Universal high-torque high-rpm electric drive of pipeline shutoff valves and accessories

FIELD: machine building.

SUBSTANCE: drive two-stage multi-plane-pinion planetary gearbox comprises input shaft 4, support central wheel 11, two-support planet carrier 6, plane pinions in number corresponding to odd number of said pinions in every stage and arranged in pairs on said carrier 6, and two-support output shaft 19 with output central wheel 12 fitted thereon. Axes of motor rotor 7, input shaft 4, carrier 6 and output shaft 19 are arranged inter-aligned and aligned with shutoff valve spindle travel axis. Stator covers rotor and is secured on the flange of housing 1. Input shaft, pinion carrier and reduction gear output shaft are hollow components. Sums of central wheel teeth in both planetary stages are equal and selected from the range of 200…400. Numbers of second stage central wheels are selected from parameters series.

EFFECT: higher reliability and efficiency, decreased sizes.

12 cl, 2 dwg

 

The invention relates to the fields of mechanical engineering and can be used in the structure of any industry machines, but primarily in the valve, pipeline transportation systems for the transportation of liquid and gaseous media.

Known use in geared actuators valves propulsion gear transmissions worm and worm-cylindrical type, for example, the actuator valve piping containing an electric motor with a gear wheel on its shaft, worm gear box with output shaft, mechanism for turning off the motor when the end positions valve, mechanism for limiting torque value, including Belleville springs located on the shaft movable along the axis of the worm on both sides of the support bearing and gear between the motor and the shaft of the worm, which is housed in a gear box connected to the housing, the housing box made of light alloy steel set glass clamp, which is resistant single row ball bearing, bearing is closed by a steel washer, which pojate to the glass of the annular flange, and the flange cover is fitted with ring thrust bearing set free with a gap and on the shaft of the worm in the glass, as well as freely with a gap on both sides between the drill is om glass and steel washer (see EN 2276751 C1, CL F16K 31/02).

The prevalence of such actuators is due to the advantages of worm gears: large gear ratio in one stage (usually uCP=10...60, rarely uCP=60...100 [1]); simple design with a small power flows (up to 2.0...2.5 kW); unilateral conductivity of power and braking.

The disadvantages of the known solutions with the worm gear are: low efficiency, especially when the gear numbers uCP=40...60 and above; increased wear and heat; the propensity for seizure and increased demands for materials timing chains and lubrication; fixed axes of rotation of the input and output shafts (90°) and, as a result, the cantilever mounting of the motor relative to the axis of movement of the spindle; large axial load on the worm; monopolist when transmitting power and limited load capacity of the material of the worm wheel strength and endurance, especially when the increase of the output torque; the impossibility of unification and universalization of the actuator in a predetermined size, and as a result, each valve has its individual drive"and therefore the need to produce a large number of sizes.

Worm drive optimal overall mass parameters only if not the most power (up to 2,0...2,5) kW when the universality of the actuator is provided at the expense of other indicators of its technical level and quality. With the growth of the power flow at the time of the actuator due to monopotente and permanence reduction ratio in one given size becomes structurally flawed and unacceptable in a competitive, performance, durability, overall mass and production reasons.

Known actuator, comprising a housing, an external drive and gear with intermediate rolling bodies, including input shaft, a Cam mounted on the input shaft and made in the form of three identical disks rigidly fixed to the bases so that their centers are symmetrically arranged around the axis of the input shaft, the Central wheel with internal teeth, a separator, in the slots of which there are three rows of intermediate rolling bodies, kinematically connected with the Cam and the Central wheel, the connection of the input shaft gear with intermediate rolling bodies and the external hard drive is implemented, the input shaft is mounted on two bearings rolling, one of the which serve as intermediate rolling elements (see EN 2258168 C1, CL F6K 31/05).

