Hydromechanical transmission

FIELD: transport engineering.

SUBSTANCE: invention can be used in automatic transmission controlled by electronic unit and hydraulic devices. Proposed 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 sun gear 8 of second planetary train, is connected through friction clutch 18 with carrier 6 of first planetary train, and through friction clutch 17, with sun gear 5 of said train which is connected with case 1 through friction brake 19. Carrier 6 is connected with ring gear 13 of third planetary train and, through friction brake 20, with case 1. Ring gear 7 of first planetary train is coupled with carrier 9 of second planetary train and with sun gear 11 of third planetary train. Ring gear 10 of second planetary train is coupled with sun gear 14 of fourth planetary train which is coupled through friction brake 22 with case 1. Carrier 15 of fourth planetary train is coupled, through friction brake 21, with case 1. Ring gear 16 of fourth planetary train is coupled with carrier 12 of third planetary train being output link of transmission.

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

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. The transmission also includes a friction controls that its purpose can be divided into two groups: brakes and clutches. A friction clutch connecting the elements of the planetary mechanism between them. Friction brakes combine elements of the planetary mechanism with the transmission case.

Using transmission planetremote in automatic transmissions for such vehicles as cars and trucks, caterpillar equipment for military and civil purposes due to the possibility of using small-sized, compact layout design, easy to fit in the limited dimensions of the body space, but is able to transmit and convert large torques.

Currently, planetary gearbox, used for cars and trucks and tracked vehicles for military and civilian purposes and consisting of the four planetary gear sets provide five or six speeds forward. To increase the number of transmissions, for example, to retrieve the ten speeds forward, developers involved in the design and manufacture of transmissions, use or more planetary gear sets, which complicates the design of transmission, or increase the number of degrees of freedom, which complicates the control system of the transmission.

Known hydromechanical transmission containing a hydrodynamic torque Converter and planetary gear, a sun gear of the second planetary number of which is connected with the output element of a hydrodynamic torque Converter, the first planetary series has a negative internal gear ratio, and carrier of the fourth planetary OC is and is connected through a friction brake with Carter, the crown gear of the first planetary series connected with a sun gear of the third planetary series carrier of the third planetary series is an output element of the gearbox, the crown gear of the fourth planetary series connected with a sun gear of the third planetary series, the crown gear of the second planetary series connected with a sun gear of the first planetary series, drove the first planetary series is connected through a friction brake with Carter, a sun gear of the fourth planetary series connected with the planet carrier of the third planetary series, which is the output element of the gearbox, the crown gear of the third planetary series is connected through a friction clutch with an output link of a hydrodynamic torque Converter, a sun gear of the first planetary series connected through a friction clutch with a planet carrier of the third planetary series, which is the output element of the gearbox, second, third and fourth planetary alignments have positive internal gear ratio through the use of dual satellite carrier of the first planetary series connected with the planet carrier of the second planetary series (US 6039670, F 16 H 3/44, 475/275, figure 10, publ. 21.03.2000).

This transmission contains to change the relationship of torque between the input and output links of the two f actionee clutches and two brakes. In the box-prototype shifting occurs due to the pairwise inclusion of four friction controls the links of the planetary alignments. This allows you to get five speeds forward and one reverse gear.

The present invention is directed to the solution of the technical problem of increasing the number of speeds forward up to ten and range up to 10.2 when saving the kinematic scheme of a transmission with four planetary series, and simplification of the structure through the use of simple planetary gear sets with a negative internal gear ratio. Achievable technical result consists in the extension of the kinematic capabilities of the transmission while maintaining the overall performance, as well as the design becomes more sophisticated.

This technical result is achieved by the fact that in the hydromechanical transmission containing a hydrodynamic torque Converter and planetary gear, a sun gear of the second planetary number of which is connected with the output element of a hydrodynamic torque Converter, the first planetary series has a negative internal gear ratio, the crown gear of the first planetary series connected with a sun gear of the third planetary series, drove the fourth planetary series is connected through a friction brake with Carter, carrier of the third planetary series is an output element of the gearbox, the output link of the hydrodynamic torque Converter is connected through a friction clutch with a sun gear of the first planetary series, the output link of the hydrodynamic torque Converter is connected through a friction clutch with a planet carrier of the first planetary series, a sun gear of the first planetary series is connected through a friction brake with Carter, drove the first planetary series connected with a crown gear of the third planetary series, the crown gear of the third planetary series is connected through a friction brake with Carter, carrier of the second planetary number is associated with the crown gear of the first planetary series, the crown gear of the second planetary series connected with a sun gear the fourth planetary series, the crown gear of the fourth planetary series connected with the planet carrier of the third planetary series, which is the output element of the gearbox, a sun gear of the fourth planetary series is connected through a friction brake with Carter, second, third and fourth planetary alignments have negative internal gear ratio.

