Hydromechanical gearbox

FIELD: transport.

SUBSTANCE: invention relates to vehicle planetary gearboxes. Automatic gearbox executes nine forward gears and one rear gear comprises crankcase (19), input link (20), output link (21), hydromechanical torque converter and planetary reduction gear. The latter consists of four planetary rows. First row consists of sun gear (3), carrier (2) and crown gear (1). Second row consists of sun gear (6), carrier (5) and crown gear (4). Third row consists of sun gear (9), carrier (8) and crown gear (7). Fourth row consists of sun gear (12), carrier (11) and crown gear (10). Input link (20) engages with output link of hydromechanical torque converter (22), first planetary row sun gear (3) and fourth planetary row sun gear (12). Output link (21) engages with third planetary row crown gear (7). First planetary row crown gear (1) engages with second planetary row carrier (5). Brake (13) couples first row carrier (2) with crankcase of gearbox (19). Brake (14) couples first row carrier (6) with crankcase of gearbox (19). Brake (15) couples engaged third planetary row carrier (8) with fourth planetary row crown gear (10). Clutch (16) engages fourth planetary row sun hear (12) engaged with sun gear (3) and input link (20) with fourth planetary row crown gear (10) engaged with carrier (8). Clutch (17) engages carrier (11) with engaged crown gear (7) and output link (21). Clutch (18) engages crown gear (3) with engaged crown gear (4) and crown gear (9).

EFFECT: increased number of gears.

1 dwg

 

The invention relates to the field of transport engineering and for the design stage planetary gearbox, which can be used in automatic transmissions, managed with the help of electronic unit and hydraulics and intended for vehicles.

Torque and rotational speed of the engine is converted transmission in accordance with changes in the driving conditions of the vehicle to ensure the vehicle is moving both forward and backward.

Part of an automatic transmission includes a hydrodynamic torque Converter (torque Converter), in which the kinetic energy of the working fluid is used to transfer torque from the engine crankshaft to the input element of the transmission. It is, as a rule, transmission of the planetary type, providing the change of torque on the propulsion and speed. Transmission also includes controls such as friction or toothed, whose purpose can be divided into two groups: brakes and clutches. Couplings connect the elements of the planetary mechanism between them. Brakes combine elements of the planetary mechanism with the transmission case.

Known hydromechanical transmission (C is the turnout PCT No. WO 2012052330, published on 26.04.2012) containing a hydrodynamic torque Converter, four planetary series and five control elements (four brakes and clutch), which is due to the joint inclusion of the two controls on each transfer manages to get six speeds forward and one reverse gear.

Analysis of the development of automatic transmissions shows that six or even seven passes are not satisfied with car manufacturers, because it does not provide a sufficient degree of smoothness when shifting gears. Therefore, at present there is a need in the kinematic schemes hydromechanical planetary gearboxes with eight or more passes. While it is preferable not to increase the power losses during transmission from the engine to the drive wheels. One of the main factors affecting the magnitude of the losses in the gearbox, in the case of use as control elements of the friction clutches and friction brakes is the number of the friction elements are in the off state. The less of these items, the higher the efficiency of the transmission.

In the box-prototype manages to get six speeds forward and one reverse gear due to the pairwise inclusion of the five frictional elements of the control links of the PLA is Yarnykh rows.

The technical result for which the present invention is directed, is expanding Arsenal of technical means, as well as increasing the number of transmission implemented in a box with a similar number of planetary alignments, and without increasing the losses in the controls, that is, while maintaining the number of elements in the off state for each realizable transfer.

This technical result is achieved by the fact that in the hydromechanical transmission containing a hydrodynamic torque Converter and planetary gear controls in the form of controlled brakes and clutches, the output element of the gearbox is connected to the crown gear of the fourth planetary number associated with the planet carrier of the second planetary series, drove the fourth planetary series connected with the transmission brake, with a sun gear of the first planetary number associated with the input element of the gearbox, and a sun gear of the second planetary range, coupling, and with a crown gear (epicycles) of the second planetary series coupling, the sun gear of the fourth planetary number associated with the crown gear of the third planetary series, are connected by means of coupling with the planet carrier of the first planetary series, a sun gear of the third planetary OC is and connected with the transmission case via a brake, carrier of the third planetary series is associated with the crown gear of the first planetary series, drove the first planetary number associated with the transmission brake, the input link is connected with the output element of the hydrodynamic torque Converter.

