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 comprises four planetary gear sets, three controlled clutches and three controlled brakes. 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). The input link (20) is connected by clutch (16) with interconnected crown gear (10) of the fourth planetary gear set and carrier (8) of the third planetary gear set. The input link (20) connected with output link (22) of hydrodynamic torque converter is connected by clutch (17) with central gear (12) of the fourth planetary gear set. The central gear (6) of the second planetary gear set is connected with the input link (20). The output link (21) connects to interconnected carrier (11) of the fourth planetary gear set and epicycle (7) of the third planetary gear set. Brake (14) connects with transmission casing (19) the interconnected crown gear (1) of the first planetary gear set and carrier (5) of the second planetary gear set. Brake (13) connects with transmission casing (19) the central gear (3) of the first planetary gear set. Brake (15) connects with transmission casing (19) the interconnected carrier (8) of the third planetary gear set and crown gear (10) of the fourth planetary gear set. Clutch (18) connects the central gear (4) of the second planetary gear set with interconnected carrier (2) of the first planetary gear set and central gear (9) of the third planetary gear set.

EFFECT: simplified design of device.

1 dwg

 

The invention relates to the field of motor engineering and concerns the design stage planetary gearbox that can be used in automatic transmissions that are managed by the electronic unit and hydraulics, and intended for vehicles.

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

The composition of an automatic transmission includes a hydrodynamic torque Converter (torque Converter), in which the kinetic energy of the working fluid is used to transmit torque from the engine crankshaft to the input element of the gearbox. Then, there is, as a rule, transmission of the planetary type, providing the change of torque on the propulsion unit and its frequency of rotation. Gearbox also includes controls, such as friction or toothed, which were divided into two groups: brakes and clutches. Couplings connect the elements of the planetary mechanism among themselves. Brake connect the elements of the planetary mechanism with the gear housing.

Known hydromechanical transmission (�atent USA No. US 7632206, published 15.12.2009) containing a hydrodynamic torque Converter, four planetary series and six controls (three brakes and three clutches), which due to the joint inclusion of the two controls on each transfer it is possible to obtain nine speeds forward; and one reverse gear.

Analysis of the development of automatic transmissions shows the desire of developers to reduce power loss during transmission from the engine to the drive wheels. One of the main factors influencing the magnitude of the losses in the gearbox, in the case of use as control elements of friction clutches and friction brakes, is the number of friction elements that are in the off state. The less of such elements, the higher the efficiency of the gearbox.

In the box-prototype gear shift is due to the pairwise inclusion of six friction controls the links of the planetary gear sets. In addition, the prototype is a permanent rigid connection of the sun gear of the first planetary series with the crankcase by means of an additional structural element, which leads to more complex structure.

The technical result for which the present invention is directed, is expanding Arsenal of technical�ical means, and also to simplify the design by reducing the number of connections, and using friction controls also reduce losses in the controls, due to the increase in the number of jointly included in each gear with the same number of planetary gear sets, as well as the number and composition used to control the friction elements.

Said technical result is achieved in that in the hydromechanical transmission containing a hydrodynamic torque Converter and planetary gearing with control elements in the form of controlled brakes and clutches, carrier of the fourth planetary series is an output element, is connected with a crown gear of the third planetary series, a sun gear of the fourth planetary gear set is connected by a clutch with a sun gear of the second planetary series, the crown gear of the fourth planetary series connected with the planet carrier of the third planetary gear set and the brake with the gear housing, carrier of the third planetary series connected coupling with the sun gear of the second planetary gear set, a sun gear of the third planetary series connected with the planet carrier of the first planetary gear set and a clutch with a crown gear of the second planetary range, carrier of the second planetary series connected with a crown gear of the first planetary gear set and brake�zoom with a gear housing, a sun gear of the second planetary series directly connected with the input element of the gearbox and is connected with the output element of the hydrodynamic torque Converter, a sun gear of the first planetary series connected brake with the transmission casing.

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

Fig.1 is a kinematic diagram of a hydromechanical nine-speed transmissions for the transmission of the vehicle.

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 provides a set of attributes.

