# Hydromechanical gear box

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

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 gearboxes planetang the type in 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 and five or six controls. However, such schemes do not implement dynamic performance requirements for vehicles, reduce the kinematic capabilities of the gearbox, reducing its durability. 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 the gearbox 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 range, which is associated friction brake with the transmission housing, the crown gear of the first planetary series connected with the planet carrier of the third planetary series, which is an output link of pen boxes the cottages, the output element of a hydrodynamic torque Converter connected friction-controlled clutch with a crown gear of the second planetary series, the crown gear of the second planetary series connected with the planet carrier of the first planetary series, the output element of the hydrodynamic torque Converter is connected with a sun gear of the second planetary series slip-controlled clutch to the sun gear of the first planetary series, the crown gear of the third planetary series connected 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, a sun gear of the first planetary number associated friction brake with the transmission housing (DE 19912480 A1, F 16 H 3/62, from 28.09.2000,).

This transmission contains to change the relationship of torque between the input and output links of the two friction clutches and three brakes. In the box-prototype shifting occurs due to the pairwise inclusion of the five frictional elements of the control 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 performance of the transport is the main means. 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 install the transmission with this configuration.

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 first planetary series connected with the planet carrier of the third planetary series, which is an output element of the gearbox, the output element of the hydrodynamic torque Converter is connected with a sun gear of the second planetary series slip-controlled clutch to the sun gear of the first planetary series, a sun gear of the third planetary series is equipped with a friction brake for its connection with the transmission housing, a sun gear of the first planetary number associated friction brake with the transmission housing, the crown gear of the second planetary number associated with the crown gear of the third planetary series, drove the first planetary number associated with dilam second planetary series the crown gear of the second planetary series connected friction-controlled clutch with the planet carrier of the first 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 first planetary series through friction driven clutch with the planet carrier of the first planetary series allowed us to obtain seven speeds forward and one reverse gear.

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

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 eight speeds forward and one reverse gear.

The connection of the crown gear of the third planetary series through friction driven clutch with the planet carrier of the third planetary series allowed us to obtain eight speeds forward and one reverse gear.

The connection at the same time a sun gear of the first planetary series through friction driven clutch drove the first planetary series, and a sun gear of the third planetary series through friction driven clutch with the planet carrier of the third planetary series allowed us to obtain nine speeds forward and one rear of turn.

The connection at the same time a sun gear of the first planetary series through friction driven clutch with the planet carrier of the first planetary series and the crown gear of the third planetary series through friction driven clutch with the planet carrier of the third planetary series allowed us to obtain nine speeds forward and one reverse gear.

The connection at the same time the crown gear of the first planetary series through friction driven clutch with the planet carrier of the first planetary series, and a sun gear of the third planetary series through friction driven clutch with the planet carrier of the third planetary series allowed us to obtain nine speeds forward and one reverse gear.

The connection at the same time the crown gear of the first planetary series through friction driven clutch with the planet carrier of the first planetary series and the crown gear of the third planetary series through friction driven clutch with the planet carrier of the third planetary series allowed us to obtain nine speeds forward and one reverse gear.

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.

Sushnost the proposed technical solution is illustrated by drawings, where

figure 1 is a kinematic diagram of the six-speed hydromechanical transmission for a vehicle transmission with one reverse gear;

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

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

figure 4 is a kinematic diagram of the seven-speed hydromechanical transmission for a vehicle transmission with one reverse gear;

figure 5 is a kinematic diagram of the eight-speed hydromechanical transmission for a vehicle transmission with one reverse gear;

figure 6 is a kinematic diagram of the eight-speed hydromechanical transmission for a vehicle transmission with one reverse gear;

7 is a kinematic diagram of a hydromechanical nine-storeyed transmission for a vehicle transmission with one reverse gear;

on Fig - kinematic scheme hydromechanical nine-storeyed transmission for a vehicle transmission with one reverse gear;

figure 9 - will cast the political scheme hydromechanical nine-storeyed transmission for a vehicle transmission with one reverse gear;

figure 10 is a kinematic diagram of a hydromechanical nine-storeyed transmission for a vehicle transmission with one reverse gear;

figure 11 is a plan of angular velocities hydromechanical nine-storeyed transmission for a vehicle transmission with one reverse gear.