A disadvantage of the known solutions is the presence of a complex kinematic linkages, which result in low reliability and low life, high sensitivity is lnost to precision (at least 4-5 quality class). Other disadvantages include: the location of the geometric axis of rotation of the rotor of the electric motor, the input and output shafts of the power transmission (90°), which makes the drive is bulky, and the impossibility of unification and universalization of the actuator in one given dimension, as is well demonstrated by the wide variety of performances of the actuators manufactured AK "Transneft": EPTS-100; EPTS-400; EPTS-800; EPTS-1000; EPTS-4000; EPTS-10000; EPTS-15000; EPTS-20000; EPTS-35,000 and EPTS-50000 using predominantly on one the corresponding latch.

The closest to the presented solution is the electric valves, containing a reversible motor, rising stem connected to the valve gate, located between the said motor and retractable spindle gear, consisting of a body, a drive eccentric shaft, bevel gear, bevel wheel, cone clutch, drive nut, hollow output shaft, ensuring alignment with sliding spindle, so that the bevel gear is dvuhvekovoi, and bevel wheel connected to the housing and interfaced with the crown dvuhvekovoi gear and conical clutch is connected with the output hollow shaft, the bottom of which is fixed chassis nut, and at the same time involves the crown dvuhvekovoi gear (see EN 2419018 C1, CL F16K 31/04).

A disadvantage of the known solution is the use of four bevel gears and two conical toothed gearings based on them, which imposes extremely stringent requirements for precision manufacturing and Assembly of the transmission, failure to comply with these requirements exclude the possibility of making a workable sample.

Other disadvantages are adenosatellites performance and high frequency portable rotation, which requires a balancing of the rotating mass. Transmission completely eliminates the possibility of varying the gear ratio in one envelope, and therefore, each valve requires his performance of the drive.

The disadvantages include: the metal housing of the actuator and its large dimensions associated with pipe diameter, limited opportunities for reproducible ratios (uCR≤50...60), monoporosa transmission power flow, the complete impossibility of unification and universalization of parts and components, the complexity of the binding of the handwheel, which makes extensive use of the known actuator valves. In addition, two bevel gearing dokvantovogo conical satellite with the input and output of the Central bevel gears require an inclined axis of proper rotations is of the satellite, in consequence, the axis of rotation of the input shaft, the axis of proper rotation of the target satellite and the axis of rotation of the output shaft is not coaxial, and therefore, the transfer may not be multi-threaded.

The invention and due to its technical result is to increase the reliability and efficiency, improving the manufacturability and Assembly, providing the possibility of unification and universalization of the gearbox in the specified size and drive in General, and reduced dimensions and material consumption due to the coaxial installation of the actuator on the valve, and expansion of kinematic and energetic possibilities of its power transmission with cylindrical gears for the given dimensions of the drive.

This result is achieved in that the actuator valves, containing a motor accommodated in the housing of the planetary gearbox comprising an input shaft, satellite, supporting the Central wheel and two output shaft with a fixed output Central wheel, characterized in that the planetary gear is made of two-stage and megasatellite, which it introduced two drove and satellites in the number corresponding to the odd number of satellites in each stage, installed in pairs in the driver, and the axis of rotation ro the ora of the motor, input shaft, the carrier and the output shaft are arranged coaxially relative to each other and coincide with the axis of movement of the spindle of the locking member, the rotor of the motor is rigidly attached to the input of the cantilever part of the input shaft, and the stator cover rotor and fixed to the flange of the housing, input shaft, the carrier and the output shaft is made hollow with through holes, allowing free movement therein, movable parts and the reducer, and the sum of the numbers of teeth of the Central wheels in both planetary stages are equal,

where:,the number of teeth of the small and the support of the Central wheel of the first stage,

,the number of teeth of the small and the output of the Central wheel of the second stage; and must be selected from the range of 200<z<400, the number of teeth of the Central wheel of the second stage is selected from a parametric seriesandso thatis not an integer andis not an integer, whilean integer, and the number of teeth of the Central wheel of the first stage and satellites both stages are set as

p> ,,and,

where:,the number of teeth of the satellites of the first and second stages, respectively,

is determined by the value of the playback gear.

