Continuously variable transmission

 

(57) Abstract:

The invention relates to mechanical engineering, in particular for a continuously variable transmission (CVT) that provides a change speed power feed. Continuously variable transmission includes a drive shaft, output shaft, a torque Converter, a compound planetary gear and the planetary transmission to selectively provide drive in the opposite direction. The pump wheel of the torque Converter connected with the possibility of transmission of drive force to one of the elements of the planetary mechanism. The turbine wheel is connected with the possibility of transmission of drive force to another element of the compound planetary gear. The stator of the torque Converter is installed between the pump wheel and the turbine wheel with freewheel. A compound planetary gear is driven by a drive shaft. The design allows to obtain a large driving force, the preferred operational characteristics for smooth and quiet operation and stepless speed change during operation in reverse. 12 C. and 4 h.p. f-crystals,1 tab., 21 Il.

The invention relates to a continuously variable transmission (CVT), and more can be transmitted to the output shaft in accordance with the current load status, applied to the output , without removal of the lock or shift when changing speed in all gears are in engagement, and that the gear when rotated in the opposite direction can also be performed continuously variable or fixed ratio, simple way.

Generally, in the transmission shift speed is performed by selecting one from a number of preset gear ratios and during the change of speed there is a problem carefully turning the transmission. Conventional automatic transmissions are temporary device type, which have a very complicated construction of the road in the manufacture and cannot be used, because they have limited headroom due to the wear, noise and slippage.

The present invention was made to solve the above problems, therefore, the present invention is to develop a continuously variable transmission that does not use a complicated mechanism, which allows you to respond quickly to load changes, to smoothly transmit the rotational force, the stepless change speed direct Vij and to ensure an extended life.

To achieve this and other objectives of the present invention includes a system for switching transmission (shift speed), which receives the power generated by the engine, change speed and transmits it to the output shaft, the system switching control transfer (change of velocity), which can automatically control the transmission ratio of the speed of rotation corresponding to the load condition of the output shaft, and 4 different types of systems reverse rotation, in which, in particular, can be performed continuously variable transmission reverse rotation.

If we summarize the structural characteristics of the system change speeds, control change speeds and system reverse rotation, you can specify that the main property of the system change of velocity is that it uses a compound planetary mechanism, that is, it has 2 sets of gears (gearbox), in which each identical element (sun gear of the planetary gear or a gear wheel with internal toothing, is derived from 2 planetary gear sets (each of which includes a sun gear, planetary carrier, and a gear wheel with internal toothing) and re the and elements (planetary) kit and simultaneously with the driving element (s), the selected (s) from 2 sets.

In the control system of shift speeds is used an improved torque Converter, which is made with improvements in comparison with the known torque Converter automatic transmissions. If we consider the design of a control system of shift speeds, using the terminology related to the structural elements used in a traditional torque Converter, for convenience of explanation, you can specify that the control system of shift speeds includes a pump wheel, which is a master (drive) element, a turbine which is driven element, the stator to increase the torque coupling shaft for connection with a change of speed, a control shaft and a fixed axis for fastening the stator.

System reverse rotation has a planetary gear set (solar gear wheel, gear wheel with internal toothing, drove) and the brake and constructed with the ability to run continuously variable reverse rotation at a corresponding combination of relationship between each structural element of the planetary set and change system speed.

For a more complete understanding of the nature and objectives of the present invention should make reference to the following detailed description, taken together with the accompanying drawings, in which:

Fig. 1-10 illustrate a first variant implementation of the continuously variable transmission according to the present invention;

Fig. 1 is a schematic drawing of the continuously variable transmission of the present invention, which can operate in the first state of reverse rotation;

Fig. 2 is a schematic drawing of the continuously variable transmission of the present invention, which can operate in the second state of reverse rotation;

Fig. 3 is a schematic drawing of the continuously variable transmission of the present invention, which can operate in the third state of reverse rotation;

Fig. 4 is a schematic drawing of the continuously variable transmission of the present invention, which can operate at the fourth state of education is Ohm continuously variable transmission according to the present invention is idling in neutral state;

Fig. 6 represents a functional image showing the state of the direct rotation of the continuously variable transmission according to the present invention;

Fig. 7 is a functional image showing the first state of reverse rotation in a continuously variable transmission according to the present invention;

Fig. 8 is a functional image showing the second state of reverse rotation in a continuously variable transmission according to the present invention;

Fig. 9 is a functional image showing the third state of reverse rotation in a continuously variable transmission according to the present invention;

Fig. 10 is a functional image showing the fourth state of reverse rotation in a continuously variable transmission according to the present invention;

Fig. 11-21 are schematic drawings 2-12 options for the implementation of a continuously variable transmission according to the present invention.

To denote similar elements in the various images of graphic materials are used similar reference numbers and symbols.

The following is a description of a continuously variable transmission, A, which are connected to the control system by changing speeds. That is, the system shifts speeds may have a different structure, and stepless change speed transmission can be performed by appropriate connection of a control system of shift speeds by changing system speeds on the different variants of implementation.

First of all, the structure 100 in the first embodiment of implementation of the present invention, consisting of a system 10 controls the change speed transmission, the system 110 of the shift speeds and system RI ~ RIV reverse rotation attached to it, are described in detail with reference to the accompanying drawings.

The system 10 controls the change speed

In the system 10 to control the change of speed is normal torque Converter of the automatic transmission, which is a well known device. In a conventional automatic gearbox, the power generated by the engine is transmitted as a driving force on the master (drive) shaft of a transmission via a torque Converter, while the design of the present invention, the power generated by the engine is transmitted directly to the driving shaft, and the rotational force of the driving shaft by pomoshyu set of gears.

At that time, as a conventional torque Converter automatic transmission performs the function of transmission power, which consists in receiving the power generated by the engine, and the direct transmission of power to the driving shaft of the automatic transmission, the control system of shift speeds according to the present invention performs two functions, one of which is to control the ratio of velocity to harmonize it with the resistance movement, and the other is the transfer of power, "passing" through the control system by changing speeds on the output shaft.

Below is described the design of the system 10 to control the change of speed. As shown in Fig. 1, a hollow coupling shaft 14 is coaxially mounted on the drive shaft 12, and the hollow shaft 16 control coaxially mounted on the connecting shaft 14. The crankcase 18 of the pump wheel made in one piece with the connecting shaft 14, and the pump wheel 20 is made in one piece with the crankcase 18 of the pump wheel. The turbine wheel 22 facing the pump wheel 20, are combined in one unit with the shaft 16 control between the pump impeller 20 and the turbine wheel 22 posted by the stator 24, a hollow stationary axle 26 is coaxially mounted on the shaft hadicurari reverse rotation of the stator 24.

