Variable-speed gear with shifted axes of rotation

FIELD: transport.

SUBSTANCE: in planetary gear each toothed satellite is rigidly connected with one more additional carrier. On additional carriers, more several tapered not toothed satellites are located which are kinematically interconnected by not toothed wheel. Tapered not toothed satellites can engage and disengage with guides located on gear wheel kinematically connected with outer wheel of planetary gear, satellite gears can roll over guides, the guides can rotate and roll over gear rack with possibility of fixation in specified position. When gear wheels roll over the rack the guides can roll and rotate together with these wheels, shafts of guides are connected by means of holders are connected with disk not toothed wheel located on output shaft, the shaft has rigid connection with wheel which is kinematically connected with outer wheel of planetary gear, disk not toothed wheel can rotate together with wheel which has kinematic connection with outer wheel of planetary gear and shift along rotation axis of shaft on which this wheel is located. The disk not toothed wheel is in contact with not toothed wheels fixed on actuating shaft, not toothed wheels on actuating shaft can roll over surface of disk not toothed wheel and to shift together with this wheel and actuating rod along rotation axis of the mentioned shaft, actuating shaft is connected with driving gear.

EFFECT: smooth variation of gear ratio.

11 dwg

 

The variator with offset axes of rotation along its purpose is similar to traditional gearboxes with both manual and automatic, used as a host vehicle having an internal combustion engine.

Description speed manual gearbox, refer to the technical literature "Mechanic", 2003 edition, the authors Chumachenko Y. T., A. Gerasimenko, I. and Russanov B. B., and automatic transmission in the manual for motorists "automatic gearboxes and transmissions", 2003 edition, the author Kosenkov A. A.

In contrast to conventional transmissions, the CVT will allow you to smoothly change the gear ratio in the transmission of rotation from the motor shaft to the drive wheels of the car.

The variator includes a planetary gear mechanism consisting of a carrier 1, Fig.1, figs.2, is rigidly fixed on the shaft 2 and connected through the shaft 2 with the motor vehicle. On the drive rod 1 is placed teeth satellites 3, kinematically connected to the outer wheel 4 of the planetary mechanism and the Central wheel 5. The 3 satellites are able to rotate around its own axis 6, and together with the planet carrier 1 around axis 7. The outer wheel 4 and the Central wheel 5 mounted on the shaft 2 and can rotate on the shaft 2. In addition, the outer wheel 4 has a kinematic connected to the e with the toothed wheel 8. The axis of rotation 7 of the carrier 1 and the axis of rotation 9 of the wheel 8, kinematically connected to the outer wheel 4 of the planetary mechanism, offset relative to each other. Each toothed satellite 3 is rigidly connected, by means of shaft 10, another planet carrier 11, Fig.1, figs.2, figs.3, Fig.4A). The timing satellites 3 and drove 11 have the opportunity to rotate around the axis 7, together with the planet carrier 1, is rigidly fixed on the shaft 2, and around its own axis 6. On Fadilah 11, rigidly connected with the gear 3 satellites, there are several cone not toothed satellites 12, connected kinematically toothed wheel 13. Cone not the timing satellites 12 can rotate around the axis 6, together with the measured including carriers 11 on which they are located, and around its own axis 14. Not a gear wheel 13 can rotate on the shaft 10, on which it is located. Cone not the timing satellites 12 have the opportunity to come into contact and out of contact with the guides 15, Fig.1, figs.5, arranged on the toothed wheel 8, kinematically connected to the outer wheel 4 of the planetary mechanism. During contact, the cone is not the timing satellites 12 have the opportunity to skate along the guides 15. Guides 15 can rotate together with the gear wheel 8 on which they are located around the axis 9, and roll on the toothed wheel 16 and the gear is th rail 17, can be locked in a predetermined position. The guides 15 are rigidly connected with a toothed wheel 16 and the shaft 18, and rolling gears 16 on the rod 17 can roll and to rotate along with the wheels 16. The shaft 18 of the guides 15, with the help of the holders 19, is connected with the disk not toothed wheel 20 located on the shaft 21. This shaft 21 is connected with the driving wheels of the vehicle and is rigidly connected with the wheel 8, which is kinematically connected to the outer wheel 4 of the planetary mechanism, Fig.1. Disk not toothed wheel 20 can rotate together with the wheel 8, having a kinematic connection to the front wheel 4 of the planetary mechanism, and to move along the axis of rotation 9 of the shaft 21, on which the wheel 20 is located. Disk not toothed wheel 20 is in contact with not the gear wheels 22 mounted on the drive shaft 23, Fig.1, figs.4B). Not gears 22 on the drive shaft 23 are able to roll along the surface of the disk is not a gear-wheel 20, and together with the wheel 20 and drive stem 23 to move along the axis of rotation 9 of the specified shaft 21. The drive rod 23 is connected with a drive mechanism 24.