In addition, the support wheel is mounted in the housing on bearings and is held from rotation clockwise or counterclockwise two force sensors installed in the housing and kinematically connected through pushers with a support wheel,

- the manual override is made on the basis of the bevel gear and kinematically connected through bevel gear with the planet carrier, and the total gear ratio from the manual drive is determined by the formula

,

where zto, zWthe number of teeth of bevel wheels and gears of the handwheel, respectively,

his body is made cylindrical and split, with flanged connections with shutoff valves and the electric motor

- supports two drove posted in two parts of the body,

- input shaft is made with two bearings in the drive rod and rigidly attached to it two crowns input small centralnervous,

- building equipment motor controls, mechanisms and sensors control the position of the locking body, the mechanisms and sensors registration and restriction of the output torque and the mechanisms of the handwheel,

- each pair of satellites two stages are installed on the same axis in the driver, with one of the satellites of the pair belongs to the first-stage planetary gear, and the other second stage

- number of satellites in each of the two steps of equal,

where:- the number of satellites in the first stage,

- number of satellites in the second stage,

- the first stage of two-stage planetary gearbox is fast with a gear ratio in the rangeand the second step is slow with the transfer number in the rangewhile the total gear ratio is defined aswhen 1≤∆j≤10,

where: j is the set of replacement wheels fast speed for a particular gate,

- output Central wheel rigidly mounted on the two output shaft, one bearing which is placed on the hub of the output of the Central wheel and the hollow input shaft

- hollow output the al is movable with two outputs: power from the drive spindle nut of the valve and kinematic side input hollow shaft reducer

overall range of the actuator is defined aswhere m is a standard module on the gears of the drive that is assigned from the range m=0,8; 1,0; 1,25; 1,5; 1,75; 2,0; 2,25; 2,5; 2,75 and 3.0 mm with the implementation of the conditions of contact and bending strength and endurance of the teeth, the magnitude of the output torque, mechanical properties of materials gears and manufacturing technologies and thermochemical hardening of the teeth. In addition, the support wheel is mounted in the housing on bearings and is held from rotation clockwise or counterclockwise two force sensors installed in the housing and kinematically connected through pushers with a support wheel.

Figure 1 shows the kinematic scheme of a universal, high-torque multi-turn actuator valves pipeline transport, figure 2 - design claimed actuator on valve setting.

The drawings made the following notations: 1 - body; 2 - motor; 3. - the rotor; 4 - input shaft; 5 - gear; 6 - led h; 7 - the first crowna1small Central wheel; 8 - second crowna2small Central wheel; 9 - the first number of satellites; 10 - second number of satellites; 11 - supporting a large Central wheel b1;12 - output large Central wheel b2; 13 - drive nut node Rope; 14 - spindle; 15 - valves; 16 - the manual override; 17, 18 - bevel gear for connection of the handwheel with the planet carrier (zW-zto); 19 - output hollow shaft; 20 - a claw coupling; 21 - tooth gear on the cantilever part of the output shaft; 22 - input sensor registration provisions of the spindle drive; 23 - adapter binding of the actuator to the valve flange; 24 - angular contact bearings.

Universal, high-torque multi-turn actuator valves pipeline transport contains an electric motor accommodated in the housing of the planetary gearbox comprising an input shaft, satellite, supporting the Central wheel, and two output shaft with a fixed output Central wheel, with planetary gearbox two-stage and performed megasatellite, for which it conducted a two-drove and satellites, in the number corresponding to the odd number of satellites in each stage, installed in pairs in the driver, and the axis of rotation of the rotor of the electric motor, the input shaft, the carrier and the output shaft are arranged coaxially relative to each other and coincide with the axis of movement of the spindle locking body, the rotor of the electric motor rigidly mounted on the input konsolen the second part of the input shaft, and its stator cover rotor and fixed to the flange of the housing, input shaft, the carrier and the output shaft is made hollow with through holes, allowing free movement therein, movable parts and the reducer, and the sum of the numbers of teeth of the Central wheels in both planetary stages are equal,

where:,- number of teeth small and supporting the Central wheel of the first stage;

,- number of teeth small and the output of the Central wheel of the second stage; and must be selected from the range of 200<z<400, the number of teeth of the Central wheel of the second stage is selected from a parametric seriesandso thatis not an integer andis not an integer, whilean integer, and the number of teeth of the Central wheel of the first stage and satellites both stages are set up as,,and,

where:,the number of teeth of the satellites of the first and second stages, with the NGO,

is determined by the value of the playback gear.