The system 110 of the shift speeds

As shown in Fig. 1, the system 110 of change of velocity with respect to the first embodiment of implementation of the present invention, the input (leading) a sun gear 112 made in one piece with the drive shaft 12, to which is supplied the engine. The first satellite 114 planetary gear is engaged with the outer side of the leading sun gear 112, and the second satellite 116 of the planetary gear made in one piece with the first satellite 114 planetary gear. The first satellite 114 planetary gear set and the second satellite 116 of the planetary gear set to the output (driven) Fadilah 118, 120 with the possibility of free rotation. The control sun gear 122 is engaged with the second satellite 116 of the planetary gear and made in one piece with the connecting shaft 14.

On the other hand, the output shaft 124 is installed coaxially with the drive shaft 212 and is connected to the slave measured including carriers 118, 120 by coupling direct connection system reverse rotation, which is installed between the slave measured including carriers 118, 120 and output shaft 124. Led led 118, 120 are combined in one unit with the shaft 16 of the control, which merged into one with turbinein system reverse rotation in the first embodiment of the present invention.

The present invention provides 4 different systems reverse rotation. For reference only, you can specify that the system of reverse rotation may be installed on the transmission line capacity, attached to the pump wheel for transmitting reverse rotation with a fixed gear ratio, however, the description of the construction and operation of such a system is reverse rotation is omitted.

1. System RI reverse rotation

As shown in Fig. 1, the system RI reverse rotation is provided between the output shaft 124 and the output (driven) measured including carriers 118, 120 of the system 110 of the shift speeds. The shaft 212 solar gear system reverse rotation is connected with the slave measured including carriers 118, 120 of the system 110 of the shift speeds to form one whole with them, and a sun gear 214 system reverse rotation made in one piece with the shaft 212 solar gear system reverse rotation. Satellite 218 planetary gear system reverse rotation is in engagement with the outer side sun gear 214 system reverse rotation and is mounted on a drive rod 218 system reverse rotation with the possibility of free rotation. The cog wheel 220 with the inner teeth of themes of reverse rotation and made in one piece with the output shaft 124. Brake 222 system reverse rotation is set on the outer side of the carrier 218 planetary gear system reverse rotation. Clutch 226 direct connection established between the output shaft 124 and the shaft 212 solar gear system reverse rotation so that the driven carrier 118 and 120 and the output shaft 124 can be connected with the actuation of the clutch 226 direct connection.

The gear train constituting this system RI reverse rotation, is a mechanism with single-stage planetary gear.

2. System RII reverse rotation

As shown in Fig. 2, the system RII reverse rotation is provided between the output shaft 124 and the driven (output) measured including carriers 118, 120 of the system 110 of the shift speeds. The sun gear 312 system reverse rotation made in one piece with the output shaft 124. Satellite 314 planetary gear system reverse rotation is in engagement with the outer side sun gear 312 system reverse rotation and mounted on the carrier 316 system reverse rotation with the possibility of free rotation. Gear 318 with internal teeth system reverse rotation is engaged with the outer Go with slaves measured including carriers 118, 120 system 110 changing speeds. Brake 320 system reverse rotation is set on the outer side of the carrier 316 system reverse rotation. Clutch 324 direct connection established between the slave measured including carriers 118, 120 and output shaft 124 so that the slaves took 118, 120 and the output shaft 124 can be connected with the actuation of the clutch 324 direct connection.

The gear train constituting this system RII reverse rotation, is a mechanism with single-stage planetary gear.

3. System RIII reverse rotation

As shown in Fig. 3, the system RIII reverse rotation is provided between the output shaft 124 and the driven (output) measured including carriers 118, 120 of the system 110 of the shift speeds. The shaft 412 solar gear system reverse rotation is connected with the slave measured including carriers 118, 120 of the system 110 of the shift speeds to form one whole, and a sun gear 414 system reverse rotation made in one piece with the shaft 412 solar gear system reverse rotation. Satellite 416 planetary gear system reverse rotation is in engagement with the outer side sun gear 414 system reverse rotation, and the other satellite 418 sq is Adachi system reverse rotation. These two satellites 416, 418 of the planetary gear system reverse rotation is set on the carrier 420 system reverse rotation with the possibility of free rotation. Drove 420 system reverse rotation made in one piece with the output shaft 124. Gear 422 with internal teeth system reverse rotation is in engagement with the outer side of the satellite 418 planetary gear system reverse rotation, and brake 424 system reverse rotation is set at the outer side gears 422 with internal teeth system reverse rotation. Clutch 428 direct connection established between the shaft 412 solar gear system reverse rotation and the planet carrier 420 system reverse rotation so that the slaves took 118, 120 and the output shaft 124 can be connected with the actuation of the clutch 428 direct connection.

The gear train constituting this system RIII reverse rotation, is a mechanism with two-stage planetary gear.

4. System RIV reverse rotation

As shown in Fig. 4, the system RIV reverse rotation is provided between the output shaft 124 and the driven (output) measured including carriers 118, 120 of the system 110 of the shift speeds. Solar the container transfer system reverse rotation is in engagement with the outer side solar gear wheel 512 system reverse rotation, and another satellite 516 planetary gear system reverse rotation is engaged (and) next to the satellite 514 planetary gear system reverse rotation. These two satellites 514, 516 planetary gear system reverse rotation mounted on a drive rod 518 system reverse rotation with the possibility of free rotation, and drove 518 system reverse rotation is connected with the slave measured including carriers 118, 120 of the system 110 of the shift speeds to form one whole. Gear 520 with internal teeth system reverse rotation is in engagement with the outer side of the satellite 516 planetary gear system reverse rotation, and brake 522 system reverse rotation is set at the outer side gears 520 with internal teeth system reverse rotation. Clutch 526 direct connection established between planet carrier 518 system reverse rotation output shaft 124 so that the slaves took 118, 120 and the output shaft 124 can be connected with the actuation of the clutch 526 direct connection.

The gear train constituting this system RIV reverse rotation, is a mechanism with two-stage planetary gear.

Each coupler 226, 324, 428, 526 directly the sludge 118, 120 and the output shaft 124 to connect as one by putting the coupling into operation in the state of forward rotation, but the clutch does not operate in a state of reverse rotation.

The following describes ways of working and the process of power transmission in accordance with these methods for each state change of speed (neutral, forward rotation and reverse rotation) of the continuously variable transmission according to the present invention with the above-described construction.

Before you explained it should be noted that although the continuously variable transmission (CVT) according to the present invention can be used in any mechanism in which a change of speed, which is the driving force, such as cars and industrial installation, as an example in this application explains the operation of the vehicle.