These characteristics are essential and interrelated with the formation of a stable set of essential features, sufficient to obtain the desired technical result.

Fig.1 is a kinematic diagram of a hydromechanical nine-storeyed transmission for a vehicle transmission.

The present invention is illustrated by a specific example, which, however, is not only possible, but clearly demonstrates the possibility of achieving the desired technical result is given by a set of attributes.

According to the invention hydromechanical transmission containing a hydrodynamic torque Converter and planetary gear controls in the form of controlled brakes and clutches, in which the output element of the gearbox is connected to the crown gear of the fourth planetary number associated with the planet carrier of the second planetary series, drove the fourth planetary series connected with the transmission brake, the sun gear is, I can pay tithing planetary series associated with the input element of the gearbox, and a sun gear of the second planetary range, coupling, and with a crown gear (epicycles) of the second planetary series clutch, the sun gear of the fourth planetary number associated with the crown gear of the third planetary series, are connected by means of coupling with the planet carrier of the first planetary series, a sun gear of the third planetary series connected with the transmission case via a brake, the carrier of the third planetary series is associated with the crown gear of the first planetary series, drove the first planetary number associated with the transmission brake, the input link is connected with the output element of the hydrodynamic torque Converter.

Below is an example of a specific implementation of the hydro-mechanical transmission for an automatic transmission, for example, passenger of all-terrain vehicles.

Automatic transmission, implements nine speeds forward and one reverse gear, contains a crankcase 19, the input element 20, the output link 21, a hydrodynamic torque Converter and planetary gear, which includes four planetary series, managed three clutches and three managed brakes.

In the gearbox, according to the invention, the planetary gear comp is it of the four planetary series. The first planetary series consists of a sun gear 3, drove 2 satellites and the crown gear 1 (epicycle). The second planetary series consists of a sun gear 6, drove 5 satellites and the crown gear 4 (epicycle). The third planetary series consists of a sun gear 9, drove 8 satellites and the crown gear 7 (epicycle). The fourth planetary series consists of a sun gear 12, drove 11 satellites and the crown gear 10 (epicycle).

Input link 20 is connected with the output link 22 hydrodynamic torque Converter 22, a sun gear 3 of the first planetary series, and also with a sun gear 6 of the second planetary series. The output link 21 is connected with a crown gear 10 of the fourth planetary series and with the planet carrier 5 of the second planetary series. Drove 8 of the third planetary series is associated with a crown gear 1 of the first planetary series. Brake 13 connects drove 2 of the first planetary series with the transmission housing 19. The brake 14 connects the sun gear 9 of the third planetary series with the transmission housing 19. Brake 15 connects the led 11 of the fourth planetary series with the transmission housing 19. The coupling 16 connects the crown gear 4 of the second planetary series with the planet carrier 11 of the fourth planetary series. A friction clutch 17 connects the led 11 of the fourth planetary series sevasanmi between an input link 20, the sun gear 3 of the first planetary series, and the sun gear 6 of the second planetary series. Coupling 18 connects the carrier 2 of the first planetary series with the interconnected crown gear 4 of the second planetary series, and the sun gear 12 of the fourth planetary series.

This embodiment of the transmission allows you to get nine speeds forward and one reverse gear, using the four planetary series and six controls. In the proposed scheme does not happen gap power when shifting gears.

Offer, according to the invention, the automatic transmission operates as follows.

After the start of vehicle motion serial shift from 1st to 9th is the vehicle accelerates to the desired speed. When the transmission is in the neutral position, none of the controls are not enabled.