The support wheel is mounted in the housing on bearings and is held from rotation clockwise or counterclockwise two force sensors installed in the housing and kinematically connected through pushers with a support wheel.

The manual override is made on the basis of the bevel gear and kinematically connected through bevel gear with the planet carrier, and the total gear ratio from the manual drive is determined by the formula

,

where zto, zWthe number of teeth of bevel wheels and gears of the handwheel, respectively.

The housing of the drive is made cylindrical and split, with flanged connections with shutoff valves and the electric motor.

Supports two drove posted in two parts of the housing and the input shaft is made with two bearings in the drive rod and rigidly attached to it two crowns input small Central wheel.

The case contains control equipment motor mechanisms and sensors control the position of the locking body, the mechanisms and sensors registration and restriction of the output torque and the mechanisms of manual double the A.

Each pair of satellites two stages are installed on the same axis in the driver, with one of the satellites of the pair belongs to the first-stage planetary gear and the other of the second stage.

The number of satellites in each of the two stages is equal to and is,

where:- the number of satellites in the first stage,

- number of satellites in the second stage.

The first stage of two-stage planetary gearbox is fast with a gear ratio in the rangeand the second step is slow with the transfer number in the rangewhile the total gear ratio is determinedwhen 1≤∆j≤10,

where: j is the set of replacement wheels fast speed for a particular valve.

The output of the Central wheel rigidly mounted on the two output shaft, one bearing which is placed on the hub of the output of the Central wheel and the hollow input shaft.

Output hollow shaft is movable with two outputs: power from the drive spindle nut of the valve and kinematic side input hollow shaft reducer for connection with the control equipment.

Overall the number of actuator defines who I am as where m is a standard module on the gears of the drive that is assigned from the range m=0,8; 1,0; 1,25; 1,5; 1,75; 2,0; 2,25; 2,5; 2,75 and 3.0 mm with the implementation of the conditions of contact and bending strength and endurance of the teeth, the magnitude of the output torque, mechanical properties of materials gears and manufacturing technologies and thermochemical hardening of teeth.

Universal, high-torque multi-turn actuator valves pipeline transport is as follows.

When you enable reversing of the electric motor 2, the rotation and power flow through the rotor 3 mounted on the cantilever part of the hollow input shaft 4, are simultaneously transmitted to the crowns of small Central wheela1andand2two planetary stagesand. Then the movement and the moment with the crown ofa1small Central wheel through satelliteswhere i is the number of steps, multithreaded transmitted through the support of the Central wheel b1the tow bars h, and with him on satellites, which simultaneously receives the motion and torque from the second crownand2small Central wheel. Movements and moments are formed on the satellitesand transferred to output the Central wheel b 2mounted on a hollow output shaft 19 connected via a dog coupling (adapter) 20 with a drive nut 13 of the spindle 14 in the actuator Yoke valves 15. Output composite hollow shaft 19 of the gearbox is based on two pillars, one of which is installed in the housing of the gearbox on the output hub of the Central wheel b2and installed on the second supporting portion in the hollow input shaft 4, while on the console of the shaft 19 posted or made integral whole timing gear 21, which forms the entrance 22 to the sensor (figure 1 and 2 is not shown) the registration provisions of the spindle 14 of the drive.

The total gear ratio in the transmission of motion and power to the drive motor is defined as

,

where,and- the gear ratio of the planetary stages and drive in General;,,,,,the number of teeth of the links of the drive.

The objectives are achieved, if the number of teeth of the Central gear units are assigned from the condition of equal amounts in two steps:

.

