Planetary gearbox

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

 

The invention relates to the field of transport engineering and for the design stage planetary gearbox, which can be used in automatic transmissions, managed with the help of electronic unit and hydraulics and intended for vehicles.

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

The composition of the powertrain includes a transmission of the planetary type, providing the change of torque on the propulsion and speed. Transmission of the planetary type consists of planetary gear sets and friction controls. The planetary series consists of a sun gear which is in constant mesh with gears, which are called satellites, drove defined therein satellites, which can rotate about their axes and the crown gear which is in constant engagement with satellites. There are planetary mechanisms of the first and second class. Planetary mechanisms of the first class have a positive internal gear (when the driver stopped the sun gear and the crown gear is rotated in one hundred the ONU). This sun gear is in constant mesh with the satellite, which is in mesh with another satellite, located on the axis in the driver, which in turn is in mesh with a crown gear. The planetary gears of the second class have a negative internal gear (when the driver stopped the sun gear and the crown gear rotate in opposite directions). This sun gear is in constant mesh with the satellite, which, in turn, is in mesh with a crown gear.

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

Part of the transmission may include a hydrodynamic torque Converter (torque Converter), in which the kinetic energy of the working fluid is used to transfer torque from the engine crankshaft to the input element of the gearbox with the ability to increase the torque.

If the hydrodynamic torque Converter (torque Converter) not used, then g is the solution of torsional vibrations, the resulting non-uniformity of rotation of the engine, between the engine and transmission installed the torsional vibration damper (damper).

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

Currently, planetary gearbox, used vehicles and providing seven to nine speeds forward and one back, include three planetary series, and from seven to nine controls. However, such schemes do not implement dynamic performance requirements for vehicles, reduce the kinematic capabilities of the gearbox, due to the complexity of the rational selection of gear ratios rows and transmission, have low efficiency. To improve the dynamic characteristics of the developers involved in the design and manufacture of automatic transmissions, use the fourth planetary line, which complicates the design of transmission, or increase the number of degrees of freedom. This leads to increased friction controls that are required is to enable transmission, that, in turn, leads to the complication of the control system.

Known transmission containing the planetary gear carrier of the first planetary number of which is connected with the input element of the gearbox, the crown gear of the first planetary number associated friction brake with the transmission housing, and a friction driven coupling with the planet carrier of the second planetary series. The sun gear of the second planetary series connected with the planet carrier of the first planetary series slip-controlled clutch with the planet carrier of the second planetary series, a sun gear of the third planetary series connected with the planet carrier of the second planetary series. The crown gear of the second planetary series connected friction-controlled clutch with the planet carrier of the third planetary series. The sun gear of the first planetary number associated with the crown gear of the third planetary series and managed through a friction clutch with a crown gear of the second planetary series. Carrier of the third planetary series is an output element of the gearbox. The sun gear of the first planetary series is equipped with a friction brake for its connection with the transmission housing. The sun gear of the third planetary series through friction driven clutch connected with the planet carrier of the third planetary series (US 6949048, figa, F16H 3/62, 27.09.2005 the ode).

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

The present invention is directed to the solution of the technical problem to improve the dynamic characteristics of the vehicle due to more rational values of the gear ratios in the transmission, as well as getting a great value gear ratio in first gear compared to the gear ratio to the second forward gear. Another technical challenge is the increase of speeds forward to 9 and increase the range of gear ratios the gearbox to 12.6. Achievable technical result consists in the extension of the kinematic capabilities of the gearbox, increase its durability, and also allows you to greatly expand the number of types of vehicles, which can accommodate the transmission of such kinematic scheme. Obtaining a large value of gear ratio in first gear compared to the gear ratio is receiving at the second forward gear will allow you to refuse the use of the hydrodynamic torque Converter (torque Converter) and use only the torsional vibration. This will reduce the number of parts, dimensions gearbox and reduction of its weight.

This technical result is achieved by the transmission containing the planetary gear carrier of the first planetary number of which is connected with the input element of the gearbox, the crown gear of the first planetary number associated friction brake with the transmission housing, and a friction driven coupling with the planet carrier of the second planetary series, a sun gear of the second planetary series connected with the planet carrier of the first planetary series slip-controlled clutch with the planet carrier of the second planetary series, a sun gear of the third planetary series connected with the planet carrier of the second planetary series, the crown gear of the second planetary series connected friction-controlled clutch with the planet carrier of the third planetary series, the crown gear of the third the planetary series is an output link transmission, a sun gear of the first planetary series connected with the planet carrier of the third planetary series, the third planetary series has a positive gear ratio, carrier of the second planetary number associated friction brake with the transmission housing, the carrier of the third planetary number associated friction brake with the transmission housing, the crown gear of the second planetary the th series is equipped with a friction brake for its connection with the transmission case.

