RU2514381C1 - Module automatic stepped planetary gearbox - Google Patents

Abstract

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 1^st, 2^nd and 3^rd rows spider, 1^st planetary row crown wheel, 2^nd row crown wheel and 3^rd 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

Description

The invention relates to the field of automotive engineering and the design of automatic speed planetary gearboxes (AKP), which can be used in automatic transmissions of vehicles.

The use of planetary gearboxes in automatic transmissions of vehicles is due to the possibility of obtaining a small-sized, compact in design layout that easily fits into the space limited by the dimensions of the body, ensuring economy, dynamism, comfort, and traffic safety.

Currently, planetary gearboxes used for cars and trucks, as well as military and civil tracked vehicles, consisting of three, four planetary gears, provide six or seven forward gears. To increase the number of gears, for example, to obtain eight or more forward gears, either more planetary gear sets are used, which complicates the gearbox design or increase the number of degrees of freedom, which complicates the gearbox control system. In addition, when shifting gears, the power flow breaks, as several controls are turned off at once.

A six-speed automatic transmission of the German company ZF 6HP26 [Kharitonov S.A. Automatic gearboxes, M., Astrel-ATS, 2003], which is based on the Ravigno planetary system and includes: one carrier with three pairs of interlinked satellites, where each pair of satellites consists of one large and one small satellite ; two independent solar central gears meshed with the carrier pair; one crown wheel, which is the output link.

Using alternately both central sun gears as input links, the planetary system provides the following gears: neutral; downshifts (first and second gears); direct; reverse gear.

When using the kinematic scheme of the Ravigno planetary system with an additional planetary gearbox in which friction blocking couplings connect the sun central gears to the drive link not directly, but through an additional planetary gearbox, the number of gears increases to six with the simultaneous inclusion of two control elements.

For the prototype taken patent RF №2384773.

The claimed invention is aimed at developing an existing prototype by achieving a technical result, which consists of:

- in increasing the range of gear ratios;

- in ensuring the harmony of the pitch gear ratios within the range;

- to improve the traction-dynamic and fuel-economic characteristics by increasing the number of gears from 4 to 14;

- to reduce the complexity of the control system and power ratio gearbox;

- in increasing the efficiency of the gearbox;

- in expanding the types of vehicles on which this gearbox can be installed.

Range, number of gears and pitch between gears are the main characteristics of the automatic transmission. In order to make the most effective use of engine power when operating a car with a different degree of load and in different road conditions, it is necessary to increase the range of gear ratios of the automatic transmission, the number of gears in increments between gears corresponding to geometric progression.

Automatic gearboxes with three degrees of freedom are characterized by a coefficient K _{AND the} use of controls, which is equal to the ratio of the combination of pairwise included controls to the number of all possible combinations. With the full use of the controls K _AND = 1. Currently, widespread in the transmission of wheeled and tracked vehicles are automatic transmissions, in which K _I = 0.5 ... 0.7 [Sharipov V.M. Design and calculation of tractors, M., Mechanical Engineering, 2004].

The specified technical result is achieved in that the modular automatic step gearbox has a planetary system, the module of which is a universal multi-threaded differential mechanism, in which a universal multi-threaded differential mechanism with three pairs of coupled three-gear satellites is common for the first, second and third planetary rows formed by two independent solar central gears coupled by three-crown satellites and three crown gears wheels, where the sun central gear of the first planetary gear set forms three differential gears with mixed gearing with coupled three-crown satellites and three ring gears of the first, second, third planetary gears, and the fourth differential gear with three-crown gears and central sun gear of the third planetary gear external gearing, the carrier is connected by a friction brake to the gearbox housing, the crown wheel of the first planetary gear set a friction brake associated with the transmission housing, crown wheel of the second planetary gear set, a friction brake is connected with the gearbox casing, a sun central gear of the third planetary set is connected to a friction brake transmission housing, crown wheel of the third planetary gear set is an output member of the gearbox.

These features are significant and interconnected by the formation of a stable set of essential features sufficient to obtain the desired technical result. The presence of mixed gearing in the differential mechanisms formed in the first, second, third rows and external gearing in the fourth differential mechanism allows us to ensure the harmony of the gear ratio step within the range. Short kinematic chains in which power transfer is realized due to the addition of two movements, one of which is the carrier’s portable movement, and the second is the relative movement of the links, provides an increase in the automatic transmission efficiency. The use of a universal multi-threaded differential mechanism in the automatic gearbox kinematic scheme makes it possible to realize various design options with a different number of gears, with incomplete use of controls characterized by a coefficient K _I , the value of which in various variants of designs varies in the range K _I = 0.5 ... 1.0.

In the embodiment, when the input link is the solar central gear connected to the input link of the first planetary gear set of the universal multi-threaded differential gear, when sequentially turning on only one control element, we get four gears: neutral; lowering (1-3 transfers); reverse gear.

In the design variant, when the input central link is the solar central gear of the first planetary gear set of the universal multi-threaded differential mechanism and there is a friction blocking clutch connecting the solar central gear of the first planetary gear set with the carrier, when only one control element is connected in series, we get five gears: neutral ; lowering (1-3 transfers); direct; reverse gear.

In a design variant that provides for the possibility of connecting the gearbox input link with the solar central gear of the first planetary gear set and the carrier using friction blocking couplings and simultaneously engaging one of the control elements, we get nine gears: neutral; lowering (1-5 transfers); direct; raising (7-8 transfers); reverse gear.

In a design variant that implements the use of an additional step-up planetary gear with a positive internal gear ratio (divider) together with a universal multi-threaded differential mechanism, when the friction brake of the divider and then one of the control elements of the universal multi-threaded differential mechanism are turned on and off, we get ten gears: neutral ; lowering (1-6 transfers); direct; boost (8th gear); reverse gear (1-2 gears).

