EA015705B1 - Hydraulic-inertia torque converter and a method of torque conversion by said device - Google Patents

Abstract

The invention relates to mechanical engineering and can be used, for instance for different transport facilities and in devices and mechanisms for shock-free engagement of driven shafts for torque conversion. The claimed invention is aimed at updating a hydraulic-inertia converter and at a method for torque conversion thereby for enhancing their technical and operational features. The achieved result increases the device efficiency in interconnected operation of the hydraulic-inertia converter and the method for torque conversion using said device. Said clamed result is achieved by using the hydraulic-inertia converter and the method for torque conversion implementing said device, the device provides reciprocating motion of plates in radially-made slots in rotor and form therein dynamically-changeable values of circulating volumes of working fluid, thus creating by convertible volumes of the working fluid an inertia component of transferred torque summed with its mechano-inertia part formed at reciprocating motion of discs moved in the rotor radial slots. The summed value of the being converted torque is adjusted to its maximum value transferred to the driven shaft by changing displacement of the driven unit from the central ring position.

Description

The invention relates to the field of engineering and can be used, for example, in various modes of transport, as well as in devices and mechanisms for shock-free switching of driven shafts in order to convert torque.

A centrifugal clutch is known in which the driving half-clutch is made in the form of at least two pairs of couplings, disks with blind tangential grooves, in which monolithic blades are located, ending with massive cylindrical bars, disks with blades and in neutral, and in the working position are inside the rings located in the cylinder filled with lubricating fluid, with the possibility of radial displacement along the guides and installation shifted x in diametrically opposite directions relative to each other (see, for example, RF patent No.2019752, 09/15/94, IPC ⁷ Ρ16Ό 43/18).

A centrifugal clutch is also known, which is one of the closest to the claimed technical solutions, containing the leading and driven half-couplings (see, for example, RF patent No. 2126501, 02.20.99, IPC Ρ16Ό 43/14). The leading coupling half is made in the form of several pairs of discs mounted on the shaft. The driven coupling half includes a drum, several rings with guides installed in the indicated drum with displacement from the central position and with the possibility of radial movement. The clutch also contains several magnets mounted with the possibility of interaction with the said rings. In the drives of the leading coupling half, grooves are made in which plungers are installed. Plungers have the ability to influence the corresponding ring of the driven half coupling under the action of centrifugal force. The cavity of the drum is filled with anti-friction substance. The grooves in the disks of the leading coupling half are made in the tangential direction with a mirror image of the direction of the grooves for each pair of disks. Each of the mentioned plungers is a plate with a cylindrical bar.

This centrifugal clutch works this way. At idle, disks with plungers and working oil rotate together inside the rings and create small torque on them, since the rings are only slightly offset in diameter from the true central position. When the leading coupling half reaches the specified number of revolutions, determined by the force of attraction of the steel rings to the permanent magnets, the centrifugal forces in the right half of the ring begin to prevail over the centrifugal forces in its left half. In this case, the rings are torn off from the permanent magnets and under the action of the increasing centrifugal forces of the plungers smoothly move in diameter and are pressed against the drum wall without impact.

The centrifugal clutch works as a hybrid of a centrifugal and hydrodynamic clutch in a single design. When the speed of the leading coupling half decreases to idle or when it stops completely, the rings shift to the initial position under the influence of the equalizing pressure of the oil, enter the zone of action of the permanent magnets and are attracted by them.

The disadvantages of the known centrifugal clutch are as follows.

1. The plungers are very massive, when working under the action of centrifugal forces, there is a lot of force on the inner surface of the ring, from which the plungers will quickly wear out and become unusable.