The principle of operation of the drive mechanism 24, Fig.1, similar to the principle of the solenoid used in an automatic transmission for regulating the fluid pressure in the main line and the control switch is ucheniem transmission.

The design of the drive mechanism 24 of Fig.1 is shown in Fig.6.

Inside of the drive mechanism is movable spool valve 25. Its position is determined by the magnetic field winding 26 that occurs when the flow of current in the winding 26. If through the winding 26 no current flows under the action of the spring 27, the valve 25 is fully shifted to the left. The pressure fluid pumped by the pump through the pipe 28 into the pipe 29, is not transmitted. When the flow of current in the winding 26, the valve 25 is shifted to the right, which leads to fluid pressure in the pipe 29. The larger current passes through the coil 26, the more the valve 25 is shifted, with the help of anchor 30, the right and the greater the pressure of the liquid at the outlet pipe 29.

The fluid from the pipe 29 can move the piston 31 in the cylinder 32. The piston 31 is connected with a drive shaft 23, Fig.6 and Fig.1. Under the action of the piston 31, Fig.6, and the spring 33, Fig.1, the disk is not a gear wheel 20, Fig.1, may be located in a fixed position and to be displaced along the axis 9.

The principle of operation of the variator is as follows.

The rotation from the engine is transmitted to the shaft 2, Fig.1. Together with the shaft 2 rotates carrier 1. The timing satellites 3 roll on the outer wheel 4 of the planetary mechanism and rotate the wheel 5. Simultaneously with this, the cone is not the timing satellites 12 are in contact with the guide rails 15, prokatilas along the guides 15, and out of contact, Fig.5.

Cone not the timing satellites 12 move along the arcs 34. Arc 34 of movement of the satellites 12 coincide with the profile of the guides 15, Fig.5, Fig.7a).

In this position the guides 15 of the rotation wheel 4 and the wheel 8 is not transmitted Fig.1, figs.5, and they remain motionless.

This mode of operation of the variator corresponds to neutral.

This is due to the fact that in the winding 26, Fig.6, the drive mechanism 24, Fig.1, there is no current.

When the flow of current in the winding 26, Fig.6, the valve 25 is shifted to the right. What causes pressure in the pipe 29 and the movement of the piston 31 in the cylinder 32. The piston 31 through the drive shaft 23 and gear 22, Fig.1, shifts to the right disk is not a gear wheel 20. Under the action of the wheel 20 and the holders of guides 19 15 roll on a rack 17 and is taking on a new fixed position. While the profile of the guides 15, Fig.5, at the site of contact with non-toothed conical satellites 12, changes and begins to cross the arc 34 motion not toothed cone satellites 12, Fig.7b). As a result, between satellites 12 and the guide 15 occurs emphasis, which causes the rotation of the wheels 8 and 4, Fig.1, and through the shaft 21, the rotation starts to be transmitted to the drive wheels of the car.

Ceteris paribus, in the traditional planetary mechanism, occurrence of the specified focus would lead to the rotation of the wheel 8 together with the planet carrier 1, and the relative angular velocity of the wheel 8 led 1 is equal to zero.

In progressive transmission, the offset of the axis of rotation 7 of the carrier 1 and the rotational axis 9 of the shaft 21 allows, when creating the above emphasis, to achieve relative rotation of the wheel 8 and walked 1, Fig.1.

As the rotation of the carrier 1 and the gear satellites 3, Fig.1, figs.5, before some not toothed satellites 12 out of contact with the guides 15, other satellites 12 are in contact with the guides 15. Thus, the continuity of the transmission of the rotation.

To change the gear ratio, in the winding 26, Fig.6, increases the strength of the current, which leads to an increase in pressure in the pipe 29 and the displacement of the piston 31. This ultimately causes the rolling of the guides 15 and toothed racks 17, Fig.1. Under the new guides 15, their profile is increasingly began to cross the arc 34 of movement of the satellites 12, Fig.5, Fig.7b).

This leads to an increase of the angle of rotation of the wheel 8 relative to the carrier 1, Fig.1, and thereby a change in gear ratio. The value of the ratio depends on the profile of the guides 15, at the site of contact with resourcetype satellites 12.

As the wheels 4 and 8 have the gearing, the gear ratio between the wheels is stetsa constant. And the change gear ratio is between the planet carrier 1, on the one hand, and the wheels 8 and 4, on the other hand.

