Hydromechanic transmission

FIELD: transport.

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

EFFECT: simplified design.

16 cl, 18 dwg

 

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

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

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

Known hydromechanical transmission (W�turnout Germany No. DE 10162883, published 10.07.2003) containing a hydrodynamic torque Converter, three planetary series and five control elements (two brakes and three clutches), which due to the pairwise inclusion of the two controls on each transfer it is possible to obtain six forward gears and one reverse gear.

The disadvantage of the prototype is the presence of three friction clutches, which greatly complicates the design of the hydraulic control system and causes the appearance of additional unwanted axial forces in the gearbox, which must be prevented, which complicates the design. In addition, the box is a permanent rigid connection of the sun gear of the third planetary gear set with Carter, which should be provided an additional element of design to ensure this self-adjustment sun gear, which in turn also complicates the design.

Analysis of the development of automatic transmissions shows the desire of developers to reduce power loss during transmission from the engine to the drive wheels. One of the main factors influencing the magnitude of the losses in the gearbox, in the case of use as controls friction clutches and friction brakes, is the number of friction elements�tov control is being disabled. The fewer controls, the higher the efficiency of the gearbox. As is known, to obtain a rigid kinematic connection in a planetary transmission having three degrees of freedom, you must include two controls. This naturally leads to lower losses in the gearbox, because for the same amount of frictional control elements, for example, two-step and three-degree-offreedom transmissions for the last number of controls are in the off state, will be less. In this regard, the use of kinematic schemes, has three degrees of freedom, the most important.

In this case it is preferable not to increase the power loss during transmission from the engine to the drive wheels. One of the main factors influencing the magnitude of the losses in the gearbox, in the case of use as control elements of friction clutches and friction brakes, is the number of friction elements that are in the off state. The less of such elements, the higher the efficiency of the gearbox.

In the box-prototype manages to get six forward gears and one reverse gear due to the pairwise inclusion of the five frictional elements of the control links of the planetary gear sets.

Technical�ical result on receipt of which the present invention is directed, is expanding Arsenal of technical means, as well as an increase in the number of transmissions sold in a box with three planetary series, and, in addition, to simplify the structure and design of the control system by reducing the number of friction clutches and reducing the number of links for the same number of gears forward stroke.

The technical result in the implementation of the six forward gears and two reverse gears is achieved in that in the hydromechanical transmission containing a hydrodynamic torque Converter and planetary gearbox is operated by three controlled brakes and managed two couplings included in pairs, as carrier of the third planetary series connected with a crown gear of the first planetary gear set and with the output element, a sun gear of the third planetary series connected brake with a gear housing, the crown gear of the third planetary series connected with the planet carrier of the second planetary gear set, a sun gear of the second planetary series connected with the output element of the hydrodynamic torque Converter and directly with the input element of the gearbox and through the clutch with the planet carrier of the second planetary range, carrier of the second planetary series is connected through �the UFT with a sun gear of the first planetary gear set, crown gear of the second planetary series connected with the planet carrier of the first planetary series, and through the brake with a gear housing, a sun gear of the first planetary series is connected through the brake with the gear housing.

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

Compound sun gear of the first planetary gear set via a controlled clutch with the input link allowed us to obtain seven speeds forward and three reverse gears.

Compound sun gear of the first planetary gear set via a controlled clutch with the planet carrier of the first planetary series allowed us to obtain seven speeds forward and two reverse gears.

The connection of the crown gear of the first planetary gear set via a controlled clutch with the planet carrier of the first planetary series allowed us to obtain seven speeds forward and two reverse gears.

The connection of the crown gear of the second planetary gear set via a controlled clutch with the planet carrier of the second planetary gear set instead of the controlled clutch connecting the driving member with the planet carrier of the second planetary series allowed us to obtain six forward gears and two reverse gears.

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

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

Compound sun gear of the second planetary gear set via a controlled clutch with the planet carrier of the third planetary series allowed us to obtain nine speeds forward and two reverse gears.

The connection at the same time a sun gear of the first planetary gear set via a controlled clutch with the input element, a sun gear of the second planetary gear set and via a controlled clutch with the planet carrier of the third planetary series, a sun gear of the first planetary gear set via a controlled clutch with the planet carrier of the first planetary series carrier of the third planetary series through controlled clutch with a crown gear of the third planetary series allowed us to obtain thirteen forward gears and three reverse gears.

The connection at the same time a sun gear of the first planetary gear set via a controlled clutch with the input element, a sun gear of the second planetary gear set black�W controlled clutch with the planet carrier of the third planetary gear set, a sun gear of the first planetary gear set via a controlled clutch with the planet carrier of the first planetary series carrier of the third planetary series through controlled clutch with a crown gear of the third planetary series and the crown gear of the second planetary gear set via a controlled clutch with the planet carrier of the second planetary gear set instead of the controlled clutch connecting the carrier of the second planetary gear set with the input level, allowed us to obtain thirteen forward gears and three reverse gears.

The connection at the same time a sun gear of the first planetary gear set via a controlled clutch with the input element, a sun gear of the second planetary gear set via a controlled clutch with the planet carrier of the third planetary series, drove the first row via a controlled clutch with a crown gear of the first row, took the third row via a controlled clutch with a crown gear of the third series allowed us to obtain thirteen forward gears and three reverse gears.

The connection at the same time a sun gear of the first planetary gear set via a controlled clutch with the input element, a sun gear of the second planetary gear set via a controlled clutch with the planet carrier of the third planetary series, drove the first row via a controlled clutch with a crown gear of the first row, took the third row through �problemoy clutch with a crown gear of the third row, and the crown gear of the second planetary gear set via a controlled clutch with the planet carrier of the second planetary gear set instead of the controlled clutch connecting the carrier of the second planetary gear set with the input level, allowed us to obtain thirteen forward gears and three reverse gears.

The connection at the same time a sun gear of the first planetary gear set via a controlled clutch with the input element, a sun gear of the second planetary gear set via a controlled clutch with the planet carrier of the third planetary series, a sun gear of the first planetary gear set via a controlled clutch with the planet carrier of the first planetary series, a sun gear of the third planetary series through controlled clutch with the planet carrier of the third planetary series allowed us to obtain thirteen forward gears and three reverse gears.

The connection at the same time a sun gear of the first planetary gear set via a controlled clutch with the input element, a sun gear of the second planetary gear set via a controlled clutch with the planet carrier of the third planetary series, the crown gear of the first planetary gear set via a controlled clutch with the planet carrier of the first planetary series, a sun gear of the third planetary series through controlled clutch with the planet carrier of the third planetary series allowed us to obtain thirteen forward x�and three reverse gears.

The connection at the same time a sun gear of the first planetary gear set via a controlled clutch with the input element, a sun gear of the second planetary gear set via a controlled clutch with the planet carrier of the third planetary series, a sun gear of the first planetary gear set via a controlled clutch with the planet carrier of the first planetary series, a sun gear of the third planetary series through controlled clutch with the planet carrier of the third planetary series and the crown gear of the second planetary gear set via a controlled clutch with the planet carrier of the second planetary gear set instead of the controlled clutch connecting the carrier of the second planetary gear set with the input level, allowed us to obtain thirteen forward gears and three reverse gears.

The connection at the same time a sun gear of the first planetary gear set via a controlled clutch with the input element, a sun gear of the second planetary gear set via a controlled clutch with the planet carrier of the third planetary series, the crown gear of the first planetary gear set via a controlled clutch with the planet carrier of the first planetary series, a sun gear of the third planetary series through controlled clutch with the planet carrier of the third planetary series and the crown gear of the second planetary gear set via a controlled clutch with the planet carrier of the second planetary gear set instead of the managed m�fty, connecting the carrier of the second planetary gear set with the input level, allowed us to obtain thirteen forward gears and three reverse gears.

Fig.1 is a kinematic diagram of a hydromechanical transmission for a vehicle powertrain with six forward and two reverse gears.