2. Due to the high friction of the plungers, the entire coupling will become very hot.

3. There is no clear inclusion of the driven coupling half from the threshold idle speed of the driving coupling half.

4. Torque is transmitted to the driven coupling half only due to the centrifugal forces of the plungers.

Also known are a hydraulic-inertial converter and a method for generating torque, which, by their totality of essential features, are most similar to the claimed technical solutions (patent No. 2259282, July 25, 03, IPC R 16 Ό43 / 18) - the closest analogue. In this converter, the drive unit is made in the form of disks with tangential grooves and blades in them freely set on a splined shaft. Each blade is composed of thin elastic plates. The driven unit is made in the form of a cylindrical body with end caps, one of which is integral with the driven shaft. Rings are installed in the casing, inside of which there are disks with blades of the drive converter assembly. Each ring is installed with the possibility of swinging along the guide, for which it is fastened to the axle shaft installed in the bed of the thrust bearing, the body of which, for example, is put into rigid engagement with the cylindrical body through the dovetail assembly. The shift of the rings from the central position to the eccentric can be carried out by one of the control systems, for example, hydraulic or electromagnetic. The disadvantages of the specified closest analogue are as follows.

1. The design is difficult to manufacture.

2. The swinging ring is not stable when shifting, since in the guide opposite the bed of the thrust bearing it contacts in a line.

3. In the work through the lattice structure of the rings, for each revolution of the leading unit a large volume of working fluid seeps, in connection with which the efficiency of the converter drops, also the lattice structure

- 1 015705 round of rings does not allow the rings to return to the central position from the eccentric, and for one return of the offset bars to their original position.

4. The control system for the movement of rings from a neutral position to an eccentric, bulky.

The objective of the invention is to improve the hydraulic inertial converter (TYPE) and method of converting torque using this device to improve their basic technical and functional characteristics. The technical result achieved is to increase the efficiency with the interconnected operation of the ISU and the method of converting torque using this device.

The specified technical result is achieved, in particular, by the fact that the ISU is made up of master and slave units, with the formation of an internal cavity filled with working fluid, executive, distribution and control mechanisms. The leading GUI unit is made in the form of a monolithic rotor planted on a splined shaft, partitioned in its outer part by radial grooves and plates located in them with the possibility of translational-reciprocal movement of the plates in the grooves when the rotor rotates. In this case, the radial grooves in the rotor of the drive unit of the converter are made through and directed along the axis of the rotor. The drive unit of the converter is made in the form of a housing bounded on the outside by a cylindrical surface with front and rear end caps. The cylindrical part of the gear shaft is built into the end cover of the driven unit housing from the side of the drive shaft without going outside, and its opposite end part is led out through the hole with the sealing element to the end cover from the side of the driven shaft. A sealing ring is located in the front cover on the drive shaft side, and the cover on the drive shaft side is integral with it. A ring is installed inside the housing of the driven unit along its entire length, with the possibility of moving to an eccentric position relative to the rotor and the driven unit.

On the outer side surface of the ring, cylindrical axes protruding beyond its length and rigidly fastened with it are installed, which, without going out, are built into the end caps of the GUI. Also on the outer lateral surface of the ring along its entire length diametrically opposite to the cylindrical axes in the body of the ring are gear teeth introduced into permanent engagement with the gear shaft.

The control mechanism of the transducer is located on the outside of the end cover with the driven shaft and is composed of a gear flag rigidly fixed to the end part of the gear shaft and a hydraulic cylinder with a spring. On the rod of the hydraulic cylinder, rack and pinion teeth are made, which are put into constant engagement with the teeth of the flag. The working cavity of the hydraulic cylinder is connected by a pipeline with a hollow part of the driven shaft, the through radial holes of which are made with abutment to the distribution mechanism equipped with end sealing elements. In this case, the distribution mechanism is hydraulically communicated by means of a pipeline with the main cylinder, and the control mechanism of the converter is equipped with a control signal generating unit in the range of discretely set rotation frequencies of the converter drive unit, which is connected to the drive actuator of the converter drive unit.

Design features of the converter include filling its internal cavity by 85-90% of its volume with a working fluid, which also plays the role of a structural element. To improve the cooling conditions of the converter, the outer cylindrical surface of its driven unit is provided with longitudinal ribs.

The specified technical result is also achieved by the method of converting torque using the GUI, in which at idle or when there is no need to transmit torque using the actuator, distribution and control mechanisms of the converter, the ring of the driven unit is installed in a central, symmetrical relative to the inner surface of the driven unit, position. Then, the driving unit is rotated, by which, by means of its rotor, with the plates located in the grooves of the rotor, the same values of the rotated volumes of the working fluid are formed in dynamically changing cavities bounded by the surface of the rotor, its plates and the inner surface of the ring of the driven unit. In this case, the load inside the ring is evenly distributed and thus the transmitted torque is reduced to zero.