In a design variant that implements the use of an additional lowering planetary gear set with a negative internal gear ratio of large units together with a universal multi-threaded differential mechanism, a serial connection of the gearbox input link with the central central gear of the first planetary gear series, a carrier of a universal multi-threaded differential mechanism using friction blocking couplings and a carrier additional planetary gear friction blocking couplings th with central solar gear of the first planetary gear set is a universal multi-threaded differential mechanism, while the inclusion of a universal multi-threaded differential mechanism controls received fourteen gears: neutral; lowering (1-9 transfers); direct; raising (11-12 transfers); reverse gear (1-2 gears).

The claimed invention is intended for the use of automatic speed planetary gearboxes in transmissions of front and rear wheel drive vehicles for various purposes.

A variant of the design of automatic stepped planetary gearboxes designed for rear-wheel drive cars involves the use of an additional differential mechanism with an internal gear ratio of one. The solar central gear of the third planetary gear set of the universal multi-threaded differential mechanism is located inside it, which makes it difficult to brake this link. This is especially important when using the proposed design options in transmissions of rear-wheel drive vehicles. The present invention provides a friction brake for connecting the solar central gear of the third planetary gear set to the automatic gearbox housing.

The essence of the proposed technical solution is illustrated by drawings, which depict:

figure 1 is a kinematic diagram of a modular automatic four-stage planetary gearbox for a front-wheel drive car with a universal multi-threaded differential mechanism;

figure 2 is a kinematic diagram of a modular automatic five-speed planetary gearbox for a front-wheel drive car;

figure 3 is a kinematic diagram of a modular automatic nine-speed planetary gearbox for a front-wheel drive car;

figure 4 is a kinematic diagram of a modular automatic ten-speed planetary gearbox for a front-wheel drive car;

figure 5 is a kinematic diagram of a modular automatic fourteen-speed planetary gearbox for front-wheel drive vehicle;

Fig.6 is a kinematic diagram of an additional planetary gear set that is built into all design options when using modular automatic speed planetary gearboxes for rear-wheel drive cars.

The modular automatic speed planetary gearbox (Fig. 1), which implements three forward gears and one reverse gear, contains a crankcase 10, an input link 9, an output link 8, four friction brakes 11, 12, 13, 14 and a universal multi-threaded differential mechanism , which includes a common carrier 5 with three planetary gears.

The first planetary gear set consists of the sun central gear 1, drove 5 satellites 2-2 "and the crown gear 6. The second planetary gear set consists of the carrier 5, interlinked satellites 2 ', 3 and the crown gear 7. The third planetary gear set consists of the sun central gear 4 , drove 5 satellites 3'-3 "and the crown wheel 8.

At the same time, the first planetary gear set, coupled three-crown satellites 2 "-2-2 ', 3-3'-3" and the ring gear 8 is a differential mechanism with a negative gear ratio between the ring gears 6 and 8.

The sun central gear 1, the second planetary gear set, satellites 3'-3 ", the ring gear 8 are a differential mechanism with a positive gear ratio between the ring gears 7 and 8.

The sun central gear 1, carrier 5, coupled satellites 2-2 ', 3-3'-3 ", the sun center gear 4 and the ring gear 8 are a differential mechanism with negative gear ratios between the sun center gears 1, 4 and between the sun the central gear 4 and the ring gear 8, with a positive gear ratio between the sun gear 1 and the ring gear 8.

Thus, the universal multi-threaded differential mechanism is a combination of four differential mechanisms with an input link, which is the sun wheel 1, the output gear is a ring gear 8 and a carrier 5, common to all four differential mechanisms.

The number of degrees of freedom of this mechanism is equal to two; for its kinematic certainty, it is necessary to specify two relations or two laws of motion of any links. With a constant number of revolutions of link 1 equal to n _1, it is necessary to set some rotation frequency to one of the links of the mechanism - for example, to brake one of the links.

When braking the crown wheel of one of the planetary rows of a multi-threaded differential mechanism, the satellites of this series begin to run around the braked crown wheel, transmitting torque through the axles to the carrier 5, which will make a portable movement. Next, the portable movement of the carrier 5 is transmitted to the link 8 connected to the output shaft. In this case, the brake of the crown wheel senses a reactive moment.

The gear ratio between input 1 and output 8 links is determined by the expression:

$$i_{\mathrm{one}-8}=i_{\mathrm{one}-5}^p\cdot i_{5-8}^p,(\mathrm{one})$$

- передаточное число между входным валом и водилом при заторможенном звене р;Where $$i_{\mathrm{one}-5}^p$$

- gear ratio between the input shaft and the carrier with the braked link p;

- передаточное число между водилом и выходным валом при заторможенном звене р. $$i_{5-8}^p$$

- gear ratio between the carrier and the output shaft with the braked link p.

When braking carrier 5, the mechanism turns into an ordinary in-line gearbox, the gear ratio between input 1 and output 8 links is determined by the expression:

$$i_{\mathrm{one}-8}=i_{\mathrm{one}-2}\cdot i_{2^{\mathrm{one}}-3}\cdot i_{3^{\mathrm{eleven}}-8}.(2)$$

The modular automatic speed planetary gearbox (figure 2), which implements four forward gears and one reverse gear, contains a crankcase 10, an input link 9, an output link 8, one friction blocking clutch 15, four friction brakes 11, 12, 13, 14 and a universal multi-threaded differential mechanism, which includes a common carrier 5 with three planetary gears.

