Two-mode super variable speed case (its versions)

FIELD: machine building.

SUBSTANCE: invention refers to machine building and can be implemented, for example in transport machine building as continuously variable transmission. The two-mode super variable speed case consists of case (1), base step-less transmission (2), and control mechanism (11) including matching planetary (12) and differential (13) gears; it also consists of output shaft of drive (27) designed to alternate kinematic connection with kinematic links of the control mechanism. Matching planetary gear (12) can be kinematically connected either with carrier (23) or with external central wheel (21) of differential gear (13). Internal central wheel (20) of differential gear (13) can be connected with output kinematic link (9) of base step-less transmission (2). External central wheel (15) of matching planetary gear (12) is connected with input kinematic link (9) of base step-less transmission (2). Internal central wheel (15) of matching planetary gear (12) is connected with fixed case (1). Output shaft of drive (27) can be connected either with external central wheel (21) or with carrier (23) of differential gear (13). The second version differs from the first one like follows: output kinematic link (9) of base step-less transmission (2) is connected to the external central wheel (21) of differential gear (13), while internal central wheel (20) contains singular tooth ring (22). The third version of the drive differs from the first two like follows: output kinematic link (9) of base step-less transmission (2) can be telescopic jointed to fixture (3 8) by means of splines (40); the fixture bears tooth ring (41) of internal mesh.

EFFECT: invention transmits torque with reduced revolution frequency from input kinematic link of step-less transmission to output link of drive which simplifies drive, increases its efficiency and eliminates high intermediate frequencies of control mechanism rotation.

9 cl, 6 dwg

 

The invention relates to mechanical engineering and can be used both in General and in the transport industry, in particular as a continuously variable transmission cars and other vehicles.

The prior art discussed below dual mode continuously variable drives, also called supervarieties taken counterparts.

Known stepless actuator on the basis of the variator, hereinafter called the base, mostly symmetrical ratio - V-belt or toroidal, allowing you to use to extend the range of variation of gear ratio drive two modes of regulation of the ratio of the base variable. One mode, for example, reducing the gear ratio of the underlying variable, is used directly, and the second increases it is used with the circulation of power in the closed mode with the differential bevel gear, transforming the increase ratio of the underlying variable in further reduction gear ratio of the entire drive. Thus, the range of variation of gear ratio of the drive significantly expanded compared with the range of variation of gear ratio of the underlying variable (see Pronin, B.A., the Roar of the GA s "Progressive", M, engineering, 1980, s, RES-185). This device is similar to the inherent disadvantages lies in the fact that the underlying variable is not a planetary scheme is symmetric on the transmission ratio, the drive contains a large number of auxiliary programs, including differential bevel gear transmission, which makes it difficult to drive and significantly reduces its efficiency.

Known dual mode continuously variable actuator, comprising a housing in which a reference variable, for example, planetary disk, with the input and output of the kinematic links, the control mechanism is kinematically associated with the variator and including termination of planetary and differential gear and the output kinematic chain drive, and the output of the kinematic link drive is made with the possibility of alternate kinematic connection with the kinematic parts of the steering mechanism (see PCT/EN 03/00298, 2003, "Wide-range continuously variable drive (superwriter), publication WO 2005/003596 from 13.01.05, author - Gulia, NV). The last technical solution adopted for the prototype, because it has the maximum sum total with the invention of the signs.

A disadvantage of the known actuator, taken as a prototype, is the high speed output of the kinematic link, to the which, in most cases, then, should decrease when the transfer to the operating Agency (e.g., wheels). It causes unnecessary power loss during transmission to the working body and the complexity of the drive. Moreover, in the operation mode, only the basic variable because of the presence of increasing impedance of the transmission decreases the efficiency of the drive.

The objective of the invention was to create a drive, allowing torque to be transmitted in the mode frequency reduction rotation from the input kinematic link base variable-speed drive to the output element of the actuator, which simplifies the drive, increases the efficiency of the underlying variable and avoids high intermediate frequencies of rotation of the elements of the steering mechanism and associated problems (vibrations etc).

This task is solved in that offered the option of performing dual mode continuously variable drive (superwriter), comprising a housing in which a reference variable with the input and output of the kinematic links, the control mechanism is kinematically associated with the base variable-speed drive and including termination of planetary and differential gear and the output kinematic chain drive, and the output of the kinematic link drive is made with the possibility of alternate kinematic connection with the kinematic parts of the control mechanism is a, in which, according to the invention, matching the planetary gear is configured to alternate kinematic connection with its carrier or planet carrier of the differential gear, or with the outer Central wheel differential gear, and an inner Central wheel differential transmission is arranged to connect the output of the kinematic link base variable-speed drive, with the outer Central wheel matching the planetary gear is connected to the input of the kinematic link base variable-speed drive, and an inner Central wheel matching the planetary transmission is connected with the stationary housing and the output shaft is made with alternating kinematic connection with the outer Central wheel differential transmission when connecting drove matching planetary gear with the planet carrier of the differential gear, or with the planet carrier of the differential transmission when connecting drove matching planetary gear set with the outer Central wheel differential gear.