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 first planetary series connected with the planet carrier of the third planetary series, which is an output element of the gearbox, the output element of the hydrodynamic torque Converter is connected with a sun gear of the second planetary series slip-controlled clutch to the sun gear of the first planetary series, a sun gear of the third planetary series is equipped with a friction brake for its connection with the transmission housing, a sun gear of the first planetary number associated friction brake with the transmission housing, the crown gear of the second planetary number associated with the crown gear of the third planetary series, drove the first planetary range connected with water the ohms of the second planetary series the crown gear of the second planetary series connected friction-controlled clutch with the planet carrier of the first planetary series.

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

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

To get eight speeds forward and one reverse gear 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, which is the output element of the transmission.

To get eight speeds forward and one reverse gear 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, which is the output element of the transmission.

To obtain nine before the forward stroke and one reverse gear according to the second 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 number, which is the output element of the transmission.

To obtain nine speeds forward and one reverse gear according to the second 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, which is the output element of the transmission.

To obtain nine speeds forward and one reverse gear according to a third 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, which is the output element of the transmission.

To obtain nine speeds forward and one reverse gear according to a third 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, which is the output element of the transmission.

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 one reverse gear contains to rter 1, 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 three 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). Crown gear 10 of the second planetary number associated with a crown gear 13 of the third planetary series incorporates a friction clutch 14 with connected planet carrier 6 of the first planetary series and planet carrier 9 of the second planetary series. Input link 3 is connected by a slip clutch 15 with the sun gear 5 of the first planetary series. The sun gear 8 of the second planetary number associated with the input link 3.

The sun gear 5 of the first planetary series is connected with the crankcase 1 gearbox friction brake 16. The friction brake 17 is connected with the crankcase 1 gearbox connected drove 6 of the first planetary range and water is about 9 of the second planetary series. The friction brake 18 is connected with the crankcase 1 transmission sun gear 11 of the third planetary series.

This embodiment of the transmission in comparison with the known six-speed transmission type ZF HP 500, ALLISON B300, 500, etc. allows you to get six speeds forward and one reverse gear, using three planetary series and five 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 first planetary number and carrier of the first planetary series, you can get a gearbox with seven speeds forward and one reverse gear.

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

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 transmission with eight speeds forward and one reverse gear.

what if it hydromechanical transmission to add a control, connecting the crown gear of the third planetary number and carrier of the third planetary series, you can get a transmission with eight speeds forward and one reverse gear.

If hydromechanical transmission at the same time to add a control, connecting the sun gear of the first planetary number and carrier of the first planetary series, and a control connecting the sun gear of the third planetary number and carrier of the third planetary series, you can get a gearbox with nine speeds forward and one reverse gear.

If hydromechanical transmission at the same time to add a control, connecting the sun gear of the first planetary number and carrier of the first planetary series, and the control that binds the crown gear of the third planetary number and carrier of the third planetary series, you can get a gearbox with nine speeds forward and one reverse gear.

If hydromechanical transmission at the same time to add a control, binding of the crown gear of the first planetary number and carrier of the first planetary series, and a control connecting the sun gear of the third planetary happy and carrier of the third planetary line is, you can get a gearbox with nine speeds forward and one reverse gear.

If hydromechanical transmission at the same time to add a control, binding of the crown gear of the first planetary number and carrier of the first planetary happy, and the control that binds the crown gear of the third planetary number and carrier of the third planetary pleased, you can get a gearbox with nine speeds forward and one reverse gear.

Equipment gearbox sixth forward 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 the automatic transmission operates as follows.

After the start of movement of the vehicle serial is inim shifting 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 brake 18 and 17, that is, the angular speed of the sun gear 11 of the third planetary series and drove 6 of the first planetary number associated with the planet carrier 9 of the second planetary number of zero.

Torque from the input element 3 through the sun gear 8 of the second planetary number is transmitted to the crown gear 10 of the second planetary series and related crown gear 13 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 second forward gear, the brake 17 is turned off, and turns on the brake 16, the brake 18 is on. Thus, the angular speed of the sun gear 5 of the first planetary series, and a sun gear 11 of the third planetary series is equal to zero.

