RU140652U1 - RANGE CONTINUOUS PLANETARY GEARBOX - Google Patents

Abstract

1. A range planetary gearbox containing a drive shaft, a driven planetary gear set and an auxiliary planetary gear set, characterized in that each planetary gear set contains three links: a sun gear, a carrier with satellites and an epicycle, any one link of a driven planetary gear set is a leading link, one any link of the driven planetary gear is a driven link and any one link of the driven planetary gear is an auxiliary link, any one link of the auxiliary planetary gear is a leading link, one o any link of the auxiliary planetary gear is a driven link and any one link of the auxiliary planetary gear is an auxiliary link, at least two links of the driven planetary gear have rotation in one direction and at least two links of the auxiliary planetary gear have rotation in one direction while the range planetary gear is configured to transmit torque from the driven link of the auxiliary planetary gear to the auxiliary link of the driven plan the tare row, and is configured to transmit torque from the driven link of the driven planetary gear to the auxiliary link of the auxiliary planetary gear, through at least two clutches and at least two gears with different gear ratios, made with the possibility of simultaneous the inclusion of one clutch and is made with the ability to control when driving on / off transmission modes by turning on / off the clutch. 2. Band �

Description

FIELD OF TECHNOLOGY

This utility model relates to planetary gearboxes and their use in automatic transmissions.

BACKGROUND

Known differential variator patent RU No. 2457379. In this variator containing a planetary gear of the first stage, consisting of a central gear and a carrier with satellites, a planetary gear of a second stage, consisting of a carrier with satellites and a central gear, and a planetary gear of the third stage, consisting of a carrier, satellites and a central wheel, the first and the third planetary gears are closed by a two-crowned crown of a certain mass, and the number of teeth is selected in such a way that it allows to obtain a variable moment on the output shaft [1].

The disadvantage of this design is the design itself, made coaxial and not having support on the housing.

Known for modern automatic transmissions. These gearboxes are used to step change the torque, as well as to provide reverse movement of the car. On automatic gearboxes, as a rule, planetary gearboxes are used, which differ in compactness and the possibility of coaxial operation. An automatic transmission consists of several (usually two) planetary gears connected in series for collaboration. The combination of planetary gears allows you to provide the required number of stages of work. Modern automatic gearboxes are six-speed, seven-speed (Mercedes) and even eight-speed (Lexus).

The planetary gearbox in the gearbox is called the planetary gear set. The planetary gear set has the following device: sun gear, satellites, ring gear, carrier.

The transmission of rotation is subject to the blocking of one or two elements of the planetary gear set (sun gear, ring gear, carrier). The locking is carried out by the corresponding friction clutches and brakes. The clutch blocks the elements of the planetary gear between each other and, thereby, provides the transmission of torque. The brake holds specific elements by connecting to the box body. Clutches and brakes are driven by hydraulic cylinders, which are controlled from a distribution module. An overrunning clutch can be used in the design of the box, which keeps the carrier from rotating in the opposite direction.

Thus, the gearshift mechanisms in the automatic gearbox are friction clutches and brakes. The operation of the automatic transmission is to perform a specific algorithm for turning on and off clutches and brakes [2].

The technical disadvantages of these gearboxes are slow gear shifting and poor dynamics of acceleration of the car.

These technical solutions are taken as a prototype, as they have the maximum combination of essential features common with the utility model.

PURPOSE OF USEFUL MODEL AND TECHNICAL RESULT

The objective of the utility model is to create the most efficient gearbox with continuous transmission of torque from the engine to the drive wheels.

The technical result is a simplification of the design and material consumption of the gearbox, reducing the number of parts responsible for switching on / off transmission modes.

DISCLOSURE OF A USEFUL MODEL

The solution of the above problem proposed in the utility model, the achievement of the goal and the required technical result is ensured by the fact that in the gearbox containing the drive shaft, the driven planetary gear and the auxiliary planetary gear, according to the utility model

each planetary gear set contains three links: a sun gear, a carrier with satellites and an epicycle, one any link of a driven planetary gear is a leading link, any one link of a driven planetary gear is a driven link and one any link of a driven planetary gear is an auxiliary link, any one link of the auxiliary planetary gear is the leading link, any one link of the auxiliary planetary gear is a driven link and any one link of the auxiliary planetary gear is an auxiliary lnym link.

At least two links of the driven and auxiliary planetary gear rotate in the same direction.

