional fasteners, such as, for example, ring clamps. In some embodiments, perform one platen 30 of the fixed bearing is located on each side of the spindle 2 with sufficient clearance to allow the rollers 30 of the fixed bearing to rotate in the radial direction on the concave surfaces 84 of the stationary supports 5A and 5b, when the box is and switches. In some versions of the concave surface 84 are concentric with the center of regulators 1 speed.

In figure 2, 3 and 11 many of elongated spacers 8 are distributed in the radial direction around the axis of the transmission and stretched mainly coaxially her. Elongated spacers 8 connect the stationary supports 5A with each other to increase the strength and rigidity of the internal structure of the box 100 transmission. Spacers 8 are oriented parallel to each other, and in some embodiments, execution of each of them passes from a point on one fixed bearing 5A around the outer circumference at the corresponding point on another fixed bearing 5b. Spacers 8 can also accurately record the distance between the stationary supports 5A and 5b, align the grooves 6 of the stationary supports 5A and 5b, to ensure the parallelism between the stationary supports 5A and 5b and to form the connection between the split shafts 98, 99. In one embodiment, the spacers 8 itresolved through the holes 46 of the spacer in the stationary supports 5A and 5b. Although shown eight spacers 8, you can use more or fewer spacers 8. In some embodiments, execution of the spacers 8 are located between the two regulators 1 speed.

In figures 1, 3 and 13 of the stationary bearing 5A, in some embodiments, execution rigidly attached to the stationary support sleeve 42, positioned and is coaxially around the split shaft 98, or, conversely, is rigidly attached to the split shaft 98, or made an integral part. Fixed coupler 42 protrudes through the wall of the tubular casing 40 and is attached to a farm 15. In some versions of the farm 15 is placed coaxially on the fixed sleeve 42 and is rigidly attached to the stationary sleeve 42. In some versions of the farm 15 uses the lever 43 torque to maintain the stationary state stationary clutch 42. The lever 43 torque ensures the stability of the box 100 transmission by the physical connection of the fixed clutch 42 through farm 15, and hence the other fixed parts fixed fixed element of the product that must be installed box 100 transmission. Nut 44 torque is screwed on the outer part of the fixed clutch 42 to hold the lever 43 torque in the position in which he engages in a farm 15. In some versions of the farm 15 feasibility to engage with the lever 43 torque in a positive way, thereby preventing rotation of the stationary clutch 42.

For example, a farm 15 may have a cross section in the form of a square equal to the thickness of the lever 43 of torque, with sides greater than the fixed sleeve, and with a round hole at its center, so that Quadra is can be worn on the stationary sleeve 42, it can then be rigidly attached. Additionally, the lever 43 torque can be shoulder thickness equal to the thickness of a farm of 15, and with the first end about a farm of 15 and a second end opposite the first. The lever 43 torque in some embodiments, execution also has a hole in one of its ends, but the hole has a square shape, and the square a little more than a farm 15 so that the lever 43 torque can slide on the farm 15, which is expressed in the rotational clutch farm 15 and the lever 43 of torque. Moreover, the lever arm 43 of torque are oriented so that the second end of the elongated so as to be attached to a farm, motorcycle, car, tractor, or another application that uses box 100 transmission, thereby counteracting any torque applied to the gear box 100 through farm 15 and the stationary sleeve 42. The bearing 48 fixed bearing worn coaxially around a stationary clutch 42 and coaxially between the outer edge of the tubular casing 40 and the lever 43 of torque. The bearing 48 fixed bearing supports tubular casing 40, allowing the tubular housing 40 to rotate relative to the stationary support of the coupling 42.

Figures 1 and 10, in some embodiments, the run switch is triggered manually by turning the rod 10 located in the p the scrap split shaft 98. The worm screw 11, the outer thread in some embodiments, execution, attached to the end of the rod 10 is in the centre of the box 100 transmission, while the other end of the rod 10 is axis out of the box 100 transmission and has an external thread on its outer surface. In one embodiment, the worm screw 11 is screwed coaxially in the sleeve 19 with internal thread, so that during the rotation of the rod 10 and the worm screw 11, the clutch 19 is moved along the axis. The clutch 19 in the General case has the form of a hollow cylinder, which there is mounted coaxially around the worm screw 11 and the rod 10 and has two ends, one about the fixed bearing 5A, and the second about the fixed bearing 5b. The clutch 19 is attached each end to the platform 13, 14. Each of the two platforms 13, 14 in the General case has the form of a ring with an inner diameter that is large enough to be worn and attached to the sleeve 19, and is formed so as to have two sides. The first side is generally a smooth surface, which dynamically in contact with the supporting member 18 and supports it in an axial direction through two sets of contact bearings 17A and 17b. The second side of each platform 13 has the shape of a convex surface. Each of the platforms 13, 14 attached to one end of the outer surface of the coupling 19 to form a circular groove around the circumference of the clutch 19. Oneplatform 13 attached to the side nearest to the fixed bearing 5A, and the other platform 14 is attached to the side closest to the fixed bearing 5b. Convex surface of the platforms 13, 14 acts as Cams, each of which is in contact with many shifting of the wheels 21 and pushes them. To accomplish this, the Cam function of platform 13, 14 preferably pass into the convex curved surface 97 around their perimeters (furthest from the cutting shafts 98, 99), which may or may not be the radii. This curve 97 is in contact with the bias wheels 21, so that the platforms 13 and 14 are moved in the axial direction, bias wheel 21 moves along the surface of the platform 13, 14 mainly in the radial direction by applying a force to the spindle support 2 in the radial direction from the split shafts 98, 99 or in the radial direction thereto, thereby changing the angle of the spindle 3 and the axis of rotation of the associated regulator 1 speed. In some versions of the bias wheel 21 into the grooves in the spindle bearings 2 on the end closest to the Central line of the box 100 transmission, and held in place by the axes 22 of the wheels.

Returning to figures 1 and 10, the supporting element 18 is located in the groove formed between the platforms 13, 14 and the clutch 19, and thus moves in unison with the platforms 13, 14 and coupling 19. In some embodiments, execution of the reference ale is NT 18 basically has one outer diameter and generally cylindrical shape in the center of its inner diameter with bearing bracket on each edge of its inner diameter. In other embodiments, the external diameter of the support element 18 can be varied and may be of any shape, such as inclined or curved. The support element 18 has two sides, one is about one of the stationary supports 5A, and the other near the other of the fixed bearing 5b. The support element 18 is moved to a two pin bearings 17A and 17b to provide a rolling contact between the supporting member 18 and the sleeve 19. Contact bearings 17A, 17b are arranged coaxially around the clutch 19, where the coupling 19 crosses platforms 13, 14, allowing the support element 18 to rotate freely around the axis of the box 100 transmission. The clutch 19 is supported along the axis of the worm screw 11 and the core 10, and therefore, with this configuration, the clutch 19 is able to slide along the axis, when the worm screw to move it. When the box is 100 transmission switches, clutch 19 is moved along the axis, and the bearings 17A and 17b, the support element 18 and the platform 13, 14, which is attached to the clutch either dynamically or stationary, move along the axis accordingly.

In some embodiments, execution of the rod 10 is fixed at its end opposite the worm screw 11, to bias the tube 50 by a nut 51 of the rod and the guide rod 52. Shifting tube 50 in the General case has the form of a tube with one open end and one almost closed end. Open end of the shift of the surrounding tube 50 has a diameter, suitable for putting on the split end of the shaft 98, which acts along the axis from the centre of the box 100 transmission. Almost closed end of the shifting tube 50 has a small hole so that the end of the rod 10 opposite to the worm screw 11 can pass through it, when shifting tube 50 is placed on the outer part of the split shaft 98. Almost closed end of the shifting tube 50 may be secured in place on the axle by a nut 51 of the rod, which is attached outside of the shifting tube 50 and the protrusion 52 of the rod which is in turn secured within a correspondingly almost closed end of the shifting tube 50. Shifting tube 50 may in some embodiments perform to rotate the cable 53 is attached to the outer part of the shifting tube 50. The cable 53 in these variants perform attached to bias the tube 50 through the cable clamp 54 and the cable screw 56, and then wrapped around the shifting tube 50, so that when tension is applied to the cable 53, around the center axis of the shifting tube 50 is produced the moment, causing it to rotate. Rotation of the shifting tube 50 may be an alternative caused by any other mechanism, such as the shaft, rotation manually, servo or other means, intended for rotation of the rod 10. In some embodiments, execution, when the cable 53 is stretched so that usausa tube 50 rotates counterclockwise on split shaft 98, the worm screw 11 rotates counterclockwise, pulling the clutch 19, the supporting element 18 and the platform 13, 14 along the axis in the direction of the shifting tube 50 and switching box 100 transmission in the direction of the low gear ratio. Worm spring 55, as shown in figure 3, which may be conical spiral spring, is capable of producing compressive stress and tension, attached to the end of the worm screw 11, is located between the fixed bearing 5b and the platform 14 and resists the switch box 100 transmission. Worm spring 55 is designed to make shifting tube 50 to rotate so that the switch box 100 transmission in the direction of low gear ratios in some embodiments, execution and direction of the high gear ratio in other executions.