To solve this problem is proposed second embodiment of a dual mode continuously variable drive (superwriter), comprising a housing in which a reference variable with the input and output of the kinematic chains, shafts, managing fur the lowland, kinematically associated with the base variable-speed drive and including termination of planetary and differential gear and the output drive shaft and the output shaft is made with alternating kinematic connection with the kinematic parts of the steering mechanism, in which, according to the invention, matching the planetary gear is configured to alternate kinematic connection with its carrier or planet carrier of the differential gear, or with the inner Central wheel of the differential gear, and the outer Central wheel differential transmission is arranged to connect the output of the kinematic link base variable-speed drive, with the outer Central wheel matching transmission is connected to the input of the kinematic link base variable-speed drive, and the internal Central matching wheel of the planetary transmission is connected with the stationary housing and the output shaft is made with alternating kinematic connection with the inner Central wheel differential transmission when connecting drove matching planetary gear set with the planet carrier of the differential gear, or with the planet carrier of the differential transmission when connecting drove matching planetary gear set with the inner Central wheel trim is anchialine transfer.

To solve the stated problem, a third embodiment of a dual mode continuously variable drive (superwriter), comprising a housing in which a reference variable with the input and output of the kinematic chains, shafts, steering mechanism kinematically associated with the base variable-speed drive and including termination of planetary and differential gear and the output drive shaft and the output shaft is made with alternating kinematic connection with the kinematic parts of the steering mechanism, in which, according to the invention, matching the planetary gear is configured to alternate kinematic connection with its carrier or planet carrier of the differential gear, or with the inner Central wheel differential transmission and the output of the kinematic link base variable-speed drive is configured to alternately connect it with both external and internal Central wheel differential gear, and the outer Central wheel matching the planetary gear is connected to the input of the kinematic link base variable-speed drive, and an inner Central wheel matching the planetary transmission is connected with the stationary housing, whereby the output shaft is made with operatingactivities connection with the outer Central wheel differential transmission when connecting drove matching planetary gear set with the planet carrier of the differential gear, or planet carrier of the differential transmission when connecting drove matching planetary gear set with the inner Central wheel of the differential gear.

Honours drive three versions of the complete drive is that the kinematic connection of the links made in the form of coupling sleeves.

Another difference of the drive is that the matching of the planetary transmission is performed with a decreasing from the input shaft to the cage gear ratio.

Among the differences should be noted that the actuator is equipped with sensors that measure the rotational speed, one of which is mounted on the inlet, and the other on the output of the kinematic links of the base of the variator, and the sensors connected to the block comparison engine speeds, which outputs a signal on the kinematic connection of the links of the drive when aligning their speeds.

Another distinctive feature of the proposed drive is that of matching the transmission is made in the form of a planetary transmission having a fixed inner Central wheel.

Among the differences should be noted that the underlying variable is made in the form of a friction disk of planetary variator with the inner and outer Central friction discs and friction satellites and provided with a drive which move the friction of the satellites relative to the inner is x and the outer Central friction discs of the variator.

Another distinctive feature of the proposed actuator is that the actuator introduced additional transmission connecting the output of the kinematic link steering mechanism with the output of the kinematic link actuator, and the output of the kinematic link actuator is configured to output rotation in both directions from the additional transfer.

Thanks to the above features run drive in three versions it provides the technical result consists in the fact that the proposed drive allows torque to be transmitted in the mode frequency reduction rotation from the input of the kinematic chain variable to the output element of the actuator, which simplifies the drive, it increases efficiency and avoids high intermediate frequencies of rotation of the elements of the steering mechanism and associated problems (vibrations etc).

The invention is illustrated by drawings. Figure 1 shows the kinematic diagram of the continuously variable drive (superwriter) in the first version of its execution mode reduction. Figure 2 shows a diagram of the drive mode animation. In fig.z presents the kinematic scheme of the second version of the drive mode reduction, and figure 4 - scheme of the same versions of the drive-mode multiplier, figure 5 presents a diagram of a third variant of rivada mode reduction and figure 6 - diagram of this version of drive mode animation.

The proposed actuator (1) includes a housing 1 in which is placed the base of the variator 2 (highlighted on the drawings dashed line), including kinematic link 3 basic variable, which serves as the input link of the drive and made in the form of a shaft passing through the drive with the ability to connect to it from both sides of the body 1, the inner 4 and outer 5 Central friction discs between which are located intermediate the conical friction discs satellites 6, and the pressure on the inner Central friction discs 4 is a spring 7, for example, Poppet. Satellites 6 is fixed rotatably on the pivot levers 8, which was planted with the possibility of rotation on the output of the kinematic link 9 of the base of the variator 2, which is the carrier of the underlying variable. The base of the variator 2 is provided with actuator 10, for example, a stepping motor, is fixed to the output kinematic link 9 of the base of the variator 2 and carries out the movement of satellites 6 relative to the inner 4 and outer 5 Central friction discs of the base of the variator 2. The actuator is provided with a control mechanism 11 (highlighted on the drawings dashed line), kinematically connected with the base variator 2 and including the SOG is yuushuu planetary gear 12 and the differential gear 13 (marked on the drawings dashed line). It should be noted that any Pets execution matching planetary and differential gear. In this case, these transmissions are gear.

