Hydromechanic transmission

FIELD: transport.

SUBSTANCE: automatic transmission implementing nine forward gears and one reverse gear contains casing (19), input link (20), output link (21), hydrodynamic torque converter and planetary reduction gear. The planetary reduction gear consists of four planetary gear sets. The first planetary gear set consists of a central gear (3), carrier (2) for satellites and a crown gear (1). The second planetary gear set consists of a central gear (6), carrier (5) for satellites and a crown gear (4). The third planetary gear set consists of a central gear (9), carrier (8) for satellites and a crown gear (7). The fourth planetary gear set consists of a central gear (12), carrier (11) for satellites and a crown gear (10). Input link (20) is connected with output link of hydrodynamic torque converter (22), with sun gear (3) of the first planetary gear set and with sun gear (12) of the fourth planetary gear set. Output link (21) is connected with crown gear (7) of the third planetary gear set. Crown gear (1) of the first planetary gear set is connected with carrier (5) of the second planetary gear set. Brake (13) connects carrier of the first set (2) with transmission case (19). Brake (14) connects sun gear (6) with transmission case (19). Brake (15) connects the interconnected carrier (8) of the third planetary gear set and crown gear (10) of the fourth planetary gear set. Clutch (16) connects sun gear (12) of the fourth planetary gear set connected with sun gear (3) of the first planetary gear set and with input link (20) with crown gear (10) of the fourth planetary gear set connected with carrier (8) of the third planetary gear set. Clutch (17) connects carrier (11) of the fourth planetary gear set with interconnected crown gear (7) of the third planetary gear set and output link (21). Clutch (18) connects the sun gear (3) of the first planetary gear set with interconnected crown gear (4) of the second planetary gear set and sun gear (9) of the third planetary gear set.

EFFECT: more gears in transmission.

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, when storing a number of items that are 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 crown gear (apical) of the third planetary series connected with the output element and coupled with the planet carrier of the fourth planetary series, the crown 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 series 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 above the turn of the first planetary series connected with the planet carrier of the second planetary series 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 crown gear (apical) of the third planetary series connected with the output element and coupled with the planet carrier of the fourth planetary series, the crown 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 coupling with lachna gear of the third planetary series 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.

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 consists of 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 corona pole is neither 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 element of the hydrodynamic torque Converter 22, a sun gear 3 of the first planetary range and with a sun gear 12 of the fourth planetary series. The output link 21 is connected with a crown gear 7 of the third planetary series. Crown gear 1 of the first planetary series connected with the planet carrier 5 of the second planetary series. Brake 13 connects the led of the first row 2 with the transmission housing 19. The brake 14 connects the sun gear 6 with the transmission housing 19. Brake 15 connects the interconnected carrier 8 of the third planetary series and the crown gear 10 of the fourth planetary series. The coupling 16 connects the sun gear 12 of the fourth planetary series connected with a sun gear 3 of the first planetary series with the input element 20, with a crown gear 10 of the fourth planetary number associated with the planet carrier 8 of the third planetary series. Clutch 17 connects the led 11 of the fourth planetary series with the interconnected crown gear 7 of the third planetary series and the output link 21. Coupling 18 connects the sun gear 3 of the first planetary series with the interconnected crown gear 4 of the second planetary series and the solar gear 9 of the third 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 6 of the second planetary series and interconnected drove 8 of the third planetary series and the crown gear 10 of the fourth planetary series is equal to zero.

Torque from the input element 20 is supplied to an associated sun gear 3 of the first planetary series, where should the crown gear 1 of the first planetary series and associated drove 5 of the second planetary series. Then, from the carrier 5 of the second planetary number of the flow of torque is transferred to the crown gear 4 of the second planetary series and connected the with her sun gear 9 of the third planetary series and then the crown gear 7 of the third 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 17, brakes 13 and 15 remain enabled. Thus, the angular speed of the carrier 2 of the first planetary series and interconnected drove 8 of the third planetary series and the crown gear 10 of the fourth planetary series is equal to zero. Thus the angular velocity of carrier 11 of the fourth planetary series of equal angular velocity interconnected crown gear 7 of the third planetary range and output link 21.

Torque from the input element 20 is supplied to an associated sun gear 12 of the fourth planetary series, where you took 11 of the fourth planetary and then through the clutch 17 on the crown gear 7 of the third planetary series, directly associated with the output link 21.

When switching to the third forward gear off the brake 15 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, a sun gear 6 of the second planetary series is equal to zero. Thus the angular velocity of carrier 11 of the fourth planetary series of equal angular velocity interconnected crown gear 7 of the third planetary range and output link 21.