These characteristics are essential and interrelated with the formation of a stable population exists, is public signs, sufficient to obtain the desired technical result.

Changing the design of the planetary mechanisms and sequence of pairwise inclusion in conjunction with the known characteristics allowed us to obtain ten speeds forward and extend the range of transmission up to 10.2, and will be used in various driving modes only piece of gear without sacrificing traction. The use of planetary gear sets with a negative internal gear ratio has simplified the design and made it more sophisticated.

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.

The essence of the proposed technical solution is illustrated by a drawing, which shows a kinematic diagram of a hydromechanical step transmission for automatic transmission vehicles.

According to the invention in a hydromechanical transmission that contains a hydrodynamic torque Converter and planetary gear, a sun gear of the second planetary number of which is connected with the output element of a hydrodynamic torque Converter, the first paragraph is unitary series has a negative internal gear ratio, the crown gear of the first planetary series connected with a sun gear of the third planetary series, took fourth planetary series is connected through a friction brake with Carter, carrier of the third planetary series is an output element of the gearbox, the output link of the hydrodynamic torque Converter is connected through a friction clutch with a sun gear of the first planetary series, the output link of the hydrodynamic torque Converter is connected through a friction clutch with a planet carrier of the first planetary series, a sun gear of the first planetary series is connected through a friction brake with Carter, drove the first planetary series connected with a crown gear of the third planetary series, the crown gear of the third planetary series is connected through a friction brake with Carter, the carrier of the second planetary number is associated with the crown gear of the first planetary series, the crown gear of the second planetary series connected with a sun gear of the fourth planetary series, the crown gear of the fourth planetary series connected with the planet carrier of the third planetary series, which is the output element of the gearbox, a sun gear of the fourth planetary series is connected through a friction brake with Carter, second, third, and fourth against the s series have negative internal gear ratio.

Below is an example of a specific implementation of the hydro-mechanical transmission for an automatic transmission, for example, a car or truck.

Hydromechanical step transmission contains a crankcase 1, a hydrodynamic torque Converter 2 (torque Converter), the input link 3, the output link 4 and the planetary gear, which includes a planetary alignments, two friction clutches and four friction brakes.

In the gearbox according to the invention, the planetary gear consists of four planetary series. The first planetary series consists of a sun gear 5, drove 6 satellites and the crown gear 7 (epicycle). The second planetary series consists of a sun gear 8, drove 9 satellites and the crown gear 10 (epicycle). The third planetary series consists of a sun gear 11, led 12 satellites and the crown gear 13 (epicycle). The fourth planetary series consists of a sun gear 14, pinion carrier 15 of the satellites and the crown gear 16 (epicycle). Input link 3 is connected by the friction coupling 17 with the sun gear 5 of the first planetary series. Input link 3 is connected by a slip clutch 18 with the planet carrier 6 of the first planetary series.

The sun gear 5 of the first planetary series is connected with the crankcase 1 gearbox friction Thor is 19 oz. The friction brake 20 is connected with the crankcase 1 gearbox connected drove 6 of the first planetary series and the crown gear 13 of the third planetary series. The friction brake 21 connects the pinion carrier 15 of the fourth planetary series with Carter 1 gearbox. Interconnected sun gear 14 of the fourth planetary series and crown gear 10 of the second planetary series connected with the crankcase 1 gearbox friction brake 22.

This embodiment of the transmission in comparison with the known transmissions, consisting of four rows of type HYUNDAY and others, allows you to get ten speeds forward and one reverse gear, using the four planetary series and six friction controls, as well as using only the planetary series with negative internal gear ratio.

Equipment gearbox ten speeds forward allowed to make changes in gear ratio and the order of the pairwise inclusion friction controls. Changing the design and parameters of sun gears, carriers, satellites and planetary gears series has allowed to expand the range of transmission up to 10.2, and will be used in various driving modes only piece of gear without sacrificing traction./p>

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

After the start of vehicle motion serial shift from 1st to 10th is the vehicle accelerates to the desired speed. When the transmission is in the neutral position, neither of friction controls are not enabled.