In figure 1, 10 and 11, the axial movement of the platforms 13, 14 defines the range switch box 100 transmission. Axial movement is limited by the inner surfaces 85 on the stationary supports 5A and 5b that are in contact with the platforms 13, 14. At extremely high gear as the platform 14 is in contact with the inner surface 85 on one of the stationary supports 5A and 5b, and at the extremely low ratio of the number of platform 13 is in contact with the inner surface 85 on the other of the stationary supports 5A and 5b. In many versions of the curvature of puklich radii platforms 13, 14 is a function of the distance from the center of the knob 1 speed to the center of the wheel 21, the radius of the wheel 21, the distance between the two wheels 21, who are attached to each encoder 1 speed, and the angle of the axis of the knob 1 speed.

Although the described worm screw 11 left-handed, can be used worm screw 11 with right-hand thread, the corresponding wrapped in the right side of the shifting tube 50 and any other combination of elements just described, which can be used to maintain lateral movement of the support element 18 and platforms 13 and 14. Additionally bias the tube 50 may have an internal thread, which engages with the external thread on the outer part of the split shaft 98. By adding this helical gear shifting tube 50 will move along the axis when it rotates around the split shaft 98, causing the rod 10 to move along the axis. This can be used to enhance the axial movement of the mufti 19 of the worm screw 11 so as to intensify the effects of the rotation of the worm screw for fast switching of the gear ratio, or alternatively to reduce the effect of the rotation of the worm screw to slow down the switching process and to provide more accurate speed control box 100 transmission.

Figure 10 and 8 manual switch can be performed by using a torque arm 132, which may be coaxially located on top of the stationary pipe, steering 130 or other structural element. In some embodiments, perform end of the cable 53 is attached to the rope fence 133, which is attached to the torque arm 132. In some embodiments, execution of internal effort boxes 100 transmission and the conical spring 55 tends to cause switching of the transmission in lower gear ratio. When the user rotates the rotating lever 132, the cable 53, which may be wrapped in the groove around the torque arm 132, untwisted or twisted, depending on the direction of rotation of the cable 53, the simultaneous rotation of the shifting tube 50 and the switch box 100 transmission in the direction of a higher gear ratio. Set hrapovic teeth 134 may be located around the circumference on one or two sides of the torque arm 132 to engage with the paired set hrapovic of teeth on the first side of the ratchet tube 135, thereby preventing rotation of the torque arm 132 in the opposite direction. Pipe clamp 136, which can knock on adjustable screw allowing variable clamping force attaches ratcheting tube 135 to the handle 130. When switching in the opposite direction of the torque arm 132 is forcibly rotated in the opposite the one direction to lower the transmission number, forcing pipe clamp 136 to rotate in unison with the rotating arm 132. The steering tube 137, located next to the ratchet tube 135 on the side opposite the ratchet teeth 134 rigidly pressed against the handle 130 pipe clamp 138, thereby preventing the release of ratchet tube 135 out of engagement with rapovymi teeth 134. Niramaya arm 131 is attached to the wheel 130 and is located next to the torque arm 132, preventing axial movement of the torque arm 132 and preventing hrapovic teeth 134 out of engagement with the ratchet tube 135.

In variants of execution, shown in figures 1, 9 and 11, one or more rollers 30 of the fixed bearing can be attached to each spindle pole 2 cotter pin roller 31, which is inserted through a hole in each spindle support 2. Cotter pins 31 of the rollers should have a size and design to allow the rollers 30 of the fixed bearing to rotate freely on each pin 31 of the platen. Rollers 30 rotate in the fixed bearing concave curved surfaces 84 on the sides of the stationary supports 5A and 5b, which are rotated, the speed controller 1. The rollers 30 of the fixed bearing to provide axial support to prevent axial movement of the spindle supports 2 and also to ensure that the spindles 3 are easily bent when the box 100 transmission switches.

In figure 1, 12, 14, and 17 is supplied with the time steps of a driving disk 34, located next to the fixed bearing 5b, partially cover, but mostly not in contact with the fixed bearing 5b. A driving disk 34 may have two or more steps or may be a solid disk. Steps to reduce weight and help in the Assembly of the box 100 transmission options run using it, however, can be used the whole disk. A driving disk 34 has two sides: the first side that is in contact with regulators 1 speed, and a second side that faces in a direction opposite to the first side. A driving disk 34 is generally a circular disk mounted coaxially with and protruding in the radial direction from the inner thread or nut 37 on its inner diameter. The outer diameter of a driving disk 34 is designed to fit in the tubular casing 40, if used tubular casing 40 of the selected type that covers the regulators 1 speed and a driving disk 34 and is engaged with tubular cap 67. A driving disk 34 is connected for rotation with regulators 1 speed external bearing surface on the edge of the first side of the master disk 34. As mentioned above, some embodiments of the master disk 34 are threaded nut 37 or 37 at its center, and a nut 37 is screwed on the screw 35, thereby introducing a driving disk 34 in engagement with the screw is m 35. The screw 35 is rigidly attached to the set of Central rays 90 screws, which are a set of raised surfaces on the annular disk, which is located coaxially on the split shaft 99. The Central rays of the screw 90 are driven by a set of Central rays drive shaft 91, which is formed similarly to the generally annular disk. The surface slope of the Central rays 91 of the drive shaft and the Central rays screw 90 can be straightforward, but can be any other shape and are in working contact with each other. The Central rays 91 of the drive shaft, coaxially and rigidly attached to the drive shaft 69, according to torque and axial force to the Central rays 90 screw, which can then be transferred to a driving disk 34. The Central element 92 leading tension, situated between the Central rays 91 of the drive shaft and the Central rays 90 screw, produces tensile and/or compressive force, ensuring that the Central rays 90, 91 in contact with each other.

In figure 1, 12, 14 and 17 of the screw 35, which is able to move along the axis, may be forced to move in the axial direction from regulators 1 speed through the annular thrust bearing 73 which is in contact with the ring on the side of the screw 35, which is addressed to regulators 1 speed. Annular thrust the washer 72, located coaxially on split shaft 99, in contact with the thrust bearing 73 and can be pushed by the pin 12, which protrudes through the slot in the slotted shaft 99. Compressing element 95, capable of generating a compressive force, is located in the hole in the floor split shaft 99 in the first end. Compressing element 95, which can be a ring, in contact with the pin 12 at one end and the second end is in contact with the rod 10. As the rod 10 is shifted toward the higher the transmission number and moves in the axial direction, it comes into contact with the gripping element 95, pushing him from pin 12. Internal efforts in box 100 transmission will cause the supporting element 18 to move toward the high gear, when the gear ratio will be for the gear ratio is 1:1 in the upward direction, and a driving disk 34 rotates slower than the tubular casing 40. This shift pushes the screw 35 in the axial direction so that he or detached from the nut 37 and no longer applies axial force or torque to the drive disk 34 or reduces the force that the screw 35 applies to the nut 37. In this situation, increases the percentage of axial force applied to the master disk 34 external rays 61. It should be noted that external force box 100 transmission will shift the th supporting element 18 in a downward direction, while supporting element 18 will not pass for position for the gear ratio 1:1 in a downward direction, and a tubular housing 40 rotates slower than driving disk 34. This is the best offset contributes to the switch when the falling number of rpm, and torque is increased when the switch in the down direction.

In figure 1, 12, 14, 17 drive shaft 69, which is a tubular sleeve with two ends and located coaxially with the outer part of the split shaft 99 has one end of the said Central rays 91 of the drive shaft attached to it, while its opposite end facing in the direction from the master disk 34. In some embodiments, execution of the thrust bearing disk 60 is attached to the drive shaft 69 and is provided to them in the motion. The thrust bearing disk 60 can be attached to a splined drive shaft 69, providing limited axial movement of the disc 60 of the thrust bearing or the thrust bearing disk 60 can be rigidly attached to the drive shaft 69. The thrust bearing disk 60 in generally a radial disk mounted coaxially on the drive shaft 69, protruding radially outwards to a radius equal to the radius of the master disk 34. The thrust bearing disk 60 is attached to the drive shaft 69 in position about a master disk 34, but far enough away to provide space for a set of external rays 61, associated skatn the x bearings 62 and the shell 64 of the bearing, and all of them are located between the master disks 34 and disc 67 of the thrust bearing. In some embodiments, execution of the set of external rays 61 may be convex and rigidly attached to the disc 60 of the thrust bearing on the side facing to the master disc 34. Alternative external rays 61 can be convex or straight depending on the use of the box 100 transmission. Alternative ferrule 64 of the thrust bearing may be replaced by a second set of external rays 97, which may be straight, convex or concave and which is rigidly attached to the drive disk 34 on the side facing the thrust bearing disk 60. Pitched bearings 62 in the General case are many bearings that match the number with the external rays 61. Each of the many pitched bearing 62 is placed between one sloped bearing 61 and the yoke bearings 64 and held in place by compressive force applied by rays 61 and the separator 63 of the bearing. The separator 63 bearing is a ring coaxial slotted shaft 99 and located in the axial direction between the concave rays 61 and convex slopes 64. The separator 63 of the bearing has a relatively large inner diameter so that the radial thickness of the separator 63 of the bearing is only slightly greater than the diameter pitched bearings 62 to hold pitched Podshipnik. Each of the sloped bearing 62 is inserted into the hole, which is formed in the radial thickness of the separator 63 bearing, and these openings together with the previously mentioned compressive force holding pitched bearings 62 on the spot. The separator 63 of the bearing can be directed in a certain position by a flange on the master disk or the disk 60 of the thrust bearing, which is slightly less than the internal diameter of the separator 63 of the bearing.