Torque from the input element 3 through the sun gear 8 of the second planetary number is transmitted to the carrier 9 of the second planetary series, and with it via the crown gear 10 of the second planetary series and related crown gear 13 of the third planetary number is transmitted to the carrier 12 of the third planetary series, where it is divided and transmitted to the connected with the planet carrier 12 of the third planet of the tion of the number of the output link 4, and through the crown gear 7 of the first planetary number is transmitted to the carrier 6 of the first planetary series and its associated carrier 9 of the second planetary series, where the combined flow of torque from the sun gear 8 of the second planetary series.

When switching to the third forward gear off the brake 16 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 planetary 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 sun gear 8 of the second planetary series, and led 9 of the second planetary number is transmitted to the crown gear 10 of the second planetary series and related crown gear 13 of the third planetary series and later on took 12 of the third planetary series, where it is divided and transmitted to the connected with the planet carrier 12 of the third planetary number of the output link 4, and the crown gear 7 of the first planetary series, and with it has taken 6 of the first planetary series, where it is combined with the flow of torque from on the Chennai friction clutches 15 and then is transmitted to the carrier 9 of the second planetary series which is connected to the torque input element 3.

When switching to the fourth 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 speed of the carrier 6 of the first planetary series and its associated carrier 9 of the second planetary number equal to the angular velocity of the crown gear 10 of the second planetary number associated with the crown gear 13 of the third planetary series.

Torque from the input element 3 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, where it is divided and enabled through the friction clutch 14 is transmitted to the carrier 9 of the second planetary series, where the combined flow of torque from the sun gear 8 of the second planetary series, and is also passed to the crown gear 13 of the third planetary series and later on took 12 of the third planetary series directly connected with the output element 4.

When switching on the fifth forward gear off the brake 18 and turns on the clutch 15, the clutch 14 remains enabled. Thus, the angular speed of the sun gear 5 of the first planetary number of equal angular is karasti input link 3, the angular velocity of the crown gear 10 of the second planetary number associated with the crown gear 13 of the third planetary number equal to the angular speed of the carrier 9 of the second planetary number associated with the planet carrier 6 of the first planetary series.

Torque from the input element 3 through the sun gear 8 of the second planetary number is transmitted to the carrier 9 of the second planetary series and then through the crown gear 9 of the second planetary number is transmitted on the friction clutch 14, where it is divided and transmitted to the carrier 9 of the second planetary series, and drove 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 element 3, and on the crown gear 7 of the first planetary series and its associated carrier 12 of the third planetary series, connected directly with the output link 4.

When switching on the sixth forward gear off the clutch 15 and turns on the brake 16, the clutch 14 remains enabled. 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 number associated with the crown gear 13 of the third planetary number equal to the angular speed of the carrier 9 of the second planetary number associated with dilam 6 of the first planetary series.

Torque from the input element 3 through the sun gear 8 of the second planetary number is transmitted to the carrier 9 of the second planetary series and then through the crown gear 9 of the second planetary number is transmitted on the friction clutch 14, where it is divided and transmitted to the carrier 9 of the second planetary series, and also through the carrier 6 of the first planetary number is transmitted to the crown gear 7 of the first planetary series and its associated carrier 12 of the third planetary series directly connected with the output element 4.

On the reverse gear includes a clutch 15 and the brake 17. 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 6 of the first planetary number associated with the planet carrier 9 of the second planetary number of zero.

Torque from the input element 3 is switched on via the friction clutch 15 is transmitted to the sun gear 5 of the first planetary series, and it drove through 6 of the first planetary number is transmitted to the crown gear 7 of the first planetary series and its associated carrier 12 of the third planetary series, connected directly to the output link 4.

With the introduction of a friction driven clutch 20, which connects the sun gear 5 of the first planetary series and drove 6 first planetang the series, transmission can implement seven speeds forward and one reverse gear.

When switching on the seventh transmission includes a clutch 20 and brake 18. 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 planetary number equal to the angular speed of the carrier 6 of the first planetary series and its associated carrier 9 of the second planetary series.