In this case, the driven link of the driven planetary gear set transmits the torque to the auxiliary link of the auxiliary planetary gear, through at least two clutches and, at least through two gears with different gear ratios, the driven link of the auxiliary planetary gear transfers the torque to the auxiliary link driven planetary gear set.

In addition, the gearbox is capable of simultaneously turning on only one clutch and with the ability to control when moving on / off modes by turning on / off the clutch.

The gearbox can also be made with reverse gear, while using a planetary gear reverse gear.

BRIEF DESCRIPTION OF THE DRAWINGS

The essence of the utility model is illustrated by drawings:

Figure 1 shows the kinematic diagram of a range planetary gearbox with four clutches according to a utility model, containing:

motor output shaft 1; gearbox drive shaft 2; gearbox output shaft 3; the leading link of the driven planetary gear 4; driven unit of the driven planetary gear 5; auxiliary link driven planetary gear 6; the leading link of the auxiliary planetary gear 7; the driven link of the auxiliary planetary gear set 8; auxiliary link of the auxiliary planetary gear 9; the intermediate shaft of the driven planetary gear set 10; clutch shaft 11; gear drive the drive shaft 12, 13; gears of an auxiliary link drive of an auxiliary planetary gear set of a zero mode 14, 18; gears of an auxiliary link drive of an auxiliary planetary gear set of the first mode 15, 19; gears of an auxiliary link drive of an auxiliary planetary gear set of the second mode 16, 20; gears of an auxiliary link drive of an auxiliary planetary gear set of the third mode 17, 21; gears of a drive of a shaft of couplings of couplings 22, 23; zero mode clutch 24; a first mode clutch 25; a second mode clutch 26; third mode clutch 27; one way clutch 28.

Figure 2 shows the kinematic diagram of a range planetary gearbox with two clutches according to a utility model, containing:

motor output shaft 1; gearbox drive shaft 2; gearbox output shaft 3; the leading link of the driven planetary gear 4; driven unit of the driven planetary gear 5; the leading link of the auxiliary planetary gear 7; auxiliary link of the auxiliary planetary gear 9; gears of a drive of a leading shaft of a transmission 12, 13; gears of an auxiliary link drive of an auxiliary planetary gear set of a zero mode 14, 18; gears of an auxiliary link drive of an auxiliary planetary gear set of the first mode 15, 19; gears of an auxiliary link drive of an auxiliary planetary gear set of the second mode 16, 20; gears of an auxiliary link drive of an auxiliary planetary gear set of the third mode 17, 21; overrunning clutch 28; the auxiliary link of the driven planetary gear and the driven link of the auxiliary planetary gear 29; the clutch shaft of the zero and second mode 30; the clutch shaft of the first and third mode 31; clutch drive gears 32, 33; the clutch of the first and third mode 34; clutch zero and second mode 35; clutch synchronizer enable zero and second mode 36; the clutch synchronizer enable the first and third mode 37.

Below, the utility model is discussed in more detail with reference to the drawings attached to the description, which show, by way of example, preferred but optional options for the possible implementation of the utility model, structural design and operation of the vehicle gearbox proposed in the utility model.

IMPLEMENTATION OF A USEFUL MODEL

Distinctive features of the claimed gearbox are:

lack of constant switching;

the presence of a drive shaft and two planetary gears: driven and auxiliary, each of which contains three links: a sun gear, a carrier with satellites and an epicycle, any one link of a driven planetary gear is a leading link, any single link of a driven planetary gear is a driven link, and any one the link of the driven planetary gear is an auxiliary link, any one link of the auxiliary planetary gear is the leading link, any one link of the auxiliary planetary gear is the driven link and o the bottom of any link of the auxiliary planetary gear is an auxiliary link;

rotation of at least two links of the driven and auxiliary planetary gear in one direction;

drive the auxiliary link of the auxiliary planetary gear set through at least two clutches and at least two gears with different gear ratios with the possibility of simultaneously turning on one clutch and with the possibility of controlling the modes on / off by turning on / off clutches;

the addition of torque from the auxiliary link to the driven link of one planetary gear set;

the desire of the output shaft to the maximum revolutions of the included clutch.

To control the clutches of the gearbox, a computerized gearbox control system can be used, including input sensors, an electronic control unit, electro-hydraulic control units and actuators that can be located directly on the gearbox housing.