If it is necessary to transfer torque from the master unit to the driven unit, the gear teeth of the ring of the driven unit are rotated with the help of the toothed rod and the gear flag connected to it with the toothed shaft and move the ring of the driven unit to an eccentric position relative to the rotor and the driven unit. Thereby, they provide reciprocating movement of the plates in grooves radially made in the rotor and form dynamically changing values of the rotated volumes of the working fluid. The hydraulic-inertial component of the transmitted torque is thereby created by the volumes of the working fluid that can be converted, summed with its mechano-inertial component, which is formed during rotation by reciprocating plates in the radial grooves of the rotor. The total amount of converted torque is adjusted to its maximum value transmitted to the secondary shaft of the gearbox, by changing the offset from the center position of the ring of the driven unit and the change in the gearbox gearbox reduction coefficient interrelated with it.

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When reducing the load or dropping the number of revolutions of the drive unit of the converter to the idle values, with the help of the spring of the hydraulic cylinder of the control mechanism, the toothed rod and the toothed flag connected to it with the toothed shaft are moved to their original position. In this case, the gear teeth of the ring of the driven unit are moved and, as a result, it is returned to a central position symmetrical with respect to the rotor and the driven unit.

Depending on the practical conditions of the application of the method, its modifications are used, according to which dynamically moving volumes of the working fluid are formed that completely or partially fill the dynamically changing volumes of the cavities with the choice of the number N1 of cavities within 2 <Νι <24.

Bringing the drive shaft into rotation and displacing the rings forms a change in the values of the volume of the cavities in the range from the minimum to the maximum value within 0.7 <(Y ₁ + 0.7 Y ₂ ) / ν ₂ <1.7, where ν ₁ is the minimum value volume of cavities, ν ₂ - the maximum value of the volume of cavities.

In this case, the displacement of the rings creates an imbalance in the center of mass of the plates, moving the center from its coincidence with the axis of symmetry of the rotor by a distance from the axis, the value of which is selected within 1.1 <(b ₁ + 1.1 b ₂ ) / b ₂ <1.4, where b ₁ is the maximum displacement of the center of mass of the plates, b ₂ is the value of the diameter of the rotor. Thus, the total driven torque Γ _{Σ is} formed on the slave unit from its hydraulic Рг and inertial Ри components in the form Ρ _Σ = Рг + Ри = Α (ν ₂ -ν ₁ ) (ω ₁ -ω ₂ ) + ΒΌΤ ₂ ω ₁ ² , where A is the experimental coefficient of proportionality between the value Rg of the hydraulic component of the torque and the maximum value (ν ₂ -ν ₁ ) of the change in the volume of the working fluid in each of the cavities when they are completely filled, ω ₁ is the rotation frequency of the drive shaft, ω ₂ is the rotation frequency driven shaft, In - experimental coefficient of proportionality between y value Pu and total dynamic unbalance of the masses moving plates Ό determined total mass of plates, as well as the values of L ₂ and ω _1. As a result, the driving torque Ρ ₁ is converted into the driven torque Р2 taking into account the magnitude of the reduction gearbox, the values of which are selected from the ratios 1 <(Р ₁ + Р ₂ / к) / Р1 <7.9, 0.2 < k <1.

It is also advisable to optimize the parameters of the method implementation using the possibilities according to which the minimum value ν _{3 of the} sum of the volumes of the working fluid relative to the maximum value of the sum ν _{4 of the} volume of cavities is chosen from the relation 1.1 <((α ₁ ν ₃ + 0.7ν ₄ ) / ν4 <1,9, adjusting ν ₃ via the pilot coefficient α, selected depending on the kind of working liquid and the maximum number N1 of cavities within 0,5 <α ₁ <1.2. The maximum value of the hydraulic component driven torque corrective dissolved using an experimental coefficient A selected within Nm ^-2 to 0.06 <A <0.69 Nm ^-2 and a maximum value of the inertial torque component of the slave are corrected by the pilot coefficient B selected within 1,9.10 ^- Hc kg ^- <Β <7, 110 ^- Ns kg ^- .