The numbers of teeth of the Central who's wheels low speed stage is selected from a parametric series andso thatandand. The number of teeth of the Central wheel speed stages and satellites both stages are defined through the number of teeth of the Central wheel low speed stage as,,and,

whereset the value of the playback gear.

In such cases, the angles of engagement in all working links,,andare equal and must be selected from the range of 20°≤αw≤30°, and the total gear ratio is given to the form

when 1≤∆j≤10,

where: j is the set of replacement wheels fast speed for specific valves with specified parameters power flow speed and time.

The last expression allows you to set the size (center distance in the working linksaw=const, the engine NFe=const) to vary the output parameters of the power flow of the drive speed and torque range i.e. ten times by changing the number of teeth of the toothed links fast speed interchangeable wheels.

In confirmation of the above can lead to the determination of the size of the driveandwfollowing from the equality of the sums of the numbers of teeth of the Central wheels of the planetary stages,

,

where m is a standard module on the gears of the drive that is assigned from the range m=0,8; 1,0; 1,25; 1,5; 1,75; 2,0; 2,25; 2,5; 2,75 and 3.0 mm with the implementation of the conditions of contact and bending strength and endurance of the teeth, the magnitude of the output torque, mechanical properties of materials gears and manufacturing technologies and thermochemical hardening of teeth.

Substituting into this formula the number of teeth replacement Central wheel speed stage, defined asandreceived:

when 1≤∆j≤10.

Thus, while variations of the module in the specified range torque output can reach 100 kNm and more.

Does not do not one of the known multi-turn actuators and none of the known power transmission in science and technology.

Thus, changing only replacement wheels,,and adapt the ry 20 and 23 binding multi-turn actuator to the valve flange and the drive spindle nut 14 node Rope you can drive in one envelope and performance to extend to valves of different diameters and pressure, with different settings for speed and torque that provides versatility and unification of the proposed multi-turn actuators. This will allow for the industry to reduce the range of modern mass-produced goods, with 300...500 to five, maximum ten performances, which is economically advantageous, and for operational reasons, it is expedient and promising, including for the unification and universalization of the new machinery for the manufacture of gears.

Thanks to multithreading isinfinite movements in streams increases the number of contact pairs in the working links, while their discharge, which increases the reliability and performance of the drive. All the links of the drive is simple in form and are made on serial machines by serial well-developed production technologies, and therefore, technological, and for group processing gears economical to manufacture. The use of convex-concave contact in the power of the most loaded operating gearing ensures high efficiency and economical operation of the drive.

To check the torque on the output shaft of the support wheel b1installed in the housing for radial-pornom bearing 24 and is prevented from rotating clockwise or counterclockwise the two force sensors, mounted in the housing and kinematically connected through pushers with a support wheel (figure 1 and figure 2 are not shown).

High-torque multi-turn actuator valves pipeline transport can be implemented using standard parts motor windings, standard sensors and electrical control nodes.

Thus, the claimed solution is higher than the reference reliability and efficiency, it is also more adaptable to production and installation, provides the possibility of unification and universalization of the gearbox in the specified size and drive in General, and reduced dimensions and material consumption due to the coaxial installation of the actuator on the valve, and expansion of kinematic and energetic possibilities of its power transmission for the given dimensions of the drive.