Input sensors monitor the speed at the input and output of the gearbox, the pressure and temperature of the oil. An electronic control unit based on sensor signals - implements the gearbox control algorithm embedded in it.

The electro-hydraulic control unit provides operation of the hydraulic circuit of the gearbox control, which may include spool valves; pressure control valves; multiplexer. The spools can be operated by the selector lever. Solenoid valves can switch from mode to mode. Pressure control valves provide friction clutch operation. Solenoid valves and pressure control valves are the actuators of the gearbox control system.

The operation of the gearbox according to the utility model is as follows and will be shown on the example of a range planetary gearbox with four clutches (Figure 1):

The range of planetary gearbox (Figure 1) is as follows. Vehicle engine started. All shaft clutches 11 are turned off. The clutch 25 of the first mode is engaged. The torque from the output shaft of the engine 1 is transmitted through gears 12 and 13 to the drive shaft 2 of the gearbox, as well as to the driving link 4 of the driven planetary gear set on this shaft and to the driving link 7 of the auxiliary planetary gear set. Next, the torque from the driven link 5 of the driven planetary gear is transmitted to the drive wheels and through gears 22 and 23 to the shaft 11 of the clutch. The gears 19 and 15 of the first mode, which are in constant gearing, drive the auxiliary link 9 of the auxiliary planetary gear set, which adds torque to the driven link 8 of the auxiliary planetary gear set. Further, the torque from the driven unit 8 of the auxiliary planetary gear set is transmitted through the intermediate shaft 10 to the auxiliary unit 6 of the driven planetary gear set, which adds torque to the driven unit 5 of the driven planetary gear set. Each clutch provides specific maximum revolutions of the output shaft 3 of the gearbox. The output shaft 3 of the gearbox tends to the maximum speed of the clutch 25 of the first mode. The revolutions of the output shaft 3 of the gearbox continue to grow, and when a certain number of revolutions is set, the clutch 25 is turned off and the clutch 26 is turned on. The output shaft 3 of the gearbox tends to the maximum revolutions of the clutch 26 of the second mode. When the revolutions of the output shaft 3 of the gearbox and also to a certain number of revolutions fall, the clutch 25 is turned off and the clutch 24 is simultaneously turned on. Now the output shaft 3 of the gearbox tends to the maximum revolutions of the clutch 24 of the zero mode (first gear), but only in the direction of reduction revolutions.

Thus, the transmission according to a utility model provides the ability to achieve the desired technical result, namely, simplifying the design and material consumption by reducing the number of parts and increasing its compactness, speeds up and simplifies the on / off transmission modes due to the possibility of using modern computerized control units and operation control.

Individual parts and components of the inventive gearbox can be manufactured using materials and technologies known in the engineering industry.

Specific dimensions and individual design features of individual parts and assemblies can be selected from standard sizes and standards of industrial engineering.

INFORMATION SOURCES

1. RU No. 2457379 F16H 3/74, publ. 07/27/12.

2.http: //systemsauto.ru/box/akpp.html.

Claims (4)

1. A range planetary gearbox containing a drive shaft, a driven planetary gear set and an auxiliary planetary gear set, characterized in that each planetary gear set contains three links: a sun gear, a carrier with satellites and an epicycle, any one link of a driven planetary gear set is a leading link, one any link of the driven planetary gear is a driven link and any one link of the driven planetary gear is an auxiliary link, any one link of the auxiliary planetary gear is a leading link, one o any link of the auxiliary planetary gear is a driven link and any one link of the auxiliary planetary gear is an auxiliary link, at least two links of the driven planetary gear have rotation in one direction and at least two links of the auxiliary planetary gear have rotation in one direction while the range planetary gear is configured to transmit torque from the driven link of the auxiliary planetary gear to the auxiliary link of the driven plan the tare row, and is configured to transmit torque from the driven link of the driven planetary gear to the auxiliary link of the auxiliary planetary gear, through at least two clutches and at least two gears with different gear ratios, made with the possibility of simultaneous the inclusion of one clutch and is made with the ability to control when moving on / off transmission modes by turning on / off the clutch. 2. The range planetary gearbox according to claim 1, characterized in that the driven link of the auxiliary planetary gear set and the auxiliary link of the driven planetary gear set are common to both planetary gear sets. 3. The range planetary gearbox according to claim 1, characterized in that it is made with reverse gear. 4. The range planetary gearbox according to claim 3, characterized in that it contains a planetary gear reverse gear.

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