In the first forward gear included brakes 13, 14 and 15, i.e. the angular velocity drove 2 of the first planetary series, a sun gear 9 of the third planetary series, and led 11 of the fourth planetary series is equal to zero.

Torque from the input element 20 is supplied to the sun gear 3 of the first planetary series, where should the crown gear 1 of the first planetary series is on its associated carrier 8 of the third planetary series. Then thread the torque should be on the crown gear 7 of the third planetary series and its associated sun gear 12 of the fourth planetary series, where should the crown gear 10 of the fourth planetary series, directly associated with the output link 21.

When switching to the second forward gear, the brake 14 is turned off and turns on the clutch 16, the brake 13 and 15 remain enabled. Thus, the angular speed of the carrier 2 of the first planetary series, and led 11 of the fourth planetary series is equal to zero. Thus the angular velocity of the crown gear 4 of the second planetary number equal to the angular speed of the carrier 11 of the fourth planetary series.

Torque from the input element 20 is supplied to the sun gear 6 of the second planetary series, where you drove a 5 second planetary series, connected directly to the output link 21.

When switching to the third forward gear off the brake 15 and turns on the brake 14, the clutch 16 and the brake 13 are enabled. Thus, the angular speed of the carrier 2 of the first planetary series, and a sun gear 9 of the third planetary series is equal to zero. Thus the angular velocity of the crown gear 4 of the second planetary number equal to the angular speed of the carrier 11 of the fourth planetary series.

Torque from the input element 2 is supplied to the sun gear 6 of the second planetary series where you drove a 5 second planetary series, which splits it into two streams. The first flow of torque from the carrier 5 of the second planetary series is supplied through an associated crown gear 10 of the fourth planetary number on the led 11 of the fourth planetary series, which splits it into two streams. The first thread kutsero moment from the led 11 of the fourth planetary number should be on the sun gear 12 of the fourth planetary series and associated crown gear 7 of the third planetary series, from where it enters the carrier 8 of the third planetary series and associated crown gear 1 of the first planetary series. Then this thread torque acts on the sun gear 3 of the first planetary number associated with the input element 20, which is merged with the original thread torque. The second flow of torque from the carrier 11 of the fourth planetary series is supplied through the coupling 16 on the crown gear 4 of the second planetary series, where you drove a 5 second planetary series, where is merged with the original thread torque. The second flow of torque from the carrier 5 of the second planetary series comes directly associated with the output link 21.

When switching to the fourth forward gear off the brake 14 and on the same way clutch 18, brake 13 and the sleeve 16 are enabled. Thus, the angular speed of the carrier 2 of the first planetary series is equal to zero. Thus the angular velocity of the crown gear 4 of the second planetary number equal to the angular speed of the carrier 11 of the fourth planetary series, and the angular velocity drove 2 of the first planetary series of equal angular velocity interconnected crown gear 7 of the third planetary series, and a sun gear 12 of the fourth planetary series.

Torque from the input element 20 is supplied to the sun gear 6 of the second planetary series, where you drove a 5 second planetary series, which splits it into two streams. The first flow of torque from the carrier 5 of the second planetary series is supplied through an associated crown gear 10 of the fourth planetary number on the led 11 of the fourth planetary series where it comes through the coupling 16 on the crown gear 4 of the second planetary series, where you drove a 5 second planetary series, where is merged with the original thread torque. The second flow of torque from the carrier 5 of the second planetary series comes directly associated with the output link 21.

When switching on the fifth forward gear off the brake 13 and turns on the brake 14, couplings 16 and 18 are enabled. Therefore clicks the zoom, the angular velocity of sun gear 9 of the third planetary series is equal to zero. Thus the angular velocity of the crown gear 4 of the second planetary number equal to the angular speed of the carrier 11 of the fourth planetary series, and the angular velocity drove 2 of the first planetary series of equal angular velocity interconnected crown gear 7 of the third planetary series, and a sun gear 12 of the fourth planetary series.

