Transmission

FIELD: transport engineering.

SUBSTANCE: invention relates to design of planetary transmission which can be used in automatic transmission systems controlled by electronic and hydraulic control units for use in road vehicles. Proposed transmission contains planetary reduction gear, carrier 6 of planetary gear train being output member 4 of transmission. Carrier 9 of second planetary gear train is coupled with crown gear (epicycle) 7 of first planetary gear train. Sun gear 5 of first planetary gear train is coupled with epicycle 10 of second planetary gear train and by brake 16, with transmission case. Sun gear 8 of second planetary gear train is coupled with sun gear 11 of third planetary gear train and by brake 18, with transmission case. Input member 3 is coupled with carrier 12 of third planetary gear train. Epicycle 13 of third planetary gear train is coupled by brake 19 with transmission case. Input member 3 is coupled by clutch 14 with carrier 9 of second planetary gear train. Epicycle 7 is provided with brake 17 for coupling with transmission case. Input member 3 is coupled by clutch 15 with sun gear 5. Input member 3 is coupled also with torsional vibration damper 2. Reduction of overall dimensions of transmission makes it possible to enlarged range of vehicle in which proposed transmission with such kinematic diagram can be used, and dynamic characteristics of vehicle are considerable improved owing to change of design of transmission and change of gear ratios of planetary gear trains and order of in-pair engagement of friction control member.

EFFECT: enlarged kinematic capabilities of transmission, increased service life, reduced mass owing to dispensing with torque converter and reduced number of transmission components.

1 dwg

 

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

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

Part of an automatic transmission includes a transmission of the planetary type, providing the change of torque on the propulsion and speed. The transmission also includes a friction controls that its purpose can be divided into two groups: brakes and clutches. A friction clutch connecting the elements of the planetary mechanism between them. Friction brakes combine elements of the planetary mechanism with the transmission case.

The use of planetary gearboxes 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 boxes in front of the h used for vehicles and providing seven speeds forward and one back, include three planetary series and six controls. However, such schemes do not implement dynamic performance requirements for vehicles, reduce the kinematic capabilities of the gearbox, reducing its durability. To improve the dynamic characteristics of the developers involved in the design and manufacture of automatic transmissions, use the fourth planetary line, which complicates the design of transmission, or increase the number of degrees of freedom. This leads to increased friction controls that you want to enable transmission, which, in turn, leads to the complication of the control system.

Known transmission containing the planetary gear carrier of the first planetary number which is the output element of the gearbox, pinion carrier of the second planetary number is associated with the crown gear of the first planetary series, a sun gear of the first planetary number associated with the crown gear of the second planetary number and friction brake with the transmission housing, a sun gear of the second planetary series connected with a sun gear of the third planetary series, frictio the NYM brake with the transmission housing, the input link is connected with the planet carrier of the third planetary series, the crown gear of the third planetary number associated friction brake with the transmission housing, the carrier of the second planetary series connected friction-controlled clutch with a crown gear of the third planetary series slip-controlled clutch with the planet carrier of the third planetary series, planet carrier of the third planetary series connected friction-controlled clutch with a sun gear of the third planetary series (US 6679802, F 16 H 3/66, figa, from 28.08.2003 year).

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

The present invention is directed to the solution of the technical problem to improve the dynamic characteristics of the vehicle, using the minimum possible number of controls. Achievable technical result consists in the extension of the kinematic capabilities of the transmission, increasing its durability, reducing the number of parts, and allows things the government to expand the number of types of vehicles, you can install the transmission with this configuration.

This technical result is achieved in that in a gear box containing a planetary gear carrier of the first planetary number which is the output element of the gearbox, pinion carrier of the second planetary number is associated with the crown gear of the first planetary series, a sun gear of the first planetary number associated with the crown gear of the second planetary number and friction brake with the transmission housing, a sun gear of the second planetary series connected with a sun gear of the third planetary number and friction brake with the transmission housing, an input link connected with the planet carrier of the third planetary series, the crown gear of the third planetary number associated friction brake with the transmission housing, the input link is connected friction-controlled clutch with the planet carrier of the second planetary series, the crown gear of the first planetary series is equipped with a friction brake for its connection with the transmission housing, an input link connected friction-controlled clutch with a sun gear of the first planetary series, the input link is connected with torsional vibration.