The input kinematic link 3 basic variator is connected to the outer Central gear wheel 14 matching planetary gear set 12, the inner Central gear wheel 15 which is connected with the fixed element, in this case the housing 1. Drove 16 matching transmission are connected by a telescopic connection, for example, spline 17, with the sleeve 18, the carrier gear 19 internal gear. The output of the kinematic link 9 of the base of the variator 2 is connected to the inner Central wheel 20 of the differential transmission 13 and the outer Central gear wheel 21 includes ring gear 22 of the external gear, in this case divided into two parts, located on its right and left edges. Drove 23 differential transmission 13 includes two of the ring gear and the external gear 24 and 25, and the crown 24 may engage with the internal crown gear 26, kinematically connected with the output shaft 27 of the drive. Gear 25 external gearing may engage with the crown 19 of the internal gear and the crown 19 may also be coupled with a wreath 22 (right part). Thus, the crown 19 together with rims 22 and 25, as well as Inez 26 with rims 22 and 24 form, accordingly, the toothed clutch. The sleeve 28 on the inner side carries fixed thereto with a possibility of free rotation of the sleeve 18, and limited in axial movement along the sleeve 28 stops 29. The sleeve 28 has a possibility of axial movement relative to the housing 1, for example, by a plug 30, driven, for example, from the electromagnet 31, and the sleeve 28 moves in the axial direction and the sleeve 18 with the stops 29. Sleeve 28 telescopically, for example, with slots 32, is connected with the output shaft 27 of the entire drive (superwriter), which may go in one right and the other left side of the housing 1, by using, for example, the gear reducer 33. The input element 3 may also extend outward in both directions - left and right - from the housing 1. The drive - switching clutch - can be carried out both manually and by using sensors 34 frequency of rotation of the link 3, the sensors 35 frequency of rotation of the link 9 and the Comparer 36, electrically connected with the sensors 34 and 35, and an electromagnet 31, switch gear clutch. In this position of the differential mechanism 13 when the rotation frequency of all its parts - wheels 20, 21 and led 23 is identical and equal to the frequency of rotation of the pinion carrier 16 of the matching transmission 12, the gear ratio which is equal to the real education is CA transmission of 1.25. Figure 1 presents the scheme of superwriter mode reduction when increasing the gear ratio of the variator 2 is increased and the gear ratio of the entire drive - superwriter, i.e. with decreasing frequency of rotation of the output of the kinematic link 9 of the variator 2 is reduced, the frequency of rotation of the shaft 27.

For simplicity, the illustrations do not show the mechanism of the reverse conducting reverse drive as not directly relevant to the principle of operation of the actuator, which may be performed by any known method, and is placed, for example, in the reduction gear 33.

Figure 2 shows a diagram of the same variant of superwriter, as in figure 1, only in the mode of the animation, i.e. when the variator 2 increases its transmission ratio, and superwriter ratio decreases, then the output shaft 27 begins to increase its speed when turning down the speed of the output element 9 of the variator 2.

Work superwriter according to the first embodiment is as follows. If we consider the operation of the actuator (superwriter) when the speed increases, its output link 27 from minimum to maximum at a constant rotational speed of the input element 3, the first should be the mode of reduction. While parts of the control mechanism 11 is connected by the clutch as the show is, but figure 1. The output link 9 of the base of the variator 2 is connected with the Central inner wheel 20, the wheel 21, which carries sprockets 22, is connected with the planet carrier 16 of the matching transmission 12 by engagement of the rims 22 of the crown 19 of the sleeve 18, the associated slot 17 with the planet carrier 16 of the matching of the planetary gear 12 and moved together with the sleeve 28 with the stops 29. The inner Central wheel 15 matching transmission 12 is still connected to the housing 1 and the outer 14 with the input link 3. Drove 23 differential transmission 13 is connected with the rims 24 and 26 with the output shaft 27 of the actuator (superwriter) through the sleeve 28, the slots 32 and the gear 33. The sleeve 28 is in the left end position, moved with a fork 30 manually or by servo - solenoid 31. The output link of the actuator 27 in this case, i.e. when superwriter mode reduction, increases the frequency of rotation substantially in a smaller range than the output link 9 of the variator 2. For example, for a real design, the range of variation of the base of the variator 2, included in superwriter, about 6, and the range of variation of the rotational speed of the output element 27 superwriter when running on 1 of about 1.4. However, the basic efficiency of the variator 2 is changed from 0.7 to 0.94, and superwriter remains approximately constant and equal 0,94-0,96 during execution of figure 1, i.e. the mode is eductio. Through the base of the variator 2 is only from 20 to 60% of full capacity, which allows it to compact.