Fig.2 - plan of angular velocities of the hydromechanical transmission for a vehicle powertrain with six forward and two reverse gears.

Fig.3 is a kinematic diagram of a hydromechanical transmission for a powertrain of a vehicle with seven forward and three reverse gears.

Fig.4 is a kinematic diagram of a hydromechanical transmission for a powertrain of a vehicle with seven forward and two reverse gears.

Fig.5 is a kinematic diagram of a hydromechanical transmission for a powertrain of a vehicle with seven forward and two reverse gears.

Fig.6 is a kinematic diagram of a hydromechanical transmission for a vehicle powertrain with six forward and two reverse gears.

Fig.7 is a kinematic diagram of a hydromechanical transmission for a vehicle powertrain with eight gears front�and two reverse gears.

Fig.8 is a kinematic diagram of a hydromechanical transmission for a vehicle powertrain with eight forward and two reverse gears.

Fig.9 is a kinematic diagram of a hydromechanical transmission for a powertrain of a vehicle with nine forward and two reverse gears.

Fig.10 is a kinematic diagram of a hydromechanical transmission for a vehicle powertrain with thirteen forward and three reverse gears;

Fig.11 is a kinematic diagram of a hydromechanical transmission for a vehicle powertrain with thirteen forward and three reverse gears;

Fig.12 - the kinematic diagram of a hydromechanical transmission for a vehicle powertrain with thirteen forward and three reverse gears;

Fig.13 - the kinematic diagram of a hydromechanical transmission for a vehicle powertrain with thirteen forward and three reverse gears;

Fig.14 - the kinematic diagram of a hydromechanical transmission for a vehicle powertrain with thirteen forward and three reverse gears;

Fig.15 - the kinematic diagram of a hydromechanical transmission for transmi�these vehicles with thirteen forward and three reverse gears;

Fig.16 - the kinematic diagram of a hydromechanical transmission for a vehicle powertrain with thirteen forward and three reverse gears;

Fig.17 - the kinematic diagram of a hydromechanical transmission for a vehicle powertrain with thirteen forward and three reverse gears;

Fig.18 plan of angular velocities of the hydromechanical transmission for a vehicle powertrain with thirteen forward and three 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 provides a set of attributes.

To obtain six forward gears and two reverse gears in the hydromechanical transmission containing a hydrodynamic torque Converter and planetary gearing driven with three controlled brakes and managed two couplings included in pairs, carrier of the third planetary series connected with a crown gear of the first planetary gear set and with the output element, a sun gear of the third planetary series connected brake with a gear housing, the crown gear of the third planetar�th row is connected with the planet carrier of the second planetary gear set, a sun gear of the second planetary series connected with the output element of the hydrodynamic torque Converter and directly with the input element of the gearbox and through the clutch with the planet carrier of the second planetary range, carrier of the second planetary series is connected through the clutch with a sun gear of the first planetary series, the crown gear of the second planetary series connected with the planet carrier of the first planetary series, and through the brake with a gear housing, a sun gear of the first planetary series is connected through the brake with the gear housing.

To obtain seven speeds forward and three reverse gears according to the first example implementation of the kinematic scheme sun gear of the first planetary series can be connected through additional controlled clutch with the input element.

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

To obtain seven speeds forward and two reverse gears according to the first example implementation of the kinematic scheme of the crown gear of the first planetary series can be connected via additional�th controlled clutch with the planet carrier of the first planetary gear set.

To obtain six forward gears and two reverse gears according to the first example implementation of the kinematic scheme of the crown gear of the second planetary series can be connected via a controlled clutch with the planet carrier of the second planetary gear set instead of the controlled clutch connecting the driving member with the planet carrier of the second planetary gear set.

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

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

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

To obtain thirteen forward gears and three reverse gears according to the second example implementation of the kinematic scheme of the solar sister�I of the second planetary gear set may be connected through additional controlled clutch with the planet carrier of the third planetary gear set, a sun gear of the first planetary series can be connected through additional controlled clutch with the planet carrier of the first planetary series, the crown gear of the third planetary series can be connected through additional controlled clutch with the planet carrier of the third planetary gear set.

To obtain thirteen forward gears and three reverse gears according to the second example implementation of the kinematic scheme sun gear of the second planetary gear set may be connected through additional controlled clutch with the planet carrier of the third planetary series, a sun gear of the first planetary series can be connected through additional controlled clutch with the planet carrier of the first planetary series carrier of the third planetary series can be connected through additional controlled clutch with a crown gear of the third planetary series, the crown gear of the second planetary series can be connected via a controlled clutch with the planet carrier of the second planetary gear set instead of the controlled clutch connecting the carrier of the second planetary gear set with the input link.

To obtain thirteen forward gears and three reverse gears according to the second example implementation of the kinematic scheme sun gear of the second planetary gear set may be connected through additional controlled coupling in�Dean of the third planetary gear set, drove the first planetary series can be connected through additional controlled clutch with a crown gear of the first planetary series carrier of the third planetary series can be connected through additional controlled clutch with a crown gear of the third planetary gear set.

To obtain thirteen forward gears and three reverse gears according to the second example implementation of the kinematic scheme sun gear of the second planetary gear set may be connected through additional controlled clutch with a crown gear of the third planetary series, drove the first planetary series can be connected through additional controlled clutch with a crown gear of the first planetary series carrier of the third planetary series can be connected through additional controlled clutch with a crown gear of the third planetary series, the crown gear of the second planetary series can be connected via a controlled clutch with the planet carrier of the second planetary gear set instead of the driven clutch, connecting the carrier of the second planetary gear set with the input element.

To obtain thirteen forward gears and three reverse gears according to the second example implementation of the kinematic scheme sun gear of the second planetary series can be connected via an additional upravlyaemomu with the planet carrier of the third planetary gear set, a sun gear of the first planetary series can be connected through additional controlled clutch with the planet carrier of the first planetary series, a sun gear of the third planetary series can be connected through additional controlled clutch with the planet carrier of the third planetary gear set.

To obtain thirteen forward gears and three reverse gears according to the second example implementation of the kinematic scheme sun gear of the second planetary gear set may be connected through additional controlled clutch with the planet carrier of the third planetary series, the crown gear of the first planetary series can be connected through additional controlled clutch with the planet carrier of the first planetary series, a sun gear of the third planetary series can be connected through additional controlled clutch with the planet carrier of the third planetary gear set.

To obtain thirteen forward gears and three reverse gears according to the second example implementation of the kinematic scheme sun gear of the second planetary gear set may be connected through additional controlled clutch with the planet carrier of the third planetary series, a sun gear of the first planetary series can be connected through additional controlled clutch with the planet carrier of the first planetary series, a sun gear of the third planets�rnogo number can be connected through additional controlled clutch with the planet carrier of the third planetary gear set, crown gear of the second planetary series can be connected via a controlled clutch with the planet carrier of the second planetary gear set instead of the controlled clutch connecting the carrier of the second planetary gear set with the input element.

To obtain thirteen forward gears and three reverse gears according to the second example implementation of the kinematic scheme sun gear of the second planetary gear set may be connected through additional controlled clutch with the planet carrier of the third planetary series, the crown gear of the first planetary series can be connected through additional controlled clutch with the planet carrier of the first planetary series, a sun gear of the third planetary series can be connected through additional controlled clutch with the planet carrier of the third planetary series, the crown gear of the second planetary series can be connected via a controlled clutch with the planet carrier of the second planetary gear set instead of the controlled clutch connecting the carrier of the second planetary gear set with the input link.

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

Automatic transmission that realizes six forward gears and two reverse gear, contains a crankcase 16, the input of pollutants�but 13, the output link 14, a hydrodynamic torque Converter and planetary gear, which includes three planetary series, managed two clutches and three controlled brakes.