In first gear includes a brake 20 and the brake 21, i.e. the angular velocity is rigidly connected or made integral drove 6 of the first planetary series and the crown gear 13 of the third planetary series is equal to zero, and the angular speed of the carrier 15 of the fourth planetary series is equal to zero.

Torque from the input element 3 is transmitted to the sun gear 8 of the second planetary series, then is transmitted to the carrier 9 of the second planetary series, which is divided, and through the crown gear 10 of the second planetary series and rigidly associated sun gear 14 of the fourth planetary number is transmitted to the crown gear 16 of the fourth planetary series, and through the sun gear 11 of the third planetary series on carrier 12 of the third planetary series. Flows with the carrier 12 of the third planetary series and the crown gear 16 of the fourth planetary series are combined on the output link 4.

When the switch is and the second transfer switches off the brake 20 and turns on the brake 19, the brake 21 is on. Thus, the angular speed of the carrier 15 of the fourth planetary series is equal to zero, and the angular speed of the sun gear 5 of the first planetary series is equal to zero.

Torque from the input element 3 is transmitted to the sun gear 8 of the second planetary series, then drove 9 of the second planetary range where it is divided into three streams. The first stream with the carrier 9 of the second planetary number is transmitted to the sun gear 11 of the third planetary series. The second stream through the crown gear 7 of the first planetary number is transmitted to the carrier 6 of the first planetary series and rigidly connected with him the crown gear 13 of the third planetary series. The third stream through the crown gear 10 of the second planetary series and rigidly associated sun gear 14 of the fourth planetary number is transmitted to the crown gear 16 of the fourth planetary series. Threads formed on the driver 12 of the third planetary series and rigidly associated crown gear 16 of the fourth planetary number associated with the output link 4.

When you switch to third gear off the brake 21 and the brake 19 and included the brake 20 and the brake 22. Thus, the angular velocity is rigidly connected or made integral drove 6 of the first planetary series and the crown gear 13 of the third paragraph is unitarnoe number equal to zero, as well as the angular velocity is rigidly connected or made integral crown gear 10 of the second planetary series, and a sun gear 14 of the fourth planetary series is equal to zero.

Torque from the input element 3 is transmitted to the sun gear 8 of the second planetary series, further rigidly connected drove 9 of the second planetary series, and the sun gear 11 of the third planetary series, and with her took 12 of the third planetary series and the associated output link 4.

When switching to the fourth transfer off the brake 20 and 22, includes a coupling 17 and the brake 21. Thus, the angular speed of the carrier 15 of the fourth planetary series is equal to zero, and the angular velocity of the input link 3 and is rigidly connected him the sun gear 8 of the second planetary number equal to the angular speed of the sun gear 5 of the first planetary series.

Torque from the input element 3 is divided and enabled through the friction coupling 17 is transmitted to the sun gear 5 of the first planetary series, then drove 6 of the first planetary series, and is transmitted to the sun gear 8 of the second planetary series and later on took 9 of the second planetary series. On the drive rod 6 of the first planetary series torque split and through the crown gear 7 of the first planetary number is transmitted to the pinion carrier of the second planetary series as well as through the crown gear 13 of the third planetary number is transmitted to the carrier 12 of the third planetary series, which splits it into two streams. The first is transmitted to the sun gear 11 of the third planetary series and rigidly connected with it took 9 of the second planetary series. On the drive rod 9 of the second planetary series combined flows from the crown gear 7 of the first planetary series, the sun gear 8 of the second planetary series, and a sun gear 11 of the third planetary series and is transmitted through the crown gear 10 of the second planetary series on the sun gear 14 of the fourth planetary series and forth on the crown gear 16 of the fourth planetary series. The second stream with the carrier 12 of the third planetary series and with the crown gear 16 of the fourth planetary series are combined on the output link 4.

When switching to another gear off the clutch 17 and the brake 21, and turns on the brake 19 and the brake 22. Thus, the angular speed of the sun gear 5 of the first planetary series is zero and angular velocity is rigidly connected or made integral crown gear 10 of the second planetary series, and a sun gear 14 of the fourth planetary series is equal to zero.

Torque from the input element 3 is transmitted to the sun gear 8 of the second planetary series, then drove 9 the second is planetarnogo series which is divided, and through the crown gear 7 of the first planetary number is transmitted to the carrier 6 of the first planetary series and rigidly connected with him the crown gear 13 of the third planetary series, as well as on the sun gear 11 of the third planetary series. Threads formed on the driver 12 of the third planetary series, and its associated output link 4.

