# Hydromechanical transmission

FIELD: transport engineering.

SUBSTANCE: invention relates to planetary transmission used in vehicle automatic transmission systems. Proposed hydromechanical transmission with six forward speeds and two reverse speeds has case 1, torque converter 2, input member 3, output member 4 and planetary reduction gear, two friction clutches and four friction brakes. Planetary reduction gear consists of three planetary gear trains. First planetary gear train consists of sun gear 5, planet pinion carrier 6 and crown gear 7. Second planetary gear train consists of sun gear 8, planet pinion carrier 9 and crown gear 10. Third planetary gear train consists of sun gear 11, planet pinion carrier 12 and crown gear 13. Carrier of second planetary gear train is connected by friction clutch 14 with input member 3. Input member 3 is connected by friction clutch 15 with sun gear 5 of first planetary gear train. Crown gear 7 of first planetary gear train is coupled with input member 3. Sun gear 5 of first planetary gear train is connected with case 1 by friction brake 16. Friction brake 17 connects intercoupled carrier 6 of first planetary gear train crown gear 13 of third planetary gear train and sun gear 8 of second planetary gear train with case 1. Friction brake 18 connects sun gear 11 of third planetary gear train with case 1. Friction brake 19 connects intercoupled carrier 9 of second planetary gear train and carrier 12 of third planetary gear train with case 1.

EFFECT: enlarged kinematic capabilities, increased service life of transmission.

5 cl, 7 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 housing. The use of planetary gearboxes type automatic transmissions of vehicles due to the possibility of obtaining a small-sized compact layout design, easy to fit in the limited dimensions of the body space.

Currently, planetary gearbox, used vehicles and providing six speeds forward and one back, include three planetary series, six friction controls and freewheel. However, such schemes do not implement dynamic performance requirements for vehicles, reduce the kinematic capabilities of the gearbox, reducing its durability. The use of freewheel clutches affects the weight and dimensions of the gearbox, makes the shift control more difficult. To improve the dynamic characteristics of the developers involved in the design and manufacture of automatic transmissions, use the fourth planetary line, which complicates the design of transmission, or increase the number of degrees of freedom. This leads to increased friction controls that are necessary to enable transmission, which, in turn, leads to the complication of the control system.

Known hydromechanical transmission containing a hydrodynamic torque Converter and a planetary gear carrier of the first planetary series is associated friction brake is zoom and freewheel with the transmission housing, the crown gear of the second planetary series is an output element of the gearbox, the output element of a hydrodynamic torque Converter connected friction-controlled clutch with a sun gear of the first planetary series carrier of the third planetary series connected with the planet carrier of the second planetary range, carrier of the second planetary number associated friction brake and freewheel with a transmission housing, a sun gear of the first planetary number associated friction brake with the transmission output element of a hydrodynamic torque Converter connected friction-controlled clutch with the planet carrier of the third planetary series slip-controlled clutch to the sun gear of the third planetary series, a sun gear of the second planetary series connected with a crown gear of the first planetary series, the crown gear of the first planetary series is equipped with a friction brake for its connection with the transmission housing (EP 1118798 A2, F 16 H 3/66, from 10.01.2001 year).

This transmission contains to change the relationship of torque between the input and output links of the three friction clutches and three brakes, and three freewheel. In the box-prototype shifting occurs due to the pairwise inclusion pole is friction controls the links of the planetary alignments. This allows you to get six speeds forward and one reverse gear.

The present invention is directed to the solution of the technical problem to improve the dynamic characteristics of the vehicle and increase reverse gears up to two. Achievable technical result consists in the extension of the kinematic capabilities of the gearbox, increase its durability, and also allows you to greatly expand the number of types of vehicles, which can accommodate the transmission of such kinematic scheme. Waiver of freewheel clutches improves weight and dimensions of the gearbox, makes the shift control is simpler.

This technical result is achieved by the fact that in the hydromechanical transmission containing a hydrodynamic torque Converter and a planetary gear carrier of the first planetary series is associated friction brake with the transmission housing, the crown gear of the second planetary series is an output element of the gearbox, the output element of a hydrodynamic torque Converter connected friction-controlled clutch with a sun gear of the first planetary series carrier of the third planetary series connected with the planet carrier of the second PLA is eternulo series carrier of the second planetary number associated friction brake with the transmission housing, a sun gear of the first planetary number associated friction brake with the transmission output element of a hydrodynamic torque Converter connected friction-controlled clutch with the planet carrier of the second planetary series, a sun gear of the third planetary series is equipped with a friction brake for its connection with the transmission housing, carrier of the first planetary series is associated with the crown gear of the third planetary series, the output element of a hydrodynamic torque Converter connected with the crown gear of the first planetary series, a sun gear of the second planetary number associated with the crown gear of the third planetary series.