The first planetary gear set consists of the sun central gear 1, drove 5 satellites 2-2 "and the crown gear 6. The second planetary gear set consists of the carrier 5, interlinked satellites 2 ', 3 and the crown gear 7. The third planetary gear set consists of the sun central gear 4 , drove 5 satellites 3'-3 "and the crown wheel 8.

At the same time, the first planetary gear set, coupled three-crown satellites 2 "-2-2 ', 3-3'-3" and the ring gear 8 are a differential mechanism with a negative gear ratio between the ring gears 6 and 8.

The sun central gear 1, the second planetary gear set, satellites 3'-3 ", the ring gear 8 are a differential mechanism with a positive gear ratio between the ring gears 7 and 8.

The sun central gear 1, carrier 5, coupled satellites 2-2 ', 3-3'-3 ", the sun center gear 4 and the ring gear 8 are a differential mechanism with negative gear ratios between the sun center gears 1, 4 and between the sun the central gear 4 and the ring gear 8, with a positive gear ratio between the sun gear 1 and the ring gear 8.

Thus, the universal multi-threaded differential mechanism is a combination of four differential mechanisms with an input link, which is the sun wheel 1, the output gear is a ring gear 8 and a carrier 5, common to all four differential mechanisms.

The number of degrees of freedom of this mechanism is equal to two; for its kinematic certainty, it is necessary to specify two relations or two laws of motion of any links. With a constant number of revolutions of link 1 equal to n _1, it is necessary to set some rotation frequency to one of the links of the mechanism - for example, to brake one of the links.

When braking the crown wheel of one of the planetary rows of the universal multi-threaded differential mechanism, the satellites of this series begin to run around the braked crown wheel, transmitting torque through the axles to the carrier 5, which makes a portable movement. Next, the portable movement of the carrier 5 is transmitted to the link 8 connected to the output shaft. In this case, the brake of the crown wheel senses a reactive moment.

The gear ratio between input 1 and output 8 links is determined by the expression:

$$i_{\mathrm{one}-8}=i_{\mathrm{one}-5}^p\cdot i_{5-8}^p,(3)$$

- передаточное число между входным валом и водилом при заторможенном звене р;Where $$i_{\mathrm{one}-5}^p$$

- gear ratio between the input shaft and the carrier with the braked link p;

- передаточное число между водилом и выходным валом при заторможенном звене р. $$i_{5-8}^p$$

- gear ratio between the carrier and the output shaft with the braked link p.

When braking carrier 5, the mechanism turns into an ordinary in-line gearbox, the gear ratio between input 1 and output 8 links is determined by the expression:

$$i_{\mathrm{one}-8}=i_{\mathrm{one}-2}<figure-callout\; id="2"\; label="\cdot \; i"\; filenames="00000020.png,00000021.png"\; state="\{\{state\}\}">\cdot \; </figure-callout>i_{}{}_{2^{\mathrm{one}}-3}\cdot i_{3^{\mathrm{eleven}}-8}.(\mathrm{four})$$

The input link 9, connected to the sun central gear 1, can be connected by a friction blocking clutch 15 to the carrier 5. As a result of this connection, link 1 and link 5 of the universal multi-threaded differential mechanism receive the same speed, the mechanism is blocked and it works like a hard shaft, by direct transmission.

The modular automatic speed planetary gearbox (Fig. 3), which implements eight forward gears and one reverse gear, contains a crankcase 10, an input link 9, an output link 8, five friction brakes 11, 12, 13, 14, 18 and a universal multi-threaded differential gear. The input links of the universal multi-threaded differential mechanism are the sun central gear 1 and carrier 5, which can be connected using friction blocking couplings 16, 17 with the input link 9 of the gearbox.

When braking the crown wheel of one of the planetary gears of a universal multi-threaded differential gear or the central sun gear of the first planetary gear, the satellites of this gear begin to run around the braked link, transmitting torque through the axles to carrier 5, which will make a portable movement. In this case, the brake of the crown wheel senses a reactive moment. Next, the portable movement of the carrier 5 is transmitted to the link 8 connected to the output shaft.

When the friction blocking clutch 17 is turned on and one of the brakes is connected in series, the gear ratio between input 1 and output 8 links is determined by the expression:

$$i_{\mathrm{one}-8}=i_{\mathrm{one}-5}^p\cdot i_{5-8}^p,(5)$$

When the friction blocking clutch 16 is turned on and one of the brakes is turned on sequentially, the gear ratio between input 5 and output 8 links is determined by the expression:

$$i_{5-8}=i_{5-8}^p.\text{(6)}$$

When the friction blocking clutch 17 is turned on and the carrier 5 is braked by the friction brake 12, the mechanism turns into a regular in-line gearbox, the gear ratio between input 1 and output 8 links is determined by the expression:

$$i_{\mathrm{one}-8}=i_{\mathrm{one}-2}<figure-callout\; id="2"\; label="\cdot \; i"\; filenames="00000020.png,00000021.png"\; state="\{\{state\}\}">\cdot \; </figure-callout>i_{}{}_{2^{\mathrm{one}}-3}\cdot i_{3^{\mathrm{eleven}}-8}.(7)$$

With the simultaneous inclusion of friction blocking clutches 16, 17, link 1 and link 5 of the universal multi-threaded differential mechanism receive the same number of revolutions, the mechanism is locked and it works like a hard shaft, performing direct transmission.

This automatic step-by-step planetary gearbox is three-stage, since in order to receive a certain transmission, one of the friction blocking clutches and one friction brake, that is, two control elements, are required to be simultaneously and characterized by the coefficient of use of the control elements K _AND = 0.77.