In figure 1, 6, 7, 8, and 15 shows the disk 60 of the thrust bearing, the outer rays 61 and pitched bearings 62 one possible implementation. Specifically, figure 6 schematically shows a pitched bearings 62 in contact with the concave outer ramp 61 and the second convex outer slope 97. Specifically, figure 7 schematically shows a pitched bearings 62, a concave external scat 61 and the second convex outer scat 97 6 the other torque or gear. The position of the pitched bearings 62 on the outer rays 61, shown in Fig.7, produces less axial force than the pitched position of the bearings 62 on the outer rays 61, shown in Fig.6. Specifically on Fig shown pitched bearings 62 in contact with the convex outer ramp 61 and second concave outer slope almost 97 in Central positions in their respective rays. It should be noted that the changes in the curves on the outer rays 61, 97 updated the t value of axial force, attached to the controllers 1 energy at different gear numbers, allowing maximized efficiency at different gear numbers and torque changes. Depending on the use of the box 100 gear you can use many combinations of curved or rectilinear external rays 61, 97. To simplify and reduce costs in some applications, one set of external rays may be removed, such as a second set of external rays 97, which is replaced by a yoke 64 of the bearing. To further reduce the cost of a set of external rays 61 may have a straight slope.

Figure 1 is a coiled spring 65 with the two ends of the wrapped coaxially around the drive shaft 69 and is attached at one end to the disc 60 of the thrust bearing and the other end to the drive disk 34. A spiral spring 65 provides the force to maintain a master disk 34 in contact with regulators 1 speed and shifts pitched bearings 62 up to the external rays 61. A spiral spring 65 is constructed so as to minimize the axial length within which it must operate, and in some versions of the cross-section of the spiral springs is a rectangle with a radial length greater than the axial length.

Figure 1 is a disc 60 of the thrust bearing is preferably in contact with the external Podshipnik tubular cap on the side of the disc 60 of the thrust bearing, opposite concave slopes 61. The outer bearing 66 of the tubular cap may be annular set of roller bearings located in the radial direction from the Central line of the box 100 gear, but coaxially her. The outer bearing 66 of the tubular cap is radially into a position where it may come into contact with tubular cap 67 and the disk 60 of the thrust bearing to ensure their joint movement relative to each other. Tubular cap 67 in the General case has the form of a disk with a hole in the middle to be worn on the drive shaft 69, and such outer diameter that it fits inside the tubular casing 40. The internal diameter of the tubular cap engages with the inner bearing 96 of the tubular cap, which is located between the tubular cap 67 and the drive shaft 69, and support radial and axial alignment of the tubular cap 67 and the drive shaft 69 relative to each other. The edge of the tubular cap 67 at its outer diameter may be threaded so that the tubular cap 67 can be is screwed into the tubular casing 40, to occlude a large part of the frame 100 of the transmission. The sprocket or pulley 38 or other leading drivers of the adapter, such as gears, may be rigidly attached to the rotating drive shaft 69, to provide input rotation. Drive shaft 69 supported is in a coaxial position with split shaft 99 conical bearing 70. Bearing cone 70 is annular bearing attached coaxially around the split shaft 99, and provides a rolling contact between the drive shaft 69 and split shaft 99. Tapered bearing 70 may be fixed in its axial position of the conical nut 71 which is screwed on the split shaft 99, or any other fastening method.

In some embodiments, the input rotation from the sprocket or pulley 38 is transmitted to the drive shaft 69, which, in turn, rotates the disk 60 of the thrust bearing and the set of external rays 61, causing pitched bearings 62 to slide from the outer rays 61 and pressed a driving disk 34 to the regulators 1 speed. Pitched bearings 62 also transmits rotational energy to a driving disk 34 when they jammed, and therefore transmit rotational energy between outer rays 61 and convex slopes 64. Rotational energy is transferred from the master disk 34 on the regulators 1 speed, which, in turn, rotate the tubular casing 40, providing an output rotation and torque box 100 transmission.

On Fig lock 115 is rigidly attached to the side of the master disk 34, which is turned into the drive thrust bearing 60, and is engaged with the hook 114 which is rigidly attached to the first of the two ends of the lever 113 of the hook. The scope of the engagement under the lumen of the castle 115 more Camerina hook 114, and provides additional space for movement of the hook 114 in a radial direction relative to the axis within the boundaries of the castle 114, when the driving disk 34 and the thrust bearing disk 60 are moved relative to each other. The lever 113 of the hook is generally a longitudinal support element for a hook 114, and at its second end of the lever 113 has made zuzelo hinge 116 of the hook, which engages with the middle hinge 119 through the first hinge axis 111. Middle hinge 119 made zuzelo with the first end of the lever 112 of the master drive, generally elongated support element with two ends. At its second end of the lever 112 of the master drive has made zuzelo hinge 117 master disk, which is engaged with the hinge loop 110 by using the second hinge axis 118. Swivel hinge 110 in the General case is the base for support hook 114, the lever 113 of the hook, swivel hook 116, the first hinge axis 111, the middle hinge 119, the lever 112 of the master drive, the second hinge axis of the hinge 118 and 117 of the master drive, and rigidly attached to the disc 60 of the thrust bearing on the side facing to the master disc 34. When the lock 73 and hook 72 engages, this prevents it from rolling pitched bearings 62 in the region on the outer rays 61, which does not provide a sufficient magnitude of axial force for a master disk 34. This ensures that the all rotational effort attached to pitched bearings 62 outer rays 61, is transmitted to the host disk 34.

Figure 1 and 17 mechanism trip to one variant of the run box 100 transmission describes the release of the master drive 34 from regulators 1 speed for the movement of the tumbler. In cases when the input rotation of the box 100 transmission ends, sprocket or pulley 38 stop spinning, but the tubular casing 40 and regulators 1 speed may continue to rotate. It makes driving disk 34 to rotate so that the internal thread 37 in the hole of a master disk 34 has navytimes on the screw 35 with an external thread, thereby moving the disk 34 in the axial direction from regulators 1 speeds up until a driving disk 34 is no longer in contact with regulators 1 speed. The toothed rack 126 rigidly attached to the drive disk 34 on the side facing the thrust bearing disk 60 has teeth that are in engagement with the toothed wheel 124 and rotate it when driving disk 34 is screwed on the screw 35 and disengages from regulators 1 speed. A gear wheel 124 has a hole in the center through which is inserted the liner 121 gears, providing rotation of the toothed wheel 124. Clamps 125, which is coaxially fixed to the liner 121 gear, fixed gear 124 in position, although there may be used any with whom estva fastening. The device 120 preload, located coaxially on the Central rays 91 of the drive shaft and fixed on them, is elongated in the radial direction from the center of the box 100 transmission. The device 120 preload, made of elastic material, is able to return to their original shape after bending, has a first end 128 and a second end 127. The first end 128 of the pre-load passes through the liner 121 gears and ends in the separator 63 of the bearing. The first end 128 of the pre-load shifts the separator 63 bearing and pitched bearings 62 to the rays 61, providing contact between the sloped bearings and rays 61 and moves the toothed wheel 124 on a rack 126. The ratchet 123 is engaged with the toothed wheel 124, and in one embodiment is engaged with the toothed wheel 124 on the side, almost opposite the toothed rail 126. The ratchet 123 has a hole through which the sleeve 122 of the ratchet, allowing the ratchet 123 to rotate. Clamps 125 or other securing means attach the ratchet 123 to the liner 121 of the ratchet. The spring 122 of the ratchet moves the rotation of the ratchet 123 so as to engage with the toothed wheel 124, thereby preventing the change of the direction of rotation of the toothed wheel 124, when leading the lawsuit 34 is screwed on the screw 35. The liner 121 of the ratchet is located on the second end of the device 127 preload, which rotates in unison with the drive shaft 69.