The offset of the axis of rotation 7 of the carrier 1 and the rotational axis 9 of the shaft 21, Fig.1, causes, during operation of the variator, a change in the distance 35 and 36, Fig.8, from the contact 37 of the satellite 12 and the guide 15 to the axes of rotation 7 and 9. Therefore, the uniformity of rotation of the moving parts in the variator is achieved by selection of the degree of curvature of the profile of the guides 15.

In Fig.9a) shows a mechanism consisting of a carrier 38, no satellite gear 39 and the wheel 40, in which the removed portion. Carrier 38 rotates around the axis 41 and the wheel 40 is around the axis 42. When the rotation of the carrier 38, 39 rolls on edge 43 of the wheel 40 and rotates the wheel 40 in a clockwise direction. When the position of the carrier 38, indicated in Fig.9a), the distance 44 from the contact 45 satellite 39 and the wheel 40 to the axis of rotation 42 of the wheel 40 is equal to the distance 46 from the contact 45 satellite 39 and the wheel 40 to the axis of rotation 41 of the carrier 38.

As the rotation of the carrier 38 and reaches the position indicated in Fig.9b), the distance 44 and the distance 46 will be different from each other.

That is, as the rotation of the carrier 38, the distance 46 will decrease in relation to the distance of 44. Thus, at a constant angular speed of the carrier 38, the angular velocity of the wheel 40 will decrease.

To align globalscale wheel 40 by changing the slice profile 43 of the wheel 40. For example, to make the angular speed of the carrier 38 and the wheels 40, Fig.10A), are equal, it is necessary to select a specific rotation step and turn this step led 38 and the wheel 40, noting points 47 of the contact areas 45 satellite 39 and wheel 40. When the connection points 47 contact 45 satellite 39 and the wheel 40 will curve 48, corresponding to the slice profile 43 of the wheel 40. The step size of the rotation of the carrier 38 and the wheels 40 may be any of 1, 2, 3, and so on

This way you can achieve any value of gear ratio. For example, if the led 38 to rotate by 2, and the wheel 40 1 and mark the points 47 designated contacts 45 satellite 39 and wheels 40, when the connection points 47 line will curve 48, corresponding to the slice profile 43. Rolling miter 43, with this profile, the satellite 39, gear ratio from the led 38 to the wheel 40 will be equal to 1/2.

To give uniformity to the rotation of the carrier 38 and the wheel 40, as well as the required transmission ratio, it is possible by selection of the curvature of the slice 43 wheel 40, as discussed above, but the distances 44 and 46 will still be changed, which will cause uneven rotation of a satellite 39. To align the angular velocity of the satellite 39 its radius 49, Fig.9a) and b), Fig.10A) and b), at the site of contact 45 with the wheel 40 must also change. This can be achieved, giving the satellite 39 a cone shape, Fig.10B). the Hanks to what line of cut 43 is located at an angle of 55, Fig.10B), to the vertical, the rotation of the carrier 38 causes the displacement of the contact areas 45 satellite 39 and wheel 40 along the axis 50, Fig.10A) and b). This leads to the change of radius 49 satellite 39 in place of the contact 45. For uniform rotation of the satellite 38, change its radius 49 should correspond to the change in the ratio of the distances 44 and 46. If at a constant angular speed of the carrier 38, Fig.10A), satellite 39 rotates with acceleration, to align its angular velocity, radius 49, Fig.10B), with the displacement of the contact 45, is expected to increase.

When rolling guide 15 on the rod 17, the curvature of the profile 51 of the guide 15, in contact with the satellite 12, is changed, Fig.1, figs.7b). This causes a change in the gear ratio. Each value of the curvature of the profile 51, in contact with the satellite 12, corresponds to the determined gear ratio. The guides 15 is determined by the strength of the current supplied to the coil 26, Fig.6, the drive mechanism 24, Fig.1. And the current is supplied to the coil 26, in turn, depends on the frequency of rotation of the wheels of the car.

Not gears 13 are designed to align the angular velocities are not toothed conical wheels 12 are in contact with the guides 15 and wheels 12 out of such contact, Fig.5.

Gear details variator allow is to give the satellites 12 and the guide rails 15, Fig.5, a certain position during their contact, for any value of gear ratio.

The wiring diagram of the CVT with engine and driving wheels of the vehicle shown in Fig.11. Where 52 - variator 2 and 21 - shafts with Fig.1, 53 - engine 54 - the leading wheel of a vehicle.

Together with the variator can be used clutch or hydraulic transformer used in automatic transmissions.

Description hydraulic transformer is provided in the manual for motorists "automatic gearboxes and transmissions", 2003 edition, the author Kosenkov A. A.