Torque from the input element 20 is supplied to the sun gear 3 of the first planetary series, which splits it into two streams. The first flow of torque from the sun gear 3 of the first planetary series arrives on the carrier 2 of the first planetary series and then through the sleeve 18 on the crown gear 7 of the third planetary series, which splits it into two streams. The first flow of torque from the crown gear 7 of the third planetary series should have taken 8 of the third planetary series and associated crown gear 1 of the first planetary series, where then should have taken 2 of the first planetary series, where it is combined with the flow of torque, moving from the sun gear 3 of the first planetary series. The second flow of torque from the crown gear 7 of the third planetary series comes to an associated sun gear 12 of the fourth planetary series, from the UDA should have taken 11 of the fourth planetary series and then through the sleeve 16 on the crown gear 4 of the second planetary series. Then this thread comes on took 5 of the second planetary series, where combined with the second flow of torque from the sun gear 3 of the first planetary series and moving through its associated sun gear 6 of the second planetary series and then falling on the carrier 5 of the second planetary series. Formed on the drive rod 5 of the second planetary number of the flow of torque is divided into two streams. The first stream is received from the carrier 5 of the second planetary range associated with the crown gear 10 of the fourth planetary series and then merged with the flow of power to the driver 11 of the fourth planetary series. The second flow of torque from the carrier 5 of the second planetary series comes directly associated with the output link 21.

When switching on the sixth forward gear off the brake 14 and turns on the clutch 17, couplings 16 and 18 are enabled. Thus the angular velocity of the crown gear 4 of the second planetary number equal to the angular speed of the carrier 11 of the fourth planetary range, the angular velocity drove 2 of the first planetary series of equal angular velocity interconnected crown gear 7 of the third planetary series, and a sun gear 12 of the fourth planetary series, and the angular velocity of connected input link 20, with the final gear 3 of the first planetary series, and a sun gear 6 of the second planetary number equal to the angular speed of the carrier 11 of the fourth planetary series.

Torque on the input link 20 is divided into two streams. The first stream passes through the coupling 17 on the carrier 11 of the fourth planetary range, which implies through the coupling 16 on the crown gear 4 of the second planetary series and then drove 5 of the second planetary series, where combined with the second stream of torque from an input link 20 to an associated sun gear 6 of the second planetary series and then coming on took 5 of the second planetary series. Formed the flow of torque from the carrier 5 of the second planetary series comes directly associated with the output link 21.

When switching on the seventh forward gear clutch 16 is switched off and turns on the brake 14, the clutches 17 and 18 are enabled. Thus, the angular velocity of sun gear 9 of the third planetary series is equal to zero. When this angular velocity was taking 2 of the first planetary series of equal angular velocity interconnected crown gear 7 of the third planetary series, and a sun gear 12 of the fourth planetary series, and the angular velocity of connected input link 20, the sun gear 3 of the first planetary series, and a sun gear 6 of the second planetary number equal to the angular speed of the carrier 11 of the fourth planetary series.

Torque with ugodnog the link 20 is fed through the coupling 17 on the carrier 11 of the fourth planetary series where is divided into two streams. The first thread from the led 11 of the fourth planetary series is supplied to the sun gear 12 of the fourth planetary series and then through the sleeve 18 on the carrier 2 of the first planetary series, which splits it into two streams. The first thread from the led 2 of the first planetary number should be on the sun gear 3 of the first planetary number associated with the input element 20, which is merged with the original thread torque. The second thread from the led 2 of the first planetary series arrives on the crown gear 1 of the first planetary series and the associated carrier 8 of the third planetary series, where should the crown gear 7 of the third planetary number associated with the sun gear 12 of the fourth planetary series, where it is combined with the first stream of torque from the carrier 11 of the fourth planetary series. The second flow of torque from the carrier 11 of the fourth planetary series arrives on the crown gear 10 of the fourth planetary series, directly associated with the output link 21.