A modular automatic speed planetary gearbox (figure 4), which implements eight forward gears and two reverse gears, contains a crankcase 10, an input link 9, an output link 8, a blocking clutch 24 and friction brakes 11, 12, 13, 14, 23 , a multi-threaded differential mechanism, an additional step-up planetary gear (divider) with a positive internal gear ratio less than unity, which consists of an input link 9 connected to the driving sun gear 19, drove 22 with two-crown satellites 20-20 ', yhodnoy sun gear 21, an overrunning clutch 25 arranged between sun gear 21 and carrier 22.

With a constant number of revolutions of link 9, it is necessary to set any rotation frequency to one or two of the links of an automatic step gearbox - for example, to brake one or two links. If it is necessary to simultaneously brake two links, one of the links is the divider carrier, and the second is the brake link of the universal multi-threaded differential mechanism.

When the friction brake 23 is disconnected, the carrier 22 tends to have a number of revolutions greater than the number of revolutions of the link 21, the freewheel 25 locks the divider, while the number of revolutions of the output link of the divider 21 is equal to the number of revolutions of the input link 9 of the gearbox.

In this case, only one link of the universal multi-threaded differential mechanism is braked and the gear ratio between input 9 and output 8 links is determined by the expression:

$$i_{9-8}=i_{9-\mathrm{<figure-callout\; id="22"\; label="one"\; filenames="00000022.png"\; state="\{\{state\}\}">one</figure-callout>}}^{22}\cdot i_{\mathrm{one}-5}^p\cdot i_{5-8}^p,(8)$$

- передаточное число между входным 9 валом и входным звеном универсального многопоточного дифференциального механизма при заторможенном водиле 22.Where $$i_{9-\mathrm{one}}^{22}$$

- gear ratio between the input 9 shaft and the input link of a universal multi-threaded differential mechanism with a braked carrier 22.

When braking by the friction brake 23 of the carrier 22 of the divider, it is converted into a multiplier with a higher number of revolutions of the output link 21, the gear ratio between the input shaft 9 and the output link 21 is determined by the expression:

$$i_{9-\mathrm{<figure-callout\; id="22"\; label="one"\; filenames="00000022.png"\; state="\{\{state\}\}">one</figure-callout>}}^{22}=i_{19-\mathrm{twenty}}\cdot i_{\mathrm{twenty}-21}.\text{(9)}$$

In this case, simultaneously with the friction brake 23, one of the friction brakes 11, 12, 13, 14 is engaged, the gear ratio between input 9 and output 8 links is determined by the expression:

$$i_{9-8}=i_{9-\mathrm{<figure-callout\; id="22"\; label="one"\; filenames="00000022.png"\; state="\{\{state\}\}">one</figure-callout>}}^{22}\cdot i_{\mathrm{one}-5}^p\cdot i_{5-8}^p.(10)$$

In order to implement direct transmission, the friction brakes of the divider and the multi-threaded differential mechanism are simultaneously disconnected and the solar central gear 4 of the multi-threaded differential mechanism is connected using the friction blocking clutch 24 with the crown wheel 8, link 4 and link 8 receive the same speed, the mechanism locks, and it operates as a rigid shaft in conjunction with the output link 21 of the divider, which is blocked by the freewheel 25.

In order to realize an increased transmission, the friction brake 23 of the divider and the friction lock clutch 24 are simultaneously engaged. In this case, the multi-threaded differential mechanism is blocked and its speed becomes equal to the increased number of revolutions of the output shaft 21 of the divider.

This automatic speed planetary gearbox is characterized by the utilization of controls

K _& = 0.77.

The modular automatic speed planetary gearbox (Fig. 5), which implements twelve forward gears and two reverse gears, contains a crankcase 10, an input link 9, an output link 8, three friction blocking clutches 16, 17, 30, five friction brakes 11, 12, 13, 14, 18, a universal multi-threaded differential mechanism, an additional lowering planetary gear set with a negative internal gear ratio, greater than one, which consists of a drive crown wheel 28, carrier 29, satellites 27 and fixed sun gear 26.

With a constant number of revolutions of link 9, it is possible to sequentially set the speed of one of the two links - the sun central gear 1 using the friction blocking clutch 17 or the carrier 5 sequentially using the friction blocking clutch 16, and then using the friction blocking clutch 30.

With successive braking of the crown wheels of one of the planetary gears of a universal multi-threaded differential mechanism, the satellites of this series begin to run around the crown gear, transmitting torque through the axles to carrier 5, which makes a portable movement. In this case, the brake of the crown wheel senses a reactive moment. Next, the portable movement of the carrier 5 is transmitted to the link 8 connected to the output shaft.

When the friction lock clutch 17 is engaged and the friction brakes are sequentially engaged, the gear ratio between input 9 and output 8 links is determined by the expression:

$$i_{9-8}=i_{\mathrm{one}-5}^p\cdot i_{5-8}^p.(\mathrm{eleven})$$

When the friction lock clutch 16 is turned on and the friction brakes are sequentially engaged, the gear ratio between input 9 and output 8 links is determined by the expression:

$$i_{9-8}=i_{5-8}^p.\text{(12)}$$

When the friction blocking clutch 30 is turned on and the friction brakes are sequentially engaged, the gear ratio between input 9 and output 8 links is determined by the expression:

$$i_{9-8}=i_{9-5}^p\cdot i_{5-8}^{\text{p}}\text{, (13)}$$

where i _{9_5} is the gear ratio between the input 9 shaft and input 5 of the universal multi-threaded differential mechanism with the friction blocking clutch 30 engaged.

When the friction blocking clutches 16, 17 of the universal multi-threaded differential mechanism are simultaneously engaged, the carrier 5 and the sun central gear 1 receive the same number of revolutions, the mechanism locks and acts like a hard shaft, performing direct transmission.

