Hydromechanical transmission

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

 

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.

The use of planetary gearboxes the IPA in automatic transmissions of vehicles as cars and trucks, caterpillar equipment for military and civil purposes due to the possibility of using small compact plant 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 seven or eight speeds forward, developers involved in the design and manufacture of automatic 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, and a sun gear of the fourth planetary series through actiony brake - with Carter, the crown gear of the third planetary number associated with the crown gear of the fourth planetary series, took fourth planetary series is an output element of the gearbox. Carrier of the first planetary series is connected through a friction brake with Carter, the crown gear of the first planetary series connected with the planet carrier of the second planetary range, carrier of the second planetary series connected with the planet carrier of the third planetary series, a sun gear of the first planetary number associated with the crown gear of the second planetary series, a sun gear of the third planetary series connected with the planet carrier of the fourth planetary series, which is the output element of the gearbox, the crown gear of the second planetary series is connected through a friction clutch with a crown gear of the third planetary series, the crown gear of the second planetary series is connected through a friction clutch with a planet carrier of the fourth planetary series, which is the output link boxes gear, the first planetary series has a negative internal gear ratio, and the second, third and fourth planetary alignments - positive due to the use of dual satellites (US, 6117039, F 16 H 57/08, 475/284, Fig, 12.09.2000).

This transmission contains to change the relationship of torque between vhodni and output links of the two friction clutches and two brakes. In the box - prototype shifting occurs due to the pairwise inclusion of four friction controls the links of the planetary gear sets.

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 6,286 while maintaining the kinematic scheme of a transmission with four planetary series, and simplify the design 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, and a sun gear of the fourth planetary series through friction brake with Carter, the first planetary series has a negative internal gear ratio, corona pole is nya third planetary number associated with the crown gear of the fourth planetary series carrier of the fourth planetary series is an output link transmission, a sun gear of the first planetary series is connected through a friction brake with Carter, and the crown gear of the first planetary series connected with the output element of a hydrodynamic torque Converter, carrier of the first planetary series connected with the planet carrier of the second planetary series, the crown gear of the second 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, the output link of the hydrodynamic torque Converter is connected through a friction clutch with a sun gear of the third planetary series, a sun gear of the third planetary series is connected through a friction brake with Carter, the crown gear of the third planetary series connected with the planet carrier of the second planetary range, the output link of the hydrodynamic torque Converter is connected through a friction clutch with a planet carrier of the third planetary series, second, third and fourth planetary alignments have negative internal gear ratio.

These characteristics are essential and interrelated with the formation of a stable set of essential features, enough is 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 increase the number of gears to ten and to expand the range of transmission up to 6,286, 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 simplified the design. 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, and a sun gear of the fourth planetary series through the clutch the first brake with Carter, the first planetary series has a negative internal gear ratio, the crown gear of the third planetary number associated with the crown gear of the fourth planetary series, took fourth planetary series is an output link transmission, a sun gear of the first planetary series is connected through a friction brake with Carter, and the crown gear of the first planetary series connected with the output element of a hydrodynamic torque Converter, carrier of the first planetary series connected with the planet carrier of the second planetary series, the crown gear of the second 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, the output link of the hydrodynamic the torque Converter is connected through a friction clutch with a sun gear of the third planetary series, a sun gear of the third planetary series is connected through a friction brake with Carter, the crown gear of the third planetary series connected with the planet carrier of the second planetary range, the output link of the hydrodynamic torque Converter is connected through a friction clutch with a planet carrier of the third planetary series, second, third and fourth planetary alignments have the negative the positive 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 planet carrier 12 of the third planetary series. Input link 3 is connected by a slip clutch 18 with a sun gear 11 of the third planetary series.

The sun gear 5 of the first planetary series is connected with the crankcase 1 gearbox friction t is mosom 19. The friction brake 20 is connected with the crankcase 1 gearbox crown gear 10 of the second planetary series. The friction brake 21 connects the sun gear 14 of the fourth planetary series with Carter 1 gearbox. The sun gear 11 of the third planetary series is 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 five speeds forward and one reverse gear, using the four planetary series and six friction controls, and using only the planetary series with negative internal gear ratio. Equipment transmission with eight 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 6,286, and will be used in various driving modes only piece of gear without sacrificing traction characteristics.

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

After the beginning of motion is the vehicle serial shifting 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, that is, the angular velocity of the crown gear 10 of the second planetary series is zero and angular velocity is rigidly interconnected or performed at the same time took 12 of the third 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 transmitted to rigidly interconnected carrier 9 of the second planetary series, the crown gear 13 of the third planetary series and the crown gear 16 of the fourth planetary series. With the crown gear 16 of the fourth planetary series torque is transmitted to the pinion carrier 15 of the fourth planetary series and the associated output link 4.

When switching to the second transfer switches off the brake 21 and turns on the brake 22, the brake 20 is on. Thus, the angular speed of the sun gear 11 of the third planetary series is zero and angular velocity is rigidly interconnected or performed at the same time took 6 of the first planetary series and the crown gear 10 of the second planetary series is equal to zero.