When switching on the eighth forward gear off the brake 14 and turns on the brake 13, the clutches 17 and 18 are enabled. Thus, the angular speed of the carrier 2 of the first planetary series is equal to zero. When this angular velocity was taking 2 of the first planetary number of equal angular RMSE of the spine connected between a crown gear 7 of the third planetary series, and a sun gear 12 of the fourth planetary series as well as the angular velocity of connected input link 20, the sun gear 3 of the first planetary series, and a sun gear 6 of the second planetary number equal to the angular speed of the carrier 11 of the fourth planetary series.

Torque from the input element 20 passes through the coupling 17 on the carrier 11 of the fourth planetary series, where should the crown gear 10 of the fourth planetary series, connected directly to the output link 21.

When switching on the ninth forward gear off the clutch 18 and turns on the brake 14, the clutch 17 and the brake 13 are enabled. Thus, the angular speed of the carrier 2 of the first planetary series, and a sun gear 9 of the third planetary series is equal to zero. When this angular velocity connected between an input link 20, the sun gear 3 of the first planetary series, and a sun gear 6 of the second planetary number equal to the angular speed of the carrier 11 of the fourth planetary series.

Torque from the input element 20 is supplied to the sun gear 3 of the first planetary series, which splits it into two streams. The first thread from the sun gear 3 of the first planetary series arrives on the crown gear 1 of the first planetary series and its associated carrier 8 of the third planetary series, where should the crown gear 7 of the third planetang the series and its associated sun gear 12 of the fourth planetary series. Then this thread torque arrives at the carrier 11 of the fourth planetary series, where it is combined with the second stream of torque, moving from the sun gear 3 of the first planetary series via a coupling 17 on the carrier 11 of the fourth planetary series. Formed the flow of torque from the carrier 11 of the fourth planetary series arrives on the crown gear 10 of the fourth planetary series, directly associated with the output link 21.

On the reverse gear activated brakes 14 and 15 and the sleeve 18. Thus, the angular speed of the sun gear 9 of the third planetary series, and led 11 of the fourth planetary series is equal to zero. When this angular velocity was taking 2 of the first planetary series of equal angular velocity interconnected crown gear 7 of the third planetary series, and a sun gear 12 of the fourth planetary series

Torque from the input element 20 is supplied to the sun gear 3 of the first planetary series, where you took 2 of the first planetary series, and then through the sleeve 18 on the crown gear 7 of the third planetary series, which splits it into two streams. The first thread from the crown gear 7 of the third planetary series arrives on the carrier 8 of the third planetary series and associated crown gear 1 of the first planetary series, where cledwyn drove 2 of the first planetary series where is merged with the original thread torque. The second thread from the crown gear 7 of the third planetary series comes to an associated sun gear 12 of the fourth planetary series and then on the crown gear 10 of the fourth planetary series, directly associated with the output link 21.

The schema changes and the sequence of the joint inclusion of controls allows to achieve the stated technical result and a significant extension of the kinematic range gearbox, and that when the switch is missing gap power. In addition, it is possible to improve the dynamic characteristics of the transmission and to increase its durability.

The present invention is industrially applicable, because its implementation does not require special new technology and special equipment, except those used in mechanical engineering in the production of gearboxes including planetary.

Hydromechanical transmission containing a hydrodynamic torque Converter and planetary gear controls in the form of controlled brakes and clutches, in which the crown gear (apical) of the third planetary series connected with the output element and coupled with the planet carrier of the fourth planetary series, Coron the I gear of the fourth planetary series connected with the planet carrier of the third planetary series with the transmission case via a brake, with a sun gear of the fourth planetary series connected with a sun gear of the first planetary series and the input link, through the clutch, the sun gear of the third planetary number associated with the crown gear of the second planetary series connected coupling with the planet carrier of the first planetary series, drove the first planetary number associated with the transmission brake, the crown gear of the first planetary series connected with the planet carrier of the second planetary range, the input link is connected with the output element of the hydrodynamic torque Converter.



 

Same patents:

FIELD: transport.