In the gearbox according to the invention, planetary gearbox has three planetary gear sets. The first planetary series consists of a sun gear 3, carrier 2 satellites and the crown gear 1 (the epicycle). The second planetary series consists of a sun gear 6, took 5 satellites and the crown gear 4 (the epicycle). The third planetary series consists of a sun gear 9, drove 8 satellites and the crown gear 7 (the epicycle).

The input element 13 is connected with a sun gear 6 of the second planetary gear set and the output element 15 of the hydrodynamic torque Converter. The output link 14 is connected with the planet carrier 8 of the third planetary series and the crown gear 1 of the first planetary gear set. Brake 12 connects the sun gear 9 of the third planetary gear set and the gear housing 16. Brake 11 connects the interconnected carrier 2 of the first planetary series and the crown gear 4 of the second planetary series with the transmission casing 16. Brake 10 connects the sun gear 3 of the first planetary series with the transmission casing 16. The coupling 18 connects the sun gear 3 of the first planetary OC�and linked with the planet carrier 5 of the second planetary series and the crown gear 7 of the third planetary gear set. Coupling 17 connects the carrier 5 of the second planetary number associated with the crown gear 7 of the third planetary gear set, containing interconnected sun gear 6 of the second planetary gear set, the input element 13 of the gearbox and output link 15 of the hydrodynamic torque Converter.

This embodiment of the gearbox allows you to get six forward gears and two reverse gears, using three planetary series and five controls. Thus in the proposed scheme there is no braking power when shifting gears.

Proposed according to the invention hydromechanical transmission operates as follows.

After the start of movement of the vehicle sequential shift gear from 1st to 6th is his acceleration to the desired speed of movement. When the gearbox is in a neutral position none of the controls are enabled.

In the first forward gear included brakes 11 and 12. Thus, the angular speed of the carrier 2 of the first planetary number associated with the crown gear 4 of the second planetary series, a sun gear 9 of the third planetary number of zero.

Torque from the input element 13 is supplied to the sun gear 6 of the second planetary gear set. Further, through tie�record between a carrier 5 of the second planetary series and the crown gear 7 of the third planetary gear set is supplied on a carrier 8 of the third planetary gear set, associated with the crown gear 1 of the first planetary gear set directly to the output link 14.

When switching to the second forward gear brake 11 turns off and the brake 10, the brake 12 is on. Thus, the angular velocity of sun gear 9 of the third planetary gear set and a sun gear 3 of the first planetary series is equal to zero.

Torque from the input element 13 is supplied to the sun gear 6 of the second planetary gear set. Then drove through 5 of the second planetary series and related crown gear 7 of the third planetary gear set is supplied on a carrier 8 of the third planetary series, where it divides into the two streams. The first stream is transmitted from the carrier 8 of the third planetary number associated with the crown gear 1 of the first planetary series, where it should on the carrier 2 of the first planetary number associated with the crown gear 4 of the second planetary gear set. Then this flow of torque comes on drove 5 of the second planetary series, where combined with the initial flow of torque. The second stream from the carrier 8 of the third planetary number is transmitted directly related to the output link 14.

When switching to the third forward gear off the brake 10 and the clutch 18, the brake 12 is on. Thus, HS�new speed sun gear 9 of the third planetary series is equal to zero. Thus the angular speed of the carrier 5 of the second planetary number associated with the crown gear 7 of the third planetary number equal to the angular speed of the sun gear 3 of the first planetary gear set.

Torque from the input element 13 is supplied to the sun gear 6 of the second planetary series and then drove 5 of the second planetary series, where it divides into the two streams. The first flow of torque from the carrier 5 of the second planetary gear set through the clutch 18 is supplied to the sun gear 3 of the first planetary series, where should be connected between the carrier 2 of the first planetary series and the crown gear 4 of the second planetary gear set. Then, entering on drove 5 of the second planetary gear set, the flow of torque is combined with the original. The second flow of torque from the carrier 5 of the second planetary series and related crown gear 7 of the third planetary gear set is supplied on a carrier 8 of the third planetary gear set. Enrolling on a carrier 8 of the third planetary gear set, the flow of torque is divided and follows through an associated crown gear 1 of the first planetary series on carrier 2 of the first planetary series, where combined the first flow of torque, and drove 8 of the third planetary number of the flow of torque is transmitted directly associated with him in�of the output link 14.

When switching to the fourth forward gear off the clutch 18 and the clutch 17, the brake 12 is on. Thus, the angular speed of the sun gear 9 of the third planetary series is equal to zero. Thus the angular speed of the carrier 5 of the second planetary number associated with the crown gear 7 of the third planetary series of equal angular velocity interconnected sun gear 6 of the second planetary gear set and the input link 13.

Torque from the input element 13 through the clutch 17 is supplied to carrier 5 of the second planetary series and related crown gear 7 of the third planetary series and then drove 8 of the third planetary number associated with the crown gear 1 of the first planetary gear set directly to the output link 14.

When switching on the fifth forward gear off the brake 12 and the clutch 18, the clutch 17 remains on. Thus, the angular speed of the sun gear 3 of the first planetary number equal to the angular speed of the carrier 5 of the second planetary number associated with the crown gear 7 of the third planetary gear set, and the equal angular velocity interconnected sun gear 6 of the second planetary gear set and the input element 13 of the gearbox.

Torque from the input element 13 is transmitted through the clutch 17 on the carrier 5 in�section, which the planetary gear set, where it divides into the two streams. The first stream is transmitted from the carrier 5 of the second planetary gear set the sun gear 6 of the second planetary number associated with the input element 13 where it is combined with the initial flow of torque. The second stream from the carrier 5 of the second planetary gear set enters through the crown gear 4 of the second planetary number associated with that gear cage 2 of the first planetary series, where it is again divided into two streams. The first stream enters from the carrier 2 of the first planetary gear set to the sun gear 3 of the first planetary series and then through the clutch 18 on the carrier 5 of the second planetary series, where combined with the initial flow of torque. The second stream is directed from the carrier 2 of the first planetary gear set on the crown gear 1 of the first planetary series connected with the planet carrier 8 of the third planetary series, as well as directly with the output link 14.

When switching on the sixth forward gear off the clutch 18 and the brake 10 is activated, the clutch 17 remains on. Thus, the angular speed of the sun gear 3 of the first planetary series is equal to zero. Thus the angular speed of the carrier 5 of the second planetary number associated with the crown gear 7 of the third planetary series of equal angular velocity interconnected sun gear 6 of the second planet�tion number and input link 13 of the gearbox.

Torque from the input element 13 is transmitted through the clutch 17 on the carrier 5 of the second planetary series, where it divides into the two streams. The first stream is transmitted from the carrier 5 of the second planetary gear set the sun gear 6 of the second planetary number associated with the input element 13 where it is combined with the initial flow of torque. The second stream from the carrier 5 of the second planetary gear set enters through the crown gear 4 of the second planetary number associated with that gear cage 2 of the first planetary series, where it should on the crown gear 1 of the first planetary series connected with the planet carrier 8 of the third planetary series, as well as directly with the output link 14.

On the first reverse gear included brake 11 and the coupling 18. Thus, the angular speed of the carrier 2 of the first planetary number associated with the crown gear 4 of the second planetary number of zero. Thus the angular speed of the sun gear 3 of the first planetary number equal to the angular speed of the carrier 5 of the second planetary number associated with the crown gear 7 of the third planetary gear set.

Torque from the input element 13 is supplied to the sun gear 6 of the second planetary series, drove on 5 of the second planetary series and then through the coupling 18 to the sun gear 3 of the first planetary gear set. Next, the flow �rotameo torque is transmitted to the crown gear 1 of the first planetary gear set, associated with the planet carrier 8 of the third planetary gear set directly to the output link 14.

When switching to the second reverse gear off the brake 11 and turns on the brake 10, the clutch 18 remains turned on. Thus, the angular speed of the sun gear 3 of the first planetary series is equal to zero. Thus the angular speed of the sun gear 3 of the first planetary number equal to the angular speed of the carrier 5 of the second planetary number associated with the crown gear 7 of the third planetary gear set.