Torque from the input element 3 is transmitted through the sun gear 8 of the second planetary series on led 9 of the second planetary series and then to the crown gear 10 of the second planetary series and related crown gear 13 of the third planetary series and later on took 12 of the third planetary series, where it is divided and transmitted to the connected with the planet carrier 12 of the third planetary number of the output link 4, and the crown gear 7 of the first planetary series, and with her took 6 of the first planetary series and further enabled through the friction clutch 20 is transmitted to the sun gear 5 of the first planetary series and then on the drive rod 6 of the first planetary series is combined with the flow of torque from the crown gear 7 of the first planetary series and is transmitted through the carrier 9 of the second planetary series, where the combined flow of torque with solar sixth is ERNI 8 of the second planetary series.

With the introduction of a friction driven clutch 21, which connects the crown gear 7 of the first planetary series and drove 6 of the first planetary series transmission can implement seven speeds forward and one reverse gear.

When switching on the seventh transmission includes a clutch 21, and the brake 18. Thus, the angular speed of the sun gear 11 of the third planetary series is equal to zero, and the angular velocity of the crown gear 7 of the first planetary number equal to the angular speed of the carrier 6 of the first planetary series and its associated carrier 9 of the second planetary series.

Torque from the input element 3 is transmitted through the sun gear 8 of the second planetary series on led 9 of the second planetary series, next to the crown gear 10 of the second planetary series and related crown gear 13 of the third planetary series and later on took 12 of the third planetary series, where it is divided and transmitted to the connected with the planet carrier 12 of the third planetary number of the output link 4, and the crown gear 7 of the first planetary series, and with it switched on via the friction clutch 21 is transmitted to the carrier 6 of the first planetary series and its associated carrier 9 of the second planetary series, where combined with the flow of torque from the sun gear 8 of the second planetary series.

With the introduction of Riccione driven clutch 22, connecting the sun gear 11 of the third planetary series and took 12 of the third planetary series transmission can implement eight speeds forward and one reverse gear.

On the seventh transmission includes a clutch 22 and the brake 17. Thus, the angular speed of the carrier 6 of the first planetary series and its associated carrier 9 of the second 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 series and related crown gear 7 of the first planetary series.

Torque from the input element 3 through the sun gear 8 of the second planetary number is transmitted to the carrier 9 of the second planetary series, and with it via the crown gear 10 of the second planetary series and related crown gear 13 of the third planetary number is transmitted to the carrier 12 of the third planetary series, where it is divided and transmitted to the connected with the planet carrier 12 of the third planetary number of the output link 4, and 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 it is combined with the flow of torque of the crown gear 13 of the third planetary series.

On the eighth transmission includes a clutch 22 and the brake 16. Thus the om, the angular speed of the sun gear 5 of the first planetary equal to zero, and the angular speed of the sun gear 11 of the third planetary number of equal angular speed led led 12 of the third planetary series and related crown gear 7 of the first planetary series.

Torque from the input element 3 through the sun gear 8 of the second planetary number is transmitted to the carrier 9 of the second planetary series, and with it via the crown gear 10 of the second planetary series and related crown gear 13 of the third planetary number is transmitted to the carrier 12 of the third planetary range where it is divided into three streams. The first thread torque is transmitted to the connected with the planet carrier 12 of the third planetary number of the output link 4. The second flow of torque through the included 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 it is combined with the flow of torque from the crown gear 13 of the third planetary series. The third flow of torque through the crown gear 7 of the first planetary number is transmitted to the carrier 6 of the first planetary series and its associated carrier 9 of the second planetary series, where the combined flow of torque from the sun gear 8 of the second planetary series.

With the introduction of f is ictional driven clutch 23, connecting the crown gear 13 of the third planetary series and took 12 of the third planetary series transmission can implement eight speeds forward and one reverse gear.

On the seventh transmission includes a clutch 23 and the brake 17. Thus, the angular speed of the carrier 6 of the first planetary series and its associated carrier 9 of the second planetary series is equal to zero, and the angular velocity of the crown gear 13 of the third planetary series and the associated crown gear 10 of the second planetary number of equal angular speed led led 12 of the third planetary series and related crown gear 7 of the first planetary series.

Torque from the input element 3 through the sun gear 8 of the second planetary number is transmitted to the carrier 9 of the second planetary series, and with her crown gear 10 of the second planetary series and related crown gear 13 of the third planetary series and further enabled through the friction clutch 23 is transmitted to the carrier 12 of the third planetary series directly connected with the output element 4.