It is advisable to illustrate the proposed objects with drawings, in which:

in FIG. 1 shows an internal view of the ISU from the end without one of the end caps, in the idle position of the ring;

in FIG. 2 - the same in the working position of the ring;

in FIG. 3 - shows a view of the ISU from the end, from the side of the driven shaft;

Fig. 4 is a side view of a transducer with a partial cutaway;

in FIG. 5 - a gearbox transmission change box is presented in a section;

in FIG. 6 - shows the ISU and its gearbox assembly with the option of hydraulic control of the gear shaft.

In more detail, the significant design features of the claimed objects and the functional interaction of their main structural elements can be characterized as follows. In accordance with the invention, the GUI comprises a leading and a slave transducer assemblies, in which a transducer master assemblage is made in the form of a monolithic rotor 2 freely mounted on a splined shaft 1 (see Figs. 1, 2, 3, 4) with radial grooves 3 and located in them plates 4. The driven unit of the Converter is made in the form of a cylindrical body 5 with front 6 and rear 7 end caps. In the front cover 6 there is a sealing ring 8. The rear cover 7 is made integral with the driven shaft 9.

In the cylindrical housing 5 of the slave node of the Converter mounted ring 10 (Fig. 1). The ring 10 on the outer lateral surface has protruding beyond its length cylindrical axes 11 and 12 that are rigidly fastened with it (Fig. 3,4), and gear wheels are made diametrically opposite to these axes 11 and 12 in the body of the ring 10 on the outer lateral surface along the entire length teeth 13, which are in constant engagement with the gear shaft 14. In the end cover 6 of the housing 5, without going outside, the cylindrical part 15 of the gear shaft 14 is built in, and the opposite end part 16, through the hole 17 with the sealing element 18, extends outside the end cover 7 from the side of the driven shaft 9.

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On the outer side of the end cover 7 is a hydraulic-mechanical control system, consisting of a gear flag 18 (Fig. 3), mounted on the end cylindrical part 16 of the gear shaft 14 and the hydraulic cylinder 19 with a spring 20. On the rod 21 of the hydraulic cylinder 19 are rack and pinion teeth which are put into permanent engagement with the teeth of the flag 18.

The working cavity of the hydraulic cylinder 19 is connected by a pipe 22 with the hollow part 23 of the driven shaft 9, the through holes 24 of which are adjacent to the distribution unit 25, with end sealing elements 26 and 27. The distribution unit 25 is in turn communicated through a pipe 28 with the main cylinder 29 ( Fig. 6). The cylindrical housing 5 externally has longitudinal ribs 30 for cooling (Fig. 4, 6).

In FIG. Figure 5 shows the checkpoint structurally designed for the full functioning of the ISU. It contains primary 31, secondary 32 and intermediate 33 splined shafts. A primary 31 shaft is introduced into the body of the secondary 32 shaft by its end portion 34, on which a needle bearing 35 is mounted. On the primary shaft 31, a gear 36 is rigidly fixed, engaged in gear with a gear 37 of the same size, which is rigidly fixed on the intermediate 33 splined shaft. On the spline portion of the intermediate 33 shaft, three 38, 39 and 40 gears of different diameters are located with splines inside, respectively, of the splines of the intermediate 33 shaft. Gears 38, 39 and 40 are rigidly interconnected and form a single intermediate gear block, which has the ability to move along the spline portion of the intermediate shaft 33 via carrier 41, into the threaded hole of which is a screw 42 shaft of an electric motor 43 of the control mechanism. On the secondary shaft 32 there are three 43, 44, 45 gears of different diameters. The first 43 gear is rigidly fixed to the secondary 32 shaft with the possibility of engagement with the first 38 gear of the gear block. The second 44th gear, also rigidly attached to the secondary 32 shaft, has the ability to mesh with the second 39th gear of the intermediate gear unit. The third 45 gear of the secondary shaft 32 is rigidly fixed on it and is constantly engaged with a satellite gear 46 located on a short 47 axis, pressed into the rear wall of the housing 48 (Fig. 6) of the box. Satellite 46 gear has the ability to mesh with the third 40 gear of the intermediate gear unit.