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

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

The essence of the proposed technical solution is illustrated by a drawing, which

shows the kinematic diagram of a hydromechanical seven speed transmission for a vehicle transmission with one reverse gear.

According to the invention the transmission containing the planetary gear carrier of the first planetary number which is the output element of the gearbox, pinion carrier of the second planetary number is associated with the crown gear of the first planetary series, a sun gear of the first planetary number associated with the crown gear of the second planetary number and friction brake with the transmission housing, a sun gear of the second planetary series connected with a sun gear of the third planetary number and friction brake with the transmission housing, an input link connected with the planet carrier of the third planetary series, the crown gear of the third planetary number associated friction brake with the transmission housing, an input link connected friction at the monitor coupling with the planet carrier of the second planetary series the crown gear of the first planetary series is equipped with a friction brake for its connection with the transmission housing, an input link connected friction-controlled clutch with a sun gear of the first planetary series, the input link is connected with torsional vibration.

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

Automatic hydromechanical transmission, implementing six speeds forward and one reverse gear, contains a crankcase 1, the torsional vibration damper 2, entry level 3, the output link 4 and the planetary gear, which includes a planetary alignments, two friction clutches and four friction brakes.

In the gearbox, according to the invention, the planetary gear consists of three planetary gear sets. The first planetary series consists of a sun gear 5, drove 6 satellites and the crown gear 7 (epicycle). The second planetary series consists of a sun gear 8, drove 9 satellites and the crown gear 10 (epicycle). The third planetary series consists of a sun gear 11, led 12 satellites and the crown gear 13 (epicycle). Input link 3 is connected by a slip clutch 14 with interconnected crown gear 7 a is pout planetary series and planet carrier 9 of the second planetary series. Input link 3 is connected by a slip clutch 15 with interconnected crown gear 10 of the second planetary series, and a sun gear 5 of the first planetary series. Drove 12 of the third planetary number associated with the input link 3. Input link 3 is connected with torsional vibration damper 2. The friction brake 16 is connected with the crankcase 1 gearbox connected between a crown gear 10 of the second planetary series, and the sun gear 5 of the first planetary series. The friction brake 17 is connected with the crankcase 1 gearbox connected between a crown gear 7 of the first planetary series, and led 9 of the second planetary series. The friction brake 18 is connected with the crankcase 1 gearbox connected between the sun gear 11 of the third planetary series, and the sun gear 8 of the second planetary series. The crown gear 13 of the third planetary series connected with the crankcase 1 gearbox friction brake 19. Drove 6 of the first planetary number associated with the output link 4 transmission.

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 seven speeds forward and one reverse gear, using three planetary series and six friction controls. In pre the proposed scheme does not happen gap power when shifting gears.

Equipment transmission seventh forward gear allowed to make changes in gear ratio and the order of the pairwise inclusion friction controls, and allowed to abandon the torque Converter and in its place install the vibration damper, which has a much smaller size and weight. The change in the structure and sequence of pairwise inclusion of control led to the fact that when switching there is no gap power. Also managed to improve the dynamic characteristics of the transmission and to extend the kinematic capabilities of the gearbox, to increase its longevity, but also significantly expand the number of types of vehicles, which can install the transmission with this configuration.

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

After the start of vehicle motion serial shift from 1st to 7th is the vehicle accelerates to the desired speed. When the transmission is in the neutral position, neither of friction controls are not enabled.

In the first forward gear included brake 17 and 19, that is, the angular velocity of the crown gear 13 of the third planetary series and is of Odil 9 of the second planetary number associated with the crown gear 7 of the first planetary series is equal to zero.