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

Compound sun gear of the third planetary series through friction driven clutch with the planet carrier of the third planetary series allowed us to obtain seven speeds forward and two reverse gears.

The connection of the crown gear of the third planetary series through friction driven clutch what Odil third planetary series allowed us to obtain seven speeds forward and two reverse gears.

Compound sun gear of the third planetary series through friction driven clutch with a crown gear of the third planetary series allowed us to obtain seven speeds forward and two reverse gears.

The connection of the crown gear of the second planetary series through friction driven clutch with the planet carrier of the second planetary series allowed us to obtain seven speeds forward and two reverse gears.

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 drawings, where

figure 1 shows the kinematic diagram of the six-speed hydromechanical transmission for a vehicle transmission with two reverse gears;

figure 2 - plan of angular velocities six-speed hydromechanical transmission for a vehicle transmission with two reverse gears;

figure 3 is a kinematic diagram of the seven-speed hydromechanical transmission for a vehicle transmission with two reverse gears;

figure 4 is a kinematic diagram of a hydromechanical seven-step the ATA transmission for a vehicle transmission with two reverse gears;

figure 5 is a kinematic diagram of the seven-speed hydromechanical transmission for a vehicle transmission with two reverse gears;

figure 6 is a kinematic diagram of the seven-speed hydromechanical transmission for a vehicle transmission with two reverse gears;

figure 7 - plan of angular velocities seven-speed hydromechanical transmission for a vehicle transmission with two reverse gears.

According to the invention hydromechanical transmission containing a hydrodynamic torque Converter and a planetary gear carrier of the first planetary series is associated friction brake with the transmission housing, the crown gear of the second planetary series is an output element of the gearbox, the output element of a hydrodynamic torque Converter connected friction-controlled clutch with a sun gear of the first planetary series carrier of the third planetary series connected with the planet carrier of the second planetary range, carrier of the second planetary number associated friction brake with the transmission housing, a sun gear of the first planetary number associated friction brake with the transmission output element hydrodynamic conversions the user torque associated friction driven coupling with the planet carrier of the second planetary series the sun gear of the third planetary series is equipped with a friction brake for its connection with the transmission housing, carrier of the first planetary series is associated with the crown gear of the third planetary series, the output element of a hydrodynamic torque Converter connected with the crown gear of the first planetary series, a sun gear of the second planetary number associated with the crown gear of the third planetary series.

To obtain seven speeds forward and two reverse gears according to the first example of implementation of the kinematic scheme sun gear of the third planetary series can be connected friction-controlled clutch with the planet carrier of the third planetary series.

To obtain seven speeds forward and two reverse gears according to the first example of implementation of the kinematic scheme of the crown gear of the third planetary series can be connected friction-controlled clutch with the planet carrier of the third planetary series.

To obtain seven speeds forward and two reverse gears according to the first example of implementation of the kinematic scheme of the crown gear of the third planetary series can be connected friction-controlled clutch with a sun gear of the third planetary series.

To obtain seven speeds forward and two gear C is the last course in the first example implementation of the kinematic scheme of the crown gear of the second planetary series can be connected friction-controlled clutch with the planet carrier of the second planetary series.

Below is an example of a specific implementation of the hydro-mechanical transmission for an automatic transmission, for example, passenger of all-terrain vehicles.

Automatic hydromechanical transmission, implementing six speeds forward and two reverse gears 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 three planetary gear sets. 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). Took 9 of the second planetary series incorporates a friction clutch 14 with the input link 3 gearbox. Input link 3 is connected by a slip clutch 15 with the sun gear 5 of the first planetary series. The crown gear 7 of the first planetary number associated with the input link 3.

The sun gear 5 of the first planetary series connection is to be with Carter 1 gearbox friction brake 16. The friction brake 17 is connected with the crankcase 1 gearbox connected drove 6 of the first planetary series, the crown gear 13 of the third planetary series, and the sun gear 8 of the second planetary series. The friction brake 18 is connected with the crankcase 1 transmission sun gear 11 of the third planetary series. Friction brake 19 is connected with the crankcase 1 transmission interconnected carrier 9 of the second planetary series, and led 12 of the third planetary series.

This embodiment of the transmission in comparison with the known 6-speed transmission type ZF HP 500, ALLISON B300, 500, etc. allows you to get six speeds forward and two reverse gears, using three planetary series and six friction controls. In the proposed scheme does not happen gap power when shifting gears.