In FIG. 6 shows the GUI and gearbox assembly, which is shown in numbers: input shaft 1 of the drive converter assembly, housing 5 of the drive converter assembly, front 6 and rear 7 end caps of the drive converter assembly, longitudinal 30 edges of the housing 5, housing 49 for the converter end cover 7, driven shaft 9 of the driven converter assembly, distribution unit 25. pipeline 28, master cylinder 29, gearbox housing 48, gearbox output shaft 32, gearbox control motor 43, electric motor wire with plus sign 50, electric motor wire with m sign inus 51, protective (fixing) casing 52.

The operation of the ISU and the method of converting torque using this device should be explained in the case of one of their main applications using a car. At the time of warming up the car engine and at idle, the ring 10 inside the driven housing 5 of the converter is set to a central position. In this case, the plates 4 of the rotor 2, rotating the working fluid evenly distribute the load inside the ring 10 and no torque is transmitted to the driven shaft 9.

To move the car from its place and then accelerate it on the end cover 7 (Fig. 3), the toothed rod 21 of the hydraulic cylinder 19 rotates the toothed flag 18, and with it rotates the toothed shaft 14, which moves the ring 10 on the axes 11 and 12 from a central position in eccentric with respect to the rotor 2. The pendulum movement of the ring 10 occurs on the shoulder equal to its outer diameter. At the same time, an increasing torque appears from the beginning from the hydraulic pulses on the driven unit of the converter, and then with an increase in the number of revolutions of the drive unit of the converter and from the inertial forces of the plates 4.

When resetting the speed of the drive unit to idle, the hydraulic control system starts to work in the opposite direction. The spring 20 of the hydraulic cylinder 19 pushes the toothed rod 21 and the toothed flag 18 connected to it with the toothed shaft 14 to its original position. In this case, the ring 10 returns to the center position.

The checkpoint developed for the ISU operates as follows. At the time of warming up the engine and idle, as mentioned above, the ring 10 is in the central position and does not transmit torque to the driven shaft 9 of the converter and, accordingly, to the gearbox. In this case, a single intermediate block of gears 38, 39 and 40 can be located in any position on the splined part of the intermediate shaft 33. With the help of a carrier 41, into the threaded hole of which a screw 42 shaft of an electric motor 43 of a control mechanism enters, a single intermediate block of gears 38, 39, 40 can switch on one of the necessary gears. Direct forward gear when the vehicle is moving on a level road is engaged by gearing 39 of the gear block with gear 44 of the secondary shaft 32. To move the car forward along a serpentine or other, with an increased load for the car, the direct gear with reduction is engaged. In this case, the gear unit gear 38 is engaged with the gear 43. To move the vehicle backward, the gear unit gear 40 is engaged with a satellite gear 46, which is constantly connected to the gear

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45. With this connection, the car moves backward with a reduction in the transmitted torque.

The achieved technical result, as shown by experimental data, can only be realized by an interconnected set of all the essential features of the claimed objects reflected in the claims. The differences indicated in it give reason to conclude that the technical solution is new, and the totality of the claimed claims in connection with their non-obviousness is about its inventive step, which is also proved by the above detailed description of the claimed objects. Compliance with the criterion of industrial applicability of the claimed objects is proved both by the wide manufacture and use of various mechanisms for this purpose, in particular, for converting torque on an industrial scale, and the absence of any practically difficult features in the claimed claims.

To illustrate the achievement of the technical result, which, as already noted, is provided only by the joint use of the declared interconnected objects for all parameter values within their specified limits, in addition to the foregoing and as additional information confirming the possibility of carrying out the invention, it is advisable to give examples of practical implementation of the claimed method in experimental devices, the description of which is impractical to repeatedly state information common to each of the examples and with varying degrees of detail is reflected in the claims and description of the invention. It is advisable to give only quantitative information that distinguishes one example from another, which for convenience is summarized in a table.