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

The connection carrier of the third planetary series of friction-controlled clutch with a sun gear of the third planetary series allowed us to obtain ten speeds forward and one reverse gear.

The connection carrier of the third planetary series of friction-controlled clutch with a crown gear of the third planetary series, which is the output element of the gearbox, giving the ten speeds forward and one reverse gear.

The connection of the input element of the gearbox with the torsional vibration allowed to damp the torsional vibrations caused by uneven rotation of the engine.

The connection of the input element of a transmission with a hydrodynamic torque Converter has allowed to increase the amount of torque coming in transmission.

The present invention is illustrated by a specific example, which, however, is not only possible, but clearly demonstrates the possibility of achieving the desired technical result is given by a set of attributes.

The essence of the proposed technical R the solutions is illustrated by drawings, where

figure 1 is a kinematic diagram of the planetary nine-storeyed transmission for a vehicle transmission with one reverse gear;

figure 2 - plan of the angular velocity of the planetary nine-storeyed transmission for a vehicle transmission with one reverse gear;

figure 3 is a kinematic diagram of the planetary step transmission for a vehicle transmission with one reverse gear;

figure 4 is a kinematic diagram of the planetary step transmission for a vehicle transmission with one reverse gear;

figure 5 is a kinematic diagram of the planetary nine-storeyed transmission for a vehicle transmission with one reverse gear, equipped with a torsional vibration damper;

figure 6 is a kinematic diagram of the planetary nine-storeyed transmission for a vehicle transmission with one reverse gear, equipped with a hydrodynamic torque Converter (torque Converter).

According to the invention the transmission containing the planetary gear carrier of the first planetary number of which is connected with the input element of the gearbox, the crown gear of the first planetary number associated friction brake is zoom with a transmission housing and a friction driven coupling with the planet carrier of the second planetary series. The sun gear of the second planetary series connected with the planet carrier of the first planetary series slip-controlled clutch with the planet carrier of the second planetary series. The sun gear of the third planetary series connected with the planet carrier of the second planetary series. The crown gear of the second planetary series connected friction-controlled clutch with the planet carrier of the third planetary series. The crown gear of the third planetary series is an output link transmission, a sun gear of the first planetary series connected with the planet carrier of the third planetary series. The third planetary series has a positive speed ratio. Carrier of the second planetary number associated friction brake with the transmission housing, the carrier of the third planetary number associated friction brake with the transmission housing, the crown gear of the second planetary series is equipped with a friction brake for its connection with the transmission case.

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

To obtain ten speeds forward and one reverse gear according to the first example of implementation to the nematic circuit carrier of the third planetary number may be associated friction driven clutch with a crown gear of the third planetary series an output element of the transmission.

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

To get eight speeds forward and one reverse gear according to the first example of implementation of the kinematic scheme sun gear of the third planetary series can be connected friction-controlled clutch with the planet carrier of the third planetary series, which is the output element of the transmission.

For damping torsional vibrations caused by uneven rotation of the engine on the first, second or third example of implementation of the kinematic scheme, the input element of the gearbox is connected with the vibration damper.

To increase the torque input to the transmission according to the first, second and third example implementation of the kinematic scheme of the input element of the gearbox is connected with the hydrodynamic torque Converter (torque Converter).

Below is an example of a specific planetary transmission for an automatic transmission, for example, passenger of all-terrain vehicles.

Automatically the traveler hydromechanical transmission, implementing six speeds forward and one reverse gear, contains a crankcase 1, the input link 3, the output link 4 and the planetary gear, which includes a planetary alignments, three friction clutches and four friction brakes.

In the gearbox, according to the invention, the planetary gear consists of three planetary gear sets. The first planetary series consists of a sun gear 5, drove 6 satellites and the crown gear 7 (epicycle). The second planetary series consists of a sun gear 8, drove 9 satellites and the crown gear 10 (epicycle). The third planetary series consists of a sun gear 11, led 12 satellites and the crown gear 13 (epicycle).