Torque from the input element 3 through the led 12 of the third planetary number is transmitted to the sun gear 11 of the third planetary series and its associated sun gear 8 of the second planetary series and then through the crown gear 10 of the second planetary series and its associated sun gear 5 of the first planetary number is transmitted to the carrier 6 of the first 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 17 is on. Thus, the angular speed of the carrier 9 of the second planetary number associated with the crown gear 7 of the first planetary series is equal to zero, and the angular velocity of the input link 3 is equal to the angular speed of the sun gear 5 of the first planetary number associated with the crown gear 10 of the second planetary series.

Torque from the input element 3 is switched on via the friction clutch 15 is transmitted to the sun gear 5 of the first planetary series and later on took 6 of the first planetary series directly connected with the output element 4.

When switching to the third forward gear off the brake 17 and activates the brake 19, the clutch 15 is on. Thus, the angular velocity of the crown gear 13 of the third planetary series Rav is and zero and the angular velocity of the input link 3 is equal to the angular speed of the sun gear 5 of the first planetary number associated with the crown gear 10 of the second planetary series.

Torque from the input element 3 is switched on via the friction clutch 15 is transmitted to the sun gear 5 of the first planetary series, where it is divided and transmitted to the carrier 6 of the first planetary series, and on the crown gear 10 of the second planetary series and later on took 9 of the second planetary series, which splits it into two streams. The first flow of torque through the crown gear 7 of the first planetary number is transmitted to the carrier 6 of the first planetary series, where it is combined with the flow of torque from the sun gear 5 of the first planetary series and further transmitted to the output link 4. The second thread torque is transmitted through the sun gear 8 of the second planetary series and its associated sun gear 11 of the third planetary series on carrier 12 of the third planetary series and later merged with the flow of torque from the input link 3.

When switching to the fourth forward gear off the brake 19 and turns on the brake 18, the clutch 15 is on. Thus, the angular speed of the sun gear 11 of the third planetary number associated with the sun gear 8 of the second planet of the aqueous series, equal to zero, and the angular velocity of the input link 3 is equal to the angular speed of the sun gear 5 of the first planetary number associated with the crown gear 10 of the second planetary series.

Torque from the input element 3 is switched on via the friction clutch 15 is transmitted to the sun gear 5 of the first planetary series, where it is divided and transmitted to the carrier 6 of the first planetary series, and through the crown gear 10 of the second planetary number is transmitted to the carrier 9 of the second planetary series and related crown gear 7 of the first planetary series and later on took 6 of the first planetary series, where it is combined with the flow of torque from the sun gear 5 of the first planetary series and further transmitted to the output link 4.

When switching on the fifth forward gear off the brake 18 and turns on the clutch 14, the clutch 15 is on. Thus, the angular velocity of the input link 3 is equal to the angular velocity of the crown gear 7 of the first planetary number associated with the planet carrier 9 of the second planetary series, and the angular velocity of the input link 3 is equal to the angular speed of the sun gear 5 of the first planetary number associated with the crown gear 10 of the second planetary series.

Torque from the input element 3 is divided and enabled through the friction clutch 15 is transmitted to the sun is Chou gear 5 of the first planetary series and later on took 6 of the first planetary series as well as enabled through the friction clutch 14 is transmitted to the carrier 9 of the second planetary series and related crown gear 7 of the first planetary series and later on took 6 of the first planetary series, where it is combined with the flow of torque from the sun gear 11 of the third planetary series and is transmitted to the output link 4.

When switching on the sixth forward gear off the clutch 15 and turns on the brake 18, the clutch 14 remains enabled. Thus, the angular velocity of the input link 3 is equal to the angular velocity of the crown gear 7 of the first planetary number associated with the planet carrier 9 of the second planetary series, and the angular speed of the sun gear 8 of the second planetary series connected with a sun gear 11 of the third planetary number of zero.

Torque from the input element 3 is switched on via the friction clutch 14 is transmitted to the carrier 9 of the second planetary range, where it is divided and through the crown gear 10 of the second planetary series and its associated sun gear 5 of the first planetary number is transmitted to the carrier 6 of the first planetary series, and through the crown gear 7 of the first planetary number is transmitted to the carrier 6 of the first planetary series, where it is combined with the flow of torque from the sun gear 5 of the first planetary series and then passed on to the output link 4.