Figure 1 is a coiled spring 65 located coaxially around the drive shaft 69, is located along the axis between the disc 60 of the thrust bearing at one end and a driving disk 34 at the other end, and is attached thereto by cotter pins or other fasteners (not shown). In some versions of the coiled spring 65 replaces the helical spring of the prior art, to provide more force and take up less axial space to reduce the overall size of the box 100 transmission. In some versions of the coiled spring 65 is made of spring steel wire of rectangular cross-section, which has a radial length or height greater than the axial length or width. When working box 100 transmission coiled spring 65 provides contact between regulators 1 speed and a leading disk 34. However, when the driving disk 34 disengages from regulators 1 speed, prevents the winding of the coil spring 65 on the driving disk 34, so that it again comes into contact with regulators 1 speed due to the coupling with the drive gear 124 and the ratchet 123. When the input sprocket, gear or pulley 38 rotates the ratchet 123 also rotates, allowing the toothed wheel 124 is to romatsa, and thus rotating the master disk 34 and otvincivatmisa with screws 35 due to the torsional force generated by the spiral spring 65. The relative movement between the ratchet 123 and the gear wheel 124 is ensured by the fact that the first end of the device 128 pre-load rotates approximately at half speed with respect to the second end of the device 127 pre-load, because the first end of the device 128 pre-load is attached to the separator 63 of the bearing. Also since pitched the bearings 62 are rotated on the outer rays 61 of the thrust bearing disk 60, the separator 63 of the bearing will rotate at half speed with respect to the disc 60 of the thrust bearing.

On Fig disclosed an alternative embodiment of the box 100 of the transmission of figure 1. In this embodiment, the output disk 201 replaces the tubular casing 40 boxes of 100 of the transmission shown in figure 1. Similarly, the master drive 34 output disk 201 is in contact with regulators 1 speed and rotates them. The output disk 201 is supported by a bearing 202 of the output disk that comes into contact with the output disk 201 and cover 202 of the stationary casing. The cap 202 housing is rigidly attached to the stationary housing 203 hull bolts 205 or any other fasteners. Fixed housing 203 may be attached to a stationary object,such as a farm, or to the machine for which it is used. Gear, sprocket or pulley 206 is fixed coaxially on the output disk 201 and attached rigidly outside of the cap 204 of the housing and the fixed housing 203. However, you may use any other type of output means, such as a transmission, for example. Can be added torsion bracket 207, which rigidly connects the split shaft 98 with the cap 204 of the housing for additional support.

On Fig and 21 is disclosed an alternative embodiment of the box 100 of the transmission of figure 1. The housing 302 of the fixed bearing is added on the side of the stationary supports 5A, facing regulators 1 speed, and is engaged with the bearing 301 of the fixed bearing and rotating the yoke 303 tubular casing to maintain the correct alignment of the stationary supports 5A with respect to the rotating tubular housing 40. Torque the bracket 304 is rigidly attached to the fixed bearing 5A, and may then be rigidly attached to a stationary external element to prevent rotation of the stationary supports 5A and 5b during operation box 300 transmission. Bearing drive shaft 306 is located at the end of the drive shaft 69, being converted to the regulators 1 speed, and engages with the clip 307 drive shaft, formed on the same end of the drive shaft 69, and a holder 305 split shaft formed on raised in radial the direction part of the split shaft 99, to provide additional support of the drive shaft 69 and the proper position of the drive shaft 69 relative to the stationary supports 5A and 5b. In the variants perform using the configuration shown in Fig, between the inner diameter of the tubular cap 67 and the position of the drive shaft 69, which is close to it, can be used for dynamic compaction, because they both can often rotate at different speeds. The seal can be used to minimize the amount of dust and debris that can get inside the rotating sleeve 40.

On Fig and 23 revealed an alternative mechanism 400 coupler box 100 of the transmission of figure 1. Gear wheel 402 is located coaxially on the liner 408 wheel and fixed in a certain position clip 413 or other fasteners so that it can rotate. The liner 408 wheel is coaxially on the first end of the device 405 advanced load having first and second ends (Fig and 23 they are both not separately identified). The device 405 advanced load elastically pressed against the Central rays 91 of the drive shaft. The first end of the device 405 advanced load passes to the separator 63 bearing, shifting the separator 63 of the bearing up to the outer rays 61. Also on the liner 408 wheel is a lever 401, which revolves around the liner 408 wheel, which supports the ratchet 411 gears and ratchet 409 gear. Ratchet 411 gears included in the gear 402 to control its rotation and located on the liner 414 gears, which is shrunk into the hole in the lever 401. Spring 412 ratchet gear shifts the ratchet 411 gears from gears 402. Ratchet 409 gears, located almost opposite the ratchet 411 gears on the lever 411, coaxially located on the liner 415 gear, which is in a different hole in the lever 401, and provides rotational movement of the ratchet 409 gears. Spring 410 gear shifts the ratchet 409 gears from gears 403.

In figure 1, 22 and 23 of the toothed wheel 403 has a hole in the center and is located coaxially on the first of the two ends of the lever rod 404. The lever rod is elongated lever which engages with the ratchet 409 gears during roll forward up until continued rotation of the sprocket, pulley or transmission 38. Pin 406 disc thrust bearing, which is attached to the disc 60 of the thrust bearing, which is in contact with the second end of the lever 404 rod during rotation of the disk 60 of the thrust bearing, thereby pushing the lever 404 of the rod to the pin 407 master disk, which is rigidly attached to the drive disk 34. This action causes the first end of the lever rod 404 to lean back from gears 402, temporarily disconnecting the memory is striated wheel 403 from gears 402, allowing a toothed wheel 402 to rotate. The hook lever 401 is attached to the lever 401 and is in contact with a lock (not shown) on the master disk 34, and, therefore, pushes back when coiled spring 65 moves the driving disk 34 for unscrewing and contact with regulators 1 speed. In cases when the input rotation of the sprocket, pulley or transmission 38 is stopped, and the regulators 1 speed continues to rotate, a driving disk 34 is screwed on the screw 35 and unlinked with regulators 1 speed. When driving disk 34 rotates, the pin 407 unlinked with lever 404 of the rod, which then causes the gear 403 in contact with the toothed wheel 402, preventing re-adhesion of the master disk 34 with regulators 1 speed.

On Fig and 25 revealed the subnode alternative set of generators 500 axial force box 300 transmission Fig. During the rotation of the input sprocket, gear or pulley 38 splined drive shaft 501 rotates the disk 60 of the thrust bearing, which may have grooves 505 in the hole to accept and coupled with the slots 506 splined drive shaft 501. The Central rays 508 of the drive shaft is rigidly attached to the disc 60 of the thrust bearing or splined drive shaft 501 and rotate the Central rays 507 screw, both of which have holes, free slots 506 from the splined drive shaft 501. The Central element 92 the tense is possible (shown in figure 1) is located between the Central rays 508 of the drive shaft and the Central rays 507 screw. Screw 502 with grooves having end grooves and the end bearing, rotates the Central rays 90 of the screw and has a groove 505 at its end bearing, which is wider than the slots 506 on the splined drive shaft 501 to provide a gap between the spline grooves 506 and 505. This gap between the spline grooves 506 and 505 allows relative movement between the screw 502 with grooves and/or disc 60 of the thrust bearing and splined drive shaft 501. When the screw 502 with grooves does not rotate the Central rays 508 of the drive shaft and the Central rays 507 screws, slots 506 splined drive shaft 501 in contact with the grooves 505 and rotate them on the screw 502 with grooves, thereby rotating the screw 502 with grooves. The annular bearing 503 of the screw comes into contact with the yoke on the end of the bearing screw 502 with grooves and located so as to maintain the screw 502 with grooved and splined drive shaft 501 relative to the axis of the split shaft 99. The screw hole 502 with grooves slightly larger than the outside diameter of the splined drive shaft 501 to allow relative movement of the screw 502 with the grooves in the axial and radial directions. Conical ferrule 504 of the screw comes into contact and engages with the annular bearing 503 of the screw and has a hole perpendicular to its axis, to allow the introduction of the pin 12. The pin 12 is engaged with the rod 10, which m who can push the pin 12 and to move the screw 502 with the grooves in the axial direction, forcing him to withdraw from engagement with the nut 37, or to reduce the axial force, which he applies to it.