Torque from the input element 13 is supplied to the sun gear 6 of the second planetary series, where it should on the crown gear 4 of the second planetary series and its associated carrier 2 of the first planetary gear set. Then the flow of torque on the crown gear 1 of the first planetary series and its associated carrier 8 of the third planetary gear set and directly on the output link 14.

With the introduction of a controllable coupling 19, which connects the related input element 13 and the sun gear of the second planetary gear set with a sun gear 6 of the first planetary gear set 3, the transmission can implement seven speeds forward and three reverse gears.

When switching on the seventh transmission forward gear includes a clutch 19 and the brake 12. Thus, the angular velocity of the solar pole�IDH 9 of the third planetary series is equal to zero. Thus the angular speed of the sun gear 3 of the first planetary series of equal angular velocity interconnected input element 13 and the sun gear 6 of the second planetary gear set.

The flow of torque to the input element 13 is divided into two streams. The first stream via a controlled clutch 19 is supplied to the sun gear 3 of the first planetary series and then drove 2 of the first planetary series, where it is divided and follows the carrier 2 of the first planetary number of the associated crown gear 4 of the second planetary series and then drove 5 of the second planetary series, where combined with the second flow of torque from the input element 13, which passed through the sun gear 6 of the second planetary series on carrier 5 of the second planetary gear set. The second flow of torque from the carrier 2 of the first planetary gear set is fed to the crown gear 1 of the first planetary series and its associated carrier 8 of the third planetary series, where it stacks up with the flow of torque, combined to the planet carrier 5 of the second planetary gear set and passed from carrier 5 of the second planetary series on the related crown gear 7 of the third planetary gear set. The joint on the planet carrier 8 of the third planetary number of threads of the torque is sent directly to the output link 14.

When you enable a third� reverse gear switch on the clutch 19, the brake 11. Thus, the angular velocity interconnected carrier 2 of the first planetary series and the crown gear 4 of the second planetary number equal to zero. Thus the angular speed of the sun gear 3 of the first planetary series of equal angular velocity interconnected input element 13 and the sun gear 6 of the second planetary gear set.

The flow of torque to the input element 13 is divided into two streams. The first stream via a controlled clutch 19 is supplied to the sun gear 3 of the first planetary series, and then on the crown gear 1 of the first planetary series and its associated carrier 8 of the third planetary gear set. The second stream from the input element 13 is supplied to the sun gear 6 of the second planetary series and then drove on 5 of the second planetary series and related crown gear 7 of the third planetary series and then drove 8 of the third planetary series, where combined with the first flow of torque. Joined to the planet carrier 8 of the third planetary gear set, the flow of torque is routed directly to the output link 14.

With the introduction of the controlled coupling 20 which connects the sun gear 3 of the first planetary gear set with connected planet carrier 2 of the first planetary series and the crown gear 4 of the second planetary series transmission can implement seven gears p�higher stroke and two reverse gears.

When switching on the seventh transmission forward gear includes a brake 12 and the sleeve 20. Thus, the angular speed of the sun gear 9 of the third planetary series is equal to zero. Thus the angular speed of the sun gear 3 of the first planetary series of equal angular velocity interconnected carrier 2 of the first planetary series and the crown gear 4 of the second planetary gear set.

Torque from the input element 13 is transmitted to the sun gear 6 of the second planetary series, drove on 5 of the second planetary series and related crown gear 7 of the third planetary series and then drove 8 of the third planetary series, where it divides into the two streams. The first stream from the carrier 8 of the third planetary gear set is fed to an associated crown gear 1 of the first planetary series and then drove 2 of the first planetary series, where it is divided and follows through the sleeve 20 to the sun gear 3 of the first planetary series and then drove on 2 of the first planetary series and the crown gear 4 of the second planetary series, where combined with the initial flow of torque. The second flow of torque from the carrier 8 of the third planetary gear set is supplied directly to the associated output link 14.

With the introduction of a controllable clutch 21 connecting the interconnected water�about 2 of the first planetary series and the crown gear 4 of the second planetary gear set, containing interconnected crown gear 1 of the first planetary series, drove 8 of the third planetary gear set and the output link 14, the transmission can implement seven speeds forward and two reverse gears.

When switching on the seventh transmission forward gear includes a brake 12 and the clutch 21. Thus, the angular speed of the sun gear 9 of the third planetary series is equal to zero. In this case the angular velocity interconnected carrier 2 of the first planetary series and the crown gear 4 of the second planetary series of equal angular velocity interconnected crown gear 1 of the first planetary series, drove 8 of the third planetary gear set and the output link 14.

The flow of torque from the input element 13 is supplied to the sun gear 6 of the second planetary series and then drove 5 of the second planetary series and related crown gear 7 of the third planetary series and then drove 8 of the third planetary series, where it divides into the two streams. The first flow of torque from the carrier 8 of the third planetary gear set is fed to an associated crown gear 1 of the first planetary series, where it should on the carrier 2 of the first planetary series, where it is divided and flows through the coupling 21 on the crown gear 1 of the first planetary series and drove 2 of the first planetary gear set nesmazannuyu with him the crown gear 4 of the second planetary series and then drove 5 of the second planetary gear set, where is merged with the original thread of torque. The second flow of torque from the carrier 8 of the third planetary gear set is supplied directly to the associated output link 14.

With the introduction of a controllable coupling 22 connecting the interconnected carrier 2 of the first planetary series and the crown gear 4 of the second planetary gear set with connected planet carrier 5 of the second planetary series and the crown gear 7 of the third planetary gear set, instead of driven clutch 17, the transmission may realize six forward gears and two reverse gears. Under such replacement driven clutch 22 is included on the same gear that turns on the controlled coupling 17, i.e., at the fourth, fifth and sixth forward gears. In this case the transmission gearbox works as follows.

When you turn on the fourth transmission forward gear includes a brake 12 and the coupling 22. Thus, the angular speed of the sun gear 9 of the third planetary series is equal to zero. In this case the angular velocity interconnected carrier 2 of the first planetary series and the crown gear 4 of the second planetary series of equal angular velocity interconnected drove 5 of the second planetary series and the crown gear 7 of the third planetary gear set.

The flow of torque from the input.�and 13 is supplied to the sun gear 6 of the second planetary series and then drove 5 of the second planetary gear set, where it divides into the two streams. The first stream from the carrier 5 of the second planetary gear set through the clutch 22 on the crown gear 4 of the second planetary series and then drove 5 of the second planetary series, where combined with the initial flow of torque. The second flow of torque from the carrier 5 of the second planetary series on the related crown gear 7 of the third planetary series and then drove 8 of the third planetary gear set and directly associated with the output link 14.

When switching on the fifth forward gear off the brake 12 and the clutch 18, the clutch 22 remains on. Thus, the angular speed of the sun gear 3 of the first planetary series of equal angular velocity interconnected drove 5 of the second planetary series and the crown gear 7 of the third planetary gear set. In this case the angular velocity interconnected carrier 2 of the first planetary series and the crown gear 4 of the second planetary series of equal angular velocity interconnected drove 5 of the second planetary series and the crown gear 7 of the third planetary gear set.

The flow of torque from the input element 13 is supplied to the sun gear 6 of the second planetary series and then drove 5 of the second planetary series, where it divides into three streams. The first thread from drove� 5 of the second planetary gear set via the coupling 18 to the sun gear 3 of the first planetary series and then drove 2 of the first planetary series and related crown gear 4 of the second planetary gear set, where is merged with the second flow of torque from the carrier 5 of the second planetary series, passed from carrier 5 of the second planetary gear set through the clutch 22 on the crown gear 4 of the second planetary gear set. The third flow of torque from the carrier 5 of the second planetary series on the related crown gear 7 of the third planetary series and then drove 8 of the third planetary series, where it divides into the two streams. The first stream from the carrier 8 of the third planetary gear set moves the associated crown gear 1 of the first planetary series and then drove 2 of the first planetary series, where combined with the first flow of torque, moving from carrier 5 of the second planetary gear set. The second flow of torque from the carrier 8 of the third planetary gear set is supplied directly to the associated output link 14.