With the purpose of definition of terms indicates that the rotation (rotation) of each satellite planetary gear means rotating around its own axis (in this case, the locking pin), and the turnover refers to the case when the rotating carrier, i.e. a situation in which usually satellite planetary gear performs Saxena counterclockwise if you look on the left side of the drawings, is taken as the direction of rotation of the drive shaft, the rotation direction similar to the direction of rotation of the driving shaft is indicated as the direction (or direction) on each drawing, the same way the direction opposite to the direction of rotation of the driving shaft is indicated as the direction (or direction), rotation after stop (acceleration) is denoted as (or stop after rotation (slow) is denoted as (or state, in which the satellite planetary gear does not rotate around its own axis after rotation and the rotating body rotate as a unit with the same number of revolutions as the number of revolutions on the input, denoted as (or

The way to neutral state and condition of the forward rotation is described on the basis of the design, which combined system RI reverse rotation.

1. The neutral state (Fig. 5): the output shaft 124 is stopped.

Drive shaft Leading solar gear wheel of the First satellite 114 planetary gear (1) Second satellite 116 of the planetary gear

The control sun gear coupling shaft sump pump 18 wheels the feats of rotation

The sun gear 214 system reverse rotation - Satellite 216 planetary gear system reverse rotation Carrier 218 system reverse rotation (idling).

A neutral condition is a condition in which the clutch 226 direct connection raceplane and brake 222 system reverse rotation is released, the output shaft 124 may not be driven in rotation by the engine power, the system is idling, as shown in Fig. 5. That is, if the clutch 226 direct connection, which is installed between the output shaft 124 and the shaft 212 solar gear system reverse rotation, forming one unit with the slave measured including carriers 118, 120, disabled, no power transmission between the system 110 of the shift speed and the output shaft 124.

Drive shaft 12 is rotated by the feed power of the engine, leading the sun gear 112, made in one piece with the drive shaft 12 also rotates in A direction identical with the direction of rotation of the drive shaft 12, and the first satellite 114 planetary gear which engages with the leading solar gear wheel 112 rotates in the direction B opposite to the direction of rotation of the leading sun gear to the transmission, is driven into rotation in the direction b, and the control sun gear 122 which engages with the inner side of the second satellite 116 of the planetary gear, is driven into rotation in A direction opposite to the direction of rotation of the second satellite 116 of the planetary gear. The connecting shaft 14, connected c managing sun gear 122 to form one whole, the crankcase 18 of the pump wheel, attached to the connector 14, and the pump wheel 20, is made in one piece with the crankcase 18 of the pump wheel are rotated in the direction A.

The turbine wheel 22, mounted so that it is facing the pump wheel 20, is driven into rotation in the direction A due to the flow of fluid, the shaft 16 management, coupled with the turbine wheel 22 to form one whole, is driven into rotation in the direction A, and the driven carrier 118, 120 connected to the shaft 16 of the control to form one whole, are rotated in the direction A. the Shaft 212 solar gear system reverse rotation, made in one piece with the slave measured including carriers 118, 120 also is driven into rotation in the direction A, the sun gear 214-back system is designed in rotation in the direction A and causes the rotation of the satellite 216 planetary gear system reverse rotation, located in engagement with the outer side sun gear 214 system reverse rotation in the direction B. Since the output (slave) the cog wheel 220 with internal teeth that are in engagement with the outer side of the satellite 216 planetary gear system of the reverse rotation is stopped due to the pressures applied by the output shaft 124, drove system reverse rotation rotates at idling speed in the direction A.

II. The state of the forward rotation (Fig. 6)

Drive shaft Leading solar gear

The first satellite 114 planetary gear

(1) the Second satellite 116 of the planetary transmission Control sun gear coupling shaft sump 18 of the pump wheel of the Pump wheel Turbine wheel Shaft 16 management

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The shaft 212 solar gear system reverse rotation (Coupling direct connection) - Output shaft

This is a condition in which the clutch 226 direct connection established between the output shaft 124 and the shaft 212 solar gear system reverse rotation, made in one piece with the slave measured including carriers 118, 120, powered.

If the engine is fed to the driving shaft 12, Weasley A, similar to the direction of rotation of the drive shaft 12, the first satellite 114 planetary gear which engages with the leading solar gear wheel 112, is driven into rotation in the direction B opposite to the direction of rotation of the leading solar gear wheel 112, as slaves drove 118, 120 is stopped due to the pressures applied by the output shaft 124 that is connected with them by means of coupling 226 direct connection. Due to the rotation of the first satellite 114 planetary gear of the second satellite 116 of the planetary gear connected with the first satellite 114 planetary gear set to form one whole, is driven into rotation in the direction In and slows down the rotation in the direction A of the control sun gear 112 which engages with the second satellite 116 of the planetary gear. Coupling shaft 14 connected with the control sun gear 122 to form one whole, the crankcase 18 of the pump wheel connected c connecting shaft 14 to form one whole, and pump wheel 20, is made in one piece with the crankcase 18 of the pump wheel, slow down and are rotated in the direction A.

In this case, considering Opera provided when the output shaft 124 that is attached to the slave vadilal 118, 120 by actuating the clutch 226 direct connection, the shaft 16 of the control and the turbine wheel 22 is stopped, the rotational force transmitted to the first satellite 114 planetary gear set through a leading solar gear wheel 112, increases with the second satellite 116 of the planetary gear and is transmitted to the Manager of the solar gear wheel 122. Increased rotational force is transferred through the connecting shaft 14, made in one piece with the control sun gear 122, and the crankcase 18 of the pump wheel, attached to the connecting shaft 14 to form one whole, and on the pump wheel 20, is made in one piece with the crankcase 18 of the pump wheel. At this point, due to the fact that the turbine wheel 22 is stopped due to the pressures applied by the output shaft 124 through the actuation of the clutch 226 direct connection, there is a mismatch of spins between pump wheel and turbine wheel.

Based on the characteristics of the torque Converter is increased rotational force of the pump wheel 20 is transmitted to the turbine impeller 22, and the rotational force is transferred to the turbine impeller 22, prasowaniem one whole, and, if the resistance force acting on the output shaft 124, and the rotational force is transmitted to the turbine wheel 22 are in balance, the output shaft 124 is driven into rotation. It represents the state of the beginning of the movement (hill start assist) with a low speed.

If the engine speed increases, the error of the spins between the pump impeller 20 and the turbine wheel 22 becomes larger and, therefore, increases the rotational force transmitted turbine impeller 22, and, if the rotational force is transferred to the turbine impeller 22, there will be more resistance forces acting on the turbine wheel 22 through the load side of the output shaft 124, the output shaft 124 is accelerated up until the rotational force of the turbine wheel 22 is transmitted from the pump wheel 20 will not come into equilibrium with the force of resistance acting on the turbine wheel 22.