Torque from the output element 20 is supplied to an associated sun gear 12 of the fourth planetary series then drove 11 fourth planetary series, where through the clutch 17 is fed to the crown gear 7 of the third planetary series, which splits it into two streams. The first thread from the crown gear 7 comes on the carrier 8 of the third planetary series, where it splits and goes through connected with the planet carrier 8 of the third planetary series crown gear 10 of the fourth planetary number on the led 11 of the fourth planetary series, where it is merged with the original thread torque. Another stream of power from the carrier 8 of the third planetary number should be on the sun gear 9 of the third planetary series and associated crown gear 4 of the second planetary series, where is transmitted to the carrier 5 of the second planetary series and related crown gear 1 of the first planetary series and then 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 crown gear 10 of the fourth planetary series comes directly associated with the output link 21.

When switching to the fourth forward gear off the brake 14 and the activated coupling 18, the brake 13 and the sleeve 17 are enabled. Thus, the angular speed of the carrier 2 of the first planetary series is equal to zero. PR is that the angular speed of the carrier 11 of the fourth planetary series of equal angular velocity interconnected crown gear 7 of the third planetary range and output link 21, the angular speed of the carrier 2 of the first planetary series of equal angular velocity related crown gear 4 of the second planetary series, and a sun gear 9 of the third planetary series.

Torque from the input element 20 is supplied to an associated sun gear 12 of the fourth planetary series, then drove 11 fourth planetary series, where through the clutch 17 is fed to the crown gear 7 of the third planetary series, which splits it into two streams. The first thread from the crown gear 7 comes on the carrier 8 of the third planetary series, then goes through connected with the planet carrier 8 of the third planetary series crown gear 10 of the fourth planetary number on the led 11 of the fourth planetary series, where it is merged with the original thread torque. The second flow of torque from the crown gear 10 of the fourth 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, the clutches 17 and 18 are enabled. Thus, the angular speed of the sun gear 6 of the second planetary series is equal to zero. Thus the angular velocity of carrier 11 of the fourth planetary series of equal angular velocity interconnected crown gear 7 of the third planetary is poison and output link 21, the angular speed of the carrier 2 of the first planetary series of equal angular velocity related crown gear 4 of the second planetary series, and a sun gear 9 of the third planetary series.

Torque from the input element 20 is supplied to an associated 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 carrier 2 of the first planetary series, where through the coupling 18 on the crown gear 4 of the second planetary series, where once again divided into two streams. The first thread from the crown gear 4 of the second planetary series arrives on the carrier 5 of the second planetary series and associated crown gear 1 of the first planetary series, where you took 2 of the first planetary series, where it is combined with the first stream of torque, as from the sun gear 3 of the first planetary series. The second stream of torque, from the crown gear 4 of the second planetary series comes to an associated sun gear 9 of the third planetary series, where transmitted cage 8 of the third planetary series and is associated with the crown gear 10 of the fourth planetary series. Further this thread goes on the carrier 11 of the fourth planetary series, where it is combined with the second thread is torque, following from the sun gear 3 of the first planetary series through its associated sun gear 12 of the fourth planetary series and then arriving at the carrier 11 of the fourth planetary series. Formed on the driver 11 of the fourth planetary series flow of torque through the clutch 17 is fed to 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, where it is combined with the second stream of torque, following from the crown gear 4 of the second planetary series through its associated sun gear 9 of the third planetary series and then falling on the carrier 8 of the third planetary series. The second flow of torque from the crown gear 7 of the third 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 16, the clutches 17 and 18 are enabled. Thus, the angular speed of the carrier 11 of the fourth planetary series of equal angular velocity interconnected crown gear 7 of the third planetary range and output link 21, the angular speed of the carrier 2 of the first planetary series of equal angular velocity related to corannulene 4 of the second planetary series, and a sun gear 9 of the third planetary series the angular velocity interconnected crown gear 10 of the fourth planetary series and took 8 of the third planetary number equal to the angular speed of the sun gear 12 of the fourth planetary series connected with a sun gear 3 of the first planetary series and the input element 20.

Torque on the input link 20 is divided into two streams. The first stream passes through the coupling 16 on the crown gear 10 of the fourth planetary series, where you took 11 of the fourth planetary series, where it is combined with the second stream of torque, as from an input link 20 via the sun gear 12 of the fourth planetary number on the led 11 of the fourth planetary series. Formed on the driver 11 of the fourth planetary series flow of torque through the friction coupling 17 is supplied to the output link 21.

When switching on the seventh forward gear off the clutch 17 and activates the brake 14, couplings 16 and 18 are enabled. Thus, the angular speed of the carrier 2 of the first planetary series of equal angular velocity related crown gear 4 of the second planetary series, and a sun gear 9 of the third planetary range, the angular velocity interconnected crown gear 10 of the fourth planetary series and took 8 of the third planetary number of equal angular RMSE of the spine of the sun gear 12 of the fourth planetary series associated with the sun gear 3 of the first planetary series and the input element 20. Thus the angular speed of the sun gear 6 of the second planetary series is equal to zero.