If hydromechanical transmission to add a control, connecting the sun gear of the third planetary number and carrier of the third planetary series, you can get a gearbox with seven speeds forward and two reverse gears.

If hydromechanical transmission to add a control, binding of the crown gear of the third planetary number and carrier of the third planetary series, it can be in order to get the gearbox with seven speeds forward and two reverse gears.

If hydromechanical transmission to add a control, binding of the crown gear of the third planetary series, and a sun gear of the third planetary series, you can get a gearbox with seven speeds forward and two reverse gears.

If hydromechanical transmission to add a control, binding of the crown gear of the second planetary number and carrier of the second planetary series, you can get a gearbox with seven speeds forward and two reverse gears.

Equipment gearbox sixth forward gear and the second reverse gear allowed to make changes in gear ratio and the order of the pairwise inclusion friction controls. The change in the structure and sequence of pairwise inclusion of control led to the fact that when switching there is no gap power. Also managed to improve the dynamic characteristics of the transmission and to extend the kinematic capabilities of the gearbox, to increase its longevity, but also significantly expand the number of types of vehicles, which can install the transmission with this configuration.

Proposed according to the invention automatic transmission works with edusim way.

After the start of vehicle motion serial shift from 1st to 6th is the vehicle accelerates to the desired speed. When the transmission is in the neutral position, neither of friction controls are not enabled.

In the first forward gear included brakes 18 and 16, that is, the angular speed of the sun gear 11 of the third planetary series, and a sun gear 5 of the first planetary series is equal to zero.

Torque from the input element 3 through the crown gear 7 of the first planetary number is transmitted to the carrier 6 of the first planetary series and related crown gear 13 of the third planetary series and later on took 12 of the third planetary series and the associated carrier 9 of the second planetary range, where it is divided and through the sun gear 8 of the second planetary number is transmitted to the crown gear 13 of the third planetary series, and is also passed to the crown gear 10 of the second planetary series, directly connected with the output element 4.

When switching to the second forward gear, the brake 17 is turned off, and turns on the clutch 15, the brake 18 is on. Thus, the angular speed of the sun gear 11 of the third planetary series is equal to zero, and the angular speed of the sun gear 5 of the first planetang the number equal to the angular velocity of the input link 3.

Torque from the input element 3 is divided and enabled through the friction clutch 15 is transmitted to the sun gear 5 of the first planetary series and later on took 6 of the first planetary series, and through the crown gear 7 of the first planetary series on led 6 of the first planetary series, where it is combined with the flow of torque from the sun gear 5 of the first planetary series and through the crown gear 13 of the third planetary number is transmitted to the carrier 12 of the third planetary series and its associated carrier 9 of the second planetary range, where it is divided and through the sun gear 8 of the second planetary number is transmitted to the crown gear 13 of the third the planetary series, and is also passed to the crown gear 10 of the second planetary series, directly connected with the output element 4.

When switching to the third forward gear off the clutch 15, and turns on the clutch 14, the brake 18 is on. Thus, the angular speed of the sun gear 11 of the third planetary series is equal to zero, and the angular velocity interconnected carrier 9 of the second planetary series, and led 12 of the third planetary number equal to the angular velocity of the input link 3.

Torque from the input element 3 is switched on via the friction clutch 14 is transmitted to the carrier 9 of the second planetary series, where time is Elaida and transferred to the crown gear 10 of the second planetary series directly connected with the output element 4 and through the sun gear 8 of the second planetary number is transmitted to the crown gear 13 of the third planetary series and later on took 12 of the third planetary series and its associated carrier 9 of the second planetary series, which is connected with a torque with included friction clutch 14.

When switching to the fourth forward gear off the brake 18, and turns on the clutch 15, the clutch 14 remains enabled. Thus, the angular velocity of interconnected carrier 9 of the second planetary series, and led 12 of the third planetary number equal to the angular velocity of the input link 3, and the angular speed of the sun gear 5 of the first planetary number equal to the angular velocity of the input link 3.

Torque from the input element 3 is switched on via the friction clutch 14 is transmitted to the carrier 9 of the second planetary range, where it is divided and transmitted to the crown gear 10 of the second planetary series, directly connected with the output element 4 and through the sun gear 8 of the second planetary number is transmitted to the carrier 6 of the first planetary series, where it is divided and through the sun gear 5 of the first planetary series and included a friction clutch 15 is transmitted to the input link 3, and through the crown gear 7 of the first planetary OC is and is transmitted on the friction clutch 14, where is combined with the power flow from the input link 3.