Torque from the input element 3 is transmitted to the sun is esterno 8 of the second planetary series next is transmitted to rigidly interconnected carrier 9 of the second planetary series and the crown gear 13 of the third planetary series, which is divided and transmitted to the carrier 12 of the third planetary series and rigidly associated with the sun gear 14 of the fourth planetary series, and on the crown gear 16 of the fourth planetary series. The streams are combined at the driver 15 of the fourth planetary series, and its associated output link 4.

When you switch to third gear off the brake 22 and turns on the coupling 18, the brake 20 is on. Thus, the angular velocity rigidly interconnected or performed at the same time took 6 of the first planetary series and the crown gear 10 of the second planetary series is equal to zero, and the angular velocity of the input link 3 is equal to the angular speed of the sun gear 11 of the third planetary series.

Torque from the input element 3 is divided and enabled through the friction clutch 18 is transmitted to the sun gear 11 of the third planetary series, and the sun gear 8 of the second planetary series, which is transmitted to the associated carrier 9 of the second planetary series and the crown gear 13 of the third planetary series. On the crown gear 13 of the third planetary series torque is divided and transmitted to the crown gear 16 fourth PLA is eternulo series and, connecting to the driver 12 of the third planetary series with the flow going with a sun gear 11 of the third planetary number, is transmitted to the sun gear 14 of the fourth planetary series. The streams are combined at the driver 15 of the fourth planetary series, and its associated output link 4.

When switching to the fourth transfer off the brake 20 and the sleeve 18 and includes a brake 19 and the brake 21. Thus, the angular speed of the sun gear 5 of the first planetary series is zero and angular velocity is rigidly interconnected or performed at the same time took 12 of the third 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 crown gear 7 of the first planetary series, then drove 6 of the first planetary series, which is transmitted to rigidly associated drove 9 of the second planetary series, the crown gear 13 of the third planetary series and the crown gear 16 of the fourth planetary series. With the crown gear 16 of the fourth planetary series torque is transmitted to the pinion carrier 15 of the fourth planetary series and the associated output link 4.

When switching to another gear off the brake 19 and the brake 21 and includes the brake 20 and the clutch 17. Thus, the angular velocity of the crown gear 10 of the second planets is REGO number equal to zero, and the angular velocity of the input link 3 is equal to the angular velocity rigidly interconnected or performed at the same time took 12 of the third planetary series, and a sun gear 14 of the fourth planetary series.

Torque from the input element 3 is divided and enabled through the friction coupling 17 is betrayed on the carrier 12 of the third planetary series and rigidly associated sun gear 14 of the fourth planetary series, and the sun gear 8 of the second planetary, then transmitted to rigidly interconnected carrier 9 of the second planetary series, the crown gear 13 of the third planetary series and the crown gear 16 of the fourth planetary series. The streams are combined at the driver 15 of the fourth planetary series, and its associated output link 4.

When switching on the sixth transfer off the brake 20 and the clutch 17 and included the brake 19 and the brake 22. Thus, the angular speed of the sun gear 5 of the first planetary series is equal to zero, and the angular speed of the sun gear 11 of the third planetary series is equal to zero.

Torque from the input element 3 is transmitted to the crown gear 7 of the first planetary series, further rigidly connected drove 6 of the first planetary series, the crown gear 13 of the third planetary series and the crown gear 16 of the fourth planetary series. Crown the gear 13 of the third planetary series torque through the led 12 of the third planetary number is transmitted to the sun gear 14 of the fourth planetary series. Flows with the crown gear 16 of the fourth planetary series, and a sun gear 14 of the fourth planetary series are combined on the driver 15 of the fourth planetary series, and its associated output link 4.

When switching on the seventh transmission is switched off, the brake 22 and turns on the coupling 18, the brake 19 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 is equal to the angular speed of the sun gear 11 of the third planetary series.

Torque from the input element 3 is divided and enabled through the friction clutch 18 is transmitted to the sun gear 11 of the third planetary series, and on the crown gear 7 of the first planetary series. With the crown gear 7 of the first planetary series torque is transmitted to rigidly associated drove 6 of the first planetary series, took 9 of the second planetary series, the crown gear 13 of the third planetary series and on the crown gear 16 of the fourth planetary series. With the crown gear 13 of the third planetary series flow of torque is transmitted to the carrier 12 of the third planetary series, where, mingling with the stream from the sun gear 11 of the third planetary number, is transmitted to the sun gear 14 of the fourth planetary series. Flows with the crown gear 16 fourth the CSOs planetary series, and a sun gear 14 of the fourth planetary series are combined on the driver 15 of the fourth planetary series, and its associated output link 4.

When switching on the eighth transmission is turned off, the clutch 18 and turns on the clutch 17, the brake 19 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 are equal angular velocity equal to the angular velocity rigidly interconnected or performed at the same time took 12 of the third planetary series, and a sun gear 14 of the fourth planetary series.