This gearbox is three-stage, since in order to receive any particular transmission it is necessary to turn on two of the control elements, and is characterized by the coefficient of use of the control elements K _AND = 0.57.

An additional planetary gear set (Fig. 6), which is integrated into all design variants when using automatic stepwise planetary gearboxes for rear-wheel drive cars, includes a sun gear 31, which is connected to the crown wheel 8, a sun central gear 4, which is connected to the carrier 34 an additional planetary gear set, satellites 32-32 ', the output sun gear 33 and the friction brake 35, with which the sun central gear 4 can be connected to the gearbox housing. When the gear ratio is equal to one, the torque on the carrier 34 is zero, and the number of revolutions and the direction of rotation of the carrier 34 can have any value, without having any effect on the motion parameters of the link 34. This allows the transmission of movement from the link 31 to the link 33 without change for any direction of movement and any angular velocity (including zero) drove 34.

Proposed according to the invention, a modular automatic speed planetary gearbox (figure 1) operates as follows. After the vehicle begins to move by sequential gear shifting from the 1st to the 3rd, it is accelerated to the required speed. In neutral, none of the friction controls are turned on.

In the first forward gear, the friction brake 12 is engaged, while the angular speed of the carrier 5 becomes equal to zero.

When braking the carrier 5, the universal multi-threaded differential mechanism operates as an in-line gearbox. The torque from the input link 9 is transmitted to the sun central gear 1 of the first planetary gear set, and from the sun central gear 1, to the coupled satellites 2-2 ', 3-3'-3 ", which are connected to the crown wheel 8 of the third planetary gear set.

When shifting to the second forward gear, the friction brake 12 is turned off and the friction brake 11 is engaged. The angular speed of the crown wheel 6 becomes equal to zero.

The torque from the input link 9 is transmitted through the carrier 5, which, carrying out a portable movement, transmits torque to the crown wheel 8.

When shifting to the third forward gear, the friction brake 11 is turned off and the friction brake 14 is engaged. In this case, the angular velocity of the sun central gear 4 becomes equal to zero.

The torque from the input link 9 is transmitted to the sun wheel 1 of the first planetary gear set, and from the central sun gear 1 to the carrier 5, where when the sun gear brakes 4 satellites, rolling it, transmit torque to the output link 8 of the gearbox.

When shifting to reverse gear, the friction brake 13 is applied, that is, the angular velocity of the crown wheel 7 becomes zero.

The torque is transmitted from the input link 9 to the sun central gear 1 of the first planetary gear set, where when braking the crown wheel 7 of the second planetary gear set 5 transfers negative moment in sign to the output link 8.

Proposed according to the invention, a modular automatic speed planetary gearbox (figure 2) operates as follows. After the vehicle begins to move by sequential gear shifting from the 1st to the 4th, it is accelerated to the required speed. In neutral, none of the friction controls are turned on.

The inclusion of control elements in the first, second, third forward gears corresponds to the description of the operation of the automatic stepped planetary gearbox of figure 1.

When shifting to the fourth forward gear, the friction blocking clutch 15 engages and the friction brake 11 disengages.

When the friction blocking clutch 15 is turned on, the sun central gear 1 and carrier 5 receive the same number of revolutions, the universal multi-threaded differential mechanism is blocked and it works like a hard shaft, performing direct transmission.

When shifting to reverse gear, the friction brake 13 is applied, that is, the angular velocity of the crown wheel 7 becomes zero.

The torque is transmitted from the input link 9 to the sun central gear 1 of the first planetary gear set, where when braking the crown wheel 7 of the second planetary gear set 5 transfers negative moment in sign to the output link 8.

Proposed according to the invention, a modular automatic speed planetary gearbox (figure 3) operates as follows. After the vehicle begins to move by sequential gear shifting from the 1st to the 8th, it is accelerated to the required speed. With the friction controls switched off, the automatic speed planetary gearbox is in the neutral position.

In the first forward gear, a friction blocking clutch 17 is connected that connects the input link 9 to the central sun gear 1 and a friction brake 12 that connects the carrier 5 to the gearbox housing. In this case, the angular velocity of carrier 5 is equal to zero, the universal multi-threaded differential mechanism operates as an in-line reducer, the input link of which is the sun central gear 1.

The torque from the solar central gear 1 through the interlocked satellites 2-2 ', 3-3 "is transmitted to the crown wheel 8 of the third planetary gear set, that is, to the output link 8.

When shifting to the second forward gear, the friction lock clutch 17 is turned off and the friction lock clutch 16 is turned on, the friction brake 12 is turned off and the friction brake 13 is turned on. In this case, the angular speed of the crown wheel 7 becomes zero.

The torque from the input link 9 is transmitted to the carrier 5 by means of a friction blocking clutch 16. The carrier 5, carrying out a portable movement when the satellites run 3 of the crown wheel 7, transmits the torque to the crown wheel 8.

When shifting to the third forward gear, the friction lock clutch 16 is turned off and the friction lock clutch 17 is turned on, the friction brake 13 is turned off and the friction brake 11 is turned on. In this case, the angular speed of the crown wheel 6 becomes zero.

The torque from the input link 9 is transmitted to the sun central gear 1 and further to the satellites 2 "-2-2 '. The carrier 5, carrying out a portable movement while running the satellites 2" around the crown wheel 6, transmits the torque to the output link 8 of the automatic transmission.

When shifting to the fourth forward gear, the friction blocking clutch 17 remains engaged, the friction brake 11 is turned off and the friction brake 14 is engaged. In this case, the angular speed of the sun central gear 4 becomes equal to zero.