When switching on the fifth forward gear off the clutch 15 and turns on the brake 16, the clutch 14 remains enabled. Thus, the angular velocity of interconnected carrier 9 of the second planetary series, and led 12 of the third planetary number equal to the angular velocity of the input link 3, 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 switched on via the friction clutch 14 is transmitted to the carrier 9 of the second planetary range, where it is divided and transmitted to the crown gear 10 of the second planetary series, directly connected with the output element 4 and through the sun gear 8 of the second planetary number is transmitted to the carrier 6 of the first planetary series and then through the crown gear 7 of the first planetary number is transmitted on the friction clutch 14, where it is combined with the power flow from the input link 3.

When switching on the sixth forward gear off the brake 16, and turns on the brake 17, the clutch 14 remains enabled. Thus, the angular velocity interconnected drove 6 of the first planetary series, the sun gear 8 of the second planetary series and the crown gear 13 of the third planetary series is equal to zero, and the angular velocity are related is between a carrier 9 of the second planetary series, and led 12 of the third planetary number equal to the angular velocity of the input link 3.

Torque from the input element 3 is switched on via the friction clutch 14 is transmitted to the carrier 9 of the second planetary series and then passed on the crown gear 10 of the second planetary series, directly connected with the output element 4.

In the first reverse gear activated clutch 15 and the brake 19. Thus, the angular speed of the sun gear 5 of the first planetary number equal to the angular velocity of the input link 3, and the angular speed of the carrier 9 of the second planetary number associated with the planet carrier 12 of the third planetary number of zero.

Torque from the input element 3 is divided and enabled through the friction clutch 15 is transmitted to the sun gear 5 of the first planetary series and later on took 6 of the first planetary series, and through the crown gear 7 of the first planetary series on led 6 of the first planetary series, where it is combined with the flow of torque from the sun gear 5 of the first planetary series and through the sun gear 8 of the second planetary number is transmitted to the carrier 9 of the second planetary series and then to the crown gear 10 of the second planetary series, directly connected with the output element 4.

In the second reverse gear activates the brake 16 and the brake 19. Thus, the angular speed of the sun gear 5 of the first planetary equal to zero, and the angular shall Corot took 9 of the second planetary series associated with the planet carrier 12 of the third planetary number of zero.

Torque from the input element 3 through the crown gear 7 of the first planetary number is transmitted to the carrier 6 of the first planetary number and an associated sun gear 8 of the second planetary series and then drove through 9 of the second planetary number is transmitted to the crown gear 10 of the second planetary series, directly connected with the output element 4.

With the introduction of a friction driven clutch 20, which connects the sun gear 11 of the third planetary series and took 12 of the third planetary series transmission can implement seven speeds forward and two reverse gears.

When switching on the seventh transmission includes a clutch 20 and brake 16. 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 number equal to the angular speed of the carrier 12 of the third planetary number associated with the planet carrier 9 of the second planetary series.

Torque from the input element 3 through the crown gear 7 of the first planetary number is transmitted to the carrier 6 of the first planetary series and related crown gear 13 of the third planetary series and later on took 12 of the third planetary series, where shared and switched on via the clutch the second clutch 20 is transmitted to the sun gear 11 of the third planetary series and later on took 12 of the third planetary series and also is transmitted to the carrier 9 of the second planetary range, where it is divided and through the sun gear 8 of the second planetary number is transmitted to the crown gear 13 of the third planetary series, where it is combined with the flow of torque from the carrier 6 of the first planetary series, and is also passed to the crown gear 10 of the second planetary series, directly connected with the output element 4.

With the introduction of a friction driven clutch 21, which connects the crown gear 13 of the third planetary series and took 12 of the third planetary series transmission can implement seven speeds forward and two reverse gears.

When switching on the seventh transmission includes a clutch 21 and the brake 16. Thus, the angular speed of the sun gear 5 of the first planetary series is equal to zero, and the angular velocity of the crown gear 13 of the third planetary number associated with the sun gear 8 of the second planetary series and planet carrier 6 of the first planetary number equal to the angular speed of the carrier 12 of the third planetary number associated with the planet carrier 9 of the second planetary series.

Torque from the input element 3 through the crown gear 7 of the first planetary number is transmitted to the carrier 6 of the first planetary series and related crown gear 13 of the third planetary series and then through enabled freak the ion coupling 21 is transmitted to the carrier 9 of the second planetary series where it is divided and transmitted to the crown gear 10 of the second planetary series, directly connected with the output element 4 and through the sun gear 8 of the second planetary number is transmitted to the crown gear 13 of the third planetary series and forth on the friction clutch 21, where it is combined with the flow of torque from the carrier 6 of the first planetary series.