When switching on the sixth forward gear clutch 18 turns off and the brake 10, the clutch 22 remains on. Thus, the angular speed of the sun gear 3 of the first planetary series is equal to zero. In this case the angular velocity interconnected carrier 2 of the first planetary series and the crown gear 4 of the second planetary series of equal angular velocity interconnected drove 5 of the second planetary series and the crown gear 7 of the third planetary R�Yes.

The flow of torque from the input element 13 is supplied to the sun gear 6 of the second planetary series and then drove 5 of the second planetary series, where it divides into the two streams. The first flow of torque from the carrier 5 of the second planetary gear set through the clutch 22 on the crown gear 4 of the second planetary series and then drove 5 of the second planetary series, where combined with the initial flow of torque. The second flow of torque from the carrier 5 of the second planetary number is supplied to the related crown gear 7 of the third planetary series and then drove 8 of the third planetary series, where it divides into the two streams. The first flow of torque from the carrier 8 of the third planetary gear set moves the associated crown gear 1 of the first planetary series and then drove 2 of the first planetary series and related crown gear 4 of the second planetary series, where combined with the first flow of torque, moving from carrier 5 of the second planetary gear set. The second flow of torque from the carrier 8 of the third planetary gear set is fed to an associated directly to the output link 14.

With the introduction of a controllable coupling 23 connecting the interconnected carrier 5 of the second planetary series and the crown gear 7 of the third planetary gear set with tie�prisoners who had been interconnected crown gear 1 of the first planetary gear set, planet carrier 8 of the third planetary gear set and the output link 14, the gearbox can realize eight forward gears and two reverse gears.

When switching on the seventh transfer included brake 11 and the coupling 23. Thus, the angular velocity interconnected carrier 2 of the first planetary series and the crown gear 4 of the second planetary number equal to zero. In this case the angular velocity interconnected drove 5 of the second planetary series and the crown gear 7 of the third planetary series of equal angular velocity interconnected crown gear 1 of the first planetary series, drove 8 of the second planetary gear set and the output link 14.

The flow of torque from the input element 13 is supplied to the sun gear 6 of the second planetary series and then drove 5 of the second planetary series and related crown gear 7 of the third planetary series, where be took 8 of the third planetary series, where it divides into the two streams. The first stream from the carrier 8 of the third planetary gear set through the clutch 23 is fed to the crown gear 7 of the third planetary series, where combined with the initial flow of torque. The second stream from the carrier 8 of the third planetary gear set is supplied directly to the associated output link 14.

When you turn on the eighth transfer included Tormo� 10 and the coupling 23. Thus, the angular speed of the sun gear 3 of the first planetary series is equal to zero. In this case the angular velocity interconnected drove 5 of the second planetary series and the crown gear 7 of the third planetary series of equal angular velocity interconnected crown gear 1 of the first planetary series, drove 8 of the second planetary gear set and the output link 14.

The flow of torque from the input element 13 is supplied to the sun gear 6 of the second planetary series and then drove 5 of the second planetary series and related crown gear 7 of the third planetary series, where be took 8 of the third planetary series, where it divides into three streams. The first stream from the carrier 8 of the third planetary gear set through the clutch 23 is fed to the crown gear 7 of the third planetary series, where combined with the flow of torque on this element. The second flow of torque from the carrier 8 of the third planetary gear set is fed to an associated crown gear 1 of the first planetary series and then drove 2 of the first planetary series and related crown gear 4 of the second planetary gear set, from where it enters the carrier 5 of the second planetary series, where combined with the initial flow of torque. The third stream from the carrier 8 of the third planetary series arrives on �neposredstvenno associated with the output link 14.

With the introduction of a controllable coupling 24, which connects the sun gear 9 of the third planetary gear set with connected planet carrier 8 of the third planetary series, the crown gear 1 of the first planetary RDA and the output link 14, the gearbox can realize eight forward gears and two reverse gears.

When switching on the seventh transfer included brake 11 and the coupling 24. Thus, the angular velocity interconnected carrier 2 of the first planetary series and the crown gear 4 of the second planetary number equal to zero. In this case the angular velocity interconnected drove 8 of the third planetary series, the crown gear 1 of the first planetary gear set and the output link 14 is equal to the angular speed of the sun gear 9 of the third planetary gear set.

The flow of torque from the input element 13 is supplied to the sun gear 6 of the second planetary series and then drove 5 of the second planetary series and related crown gear 7 of the third planetary series, where be took 8 of the third planetary series, where it divides into the two streams. The first stream from the carrier 8 of the third planetary gear set is fed through the coupling 24 to the sun gear 9 of the third planetary series and then drove 8 of the third planetary series, where combined with the initial flow of torque. Storeybook drove from 8 of the third planetary gear set is supplied directly to the associated output link 14.

When you turn on the eighth transfer included the brake 10 and the coupling 24. Thus, the angular speed of the sun gear 3 of the first planetary series is equal to zero. In this case the angular velocity interconnected drove 8 of the third planetary series, the crown gear 1 of the first planetary gear set and the output link 14 is equal to the angular speed of the sun gear 9 of the third planetary gear set.

The flow of torque from the input element 13 is supplied to the sun gear 6 of the second planetary series and then drove 5 of the second planetary series and related crown gear 7 of the third planetary series, where be took 8 of the third planetary series, where it divides into three streams. The first stream from the carrier 8 of the third planetary gear set is fed through the coupling 24 to the sun gear 9 of the third planetary series and then drove 8 of the third planetary series, where combined with the flow of torque on this element. The second flow of torque from the carrier 8 of the third planetary gear set is fed to an associated crown gear 1 of the first planetary series and then drove 2 of the first planetary series and related crown gear 4 of the second planetary series, drove on 5 of the second planetary series, where combined with the initial flow of torque. The third stream in from�silt 8 of the third planetary gear set is supplied directly to the associated output link 14.

With the introduction of a controllable clutch 25, which connects the related input element 13 and the sun gear 6 of the second planetary gear set with connected planet carrier 8 of the third planetary series, the crown gear 1 of the first planetary gear set and the output link 14, the transmission may realize nine forward gears and two in the rear.

When switching on the seventh transfer included brake 11 and the sleeve 25. Thus, the angular velocity interconnected carrier 2 of the first planetary series and the crown gear 4 of the second planetary number equal to zero. In this case the angular velocity related input element 13 and the sun gear 6 of the second planetary series of equal angular velocity interconnected drove 8 of the third planetary series, the crown gear 1 of the first planetary gear set and the output link 14.

The flow of torque from the input element 13 is supplied to an associated sun gear 6 of the second planetary series, where it divides into the two streams. The first stream from the sun gear 6 of the second planetary gear set is supplied on a carrier 5 of the second planetary series and related crown gear 7 of the third planetary series and then drove 8 of the third planetary series, where combined with the second flow of torque, moving from a sun gear 6 of the second PL�nyamogo range through the coupling 25 on the carrier 8 of the third planetary gear set. Joined to the planet carrier 8 of the third planetary gear set, the flow of torque is routed directly to the output link 14.

When you turn on the eighth transfer included the brake 10 and the coupling 25. Thus, the angular speed of the sun gear 3 of the first planetary series is equal to zero. In this case the angular velocity related input element 13 and the sun gear 6 of the second planetary series of equal angular velocity interconnected drove 8 of the third planetary series, the crown gear 1 of the first planetary gear set and the output link 14.