When the reduction gear ratio of the underlying variable by moving satellites 6 to the center of the actuator 10 and the achievement of the output element 9 of the base variable-speed drive maximum speed and gear ratio, respectively, the minimum value, which is reflected, for example, the sensors 34 and 35 through the block comparison 36, the plug 30 manually or by servo - solenoid 31 is electrically connected with the Comparer 36 - switches, moving the sleeve 28 to the right, and without breaking the flow of power to keep the current speed of all parts of the drive, superwriter switches to the mode of the animation (see figure 2). While the outer Central wheel 21 of the differential transmission 13 is connected by edges 22 and 26 with the output element 27 superwriter through the reduction gear 33 and the slots 32 on the sleeve 28, and drove 23 differential transmission 13 with rims 25 and 19 in the sleeve 18 is connected with the planet carrier 16 of the matching transmission 12. Now the gear ratio of the base variable-speed drive 2 drive 10 is changed from the minimum to the maximum value, the rotational speed of the output element 9 of the base of the variator is changed from the maximum to the minimum value in this particular execution of the range of variation of about 6, i.e. the frequency of rotation of the link 9 is reduced in 6 times, and the output link 27 superwriter increases the frequency of its rotation in 1.5 times in the execution of figure 2. Efficiency superwriter this changes approximately from 0.93 to 0.97 in the execution of figure 2, and through the underlying variable goes from 50 to 5% power. Thus, superwriter is a mechanical variator with a fairly narrow range of variation, but with high efficiency. When performing in figure 1 and figure 2, the range of variation is very narrow (about 2.1) and requires additional steps in the transmission, however, the efficiency is extremely high for a variable.

Increasing the gear ratio of the drive (superwriter) is in the reverse order.

It should be noted that the continuity of power flow in the drive (supervarieties) when switching from mode to the reduction mode animation and back is achieved in that the toothed clutch formed by the toothed rims 19 and 22-25 and rims 26 and 22-24, switch without releasing from the previous communication, remaining certain period of time included in two positions. The same speed all the included links allows you to do it. For example, the crown 19, passing from engagement with the crown 22 on the crown 25, some time, at least a fraction of a second, is in engagement with the crown 22 and the crown 25. The same self which occurs at the transition of the crown 26 of the crown 22 to the crown 24 and back. The ratio of the width of the rims 19 and 26 with the gaps between the crowns 22 and 25, and 22 and 24 allows you to do this.

Shown in figure 3 and 4 a second embodiment of the actuator is different from the above because it has a wider range of variation ratio of superwriter - up to 5 at a somewhat reduced with respect to the first embodiment efficiency - from 0.9 to 0.95 in the mode of reduction and 0, 85 to 0.95 in the mode of animation. However, compared to the base variator 2 efficiency superwriter in the second option above. Structurally, the second embodiment of superwriter different from the first so that the output of the kinematic link 9 of the base of the variator 2 is connected with the outer Central wheel 21 of the differential transmission 13 and the inner Central gear wheel 20 has gear 22, which, unlike the first version, made in the singular.

Work superwriter according to the second variant differs from the first variant the fact that the mode of reduction (fig.z) output level 9 base variator is connected to the Central outer wheel 21, and the wheel 20, which bears the crown gear 22 with external toothing, is connected with the planet carrier 16 of the matching transmission 12 by the engagement of the crown 22 and the crown 19 of the sleeve 18, the associated slot 17 with the planet carrier 16, and moves together with the sleeve 28 with the stops 29, VI is some 30 and the electromagnet 31.

Work superwriter according to the second variant differs from the first variant that mode multiplier (figure 4) inner Central wheel 20 of the differential transmission 13 is connected by edges 22 and 26 with the output element 27 superwriter, and drove 23 differential transmission 13 with rims 25 and 19 in the sleeve 18 is connected with the planet carrier 16 of the matching transmission 12.

Now, when the change gear ratio of the base of the variator 2 from a minimum of 1.3 to a maximum of 8 values, in particular the execution of superwriter according to the second variant, in the mode of multiplication ratio of superwriter vary from a maximum of 1.3 to a minimum of 0.53. Mode superwriter on the second version when the change gear ratio of the variator 2 from 8 to 1.3 ratio of superwriter varies from 2.6 to 1.3. The total range of change of the gear ratio of superwriter the second option is approximately equal to 5, which makes possible its use as a continuously variable transmission for a number of vehicles without additional steps in the transmission.

When superwriter the second option in the mode of reduction through the base of the variator 2 flows up to 70% of the total power flow, while at his work in the mode of animation through the base of the variator 2 flows up to 140% rated the STI, especially in the regime of minimum ratios of the base of the variator 2. This requires strengthening the overall mass of the indicators mentioned basic variator 2 compared to the first option.