When switching on the sixth transfer off the brake 22 and the brake 19 and included the brake 21 and the coupling 18. Thus, the angular speed of the carrier 15 of the fourth planetary series is equal to zero, and the angular velocity of the input link 3 and is rigidly associated sun gear 8 of the second planetary series of equal angular velocity rigidly interconnected or performed at the same time took 6 of the first planetary series and the crown gear 13 of the third planetary series.

Torque from the input element 3 is divided and enabled through the friction clutch 18 is betrayed on the carrier 6 of the first planetary series and rigidly connected with him the crown gear 13, and is transmitted to the sun gear 8 of the second planetary series, which through the crown gear 10 of the second planetary number is transmitted to the sun gear 14 of the fourth planetary series and forth on the crown gear 16 of the fourth planetary series. The flow of torque with the crown gear 1 of the third planetary number is transmitted to the carrier 12 of the third planetary series where is split, and through the sun gear 11 of the third planetary number is transmitted to the carrier 9 of the second planetary series. The second stream with the carrier 12 of the third planetary series and with the crown gear 16 of the fourth planetary series are combined on the output link 4.

When switching on the seventh transfer off the brake 21 and the clutch 18 and includes the brake 22 and the clutch 17. Thus, the angular velocity is rigidly connected or made integral crown gear 10 of the second planetary series, and a sun gear 14 of the fourth planetary series is equal to zero, and the angular velocity of the input link 3 and is rigidly associated sun gear 8 of the second planetary number equal to the angular speed of the sun gear 5 of the first planetary series.

Torque from the input element 3 is divided and transmitted to the sun gear 8 of the second planetary series and later on took 9 of the second planetary happy, and enabled through the friction coupling 17 is transmitted to the sun gear 5 of the first planetary series, then drove 6 of the first planetary series. On the drive rod 9 of the second planetary series is divided and transmitted to the crown gear 7 of the first planetary series, as well as on the sun gear 11 of the third planetary series. On the drive rod 6 of the first planetary series combined flows of torque with Sol is echnol gear 5 of the first planetary series and the crown gear 7 of the first planetary number and passed on the crown gear 13 of the third planetary series. Threads formed on the driver 12 of the third planetary series, and its associated output link 4.

When switching on the eighth transmission is turned off, the clutch 17, and enables coupling 18, the brake 22 is on. Thus, the angular velocity is rigidly connected or made integral crown gear 10 of the second planetary series, and a sun gear 14 of the fourth planetary series is equal to zero, and the angular velocity of the input link 3 and is rigidly associated sun gear 8 of the second planetary series of equal angular velocity rigidly connected or made integral drove 6 of the first planetary series and the crown gear 13 of the third planetary series.

Torque from the input element 3 is divided and enabled through the friction clutch 18 is transmitted to rigidly associated drove 6 of the first planetary series and the crown gear 13 of the third planetary series, as well as on the sun gear 8 of the second planetary series, then drove through 9 of the second planetary series on the sun gear 11 of the third planetary series. Threads formed on the driver 12 of the third planetary series, and its associated output link 4.

When switching on the ninth transmission is switched off, the brake 22 and turns on the coupling 18, the clutch 17 is on. Thus, the angular velocity of the input link 3 and rigidly include the Noah with him the sun gear 8 of the second planetary number equal to the angular speed of the sun gear 5 of the first planetary series and the angular velocity of the input link 3 and is rigidly associated sun gear 8 of the second planetary series of equal angular velocity rigidly connected or made integral drove 6 of the first planetary series and the crown gear 13 of the third planetary series.

Torque from the input element 3 through the clutch 18 is transmitted to the carrier 6 of the first planetary range where it is divided into three streams. The first flow of torque from the carrier 6 of the first planetary number is transmitted to the sun gear 5 of the first planetary series and then through the clutch 17 on the input link 3. The second thread torque is transmitted to the crown gear 13 of the third planetary series. A third thread torque is transmitted to rigidly associated crown gear 7 of the first planetary series, and the sun gear 11 of the third planetary series. Threads formed on the driver 12 of the third planetary series, and its associated output link 4.

When switching on the tenth transmission is turned off, the clutch 17 and activates the brake 19, the clutch 18 is on. Thus, the angular speed of the sun gear 5 of the first planetary series is equal to zero, and the angular velocity of the input link 3 and is rigidly associated sun gear 8 of the second planetary series of equal angular velocity rigidly connected or made integral is of Odil 6 of the first planetary series and the crown gear 13 of the third planetary series.