If the output shaft 124 is accelerated, the load acting from the side of the output shaft 124 is reduced, therefore, also decreases the resistance force acting on the turbine wheel 22. If the resistance force acting on the turbine wheel 22, decreases, the error of the spins between the pump is therefore accelerating the rotation of the turbine wheel 22 in A direction identical with the direction of rotation of the pump wheel 20, as well as accelerating the rotation in the direction of A driven carrier 118, 120 connected to the turbine wheel 22. The rotation of the output shaft 124 combined into one unit with the slave measured including carriers 118, 120 is accelerated, and, if the load acting from the side of the output shaft 124, further reduced due to the acceleration of rotation of the output shaft 124, and thus the load comes into equilibrium with the driving force of the driving shaft 12, the pump impeller 20 and the turbine wheel 22 are rotated with gear ratio 1:1, and the first satellite 114 planetary gear set and the second satellite 116 of the planetary gear does not rotate around their own axes, but all of a rotating body rotate as one unit. This is a high-speed condition.

In this embodiment, considering the rotational force transmitted to the pump wheel 20, it is possible to indicate that, since the rotational force is increased compared with the rotational force of the driving shaft 12 through the first satellite 114 planetary gear set and the second satellite 116 of the planetary gear, acts on the pump wheel 20 th wheel 22, then to the output shaft 124 in a state (of motion) with a low speed will be accompanied by a large rotational force is thus achieved very good acceleration and efficiency.

III. The state of reverse rotation (Fig. 7 - 10)

1. I state of reverse rotation (Fig. 7)

Drive shaft Leading solar gear

The first satellite 114 planetary gear

(1) the Second satellite 116 of the planetary gear

The control sun gear coupling shaft sump 18 of the pump wheel of the Pump wheel Turbine wheel Shaft 16 management

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The shaft 212 solar gear system reverse rotation Sun gear 214 system reverse rotation of the Satellite 216 planetary gear system reverse rotation

(3) Took 218 system reverse rotation: stopped (due to actuate the brake system reverse rotation)

(4) the Cog wheel 220 with internal teeth system reverse rotation of the Output shaft 124

In the first state of reverse rotation clutch 226 direct connection is disconnected and the brake 222 system reverse rotation, mounted on Fadilah 218 system reverse rotation, powered (included).

If the power of the engine is driven in the direction A, similar to the direction of rotation of the drive shaft 12. Because slaves were taken 118, 120, shaft 212 solar gear system reverse rotation, connected c slave measured including carriers 118, 120 to form one whole, and a sun gear 214 system reverse rotation, made in one piece with the shaft 212 solar gear system reverse rotation, are in an instant standstill together with the output shaft 124 through the brake 222 system reverse rotation, the first satellite 114 planetary gear which engages with the leading solar gear wheel 112, is driven into rotation in the direction B, opposite to the direction of rotation of the leading solar gear wheel 112, and slows down and causes the rotation in the direction And control of the solar gear wheel 122 with the second satellite 116 of the planetary gear. In addition, the connecting shaft 14, connected to the control sun gear wheel 122 to form one whole, the crankcase 18 of the pump wheel, made in one piece with the connecting shaft 14, and the pump wheel 20, is made in one piece with the crankcase 18 of the pump wheel, slow down and are rotated in the direction A.

If the engine speed increases, the error of the spins between the pump impeller 20 and the turbine wheel 22 becomes large, and therefore, increases the rotational force transmitted turbine impeller 22, and when the rotational force is transferred to the turbine impeller 22, there will be more resistance forces acting on the turbine wheel 22 through the sun gear 214 system reverse rotation due to the load side of the output shaft 124, a sun gear 214 system reverse rotation is accelerated up until the rotational force of the turbine wheel 22 is transmitted from the pump wheel 20, would not be in equilibrium c force acting on the turbine wheel 22, and the rotation of the gear wheel 220 with internal teeth system reverse rotation, made in one piece with the output shaft 124, is accelerated in the direction B by using satellite 216 planetary gear si is adequate from the side of the output shaft 124, decreases decreases resistance force acting on the turbine wheel 22 through the sun gear 214 system reverse rotation. If the resistance force acting on the turbine wheel 22, decreases, the error of the spins between the pump impeller 20 and the turbine wheel 22 to until the rotational force would not be in equilibrium with the force of resistance. Therefore, accelerates the rotation of the turbine wheel 22 in A direction identical with the direction of rotation of the pump wheel 20, as well as accelerating the rotation in the direction of A shaft 16 control connected to the turbine wheel 22 to form one whole, and the rotation in the direction of A driven carrier 118, 120 connected with the shaft 16 of the control with the formation of one whole. If accelerated rotation of the driven carrier 118, 120, it also accelerates the rotation shaft 212 solar gear system reverse rotation connected to the slave measured including carriers 118, 120 to form one whole, and a sun gear 214 system reverse rotation, and, in addition, with the help of satellite 216 planetary gear system reverse rotation also accelerates the rotation of the gear wheel 220 with internal teeth system reverse VRO rotation according to the system of RI reverse rotation according to the present invention (similar to other systems of reverse rotation) is what stepless drive (stepless movement in the opposite direction can be performed in accordance with the load side of the output shaft 124 even at the time of reverse rotation.

Considering the rotational force transmitted to the output shaft 124 when the system RI reverse rotation according to the present invention, it is possible to indicate that the rotational force is increased to a greater extent in comparison with the rotational force of the driving shaft 12 through the first satellite 114 planetary gear set and the second satellite 116 of the planetary gear is transmitted to the control sun gear 122 which acts on the pump wheel 20 through the connecting shaft 14, and the rotational force is additionally increased by the pump wheel 20, which acts on the turbine wheel 22, also transmitted to the sun gear wheel 214 system reverse rotation through the shaft 16 of the control that is attached to the turbine wheel 22 to form one whole, and through guided drove 118, 120, attached to the control shaft and to the shaft 212 solar gear system reverse rotation to form one whole, and with the help of satellite 216 planetary gear system reverse rotation leads pohodnym shaft 124, and thus, during the reverse rotation of the output shaft 124 is driven large rotational force, so that the acceleration increases and efficiency, and can ensure a smooth and quiet ride even during operation in reverse.