Depicted in figure 5 and 6 a third embodiment of the actuator is different from the first two in that it has high efficiency as in the first embodiment, at a somewhat larger range of variation ratio of superwriter compared with the first option - about 3.5 with the same parameters matching 12 and differential 13 transmission, as in the first two variants. This range is slightly lower than in the second option, but it is important that through the underlying variable 2 in both modes as the reduction and animation - is not more than 60... 70% of total capacity (it is almost twice less than in the second embodiment, in the mode of animation)that allows it to be as compact as in the first embodiment. Structurally, the third embodiment of superwriter differs from the first two so that the output of the kinematic link 9 of the base of the variator 2 is made with the possibility of a telescopic connection, for example, with slots 40 with the yoke 38, bearing on himself crown gear 41 internal gearing connecting mode reduction (figure 5) with a ring gear 22 on the outer Central gear wheel 21 differential the territorial transfer 13. Thus, in the mode of reduction of the wheel 21 is connected with the output of the kinematic link 9 of the base of the variator 2, as was done in the second variant of superwriter. Mode multiplier (6) the output of the kinematic link 9 of the base of the variator 2 with slots 40, the crown 41 on the shroud 38 and the left crown 37 on the wheel 20 is connected to the inner Central gear wheel 20 of the differential transmission 13 as it was in the first version of superwriter. Axial movement of the shroud 38 by using the stop 39 on the yoke 28, telescopically connected with slots 32 with the output shaft 27 of the entire drive. The axial displacement of the cage 28 is the same as in the first two variants of superwriter. Using the stop 29 on the clip 28 from its axial movement is provided ferrule 18 with ring 19 made with the possibility of a connection mode of reduction with the right crown wheel 37 20 (figure 5), and animation - crown drove 25 23 differential transmission 13. The crown 26 to the holder 28 in the mode of reduction is connected with the crown 25 of the carrier 23 of the differential transmission 13, and animation - crown 22 on the outer Central gear wheel 21 of the differential transmission 13, connecting the wheel with the output shaft 27. The connection of the crown 19 of the yoke 18 with ring 25 on the carrier 23, and with the right crown 37 on the inner Central is ovcata wheel 20 is made in the same way, as in the second embodiment of superwriter, with the difference that the crown wheel 20 was in a single copy and designated by the numeral 22, and in the third variant of these two crowns - right and left, and indicated they already figure 37.

Work superwriter by the third variant execution is characterized by the fact that the mode of reduction, when the gear ratio of the base of the variator 2 is maximal and equal to the considered real sample of about eight, the output link 9 of the base of the variator 2 is connected by moving the clip 28 figure 5 right at the fork 30 and the electromagnet 31, and slave it with the stop 29 of the shroud 38 associated slot 40 with the link 9 and the bearing on himself the crown 41, crown 22 on the outer Central gear wheel 21 of the differential transmission 13. This same movement of the clip 28 with the stop 29 drove 16 matching transmission 12 is connected by means of the crown 19 and a gear ring 37 with the inner Central wheel 20 of the differential transmission 13. The output shaft 27 superwriter while connected through the rims 26 and 25 with the planet carrier 23 of the differential transmission 13. The ratio superwriter about 2.9 and with the change gear ratio of the base of the variator 2 using the actuator 10 to 1.25 changes to 1.25. Efficiency and range of the change gear ratio of superwriter while RA what are the corresponding values for the second variant of the actuator, when the output level 9 base of the variator 2 is connected to an external Central gear wheel of the differential transmission 13.

For transition superwriter by the third variant of execution mode of the animation of the yoke 28, and all connected with her cage and crowns with a fork 30 and the electromagnet 31 is moved on the circuit 6 to the left. The output link 9 of the base of the variator 2 is connected with the crown 37 with the inner Central gear wheel 20 of the differential transmission 13 as in the first embodiment of superwriter. All provisions of connected links of the drive is presented on Fig.6, and they are similar to the first option run superwriter. Efficiency and range of variation of superwriter also equal to the corresponding values for the first variant implementation of superwriter.

In the third embodiment of superwriter at the greatest possible efficiency for all cases is the range of variation greater than the first option, with the share of power flowing through the base of the variator 2 not exceeding appropriate in the first embodiment, and less than the second version. So many assignments superwriter, for example, for a hybrid powertrain vehicles, this third is the best option.

Supervarieties as in the first embodiment, the second and third Avenue is switching modes do not cause rupture of the power flow and do not cause any change in speed or acceleration of the vehicle.

The most rational use of the described invention is a continuously variable transmission vehicles, especially buses and trucks, transmission mechanical and electro-mechanical hybrid powertrain city buses, as well as the powerful drives of a variety of machines, General purpose conveyors, crushers, mixing machines, winding devices, drilling machines and other machines and devices that require a stepless drive.

1. Dual mode continuously variable drive superwriter, comprising a housing in which a reference variable with the input and output of the kinematic chains, shafts, steering mechanism kinematically associated with the base variable-speed drive and including termination of planetary and differential gear, and an output drive shaft and the output shaft is made with alternating kinematic connection with the kinematic parts of the steering mechanism, wherein matching the planetary gear is configured to alternate kinematic connection with its carrier or planet carrier of the differential gear, or with the outer Central wheel differential gear, and an inner Central wheel differential transmission is made with the possibility of connection his weekends with kinetic is eticheskim link base variable-speed drive, while the outer Central wheel matching the planetary gear is connected to the input of the kinematic link base variable-speed drive, and an inner Central wheel matching the planetary transmission is connected with the stationary housing and the output shaft is made with alternating kinematic connection with the outer Central wheel differential transmission when connecting drove matching planetary gear set with the planet carrier of the differential gear, or with the planet carrier of the differential transmission when connecting drove matching planetary gear set with the outer Central wheel differential gear.