According to the invention hydromechanical transmission includes a hydrodynamic torque Converter and planetary gearing with control elements in the form of controlled brakes and clutches, carrier of the fourth planetary series is an output element, is connected with a crown gear of the third planetary series, a sun gear of the fourth planetary gear set is connected by a clutch with a sun gear of the second planetary gear set, Coron�I gear of the fourth planetary series connected with the planet carrier of the third planetary gear set and a brake with a gear housing, carrier of the third planetary series connected coupling with the sun gear of the second planetary series, a sun gear of the third planetary series connected with the planet carrier of the first planetary gear set and a clutch with a crown gear of the second planetary range, carrier of the second planetary series connected with a crown gear of the first planetary gear set and a brake with a gear housing, a sun gear of the second planetary series directly connected with the input element of the gearbox and is connected with the output element of the hydrodynamic torque Converter, a sun gear of the first planetary series connected brake with the transmission casing.

Below is an example of specific performance hydromechanical transmission for an automatic transmission, for example, a passenger car of the raised passableness.

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

In the gearbox according to the invention, the planetary gear comprises four planetary gear sets. The first planetary radtastic of the sun gear 3, drove 2 satellites and the crown gear 1 (the epicycle). The second planetary series consists of a sun gear 6, took 5 satellites and the crown gear 4 (the epicycle). The third planetary series consists of a sun gear 9, drove 8 satellites and the crown gear 7 (the 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 by coupling 16 with related crown gear 10 of the fourth planetary series and planet carrier 8 of the third planetary gear set. Input link 20 connected with the output element 22 of the hydrodynamic torque Converter, connected to the coupling 17 with the sun gear 12 of the fourth planetary gear set. A sun gear 6 of the second planetary series connected with the input element 20. The output link 21 is connected with linked planet carrier 11 of the fourth planetary gear set and the epicycle 7 of the third planetary gear set. The brake 14 is connected with the gear housing 19 is connected between the crown gear 1 of the first planetary series and drove 5 of the second planetary gear set. The brake 13 is connected with the gear housing 19 sun gear 3 of the first planetary gear set. The brake 15 is connected with the gear housing 19 is connected between the carrier 8 of the third planetary series and the crown gear 10 odd�artigo planetary gear set. The coupling 18 connects the crown gear 4 of the second planetary gear set with linked carrier 2 of the first planetary gear set and the sun gear 9 of the third planetary gear set.

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

After the start of movement of the vehicle sequential shift gear from 1st to 9th is his acceleration to the desired speed of movement. When the gearbox is in a neutral position none of the controls are enabled.

In the first forward gear included brakes 14 and 15 and the sleeve 18, i.e., the angular velocity of the crown gear 1 of the first planetary series connected with the planet carrier 5 of the second planetary series and drove 8 of the third planetary number associated with the crown gear 10 of the fourth planetary series is equal to zero, and the angular velocity of the crown gear 4 of the second planetary gear set and a sun gear 9 of the third planetary number associated with the carrier 2 of the first planetary gear set, equal.

Torque from the input element 20 via the sun gear 6 of the second planetary number is transmitted to the crown gear 4 of the second planetary gear set. Then through the clutch 18 is transmitted to the sun gear 9 of the third planetary series and the crown gear 7 of the third PLA�eternulo series associated with the planet carrier 11 of the fourth planetary gear set directly to the output link 21.

When switching to the second forward gear, the brake 14 is turned off and the clutch 17, the brake 15 and the clutch 18 remains on. Thus, the angular speed of the carrier 8 of the third planetary number associated with the crown gear 10 of the fourth planetary series is equal to zero, and the angular velocity of the input link 20, connected with a sun gear 6 of the second planetary number equal to the angular speed of the sun gear 12 of the fourth planetary gear set. Thus the angular velocity of the crown gear 4 of the second planetary series of equal angular velocity of sun gear 9 of the third planetary number associated with the carrier 2 of the first planetary gear set.

Torque from the input element 20 via the included coupler 17 is transmitted to the sun gear 12 of the fourth planetary series and then drove 11 of the fourth planetary gear set, which is transmitted directly linked with it the output link 21.

When switching to the third forward gear off the brake 15 and turns on the brake 14, the clutches 17 and 18 remain enabled. Thus, the angular velocity of the crown gear 1 of the third planetary number associated with the planet carrier 5 of the second planetary number equal to zero, and the angular velocity of the input link 20, tie�fucking with a sun gear 6 of the second planetary gear set, equal to the angular speed of the sun gear 12 of the fourth planetary gear set. Thus the angular velocity of the crown gear 4 of the second planetary series of equal angular velocity of sun gear 9 of the third planetary number associated with the carrier 2 of the first planetary gear set.