The flow of torque from the input element 13 is supplied to an associated sun gear 6 of the second planetary series, where it divides into the two streams. The first stream from the sun gear 6 of the second planetary gear set is supplied on a carrier 5 of the second planetary series and related crown gear 7 of the third planetary series and then drove 8 of the third planetary series, where it divides into the two streams, the first of which should be from the carrier 8 of the third planetary number of the associated crown gear 1 of the first planetary series and then drove 2 of the first planetary series and related crown gear 4 of the second planetary gear set, from where it enters the carrier 5 of the second planetary gear set, where is merged with the first thread torque�and, moving from a sun gear 6 of the second planetary gear set. The second flow of torque from the sun gear 6 of the second planetary gear set moves through the sleeve 25 on the carrier 8 of the third planetary series, where combined with the second flow moving from the carrier 8 of the third planetary gear set. Together, the flow of torque from the carrier 8 of the third planetary gear set is supplied directly to the associated output link 14.

When you turn on ninth transmission includes coupling 18 and 25. Thus, the angular speed of the carrier 5 of the second planetary number associated with the crown gear 7 of the third planetary series of equal angular velocity interconnected sun gear 6 of the second planetary gear set and the input element 13 of the gearbox. In this case the angular velocity related input element 13 and the sun gear 6 of the second planetary series of equal angular velocity interconnected drove 8 of the third planetary series, the crown gear 1 of the first planetary gear set and the output link 14.

The flow of torque from the input element 13 is supplied to an associated sun gear 6 of the second planetary series, where it divides into the two streams. The first stream from the sun gear 6 of the second planetary gear set is supplied on a carrier 5 of the second planetary series and the associated Coron�th gear 7 of the third planetary series and then drove 8 of the third planetary gear set, where is split into two streams, the first of which should be from the carrier 8 of the third planetary number of the associated crown gear 1 of the first planetary series and forth on the sun gear 3 of the first planetary series and then drove 5 of the second planetary series, where combined with the first flow of torque, moving from a sun gear 6 of the second planetary gear set. The second flow of torque from the sun gear 6 of the second planetary gear set moves through the sleeve 25 on the carrier 8 of the third planetary series, where combined with the second flow moving from the carrier 8 of the third planetary gear set. Together, the flow of torque from the carrier 8 of the third planetary gear set is supplied directly to the associated output link 14.

Subsequent the introduction of managed couplings 19, 20, 21, 22, 23, 24, 25 in combination with controlled couplings according to the first example implementation 17-18-19-20-23-25 (see Fig.10), 17-18-19-21-23-25 (see Fig.12), 17-18-19-20-24-25 (see Fig.14), 17-18-19-21-24-25 (see Fig.15) and on the fifth example implementation 18-19-20-22-23-25 (see Fig.11), 18-19-21-22-23-25 (see Fig.13), 18-19-20-22-24-25 (see Fig.16), 18-19-21-22-24-25 (see Fig.17) the number of ongoing transmissions in forward and reverse fold, and the flow of torque is not changed.

The schema change and the sequence of the joint inclusion of controls allows you to achieve �ablanovo technical result and a significant extension of the kinematic range of the gearbox, and also the fact that when you switch missing gap power. In addition, due to this it is possible to improve the dynamic characteristics of a transmission and to increase its longevity.

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

1. Hydromechanical transmission containing a hydrodynamic torque Converter and planetary gearing with control elements in the form of three controlled brakes and managed two clutches, in which the carrier of the third planetary series connected with a crown gear of the first planetary gear set and with the output element, a sun gear of the third planetary series connected brake with a gear housing, the crown gear of the third planetary series connected with the planet carrier of the second planetary series, a sun gear of the second planetary series connected with the output element of the hydrodynamic torque Converter and directly with the input element of the gearbox and through the clutch with the planet carrier of the second planetary gear set, carrier of the second planetary series is connected through the clutch with a sun gear of the first planetary series, the crown �esterna of the second planetary series connected with the planet carrier of the first planetary gear set, and through the brake with a gear housing, a sun gear of the first planetary series is connected through the brake with the gear housing.

2. Gearbox according to claim 1, characterized in that the sun gear of the first planetary series is connected through a controlled clutch with the input element.

3. Gearbox according to claim 1, characterized in that the sun gear of the first planetary series is connected through a controlled clutch with the planet carrier of the first planetary gear set.

4. Gearbox according to claim 1, characterized in that the crown gear of the first planetary series is connected through a controlled clutch with the planet carrier of the first planetary gear set.

5. Gearbox according to claim 1, characterized in that the crown gear of the second planetary series is connected through a controlled clutch with the planet carrier of the second planetary gear set, and the controlled clutch connecting the driving member with the planet carrier of the second planetary gear set, removed.

6. Gearbox according to claim 1, characterized in that the crown gear of the third planetary series is connected through a controlled clutch with the planet carrier of the third planetary gear set.

7. Gearbox according to claim 1, characterized in that the sun gear of the third planetary series is connected through a controlled clutch with the planet carrier of the third planetary gear set.

8. Gearbox according to claim 1, characterized in that the sun gear of the second p�hanatamago row are connected via a controlled clutch with the planet carrier of the third planetary gear set.

9. Gearbox according to claim 1, characterized in that simultaneously connected to a sun gear of the first planetary gear set via a controlled clutch with the input element, and the sun gear of the second planetary gear set via a controlled clutch with the planet carrier of the third planetary gear set and a sun gear of the first planetary gear set via a controlled clutch with the planet carrier of the first planetary series and the crown gear of the third planetary series through controlled clutch with the planet carrier of the third planetary gear set.

10. Gearbox according to claim 1, characterized in that simultaneously connected to a sun gear of the first planetary gear set via a controlled clutch with the input element, and the sun gear of the second planetary gear set via a controlled clutch with the planet carrier of the third planetary number and carrier of the first row are connected via a controlled clutch with a sun gear of the first row, and drove the third row are connected via a controlled clutch with a crown gear of the third row and crown gear of the second planetary series is connected through a controlled clutch with the planet carrier of the second planetary gear set, removed controlled clutch connecting the carrier of the second planetary gear set with the input link.

11. Gearbox according to claim 1, characterized in that simultaneously connected to a sun gear of the first planetary gear set via control�trolled coupling with the input link, and a sun gear of the second planetary gear set via a controlled clutch with the planet carrier of the third planetary series and the crown gear of the first planetary gear set via a controlled clutch with the planet carrier of the first planetary series and the crown gear of the third planetary series through controlled clutch with the planet carrier of the third planetary gear set.

12. Gearbox according to claim 1, characterized in that simultaneously connected to a sun gear of the first planetary gear set via a controlled clutch with the input element, and the sun gear of the second planetary gear set via a controlled clutch with the planet carrier of the third planetary number and carrier of the first row are connected via a controlled clutch with a crown gear of the first row, and drove the third row are connected via a controlled clutch with a crown gear of the third row and crown gear of the second planetary series is connected through a controlled clutch with the planet carrier of the second planetary gear set, removed controlled clutch connecting the carrier of the second planetary gear set with the input link.

13. Gearbox according to claim 1, characterized in that simultaneously connected to a sun gear of the first planetary gear set via a controlled clutch with the input element, and the sun gear of the second planetary gear set via a controlled clutch with the planet carrier of the third planetary gear set and a sun gear �pervogo the planetary gear set via a controlled clutch with the planet carrier of the first planetary gear set, and a sun gear of the third planetary series through controlled clutch with the planet carrier of the third planetary gear set.

14. Gearbox according to claim 1, characterized in that simultaneously connected to a sun gear of the first planetary gear set via a controlled clutch with the input element, and the sun gear of the second planetary gear set via a controlled clutch with the planet carrier of the third planetary series and the crown gear of the first planetary gear set via a controlled clutch with the planet carrier of the first planetary gear set and a sun gear of the third planetary series through controlled clutch with the planet carrier of the third planetary gear set

15. Gearbox according to claim 1, characterized in that simultaneously connected to a sun gear of the first planetary gear set via a controlled clutch with the input element, and the sun gear of the second planetary gear set via a controlled clutch with the planet carrier of the third planetary gear set and a sun gear of the first planetary gear set via a controlled clutch with the planet carrier of the first planetary gear set and a sun gear of the third planetary series through controlled clutch with the planet carrier of the third planetary series and the crown gear of the second planetary gear set via a controlled clutch with the planet carrier of the second planetary gear set, removed controlled clutch, connecting the carrier of the second planetary gear set with the input W�ene.