2. Dual mode continuously variable drive superwriter, comprising a housing in which a reference variable with the input and output of the kinematic chains, shafts, steering mechanism kinematically associated with the base variable-speed drive and including termination of planetary and differential gear, and an output drive shaft and the output shaft is made with alternating kinematic connection with the kinematic parts of the steering mechanism, wherein matching the planetary gear is configured to alternate kinematic connection with its carrier or planet carrier of the differential transmission, or in the morning Central wheel differential gear, and the outer Central wheel differential transmission is arranged to connect the output of the kinematic link base variable-speed drive, with the outer Central wheel matching the planetary gear is connected to the input of the kinematic link base variable-speed drive, and an inner Central wheel matching the planetary transmission is connected with the stationary housing, whereby the output shaft is made with alternating kinematic connection with the inner Central wheel differential transmission when connecting drove matching planetary gear set with the planet carrier of the differential gear, or with the planet carrier of the differential transmission when connecting drove matching planetary gear set with the inner Central wheel of the differential gear.

3. Dual mode continuously variable drive superwriter, comprising a housing in which a reference variable with the input and output of the kinematic chains, shafts, steering mechanism kinematically associated with the base variable-speed drive and including termination of planetary and differential gear and the output drive shaft and the output shaft is made with alternating kinematic connection with the kinematic parts of the steering mechanism, wherein the SOG is Asuma planetary gear is configured to alternate kinematic connection with its carrier or planet carrier of the differential gear, or with the inner Central wheel of the differential gear, and the output of the kinematic link base variable-speed drive is configured to alternately connect it with both external and internal Central wheel differential gear, and the outer Central wheel matching the planetary gear is connected to the input of the kinematic link base variable-speed drive, and an inner Central wheel matching the planetary transmission is connected with the stationary housing, whereby the output shaft is made with alternating kinematic connection with the outer Central wheel differential transmission when connecting drove matching planetary gear set with the planet carrier of the differential gear, or with the planet carrier of the differential transmission when connecting drove matching planetary gear with the inner Central wheel of the differential gear.

4. The actuator according to claim 3, characterized in that the kinematic connection of the links of the drive is made in the form of a coupling sleeve.

5. The actuator according to claim 3, characterized in that the matching of the planetary transmission is performed with a decreasing from the input shaft to the cage gear ratio.

6. The actuator according to claim 3, characterized in that the actuator is equipped with sensors that measure the rotational speed, one of which is mounted on the inlet, and the other is th at the output of the kinematic links of the base variable-speed drive, moreover, the sensors are connected to the block comparison engine speeds, which outputs a signal on the kinematic connection of the links of the drive when aligning their speeds.

7. The actuator according to claim 3, characterized in that the matching of the planetary transmission is performed with a fixed inner Central gear wheel.

8. The actuator according to claim 3, characterized in that the base variable is made in the form of a friction disk of planetary variator with the inner and outer Central friction discs and friction satellites, and provided with an actuator engaged radial movement of the friction of the satellites relative to the inner and outer Central friction discs of the underlying variable.

9. The actuator according to claim 3, characterized in that it introduced additional transmission connecting the output of the kinematic link steering mechanism with the output drive shaft and the output shaft of the actuator is configured to output rotation in both directions from the additional transfer.



 

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21 cl, 18 dwg, 3 tbl

FIELD: mechanical engineering, automobile construction, in particular, rotational speed changing technique.

SUBSTANCE: variator has speed regulating mechanism made in the form of toothed differential mechanism, drive for speed regulation mechanism, planetary working frame 4 and planetary balancing frame 5, frame guide 11 and frame rotation casing 12. Frames 4, 5 are meshed with central toothed gear 3 and are placed, in conjunction with said gear, within frame guide 11. Two planetary working toothed gears 6, 10 are fixed within frame 4. Planetary working toothed gear 6 is fixed through cardan drive 8 and shaft 9 to variator housing 7 to rotate relative to frame 4. Planetary toothed gear 10 is connected through second cardan drive 8, intermediate toothed gears 21, 22 and toothed gear 23 to variator driven shaft 24 to run around first planetary working toothed gear 6. On increase of rotational speed or adjustment, frames 4, 5 are offset by centrifugal force relative to rotational center of drive shaft 1. On offsetting of frames, radii of rotation of planetary working gears 6, 10 relative to rotational center of drive shaft 1 are increased and transmission ratio is changed.

EFFECT: increased efficiency and provision for transmission of great powers by toothed transmission.

12 dwg

FIELD: mechanical engineering.

SUBSTANCE: continuously variable transmission comprises housing, input and output shafts, reverse mechanism and multi-disk planet variator provided with planet reduction gear, which define a variator. The solar pinion of the reduction gear is fit on the output shaft with interference and its epicycle is secured to the housing of the transmission. The variator has epicycle mounted in the housing of the transmission and made of a stack of disks and solar pinion made of a disk stack mounted on the output shaft of the variator connected with the output shaft of the reverse mechanism. The carrier of the variator is connected with the carrier of the planet reduction gear and consists of two disks interconnected by means of tension bolts. The disks of the carrier have shaped slots the number of which is equal to the number of axles mounted in the shaped slots for permitting change of position and interaction with the disks of the solar pinion and epicycle. The gear ration controller is build in the carrier of the variator. The planet reduction gear, planet multi-disk variator, and reverse mechanism are axially aligned.

EFFECT: prolonged service life and expanded functional capabilities.

18 cl, 8 dwg

FIELD: mechanical engineering, particularly continuous transmissions used as wide-range transmission mechanism.