With the introduction of a friction driven clutch 22, which connects the sun gear 11 of the third planetary series and the crown gear 13 of the third planetary series transmission can implement seven speeds forward and two reverse gears.

When switching on the seventh transmission includes a clutch 22 and the brake 16. 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 number equal to the angular velocity of the crown gear 13 of the third planetary number associated with the sun gear 8 of the second planetary series and planet carrier 6 of the first planetary series.

Torque from the input element 3 through the crown gear 7 of the first planetary number is transmitted to the carrier 6 of the first planetary series and related crown gear 13 of the third planetary series, where it is divided and transmitted to the carrier 12 of the third planetary series is also enabled through the friction clutch 22 is transmitted to the sun gear 11 of the third planetary series and later on took 12 of the third planetary series where is merged with the flow of torque from the crown gear 13 of the third planetary number and transmitted to the carrier 9 of the second planetary range, where it is divided and transmitted to the crown gear 10 of the second planetary series, directly connected with the output element 4 and through the sun gear 8 of the second planetary number is transmitted to the crown gear 13 of the third planetary series, where it is combined with the flow of torque from the carrier 6 of the first planetary series.

With the introduction of a friction driven clutch 23, which connects the crown gear 10 of the second planetary series, and led 9 of the second planetary series transmission can implement seven speeds forward and two reverse gears.

When switching on the seventh transmission includes a clutch 23 and the brake 16. Thus, the angular speed of the sun gear 5 of the first planetary series is equal to zero, and the angular velocity of the crown gear 10 of the second planetary series, which is the output element of the gearbox, is equal to the angular speed of the carrier 12 of the third planetary number associated with the planet carrier 9 of the second planetary series.

Torque from the input element 3 through the crown gear 7 of the first planetary number is transmitted to the carrier 6 of the first planetary number and an associated sun gear 8 of the second planetary the poison on the carrier 9 of the second planetary series where shared and switched on via the friction clutch 23 is transmitted to the output link 4, and is transmitted to the crown gear 10 of the second planetary series, directly connected with the output element 4.

The present invention allows transmissions having three planetary series, to provide six to nine speeds forward and one to three reverse gears without increasing the number of planetary gear sets and a substantial increase in the size of the crankcase due to the increase in the number of controls and changes the sequence of pairwise inclusion of controls.

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.

1. Hydromechanical transmission containing a hydrodynamic torque Converter and a planetary gear carrier of the first planetary series is associated friction brake with the transmission housing, the crown gear of the second planetary series is an output element of the gearbox, the output element of a hydrodynamic torque Converter connected friction-controlled coupling with solar destinatario planetary series carrier of the third planetary series connected with the planet carrier of the second planetary range, carrier of the second planetary number associated friction brake with the transmission housing, a sun gear of the first planetary number associated friction brake with the transmission housing, wherein the output element of a hydrodynamic torque Converter connected friction-controlled clutch with the planet carrier of the second planetary series, a sun gear of the third planetary series is equipped with a friction brake for its connection with the transmission housing, carrier of the first planetary series is associated with the crown gear of the third planetary series, the output element of a hydrodynamic torque Converter connected with the crown gear of the first planetary series, a sun gear the second planetary number associated with the crown gear of the third planetary series.

2. Transmission according to claim 1, characterized in that the sun gear of the third planetary series connected friction-controlled clutch with the planet carrier of the third planetary series.

3. Transmission according to claim 1, wherein the crown gear of the third planetary series connected friction-controlled clutch with the planet carrier of the third planetary series.

4. Transmission according to claim 1, characterized in that the solar sister the I of the third planetary series connected friction-controlled clutch with a crown gear of the third planetary series.

5. Transmission according to claim 1, characterized in that the carrier of the second planetary series connected friction-controlled clutch with a crown gear of the second planetary series, which is the output element of the transmission.

**Same patents:**

FIELD: transport engineering.

SUBSTANCE: invention relates to planetary transmission used in vehicle automatic transmission systems. Proposed hydromechanical tansmission with seven forward speeds and one reverse speed has case 1, torque converter 2, input member 3, output member 4 and planetary reduction gear, three friction clutch and three friction brakes. Planetary reduction fear consists of three planetary gear trains. First planetary gear train consists of sun gear 5, planet pinion carrier 6 and gear 7. Second planetary gear train consists of sun gear 8, planet pinion carrier 9 and crown gear 10. Third planetary gear train consists of sun gear 11, planet pinion carrier 12 and crown gear 13. Input member 3 is connected by friction clutch 14 with intercoupled sun gear 8 and sun gear 11 and it is coupled also by friction clutch 15 with intercoupled carrier 9 and carrier 12. Carrier 9 coupled with carrier 12 is connected by friction clutch 16 with sun gear 11 coupled with sun gear 8. Sun gear is coupled with input member 3. Carrier 6 is connected with case 1 by friction brake 18 connects intercoupled carrier 9 and carrier 12 with case 1. Friction brake 19 connects intercoupled sun gear 8 and sun gear 11 with case 1.