The torque from the input link 9 is transmitted to the sun central gear 1 of the first planetary gear set through the friction clutch 17 and then to the satellites 2 "-2-2 ', 3-3'-3". Drove 5, carrying out a portable movement when running in satellites 3'-3 "of the solar central gear 4, transmits torque to the output link 8.

When switching to the fifth forward gear, the friction lock clutch 17 is turned off and the friction lock clutch 16 is turned on, the friction brake 14 is turned off and the friction brake 18 is turned on. In this case, the angular speed of the sun central gear 1 becomes equal to zero.

The torque from the input link 9 is transmitted to the carrier 5 by means of a friction clutch 16. The carrier 5, performing a portable movement when the satellites 2 run in the solar central gear 1, transmits the torque to the crown wheel 8.

When switching to the sixth forward gear, the friction brake 18 is turned off, the friction lock clutch 16 remains engaged and the friction lock clutch 17 is engaged.

The torque is transmitted from the input link 9 to the carrier 5 through the friction blocking clutch 16 and to the sun central gear 1 through the friction blocking clutch 17. In this case, two links of the universal multi-threaded differential mechanism receive the same angular velocities. Thus, the multi-threaded differential mechanism is blocked and it works like a hard shaft, providing direct transmission.

When shifting to the seventh forward gear, the friction blocking clutch 17 is turned off, the friction blocking clutch 16 remains engaged, and the friction brake 14 is engaged. In this case, the angular velocity of the sun central gear 4 becomes zero.

The torque is transmitted from the input link 9 to the carrier 5 through the friction blocking clutch 16. When the solar central gear 4 of the third planetary gear is braked and driven by its satellites 3 ', the carrier 5 makes a portable movement and transfers torque to the output link 8 of the automatic transmission.

When shifting to the eighth forward gear, the friction lock clutch 16 remains engaged, the friction brake 14 is turned off and the friction brake 11 is engaged. In this case, the angular velocity of the crown wheel 6 becomes zero.

The torque from the input link 9 is transmitted to the carrier 5 by means of a friction clutch 16. The carrier 5, carrying out a portable movement when the satellites run 2 "of the crown wheel 6, transmits the torque to the crown wheel 8.

When the reverse gear is engaged, the friction blocking clutch 17 is turned on and the friction brake 13 is engaged. The angular speed of the crown wheel 7 of the second planetary gear set becomes zero.

Torque is transmitted from the input link 9 by means of a friction blocking clutch 17 to the solar central gear 1 of the first planetary gear set. When braking the crown wheel 7 of the second planetary gear set, the satellites 3 run in relative to it, the carrier 5 makes a portable movement and transmits a negative sign of torque to the output link 8.

Proposed according to the invention, a modular automatic speed planetary gearbox (figure 4) operates as follows. After the vehicle begins to move by sequential gear shifting from the 1st to the 8th, it is accelerated to the required speed. With the friction controls switched off, the automatic speed planetary gearbox is in the neutral position.

The divider that this automatic gearbox is equipped with due to the peculiarity inherent in differential mechanisms with a positive internal gear ratio less than unity, namely that all its links have the same direction that coincides with the direction of rotation of the input link. When the internal gear ratio of the differential mechanism is greater than 0.5, but less than 1.0, the carrier 22 of the divider will have a number of revolutions greater than the number of revolutions of the input and output shafts and, therefore, will provide closure of the freewheel 25 installed between the carrier 22 and the output link 21. Then the output link 21 will rotate with a number of revolutions equal to the number of revolutions of the input link 9, that is, direct transmission will be carried out.

With the braked carrier 22, the divider operates as an in-line gearbox with an increasing positive gear ratio.

In the first forward gear, the friction brake 12 is engaged, that is, the angular velocity of the carrier 5 becomes equal to zero. Since the carrier 22 of the divider is not braked, the torque from the input link 9 is transmitted to the sun central gear 1, from the sun central gear 1 to the satellites 2-2 ', 3-3 ", which are connected to the output link 8, that is, when braking Drove 5 universal multi-threaded differential mechanism works as a line gear.

When shifting to the second forward gear, the friction brake 12 remains engaged and the friction brake 23 is engaged. Thus, the angular velocity of the carrier 5 and the carrier 22 become equal to zero.

The torque from the input link 9 through an additional raising planetary gear (divider) with a positive internal gear ratio less than unity is transmitted to the central sun gear 1, then through the satellites 2-2 ', 3-3 ", which are connected to the output link 8, that is, when braking carrier 5 and carrier 22, the universal multi-threaded differential mechanism and divider operate as in-line gearboxes.

When switching to the third forward gear, the friction brakes 12, 23 are turned off and the friction brake 11 is turned on. Thus, the angular speed of the crown wheel 6 is zero.

Torque from input link 9 is transmitted to the sun central gear 1, and from the sun central gear to carrier 5, where when braking the ring gear 6 of the first planetary gear set of the 2 "satellite, rolling it, transmit torque to output link 8 of the gearbox.

When shifting to the fourth forward gear, the friction brake 11 remains engaged and the friction brake 23 is engaged. Thus, the angular velocity of the crown wheel 6 and the carrier 22 is zero.

Torque from the input link 9 is transmitted through the divider to the solar central wheel 1, from the solar central gear 1, to carrier 5 - coupled satellites 2 "-2-2 ', 3-3'-3", where carrier 5 distributes torque. When braking the crown wheel 6 of the first planetary gear set, satellites 2 "run around it and transmit torque to the transmission output link 8.

When switching to the fifth forward gear, the friction brakes 11, 23 are turned off and the friction brake 14 is turned on, that is, the angular velocity of the sun central gear 4 is zero.