Sources of information

1. Iosilevich G.B. machine Parts. M: mechanical engineering, 1988. 368 C.

1. The actuator valves, containing a motor accommodated in the housing of the planetary gearbox comprising an input shaft, satellite, supporting the Central wheel and two output shaft with a fixed output Central wheel, characterized in that the planetary gear is made of two-stage and megasatellite, for che is about to enter a two-drove and satellites in number, the corresponding odd number of satellites in each stage, installed in pairs in the driver, and the axis of rotation of the rotor of the electric motor, the input shaft, the carrier and the output shaft are arranged coaxially relative to each other and coincide with the axis of movement of the spindle of the locking member, the rotor of the motor is rigidly attached to the input of the cantilever part of the input shaft, and the stator cover rotor and fixed to the flange of the housing, input shaft, the carrier and the output shaft is made hollow with through holes, allowing free movement therein, movable parts and the reducer, and the sum of the numbers of teeth of the Central wheels in both planetary speed equal between aare assigned from the range of 200<zΣ<400,
where,the number of teeth of the small and the support of the Central wheel of the first stage;
,the number of teeth of the small and the output of the Central wheel of the second stage,
the number of teeth of the Central wheel of the second stage is selected from a parametric seriesandso thatis not an integer, andis not an integer, while
an integer, and the number of teeth of the Central wheel of the first stage and satellites both stages are set as
,,and,
where,the number of teeth of the satellites of the first and second stages, respectively,
is determined by the value of the playback gear.

2. The actuator according to claim 1, characterized in that the supporting wheel mounted in the housing on bearings and is held from rotation clockwise or counterclockwise two force sensors installed in the housing and kinematically connected through pushers with a support wheel.

3. The actuator according to claim 1, characterized in that the manual override is made on the basis of the bevel gear and kinematically connected through bevel gear with the planet carrier, and the total gear ratio from the manual drive is determined by the formula

where zto, zWthe number of teeth of the bevel wheel and pinion of the handwheel, respectively.

4. The actuator according to claim 1, characterized in that its body is made cylindrical and split with flanged connections with constipation the second valve and the motor.

5. The actuator according to claim 1, characterized in that the input shaft is made with two bearings in the drive rod and rigidly attached to it two crowns input small Central wheel.

6. The actuator according to claim 1, characterized in that building equipment motor controls, mechanisms and sensors control the position of the locking body, the mechanisms and sensors registration and restriction of the output torque and the mechanisms of the handwheel.

7. The actuator according to claim 1, characterized in that each pair of satellites two stages are installed on the same axis in the driver, with one of the satellites of the pair belongs to the first-stage planetary gear and the other of the second stage.

8. The actuator according to claim 1, characterized in that the number of satellites in each of the two steps of equal,
where- the number of satellites in the first degree;
- number of satellites in the second stage.

9. The actuator according to claim 1, characterized in that the first stage of two-stage planetary gearbox is fast with a gear ratio in the rangeand the second step is slow with the transfer number in the rangewhile the total gear ratio is defined as when 1≤∆j≤10,
where j is the set of replacement wheels fast speed for a particular valve.

10. The actuator according to claim 1, characterized in that the output of the Central wheel rigidly mounted on the two output shaft, one bearing which is placed on the hub of the output of the Central wheel and the hollow input shaft.

11. The actuator according to claim 1, characterized in that the output hollow shaft is movable with two outputs: power from the drive spindle nut of the valve and kinematic side hollow input shaft of the gearbox.

12. The actuator according to claim 1, characterized in that its overall range is defined aswhere m is a standard module on the gears of the drive that is assigned from the range m=0,8; 1,0; 1,25; 1,5; 1,75; 2,0; 2,25; 2,5; 2,75 and 3.0 mm with the implementation of the conditions of contact and bending strength and endurance of the teeth, the magnitude of the output torque, mechanical properties of materials gears and manufacturing technologies and thermochemical hardening of the teeth.



 

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Actuating mechanism // 2268431

FIELD: the invention refers to armature construction namely to actuating mechanisms for pipeline armature.

SUBSTANCE: the actuating mechanism has a flange 1 with an opening for installation on the armature, a located under it a bridge 5 with a co-axial opening and an arrangement for fastening of the rod of the armature. The actuating mechanism has also a drive interacting with one of the two cog-wheels located diametrically to the opening of the flange 1 and placed in bearings. The cog-wheels are connected with the bridge 5 through screw mechanisms for its reciprocal movement relatively to the flange. The connection between the cog-wheels is fulfilled through a hollow cog-wheel covering the opening of the flange 1 and having ledges. The hollow cog-wheel contacts with the rollers installed at its both sides.

EFFECT: high meanings of mechanical transmission are achieved.

4 cl, 5 dwg

Gearbox // 2453751

FIELD: machine building.

