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 (6) of the second planetary gear set. Output link (21) is connected with crown gear (10) of the fourth planetary gear set and with carrier (5) of the second planetary gear set . Brake (13) connects the interconnected crown gear (7) of the third planetary gear set and carrier (2) of the first planetary gear set with transmission case (19). Brake (14) connects sun gear (9) of the third planetary gear set with transmission case (19). Brake (15) connects carrier (11) of the fourth planetary gear set with transmission case (19). Clutch (16) connects crown gear (4) of the second planetary gear set with carrier (11) of the fourth planetary gear set. Clutch (17) connects the carrier (11) of the fourth planetary gear set with interconnected input link (20), sun gear (3) of the first planetary gear set and sun gear (6) of the second planetary gear set. Clutch (18) connects the crown gear (1) of the first planetary gear set with interconnected carrier (8) of the third planetary gear set and sun gear (12) of the fourth 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 (who avca 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 the 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 output element of the gearbox is connected with a crown gear (epicycles) of the fourth planetary number associated with the planet carrier of the second planetary series, drove the fourth planetary series connected with the transmission case via a brake, with a sun gear of the first planetary number associated with the input element, and a sun gear of the second planetary series, using couplings, with a crown gear of the second planetary series using clutch, the sun gear of the fourth planetary number associated with the planet carrier of the third planetary series, is connected with the crown gear of the first planetary series using clutch, the sun gear of the third planetary is in the second row is connected with the transmission brake, the crown gear of the third planetary number associated with the planet carrier of the first planetary series, is connected with the transmission case via a 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 with a crown gear (epicycles) of the fourth planetary number associated with the planet carrier of the second planetary series, drove the fourth planetary series connected with the transmission case via a brake, with solar destinatario planetary series associated with the input link and a sun gear of the second planetary series, using couplings, with a crown gear of the second planetary series using clutch, the sun gear of the fourth planetary number associated with the planet carrier of the third planetary series, is connected with the crown gear of the first planetary series using clutch, the sun gear of the third planetary number associated with the transmission brake, the crown gear of the third planetary number associated with the planet carrier of the first planetary series, is connected with the transmission case via a 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 consists of four planetary series. The first plan is tare range 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 element of the hydrodynamic torque Converter 22, a sun gear 3 of the first planetary range and 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. Brake 13 connects interconnected crown gear 7 of the third planetary series and took 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. Clutch 17 connects the led 11 of the fourth planetary series with the connected input link 20, the sun gear 3 of the first planetary series and Sunny the gear 6 of the second planetary series. Coupling 18 connects the crown gear 1 of the first planetary series with connected planet carrier 8 of the third planetary series, and a 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 and 15 and the sleeve 18, that is, the angular velocity of the crown gear 7 of the third planetary number associated with the planet carrier 2 of the second planetary series, and took 11 of the fourth planetary series is equal to zero. Thus the angular velocity of the crown gear 1 of the first planetary number equal to the angular speed of the carrier 8 of the third planetary number associated with the sun gear 12 of the fourth planetary series.

Torque from the input link mostwant on the sun gear 3 of the first planetary series where should the crown gear 1 of the first planetary series. Then this thread comes through the sleeve 18 on the carrier 8 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 clutch 18 is switched off and is switched to the clutch 16, the brake 13 and 15 remain enabled. Thus, the angular velocity of the crown gear 7 of the third planetary number associated with the planet carrier 2 of the second planetary series, and took 11 of the fourth planetary series is equal to zero. Thus the angular velocity of the crown gear 4 of the third 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 an associated sun gear 6 of the second planetary series, where then should have taken 5 of the second planetary series that is directly connected to the output link 21.

When switching to the third forward gear off the brake 15 and the activated coupling 18, the clutch 16 and the brake 13 are enabled. Thus, the angular velocity of the crown gear 7 of the third planetary number associated with the planet carrier 2 of the second planetary number of zero. Angular / min net is the crown gear 4 of the third planetary number equal to the angular speed of the carrier 11 of the fourth planetary series as well as the angular velocity of the crown gear 1 of the first planetary number equal to the angular speed of the carrier 8 of the third planetary number associated with the sun gear 12 of the fourth planetary series.