EFFECT: enlarged kinematic capabilities, reduced consumption of fuel, increased service life of transmission, enlarged number of types of vehicles which can operate with transmission of proposed kinematic diagram.

4 cl, 6 dwg

FIELD: transport engineering.

SUBSTANCE: invention relates to planetary transmission used in vehicle automatic transmission systems. Proposed hydromechanical tansmission with six forward speeds and one reverse speed has case 1, torque converter 2, input member 3, output member 4 and planetary reduction gear, two friction clutches and three friction brakes. Planetary reduction gear consists of three planetary gear trains. First planetary gear train consists of sun gear 5, planet pinion carrier 6 and crown gear 7 (epicycle). Second planetary gear train consists of sun gear 8, planet pinion carrier 9 and crown gear 10 (epicycle). Third planetary gear train consists of sun gear 11, planet pinion carrier 12 and crown gear 13 (epicycle). Crown gear 10 of second planetary gear train is connected by friction clutch 14 with carrier 9 of second planetary gear train. Input member 3 is connected by friction clutch 15 with sun gear 5 of first planetary gear train. Sun gear 8 of second planetary gear train is coupled with input member 3. Sun gear 5 of first planetary gear train is connected with case 1 by friction brake 16. Friction brake 17 connects intercoupled carrier 6 of first planetary gear train and crown gear 10 of second planetary gear train with case 1. Friction brake 18 connected sun gear 11 of third planetary gear train with case 1.

EFFECT: enlarged kinematic capabilities, increased service life of transmission.

18 cl, 20 dwg

FIELD: mechanical engineering.

SUBSTANCE: hydromechanical gear box comprises hydrodynamic converter of torque (2) and planet reduction gear. Carrier (6) of the first planet row is connected with crankcase of the gear box (1) through friction brake (17). Corona pinion (7) of the first planet row is connected to carrier (12) of the third planet row that is output link (4) of the gear box. Output member (3) of the hydrodynamic converter of torque is connected with solar pinion (8) of the second planet row and with solar pinion (5) of the first planet row through friction controlled clutch (15). Solar pinion (11) of the third planet row is connected with the crankcase of the gear box through friction brake (18). Solar pinion (5) of the first planet row is connected with crankcase of the gear box through friction brake (16). Corona pinion (10) of the second planet row is connected with corona pinion (13) of the third planet row. Carrier (6) of the first planet row is connected with carrier (9) of the second planet row. Corona pinion (10) of the second planet row is connected with carrier (6) of the first planet row through friction controlled clutch (14).

EFFECT: expanded functional capabilities and prolonged service life.

8 cl, 11 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

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. 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.

1 dwg

FIELD: transport engineering.

SUBSTANCE: invention relates to planetary transmission used in vehicle automatic transmission systems. Proposed hydromechanical tansmission with seven forward speeds and one reverse speed has case 1, torque converter 2, input member 3, output member 4 and planetary reduction gear, three friction clutch and three friction brakes. Planetary reduction fear consists of three planetary gear trains. First planetary gear train consists of sun gear 5, planet pinion carrier 6 and gear 7. Second planetary gear train consists of sun gear 8, planet pinion carrier 9 and crown gear 10. Third planetary gear train consists of sun gear 11, planet pinion carrier 12 and crown gear 13. Input member 3 is connected by friction clutch 14 with intercoupled sun gear 8 and sun gear 11 and it is coupled also by friction clutch 15 with intercoupled carrier 9 and carrier 12. Carrier 9 coupled with carrier 12 is connected by friction clutch 16 with sun gear 11 coupled with sun gear 8. Sun gear is coupled with input member 3. Carrier 6 is connected with case 1 by friction brake 18 connects intercoupled carrier 9 and carrier 12 with case 1. Friction brake 19 connects intercoupled sun gear 8 and sun gear 11 with case 1.

EFFECT: enlarged kinematic capabilities, reduced consumption of fuel, increased service life of transmission, enlarged number of types of vehicles which can operate with transmission of proposed kinematic diagram.