SUBSTANCE: notable portion of power is transferred via differential gear and portion of power is transferred via gearbox. The latter incorporates two stepped shafts and two gear inverted-tooth chain to allow power transfer in gearshifting. In direct gear, it is possible to cut off gearbox.

EFFECT: higher efficiency, lower weight and costs.

7 dwg

FIELD: machine building.

SUBSTANCE: proposed adjustable differential gear comprises differential mechanism 5 with its input shaft 4 coupled with motor 1 and another shaft 7 coupled with load, and gear ratio adjustment device made up of friction variator. Gear wheel 6 engages via differential mechanism pinion frame with worm shaft 8 and friction variator disc 9. Aforesaid input shaft 4 is engaged via gearing with friction variator second disc 11. Discs 9, 11 are coupled via roller friction gearing with its case 14 coupled with liner displacement drive15. Worm wheel 5 and worm shaft 8 feature helix angle equal to that of friction there between.

EFFECT: simplified design, higher efficiency and reliability.

2 cl, 2 dwg

Steering device // 2441792

FIELD: transport machinery.

SUBSTANCE: this invention covers crawler-type vehicles. A steering device includes two differentials (1, 2) and auxiliary source of torque (3). Input element (4) of the first differential is connected to the drive. Output elements (5, 6) of the first differential are connected to input elements (8, 9) of the second differential so that the output elements of the second differential rotate in opposite direction. Input element (7) of the second differential is connected to auxiliary source of torque (3).

EFFECT: simplification of design.

1 dwg

Differential // 2429143

FIELD: machine building.

SUBSTANCE: differential consists of power elements, of devices for locking and unlocking kinematic link between power elements and of lock members. As power elements there are used worms and worm gears forming self-braking worm pairs. As devices for locking and unlocking kinematic link between power element there are used controlled gear drives of worms from output shafts. The gear drives have similar gear ratios with worm pairs.

EFFECT: raised reliability of differential.

2 dwg

FIELD: machine building.

SUBSTANCE: drive consists of stepless reversible transmission (1), of control mechanism of drive including differential transmission (4) and matching transmission (5). Differential transmission (4) consists of two differential mechanisms (7, 9) kinematically connected with stepless transmission (1). Carrier (6) is connected with an output link of stepless transmission (1) in first differential mechanism (7). One of central wheels (8) is connected with an input link of stepless transmission (1) in the second differential mechanism (9). Matching transmission (5) periodically connects its shaft with one of its central wheels of first differential mechanism (7) and with the carrier of the second differential mechanism (9). Transmission ratios of tooth pairs formed with a kinematic link of the differential and matching transmissions are made to facilitate coincident by frequency and direction rotation of any two driven links coaxial with a shaft of matching transmission (5) and periodically connected with this shaft.

EFFECT: simplified mechanism of control of transmission and implementation of any known types of variators in structure of drive.

13 cl, 14 dwg

FIELD: transport.

SUBSTANCE: invention relates to multiaxle trucks. Proposed system comprises cabin, cargo platform, engine, transmission, running gear and control system. Cargo platform is mounted on two wheeled bogies. Wheeled bogie top and bottom rotary supports accommodate guide posts with their axles supporting balance levers and wheels. Wheeled bogie top part accommodate top reduction gears engaged via gimbal drive with central reduction gears of dual spaced apart final drives with their driven shafts engaged with wheel reduction gears. Wheeled bogies accommodate power hydraulic cylinders. Guide post thrust disks are fitted in slots of hydraulic cylinder piston heads. Two-stage ordinary planetary mechanism is engaged via shafts and reduction gears with combined steering mechanisms. Screw-ball nut-toothed rack-variable gear ratio gears. Gear wheels are locked on bottom rotary supports of guide posts while toothed racks are articulated with rods and pistons of steering hydraulic cylinders. Said power hydraulic cylinders and those of guide posts are communicated via hydraulic lines with pump station, oil tank, control and servo components.

EFFECT: expanded operating performances.