When comparing the results of the experiments, reflected in the examples, with respect to the claimed technical solution and the closest analogue, it turned out to be advisable to use as a parameter characterizing the achieved technical result, for example, parameter Ό, which determines the ratio of their efficiency under adequate experimental conditions. As follows from the table, in the best case (example 1 of the table) the highest value of the above result was achieved: Ό = 1.2. The lower and upper values of the declared limits were obtained on the basis of statistical processing of the results of experimental studies, analysis and generalization of them and known from published data sources, based on the condition that parameter Ό approaches 1. Examples 2-6 of the table reflect various options for implementing the declared objects when finding the parameters characterizing their essential features, within the limits reflected in the claims.

Table

No. No. p / p Parameter Name Practical Implementation Numbers one 2 3 4 5 6 one Νι 2 3 4 6 12 24 2 (V! + 0.7½) / ν ₂ 1,2 0.7 1,2 1.3 1,5 1.7 3 (11 + 1.1½) / b ₂ 1,2 1,1 1.14 1.27 1.3 1.4 4 (P1 + P ₂ / c) / ₽! 2.7 1,0 1.8 2,3 3.6 7.9 5 TO 0.6 0.2 0.4 0.5 0.8 one b (ЩУ, + 0,7ν ₄ ) / ν ₄ 1.7 1,1 1.3 1,6 1.8 1.9 7 αι 1,1 0.5 0.7 0.8 0.9 1,2 8 A, Nm ² sec 0.31 0.06 0.19 0.25 0.53 0.69 nine B, N sec ² kg ' ^! 0.41.10 ^-2 1.9.Ι0 ' ³ 3,2.10 ' ³ 5.3.10 ' ³ 6,4.10- ³ 7.1.10 ^-3 10 υ 1,2 1,1 1.15 1,08 1.12 1.14

In addition, with the practical implementation of the HID and the method of converting torque using this device, the convenience of operation is improved, it is also ensured that the slave unit of the converter can be switched on smoothly and clearly in a wide range of speeds of the drive unit and increase their reliability and durability.

Claims (6)