Torque from the input element 20 is supplied to an associated sun gear 6 of the second planetary series, where you drove a 5 second planetary series, which splits it into two streams. The first thread from the carrier 5 of the second planetary series comes to an associated crown gear 10 of the fourth planetary series, then drove on 11 of the fourth planetary series, which splits it into two streams. The first thread from the led 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 5 of the second planetary range, where it is merged with the original thread torque. The second thread from the led 11 of the fourth planetary series of acts on the sun gear 12 of the fourth planetary series and through the sleeve 18 on the crown gear 1 of the first planetary series, which comes 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 5 of the second planetary series goes on neposredstvennostb with it the output link 21.

When switching to the fourth forward gear off the clutch 18 and turns on the brake 14, the brake 13 and the sleeve 16 are enabled. Thus, the angular velocity of the crown gear 7 of the third planetary number associated with the planet carrier 2 of the second planetary series, and 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 third 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 an associated sun gear 6 of the second planetary series, where you drove a 5 second planetary series, which splits it into two streams. The first thread from the carrier 5 of the second planetary series comes to an associated crown gear 10 of the fourth planetary series, then drove on 11 of the fourth planetary series, which comes through the coupling 16 on the crown gear 4 of the second planetary series and then on took 5 of the second planetary range, where it 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 coupling 18, the clutch 16 and t is RMOS 14 remain enabled. Thus, 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 third planetary number equal to the angular speed of the carrier 11 of the fourth planetary series, and the angular velocity of the crown gear 1 of the first planetary number equal to the angular speed of the carrier 8 of the third planetary number associated with the sun gear 12 of the fourth 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 should have taken 2 of the first planetary series and associated crown gear 7 of the third planetary series, which comes on the carrier 8 of the third planetary series, which splits it into two streams. The first thread from the carrier 8 of the third planetary series through the sleeve 16 should be on the crown gear 1 of the first planetary series and then drove 2 of the first planetary series, where it is combined with the first stream of torque, moving from the sun gear 3 of the first planetary series. The second stream from the carrier 8 of the third planetary series comes to an associated sun gear 12 of the fourth planetary series and then drove 11 fourth planetary series. The ZAT is the flow through the clutch 16 is fed to the crown gear 4 of the second planetary series where you drove 5 of the second planetary range, where it is combined with the second stream of torque, moving from the sun gear 3 of the first planetary series to the associated sun gear 6 of the second planetary series and then to the cage 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 thread from the carrier 5 of the second planetary number of moves associated with the crown gear 10 of the fourth planetary series and then drove 11 fourth planetary series, where combined with the power flow, moving from the carrier 8 of the third planetary line through an associated sun gear 12 of the fourth planetary series and then falling on the led 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 third planetary number equal to the angular speed of the carrier 11 of the fourth planetary range, the angular velocity of the crown gear 1 of the first planetary number equal to the angular speed of the carrier 8 of the third planetary line is, associated with the sun gear 12 of the fourth planetary series, and the angular speed of the carrier 11 of the fourth planetary series of equal 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 series.

Torque on the input link 20 is divided into two streams. The first stream flows through the coupling 17 on the carrier 11 of the fourth planetary series and then through the sleeve 16 on the crown gear 4 of the second planetary series, where you drove 5 of the second planetary range, where it is combined with the second stream of torque, moving from an input link 20 through the associated sun gear 6 of the second planetary series to the cage 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 the crown gear 1 of the first planetary number equal to the angular speed of the carrier 8 of the third planetary number associated with the sun gear 12 of the fourth planetary series, and the angular speed of the carrier 11 of the fourth planetary range of equal main the speed connected between an input link 20, the sun gear 3 of the first planetary series, and a sun gear 6 of the second planetary series. Thus the angular velocity of sun gear 9 of the third planetary series is equal to zero.

Torque from the input element 20 through the clutch 17 is supplied to led 11 of the fourth planetary series, which splits it into two streams. The first thread from the led 11 of the fourth planetary number should be on the sun gear 12 of the fourth planetary series and the associated carrier 8 of the third planetary series, which comes on the crown gear 7 of the third planetary series and the associated drove 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 flow of torque from the carrier 2 of the first planetary series arrives on the crown gear 1 of the first planetary series and then through the sleeve 18 on the carrier 8 of the third planetary series, where combined with the power flow, moving from the led 11 of the fourth planetary line through the sun gear 12 of the fourth planetary number of the associated carrier 8 of the third planetary series. The second flow of torque from the carrier 11 fourth against the th row is supplied to the crown gear 10 of the fourth planetary series and related directly to the output link 21.