On Fig disclosed an alternative means 600 tripping means 400 tripping on Fig and 23. The lever 401 is changed so as to eliminate T-shaped, used to attach ratchet 409 gear and ratchet 411 toothed wheel, so that a new lever 601 is only attached to the ratchet 411 toothed wheel. The second lever 602 has a first end and a second end. Ratchet 409 gear in the work attached to the first end of the second lever 602. The second lever 602 has a first opening through which is introduced the first end of the device 405 pre-load. The second lever 602 is attached rotatably to the first end of the device 405 pre-load. The second lever 602 has a second opening at its second end through which is entered a second end of the device 603 advanced load. When the rotation of the sprocket, transfer or pulley 38 stops driving disk 34 continues to rotate forward and screwed on the screw 36 until it disengages with regulators 1 speed. The first end of the device 405 advanced load rotates forward, forcing the ratchet 409 gear to contact with the gear 403 and rotate it clockwise. This causes the gear wheel 402 to rotate p is otiv clockwise so, the ratchet 411 gears passes one or more teeth of the wheel 402, stopping a driving disk 34 and prevent it from unscrewing of the screw 36 and the contact with regulators 1 speed. When the rotation of the sprocket, transfer or pulley 38 continues, the second end of the device 603 advanced load rotates in contact with the second end of the second lever 602, causing the ratchet 409 gear swerve in and out of engagement with the gear 403, thereby allowing the master disk 34 to adventitia and re-engage with regulators 1 speed.

With this description, will now be described some specific improvements and advantages of the present invention. Note that not all of these improvements are needed in all versions of the invention.

Figure 1 is a current improvement in some embodiments, execution includes providing a variable axial force on the driving disk 34 to respond to different loads or usage. This can be accomplished by using multiple generators axial forces. The production of axial force can switch between the screw 35 and nut 37 with associated Central rays 91 of the drive shaft and the rays 90 screws on the outer rays 61, 64. Otherwise, the screw 35, the Central rays 90, 91 and the outer rays 61, 64 may jointly Khujand is indeed the production of axial force. Moreover, the axial force on the outer rays 61, 64 may be variable. This can be done by using rays of different slope and deflection, including concave and convex slopes. Figures 1 and 6-8 and in accordance with the foregoing detailed description of the disclosed embodiment of where the thrust bearing disk 60 is attached the first set of external rays 61, which may be concave and which adjoin pitched bearings 62. Opposite the first set of external rays 61 is a second set of external rays 97, attached to the drive disk 34, which may be convex and which is in contact with a pitched ball bearings 62. The use of concave and convex slopes for contact with a pitched ball bearings 62 allows a non-linear increase and decrease of the axial load on the driving disk 3 in response to adjustments in the position of regulators 1 speed and the support element 18.

Another improvement of some embodiments includes a positive engagement of the thrust bearing disk 60 and a master disk 34 to provide a higher rotational transmission and constant axial pressure on some levels, the transmission of torque. In the embodiment shown in figure 1, as described above, this can be accomplished, for example, by using a combination of the hook 114 and 115 castle, where the hook 114 at the Sol to the separator 63 bearing, where are pitched bearings 62 between the master disk 34 and the thrust bearing disk 60, and the lock 115 is attached to the drive disk 34, which is engaged with hooks 114 when pitched bearings 62 reach their respective boundary conditions on the surfaces of the slopes. Although this configuration is intended for example, it should be clear that the hook 114 and 115 castle can be attached to the opposite element, described above, or that many other mechanisms can be used to achieve the positive engagement of the thrust bearing disk 60 and a master disk 34 in the boundary positions pitched bearings 62.

A further improvement in some embodiments, compared with the previous developments is driving disk 34 having a radial steps (not separately labeled)that reduces the weight of the node box 100 transmission. In a specific embodiment, the driving disk 34 has three steps, separated from each other at equal distances, which allows you to access other elements to hook 114 and 115 castle.

Another improvement of some embodiments includes the use of thread 35, such as a trapezoidal thread to move the driving disk axis, when there is relative rotational movement between the master disk 34 and the thrust bearing disk 60. In the implementation, shown in figure 1, the screw 35 with an external thread can be screwed into the internal thread 37 or nut 37 in the bore of the master drive 34. This allows the master drive to come out of engagement with regulators 1 speed when driving disk ceases to provide input torque, as when coasting or rolling in neutral, as well as to promote a greater or lesser axial forces on the regulators 1 speed. Moreover, the screw 35 with an external thread is also designed to transmit axial force on the driving disk 34 through the external threads 37.

Another improvement in some embodiments, compared with the preceding invention consists of an improved method for switching boxes transfer to a higher or lower gear ratio. Again in the embodiment shown in figure 1, this method can be performed by use of the rod 10 with thread, which includes, for example, the worm screw 11 with left-hand thread and the corresponding bias the tube 50, or coupling, with right-hand thread, which works remotely with a cable 53 or remote motor or other remote means. Alternate left-hand thread can be used as a worm screw 11, and bias of the tube, or may be used to bias the tube 50 without thread or any combination of them, which can also be used as a tribute to the impact on the switching speed of the box 100 transmission in relation to the speed of rotation of the shifting tube 50. Additionally can be used conical spring 55, to help the operator to maintain the proper position of the shifting tube 50. The worm screw 11 is preferably connected to the sleeve 19 is threaded to align along the axis of the supporting element, so that when the worm screw 11 is rotated, the supporting element 18 will move along the axis.

Another improvement some embodiments compared to previous inventions is the tripping mechanism for a carton 100 transmission. The tripping mechanism allows the input sprocket, pulley or transmission 38 to rotate in the opposite direction, and also allows the gear box 100 move coasting on neutral gear by disengagement of the master drive 34 from regulators 1 speed.

The above description details certain embodiments of the invention. It should be clear, however, that no matter how detailed the above appears in the text, the invention can be embodied in a number of ways. And as mentioned earlier, it should be noted that the use of specific technologies in specific distinguishing features or aspects of the invention should not podrazumeva the , that terminology here revised as subject to restriction, to include any specific characteristics of the distinguishing features or aspects of the invention, which is associated terminology. Scope of the invention should therefore be construed in accordance with the attached claims and any equivalents.

1. Continuously variable transmission with a longitudinal axis that contains many speed controllers, each of which has an axis of rotation with adjustable tilt, and each speed controller is located radially outward from the longitudinal axis, a driving disk, rotatable koltseobrazno around the longitudinal axis in contact with the first point on each of the speed controllers and having a first side facing the speed controller, and a second side facing outward from the speed controllers, a driven disk, rotatable koltseobrazno around the longitudinal axis in contact with the second point on each of the speed controllers, generally cylindrical support element, able to rotate koltseobrazno around the longitudinal axis in contact with the third point on each of the speed controllers, disk thrust bearing, rotatable koltseobrazno around the longitudinal axis and adapted to apply torque force on the driving disk, at least on the and of the axial force generator, located between the master disk and the slave disk and disk thrust bearing, and each axial force generator is configured to apply a component of the axial force to the drive disk, thereby improving the contact of the master drive and speed controllers, many of the Central rays that contains a set of Central rays of the drive shaft and a set of Central rays of the screw, providing torque to at least one of the at least two axial force generators, and mechanism of the clutch, positioned between the thrust bearing disk and the leading disk and adapted to output a driving disk from engagement with the speed controllers.

2. Transmission according to claim 1, in which component of the axial force generated by each of at least two axial force generators, changes when switched transmission.

3. Transmission according to claim 1, in which the axial force is greater in many low gear ratios than many of the high gear ratio to a corresponding change of the gear ratio.

4. Transmission according to claim 1, in which at least two generators axial forces together produce an axial force to the master drive.

5. Transmission according to claim 1, in which at least two axial force generator to produce the axial force separately and is one of at least two axial force generators produces almost all of the axial force, apply to the master drive in high gear, and the second of the at least two axial force generators produces almost all of the axial force applied to the master drive in low gear.

6. Transmission according to claim 1, in which one of the at least two axial force generators includes a nut attached to the inner hole of the master drive, and the screw, which in General has a cylindrical shape and is coaxial with the longitudinal axis and around it, to grapple with the nut.

7. Transmission according to claim 6, in which the screw has an external thread adapted for engagement with internal threads on the nut in such a way that allows axial movement of the screw and nut with respect to each other without rotation.

8. Transmission according to claim 6, in which the screw has a side facing to the speed controllers, and has a ring bearing bracket, which is adapted to take the emphasis from the thrust bearing to bias the screw in the direction of the speed controllers.

9. Transmission according to claim 6, in which the screw and nut producing almost all of the axial force to the master drive in high gear.

10. Transmission according to claim 7, in which the set of Central rays in contact with the screw, to allow the screw to produce an axial force that the butt is provided to the master drive, moreover, all Central rays have the same angle of inclination.

11. Transmission of claim 10, in which the axial force produced by a set of Central rays will be transmitted to the master drive screw and nut.

12. Transmission of claim 10, further containing an element of tension that is located between the set of Central rays of the drive shaft and a set of Central rays of the screw, adapted to maintain engagement of the set of Central rays of the drive shaft and a set of Central rays of the screw.

13. Transmission according to claim 1, in which one of the at least two axial force generators is the set of external rays, attached to the drive thrust bearing and adapted to produce an axial force that is transmitted to the driving disk.