Input link 3 is connected rigidly interconnected with the planet carrier 6 of the first planetary series, and a sun gear 8 of the second planetary series. The crown gear 13 of the third planetary number associated with the output link 4 transmission. Took 9 of the second planetary number associated friction driven clutch 14 with a crown gear 7 of the first planetary number and friction driven clutch 15 with the planet carrier 6 of the first planetary series, which is rigidly connected with the sun gear 8 of the second planetary series. Crown gear 10 of the second planetary number associated friction driven clutch 16 with the planet carrier 12 of the third planetary R is Yes, which is rigidly connected with the sun gear 5 of the first planetary series.

The friction brake 17 is connected with the crankcase 1 gearbox crown gear 7 of the first planetary series. The friction brake 18 is connected with the crankcase 1 transmission interconnected carrier 9 of the second planetary series, and the sun gear 11 of the third planetary series. Friction brake 19 is connected with the crankcase 1 gearbox crown gear 10 of the second planetary series. The friction brake 20 is connected with the crankcase 1 transmission interconnected carrier 12 of the third planetary series, and the sun gear 5 of the first planetary series.

This embodiment of the transmission in comparison with the known seven-speed gearbox type MERCEDES 7G-TRONIC, BMW SMG III, etc. allows you to get nine speeds forward and one reverse gear, using three planetary series and seven friction controls. In the proposed scheme does not happen gap power when shifting gears.

If planetary gearbox add friction driven clutch 21 connecting the sun gear of the third planetary number and carrier of the third planetary series, you can get a gearbox with ten speeds forward and one reverse gear.

If the planet is Noah gearbox add friction driven clutch 22, connecting the carrier of the third planetary series and the crown gear 13 of the third planetary number associated with the output link 4 planetary gearbox, you can get a gearbox with ten speeds forward and one reverse gear.

If planetary gearbox add the torsional vibration damper 2, associated with the input element of the gearbox 3, it appears, absorbing torsional vibrations caused by uneven rotation of the engine.

If planetary gearbox add hydromechanical torque Converter (torque Converter) 2A associated with the input element of the gearbox 3, it appears that increases the amount of torque applied to the input link 3 planetary gearbox.

Equipment transmission ninth forward gear allowed to make changes in gear ratio and the order of the pairwise inclusion friction controls, and allowed to use the scheme as a torque Converter, or just with vibration damper. The change in the structure and sequence of pairwise inclusion of control led to the fact that when switching there is no gap power. Also managed to improve the dynamic characteristics of Korobkina and extend the kinematic capabilities of the gearbox, to increase its durability, as well as significantly expand the number of types of vehicles, which can install the transmission with this configuration.

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

After the start of vehicle motion serial shift from 1st to 9th is the vehicle accelerates to the desired speed. When the transmission is in the neutral position, neither of friction controls are not enabled.

In the first forward gear included brakes 19 and 20. That is, the angular velocity of the crown gear 10 of the second planetary series and took 12 of the third planetary number associated with the sun gear 5 of the first planetary number of zero.

Torque from the input element 3 through the carrier 6 of the first planetary series and rigidly associated with the sun gear 8 of the second planetary number is transmitted to the carrier 9 of the second planetary series and rigidly associated with the sun gear 11 of the third planetary series and forth on the crown gear 13 of the third planetary series, directly connected with the output element 4.

When switching to the second forward gear, the brake 19 is turned off, and turns on the clutch 15, the brake 20 is on. So about what atom, the angular speed of the carrier 12 of the third planetary number associated with the sun gear 5 of the first planetary series is equal to zero, and the angular velocity of the input link 3, rigidly connected to the planet carrier 6 of the first planetary series of rigidly connected to the sun gear 8 of the second planetary number equal to the angular speed of the carrier 9 of the second planetary series of rigidly connected to the sun gear 11 of the third planetary series.

Torque from the input element 3 through the carrier 6 of the first planetary series and further enabled through the friction clutch 15 is transmitted to the carrier 9 of the second planetary series and rigidly associated with the sun gear 11 of the third planetary series and forth on the crown gear 13 of the third planetary series, directly connected with the output element 4.

When switching to the third forward gear off the clutch 15 and turns on the clutch 14, the brake 20 is on. Thus, the angular speed of the carrier 12 of the third planetary number associated with the sun gear 5 of the first planetary series is equal to zero, and the angular velocity of the crown gear 7 of the first planetary number equal to the angular speed of the carrier 9 of the second planetary series of rigidly connected to the sun gear 11 of the third planetary series.