2. II the state of reverse rotation (Fig. 8)

Drive shaft Leading solar gear

The first satellite 114 planetary gear (1) Second satellite 116 of the planetary transmission Control sun gear coupling shaft sump 18 of the pump wheel of the Pump wheel Turbine wheel Shaft 16 management

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Gear 318 with internal teeth system reverse rotation

(3) Drove 316 system reverse rotation: stopped (due to actuate the brake system reverse rotation)

(4) Satellite 314 planetary gear system reverse rotation Sun gear 312 system reverse rotation of the Output shaft

In the second state of reverse rotation clutch 324 direct connection is disconnected and the brake 320 system reverse rotation, mounted on a drive rod 316 system reverse rotation enabled.

Since the direction of rotation and the power at the second state of reverse rotation to and when I state reverse rotation, described above for the system RI reverse rotation, their description is omitted here and only describes the procedure for transferring power to the output shaft 124 through the system RII reverse rotation.

As shown in Fig. 8, the gear 318 with internal teeth system reverse rotation, coupled with the slave measured including carriers 118, 120 to form one whole, is driven into rotation in the direction A, the same as the direction of rotation of the driven carrier 118, 120, due to the rotation of the driven carrier 118, 120 of the system 110 of the shift speeds. Because led 316 system reverse rotation is stopped due to the brake system 220 reverse rotation, the satellite 314 planetary gear system reverse rotation which engages with the inner side gears 318 with internal teeth system reverse rotation, is driven into rotation in A direction identical with the direction of rotation of the gears 318 with internal teeth system reverse rotation, and causes the rotation of the sun gear 312 system reverse rotation which engages with the inner side of the satellite 314 planetary gear system reverse rotation in the direction B opposite to the direction A. the AOC is m one whole, is driven into rotation in the direction B due to the rotation of the sun gear 312 system reverse rotation.

3. III the state of reverse rotation (Fig. 9)

Drive shaft Leading solar gear

The first satellite 114 planetary gear (1) Second satellite 116 of the planetary gear

The control sun gear coupling shaft sump 18 of the pump wheel of the Pump wheel Turbine wheel Shaft 16 management

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The shaft 412 solar gear system reverse rotation of the Satellite 416 planetary gear system reverse rotation

(3) Satellite 418 planetary gear system reverse rotation Gear 422 of the internal teeth of a system of reverse rotation is stopped (due to actuate the brake system reverse rotation)

(4) Led 420 system reverse rotation of the Output shaft 124

In the III system state reverse rotation clutch 428 direct connection is disconnected and the brake 424 system reverse rotation, mounted on the toothed wheel 422 with internal teeth system reverse rotation enabled.

Since the direction of rotation and the power at the third state of reverse rotation p and when I state reverse rotation, described above for the system RI reverse rotation, their description is omitted here and only describes the procedure for transferring power to the output shaft 124 through the system RIII reverse rotation.

As shown in Fig. 9, the shaft 412 solar gear system reverse rotation attached to the slave vadilal 118, 120 c form one whole with them, is driven into rotation in A direction identical with the direction of rotation of the driven carrier 118, 120, due to the rotation of the driven carrier 118, 120 of the system 110 of the shift speeds, and a sun gear 414 system reverse rotation, made in one piece with the shaft 412 solar gear system reverse rotation, is driven into rotation in the direction A. the Sun gear 414 system reverse rotation causes the rotation in the opposite direction B satellite 416 planetary gear system reverse rotation which engages with a sun gear 414 system reverse rotation, and the satellite 416 planetary gear system reverse rotation causes the rotation in the direction of A different satellite 418 planetary gear system reverse rotation adjacent and in engagement with satellite 416 planetary the rotation tends to rotate the gear 422 with internal teeth system reverse rotation, located in engagement with the outer side of the satellite 418 planetary gear system reverse rotation as the gear 422 with internal teeth system reverse rotation is stopped due to the inclusion of brake 424 system reverse rotation, the satellite 418 planetary gear system reverse rotation causes the led 420 system reverse rotation into rotation in the direction C. in Addition, the output shaft 124, is attached to the cage 420 system reverse rotation to form one whole, rotates in the direction B.

4. IV the state of the system reverse rotation (Fig. 10)

Drive shaft Leading solar gear

The first satellite 114 planetary gear

(1) the Second satellite 116 of the planetary transmission Control sun gear coupling shaft sump 18 of the pump wheel of the Pump wheel Turbine wheel Shaft 16 management

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Drove 518 system reverse rotation

(3) the Satellite 516 planetary gear system reverse rotation Gear 520 with internal teeth system reverse rotation: stopped (due to actuate the brake system reverse rotation)

(4) Satellite 514 planetary gear system clicks the system reverse rotation clutch 526 direct connection disabled and brake 522 system reverse rotation, mounted on the toothed wheel 522 with internal teeth system reverse rotation enabled.

Since the direction of rotation and the procedure of the transmission power when the fourth state of reverse rotation according to the present invention when the system 110 of the shift speeds, and the system 10 controls the shift speeds are the same as when I state reverse rotation described above for system RI reverse rotation, their description is omitted here and only describes the procedure for transferring power to the output shaft 124 through the system RIV reverse rotation.

As shown in Fig. 10, drove 518 system reverse rotation attached to the slave vadilal 118, 120 to form with them one whole, is driven into rotation in A direction identical with the direction of rotation of the driven carrier 118, 120, due to the rotation of the driven carrier 118, 120 of the system 110 of the shift speeds. The rotation is transmitted to the satellites 514, 516 planetary gear system reverse rotation when the rotation of the carrier 518 system reverse rotation, and since the gear 520 with internal teeth system reverse rotation which engages with the outer side of the satellite 516 planetary gear system Obratnaya system reverse rotation is driven in the opposite direction B and causes the rotation in the direction of A satellite 514 planetary gear system reverse rotation, being engaged (and) next to it. Solar gear wheel 512 system reverse rotation which engages with the inner side of the satellite 514 planetary gear system reverse rotation, rotates in the opposite direction B, and rotates the output shaft 124 attached to it to form one whole, in the same direction B.

The following describes embodiments of the present invention from the 2nd to the 12th. In the description of embodiments of the present invention from the 2nd to the 12th, taking into account the fact that the construction and method of operation of the control system by changing the speeds are the same as in the case of a control system of change of velocity with respect to the first variant of implementation, the description of the construction and method of operation of the control system by the change of speed is lowered, and despite the fact that there is a difference also in the design of the system change speeds, way of working or change speeds similar to the way you work or the process of change of velocity with respect to the first variant of implementation, and therefore, detailed description of them is omitted. Similarly, because the design principle system installation reverse rotation is the same as in the first embodiment, sushestvovanie omitted.