4 cl, 6 dwg

FIELD: transport engineering.

SUBSTANCE: invention relates to planetary transmission used in vehicle automatic transmission systems. Proposed hydromechanical tansmission with six forward speeds and one reverse speed has case 1, torque converter 2, input member 3, output member 4 and planetary reduction gear, two friction clutches and three friction brakes. Planetary reduction gear consists of three planetary gear trains. First planetary gear train consists of sun gear 5, planet pinion carrier 6 and crown gear 7 (epicycle). Second planetary gear train consists of sun gear 8, planet pinion carrier 9 and crown gear 10 (epicycle). Third planetary gear train consists of sun gear 11, planet pinion carrier 12 and crown gear 13 (epicycle). Crown gear 10 of second planetary gear train is connected by friction clutch 14 with carrier 9 of second planetary gear train. Input member 3 is connected by friction clutch 15 with sun gear 5 of first planetary gear train. Sun gear 8 of second planetary gear train is coupled with input member 3. Sun gear 5 of first planetary gear train is connected with case 1 by friction brake 16. Friction brake 17 connects intercoupled carrier 6 of first planetary gear train and crown gear 10 of second planetary gear train with case 1. Friction brake 18 connected sun gear 11 of third planetary gear train with case 1.

EFFECT: enlarged kinematic capabilities, increased service life of transmission.

18 cl, 20 dwg

FIELD: mechanical engineering.

SUBSTANCE: gear box comprises axially aligned driving (1) and driven (2) shafts and one or more transmitting modules mounted in housing (3) and made of two or more rotating links arranged coaxially one to the other and to the shafts of the gear box. The controlled members for gear shifting have inter-module shifting gears (19)-(21) and housing shifting gears (30)-(31). Inter-module shifting gears (19)-(21) can be connected with at least two links of the module. Housing shifting gears (30)-(31) of three- or four-link modules provide connection of the housing with at least two links of the module. Depending on the position of the shifting gears, the input and the output of the module as well as the bearing link of three- or four-link module can be any links.

EFFECT: expanded functional capabilities.

10 cl, 4 tbl

FIELD: mechanical engineering.

SUBSTANCE: hydromechanical gear box comprises hydrodynamic converter of torque (2) and planet reduction gear. Carrier (6) of the first planet row is connected with crankcase of the gear box (1) through friction brake (17). Corona pinion (7) of the first planet row is connected to carrier (12) of the third planet row that is output link (4) of the gear box. Output member (3) of the hydrodynamic converter of torque is connected with solar pinion (8) of the second planet row and with solar pinion (5) of the first planet row through friction controlled clutch (15). Solar pinion (11) of the third planet row is connected with the crankcase of the gear box through friction brake (18). Solar pinion (5) of the first planet row is connected with crankcase of the gear box through friction brake (16). Corona pinion (10) of the second planet row is connected with corona pinion (13) of the third planet row. Carrier (6) of the first planet row is connected with carrier (9) of the second planet row. Corona pinion (10) of the second planet row is connected with carrier (6) of the first planet row through friction controlled clutch (14).

EFFECT: expanded functional capabilities and prolonged service life.

8 cl, 11 dwg

FIELD: transport engineering.

SUBSTANCE: invention relates to planetary transmission used in vehicle automatic transmission systems. Proposed hydromechanical tansmission with seven forward speeds and one reverse speed has case 1, torque converter 2, input member 3, output member 4 and planetary reduction gear, three friction clutch and three friction brakes. Planetary reduction fear consists of three planetary gear trains. First planetary gear train consists of sun gear 5, planet pinion carrier 6 and gear 7. Second planetary gear train consists of sun gear 8, planet pinion carrier 9 and crown gear 10. Third planetary gear train consists of sun gear 11, planet pinion carrier 12 and crown gear 13. Input member 3 is connected by friction clutch 14 with intercoupled sun gear 8 and sun gear 11 and it is coupled also by friction clutch 15 with intercoupled carrier 9 and carrier 12. Carrier 9 coupled with carrier 12 is connected by friction clutch 16 with sun gear 11 coupled with sun gear 8. Sun gear is coupled with input member 3. Carrier 6 is connected with case 1 by friction brake 18 connects intercoupled carrier 9 and carrier 12 with case 1. Friction brake 19 connects intercoupled sun gear 8 and sun gear 11 with case 1.

EFFECT: enlarged kinematic capabilities, reduced consumption of fuel, increased service life of transmission, enlarged number of types of vehicles which can operate with transmission of proposed kinematic diagram.

4 cl, 6 dwg

FIELD: transport engineering.