Torque from the input element 3 is switched on via the friction clutch 18 is transmitted to the carrier 6 of the first planetary series, where it is divided and transmitted to the crown gear 13 of the third planetary series, as well as through the crown gear 7 of the first planetary number is transmitted to the sun gear 11 of the third planetary series. Threads formed on the driver 12 of the third planetary series, and its associated output link 4.

On the reverse gear activated brake 20 and the clutch 17, i.e. the angular velocity is rigidly connected or made integral drove 6 of the first planetary series and the crown gear 13 of the third planetary series is equal to zero, and the angular velocity of the input link 3 and is rigidly associated sun gear 8 of the second planetary number equal to the angular speed of the sun gear 5 of the first planetary series.

Torque from the input element 3 through the clutch 17 is transmitted to the sun gear 5 of the first planetary series, with her on the crown gear 7 of the first planetary series and rigidly associated sun gear 11 of the third planetary series. The sun gear 11 of the third planetary series torque is transmitted to the carrier 12 of the third planetary series and the associated output link 4.

The present invention allows transmissions with four PLA is Yarnykh series provides five speeds forward, to organize ten speeds forward without increasing the number of planetary alignments and increasing the degree of freedom of the transmission. The use of planetary gear sets with a negative internal gear ratio has simplified the design and made it more sophisticated.

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

Hydromechanical transmission containing a hydrodynamic torque Converter and planetary gear, a sun gear of the second planetary number of which is connected with the output element of a hydrodynamic torque Converter, the first planetary series has a negative internal gear ratio, the crown gear of the first planetary series connected with a sun gear of the third planetary series, took fourth planetary series is connected through a friction brake with Carter, carrier of the third planetary series is an output element of the gearbox, characterized in that the output link of the hydrodynamic torque Converter is connected through friction the clutch to the sun gear of the first planetary series the output link of the hydrodynamic torque Converter is connected through a friction clutch with a planet carrier of the first planetary series, a sun gear of the first planetary series is connected through a friction brake with Carter, drove the first planetary series connected with a crown gear of the third planetary series, the crown gear of the third planetary series is connected through a friction brake with Carter, carrier of the second planetary number is associated with the crown gear of the first planetary series, the crown gear of the second planetary series connected with a sun gear of the fourth planetary series, the crown gear of the fourth planetary series connected with the planet carrier of the third planetary series, which is the output element of the gearbox, a sun gear of the fourth planetary series connected through a friction brake with Carter, second, third and fourth planetary alignments have negative internal gear ratio.



 

Same patents:

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. Output link of torque converter is coupled with sun gear 8 of second planetary train, is connected through friction clutch 18 with carrier 12 of third planetary train and through friction clutch 17, with gear 11 of this train which is connected with case 1 through friction brake 22. Sun gear 5 of first planetary train is connected with case 1 through friction brake 19. Ring gear 10 of second planetary train is coupled with carrier 6 of first planetary train and through friction brake 20, with case 1. Ring gear 7 of first planetary train is coupled with carrier 9 of second planetary train and with rings gears 13 and 16 of third and fourth planetary gear trains. 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 gear train is output link of transmission.

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

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.

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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. Output link of torque converter is coupled with sun gear 8 of second planetary train, is connected through friction clutch 18 with carrier 12 of third planetary train and through friction clutch 17, with gear 11 of this train which is connected with case 1 through friction brake 22. Sun gear 5 of first planetary train is connected with case 1 through friction brake 19. Ring gear 10 of second planetary train is coupled with carrier 6 of first planetary train and through friction brake 20, with case 1. Ring gear 7 of first planetary train is coupled with carrier 9 of second planetary train and with rings gears 13 and 16 of third and fourth planetary gear trains. 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 gear train is output link of transmission.

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

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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.

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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

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. Output link of torque converter is coupled with sun gear 8 of second planetary train, is connected through friction clutch 18 with carrier 12 of third planetary train and through friction clutch 17, with gear 11 of this train which is connected with case 1 through friction brake 22. Sun gear 5 of first planetary train is connected with case 1 through friction brake 19. Ring gear 10 of second planetary train is coupled with carrier 6 of first planetary train and through friction brake 20, with case 1. Ring gear 7 of first planetary train is coupled with carrier 9 of second planetary train and with rings gears 13 and 16 of third and fourth planetary gear trains. 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 gear train is output link of transmission.

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

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