In addition, despite the fact that the provisions of the pump wheel I and the turbine wheel T can be changed in the control system of shift speeds, because the way of working and procedure of the transmission power during the change of speed in the control system by changing speeds similar way of working and the process of power transmission in the first embodiment of implementation of the present invention, their description is also omitted.

Therefore, given the similarity of construction, method of work and procedures of the shift speeds described above, the design of each alternative implementation is shown schematically for simplicity and ease of explanation.

That is, in Fig. 11-21 shows schematic drawings of embodiments 2 to 12, and shows the structure that is attached to the system RI reverse rotation.

Despite the fact that in the system of change of velocity is mainly used complex planetary gear (gear), there are differences in the way the supply (capacity), the connection method of the block of gear wheels of the pump wheel and the turbine wheel and the way of combining the components of the structural elements. However, since the operation method and the procedure for changing the speeds are the same as S together with the corresponding image on the appropriate drawing.

For reference below describes the symbols of the basic elements used in tables and figures.

I: pump wheel T: turbine wheel

S: stator B1: brake system reverse rotation

CLD: coupling direct connection

DP: the set of satellites in two-stage planetary gear

DP12: the first set of satellites two-stage planetary gear

DP21: a second set of satellites as a two-stage planetary gear

SP: a set of satellites single-stage planetary gear

SP12: the first set of satellites single-stage planetary gear

SP21: a second set of satellites single-stage planetary gear

S1: the first sun gear

S2: the second sun gear

C1: first drove C2: second drove

C12, C21: the planetary carrier

RI: the first gear wheel with internal toothing

R2: the second gear wheel with internal toothing

SR: Sunny gear system reverse rotation

CR: the planetary carrier system reverse rotation

RR: gear wheel with internal toothing system reverse rotation

In this case, the order is indicated by the number 1 and second (or left) is indicated by the number 2. Two figures (12 or 21) for index mean integrated type, i.e. mean that the elements are connected to each other to form one whole. In this case, 12 denotes a right side and 21 denotes the left part. The planetary gear is used in the system RI ~ RIV reverse rotation, is a single-stage planetary gear or two-stage planetary transmission. Single-stage planetary gear includes a sun gear SRsystem reverse rotation, a set of satellites SP single-stage planetary gear, carrier CRplanetary gear system reverse rotation and a gear wheel RRwith the internal toothing system reverse rotation. Two-stage planetary gear includes a sun gear SRsystem reverse rotation, a set of satellites DP two-stage planetary gear, carrier CRplanetary gear system reverse rotation and a gear wheel RRwith the internal toothing system reverse rotation.

Each reference number in the first embodiment corresponds to the notation given in the end of the description.

In the present invented the Dila, employee support the satellite and the gear wheel with internal toothing and by creating an appropriate combination of all elements, the proper choice of the input (master) element and how to set the gear ratio, and, in addition, accession to the turbine impeller, and pump wheel and brake system reverse rotation may vary, therefore, the scope of the present invention is not limited variant implementation, shown as examples.

For example, a 5th option implementation (this design is denoted as (T) (I) (A)) shown in Fig. 14, and in this case, the desired goal can be achieved by using a design in which the lateral location (T) (turbine wheel) and (I) (pump impeller) reversed, that is, constructions (I)(T) (A), and its example is shown in Fig. 14A.

In addition, even if the input element is changed in relation to the symmetry of the input (master) element, the desired goal can be achieved. Namely, the example design (T) (I) (B), in which the input (master) element is changed from the point of view of symmetry in the 5th embodiment shown in Fig. 14B, and in this case, the desired goal can be achieved by using a design in which ptx2">

For reference, you can specify that, if instead of system reverse rotation (RI ~ RIV) has a system of reverse rotation, which is installed on the transmission line power is connected to the pump wheel in the operation of the actuator when the reverse rotation is performed at a fixed ratio), (T) and (I) can be placed on the side of the output shaft, and an example of this design (A)-(T) (I) is shown in Fig. 14D. In this case, the sample design, in which lateral location (T) and (I) reversed, that is, constructions (A)-(I) (T), shown in Fig. 14E.

In constructions in which the input element is changed from the point of view of symmetry of the input element, if there is a system of reverse rotation, which is installed on the transmission line power is connected to the pump wheel, (T) and (I) can be placed on the side of the output shaft, and an example of this design (B)-(T) (I) is shown in Fig. 14F, and in this case, the sample design, in which lateral location (T) and (I) reversed, i.e. design (B) - (I) (T), shown in Fig. 14C.

As described above, the present invention based on the embodiment shown as an example, you can decree Obedinenie the turbine wheel and the pump wheel, and naturally functioning designs will vary in accordance with characteristics of each alternative implementation. Despite the fact that each of these possible examples are not particularly described herein, such possible examples naturally be within the scope of the present invention, taking into account the meaning of the present invention.

Despite the fact that the gear ratio between the first and second satellites planetary gear and the gear ratio between the sun gear and the gear wheel with internal toothing is not described in the claims, because you can fully understand embodiments of the present invention, taking into account the principle of operation of the structures of the present invention or, if necessary, considering the drawings, it is of course the exception of the description of the gear ratio does not restrict the scope of the present invention.

Obviously, continuously variable transmission according to the present invention is not limited presents options for implementation, but can be used in all devices, which allows speed change (application) driving the present invention, and that within the scope of the present invention can be made of various modifications and changes.

As described above, the continuously variable transmission of the present invention is able to react quickly to load changes and smoothly transmit the rotational force in the state in which all gears are in engagement, and, in addition, can steplessly change the speed in the forward rotation and reverse rotation with a simple design, it also enables to reduce the manufacturing costs and provide increased durability.

1. Continuously variable transmission (CVT), comprising: a drive shaft IS to supply power to the transmission; an output shaft OS for transmitting power from the gearbox; a compound planetary gear mechanism that includes:(i) the first sun gear SI, driven drive shaft IS; (ii) the first set of satellites SP12 single-stage planetary gear which engages with the first sun gear SI; (iii) a second set of satellites SP21 single-stage planetary gear, is attached rotatably to the first set of satellites SP12 single-stage planetary gear; (iv) vtoi planetary gear, and (v) drove C12, C21 planetary gear set to provide a support rotatably to the above first and second sets of satellites SP12, SP21, pump wheel (I), connected with the possibility of transmission of drive force to the second sun gear wheel S2; the turbine wheel (T), connected with the possibility of transmission of drive force to the cage C12, C21 planetary gear set, and the stator (S), installed between the pump wheel and turbine wheel with freewheel.