SUBSTANCE: device for power transmission with variable velocity ratio comprises input 21 and output 27 members, leading draft member 7 and disc member 1 rotationally installed in case. Input member 21 transmits rotational moment of at least one leading draft member 7. Disc member 1 is coaxial to rotary shaft 2 brought into drive connection with at least one leading draft member 7 and is formed as driven member. Disc member 1 may be selectively moved in axial direction along rotary shaft 2 to change position of disc member 1 relative at least one leading draft member 7 to selectively change draft velocity ratio between leading draft member 7 and disc member 1. Output member 27 is displaced by rotary shaft 2 and is selectively brought into engagement with it to transmit rotational moment under determined velocity ratio relative input member 21.

EFFECT: extended velocity range.

27 cl, 4 dwg

Transformer torque // 2188973

The invention relates to the field of engineering

FIELD: mechanical engineering, particularly continuous transmissions used as wide-range transmission mechanism.

SUBSTANCE: device for power transmission with variable velocity ratio comprises input 21 and output 27 members, leading draft member 7 and disc member 1 rotationally installed in case. Input member 21 transmits rotational moment of at least one leading draft member 7. Disc member 1 is coaxial to rotary shaft 2 brought into drive connection with at least one leading draft member 7 and is formed as driven member. Disc member 1 may be selectively moved in axial direction along rotary shaft 2 to change position of disc member 1 relative at least one leading draft member 7 to selectively change draft velocity ratio between leading draft member 7 and disc member 1. Output member 27 is displaced by rotary shaft 2 and is selectively brought into engagement with it to transmit rotational moment under determined velocity ratio relative input member 21.

EFFECT: extended velocity range.

27 cl, 4 dwg

FIELD: mechanical engineering.

SUBSTANCE: continuously variable transmission comprises housing, input and output shafts, reverse mechanism and multi-disk planet variator provided with planet reduction gear, which define a variator. The solar pinion of the reduction gear is fit on the output shaft with interference and its epicycle is secured to the housing of the transmission. The variator has epicycle mounted in the housing of the transmission and made of a stack of disks and solar pinion made of a disk stack mounted on the output shaft of the variator connected with the output shaft of the reverse mechanism. The carrier of the variator is connected with the carrier of the planet reduction gear and consists of two disks interconnected by means of tension bolts. The disks of the carrier have shaped slots the number of which is equal to the number of axles mounted in the shaped slots for permitting change of position and interaction with the disks of the solar pinion and epicycle. The gear ration controller is build in the carrier of the variator. The planet reduction gear, planet multi-disk variator, and reverse mechanism are axially aligned.

EFFECT: prolonged service life and expanded functional capabilities.

18 cl, 8 dwg

FIELD: mechanical engineering, automobile construction, in particular, rotational speed changing technique.

SUBSTANCE: variator has speed regulating mechanism made in the form of toothed differential mechanism, drive for speed regulation mechanism, planetary working frame 4 and planetary balancing frame 5, frame guide 11 and frame rotation casing 12. Frames 4, 5 are meshed with central toothed gear 3 and are placed, in conjunction with said gear, within frame guide 11. Two planetary working toothed gears 6, 10 are fixed within frame 4. Planetary working toothed gear 6 is fixed through cardan drive 8 and shaft 9 to variator housing 7 to rotate relative to frame 4. Planetary toothed gear 10 is connected through second cardan drive 8, intermediate toothed gears 21, 22 and toothed gear 23 to variator driven shaft 24 to run around first planetary working toothed gear 6. On increase of rotational speed or adjustment, frames 4, 5 are offset by centrifugal force relative to rotational center of drive shaft 1. On offsetting of frames, radii of rotation of planetary working gears 6, 10 relative to rotational center of drive shaft 1 are increased and transmission ratio is changed.

EFFECT: increased efficiency and provision for transmission of great powers by toothed transmission.

12 dwg

FIELD: machine engineering, namely stable-speed drives of subsidiary aggregates.

SUBSTANCE: drive includes planetary ball gearing 1000 with gradual variation of gear ratio; step motor, worm gearing. Planetary ball gearing includes planetary members having rolling contact with inner and outer raceways and it may gradually vary gear ratio in range 0.3 - 1.0. Inlet shaft of said gearing is joined with primary propeller such as crankshaft of transport vehicle engine through driving belt B1. Gearing includes at least one outlet shaft coaxial to inlet shaft. Processor analyzes revolution number of crankshaft and respectively varies gear ratio with use of step motor joined with worm gearing for keeping stable revolution number at outlet regardless of revolution number of crankshaft.

EFFECT: possibility for keeping stable revolution number of gearing regardless of revolution number of crankshaft of primary propeller.

21 cl, 18 dwg, 3 tbl

FIELD: machine building.

SUBSTANCE: invention refers to the sphere of machine building and may be utilised for design of transmission gears of tractive, transportation and other machinery as well as machine tool drives and other mechanisms to provide for smooth regulation of speed, speed reversal and brakeage of their actuator devices, the device described being capable of functioning as a master clutch, a gearbox, a reduction gear, a reverse box, a steering clutch or a brake. With the proposed planetary variator the central wheels (1, 2) are represented by hollow cone frusta whose outer and inner surfaces simultaneously contact the satellites (3) via a tooth-and-plate or toothed and tooth-and-plate gearing.