Torque from the input element 3 through the carrier 6 of the first against the second number is transmitted to the crown gear 7 of the first planetary series and further enabled through the friction clutch 14 is transmitted to the carrier 9 of the second planetary series and rigidly associated with the sun gear 11 of the third the planetary series and forth on the crown gear 13 of the third planetary series, directly connected with the output element 4.

When switching to the fourth forward gear off the brake 20 and turns on the clutch 15, the clutch 14 remains enabled. Thus, the angular velocity of the crown gear 7 of the first planetary number equal to the angular speed of the carrier 9 of the second planetary series of rigidly connected to the sun gear 11 of the third planetary series, and the angular velocity of the input link 3, rigidly connected to the planet carrier 6 of the first planetary series of rigidly connected to the sun gear 8 of the second planetary number equal to the angular speed of the carrier 9 of the second planetary series of rigidly connected to the sun gear 11 of the third planetary series.

Torque from the input element 3 is transmitted to the carrier 6 of the first planetary series, where it is divided and transmitted to the sun gear 5 of the first planetary series and rigidly connected with it took 12 of the third planetary series, and through the crown gear 7 of the first planetary number is transmitted to the friction clutch 14 and further drove 9 of the second planetary series, which splits it into two streams. The first flow of torque through the friction clutch 15 is transmitted to the carrier 6 of the first planetary series, where it is combined with the flow of torque moments input link 3. The second flow of torque through the sun gear 11 of the third planetary number is transmitted to the carrier 12 of the third planetary series, where it is combined with the flow of torque from the sun gear 5 of the first planetary series and then passed on the crown gear 13 of the third planetary series, directly connected with the output element 4.

When switching on the fifth forward gear off the clutch 15 and turns on the brake 19, the clutch 14 remains enabled. Thus, the angular velocity of the crown gear 10 of the second planetary series is equal to zero, and the angular velocity of the crown gear 7 of the first planetary number equal to the angular speed of the carrier 9 of the second planetary series of rigidly connected to the sun gear 11 of the third planetary series.

Torque from the input element 3 is transmitted to the carrier 6 of the first planetary series, where it is divided and transmitted to the sun gear 5 of the first planetary series and rigidly connected with it took 12 of the third planetary series, and through the crown gear 7 of the first planetary number is transmitted to the friction clutch 14 and further drove 9 of the second planetary series, which splits it into two streams. The first flow of torque through the sun gear 8 of the second planetary number is transmitted to the carrier 6 of the first planetary series, where the question what is the flow of torque from the input element 3. The second flow of torque through the sun gear 11 of the third planetary number is transmitted to the carrier 12 of the third planetary series, where it is combined with the flow of torque from the sun gear 5 of the first planetary series and then passed on the crown gear 13 of the third planetary series, directly connected with the output element 4.

When switching on the sixth forward gear off the brake 19 and turns on the brake 17, the clutch 14 remains enabled. Thus, the angular velocity of the crown gear 7 of the first planetary series is equal to zero, and the angular velocity of the crown gear 7 of the first planetary number equal to the angular speed of the carrier 9 of the second planetary series of rigidly connected to the sun gear 11 of the third planetary series.

Torque from the input element 3 through the carrier 6 of the first planetary number is transmitted to the sun gear 5 of the first planetary series and rigidly connected with it took 12 of the third planetary series and forth on the crown gear 13 of the third planetary series, directly connected with the output element 4.

When switching on the seventh forward gear off the clutch 14 and turns on the brake 19, the brake 17 is on. Thus, the angular velocity of the crown gear 7 of the first planetary series is equal to zero, and the angular / min net is the crown gear 10 of the second planetary series is equal to zero.

Torque from the input element 3 is transmitted to the carrier 6 of the first planetary series, where it is divided and transmitted to the sun gear 5 of the first planetary series and rigidly connected with it took 12 of the third planetary series, and through the sun gear 10 of the second planetary number is transmitted to the carrier 9 of the second planetary series and rigidly associated with the sun gear 11 of the third planetary series and later on took 12 of the third planetary series, where it is combined with the flow of torque from the sun gear 5 of the first planetary series and then passed on the crown gear 13 of the third planetary series, connected directly with the output link 4.