When switching on the seventh forward gear off the brake 18 and turns on the brake 19, the clutch 14 remains enabled. Thus, the angular velocity of the input link 3 is equal to the angular velocity of the crown gear 7 of the first planetary number associated with the planet carrier 9 of the second planetary series, and the angular velocity of the crown gear 13 of the third planetary series is equal to zero.

Torque from the input element 3 is divided and enabled through the friction clutch 14 is transmitted to the carrier 9 of the second planetary series, and also through the carrier 12 of the third planetary number is transmitted to the sun gear 11 of the third planetary series and its associated sun gear 8 of the second planetary series, and then is transmitted to the carrier 9 of the second planetary series, where the combined flow of torque with included friction clutch 14. On the drive rod 9 of the second planetary range torque is divided and transmitted through the crown gear 7 of the first planetary series on led 6 of the first planetary series, and through the crown gear 10 of the second planetary series and its associated sun gear 5 of the first planetary series on led 6 of the first planetary series, where it is combined with the flow of torque from the crown gear 7 of the first planetary series and further transmitted to the output link 4.

On the front of the che reversing included brake 16 and the brake 19. Thus, the angular velocity of the crown gear 13 of the third planetary equal to zero, and the angular velocity of the crown gear 10 of the second planetary series connected with a sun gear 5 of the first planetary number of zero.

Torque from the input element 3 through the led 12 of the third planetary number is transmitted to the sun gear 11 of the third planetary series and its associated sun gear 8 of the second planetary series and then drove through 9 of the second planetary series and related crown gear 7 of the first planetary number is transmitted to the carrier 6 of the first planetary series directly connected with the output element 4.

The present invention allows transmissions having three planetary series, to provide seven 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.

Transmission containing PL is nearly reducer, carrier of the first planetary number which is the output element of the gearbox, pinion carrier of the second planetary number is associated with the crown gear of the first planetary series, a sun gear of the first planetary number associated with the crown gear of the second planetary number and friction brake with the transmission housing, a sun gear of the second planetary series connected with a sun gear of the third planetary number and friction brake with the transmission housing, an input link connected with the planet carrier of the third planetary series, the crown gear of the third planetary number associated friction brake with the transmission housing, wherein the input link is connected friction-controlled clutch with the planet carrier of the second planetary series, the crown gear of the first planetary series is equipped with a friction brake for its connection with the transmission housing, an input link connected friction-controlled clutch with a sun gear of the first planetary series, the input link is connected with torsional vibration.



 

Same patents:

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FIELD: mechanical engineering.

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The invention relates to mechanical engineering and can be used in industry, with the release of a high-performance machine with reciprocating movement of the working tool of continuous action

The invention relates to mechanical engineering and can be used in vehicles

Vehicle // 2283243

FIELD: transport engineering; entertainments.

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FIELD: transport engineering.

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Vehicle gearbox // 2276640

FIELD: transport engineering.

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4 dwg

FIELD: mechanical engineering.

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EFFECT: enhanced reliability and reduced sizes.

5 cl, 11 dwg

FIELD: transport engineering.

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1 tbl, 2 dwg

FIELD: transport engineering.

SUBSTANCE: proposed multiple-speed gearbox contains housing 1, drive shaft 2, main shaft 3 and countershaft 4. Drive shaft 2 and main shaft 3 are installed coaxially. Countershaft 4 is arranged in parallel with shafts stated above. Gear 6 of drive shaft 2 is in meshing with gear 7 of countershaft 4. Gears 8-12 of countershaft 4 engage in pairs with gears 13-17 freely fitted on main shaft 3. Low-speed gears 11, 12 and reverse speed gear 18 are secured on countershaft 4. Three-position shifter speed E is fitted on hub of main shaft 3 between rows of low speed gears. Four two-position twin shifter sleeves A - D are arranged between first five rows of gears. Said twin shifter sleeves consist, each, of two two-position sleeve members arranged on gears of adjacent parallel shafts interacted by shifter forks 23, 26, 29, 32, respectively. One of shifter sleeve members is fitted on rim of gear freely fitted relative to countershaft 4, and other shifter sleeve member is installed opposite to first one on rim of gear of main shaft or drive shaft.