Torque from the input link 9 is transmitted to the sun central gear 1, and from the sun central gear 1 to the carrier 5, where when braking the solar central gear 4 of the third planetary gear carrier 5 distributes the satellites with 5 satellites and transfers it to the output link 8.

When switching to the sixth forward gear, the friction brake 14 remains engaged and the friction brake 23 is engaged. Thus, the angular velocity of the carrier 22 and the sun central gear 4 is zero.

Torque from the input link 9 is transmitted through the divider to the sun central gear 1, from the sun central gear 1 to the carrier 5, coupled satellites 2-2 ', 3-3'-3 ", where when braking the sun central gear 4 of the third planetary gear set the moment is transmitted to the output link 8.

When shifting to the seventh forward gear, the friction brakes 14 and 23 are turned off and the friction lock clutch 24 is engaged.

Torque from the input link 9 is transmitted to link 1, and then through coupled satellites 2-2 ', 3-3'-3 "to link 4 and link 8. When the friction blocking clutch 24 is turned on, the sun central gear 4 and the ring wheel 8 receive the same number of revolutions, a universal multi-threaded differential mechanism is blocked and it works like a hard shaft, performing direct transmission.

When shifting to the eighth forward gear, the friction lock clutch 24 remains engaged and the friction brake 23 is engaged.

The torque is transmitted from the input link 9 through the divider to the sun central gear 1 and carrier 5. Thus, carrier 5 and the sun central gear 1 receive the same number of revolutions, the mechanism is blocked and it works like a hard shaft, but transmitting an increased gear.

When shifting to first reverse gear, the friction brake 13 is engaged, that is, the angular velocity of the crown wheel 7 is zero.

The torque is transmitted from the input link 9 to the sun gear 1, where when braking the crown wheel 7 drove 5, the coupled satellites 2-2 ', 3-3 "distribute the moment and the negative value is transmitted to the output link 8.

When shifting to second reverse gear, friction brakes 13 and 23 are engaged. Thus, the angular velocity of carrier 22 and crown wheel 7 is zero.

The torque is transmitted from the input link 9 through the divider to the sun gear 1, where when braking the ring gear 7 it drove 5, the coupled satellites 2-2 ', 3-3 "distribute the moment and the moment negative in value is transmitted to the output link 8.

Proposed according to the invention, a modular automatic speed planetary gearbox (figure 5) operates as follows.

In the first forward gear, the friction blocking clutch 30 and the friction brake 12 are engaged. In this case, the angular velocity of carrier 5 becomes equal to zero.

The torque from the input link 9 through the carrier 29 of an additional lowering planetary gear set is transmitted to the sun central gear 1 using the friction blocking clutch 30. Next, the torque from the sun central gear 1 is transmitted to the crown wheel 8 through the coupled satellites 2-2 ', 3-3 " third planetary gear, that is, to the output link.

The second forward gear is engaged using the friction blocking clutch 16 and the friction brake 13, which corresponds to the inclusion of the second gear of FIG. 3.

When shifting to the third forward gear, the friction blocking clutch 16 and the friction brake 13 are turned off, the friction blocking clutch 30 and the friction brake 11 are engaged. In this case, the angular speed of the ring gear 6 becomes zero.

The torque from the input link 9 through the carrier 29 of an additional lowering planetary gear is transmitted to the solar central gear 1 and then to the satellites 2. The carrier 5, carrying out a portable movement when the satellites 2 ”drive around the crown wheel 6, transmits torque to the output link 8.

The fourth gear is engaged using the friction blocking clutch 17 and the friction brake 12, which corresponds to the inclusion of the first gear of figure 3.

When switching to the fifth forward gear, the friction blocking clutch 17 and the friction brake 12 are turned off, the friction blocking clutch 30 and the friction brake 14 are engaged. The angular speed of the sun central gear 4 of the third planetary gear set becomes zero.

The torque from the input link 9 through the carrier 29 of an additional lowering planetary gear set is transmitted to the solar central gear 1 and then to the satellites 2-2 ', 3-3'-3 ". The carrier 5, making a portable movement when running the satellites 3' of the solar central gear 4 transmits torque to the output link 8.

The sixth forward gear is engaged by means of a friction blocking clutch 17 and a friction brake 11, which corresponds to engaging a third gear of FIG. 3.

When switching to the seventh forward gear, the friction lock clutch 17 and the friction brake 11 are turned off, the friction lock clutches 16, 30 are turned on.

Torque is simultaneously transmitted to the solar central gear 1 of the universal multi-threaded differential mechanism via the kinematic stream 9-28-17-29-30-1 and to carrier 5 via the kinematic stream 9-16-5. A universal multi-threaded differential mechanism summarizes these two movements in the form of the movement of the output link 8.

The eighth forward gear is engaged by means of a friction lock clutch 16 and a friction brake 18, which corresponds to engaging the fifth gear of FIG. 3.

When switching to the ninth forward gear, the friction lock clutch 16 and the friction brake 18 are turned off, the friction lock clutch 17 and the friction brake 14 are engaged, which corresponds to engaging the fourth gear of FIG. 3.

When switching to the tenth forward gear, the friction brake 14 is turned off, the friction lock clutch 17 remains engaged, the friction lock clutch 16 is engaged. In this case, the differential mechanism is locked, which corresponds to the inclusion of the sixth gear of FIG. 3.

When shifting to the eleventh forward gear, the friction lock clutch 17 is turned off, the friction lock clutch 16 remains engaged, the friction brake 14 is engaged, which corresponds to engaging the seventh gear of FIG. 3.