EFFECT: variator load capacity increase.

2 cl, 4 dwg

FIELD: machine building.

SUBSTANCE: automatic continuously variable gear box contains planetary friction variator and mechanism of variation of gear ratio and pressure made in form of pivot arm (17) with pushers (23) installed so as to travel in guiding cuts (24) of disk (25) connected to low speed driven shaft (26). Guiding cuts (24) are made in form of two notches in disk (25) and have the form of spiral segments situated on both sides of their maximum radius of distance from the variator axis. Notches converge in the point of their maximum radius of distance from the variator axis.

EFFECT: invention facilitates reversed rotating of output low-speed shaft and also maintains automatism and reliability of operation of gear.

4 cl, 3 dwg

FIELD: machine building.

SUBSTANCE: disk planetary variator contains body (10) wherein planetary row is installed; said planetary row includes central exterior (9) and interior (6) friction disks from both ends enveloping intermediate friction disks (7), secured of axes (20), designed to travel in carrier (25) and pressed to intermediate disks (7) with hold-down devices. Rolling races on the central friction disks contacting with the surface of intermediate disks (7) are made convex toroidal. Contact zones of resilient members (8) of axial action with circular stops (3) are situated on their peripheral circular part. Circular stops (3) are designed to travel in axial direction in body (10). In the variator there is facilitated optimal pressing of friction disks one to another, also there are avoided edge contacts at disks warps and there is reduced wear of contact zones of friction disks with one another and with circular stops.

EFFECT: invention increases efficiency and service life of variator.

8 cl, 7 dwg

FIELD: transport.

SUBSTANCE: invention relates to machine building and can be sued in automotive stepless transmissions. Proposed variator comprises inner (1) and outer (2) central friction disks coupled with drive shaft (13) and planetary mechanism annular ring (8), comprising satellite gears (6) fitted on axles (17) in pinion frame (18) articulated with variator output shaft (19). Disks (1) and (2) are coupled with shaft (13) and annular ring (8) via rolling bearings (14) fitted in inclined grooves (15) and (16) made in disks-stops (11) and (12) fitted on shaft (13) and annular ring (8), as well as in adjoining inner (1) and outer (2) central friction disks.

EFFECT: higher efficiency in wide range of torques.

8 cl, 14 dwg

FIELD: machine building.

SUBSTANCE: invention refers to machine building and can be implemented, for example in transport machine building as continuously variable transmission. The two-mode super variable speed case consists of case (1), base step-less transmission (2), and control mechanism (11) including matching planetary (12) and differential (13) gears; it also consists of output shaft of drive (27) designed to alternate kinematic connection with kinematic links of the control mechanism. Matching planetary gear (12) can be kinematically connected either with carrier (23) or with external central wheel (21) of differential gear (13). Internal central wheel (20) of differential gear (13) can be connected with output kinematic link (9) of base step-less transmission (2). External central wheel (15) of matching planetary gear (12) is connected with input kinematic link (9) of base step-less transmission (2). Internal central wheel (15) of matching planetary gear (12) is connected with fixed case (1). Output shaft of drive (27) can be connected either with external central wheel (21) or with carrier (23) of differential gear (13). The second version differs from the first one like follows: output kinematic link (9) of base step-less transmission (2) is connected to the external central wheel (21) of differential gear (13), while internal central wheel (20) contains singular tooth ring (22). The third version of the drive differs from the first two like follows: output kinematic link (9) of base step-less transmission (2) can be telescopic jointed to fixture (3 8) by means of splines (40); the fixture bears tooth ring (41) of internal mesh.

EFFECT: invention transmits torque with reduced revolution frequency from input kinematic link of step-less transmission to output link of drive which simplifies drive, increases its efficiency and eliminates high intermediate frequencies of control mechanism rotation.

9 cl, 6 dwg

FIELD: mechanical engineering.

SUBSTANCE: invention relates to mechanical engineering and can be used, particularly in transmission of vehicles, in the first place, cars. Multiplate planetary variator contains carrier (11), consisting of two sidewalls, connected by cylindrical tension buckle (10) by number of planetary gear (5) in row, got on by several rows with ability of rotation on axis (6), rigidly fixed between ends of extreme pivot rods (7), other ends of which, as a minimum, one group form them, located at one of sidewalls of carrier (11), are controlled and its movement it is regulated advantage of variator. Middle parts of extreme revolute arms (7) are connected to each other by pipes (9), inside of which there are located cylindrical tension buckle (10) of carrier (11) with ability of reciprocal rotation. Pipes (9), on which there are fixed revolute arms (7) and axis (6) of planetary gears (5) between its rods are rigidly connected by blackets. Revolute arms (7), its ties, blackest and axis of planetary gears form rigid system, but with ability of total or partial disassembling.

EFFECT: providing the ability to resist by dangerous bending stress and huge caving in of planetary gears with several rows of planetary gears on it, appearing at high rotating frequency of carrier, and also toughening junction by tension buckles of sidewalls of carrier at transferring of high rotational moments.

2 cl, 3 dwg

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