14. Transmission according to item 13, further containing a set in a common annular sloped bearing contact with the outer rays and located between the thrust bearing disk and the leading disk, and a set of annular bearing adapted to transmit axial force to the master disc, the outer rays produced almost all of the axial force to the master drive in low gear.

15. Transmission according to claim 1, in which the tripping mechanism includes at least one toothed wheel and at least one ratchet, which is adapted to prevent the treatment of the master drive on the speed controllers as long until the transfer is not applied input force.

16. Transmission indicated in paragraph 15, in which the tripping mechanism includes at least two ratchet.

17. Transmission according to clause 16, in which the tripping mechanism includes a nut attached to the inner hole of the master drive, and the screw, which has a General cylindrical shape and is coaxial with the longitudinal axis and to engage the nut, and a driving disk rotates the nut to engage the screw, thereby disconnecting the master drive speed controllers.

19. Transmission according to claim 1, in which the tripping mechanism includes a pre-load having first and second ends and located coaxially around the longitudinal axis of the transmission, and the first end of the device pre-load supports at least one toothed wheel is engaged with a bearing separator and adapted to rotate around the longitudinal axis with a rotation speed different from the speed of rotation of the second end of the device pre-load, the other end of which supports at least one ratchet, thereby providing relative movement between the at least one ratchet and at least one toothed wheel, providing a clutch that serves to prevent occurrences in the future disk engages with the speed controllers as long until the transfer is not applied input force.

19. Transmission on p, in which the pre-load provides a clamping force to the element to which it is rigidly attached.

20. Transmission according to claim 19, in which the pre-load has a profile cross-section at its inner diameter, which provides radial stability.

21. Transmission according to claim 20, in which the cross-section of pre-load in the General case is rectangular in shape.

22. Transmission on p, in which the tripping mechanism includes a nut attached to the inner hole of the master drive, and the screw, which in General has a cylindrical shape and is coaxial with the longitudinal axis and to engage the nut, and a driving disk rotates the nut through the Central rays for coupling with the screw, thereby disconnecting the master drive speed controllers.

23. Transmission according to claim 1, further containing a spiral spring, which is adapted to enter the master disk engages with the speed controllers after application of the input rotation to the transmission.

24. Transmission according to article 22, in which the screw and nut are threaded with respect to the rotation gearbox clockwise from the relative perspective of the disk under the etnica, addressed to the speed controllers.

25. Transmission according to article 22, in which the screw and nut have a right-hand thread in relation to the rotation of the gearbox clockwise from the relative perspective of the disc thrust bearing, which is converted to the speed controllers.

26. Transmission according to article 22, in which the screw is adapted to apply axial force to the drive disk.

27. Transmission according to claim 1, in which the continued rotation of the transmission causes the nut to rotate relative to the screw, thereby forcing leading the drive to get in touch with speed controllers.

28. Continuously variable transmission with a longitudinal axis that contains many speed controllers, each of which has an axis of rotation with adjustable tilt, and each speed controller is located radially outward from the longitudinal axis, a driving disk, rotatable koltseobrazno around the longitudinal axis in contact with the first point on each of the speed controllers and having a first side facing the speed controller, and a second side facing outward from the speed controllers, a driven disk, rotatable koltseobrazno around the longitudinal axis in contact with the second point on each of the speed controllers, disk thrust bearing, rotatable koltseobrazno around the longitudinal axis and adapted paragraph is to Radauti torque force on the master disk, supporting element is able to rotate koltseobrazno around the longitudinal axis in contact with the third point on the speed controllers and adapted to move to slower rotation of the master disk and the slave disk, at least two axial force generator located between the master disk and the disk thrust bearing, and each axial force generator adapted to apply a component of axial force to the drive disk, thereby improving the contact of the master drive and speed controllers, many of the Central rays that contains a set of Central rays of the drive shaft and a set of Central rays of the screw, providing torque to at least one of the at least two generators axial forces, and the sub-node linkage with hook and lock, adapted for clutch master disk and the thrust bearing disk.

29. Transmission on p, in which a driving disk has many radial steps positioned between the center of the master disk and the perimeter of the master disk.

30. Transmission on p, in which the supporting element is adapted to move to a sufficiently high transmission number, when it is located near the side of the speed controller, which is facing to the master disc.

31. Transmission on p, in which the supporting element is adapted per mestisa to a relatively low transmission number, when it is closer to the side of the speed controller, which is converted to the output disk.

32. Transmission on p, in which the supporting element is adapted to move to a relatively low transmission number, when the transmission goes out of gear ratio 1:1 in a downward direction.

33. Transmission on p, in which the supporting element is adapted to move to a relatively high transmission number, when the transmission goes out of gear ratio 1:1 in the upward direction.

34. Transmission on p, in which the lock is adapted to provide limited movement of the hook in the radial direction relative to the longitudinal axis, when there is relative movement between the master disk and the disk thrust bearing, while the hook is attached to the drive thrust bearing, and the lock is attached to the master disk, and the said hook and the lock engage and limit the movement between the thrust bearing disk and the leading disk.

35. Transmission on p, in which the linkage supporting the hook has at least one hinge.

36. Continuously variable transmission with a longitudinal axis that contains many spherical speed controllers, each of which has an axis of rotation with tilt adjustment and a hole through its center, and each speed controller is located in the radial direction Nar is Zhu from the longitudinal axis, many in the General cylindrical spindle with two ends, with one spindle is located in the hole of each of the speed regulator, set the spindle supports, with the platform end and the spindle end, each spindle two spindle bearings, and the spindle end of each spindle support in the work connected with one of the two ends of one of the many spindles, set of wheels fixed bearing, and at least one wheel of the fixed bearing is attached rotatably to the spindle end of each spindle support, a driving disk, rotatable koltseobrazno around the longitudinal axis in contact with the first point on each from the speed controller and having a first side facing the speed controller, and a second side facing outward from the speed controllers, a driven disk, rotatable koltseobrazno around the longitudinal axis in contact with the second point on each of the speed controllers, disk thrust bearing, rotatable koltseobrazno around the longitudinal axis and adapted to apply torque force on the driving disk, at least two axial force generator located between the master disk and the disk thrust bearing, and each axial force generator adapted to apply axial component condition is Leah to the master drive, thereby improving the contact of the master drive and speed controllers, many of the Central rays that contains a set of Central rays of the drive shaft and a set of Central rays of the screw, providing torque to at least one of the at least two axial force generators, generally cylindrical supporting element is able to rotate koltseobrazno around the longitudinal axis in contact with the third point on each of the speed controllers, annular first and second stationary supports, each of which has a first side facing the speed controller, and a second side facing outward from the speed controllers, each of the first and the second fixed support also has a concave surface on the first side and the first fixed support located near the leading disk and the second fixed support located next to the slave drive, helical spring located between the thrust bearing disk and the leading disk and adapted to enter the master disk engages with the speed controllers after application of the input rotation to the transmission, and in General a cylindrical drive shaft with the surface of the outer diameter, and the drive shaft has a capability when operating to transmit torque to the clutch disc.

37. Transmission on p, which is concave on the Ergneti first and second fixed supports are concentric with the centers of all speed controllers, and the ends of the spindles are concave surfaces of the wheels fixed support when you shift the transmission.

38. Transmission on p containing further end face located radially inward from the concave surface of each of the fixed bearing and the end face is configured to restrict movement of the ends of the spindles in the radial direction, thereby limiting the gear ratio of the transmission.

39. Transmission on p, in which both the fixed bearing further contain a number of radial grooves and radial grooves correspond to the radial paths of the ends of each of the spindles, and the end of each of the spindle passes through a fixed bearing in the corresponding groove, and each wheel of the fixed bearing coupled for rotation with a corresponding concave surface adjacent to the respective grooves.

40. Transmission on p, further containing a variety of spindle rollers, each roller spindle is coaxially on the end of one of the spindles, which passes over the spindle bearing, spindle and rollers coupled for rotation with grooves to guide the spindles when switching the transmission.

41. Transmission on p, in which each of the grooves further includes first and second vertical is by hand, each of the multiple spindle roller, which is configured to be coupled for rotation with a corresponding groove in the first fixed bearing, is engaged with the first vertical side grooves with a relatively high gear ratio numbers and engages with the second vertical side grooves with a relatively low gear ratio numbers.

42. Transmission on p, in which each of the grooves further includes first and second vertical sides, each of the multiple spindle roller, which is configured to be coupled for rotation with a corresponding groove in the second fixed bearing, engages with the second vertical side grooves with a relatively high gear ratio numbers and is engaged with the first vertical side grooves with a relatively low gear ratio numbers.

43. Transmission on p containing the next set of spacers having a longitudinal axis and two ends, and the spacers are adapted to connect between a fixed bearing, thereby maintaining the orientation of the first anchor relative to the second anchor.