2. Continuously variable transmission (CVT), comprising: a drive shaft IS to supply power to the transmission; an output shaft OS for transmitting power from the gearbox; a compound planetary gear mechanism that includes: (i) a first toothed wheel RI with internal gearing; (ii) the first set of satellites SP12 single-stage planetary gear which engages with the first toothed wheel RI with internal gearing; (iii) a second set of satellites SP21 single-stage planetary gear, is attached rotatably to the first set of satellites SP12 single-stage planetary gear; (iv) second gear R2 with internal toothing which engages with the second complex, C21 planetary gear set to provide a support for rotation for the first and second sets of satellites SP12, SP21, pump wheel (I), connected with the possibility of transmission of drive force to the first gear wheel RI with internal gearing; the turbine wheel (T), connected with the possibility of transmission of drive force to the cage C12, C21 planetary gear set, and the stator (S), installed between the pump wheel and turbine wheel with freewheel.

3. Continuously variable transmission (CVT), comprising: a drive shaft IS to supply power to the transmission; an output shaft OS for transmitting power from the gearbox; a compound planetary gear mechanism that includes: (i) the first sun gear SI; (ii) the first set of satellites SP12 single-stage planetary gear which engages with the first sun gear SI; (iii) a second set of satellites SP21 single-stage planetary gear, is attached rotatably to the first set of satellites SP12 single-stage planetary gear; (iv) the second sun gear S2, located in engagement with the second set of satellites SP21 single-stage planetary perezajennogo and second sets of satellites SP12, SP21 and driven drive shaft IS; a pump wheel (I), connected with the possibility of transmission of drive force to the first sun gear S1 wheel; a turbine wheel (T), connected with the possibility of transmission of drive force to the second sun gear wheel S2, and the stator (S), installed between the pump wheel and turbine wheel with freewheel.

4. Continuously variable transmission (CVT), comprising: a drive shaft IS to supply power to the transmission; an output shaft OS for transmitting power from the gearbox; a compound planetary gear mechanism that includes: (i) the first gear R1 with internal gearing; (ii) the first set of satellites SP12 single-stage planetary gear which engages with the first gear R1 with internal gearing; (iii) a second set of satellites SP21 single-stage planetary gear, is attached rotatably to the first set of satellites SP12 single-stage planetary gear; (iv) second gear R2 with internal toothing which engages with the second set of satellites SP21 single-stage planetary gear, and (v) drove C12, C21 planetary gear set, p is, P21 and driven drive shaft IS; a pump wheel (I), connected with the possibility of transmission of drive force to the second gear wheel R2 with internal gearing; the turbine wheel (T), connected with the possibility of transmission of drive force to the first gear wheel R1 with internal gearing, and the stator (S), installed between the pump wheel and turbine wheel with freewheel.

5. Continuously variable transmission (CVT), comprising: a drive shaft IS to supply power to the transmission; an output shaft OS for transmitting power from the gearbox; a compound planetary gear mechanism that includes: (i) the first sun gear S1, a driven drive shaft IS; (ii) the first set of satellites DP12 two-stage planetary gear which engages with the first sun gear SI; (iii) a second set of satellites DP21 two-stage planetary gear, is attached rotatably to the first set of satellites DP12 two-stage planetary gear; (iv) the second sun gear S2, which is in mesh with a second set of satellites DP21 two-stage planetary transmission, and (v) drove C12, C21 plane, DP21; a pump wheel (I), connected with the possibility of transmission of drive force to the second sun gear wheel S2; the turbine wheel (T), connected with the possibility of transmission of drive force to the cage C12, C21 planetary gear set, and the stator (S), installed between the pump wheel and turbine wheel with freewheel.

6. Continuously variable transmission (CVT), comprising: a drive shaft IS to supply power to the transmission; an output shaft OS for transmitting power from the gearbox; a compound planetary gear mechanism that includes: (i) the first sun gear S1, a driven drive shaft IS; (ii) the first set of satellites SP12 single-stage planetary gear which engages with the first sun gear S1; and (iii) a second set of satellites DP21 two-stage planetary gear, is attached rotatably to the first set of satellites SP12 single-stage planetary gear; (iv) the second sun gear S2, which is in mesh with a second set of satellites DP21 two-stage planetary transmission, and (v) drove C12, C21 planetary gear set to provide a support rotatably to pervogo efforts to cage C12, C21; the turbine wheel (T), connected with the possibility of transmission of drive force to the second sun gear wheel S2, and the stator (S), installed between the pump wheel and turbine wheel with freewheel.

7. Continuously variable transmission (CVT), comprising: a drive shaft IS to supply power to the transmission; an output shaft OS for transmitting power from the gearbox; a compound planetary gear mechanism that includes: (i) the first sun gear S1, a driven drive shaft IS; (ii) the first set of satellites DP12 two-stage planetary gear which engages with the first sun gear S1; and (iii) a second set of satellites SP21 single-stage planetary gear, is attached rotatably to the first set of satellites DP12 two-stage planetary gear; (iv) the second sun gear S2, which is in mesh with a second set of satellites SP21 single-stage planetary gear, and (v) drove C12, C21 planetary gear set to provide a support for rotation for the first and second sets of satellites DP12, SP21, pump wheel (I) connected with the transmission drive mu sun gear wheel S2; and the stator (S), installed between the pump wheel and turbine wheel with freewheel.

8. Continuously variable transmission (CVT), comprising: a drive shaft IS to supply power to the transmission; an output shaft OS for transmitting power from the gearbox; a compound planetary gear mechanism that includes: (i) the first gear R1 with internal gearing driven drive shaft IS; (ii) the first set of satellites DP12 two-stage planetary gear which engages with the first gear R1 with internal gearing; (iii) a second set of satellites DP21 two-stage planetary gear, attached rotatably to the first set of satellites DP12 two-stage planetary transmission; (iv) a second gear R2 with internal toothing which engages with the second set of satellites DP21 two-stage planetary transmission, and (v) drove C12, C21 planetary gear set to provide a support for rotation for the first and second sets of satellites DP 12, DP21, pump wheel (I), connected with the possibility of transmission of drive force to the second gear wheel R2 with internal gearing; the turbine wheel is(S), installed between the pump wheel and turbine wheel with freewheel.

9. Continuously variable transmission (CVT), comprising: a drive shaft IS to transmit power to the transmission; an output shaft OS for transmitting power from the gearbox; a compound planetary gear mechanism that includes: (i) the first gear R1 with internal gearing driven drive shaft IS; (ii) the first set of satellites SP12 single-stage planetary gear which engages with the first gear R1 with internal gearing; (iii) a second set of satellites DP21 two-stage planetary gear, attached rotatably to the first set of satellites SP12 single-stage planetary gear; (iv) a second gear R2 with internal toothing which engages with the second set of satellites DP21 two-stage planetary transmission, and (v) drove C12, C21 planetary gear set to provide a support for rotation for the first and second sets of satellites SP12, DP21, pump wheel (I), connected with the possibility of transmission of drive force to the cage C12, C21; the turbine wheel (T), attached to the possibility of transferring the PRIOME and turbine wheel with freewheel.