When switching on the eighth forward gear off the brake 19 and turns on the clutch 15, the brake 17 is on. Thus, the angular velocity of the crown gear 7 of the first planetary series is equal to zero, and the angular velocity of the input link 3, rigidly connected to the planet carrier 6 of the first planetary series of rigidly connected to the sun gear 8 of the second planetary number equal to the angular speed of the carrier 9 of the second planetary series of rigidly connected to the sun gear 11 of the third planetary series.

Torque from the input element 3 is transmitted to the carrier 6 of the first planetary series, where it is divided and transmitted to the u is Chou gear 5 of the first planetary series and rigidly connected with it took 12 of the third planetary series and through the friction clutch 15 is transmitted to the carrier 9 of the second planetary series and rigidly associated with the sun gear 11 of the third planetary series and later on took 12 of the third planetary series, where it is combined with the flow of torque from the sun gear 5 of the first planetary series and then passed on the crown gear 13 of the third planetary series, directly connected with the output element 4.

When switching on the ninth forward gear off the clutch 15 and turns on the clutch 16, the brake 17 is on. Thus, the angular velocity of the crown gear 7 of the first planetary series is equal to zero, and the angular velocity of the crown gear 10 of the second planetary number equal to the angular speed of the carrier 12 of the third planetary series of rigidly connected to the sun gear 5 of the first planetary series.

Torque from the input element 3 is transmitted to the carrier 6 of the first planetary series, where it is divided and transmitted to the sun gear 5 of the first planetary series and rigidly connected with it took 12 of the third planetary series, and through the sun gear 8 of the second planetary number 5 is transmitted to the carrier 9 of the second planetary series and rigidly associated with the sun gear 11 of the third planetary series and later on took 12 of the third planetary series, where obyedinyaet the flow of torque from the sun gear 5 of the first planetary number and then divided into two streams. The first thread torque is transmitted to the crown gear 13 of the third planetary series, directly connected with the output element 4. The second stream of torque transmitted through the included friction clutch 16 on the crown gear 10 of the second planetary series and later on took 9 of the second planetary series, where the combined flow of torque from the sun gear 8 of the second planetary series.

On the reverse gear is activated, the brake 18 and the sleeve 16. Thus, the angular speed of the carrier 9 of the second planetary series and rigidly associated sun gear 11 of the third planetary series is equal to zero, and the angular velocity of the crown gear 10 of the second planetary number equal to the angular speed of the carrier 12 of the third planetary series of rigidly connected to the sun gear 5 of the first planetary series.

Torque from the input element 3 through the carrier 6 of the first planetary series and rigidly associated with the sun gear 8 of the second planetary number is transmitted to the crown gear 10 of the second planetary series and further enabled through the friction clutch 16 is transmitted to the carrier 12 of the third planetary series and forth on the crown gear 13 of the third planetary series, directly connected with the output element 4.

With the introduction of a friction driven clutch 21, which connects the solar the stubble 11 of the third planetary series rigidly connected with the planet carrier 9 of the second planetary series, and took 12 of the third planetary series, rigidly connected with the sun gear 5 of the first planetary series planetary gearbox can implement ten speeds forward and one reverse gear.

When switching on the tenth transmission includes a clutch 21 and the brake 19. Thus, the angular velocity of the crown gear 10 of the second planetary series is equal to zero, and the angular speed of the sun gear 11 of the third planetary series, rigidly connected with the planet carrier 9 of the second planetary number equal to the angular speed of the carrier 12 of the third planetary series of rigidly connected to the sun gear 5 of the first planetary series.

Torque from the input element 3 through the carrier 6 of the first planetary series and rigidly associated with the sun gear 8 of the second planetary number is transmitted to the carrier 9 of the second planetary series and rigidly associated with the sun gear 11 of the third planetary series and later on took 12 of the third planetary series, where it is divided and transmitted to the crown gear 13 of the third planetary series, directly connected with the output element 4, and also enabled through the friction clutch 21 is transmitted to the sun gear 11 of the third planetary series, where it is combined with torque from the carrier 9 of the second plan is ary number.

With the introduction of a friction driven clutch 22, which connects the carrier 12 of the third planetary series, rigidly connected with the sun gear 5 of the first planetary series, and the crown gear 13 of the third planetary series planetary gearbox can implement ten speeds forward and one reverse gear.