When switching on the eighth forward gear off the clutch 17 and activates the brake 13, the clutch 18 and the brake 14 are enabled. Thus, the angular velocity of sun gear 9 of the third planetary range and the angular velocity of the crown gear 7 of the third planetary number associated with the planet carrier 2 of the second planetary number of zero. Thus the angular velocity of the crown gear 1 of the first planetary number equal to the angular speed of the carrier 8 of the third planetary number associated with the sun gear 12 of the fourth planetary series.

Torque from the input element 20 through the clutch 17 is supplied to led 11 of the fourth planetary series, where should the crown gear 10 of the fourth planetary series and directly associated with the output link 21.

When switching on the ninth forward gear off the brake 14 and turns on the clutch 17, the clutch 18 and the brake 13 are enabled. Thus, the angular velocity of the crown gear 1 of the first planetary number equal to the angular speed of the carrier 8 of the third planetary number associated with the sun gear 12 of the fourth planetary series, and the angular speed of the carrier 11 of the fourth planetary series of equal angular velocity connected between an input link 20, the sun gear 3 of the first planetary series and solar sixth is ERNI 6 of the second planetary series. Thus the angular velocity of the crown gear 7 of the third planetary number associated with the planet carrier 2 of the second planetary number of zero.

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 then through the sleeve 18 on the carrier 8 of the third planetary series and its associated sun gear 12 of the fourth planetary series, and then drove 11 fourth planetary series, where it is combined with the second stream of torque, as from the sun gear 3 of the first planetary series through its associated sun gear 6 of the second planetary series, and then through the clutch 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 and related directly to the output link 21.

On the reverse gear activated brakes 14 and 15 and the sleeve 18. Thus, the angular velocity of the crown gear 1 of the first planetary number equal to the angular speed of the carrier 8 of the third planetary number associated with the sun gear 12 of the fourth planetary series. Angular soon is here the sun gear 9 of the third planetary range and the angular speed of the carrier 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 and then drove 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 associated with the crown gear 7 of the third planetary series and then drove 8 of the third planetary series, where it is combined with the second stream of torque, moving from the led 2 of the first planetary series on the crown gear 1 of the first planetary series and then through the coupling 18 on the carrier 8 of the third planetary series. The formed thread torque drove 8 of the third planetary number should be associated with the sun gear 12 of the fourth planetary series, where falls on the crown gear 10 of the fourth 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 for R the implementation does not need 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 output element of the gearbox is connected with a crown gear (epicycles) of the fourth planetary number associated with the planet carrier of the second planetary series, drove the fourth planetary series connected with the transmission case via a brake, with a sun gear of the first planetary number associated with the input link and a sun gear of the second planetary series, using couplings, with a crown gear of the second planetary series using clutch, the sun gear of the fourth planetary series associated with the planet carrier of the third planetary series, is connected with the crown gear of the first planetary series using clutch, the sun gear of the third planetary number associated with the transmission brake, the crown gear of the third planetary number associated with the planet carrier of the first planetary series, is connected with the transmission case via a brake, the input link is connected with the output element of the hydrodynamic torque Converter.



 

Same patents:

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

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

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: for braking purpose an output shaft of automatic gearbox is connected to a turbine shaft of hydrodynamic torque converter. The external crown (16) of turbine gear under disconnected multidisk brake (11) of reverse gear (10) is slown down or stopped.

EFFECT: higher reliability of the device.

5 cl, 2 dwg

FIELD: transport.

SUBSTANCE: automatic gearbox 1 comprises+ drive side 3, hydrodynamic torque converter 2 and drive side 6. Gearbox 1 has power train flow via said converter 2, mechanical power flows there around and combined power flows. Driven side 6 incorporates one planetary train 7. Besides, it incorporates brake 18 to stop the converter turbine.

EFFECT: compact design and expanded operating performances.

7 cl, 4 dwg

FIELD: machine building.

SUBSTANCE: fluid converter contains centrifugal impeller (1), centripetal turbine wheel (3), axial reactor (5), planetary gear, brake (10) reactor and brake (11) of carrier (9) of the planetary gear unit. Impeller and turbine wheel rotate in one direction. The torque acting on the centreline of reactor (5), rotating in the opposite direction, is added to the torque of centripetal turbine wheel (3), increasing the torque at the output shaft. When h reaches the gear ratio of 0.7, the torque converter operates the in mode of coupling, thereby increasing operating range up to 5.