Torque from the input element 20 via the included coupler 17 is transmitted to the sun gear 12 of the fourth planetary series and then drove 11 of the fourth planetary series, where it divides into three streams. The first stream is transmitted from the carrier 11 of the fourth planetary gear set related crown gear 7 of the third planetary series, which is transmitted at a cage 8 of the third planetary series, where combined with the second flow moving from the led 11 of the fourth planetary gear set to the crown gear 10 of the fourth planetary series connected with the planet carrier 8 of the third planetary gear set. Joined to the planet carrier 8 of the third planetary gear set, the streams are transmitted to the sun gear 9 of the third planetary gear set. Further from the sun gear 9 of the third planetary number of the flow of torque transferred through the clutch 18 of the crown gear 4 of the second planetary series, and then the sun gear 6 of the second planetary series, where combined with the flow of torque to the input element 20. A third thread torque is transmitted from the carrier 11 Thu�REGO planetary series directly connected with the output link 21.

When switching to the fourth forward gear off the clutch is 18 and turns on the brake 13, the clutch 17 and the brake 14 are included. Thus, the angular velocity of the crown gear 1 of the first planetary number associated with the planet carrier 5 of the second planetary series, and the angular speed of the sun gear 3 of the first planetary series is equal to zero. Thus the angular velocity of the input link 20, connected with a sun gear 6 of the second planetary number equal to the angular speed of the sun gear 12 of the fourth planetary gear set.

Torque from the input element 20 via the included coupler 17 is transmitted to the sun gear 12 of the fourth planetary series and then drove 11 of the fourth planetary series, where it divides into the two streams. The first thread torque is transmitted from the carrier 11 of the fourth planetary gear set crown gear 10 of the fourth planetary series connected with the planet carrier 8 of the third planetary series, where is transmitted to the crown gear 7 of the third planetary series, and then to be associated with this gear carrier 11 of the fourth planetary series, where combined with the second stream transmitted from the led 11 of the fourth planetary series directly connected with the output link 21.

When switching on the fifth forward gear off the brake 14 and incl�tsya coupling 18, the clutch 17 and the brake 13 stay on. Thus, the angular speed of the sun gear 3 of the first planetary series is equal to zero. Thus the angular velocity of the input link 20, connected with a sun gear 6 of the second planetary number equal to the angular speed of the sun gear 12 of the fourth planetary gear set, and the angular velocity of the crown gear 4 of the second planetary series of equal angular velocity of sun gear 9 of the third planetary number associated with the carrier 2 of the first planetary gear set.

Torque from the input element 20 is transmitted to the sun gear 6 of the second planetary series, where it divides into the two streams. The first stream is transmitted from the sun gear 6 of the second planetary gear set cage 5 of the second planetary number associated with the crown gear 1 of the first planetary series, where it should on the carrier 2 of the first planetary gear set. Then this flow of torque is divided and transmitted through the coupling 18 of the crown gear 4 of the second planetary series and then the cage 5 of the second planetary series, where combined with the first flow power, and also is transmitted to the sun gear 9 of the third planetary series, where from then on drove 8 of the third planetary gear set. The second thread torque is transmitted from the sun gear 6 of the second planetary gear set through the clutch 17 solar�th gear 12 of the fourth planetary series, and then the driver 11 of the fourth planetary gear set, where it divides into the two streams. The first stream is transmitted from the carrier 11 of the fourth planetary number associated with the crown gear 7 of the third planetary series driver 8 of the third planetary series, where combined with the power flow transferred to the driver 8 of the third planetary gear set sun gear 9 of the third planetary series, where it connected with the planet carrier 8 of the third planetary gear set crown gear 10 of the fourth planetary series and then drove 11 of the fourth planetary series, where combined with the second flow of power transmitted from the carrier 11 of the fourth planetary gear set directly to the output link 21.

When switching on the sixth forward gear off the brake 13 and the clutch 16, the clutches 17 and 18 remain enabled. Thus, the angular velocity of the input link 20, connected with a sun gear 6 of the second planetary number equal to the angular speed of the sun gear 12 of the fourth planetary gear set, and the angular velocity of the crown gear 4 of the second planetary series of equal angular velocity of sun gear 9 of the third planetary number associated with the carrier 2 of the first planetary gear set. Also the angular speed of the carrier 8 of the third planetary number associated with the crown gear 10 of the fourth planetary series of equal angular velocity of sun gear 6 of the WTO�CSOs planetary gear set, associated with the input link 20.