When switching on the tenth transmission includes a clutch 21 and the brake 19. Thus, the angular velocity of the crown gear 10 of the second planetary series is equal to zero, and the angular velocity of the crown gear 13 of the third planetary number equal to the angular speed of the carrier 12 of the third planetary series of rigidly connected to the sun gear 5 of the first planetary series.

Torque from the input element 3 through the carrier 6 of the first planetary series and rigidly associated with the sun gear 8 of the second planetary number is transmitted to the carrier 9 of the second planetary series and rigidly associated with the sun gear 11 of the third planetary series and then drove through 12 of the third planetary number is transmitted to the crown gear 13 of the third planetary series, where it is divided and transmitted directly to the output link 4, and enabled through the friction clutch 22 is transmitted to the carrier 12 of the third planetary series, where it is combined with the torque from the sun gear 11 of the third PLA is eternulo series.

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

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

1. Transmission containing the planetary gear carrier of the first planetary number of which is connected with the input element of the gearbox, the crown gear of the first planetary number associated friction brake with the transmission housing, and a friction driven coupling with the planet carrier of the second planetary series, a sun gear of the second planetary series connected with the planet carrier of the first planetary series slip-controlled clutch with the planet carrier of the second planetary series, a sun gear of the third planetary series connected with the planet carrier of the second planetary series, the crown gear of the second planetary series connected friction-controlled clutch with the planet carrier of the third against the second number, wherein the crown gear of the third planetary series is an output link transmission, a sun gear of the first planetary series connected with the planet carrier of the third planetary series, the third planetary series has a positive gear ratio, carrier of the second planetary number associated friction brake with the transmission housing, the carrier of the third planetary number associated friction brake with the transmission housing, the crown gear of the second planetary series is equipped with a friction brake for its connection with the transmission case.

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

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

4. Transmission according to any one of claims 1 to 3, characterized in that the input element of the gearbox is connected with the vibration damper.

5. Transmission according to any one of claims 1 to 3, characterized in that the input element of the gearbox is connected with the hydrodynamic torque Converter.



 

Same patents:

FIELD: mechanical engineering.

SUBSTANCE: proposed hydromechanical variable-speed drive has drive and driven shafts, torque converter and two planetary trains. First planetary train has epicyclical gear connected with driven shaft, sun gear, central gear connected with torque converter impeller, and carrier with two-rim planet pinions connected with driven shaft. Reactor of torque converter is connected with driven shaft. Second planetary train has epicyclical gear, sun gear and carrier with planet pinions. Epicyclical gear of first planetary train is in meshing with small rims of two-rim planet pinions. Turbine of torque converter is connected with carrier of second planetary train, and its epicyclical gear is connected with driven shaft.

EFFECT: simplified design, increased service life of engine, reduced consumption of fuel.

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FIELD: transport engineering; automatic transmissions.

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

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EFFECT: expanded functional capabilities and prolonged service life.

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SUBSTANCE: hydromechanical gear box comprises crankcase (1), torsional vibration damper (2), input link (3), output link (4), planet gear made of three planet rows, two friction clutches, and four friction brakes. First planet row is made of solar pinion (5), carrier (6) of satellites, and corona pinion (7). Second planet row is made of solar pinion (8), carrier (9) of satellites, and corona pinion (10). Third planet row is made of solar pinion (11), carrier (12) of satellites, and corona pinion (13). Input link (3) is connected with corona pinion (13) and carrier (9) through friction clutch (14). Input link (3) is connected corona pinion (10) and solar pinion (11) through friction clutch (15). Carrier (6) is connected with input link (3). Input link (3) is connected with torsional vibration damper (2). Friction brake (16) connects corona pinion (10) and solar pinion (11) with crankcase (1) of the gear box. Friction brake (17) connects corona pinion (13) and carrier (9) with crankcase (1) of the gear box. Friction brake (18) connects solar pinion (5) and solar pinion (8) with crankcase (1) of the gear box. Corona pinion (7) is connected with crankcase (1) through friction brake (19). Carrier (12) is connected with output link (4) of the gear box.

EFFECT: expanded functional capabilities and prolonged service life.

1 dwg

FIELD: mechanical engineering.