44. Transmission according to item 43, further containing a number of holes in each of the fixed supports, and each of the holes adapted to accept the mother of the introduction of one of the two ends of one of the spacers.

45. Transmission according to item 44, in which the holes almost curved and each end of each spacer is adapted to enter a corresponding one of the holes.

46. Transmission in 42, in which each of the spacers is located so that the axis of each of the spacers is equal distance from the axes of rotation of at least two of the speed controllers.

47. Transmission on p containing the next set of wheels platforms attached rotatably to the platform end of the spindle bearings, the first and second platforms, which are in General circular disks coaxially with the longitudinal axis, and are located on each side of the support element, and each platform has a platform side, facing outward from the support element, and each of the platforms has a convex surface on the platform side, and thus each of the wheels of the platform configured to be coupled for rotation with one of the convex surfaces for the axial displacement of the platform caused the switch boxes transmission.

48. Transmission on p, in which each of the wheels of the platform attached to the platform end of one of the multiple spindle poles in a groove formed in the platform end of the spindle support, which is adapted to hold the wheel platform.

49. To the timid transmission p, in which each spindle bearing has at least three openings formed through it, so that each spindle bearing is adapted to support one of the spindles, at least one of the wheels of the fixed bearing and one of the wheels of the platform.

50. Transmission on p, in which the spiral spring has a cross-section, where the radial length of the coil spring is greater axial thickness of the coil spring.

51. Transmission on p, in which the spiral spring has a cross-section, which is almost rectangular.

52. Transmission on p, further containing in total split tubular shaft, coaxially, the longitudinal axis of the transmission and having a threaded end, the rod having first and second ends and located coaxially within the slotted shaft, a worm screw that is attached to the first end of the rod and having an external thread, the clutch to change gear transmission having an internal thread, which is mounted on the external threads of the worm screw and coupled with it, and bias the tube which engages with the second end of the rod and has an internal thread, which is mounted on the threaded end of the split shaft and coupled with him, and the rotation of the bias of the tube causes the axial displacement of the coupling and the corresponding change of the gear ratio.

53. Transmission is on paragraph 52, contains the next worm spring adapted to bias the rotation of the rod, while the worm spring includes a conical spring with a first end and a second end, and a worm spring wearing coaxially to the longitudinal axis of the transmission and is attached to the first end of the rod, and a second end to a stationary object.

54. Transmission in paragraph 52, further containing remote switching device containing a rotating handle, file with the first end and the second end, the first end coupled with the handle and a second end coupled with the bias of the tube, and when this arm is adapted to apply tension to the tether, and the tether is adapted to affect the bias of the tube during the application of tension.

55. Transmission on p, in which the external surface of the master disk has longitudinal slots attached to his side.

56. Transmission on p containing further in General, a tubular screw coaxially with the longitudinal axis, which has a threaded outer surface and has a first end facing the speed controller, which has the bearing shell at its inner diameter, and an annular bearing, is placed in contact with the yoke at the first end of the screw and coaxially with it, and located on an axis near the first end of the screw, the bearing is adapted for axial AC is recorded.

57. Transmission on p, in which the screw has an internal diameter greater than the outer diameter of the drive shaft, and fitted on the drive shaft so that the bearing provides support for the screw and drive shaft, and the screw can rotate relative to the drive shaft.

58. Transmission on p containing further longitudinal inner surface with grooves, and in which the splines of the drive shaft adapted to engage with grooves and thereby rotate the screw grooves.

59. Continuously variable transmission with a longitudinal axis that contains many speed controllers, each of which has an axis of rotation with adjustable tilt, and each speed controller is located radially outward from the longitudinal axis, a driving disk, rotatable koltseobrazno around the longitudinal axis and in contact with the first point on each of the speed controllers, a driven disk, rotatable koltseobrazno around the longitudinal axis and located on an axis between speed controllers, disk thrust bearing, rotatable koltseobrazno around the longitudinal axis, a set of annular bearings located between the master disk and the disk thrust bearing, which transmit rotational and axial force drive thrust bearing to the master disk and held in the annular and radial orientation cage bearing is, many Central rays that contains a set of Central rays of the drive shaft and a set of Central rays of the screw, adapted to apply torque to the Central part of the master drive through the Central screw, the tripping mechanism placed between the thrust bearing disk and the leading disk adapted to disconnect the master drive speed controllers, and the tripping mechanism includes at least one gear wheel, at least one ratchet to grapple with at least one toothed wheel, at least one arm adapted to concatenate at least one ratchet with at least one toothed wheel, and the pre-load with the first and second ends, which is elastic clamping a support for at least one toothed wheel and at least one ratchet, and the pre-load is located coaxially around the longitudinal axis of the transmission, and the first end of the device pre-load supports at least one of the at least one gear wheel engages with the bearing separator and adapted to rotate around the longitudinal axis with a rotation speed different from the speed of rotation of the second end of the device pre-load, the second end of the support measures at the one of the at least one ratchet, thereby providing relative movement between at least one of the at least one ratchet and at least one of the at least one toothed wheels, providing them with the grip that prevents the clutch master drive with speed controllers as long as the gearbox is not applied input force.

60. Transmission on p, further containing at least two ratchet and at least two gears.

61. Transmission on p, in which at least one lever rotates around the axis defined by the first end of the device pre-load.

62. Transmission on p containing next, the second lever and the second lever rotates around the axis defined by the second end of the pre-load.



 

Same patents:

FIELD: mechanical engineering.

SUBSTANCE: friction toroidal variator comprises inlet disk (2) and outlet disk (3) provided with toroidal surfaces, friction roller (5), spider whose one axle is provided with roller (5), holder (8) of friction roller, control mechanism, and mechanism for control of gear ratio. The second axle of the spider is fit in holder (8) of the friction roller that can rotate around the main axle of the variator. The control mechanism and mechanism for control of gear ration are made of gear sector (9) that rotates on the second axle of the spider secured to the first axle of the spider and housing (12) by means of worm gearing and spring (15) secured in housing (12) and connected with holder (8) directly or through the reduction gear.

EFFECT: simplified control and control of gear ratio.

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FIELD: mechanical engineering.

SUBSTANCE: variator comprises rotating driving member (69), at least three power controllers, bearing member (18) for the friction contact with each of the power controllers, at least one platform (13a) and (13c), at least one unmovable base (5a) and (5c), and a number of shaft holders. Each shaft holder slides over the convex surface of platform (13a) and (13 c) and concave surface of unmovable base (5a) and (5c) and controls axis of rotation in response to the axial movement of the platform.

EFFECT: enhanced reliability and simplified structure.

73 cl, 16 dwg

FIELD: transport engineering.

SUBSTANCE: invention can be used in wide range of vehicles, for instance, in minicars or trucks, snow movers, carts used when playing golf, cross country cars and scooters. Proposed driving pulley contains two centrifugal mechanisms, namely, positive unit and negative unit. Both units contains corresponding group of flyweights exposed to action of centrifugal force at rotation of driving pulley. Positive unit is used as standard speed governor which shifts one of two flanges of driving pulley towards other flange to increase diameter of running-over-over of driving pulley when speed rises. Negative unit is used to apply opposite force of positive unit when speed of rotation exceeds threshold value to delay rise of ratio of steplessly adjustable drive to higher ratio under action of positive unit. It provides maintenance of high speed of rotation at intensive acceleration and slow speed of rotation at slow speeds of vehicle.

EFFECT: provision of additional control over entire range of change of ratio of steplessly adjustable drive to decrease force created by centrifugal system of driving pulley.

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The invention relates to continuously variable transmissions of the type band - gutter knock wheel

The invention relates to a mechanical transmission with a continuously variable change speed of the driven shaft and can be used in the automotive industry

FIELD: mechanical engineering.

SUBSTANCE: variator comprises rotating driving member (69), at least three power controllers, bearing member (18) for the friction contact with each of the power controllers, at least one platform (13a) and (13c), at least one unmovable base (5a) and (5c), and a number of shaft holders. Each shaft holder slides over the convex surface of platform (13a) and (13 c) and concave surface of unmovable base (5a) and (5c) and controls axis of rotation in response to the axial movement of the platform.

EFFECT: enhanced reliability and simplified structure.

73 cl, 16 dwg

FIELD: mechanical engineering.

SUBSTANCE: infinitely variable gear box comprises a number of velocity governors. Driving disk (34), driven disk, and cylindrical bearing member (18) are in contact with the first, second, and third points on each of the velocity governors. Disk (60) of the thrust bearing transmits rotation to the driving disk. At least two generators of axial loading are interposed between the driven and driving disks and disk of the thrust bearing and can apply the axial loading to the driven disk.

EFFECT: improved structure.

62 cl, 27 dwg

One-track bicycle // 2424940

FIELD: transport.