SUBSTANCE: invention relates to vehicle planetary gearboxes. Automatic gearbox executes nine forward gears and one rear gear comprises crankcase (19), input link (20), output link (21), hydromechanical torque converter and planetary reduction gear. This reduction gear comprises four planetary rows, three controlled clutches and three controlled brakes. First row consists of sun gear (3), carrier (2) and crown gear (1). Second row consists of sun gear (6), carrier (5) and crown gear (4). Third row consists of sun gear (9), carrier (8) and crown gear (7). Fourth row consists of sun gear (12), carrier (11) and crown gear (10). Input link (20) engages with output link of hydromechanical torque converter (22), first planetary row sun gear (3) and second planetary row sun gear (6). Output link (21) engages with fourth planetary row crown gear (10). First planetary row crown gear (1) engages with third planetary row carrier (8). Brake (13) couples first planetary row carrier (2) with crankcase of gearbox (19). Brake (14) couples third planetary row carrier (9) with crankcase of gearbox (19). Brake (15) engages engaged fourth planetary row carrier (11) and second planetary row crown gear (4) with gearbox crankcase (19). Clutch (16) engages first planetary row carrier (2) with engaged third planetary row crown gear (7) and fourth planetary row sun gear (12). Clutch (17) engages second planetary row carrier (5) with engaged fourth planetary row crown gear (10) and output link (21). Clutch (18) engages third planetary row carrier (5) with engaged second planetary row crown gear (4) and fourth planetary row carrier (11).

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FIELD: transport.

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EFFECT: high efficiency and wide range of gear ratio, reduced metal input.

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15 cl, 30 dwg

FIELD: transport.

SUBSTANCE: invention relates to modular A/T. Modular gearbox has planetary system composed of universal range differential wherein spider (5) with three pairs of engaged three-rim pinions is shared by 1st, 2nd and 3rd rows spider, 1st planetary row crown wheel, 2nd row crown wheel and 3rd row central sun gear are engaged by friction brakes with gearbox crankcase. Crown wheel makes an output link of gearbox. Said A/T universal range differential and extra planetary rows allows various design versions.

EFFECT: higher efficiency of gearbox.s

6 cl, 6 dwg

FIELD: physics.

SUBSTANCE: planetary mechanism comprises a photometer consisting of a disc (1), which is equipped with an axle (2), having openings that are equidistant from each other and from the centre of the disc, in which light filters are located. The axle (2) interacts with the disc through a free-wheel clutch (3). In the openings of the disc there are rotatable adapters (4), the outer surface of which is in form of gear wheels which interact with a central gear wheel (5), immovably mounted on the axle (2). The disc interacts with the base through another free-wheel clutch (7). Directions of the working strokes of the free-wheel clutches (3, 7) are opposite.

EFFECT: along with the possibility of moving the light filters, the invention enables to turn each of the light filters about its own axis.

1 dwg

FIELD: automobile production.

SUBSTANCE: automatic gearbox has one planetary gear set (4) and a torque moment transfer route passing parallel to that planetary gear set (4). Planetary gear set (4) at one transmission stage of gearbox (1) is not used for torque moment transfer and is rotated without any relative number of revolutions of its components relative to each other. With that, at the above transmission stage, the structure of the connection of the same planetary gear set (4) has the possibility of being changed by means of coupling clutches (10,11) so that gear transmission ratio of planetary gear set (4) changes from gear transmission ratio of reduced transmission to gear transmission ratio of increased transmission, or vice versa.

EFFECT: simpler design of the device.

10 cl, 33 dwg

FIELD: machine building.

SUBSTANCE: gearbox includes a cylindrical helical planetary reduction gear, a carrier with satellites and their axes, a friction coupling, centrifugal weights on the coupling housing and an automatic control system of the state of a sun gear (locking, unlocking). Crown gear of planetary reduction gear is installed in a movable manner on a drive shaft, sun gear is installed freely. Carrier with satellites and their axes are fixed on a driven shaft. Drive disks of friction coupling are connected through splines to crown gear, and driven ones are connected through the coupling housing to the carrier. Automatic control system of the sun gear state includes a brake consisting of a pulley fixed on a hub of the sun gear, the brake band of which is connected through rods and two-arm levers with a spring to crown gear and two-arm control lever through a rod directly from the carrier. Gearbox has three modules so that driven shaft of the previous module is a drive shaft of the following one, which is installed after the last module of a reverse mechanism.