SUBSTANCE: hydromechanical gear box comprises crankcase (1), fluid transformer (2), input link (3), output link (4), planet reduction gear, three friction clutches, and three friction brakes. The planet reduction gear is made of three planet rows. First planet row is made of solar pinion (5), carrier (6) of satellites, and corona pinion (7). Second planet row is made of solar pinion (8), carrier (9) of satellites, and corona pinion. Third planet row is made of solar pinion (11), carrier (12) of satellites, and corona pinion (13). Input link (3) is connected with interconnected solar pinion (8) and solar pinion (11) through friction clutch (14) and with interconnected carrier (9) and (12) through friction clutch (15). Carrier (9) is connected with corona pinion (13) connected with the output link (4) of the gear box through friction clutch (16). Solar pinion (5) is connected with input link (3). Carrier (6) is connected with crankcase (1) of the gear box through friction brake (17). Friction brake (18) connects interconnected carrier (9) and (12) with crankcase (1). Friction brake (19) connects interconnected solar pinion (8) and (11) with crankcase (1).

EFFECT: expanded functional capabilities.

3 cl, 6 dwg

FIELD: mechanical engineering.

SUBSTANCE: hydromechanical gear box comprises crankcase (1), fluid transformer (2), input link (3), output link (4), planet reduction gear, three friction clutches, and three friction brakes. The planet reduction gear consists of three planet rows. First planet row is made of solar pinion (5), carrier (6) of satellites, and corona gear (7). Second planet row is made of solar pinion (8), carrier (9) of satellites, and corona gear (10). Third planet row is made of solar pinion (11), carrier (12) of satellites, and corona gear (13). Input link (3) is connected with interconnected solar pinion (8) and solar pinion (11) through friction clutch (14) and with interconnected carrier (9) and carrier (12) through friction clutch (15). Carrier (9) is connected with corona gear (10) connected with corona gear (7) through friction clutch (16). Solar pinion (5) is connected with output link (3). Carrier (6) is connected with crankcase (1) of the gear box through friction brake (17). Friction brake (18) connects interconnected carries (9) and (12) with crankcase (1). Friction brake (19) connects interconnected solar gear (8) and (11) with crankcase (1).

EFFECT: expanded functional capabilities.

3 cl, 6 dwg

FIELD: automotive industry.

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

EFFECT: expanded functional capabilities.

8 cl, 11 dwg

FIELD: automotive industry.

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

EFFECT: expanded functional capabilities.

8 cl, 11 dwg

FIELD: automotive industry.

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

EFFECT: expanded functional capabilities and prolonged service life.

8 cl, 11 dwg

FIELD: automotive industry.

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

EFFECT: expanded functional capabilities and prolonged service life.

8 cl, 11 dwg

FIELD: mechanical engineering.

SUBSTANCE: hydromechanical gear box comprises crankcase (1), fluid transformer (2), input link (3), output link (4), planet reduction gear, three friction clutches, and three friction brakes. The planet reduction gear is made of three planet rows. First planet row is made of solar pinion (5), carrier (6) of satellites, and corona pinion (7). Second planet row is made of solar pinion (8), carrier (9) of satellites, and corona pinion. Third planet row is made of solar pinion (11), carrier (12) of satellites, and corona pinion (13). Input link (3) is connected with interconnected solar pinion (8) and solar pinion (11) through friction clutch (14) and with interconnected carrier (9) and (12) through friction clutch (15). Carrier (9) is connected with corona pinion (13) connected with the output link (4) of the gear box through friction clutch (16). Solar pinion (5) is connected with input link (3). Carrier (6) is connected with crankcase (1) of the gear box through friction brake (17). Friction brake (18) connects interconnected carrier (9) and (12) with crankcase (1). Friction brake (19) connects interconnected solar pinion (8) and (11) with crankcase (1).

EFFECT: expanded functional capabilities.

3 cl, 6 dwg

FIELD: mechanical engineering.

SUBSTANCE: hydromechanical gear box comprises crankcase (1), fluid transformer (2), input link (3), output link (4), planet reduction gear, three friction clutches, and three friction brakes. The planet reduction gear consists of three planet rows. First planet row is made of solar pinion (5), carrier (6) of satellites, and corona gear (7). Second planet row is made of solar pinion (8), carrier (9) of satellites, and corona gear (10). Third planet row is made of solar pinion (11), carrier (12) of satellites, and corona gear (13). Input link (3) is connected with interconnected solar pinion (8) and solar pinion (11) through friction clutch (14) and with interconnected carrier (9) and carrier (12) through friction clutch (15). Carrier (9) is connected with corona gear (10) connected with corona gear (7) through friction clutch (16). Solar pinion (5) is connected with output link (3). Carrier (6) is connected with crankcase (1) of the gear box through friction brake (17). Friction brake (18) connects interconnected carries (9) and (12) with crankcase (1). Friction brake (19) connects interconnected solar gear (8) and (11) with crankcase (1).