EFFECT: enlarged operating capabilities of vehicle owing to increased number of forward speeds up to 32 and reverse speeds up to 16.

3 dwg

FIELD: transport engineering.

SUBSTANCE: invention relates to conventional gearboxes of transport and traction vehicles. Each speed in multiple-shaped gearbox contains drive and driven shafts with fitted-on gears and intermediate gears freely fitted on curvilinear axle for rotation and equipped with stop. Curvilinear axle is secured in gearbox for turning around axis of drive or driven shaft. Intermediate gears are installed on axle with angular shift, being in constant meshing either with gears of drive shaft or gears of driven shaft. At gear-shifting, common axle of intermediate gears of shifted-in and shifted-out speeds is unlocked and rotated around axis of gearbox shaft with gear of which intermediate gears are in constant meshing. Intermediate gear of shifted-out speed is brought out of meshing with gear of other shaft, and gear of shifted-in speed is brought synchronously into meshing with gear of other shaft for complete engagement of corresponding speed, after which axle of intermediate gears is locked. To select direction of change-over, engine of vehicle is changed over for traction or braking conditions.

EFFECT: provision of gear-shifting practically without breaking of power flow and without synchronization of gear speeds.

3 cl, 4 dwg

Gear box // 2267675

FIELD: mechanical engineering.

SUBSTANCE: gear box comprises housing (1), shafts (16), (17), (18), and (19) with pinions, and three-sprocket planet mechanism (37) provided with a device for its locking. Crown wheel (39) of the planet mechanism is connected with the reaction gearing member (38) mounted on the inner surface of back outer wall (10) of the housing.

EFFECT: reduced sizes.

5 cl, 4 dwg

FIELD: transport engineering.

SUBSTANCE: proposed multi-speed gearbox has housing 1, input shaft 2 and output shaft 4 arranged in parallel. Gear 6 is fixed, and gears 7 and 8 are installed for sliding on input shaft 2. gears 9, 11, 12, 19 are combined into cluster by shaft 3. Gears 6-12 are engaging in pairs with gears 13-18 freely fitted on output shaft 4. Three two-position twin shifter sleeves A, B and C are installed between four pairs of gears 6-13, 7-14, 8-15 and 9-16. Each shifter sleeve consists of two-position members located on gears of adjacent rows of parallel shafts intercoupled by shifter for. Member 23 is installed on rim of hear 7 of input shaft 2, and member 24 is installed opposite to first member on rim of gear 13 of output shaft 4. Two shifter sleeves D and C are installed on hubs of output shaft 4 between two pairs of low gears and reverse gear.

EFFECT: enlarged operating capabilities of vehicle owing to increased number of speeds.

1 tbl, 2 dwg

FIELD: transport engineering; tractors.

SUBSTANCE: invention relates to hydraulically operated friction clutches. Proposed friction clutch contains hub secured on shaft of gearbox, hydraulic cylinder with radial projections made on hub, piston with pressure disk, thrust disk, inner drum made integral with driven gear and connected by gear joint with driving disks, driven disks connected with outer drum, ring groove made on inner surface of outer drum, and lockring. Novelty is that outer drum and thrust disk are made in form of common part, outer drum is provided with longitudinal projections, with outer projections of driven disks fitted in slots between longitudinal projections. Ends of projections of outer drum are installed between radial projections of hydraulic cylinder, and lockring is arranged in ring channel formed by ring grooves made on inner surface of outer drum and on outer surface of hydraulic cylinder.

EFFECT: reduced wear of disks, increased transmitted power and improved repairability of clutch.

2 dwg

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