EFFECT: reduction of fatigability of a driver and accident risk; improving reliability of a friction coupling.

1 dwg

Automotive gearbox // 2486389

FIELD: transport.

SUBSTANCE: gearbox comprises planetary step-down helical gearbox and automatic system of shifting from 1st to 2nd gear. Said planetary reduction gear consists of drive shaft 1 supporting crown gear 2 with drive disc secured thereat, sun gear 3 running on driven shaft 4 with carrier 5 rigidly secured thereat with axles 6 and pinions 7 engaged with crown and sun gears. Automatic gear shifting system consists of friction coupling with its drive discs 8 coupled via splines with crown gear and driven discs coupled via case 10 and disc with pinion axles and carrier and with driven shaft of centrifugal weights 11 with springs 12, and automatic sun gear control system. Cases of coupling 10, disc 26 and axles of pinions 6 and carrier are rigidly interconnected. Extreme left drive disc of coupling 27 is bolted to crown gear. Slave arms of centrifugal weights with sleeves at their ends are pressed via working springs to crown gear for compression of coupling discs.

EFFECT: higher reliability.

1 dwg

FIELD: transport.

SUBSTANCE: invention relates to automotive industry and may be used in agricultural machinery and trackless machines. Proposed vehicle comprises body 2 to house two-stage planetary final drive 2 coupled via gearshift mechanism 3 with engine 4. Said planetary final drive 2 comprises two planetary trains 5. Planetary train 5 consists of carrier 6 with pinions 7 engaged with side brake 8, sun gear 9 and ring gear 11. Clutches of sun and ring gears locking and sun gear brakes are composed of inertial synchromesh units, each being engaged with sun gear of appropriate planetary train to be locked with ring gear or final drive housing.

EFFECT: higher reliability, reduced power loss in turns.

2 dwg

Variator // 2484335

FIELD: machine building.

SUBSTANCE: variator comprises input shaft whereto external torque is applied, set of driven gears, variable crank, variable input link, unidirectional couplings, set of crankshafts and set of working links. Driven gears are arranged around input shaft at one radius, each being shifted relative to the other one through definite angle. Variable crank is arranged in variable input element to vary radius of rotation. Variable input link is coupled with input shaft. Unidirectional couplings are fitted on inner surface on every gear to run in one direction. Crankshafts are arranged inside said unidirectional couplings to turn in housing. One end of every working link is connected with variable crank while opposite end is engaged with each of crankshafts to run therewith.

EFFECT: decreased overall dimensions, longer life.

7 cl, 5 dwg

FIELD: transport engineering.

SUBSTANCE: invention can be used in automatic transmissions controlled by electronic unit and hydraulic devices. Proposed hydromechanical transmission contains hydrodynamic torque converter 2 and planetary reduction gear consisting of four planetary trains. All planetary trains have negative inner ratio. Output link of torque converter is coupled with ring gear 7 of first planetary train, with sun gear 8 of second planetary train and, through friction clutch 18, with carrier 12 of third planetary train, and through friction clutch 17, with sun gear 11 of the same train which is connected with case 1 through friction brake 22. Sun gear 5 of first planetary train is coupled with case 1 through friction brake 19. Carrier 6 of this train is coupled with carrier 9 of second planetary train, with ring gears 13 and 16 of third and fourth and fourth planetary trains. Ring gear 10 second planetary train is connected with case 1 through friction brake 20. Sun gear 14 of fourth planetary train is coupled with carrier 12 of third planetary train and, through friction brake 21, with case 1. Carrier 15 of fourth planetary train is output link 4 of transmission.

EFFECT: enlarged mechanical capabilities of transmission owing to provision of ten forward speeds, one reverse speed and enlargement of range up to 6.286 at preservation of overall dimensions.

1 dwg

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