EFFECT: expanded functional capabilities.

3 cl, 6 dwg

FIELD: automotive industry.

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

EFFECT: expanded functional capabilities.

8 cl, 11 dwg

FIELD: automotive industry.

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

EFFECT: expanded functional capabilities.

8 cl, 11 dwg

FIELD: automotive industry.

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

EFFECT: expanded functional capabilities and prolonged service life.

8 cl, 11 dwg

FIELD: automotive industry.

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

EFFECT: expanded functional capabilities and prolonged service life.

8 cl, 11 dwg

FIELD: transport engineering.

SUBSTANCE: invention relates to planetary transmission used in vehicle automatic transmission systems. Proposed transmission contains hydrodynamic torque converter 2 and planetary reduction gear. Carrier 6 of first planetary gear train is coupled by friction brake 17 with transmission case. Crown gear 7 of first planetary gear train is coupled with carrier 12 of third planetary gear train being output member 4 of transmission. Output member 3 of hydrodynamic torque converter is coupled with sun gear 8 second planetary gear train and by friction controlled clutch 15 with sun gear 5 of first planetary gear train. Sun gear 11 of third planetary gear is coupled by friction brake 18 with transmission case. Output member 3 of hydraulic torque converter is coupled by friction controlled clutch 14 with carrier 6 of first planetary gear train. Sun gear 5 of first planetary gear train is coupled by friction brake 16 with transmission case 1. Crown gear 10 of second planetary gear train is coupled with crown gear 13 of third planetary gear train. Carrier 6 of first planetary gear train is coupled with carrier 9 of second planetary gear train.

EFFECT: enlarged kinematic capabilities increased service life of transmission.

9 cl, 11 dwg

FIELD: transport engineering.

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

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

12 cl, 14 dwg

FIELD: transport engineering.

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

EFFECT: enlarged kinematic capabilities increased service life of transmission.

24 cl, 26 dwg

FIELD: transport engineering.

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

EFFECT: enlarged kinematic capabilities, increase life of transmission.

24 cl, 28 dwg

FIELD: transport engineering.

SUBSTANCE: input shaft 2 and primary shaft 3 are coaxially installed in supports of gearbox housing. Secondary shaft 4, carrier shaft 5 and output shaft 6 are arranged parallel to coaxial shafts 2 and 3. Gear 7 is fixed on primary shaft 3, gear 8 is freely fitted at one side and gear cluster consisting of two gears 9 and 10 is installed at other side. Gear cluster consisting of gears 11 and 12 engaging with gears 8 and 7 of primary shaft and gears 13 and 14 engaging with cluster of gears 9 and 10 on primary shaft are installed on secondary shaft 4. Sun gear 15a of planetary mechanism is secured at output of secondary shaft 4, said gear being engaged with planet pinions 16 arranged on axles of carrier 17H. Planet pinions 16 are in meshing with epicyclic wheel 18b. Gear 8 is connected by tubular shaft 19 with gear rim 20, gear rim 21 is secured on primary shaft 3, and three-position gear rim 22 is secured on input shaft 2, three-position shifter clutch 23A being fitted on gear rim 22. Two position twin clutch B consists of clutches 24 and 25 interconnected by shifter fork 26. Clutch 24 is installed on gear rim of gear 7 of primary shaft 3, and clutch 25, on gear rim of gear 13 of secondary shaft 4. Two-position clutch 27C is fitted on hub of secondary shaft 4 between gears 13 and 14. Gear rim 28 is secured on tubular shaft 29 of housing of epicyclic wheel 18. Two-position gear rim 30 is secured on carrier shaft 5. Three-position gear rim 31 is secured on output shaft 6 which carries shifter clutch 32 connected for sliding with slider 33. Gear rim 34 with internal and external meshing is secured on slider 33, external teeth being engaged with three-position gear rim 35 of housing 1, and gear rim 36 of carrier 17 and gear rim 37 of housing of epicyclic wheel 18 are arranged opposite to external gearing.

EFFECT: reduced metal usage, simplified design of gearbox.

2 dwg

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