The torque on the input link 20 is divided into two streams. The first stream is transmitted through the clutch 16 driver 8 of the third planetary number associated with the crown gear 10 of the fourth planetary gear set, which is transmitted at the cage 11 of the fourth planetary gear set. The second flow of torque transmitted through the clutch 17 the sun gear 12 of the fourth planetary gear set, which is transmitted at the cage 11 of the fourth planetary series, where combined with the first flow of torque and is transmitted from the carrier 11 of the fourth planetary series directly connected with the output link 21.

When switching on the seventh forward gear off the clutch 17 and the brake will be applied 13, the clutches 16 and 18 remain enabled. Thus, the angular velocity of the crown gear 4 of the second planetary series of equal angular velocity of sun gear 9 of the third planetary number associated with the carrier 2 of the first planetary series, and the angular speed of the carrier 8 of the third planetary number associated with the crown gear 10 of the fourth planetary series of equal angular velocity of sun gear 6 of the second planetary number associated with the input link 20. Also the angular speed of the sun gear 3 of the first planetary series is equal to zero.

Torque from the input element 20 transmits�I through the clutch 16 driver 8 of the third planetary gear set, where it divides into the two streams. The first stream is transmitted from the carrier 8 of the third planetary gear set the sun gear 9 of the third planetary number associated with the carrier 2 of the first planetary series, which is transmitted at a crown gear 1 of the first planetary series connected with the planet carrier 5 of the second planetary series, where it is divided and transmitted to the crown gear 4 of the second planetary series and then through the coupling 18 is combined with the first flow of torque, and a sun gear 6 of the second planetary series, where combined with the flow of torque to the input element 20. The second thread torque is transmitted from the carrier 8 of the third planetary series through interconnected crown gear 7 of the third planetary gear set and the carrier 11 of the fourth planetary number of the output link 21.

When switching to the eighth forward gear off the clutch 18 and the brake will be applied 14, clutch 16 and the brake 13 stay on. Thus, the angular speed of the carrier 8 of the third planetary number associated with the crown gear 10 of the fourth planetary series of equal angular velocity of sun gear 6 of the second planetary number associated with the input link 20. Also the angular speed of the sun gear 3 of the first planetary gear set and the angular speed of the carrier 5 of the second planetary number associated with the crown� gear 1 of the first planetary gear set, zero.

Torque from the input element 20 is transmitted through the clutch 16 driver 8 of the third planetary series, which is transmitted through interconnected crown gear 7 of the third planetary gear set and the carrier 11 of the fourth planetary gear set connected directly with them to the output link 21.

When switching to the ninth forward gear off the brake 13 and the clutch 18, the clutch 16 and the brake 14 are included. Thus, the angular speed of the carrier 8 of the third planetary number associated with the crown gear 10 of the fourth planetary series of equal angular velocity of sun gear 6 of the second planetary number associated with the input link 20, and the angular velocity of the crown gear 4 of the second planetary series of equal angular velocity of sun gear 9 of the third planetary number associated with the carrier 2 of the first planetary gear set. Also the angular speed of the carrier 5 of the second planetary number associated with the crown gear 1 of the first planetary number of zero.

Torque from the input element 20 is transmitted to the sun gear 6 of the second planetary series, where it divides into the two streams. The first stream is transmitted from the sun gear 6 of the second planetary gear set crown gear 4 of the second planetary series and then through the coupling 18 of the sun gear 9 of the third planetary�about series where should be took 8 of the third planetary gear set. The second flow of torque through the clutch 16 is transmitted to the driver 8 of the third planetary series, where combined with the first stream and on the crown gear 7 of the third planetary series connected with the planet carrier 11 of the fourth planetary gear set, which is transmitted directly linked with them to the output link 21.

On the reverse included brakes 13 and 15 and the coupling 18. Thus, the angular speed of the sun gear 3 of the first planetary gear set and the angular speed of the carrier 8 of the third planetary number associated with the crown gear 10 of the fourth planetary series is equal to zero. Also the angular velocity of the crown gear 4 of the second planetary series of equal angular velocity of sun gear 9 of the third planetary number associated with the carrier 2 of the first planetary gear set.

The torque is transmitted from the input element 20 of the sun gear 6 of the second planetary series, which is transmitted at the cage 5 of the second planetary number associated with the crown gear 1 of the first planetary gear set. Further, the torque is transmitted from the crown gear 1 of the first planetary series driver 2 of the first planetary series, where it divides into the two streams. The first stream from the carrier 2 of the first planetary number is transmitted via the coupling 18 of the crown gear 4 of the second planet�tion number, whence it follows that on drove 5 of the second planetary series, where combined with the flow of torque, transferred to the cage 5 of the second planetary gear set sun gear 6 of the second planetary gear set. The second thread torque is transmitted from the carrier 2 of the first planetary number associated with the sun gear 9 of the third planetary series, where is transmitted to the crown gear 7 of the third planetary series connected with the planet carrier 11 of the fourth planetary gear set directly to the output link 21.