Torque from the input element 3 is divided and transmitted to the crown gear 7 of the first planetary series, and also enabled through the friction coupling 17 is transmitted to the carrier 12 of the third planetary series and rigidly connected with him the sun gear 14 of the fourth planetary series. With the crown gear 7 of the first planetary series torque is transmitted to rigidly associated drove 6 of the first planetary series, took 9 of the second planetary series, the crown gear 13 of the third planetary series and the crown gear 16 of the fourth planetary series. The streams are combined at the driver 15 of the fourth planetary series, and its associated output link 4.

When switching on the ninth transmission is switched off, the brake 19, and enables coupling 18, the clutch 17 is on. Thus, the angular velocity of the input link 3 is equal to the angular velocity rigidly interconnected or comply with the data at the same time took 12 of the third planetary series, and a sun gear 14 of the fourth planetary series and the angular velocity of the input link 3 is equal to the angular speed of the sun gear 11 of the third planetary series.

Torque from the input element 3 is switched on via the friction coupling 17 is betrayed by rigidly associated carrier 12 of the third planetary range where it is divided into three streams. The first thread torque transmitted to the sun gear 11 of the third planetary series, and then through the clutch 17 and 18 on the carrier 12 of the third planetary series. The second flow of torque through the crown gear 13 of the third planetary number is transmitted to the crown gear 16 of the fourth planetary series. The third flow of torque from the carrier 12 of the third planetary number is transmitted to the sun gear 14 of the fourth planetary series. The second and third streams are combined on the driver 15 of the fourth planetary series, and its associated output link 4.

When switching on the tenth transmission is turned off, the clutch 18 and turns on the brake 22, the clutch 17 is on. Thus, the angular velocity of the input link 3 are equal angular velocity equal to the angular velocity rigidly interconnected or performed at the same time took 12 of the third planetary series, and a sun gear 14 of the fourth planetary series, and the angular speed of the sun gear 11 of the third planetary glad equal to zero.

Torque from the input frame link guides the 3 is switched on via the friction coupling 17 is betrayed on the carrier 12 of the third planetary series where it is divided and transmitted to the sun gear 14 of the fourth planetary series, and through the crown gear 13 of the third planetary number is transmitted to the crown gear 16 of the fourth planetary series. The streams are combined at the driver 15 of the fourth planetary series, and its associated output link 4.

On the reverse gear includes a clutch 18 and the brake 21, that is, the angular velocity of the input link 3 is equal to the angular speed of the sun gear 11 of the third planetary series, and the angular velocity rigidly interconnected or performed at the same time took 12 of the third planetary series, and a sun gear 14 of the fourth planetary series is equal to zero.

Torque from the input element 3 through the clutch 18 is transmitted to the sun gear 11 of the third planetary series, with her crown gear 13 of the third planetary series and rigidly associated with the crown gear 16 of the fourth planetary series. With the crown gear 16 of the fourth planetary series torque is transmitted to the pinion carrier 15 of the fourth planetary series and the associated output link 4.

The present invention allows transmissions having four planetary series provides five speeds forward, to organize ten speeds forward without increasing the number of planetary alignments and increasing the degree of freedom is s transmission. The use of planetary gear sets with a negative internal gear ratio simplified the design. 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, and a sun gear of the fourth planetary series through friction brake with Carter, the crown gear of the third planetary number associated with the crown gear of the fourth planetary series, took fourth planetary series is an output element of the gearbox, the first planetary series has a negative internal gear, wherein the sun gear of the first planetary series is connected through a friction brake with Carter, and the crown gear of the first planetary number associated with the output link of the hydrodynamic torque Converter, carrier of the first planetary number associated with dilam second planetary series the crown gear of the second 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, the output link of the hydrodynamic torque Converter is connected through a friction clutch with a sun gear of the third planetary series, a sun gear of the third planetary series is connected through a friction brake with Carter, the crown gear of the third planetary series connected with the planet carrier of the second planetary range, the output link of the hydrodynamic torque Converter is connected through a friction clutch with a planet carrier of the third planetary series, second, third and fourth planetary alignments have negative internal gear ratio.



 

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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.

1 dwg

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

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 gear ratio output link of torque converter is coupled with sun gear 8 of second planetary trains and is connected through friction clutch 17 with carrier 6 of first planetary train. Carrier 6 is coupled with sun gear 14 of fourth planetary train and, through friction brake 21, with case 1. Sun gear 5 of first planetary train is coupled with case 1 through friction brake 20. Ring gear 10 of second planetary train is connected through friction brake 19 with case 1 and through friction clutch 18, with carrier 12 of third planetary train. Carrier of 9 of second planetary train is coupled with sun gear 11 of third planetary train. Ring gear 13 of third planetary train is coupled with carrier 15 of fourth planetary train which is coupled with case through friction brake 22. Ring gear 7 of first planetary train is connected with ring gear 16 of fourth planetary train and with carrier 12 of third planetary train which is coupled link of transmission.

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

1 dwg

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