10. Continuously variable transmission (CVT), comprising: a drive shaft IS to supply power to the transmission; an output shaft OS for transmitting power from the gearbox; a compound planetary gear mechanism that includes: (i) the first gear R1 with internal gearing driven drive shaft IS; (ii) the first set of satellites DP12 two-stage planetary gear which engages with the first gear R1 with internal gearing; (iii) a second set of satellites SP21 single-stage planetary gear, attached rotatably to the first set of satellites DP12 two-stage planetary transmission; (iv) a second gear R2 with internal toothing which engages with the second set of satellites SP21 single-stage planetary gear, and (v) drove C12, C21 planetary gear set to provide a support for rotation for the first and second sets of satellites DP12, SP21, pump wheel (I), connected with the possibility of transmission of drive force to the cage C12, C21; the turbine wheel (T), attached is able to transmit drive force to the second gear wheel R2 with internal gearing, and the stator (S) installed between the heredoc (variable), contains: drive shaft IS to supply power to the transmission; an output shaft OS for transmitting power from the gearbox; a compound planetary gear mechanism that includes: (i) the first sun gear S1; (ii) the first set of satellites DP12 two-stage planetary gear which engages with the first sun gear S1; and (iii) a second set of satellites DP21 two-stage planetary gear, is attached rotatably to the first set of satellites DP12 two-stage planetary transmission; (iv) the second sun gear S2, located in engagement with the second set of satellites DP21 two-stage planetary transmission, and (v) drove C12, C21 planetary gear designed to support rotatably to the first and second sets of satellites DP12, DP21 and driven drive shaft IS; a pump wheel (I), connected with the possibility of transmission of drive force to the first sun gear S1 wheel; a turbine wheel (T), connected with the possibility of transmission of drive force to the second sun gear wheel S2, and the stator (S), installed between the pump wheel and turbine wheel with clutch svobodnogo transmission; the output shaft OS for transmitting power from the gearbox; a compound planetary gear mechanism that includes: (i) the first gear R1 with internal gearing; (ii) the first set of satellites DP12 two-stage planetary gear which engages with the first gear R1 with internal gearing; (iii) a second set of satellites DP21 two-stage planetary gear, is attached rotatably to the first set of satellites DP12 two-stage planetary transmission; (iv) a second gear R2 with internal toothing which engages with the second set of satellites DP21 two-stage planetary gear, and (v) drove C12, C21 planetary gear designed to support rotatably to the first and second sets of satellites DP12, DP21 and driven drive shaft IS; a pump wheel (I), connected with the possibility of transmission of drive force to the first gear wheel R1 with internal gearing; the turbine wheel (T), connected with the possibility of transmission of drive force to the second gear wheel R2 with internal gearing, and the stator (S), installed between the pump wheel and the turbine wheel by coupling documenatry planetary gearing to selectively provide drive (movement) in the opposite direction, includes: (i) a sun gear SRsystem reverse rotation, connected with the possibility of transmission of drive force to the output drive element of the compound planetary mechanism; (ii) the set of satellites SP single-stage planetary gear being in mesh with a sun gear SRsystem reverse rotation; (iii) drove CRsystem reverse rotation designed to provide support to rotate for a set of satellites SP single-stage planetary gear; (iv) a gear wheel RRwith the internal toothing system reverse rotation which engages with a set of satellites SP single-stage planetary gear and join in the working position to the output shaft OS; brake B1 system reverse rotation for selective entry into the contact (adhesion) with the planet carrier CRfor reversing the movement and clutch CLD direct connection for selectively coupling the output drive element of the compound planetary gear with the output shaft OS to ensure movement (actuator) in the forward direction (forward).

14. Continuously variable transmission according to any one of paragraphs.1-12, more in the opposite direction, includes: (i) a sun gear SRsystem reverse rotation, connected with the possibility of transmission of drive force to the output shaft OS; (ii) the set of satellites SP single-stage planetary gear being in mesh with a sun gear SRsystem reverse rotation; (iii) drove CRsystem reverse rotation designed to provide support to rotate for a set of satellites SP single-stage planetary gear; (iv) a gear wheel RRwith the internal toothing system reverse rotation, connected with the possibility of transmission of drive force to the output drive element of the compound planetary gear and being in engagement with a set of satellite SP single-stage planetary gear; brake B1 system reverse rotation for selective coupling with the planet carrier CRfor reversing the movement and clutch CLD direct connection for selectively coupling the output drive element of the compound planetary gear with the output shaft OS to ensure movement (actuator) in the forward direction (forward).

15. Continuously variable transmission according to any one of paragraphs.1-12, d is to be placed) in the opposite direction, includes: (i) a sun gear SRsystem reverse rotation, connected with the possibility of transmission of drive force to the output drive element of the compound planetary mechanism; (ii) the set of satellites DP two-stage planetary gear being in mesh with a sun gear SRsystem reverse rotation; (iii) drove CRsystem reverse rotation designed to provide support to rotate for a set of satellites DP two-stage planetary gear and connected with the possibility of transmission of drive force to the output shaft OS, and (iv) a gear wheel RRwith the internal toothing system reverse rotation which engages with a set of satellites DP two-stage planetary gear; brake B1 system reverse rotation for selective coupling with a gear wheel RRwith the internal toothing system reverse rotation for reverse motion and clutch CLD direct connection to selectively clutch carrier CRsystem reverse rotation with the output drive element of the compound planetary mechanism to ensure movement (actuator) in direct naprawa: two-stage planetary transmission to selectively provide drive (movement) in the opposite direction, includes: (i) a sun gear SRsystem reverse rotation, connected with the possibility of transmission of drive force to the output shaft OS; (ii) the set of satellites DP two-stage planetary gear being in mesh with a sun gear SRsystem reverse rotation; (iii) drove CRsystem reverse rotation designed to provide support to rotate for a set of satellites DP two-stage planetary gear and connected with the possibility of transmission of drive force to the output drive element of the compound planetary mechanism, and (iv) a gear wheel RRwith the internal toothing system reverse rotation which engages with a set of satellites DP two-stage planetary gear; brake B1 system reverse rotation for selective coupling with a gear wheel RRwith the internal toothing system reverse rotation for reverse motion and clutch CLD direct connection to selectively clutch carrier CRsystem reverse rotation with the output shaft OS to ensure movement (actuator) in the forward direction (forward).

 

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