On the eighth 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 13 of the third planetary series and sasenai with her crown gear 10 Vtorov the planetary series of equal angular speed of the carrier 12 of the third planetary series and related crown gear 7 of the first planetary series.

Torque from the input element 3 through the sun gear 8 of the second planetary number is transmitted to the carrier 9 of the second planetary series, and with her crown gear 10 of the second planetary series and related crown gear 13 of the third planetary series and further enabled through the friction clutch 23 is transmitted to the carrier 12 of the third planetary series, where it is divided and transmitted to the connected with the planet carrier 12 of the third planetary number of the output link 4, and enabled through the friction clutch 23 is transmitted to the crown gear 7 of the first planetary series, and then is transmitted to the carrier 6 of the first planetary series and related took 9 of the second planetary series, where the combined flow of torque from the sun gear 8 of the second planetary series.

Subsequent simultaneous conduct of friction controlled clutches 20, 21, 22, 23 in combination 20-22, 20-23, 21-22, 21-23 the number of forward and reverse folds, and the flow of torque is not changed.

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, as well as from Univ 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 first planetary series connected with the planet carrier of the third planetary series, which is an output element of the gearbox, the output element of the hydrodynamic torque Converter is connected with a sun gear of the second planetary series slip-controlled clutch to the sun gear of the first planetary series, a sun gear of the third planetary series is equipped with a friction brake for its connection with the transmission housing, a sun gear of the first planetary number associated friction brake with the transmission housing, characterized in that the crown gear of the second planetary number associated with the crown gear of the third planetary series, drove the first planetary series connected with the planet carrier of the second planetary series, the crown gear of the second planetary nagaswara friction driven coupling with the planet carrier of the first planetary series.

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

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

4. 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, which is the output element of the transmission.

5. 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, which is the output element of the transmission.

6. Transmission according to claim 2, characterized in that the sun gear of the third planetary series connected friction-controlled clutch with the planet carrier of the third planetary series, which is the output element of the transmission.

7. Transmission according to claim 2, characterized in that the crown gear of the third planetary series connected friction-controlled clutch with the planet carrier of the third planetary series, which is the output element of the transmission.

8. Transmission according to claim 3, characterized in that the sun gear of the third PLA is eternulo number associated friction driven coupling with the planet carrier of the third planetary series an output element of the transmission.

9. Transmission according to claim 3, characterized in that the crown gear of the third planetary series connected friction-controlled clutch with the planet carrier of the third planetary series, which is the output element of the transmission.

**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. 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 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

FIELD: transport engineering.

SUBSTANCE: invention can be used in transmissions of tractors and road-building machines under unstable motion conditions. Proposed transmission of vehicle has planetary reduction gear coupled with engine, pneumohydraulic accumulator, hydraulic pump mechanically coupled with one of links of planetary reduction gear. Fitted in pressure main lone are hydraulic distributor and additional three-dimensional member containing adjustable restrictor connected with variable rigidity pneumohydraulic accumulator. Drain main line of pneumohydraulic accumulator is connected through reduction valve with suction main line of hydraulic pump and drain main line of hydraulic distributor.

EFFECT: protection of engine and parts of power train from peak loads by means of reducing valve and from dynamic loads at starting from half, optimization of operation of engine, reduced specific consumption on fuel.

1 dwg

FIELD: gearing.

SUBSTANCE: method comprises changing the state of blocking friction clutch through the period of its pulse engaging-disengaging.

EFFECT: enhanced efficiency.

4 dwg

FIELD: mechanical engineering.

SUBSTANCE: positive-displacement hydraulic transmission comprises reverse pump and hydraulic motor interconnected through fluid pipelines, safety valves, and hydraulic line with check valves connected with the source. The source is made of pressure-tight hydraulic tank with the air space above the fluid. The air space of the tank is in communication with the atmosphere through the valving system. The hydraulic tank has inlet for drain lines that connects it with the hydraulic motors.

EFFECT: expanded functional capabilities.

3 dwg

FIELD: transport engineering.

SUBSTANCE: device to control friction clutch of drive of pumping unit consisting of main and make-up pumps has spring-loaded lever to move spring-loaded pressure plate of clutch from friction plate, hydraulic cylinder to turn lever for closing clutch disks by means of springs interacting with pressure plate, vessel with liquid communicating with hydraulic cylinder, valve to communicate air space of vessel with compressed air source. Valve electric control circuit includes switches operated by compressed air source pressure sensor, sensors of pressure built by make-up pump and additional pump driven from engine shaft, maximum temperature sensor and working liquid minimum level sensor in hydraulic tank.