16. Gearbox according to claim 1, characterized in that simultaneously connected to a sun gear of the first planetary gear set via a controlled clutch with the input element, and the sun gear of the second planetary gear set via a controlled clutch with the planet carrier of the third planetary series and the crown gear of the first planetary gear set via a controlled clutch with the planet carrier of the first planetary gear set and a sun gear of the third planetary series through controlled clutch with the planet carrier of the third planetary series and the crown gear of the second planetary gear set via a controlled clutch with the planet carrier of the second planetary gear set, removed controlled clutch connecting the carrier of the second planetary gear set with the input link.



 

Same patents:

FIELD: transport.

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

EFFECT: more gears in transmission.

1 dwg

FIELD: transport.

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

EFFECT: more gears in transmission.

1 dwg

FIELD: transport.

SUBSTANCE: invention relates to vehicle planetary gearboxes. Automatic gearbox executes nine forward gears and one rear gear comprises crankcase (19), input link (20), output link (21), hydromechanical torque converter and planetary reduction gear. The latter consists of four planetary rows. First row consists of sun gear (3), carrier (2) and crown gear (1). Second row consists of sun gear (6), carrier (5) and crown gear (4). Third row consists of sun gear (9), carrier (8) and crown gear (7). Fourth row consists of sun gear (12), carrier (11) and crown gear (10). Input link (20) engages with output link of hydromechanical torque converter (22), first planetary row sun gear (3) and fourth planetary row sun gear (12). Output link (21) engages with third planetary row crown gear (7). First planetary row crown gear (1) engages with second planetary row carrier (5). Brake (13) couples first row carrier (2) with crankcase of gearbox (19). Brake (14) couples first row carrier (6) with crankcase of gearbox (19). Brake (15) couples engaged third planetary row carrier (8) with fourth planetary row crown gear (10). Clutch (16) engages fourth planetary row sun hear (12) engaged with sun gear (3) and input link (20) with fourth planetary row crown gear (10) engaged with carrier (8). Clutch (17) engages carrier (11) with engaged crown gear (7) and output link (21). Clutch (18) engages crown gear (3) with engaged crown gear (4) and crown gear (9).

EFFECT: increased number of gears.

1 dwg

FIELD: transport.

SUBSTANCE: invention relates to vehicle planetary gearboxes. Automatic gearbox executes nine forward gears and one rear gear comprises crankcase (19), input link (20), output link (21), hydromechanical torque converter and planetary reduction gear. This reduction gear comprises four planetary rows, three controlled clutches and three controlled brakes. First row consists of sun gear (3), carrier (2) and crown gear (1). Second row consists of sun gear (6), carrier (5) and crown gear (4). Third row consists of sun gear (9), carrier (8) and crown gear (7). Fourth row consists of sun gear (12), carrier (11) and crown gear (10). Input link (20) engages with output link of hydromechanical torque converter (22), first planetary row sun gear (3) and second planetary row sun gear (6). Output link (21) engages with fourth planetary row crown gear (10). First planetary row crown gear (1) engages with third planetary row carrier (8). Brake (13) couples first planetary row carrier (2) with crankcase of gearbox (19). Brake (14) couples third planetary row carrier (9) with crankcase of gearbox (19). Brake (15) engages engaged fourth planetary row carrier (11) and second planetary row crown gear (4) with gearbox crankcase (19). Clutch (16) engages first planetary row carrier (2) with engaged third planetary row crown gear (7) and fourth planetary row sun gear (12). Clutch (17) engages second planetary row carrier (5) with engaged fourth planetary row crown gear (10) and output link (21). Clutch (18) engages third planetary row carrier (5) with engaged second planetary row crown gear (4) and fourth planetary row carrier (11).

EFFECT: increased number of gears.

1 dwg

FIELD: automobile production.

SUBSTANCE: automatic gearbox has one planetary gear set (4) and a torque moment transfer route passing parallel to that planetary gear set (4). Planetary gear set (4) at one transmission stage of gearbox (1) is not used for torque moment transfer and is rotated without any relative number of revolutions of its components relative to each other. With that, at the above transmission stage, the structure of the connection of the same planetary gear set (4) has the possibility of being changed by means of coupling clutches (10,11) so that gear transmission ratio of planetary gear set (4) changes from gear transmission ratio of reduced transmission to gear transmission ratio of increased transmission, or vice versa.

EFFECT: simpler design of the device.

10 cl, 33 dwg

FIELD: machine building.

SUBSTANCE: for braking purpose an output shaft of automatic gearbox is connected to a turbine shaft of hydrodynamic torque converter. The external crown (16) of turbine gear under disconnected multidisk brake (11) of reverse gear (10) is slown down or stopped.

EFFECT: higher reliability of the device.

5 cl, 2 dwg

FIELD: transport.

SUBSTANCE: automatic gearbox 1 comprises+ drive side 3, hydrodynamic torque converter 2 and drive side 6. Gearbox 1 has power train flow via said converter 2, mechanical power flows there around and combined power flows. Driven side 6 incorporates one planetary train 7. Besides, it incorporates brake 18 to stop the converter turbine.

EFFECT: compact design and expanded operating performances.

7 cl, 4 dwg

FIELD: machine building.

SUBSTANCE: fluid converter contains centrifugal impeller (1), centripetal turbine wheel (3), axial reactor (5), planetary gear, brake (10) reactor and brake (11) of carrier (9) of the planetary gear unit. Impeller and turbine wheel rotate in one direction. The torque acting on the centreline of reactor (5), rotating in the opposite direction, is added to the torque of centripetal turbine wheel (3), increasing the torque at the output shaft. When h reaches the gear ratio of 0.7, the torque converter operates the in mode of coupling, thereby increasing operating range up to 5.

EFFECT: invention enables to extend the working range of the fluid converter with a forced rotation of the reactor.

1 dwg

Planetary variator // 2374528

FIELD: machine building.

SUBSTANCE: variator contains two planetary rows, control mechanism and controlling link (6). Driving shaft (1) is implemented as through with ability of installation of actuating motor to any its end. The first and the planetary rows are located successively, each of which includes central and crown wheel, spider with satellites. Controlling mechanism is implemented as hydraulic, allows ability of changing of overall gear ratio of variator independently on revolutions of actuating motor is located on driving shaft (1), is immovable fixed on casing (30) and contains monitoring and actuating devices.

EFFECT: invention provides regulation of reduction rates at established modes of driving engine and allows high coefficient of efficiency, high adjustment control area of overall gear ratio, ability of self-adaptation to influence of different external loads.

3 cl, 8 dwg

Planetary gearbox // 2324850

FIELD: transportation, trackless surface vehicles.

SUBSTANCE: invention pertains to the field of motor transport engineering and relates to staggered planetary gear box. The automatic hydro mechanical gear box consists of casing (1), input link (3), output link (4) and planetary reduction gear. In the planetary reduction gear, there are three frictional clutches and four friction brakes. The first planetary gear set consists of central gear (5), drive (6) for satellites and crown gear (7). The second planetary gear set consists of central gear (8), drive (9) for satellites and crown gear (10). The third planetary gear set consists of central gear (11), drive (12) for satellites and crown gear (13). The input link (3) is joined to rigidly interconnected drive (6) and the central gear (8). The crown gear (13) is connected to the output link (4) of the gear box. Drive (9) is connected to the control frictional clutch (15) through drive (6), which is rigidly connected to the central gear (8). Crown gear (10) is connected through the control frictional clutch (16) to drive (12), which is rigidly fixed to the central gear (5). Frictional brakes (17) joins the crown gear (7) to the casing (1) of the gear box. Frictional brakes (18) connect interconnected drive (9) and central gear (11) to the casing (1) of the gear box. Frictional brakes (19) connects the crown gear (10) to the casing (1) of the gear box. Frictional brakes (20) connects interconnected drive (12) and the central gear (5) to the casing (1) of the gearbox. This allows for enhancement of dynamic properties and broadening of the range of transmission ratios.