SUBSTANCE: bicycle relates to bicycles with backrests. Turning handlebar 21 about vertical axis 20 allows turning front wheel 4. Inclination of handlebar 21 relative to horizontal axis 17 allows lifting or lowering extra lateral wheels 36. With wheels 36 lowered, bicycle starts and stops. Abrupt lowering of wheels 36 prevents overturn at cross-wind burst. Disks are secured to wheels 36 to engage with rear wheel tire 3. With wheels 36 lifted in downhill, said wheels accumulate energy by means of disks to be given up in climbing to provide for stability due to wheeling and gyro moment.

EFFECT: higher stability at cross-wind burst.

4 cl, 4 dwg

FIELD: transport.

SUBSTANCE: invention relates to bicycle rear wheel variators. Variator has discs 4, 5 that stay in direct friction contact. One of said discs is tapered disc. Surfaces of said discs converge at acute angle. Driven sp[rocket 10 is fitted on hollow shaft 8 to transmit torque to drive disc 5 and presses the latter to driven disc 4 fitted on wheel hub 2 of overrunning coupling 3. Control cables 20 displace sliding disc 14 with hollow shaft 8 and driven and drive discs 10 and 5, respectively, fitted thereon. This allows drive disc 5 to displace relative driven disc 4 with stepless variation of gear ratio. Variator can be uncased for protection against ambient effects.

EFFECT: reduced weight.

2 cl, 6 dwg

Stepless gearbox // 2499932

FIELD: machine building.

SUBSTANCE: stator plate for stepless gearbox contains several satellites installed around the main axis of rotation with power transmission due to engagement. Stator plate contains disk-shaped body installed coaxial to the main axis of rotation and several radially displaced guides arranged on the front surface of disk-shaped body and installed at an angle to the centre. Each radially displaced guide is displaced in linear direction from axial line of disk-shaped body.

EFFECT: improving performance.

14 cl, 17 dwg

FIELD: transport.

SUBSTANCE: invention relates to a continuously variable transmission and a control method. The transmission comprises a first drive tilting of few balls at an angle around the longitudinal axis and in contact with the first disc; the second disc in contact with several tilting balls; roller, radially disposed within the tilting balls and in contact with them, the cell connected with several balls. It also includes a first adgerence assembly connected to drive the first cell and the second clutch assembly coupled to the cage and the first disc. Two of the following: the first drive, the second drive roller and adaptedto the adapted to receive the cell input capacity. In this case one of a first drive, the second drive roller and the cage is adapted to provide output power.

EFFECT: invention provides a simplified design of transmission, lower cost and size of the device.

17 cl, 22 dwg

FIELD: mechanical engineering.

SUBSTANCE: variator comprises rotating driving member (69), at least three power controllers, bearing member (18) for the friction contact with each of the power controllers, at least one platform (13a) and (13c), at least one unmovable base (5a) and (5c), and a number of shaft holders. Each shaft holder slides over the convex surface of platform (13a) and (13 c) and concave surface of unmovable base (5a) and (5c) and controls axis of rotation in response to the axial movement of the platform.

EFFECT: enhanced reliability and simplified structure.

73 cl, 16 dwg

FIELD: mechanical engineering.

SUBSTANCE: infinitely variable gear box comprises a number of velocity governors. Driving disk (34), driven disk, and cylindrical bearing member (18) are in contact with the first, second, and third points on each of the velocity governors. Disk (60) of the thrust bearing transmits rotation to the driving disk. At least two generators of axial loading are interposed between the driven and driving disks and disk of the thrust bearing and can apply the axial loading to the driven disk.

EFFECT: improved structure.

62 cl, 27 dwg

FIELD: machine building.

SUBSTANCE: transmission consists of multiple traction spherical planetary mechanisms, multiple planetary axes, clamping plates and control system. Each planetary axis is functionally connected to each spherical planetary mechanism. Each planetary axis defines the slope of rotation axis of each traction spherical planetary mechanism and is mounted capable of providing angular movement in the first and the second planes. The first clamping plate is functionally connected to the first end of each of planetary axes, the second clamping plate is functionally connected to the second end of each of planetary axes. The first and the second clamping plates are formed to rotate round the longitudinal axis and relatively each other. Also there described is the method of control of transmission with stepless speed regulation and method for performing adjustment of transmission speed ratio.

EFFECT: increase of reliability and functional control of the device.

19 cl, 58 dwg

Stepless gearbox // 2499932

FIELD: machine building.

SUBSTANCE: stator plate for stepless gearbox contains several satellites installed around the main axis of rotation with power transmission due to engagement. Stator plate contains disk-shaped body installed coaxial to the main axis of rotation and several radially displaced guides arranged on the front surface of disk-shaped body and installed at an angle to the centre. Each radially displaced guide is displaced in linear direction from axial line of disk-shaped body.

EFFECT: improving performance.

14 cl, 17 dwg

FIELD: machine building.

SUBSTANCE: friction variable-speed drive contains a support contour, drive and driven shafts, rod being support for the driven gear link. Stepless change of the kinematic characteristics of the gear is ensured by the controlled rolling contact without sliding of the mate links, having spherical shape of the work surface. The gear ratio changes by rotation of the supporting contour and/or by change of the inclination angle of the driven shaft in relation to the drive shaft.

EFFECT: stepless versatile change of the movement kinematic characteristics.

1 dwg

FIELD: machine building.

SUBSTANCE: invention relates to a switching mechanism for continuously variable transmission. Embodiments provide components, assemblies, systems and/or methods for infinitely variable transmissions (IVT). In one embodiment, a control system is adapted to facilitate a change in ratio of an IVT. In another embodiment, a control system includes a carrier member configured to have a number of radially offset slots. Various inventive carrier members and carrier drivers can be used to facilitate shifting ratio of an IVT. In some embodiments, traction planet assemblies include planet axles (115) configured to cooperate with carrier members (116, 118). In one embodiment, carrier member is configured to rotate and apply a skew condition to each of planet axles. In some embodiments, a carrier member is operably coupled to a carrier driver.

EFFECT: higher efficiency of device.

26 cl, 38 dwg

FIELD: transport.

SUBSTANCE: invention relates to a continuously variable transmission and a control method. The transmission comprises a first drive tilting of few balls at an angle around the longitudinal axis and in contact with the first disc; the second disc in contact with several tilting balls; roller, radially disposed within the tilting balls and in contact with them, the cell connected with several balls. It also includes a first adgerence assembly connected to drive the first cell and the second clutch assembly coupled to the cage and the first disc. Two of the following: the first drive, the second drive roller and adaptedto the adapted to receive the cell input capacity. In this case one of a first drive, the second drive roller and the cage is adapted to provide output power.

EFFECT: invention provides a simplified design of transmission, lower cost and size of the device.

17 cl, 22 dwg

FIELD: transport engineering.

SUBSTANCE: invention can be used in wide range of vehicles, for instance, in minicars or trucks, snow movers, carts used when playing golf, cross country cars and scooters. Proposed driving pulley contains two centrifugal mechanisms, namely, positive unit and negative unit. Both units contains corresponding group of flyweights exposed to action of centrifugal force at rotation of driving pulley. Positive unit is used as standard speed governor which shifts one of two flanges of driving pulley towards other flange to increase diameter of running-over-over of driving pulley when speed rises. Negative unit is used to apply opposite force of positive unit when speed of rotation exceeds threshold value to delay rise of ratio of steplessly adjustable drive to higher ratio under action of positive unit. It provides maintenance of high speed of rotation at intensive acceleration and slow speed of rotation at slow speeds of vehicle.

EFFECT: provision of additional control over entire range of change of ratio of steplessly adjustable drive to decrease force created by centrifugal system of driving pulley.

12 cl, 6 dwg

FIELD: mechanical engineering.

SUBSTANCE: variator comprises rotating driving member (69), at least three power controllers, bearing member (18) for the friction contact with each of the power controllers, at least one platform (13a) and (13c), at least one unmovable base (5a) and (5c), and a number of shaft holders. Each shaft holder slides over the convex surface of platform (13a) and (13 c) and concave surface of unmovable base (5a) and (5c) and controls axis of rotation in response to the axial movement of the platform.

EFFECT: enhanced reliability and simplified structure.

73 cl, 16 dwg

FIELD: mechanical engineering.

SUBSTANCE: friction toroidal variator comprises inlet disk (2) and outlet disk (3) provided with toroidal surfaces, friction roller (5), spider whose one axle is provided with roller (5), holder (8) of friction roller, control mechanism, and mechanism for control of gear ratio. The second axle of the spider is fit in holder (8) of the friction roller that can rotate around the main axle of the variator. The control mechanism and mechanism for control of gear ration are made of gear sector (9) that rotates on the second axle of the spider secured to the first axle of the spider and housing (12) by means of worm gearing and spring (15) secured in housing (12) and connected with holder (8) directly or through the reduction gear.

EFFECT: simplified control and control of gear ratio.

8 dwg

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