SUBSTANCE: invention relates to planetary transmission used in vehicle automatic transmission systems. Proposed hydromechanical tansmission with six forward speeds and one reverse speed has case 1, torque converter 2, input member 3, output member 4 and planetary reduction gear, two friction clutches and three friction brakes. Planetary reduction gear consists of three planetary gear trains. First planetary gear train consists of sun gear 5, planet pinion carrier 6 and crown gear 7 (epicycle). Second planetary gear train consists of sun gear 8, planet pinion carrier 9 and crown gear 10 (epicycle). Third planetary gear train consists of sun gear 11, planet pinion carrier 12 and crown gear 13 (epicycle). Crown gear 10 of second planetary gear train is connected by friction clutch 14 with carrier 9 of second planetary gear train. Input member 3 is connected by friction clutch 15 with sun gear 5 of first planetary gear train. Sun gear 8 of second planetary gear train is coupled with input member 3. Sun gear 5 of first planetary gear train is connected with case 1 by friction brake 16. Friction brake 17 connects intercoupled carrier 6 of first planetary gear train and crown gear 10 of second planetary gear train with case 1. Friction brake 18 connected sun gear 11 of third planetary gear train with case 1.

EFFECT: enlarged kinematic capabilities, increased service life of transmission.

18 cl, 20 dwg

FIELD: mechanical engineering.

SUBSTANCE: transmission comprises pump station provided with the pressure-tight hydraulic tank, high-pressure tank, make-up pump, and hydraulic motors for driving wheels. The hydraulic motors are in communication with the pump station through hydraulic pipelines that define a circulating hydraulic circuit. The by-pass hydraulic lines connected with the main hydraulic lines receive relief valves provided with a valving member. The drain hydraulic line receives the pilot valve controlled by means of the fluid pressure gage in the supplying hydraulic line and pressure gage of compressed air in the pneumatic system. The friction clutch has a fluid-pressure drive for its disconnecting which is set in operation by the valve for supplying compressed air and is controlled by means of temperature transducer and pickup of the level of the fluid in the hydraulic tank, air pressure gage in the air space of the hydraulic tank, and pickup of position of the valving member of the shut-off valve mounted in the sucking hydraulic line of the make-up pump.

EFFECT: enhanced reliability.

3 cl, 2 dwg

FIELD: mechanical engineering.

SUBSTANCE: hydromechanical gear box comprises hydrodynamic converter of torque (2) and planet reduction gear. Carrier (6) of the first planet row is connected with crankcase of the gear box (1) through friction brake (17). Corona pinion (7) of the first planet row is connected to carrier (12) of the third planet row that is output link (4) of the gear box. Output member (3) of the hydrodynamic converter of torque is connected with solar pinion (8) of the second planet row and with solar pinion (5) of the first planet row through friction controlled clutch (15). Solar pinion (11) of the third planet row is connected with the crankcase of the gear box through friction brake (18). Solar pinion (5) of the first planet row is connected with crankcase of the gear box through friction brake (16). Corona pinion (10) of the second planet row is connected with corona pinion (13) of the third planet row. Carrier (6) of the first planet row is connected with carrier (9) of the second planet row. Corona pinion (10) of the second planet row is connected with carrier (6) of the first planet row through friction controlled clutch (14).

EFFECT: expanded functional capabilities and prolonged service life.

8 cl, 11 dwg

FIELD: transport mechanical engineering.

SUBSTANCE: method comprises supplying the fluid from tank (14) to hydraulic motors (3) and hydraulic pumps through pipelines (5) and discharging the fluid to tank (14) through drain pipelines (6) through the fluid cooler when a vehicle moves forward. The electromechanical valving members in drain (6) pipeline (6) and pipelines that connect the supplying pipelines with tank (14) and fluid-pressure accumulator (2) are closed. The electromechanical valving members in supplying pipeline (5) and pipelines that connect the tank with the drain pipelines are open. When braking, the fluid is fed through pipelines from tank (14) via fluid cooler to the fluid-pressure accumulator (20) by means of hydraulic pumps (3). The electromechanical valving members in supplying and discharging pipelines are closed, and valving members in pipelines that connect the fluid-pressure accumulator with the supplying pipelines and tank with drain pipelines are open. When vehicle moves back, the fluid is supplied through drain pipelines (6) and is discharged through supplying pipelines (5). The hydraulic drive has hydraulic pump (1) connected to hydraulic motors (3) through supplying (5) and discharging (6) pipelines.

EFFECT: reduced fuel consumption, prolonged service life, and reduced harmful emission.

12 cl, 1 dwg