1. A hydraulic-inertial torque converter containing leading and driven units with the formation of an internal cavity filled with working fluid, executive, distribution and control mechanisms, in which the driving unit is made in the form of a monolithic rotor mounted on a splined shaft, partitioned in its outer part radial grooves and the plates located in them with the possibility of translational-reciprocal movement of the plates in the grooves during rotation of the rotor, while the radial grooves in the rotor lead about the converter assembly is made through and directed along the axis of the rotor, the driven converter assembly is made in the form of a housing bounded externally with a front and rear end covers, into the end housing of the driven assembly housing, from the drive shaft side, the cylindrical part of the gear shaft is integrated without going outside, and its opposite end part through the hole with the sealing element is brought out into the end cover from the side of the driven shaft, in the cover from the side of the drive shaft is located a protective ring, and the cover on the side of the driven shaft is made integral with it, a ring is installed inside the housing of the driven unit along its entire length, with the possibility of moving to an eccentric position relative to the rotor and the driven assembly, protruding beyond its side surface and rigidly mounted on the outer side surface of the ring the cylindrical axes attached to it, which are built into the end caps without going outside, on the outer side surface of the ring along its entire length is diametrically opposite to the cylindrical axes in the body gear teeth made in permanent engagement with the gear shaft, the control mechanism of the converter is located on the outer side of the end cover with the driven shaft and is composed of a gear flag rigidly fixed to the end of the gear shaft, and a hydraulic cylinder with a spring, on the rod of which gear rack teeth are made gears engaged in permanent engagement with the teeth of the flag, the working cavity of the hydraulic cylinder is connected by a pipeline with a hollow part of the driven shaft, the through radial holes of which are made adjacent to the distribution mechanism equipped with end sealing elements, the distribution mechanism is hydraulically connected via a pipeline to the main cylinder, and the control mechanism of the converter is equipped with a generating unit for a control electric signal in the range of discretely set rotation frequencies of the drive unit of the converter, which is connected to the actuator for switching on the follower converter assembly. 2. The Converter according to claim 1, the inner cavity of which is 85-90% of its volume is filled with a working fluid. 3. The Converter according to claim 1, in which the outer cylindrical surface of the driven unit is provided with longitudinal ribs for cooling. 4. The method of converting torque using the device according to claims 1 to 3, in which at idle speed or when there is no need to transmit torque using the actuator, distribution and control mechanisms of the converter, the ring of the driven unit is installed in a central, symmetrical with respect to the inner surface of the driven unit, position, drive the drive unit into rotation, by which, with its rotor, with the plates located in the grooves of the rotor, form the same values of the rotated volumes p fluid in dynamically changing cavities bounded by the surface of the rotor, its plates and the inner surface of the ring of the driven unit, evenly distribute the load inside the ring and thereby reduce the transmitted torque to zero, if necessary, transfer torque from the driving unit to the driven unit gear teeth of the driven unit ring with the help of the toothed rod and the gear flag connected to it with the gear shaft and move the driven unit ring to an eccentric rel relative to the rotor and the driven unit, the position thereby ensures reciprocating movement of the plates in grooves radially made in the rotor and thereby form dynamically changing values of the rotated volumes of the working fluid, thereby creating a hydraulically inertial component of the transmitted torque, which is converted by the volumes of the working fluid, summed with its mechanical inertia component, formed during rotation by reciprocating plates in the radial grooves of the rotor, regulate the the magnitude of the converted torque to its maximum value transmitted to the secondary shaft of the gearbox, changing the offset from the central position of the ring of the driven unit and the interconnected change in the gearbox reduction coefficient, while reducing the load or dropping the speed of the drive unit to the idle stroke, with the help of the spring of the hydraulic cylinder of the control mechanism, the toothed rod and the toothed flag connected to it with the toothed shaft in the initial position, while the gear teeth of the ring of the driven unit are moved and eventually returned to a central position symmetrical with respect to the rotor and the driven unit. 5. The method according to claim 4, in accordance with which dynamically moving volumes of the working fluid are formed, which completely or partially fill the dynamically changing volumes of the cavities, the number Νι of cavities is chosen in the range -> ^Μ ι \ 24. driving the drive shaft and shifting the rings - 6 015705 change the values of the volume of the cavities in the range from the minimum to the maximum value within where V1 is the minimum value of the volume of the cavities, ν ₂ is the maximum value of the volume of the cavities, while the displacement of the rings creates an imbalance in the center of mass of the plates, moving the center from its coincidence with the axis rotor symmetry at a distance from the axis, the value of which is chosen within 1.1 <(b1 + 1.1 b ₂ ) / b2 <1 ₅ 4, where b ₁ is the maximum displacement of the center of mass of the plates, B ₂ - the value of the diameter of the rotor, and thereby on the slave node form the total driven torque Ρ _Σ from its hydraulic Rg and inertial Ri components in the form Р ₂ = Рг + Ри = А (ν ₂ - V)) (c) 1-oe ₂ ) + В О Er ad ζ where А is the experimental coefficient of proportionality between the value Рг of the hydraulic component of the torque and the maximum value (ν ₂ -ν ₁ ) changes in the volumes of the working fluid in each of the cavities when they are completely filled, ω ₁ is the rotation frequency of the drive shaft, ω ₂ is the rotation frequency of the driven shaft, B is the experimental coefficient of proportionality between the value of Pu and the total dynamic imbalance Ό of the masses of the moving plates, determined by the total mass of the plates, as well as the values of L ₂ and ω ₁ , as a result of which the leading Ρ ₁ torque is converted into the driven P ₂ torque taking into account the reduction gearboxes, the values of which are selected from the relations 1 <(P] + P ₂ / k) / P1 <7.9, 0.2 <k <1. 6. The method according to claim 5, in which the minimum value ν _{3 of the} sum of the volumes of the working fluid relative to the maximum value of the sum ν _{4 of the} volumes of the cavities is selected from the ratio 1.1 <(αιν ₃ + 0.7U ₄ ) / Y ₄ <1.9, adjusting ν ₃ using the experimental coefficient α ₁ , selected depending on the type of working fluid and the maximum number Ν _{1 of} cavities within 0.5 <ss <1.2, and the maximum value of the hydraulic component of the driven torque is adjusted using the experimental coefficient A, chosen within 0.06 Nm ' ² s <A <0.69 Nm ² s, and the maximum value of the inertial component of the driven torque is adjusted using the experimental coefficient B, selected within