The schema change and the sequence of the joint inclusion of controls, as well as a reduction in the number of connections in comparison with the prototype allows to achieve the claimed technical result and a significant extension of the kinematic range of the gearbox, and also the fact that when you switch missing gap power. In addition, due to this it is possible to improve the dynamic characteristics of a transmission and to increase its longevity.

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 PTO�NTA and planetary reducer controls in the form of controlled brakes and clutches, in which the carrier of the fourth planetary series is an output element of the gearbox and is connected with a crown gear of the third planetary series, a sun gear of the fourth planetary gear set is connected by a clutch with a sun gear of the second planetary series, the crown gear of the fourth planetary series connected with the planet carrier of the third planetary gear set and the brake with the gear housing, carrier of the third planetary series connected coupling with the sun gear of the second planetary series, a sun gear of the third planetary series connected with the planet carrier of the first planetary gear set and a clutch with a crown gear of the second planetary gear set, carrier of the second planetary series connected with a crown gear of the first planetary gear set and a brake with a gear housing, a sun gear of the second planetary series directly connected with the input element of the gearbox and is connected with the output element of the hydrodynamic torque Converter, a sun gear of the first planetary series connected brake with the transmission casing.



 

Same patents:

FIELD: transport.

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

EFFECT: higher operating performance.

1 dwg

FIELD: transport.

SUBSTANCE: invention relates to fixed-ratio planetary transmission design. automatic transmission implementing six forward gears and two reverse gears contains casing (16), input link (13), output link (14), hydrodynamic torque converter and planetary reduction gear comprising three planetary gear sets, two controlled clutches and three controlled brakes. Planetary reduction gear consists of three 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 input link (13) is connected with central gear (6 )of the second planetary gear set and with output link (15) of hydrodynamic torque converter. The output link (14) is connected with carrier (8) of the third planetary gear set and with crown gear (1) of the first planetary gear set. Brake (12) interconnects central gear (9) of the third planetary gear set and transmission casing (16). Brake (11) connects interconnected carrier (2) of the first planetary gear set and crown gear (4) of the second planetary gear set with transmission casing (16). Brake (10) connects central gear (3) of the first planetary gear set with transmission casing (16). Clutch (18) connects central gear (3) of the first planetary gear set with interconnected carrier (5) of the second planetary gear set and crown gear (7) of the third planetary gear set. Clutch (17) connects carrier (5) of the second planetary gear set connected with crown gear (7) of the third planetary gear set with interconnected central gear (6) of the second planetary gear set, transmission input link (13) and output link (15) of hydrodynamic torque converter.

EFFECT: simplified design.

16 cl, 18 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 (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

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

FIELD: transport.

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

EFFECT: higher operating performance.

1 dwg

FIELD: transport.

SUBSTANCE: invention relates to fixed-ratio planetary transmission design. automatic transmission implementing six forward gears and two reverse gears contains casing (16), input link (13), output link (14), hydrodynamic torque converter and planetary reduction gear comprising three planetary gear sets, two controlled clutches and three controlled brakes. Planetary reduction gear consists of three 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 input link (13) is connected with central gear (6 )of the second planetary gear set and with output link (15) of hydrodynamic torque converter. The output link (14) is connected with carrier (8) of the third planetary gear set and with crown gear (1) of the first planetary gear set. Brake (12) interconnects central gear (9) of the third planetary gear set and transmission casing (16). Brake (11) connects interconnected carrier (2) of the first planetary gear set and crown gear (4) of the second planetary gear set with transmission casing (16). Brake (10) connects central gear (3) of the first planetary gear set with transmission casing (16). Clutch (18) connects central gear (3) of the first planetary gear set with interconnected carrier (5) of the second planetary gear set and crown gear (7) of the third planetary gear set. Clutch (17) connects carrier (5) of the second planetary gear set connected with crown gear (7) of the third planetary gear set with interconnected central gear (6) of the second planetary gear set, transmission input link (13) and output link (15) of hydrodynamic torque converter.

EFFECT: simplified design.

16 cl, 18 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 (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

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 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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