5 dwg

FIELD: machine building.

SUBSTANCE: gear box consists of six-step coaxial three-shaft reducer wherein there are installed eight gears of forward running and two rows of gears of back running, and also simple planetary mechanism ensuring three modes of operation and four clutches of speed change.

EFFECT: expanded operational functionality due to extended range and gear ratio of back and forward running.

2 dwg

FIELD: machine building.

SUBSTANCE: fourteen-step non-axial power-planetary gear box consists of two-shaft non-axial reducer in supports of which there are axially installed input shaft and additional shaft. Parallel to them there is mounted a secondary shaft and an output shaft of the carrier of the three-link planetary mechanism. Two pinions are united into a block on the secondary shaft and engage a pinion of the input shaft and a drive pinion of the additional shaft. 3-position shift collar is installed between these pinions on a rim of the input shaft. Two pinions of forward running are arranged on the additional shaft; they engage pinions freely mounted on the secondary shaft. The drive pinion of back running engages a driven gear of back running of the secondary shaft via the additional pinion. The first 3-position shift collar of the secondary shaft is located on the first rim next to the pinion block. The second 3-position shift collar of the secondary shaft is located on the second rim next to the driven gear of back running. The rim of the output shaft of the carrier is 2-positioned; while the rim of the output shaft of the aggregate is 3-positioned. 3-position shift collar on this rim has three internal rims; also a rim of internal and external engagement is mounted on a slider of this shift collar, and its external engagement is coupled with 3-position rim of the aggregate case.

EFFECT: expanded operational functionality of process vehicles due to extended range and gear ratio of back and forward running.

2 dwg

FIELD: transport.

SUBSTANCE: transfer gear is intended to be used in driveline of three-axis wheeled vehicle and contains housing (1) in the form of casing with parallel carrying walls (2) and (3). Input shaft (4) with gear wheel (5) is installed in the wall (2) and cover (7). In the wall (3) and cover (10), shaft (9) is installed coaxially with the shaft (4) for actuating the rear driving axle. The shat (9) is connected with the shaft (4) via gear clutch (8). In the walls (2, 3), intermediate shaft (15) is installed. It has gear wheel (14) engaged with gear wheel (17) installed in walls (2, 3) on bearings (18). Output shafts (19) and (20) for actuating the front driving axle and another rear driving axle are interconnected via cone-shaped differential gear (21) covered with cap (24). Carrier (22) of the gear (21) is made in the form of stepped socket the journal (23) of which is inserted into axial hole in the gear wheel (17).

EFFECT: increased reliability of transfer gear and its functionality enhancement.

2 cl, 1 dwg

FIELD: machine building.

SUBSTANCE: pulse variator consists of generator of mechanic oscillations, of regulating mechanism and of rectifying mechanism. The rectifying mechanism consists of summing and differential mechanisms, driven shafts of which are coupled with brakes (14, 14', 15, 15') by means of controlled transmission gears (17, 17', 18, 18') with varied gear ratio. The generator creates oscillating motion of driven links with trapezoid law of variation of their velocity and with phases successively set off relative to each other at a quarter-period and successively summed. By means of controlled transmission gears brakes operate at continuous torque under an optimal mode at any gear ratio of the variator; brakes operation is synchronised with generator operation.

EFFECT: increased reliability, service life and efficiency of variator.

2 dwg

FIELD: mechanical engineering.

SUBSTANCE: gear transmission comprises planetary reduction gear and worm pair which engages the planetary reduction gear. Worm (1) of the worm pair is mounted for permitting rotation and axial movement along the driving shaft of the gear transmission and is kinematically connected with satellite (7) of the planetary reduction gear. Driving shaft (2) carries small central wheel (9) of the planetary reduction gear and kinematically connected with satellite (10) of the planetary reduction gear. Satellite (10) is kinematically connected with worm wheel (3). The axle of wheel (3) freely rotates around carrier (4). The axle of large central wheel (8) of the planetary reduction gear is the driven shaft of the gear transmission.

EFFECT: improved design.

1 dwg

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