The variator with offset axes of rotation is a node in a motor vehicle having an internal combustion engine, characterized in that it includes a planetary gear mechanism consisting of a carrier rigidly mounted on the shaft and connected through this shaft to the motor vehicle, the driver placed the timing satellites, kinematically connected to the outer wheel of the planetary mechanism and the Central wheel, the satellites are able to rotate around its own axis, and together with the planet carrier, the outer wheel and the center wheel is placed on the shaft and can rotate on this shaft, in addition, the outer wheel has a kinematic connection with the toothed wheel, the axis of rotation of the carrier and the axis of rotation of the wheel, kinematics and connected to the external wheel of the planetary mechanism, displaced relative to each other, each gear satellite rigidly connected by a shaft, a planet carrier, gear satellites and drove have the opportunity to rotate around the axis together with the planet carrier rigidly mounted on the shaft and around its own axis at Fadilah, rigidly connected with a toothed satellites, there are several cone not toothed satellites connected kinematically toothed wheel (13), cone not the timing satellites can rotate around the axis together with the measured including carriers on which they are located, and around its own axis, no gear can rotate on the shaft on which it is located, conical, not toothed satellites have the opportunity to come into contact and out of contact with guides arranged on the toothed wheel, kinematically connected with the outer wheel of the planetary mechanism, during contact, cone not the timing satellites have the opportunity to skate along the guides, the guides can rotate together with the gear wheel on which they are located, and to roll on the toothed wheels on a rack which can be locked in a predetermined position, the guides are rigidly connected with the toothed wheel shaft, and rolling gears rail, can roll and to rotate together with these wheels,rollers, with the help of the holders, are connected with the disk, not the drive gear located on the shaft, the shaft connected to driving wheels of the vehicle and is rigidly connected with the wheel, which is kinematically connected to the outer wheel of the planetary mechanism, the disk is not toothed wheel can rotate together with a wheel having a kinematic connection with the external wheel of the planetary mechanism, and to move along the axis of rotation of the shaft on which the wheel is located, the disk is not toothed wheel is in contact with not the gear wheels mounted on the drive shaft, no gears on the drive shaft have the opportunity to roll on the surface of the disk is not gears, and with that wheel and drive stem to move along the axis of rotation of the specified shaft, drive shaft connected to the drive mechanism.



 

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Transmission // 2284925

FIELD: transport engineering.

SUBSTANCE: invention relates to design of planetary transmission which can be used in automatic transmission systems controlled by electronic and hydraulic control units for use in road vehicles. Proposed transmission contains planetary reduction gear, carrier 6 of planetary gear train being output member 4 of transmission. Carrier 9 of second planetary gear train is coupled with crown gear (epicycle) 7 of first planetary gear train. Sun gear 5 of first planetary gear train is coupled with epicycle 10 of second planetary gear train and by brake 16, with transmission case. Sun gear 8 of second planetary gear train is coupled with sun gear 11 of third planetary gear train and by brake 18, with transmission case. Input member 3 is coupled with carrier 12 of third planetary gear train. Epicycle 13 of third planetary gear train is coupled by brake 19 with transmission case. Input member 3 is coupled by clutch 14 with carrier 9 of second planetary gear train. Epicycle 7 is provided with brake 17 for coupling with transmission case. Input member 3 is coupled by clutch 15 with sun gear 5. Input member 3 is coupled also with torsional vibration damper 2. Reduction of overall dimensions of transmission makes it possible to enlarged range of vehicle in which proposed transmission with such kinematic diagram can be used, and dynamic characteristics of vehicle are considerable improved owing to change of design of transmission and change of gear ratios of planetary gear trains and order of in-pair engagement of friction control member.

EFFECT: enlarged kinematic capabilities of transmission, increased service life, reduced mass owing to dispensing with torque converter and reduced number of transmission components.

1 dwg

FIELD: transport engineering.

SUBSTANCE: invention relates to gearbox of automobiles, crawler vehicles, two-member crawlers, crawler chassis of loggers, etc. proposed hydromechanical transmission has input shaft 1 and output shaft 2, four differential mechanisms, each including carrier, planet pinions, sun and epicyclic gears and six friction control members in form of clutches 11, 12 and brakes 7-10. Three differentials, whose sun gears 31, 27, 23 are installed on input shaft 1, form main planetary gear transmission. Epicyclic gears 28, 20 of first and third differentials are connected with carrier 25 of second differential. Carrier 29 of first differential is connected with brake 7 and, through friction clutch 11, with input shaft 1. Carrier 21 of third differential is connected with output shaft 2 through fourth differential used as divider at output.

EFFECT: simplified design, reduced speed of rotation of differential members and friction members, multipurposeness of transmission.

2 dwg

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