EFFECT: enhancement of dynamic properties and broadening of the range of transmission ratios.

5 cl, 6 dwg

FIELD: transport.

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

EFFECT: more gears in transmission.

1 dwg

FIELD: transport.

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

EFFECT: more gears in transmission.

1 dwg

FIELD: transport.

SUBSTANCE: in planetary gear each toothed satellite is rigidly connected with one more additional carrier. On additional carriers, more several tapered not toothed satellites are located which are kinematically interconnected by not toothed wheel. Tapered not toothed satellites can engage and disengage with guides located on gear wheel kinematically connected with outer wheel of planetary gear, satellite gears can roll over guides, the guides can rotate and roll over gear rack with possibility of fixation in specified position. When gear wheels roll over the rack the guides can roll and rotate together with these wheels, shafts of guides are connected by means of holders are connected with disk not toothed wheel located on output shaft, the shaft has rigid connection with wheel which is kinematically connected with outer wheel of planetary gear, disk not toothed wheel can rotate together with wheel which has kinematic connection with outer wheel of planetary gear and shift along rotation axis of shaft on which this wheel is located. The disk not toothed wheel is in contact with not toothed wheels fixed on actuating shaft, not toothed wheels on actuating shaft can roll over surface of disk not toothed wheel and to shift together with this wheel and actuating rod along rotation axis of the mentioned shaft, actuating shaft is connected with driving gear.

EFFECT: smooth variation of gear ratio.

11 dwg

FIELD: machine building.

SUBSTANCE: invention relates to the movement devices based on the converter of rotational motion in progressive motion. The movement device under permanent and variable conditions based on the gear of rotation of the massive body, weight, in which the centre of weight rotation is eccentric relatively to the gear axis of rotation. In the converter of the rotation motion in the progressive motion a rod with weights rotation gear is made, at that centre of rotation of the rod periodically moves relatively the driven axis of rotation, thus ensuring the weights movement over the eccentric wheel and creation of the guiding force and device movement.

EFFECT: simplification of the device.

4 cl, 15 dwg

FIELD: transport.

SUBSTANCE: dual clutch is arranged at gearbox input with portion of clutch driven discs fitted at primary shaft and another portion fitted at tubular shaft. Gears engaged with countershaft gears are fitted on said shafts. Countershaft carries six gears, two being engaged with gears fitted on secondary shaft. Three-position clutch with reverse driven gear is arranged there between. Gear engaged with countershaft gear and three-position shift collar are fitted on countershaft tubular extension 8. Simple three-link planetary mechanism and three position clutch 35 is arranged at gearbox output side.

EFFECT: enhanced performances, higher flotation and perfected control.

2 dwg

FIELD: transport.

SUBSTANCE: invention relates to vehicle planetary gearboxes. Automatic gearbox executes nine forward gears and one rear gear comprises crankcase (19), input link (20), output link (21), hydromechanical torque converter and planetary reduction gear. The latter consists of four planetary rows. First row consists of sun gear (3), carrier (2) and crown gear (1). Second row consists of sun gear (6), carrier (5) and crown gear (4). Third row consists of sun gear (9), carrier (8) and crown gear (7). Fourth row consists of sun gear (12), carrier (11) and crown gear (10). Input link (20) engages with output link of hydromechanical torque converter (22), first planetary row sun gear (3) and fourth planetary row sun gear (12). Output link (21) engages with third planetary row crown gear (7). First planetary row crown gear (1) engages with second planetary row carrier (5). Brake (13) couples first row carrier (2) with crankcase of gearbox (19). Brake (14) couples first row carrier (6) with crankcase of gearbox (19). Brake (15) couples engaged third planetary row carrier (8) with fourth planetary row crown gear (10). Clutch (16) engages fourth planetary row sun hear (12) engaged with sun gear (3) and input link (20) with fourth planetary row crown gear (10) engaged with carrier (8). Clutch (17) engages carrier (11) with engaged crown gear (7) and output link (21). Clutch (18) engages crown gear (3) with engaged crown gear (4) and crown gear (9).

EFFECT: increased number of gears.

1 dwg

FIELD: transport.

SUBSTANCE: invention relates to vehicle planetary gearboxes. Automatic gearbox executes nine forward gears and one rear gear comprises crankcase (19), input link (20), output link (21), hydromechanical torque converter and planetary reduction gear. This reduction gear comprises four planetary rows, three controlled clutches and three controlled brakes. First row consists of sun gear (3), carrier (2) and crown gear (1). Second row consists of sun gear (6), carrier (5) and crown gear (4). Third row consists of sun gear (9), carrier (8) and crown gear (7). Fourth row consists of sun gear (12), carrier (11) and crown gear (10). Input link (20) engages with output link of hydromechanical torque converter (22), first planetary row sun gear (3) and second planetary row sun gear (6). Output link (21) engages with fourth planetary row crown gear (10). First planetary row crown gear (1) engages with third planetary row carrier (8). Brake (13) couples first planetary row carrier (2) with crankcase of gearbox (19). Brake (14) couples third planetary row carrier (9) with crankcase of gearbox (19). Brake (15) engages engaged fourth planetary row carrier (11) and second planetary row crown gear (4) with gearbox crankcase (19). Clutch (16) engages first planetary row carrier (2) with engaged third planetary row crown gear (7) and fourth planetary row sun gear (12). Clutch (17) engages second planetary row carrier (5) with engaged fourth planetary row crown gear (10) and output link (21). Clutch (18) engages third planetary row carrier (5) with engaged second planetary row crown gear (4) and fourth planetary row carrier (11).

EFFECT: increased number of gears.

1 dwg

Gearbox // 2531995

FIELD: transport.

SUBSTANCE: invention relates to gearboxes. Gearbox comprises fixed housing, input and output differentials. Every said differential consists of interacting links: sun gear, epicycle, carrier with pinions, input link engaged with input differential sun gear, output link engaged with output differential carrier, gears, controlled clutches, shafts engaged with differential links and articulation between shafts to be thrown in by controlled clutches. Besides, gearbox comprises idler wheel and controlled interlocking clutches for engagement of epicycle with input differential carrier and epicycle with output differential sun gear. This gearbox allows thirteen different speeds of output link revolution on one direction and two speeds in opposite direction.

EFFECT: high efficiency and wide range of gear ratio, reduced metal input.

4 cl, 4 dwg, 1 tbl

FIELD: transport.

SUBSTANCE: group of invention relates to versions of bicycle design and belt drive system. Bicycle comprises the frame and at least one wheel secured to said frame. Wheel has hub, second planetary gearbox arranged therein and belt for torque transmission between first planetary gearbox and second planetary gearbox. In compliance with first version, this frame comprises receiver to accommodate said first planetary gearbox. In compliance with second version, this frame also comprises receiver to accommodate said first planetary gearbox of different design version. In compliance with first version, belt drive system comprises frame, receiver, first planetary gearbox located therein and second planetary gearbox located in wheel hub. In compliance with second version, belt drive system comprises first planetary gearbox arranged in first receiver and second planetary gearbox arranged in second receiver.

EFFECT: decreased weight, better frame clearance.

15 cl, 30 dwg

FIELD: transport.

SUBSTANCE: invention relates to modular A/T. Modular gearbox has planetary system composed of universal range differential wherein spider (5) with three pairs of engaged three-rim pinions is shared by 1st, 2nd and 3rd rows spider, 1st planetary row crown wheel, 2nd row crown wheel and 3rd row central sun gear are engaged by friction brakes with gearbox crankcase. Crown wheel makes an output link of gearbox. Said A/T universal range differential and extra planetary rows allows various design versions.

EFFECT: higher efficiency of gearbox.s

6 cl, 6 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

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