When switching to the twelfth gear, the friction brake 14 is turned off, the friction lock clutch 16 remains engaged, the friction brake 11 is engaged, which corresponds to engaging the eighth gear of FIG. 3.

When shifting to first reverse gear, the friction blocking clutch 30 and the friction brake 13 are engaged. In this case, the angular speed of the crown wheel 7 of the second planetary gear set becomes zero.

The torque from the input link 9 through the carrier 29 of an additional lowering planetary gear is transmitted to the solar central gear 1 by means of a friction blocking clutch 30. When the crown wheel 7 is braked, the satellites 3 roll around relative to it, carrier 5 performs a portable movement and transmits torque negative in sign to output link 8.

When switching to the second reverse gear, the friction blocking clutch 17 and the friction brake 13 are engaged, which corresponds to engaging the reverse gear of FIG. 4.

The present invention makes it possible to provide from four to twelve forward gears, including with one or two accelerating gears and with one or two reverse gears, in automatic speed planetary gearboxes, which are based on the planetary system of a universal multi-threaded differential gear, change the range of gear ratios in the direction of its increase with a minimum number of planetary gears, and with a constant range of gear ratios due to values of the number of gears to reduce the interval between gear ratios, that is, the discreteness of the gear ratios of the automatic gearbox will be significantly less, which provides a greater ability of the engine to adapt to changing conditions of road resistance and provide higher traction-dynamic and fuel-economic indicators of the car (vehicle) efficiency due to short kinematic chains and the combination of two movements, one of which is portable and, accordingly, has a high e value of efficiency, significantly lower energy consumption for creating high pressure in the hydraulic control system of the automatic gearbox, which is ensured by the minimum use of friction blocking couplings, in the hydraulic systems of which the maximum losses of the working fluid flow through the rotating seals occur, gear changes without breaking the power flow due to the minimum quantity at the same time switchable control elements, reducing dimensions due to fewer control elements with the same number of tv gear in comparison with the prototype.

The use of the proposed automatic gearbox on the basis of a universal multi-threaded differential mechanism is applicable both for cars and trucks, and for military and civil tracked vehicles.

The present invention is industrially applicable, since its implementation does not require special new technology and special equipment, in addition to that which uses mechanical engineering in the manufacture of gearboxes, including planetary ones.

Claims (6)

1. The modular automatic stepwise planetary gearbox has a planetary system, the module of which is a universal multi-threaded differential mechanism, characterized in that the carrier of a universal multi-threaded differential mechanism with three pairs of coupled three-crown satellites is common to the first, second and third planetary rows formed by two independent solar central gears coupled by three-crown satellites and three crown gears, where the sun I, the central gear of the first planetary gear set forms three differential gears with mixed gearing with the coupled three-crown gears and three crown gears of the first, second, third planetary gears, and the fourth differential gear with external gearing, with the gears of the three-gear satellite and the central sun gear of the third planetary gear clutch connected by a friction brake to the gear housing, the crown wheel of the first planetary gear set is connected by a friction brake ohm with sump gearbox, the crown wheel of the second planetary gear set, a friction brake is connected with the gearbox casing, a sun central gear of the third planetary set is connected to a friction brake transmission housing, crown wheel of the third planetary gear set is an output member of the gearbox. 2. The modular automatic speed planetary gearbox according to claim 1, characterized in that it has a friction blocking clutch connecting the central sun gear of the first planetary gear and a universal multi-threaded differential mechanism. 3. The modular automatic stepped planetary gearbox according to claim 1, characterized in that it has two friction blocking clutches that can connect the sun gear of the first planetary gear set and the carrier of the universal multi-threaded differential mechanism to the input link of the gearbox, and block the multi-threaded differential gear at the same time differential mechanism, the central sun gear of the first planetary gear set of a multi-threaded differential mechanism is connected using a friction o brakes with gear housing. 4. The modular automatic speed planetary gearbox according to claim 1, characterized in that it has an additional boosting planetary gear (divider) with a positive internal gear ratio less than one, which consists of a leading solar central gear, a carrier with twin-crown gears, a friction brake, the output of the solar central gear and the freewheel installed between the output of the solar central gear and the carrier of the divider, the carrier of the divider is connected by a friction brake m with the gear housing, the universal multi-threaded differential mechanism has a friction blocking clutch connecting the central sun gear of the third planetary gear set and the ring gear of the third planetary gear set of the universal multi-threaded differential gear, while blocking it. 5. The modular automatic stepped planetary gearbox according to claim 1, characterized in that it has an additional reduction planetary gear set with a negative internal gear ratio, greater than one, which consists of a fixed sun gear, a drive crown wheel, a carrier with satellites and a friction blocking clutch connecting the carrier of an additional lowering planetary gear set with the solar central gear of the first planetary gear set of a universal multi-threaded differential gear mechanism, of two friction blocking couplings connecting the crown wheel of the additional lowering planetary gear set with the solar central gear of the first planetary gear set and the carrier of the universal multi-threaded differential mechanism, the solar central gear of the first planetary gear set of the universal multi-threaded differential gear is connected with the help of the friction brake to the transmission case. 6. The modular automatic stepwise planetary gearbox according to any one of claims 1 to 5, characterized in that it has an additional planetary gear set consisting of a central sun gear connected to the crown gear of the third planetary gear set of a multi-threaded differential gear, a carrier connected to the central sun gear the third planetary gear set of the universal multi-threaded differential mechanism, satellites, the solar central gear, which is the output link of the additional planetary gear and a number of transmissions, friction brake, the carrier binding additional planetary gear set and connected with it the central solar gear of the third planetary gear set is a universal multi-threaded differential mechanism from the gearbox housing.

Images