EFFECT: provision of convenient control of friction clutch with monitoring condition of hydrostatic transmission to prevent emergency situations by switching off pumping unit drive.

2 cl, 1 dwg

FIELD: transport engineering.

SUBSTANCE: proposed transmission of hydraulically powered vehicle has pumping unit driven from heat engine through friction clutch and consisting of main and make-up pumps, hydraulic motors connected with pumping unit by main hydraulic lines and forming hydraulic circuit, and self-contained pump with drive from electric motor. Clutch control mechanism contains spring-loaded lever to move spring-loaded pressure plate of clutch from friction plate, hydraulic cylinder to move lever closing clutch plate by spring engaging with pressure plate, vessel with liquid communicating with hydraulic cylinder, valve for communicating vessel with compressed air source. Valve control, electric circuit is provided with switches operated by compressed air source pressure sensor, engine shaft speed sensor, pressure sensor of make-up pump and sensors of maximum temperature and minimum liquid level in hydraulic tank. Electric control circuit of self-contained pump drive motor has switch controlled manually and switches controlled by pumping unit shaft speed sensor, hydraulic tank working liquid minimum level sensor, shutoff element of two-position valve communicating suction space of self-contained pump in turn hydraulic tank and with device for filling hydraulic tank with working liquid.

EFFECT: improved reliability of transmission of hydraulic powered vehicle by monitoring its condition to prevent emergency situations.

2 cl, 1 dwg

FIELD: transport mechanical engineering.

SUBSTANCE: cooling system comprises tank for fluid, supplying hydraulic pump for the cooling system, cooler for fluid mounted at the drain of the fluid from the hydraulic transformer, drain valve interposed between the hydraulic transformer and cooler, and differential reduction valve which has main working space connected with the pressure line of the hydraulic pump and auxiliary working space connected with the inlet of the cooler. The fluid cooling circuit of the hydraulic transformer between the auxiliary space of the differential reduction valve and drain valve is connected with the cooling circuit of the internal combustion engine through the heat exchanger. The passage that connects the drain valve with the cooler of the hydraulic transformer is provided with the two-positioned distributor.

EFFECT: expanded functional capabilities.

1 dwg

FIELD: mechanical engineering.

SUBSTANCE: positive-displacement hydraulic-mechanical transmission comprises input shaft (1), output shaft (2), two interconnected reversible controlled hydraulic motors (3) and (4), four-link differential (5), and pumping devices (12), (13), (14), and (15). Satellites (7) and (8) of differential (5) are made in pairs and engage each other. Satellite (8) is wide and interposed between the large solar gear (10) and central wheel (11) with the inner engagement. Satellite (7) is narrow and engages small solar gear (9). Two switching devices (14) and (15) connect the shaft of hydraulic motor (4) with input shaft (1) of the transmission and central wheel (11) with the inner engagement. Two switching devices (12) and (13) connect the shaft of hydraulic motor (3) with output shaft (2) of the transmission and small solar gear (9) of the differential.

EFFECT: reduced mass and sizes and enhanced efficiency.

1 dwg, 1 tbl

FIELD: mechanical engineering.

SUBSTANCE: invention can be used in drives of small-size farm tractors and road-building machines. Proposed hydraulic drive contains variable-capacity pump connected with engine, vehicle wheel drive hydraulic motor, working equipment drive hydraulic motor, hydraulic motor shaft speed governor, pressure differential valve and logic OR gate. Variable-capacity pump is connected with wheel drive hydraulic motor through pressure differential valve whose spring space is connected with speed governor, and opposite end face space, with pressure hydraulic line of pump through OR gate. Working equipment drive hydraulic motor is connected with variable-capacity pump through speed governor. Distributor with check valves is installed in return hydraulic lines of hydraulic motors.

EFFECT: enlarged operating capabilities of hydraulic drive, provision of stepless control of speeds of equipment and self-propelled vehicle drives, possibility of reversing and braking of hydraulic motors of vehicle drive and working equipment drive.

3 cl, 2 dwg