Torque from the input element 20 passes through the coupling 16 on the carrier 8 of the third planetary series, which splits it into two streams. The first flow of torque from the carrier 8 of the third planetary series of acts on the sun gear 9 of the third planetary series and related crown gear 4 of the second planetary range, which implies 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 series of acts on the sun gear 3 of the first planetary series and the associated input link 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 associated drove 5 of the second planetary series, where should the crown gear 4 of the second planetary series, where it is combined with the first stream of torque, moving from carrier 8 of the third planetary line through the sun gear 9 of the third planetary number associated directly with a crown gear 4 of the second planetary series. The second flow of torque from the carrier 8 t is Atego planetary number is passed to the crown gear 7 of the third 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, couplings 16 and 18 are enabled. Thus, the angular speed of the carrier 2 of the first planetary series of equal angular velocity related crown gear 4 of the second planetary series, and a sun gear 9 of the third planetary range, the angular velocity interconnected crown gear 10 of the fourth planetary series and took 8 of the third planetary number equal to the angular speed of the sun gear 12 of the fourth planetary series connected with a sun gear 3 of the first planetary series and the input element 20. When this angular velocity was taking 2 of the first planetary series is equal to zero.

Torque from the input element 20 passes through the coupling 16 on the carrier 8 of the third planetary series, where should the crown gear 7 of the third planetary series and directly associated with the output link 21.

When switching on the ninth forward gear off the clutch 18 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 6 of the second planetary series is equal to zero. When this angular velocity interconnected crown gear 10 Thu is REGO planetary series and took 8 of the third planetary number equal to the angular speed of the sun gear 12 of the fourth planetary series associated with the sun gear 3 of the first planetary series and the input element 20.

Torque from the input element 20 is supplied to an associated 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 associated drove 5 of the second planetary series, where should the crown gear 4 of the second planetary series and its associated sun gear 9 of the third planetary series and then drove 8 of the third planetary series, where it is combined with the second flow of torque from the sun gear 3 of the first planetary range, passing through the coupling 16 on the carrier 8 of the third planetary series. Formed on the drive rod 8 of the third planetary series power flow on the crown gear 7 of the third planetary series and 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 6 of the second planetary series and interconnected drove 8 of the third planetary series and the crown gear 10 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 connected between sabonervnih gear 4 of the second planetary series, and a sun gear 9 of the third planetary series.

Torque from the input element 20 is supplied to an associated 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 4 of the second planetary series, which splits it into two streams. The first thread from the crown gear 4 of the second planetary series should have taken 5 of the second planetary series and related crown gear 1 of the first planetary series and then drove 2 of the first planetary series, where it is merged with the original thread torque. The second flow of torque from the crown gear 4 of the second planetary number should be associated sun gear 9 of the third planetary series, which comes on the crown gear 7 of the third planetary series and related directly to 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 as it isn't Tr the need for a special new technology and special equipment, in addition to 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, the crown 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 by a 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. 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

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).

EFFECT: increased number of gears.

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FIELD: transport.

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FIELD: transportation, trackless surface vehicles.

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EFFECT: enhancement of dynamic properties and broadening of the range of transmission ratios.

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FIELD: mechanical engineering.

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FIELD: transport engineering; automatic transmissions.

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FIELD: transport.

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EFFECT: simplification of the device.

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FIELD: transport.

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EFFECT: enhanced performances, higher flotation and perfected control.

2 dwg

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

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).

EFFECT: increased number of gears.

1 dwg

Gearbox // 2531995

FIELD: transport.

SUBSTANCE: invention relates to gearboxes. Gearbox comprises fixed housing, input and output differentials. Every said differential consists of interacting links: sun gear, epicycle, carrier with pinions, input link engaged with input differential sun gear, output link engaged with output differential carrier, gears, controlled clutches, shafts engaged with differential links and articulation between shafts to be thrown in by controlled clutches. Besides, gearbox comprises idler wheel and controlled interlocking clutches for engagement of epicycle with input differential carrier and epicycle with output differential sun gear. This gearbox allows thirteen different speeds of output link revolution on one direction and two speeds in opposite direction.

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

4 cl, 4 dwg, 1 tbl

FIELD: transport.

SUBSTANCE: group of invention relates to versions of bicycle design and belt drive system. Bicycle comprises the frame and at least one wheel secured to said frame. Wheel has hub, second planetary gearbox arranged therein and belt for torque transmission between first planetary gearbox and second planetary gearbox. In compliance with first version, this frame comprises receiver to accommodate said first planetary gearbox. In compliance with second version, this frame also comprises receiver to accommodate said first planetary gearbox of different design version. In compliance with first version, belt drive system comprises frame, receiver, first planetary gearbox located therein and second planetary gearbox located in wheel hub. In compliance with second version, belt drive system comprises first planetary gearbox arranged in first receiver and second planetary gearbox arranged in second receiver.

EFFECT: decreased weight, better frame clearance.

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: 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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