EFFECT: invention enables to extend the working range of the fluid converter with a forced rotation of the reactor.

1 dwg

Planetary variator // 2374528

FIELD: machine building.

SUBSTANCE: variator contains two planetary rows, control mechanism and controlling link (6). Driving shaft (1) is implemented as through with ability of installation of actuating motor to any its end. The first and the planetary rows are located successively, each of which includes central and crown wheel, spider with satellites. Controlling mechanism is implemented as hydraulic, allows ability of changing of overall gear ratio of variator independently on revolutions of actuating motor is located on driving shaft (1), is immovable fixed on casing (30) and contains monitoring and actuating devices.

EFFECT: invention provides regulation of reduction rates at established modes of driving engine and allows high coefficient of efficiency, high adjustment control area of overall gear ratio, ability of self-adaptation to influence of different external loads.

3 cl, 8 dwg

Planetary gearbox // 2324850

FIELD: transportation, trackless surface vehicles.

SUBSTANCE: invention pertains to the field of motor transport engineering and relates to staggered planetary gear box. The automatic hydro mechanical gear box consists of casing (1), input link (3), output link (4) and planetary reduction gear. In the planetary reduction gear, there are three frictional clutches and four friction brakes. The first planetary gear set consists of central gear (5), drive (6) for satellites and crown gear (7). The second planetary gear set consists of central gear (8), drive (9) for satellites and crown gear (10). The third planetary gear set consists of central gear (11), drive (12) for satellites and crown gear (13). The input link (3) is joined to rigidly interconnected drive (6) and the central gear (8). The crown gear (13) is connected to the output link (4) of the gear box. Drive (9) is connected to the control frictional clutch (15) through drive (6), which is rigidly connected to the central gear (8). Crown gear (10) is connected through the control frictional clutch (16) to drive (12), which is rigidly fixed to the central gear (5). Frictional brakes (17) joins the crown gear (7) to the casing (1) of the gear box. Frictional brakes (18) connect interconnected drive (9) and central gear (11) to the casing (1) of the gear box. Frictional brakes (19) connects the crown gear (10) to the casing (1) of the gear box. Frictional brakes (20) connects interconnected drive (12) and the central gear (5) to the casing (1) of the gearbox. This allows for enhancement of dynamic properties and broadening of the range of transmission ratios.

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

5 cl, 6 dwg

FIELD: mechanical engineering.

SUBSTANCE: proposed hydromechanical variable-speed drive has drive and driven shafts, torque converter and two planetary trains. First planetary train has epicyclical gear connected with driven shaft, sun gear, central gear connected with torque converter impeller, and carrier with two-rim planet pinions connected with driven shaft. Reactor of torque converter is connected with driven shaft. Second planetary train has epicyclical gear, sun gear and carrier with planet pinions. Epicyclical gear of first planetary train is in meshing with small rims of two-rim planet pinions. Turbine of torque converter is connected with carrier of second planetary train, and its epicyclical gear is connected with driven shaft.

EFFECT: simplified design, increased service life of engine, reduced consumption of fuel.

1 dwg

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

FIELD: transport.

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

EFFECT: smooth variation of gear ratio.

11 dwg

FIELD: machine building.

SUBSTANCE: invention relates to the movement devices based on the converter of rotational motion in progressive motion. The movement device under permanent and variable conditions based on the gear of rotation of the massive body, weight, in which the centre of weight rotation is eccentric relatively to the gear axis of rotation. In the converter of the rotation motion in the progressive motion a rod with weights rotation gear is made, at that centre of rotation of the rod periodically moves relatively the driven axis of rotation, thus ensuring the weights movement over the eccentric wheel and creation of the guiding force and device movement.

EFFECT: simplification of the device.

4 cl, 15 dwg

FIELD: transport.

SUBSTANCE: dual clutch is arranged at gearbox input with portion of clutch driven discs fitted at primary shaft and another portion fitted at tubular shaft. Gears engaged with countershaft gears are fitted on said shafts. Countershaft carries six gears, two being engaged with gears fitted on secondary shaft. Three-position clutch with reverse driven gear is arranged there between. Gear engaged with countershaft gear and three-position shift collar are fitted on countershaft tubular extension 8. Simple three-link planetary mechanism and three position clutch 35 is arranged at gearbox output side.

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: 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

Up!