RU2701306C1 - Rotary bulk machine - Google Patents

Abstract

FIELD: machine building.

SUBSTANCE: invention relates to machine building, particularly, to rotary volumetric machines. Machine comprises housing with end covers, in bores of which there are drive and driven working gears, forming axial transmission. Each gear consists of a hollow hub and a disk with teeth arranged on its periphery, in the form of a crown, consisting of separate sections with an asymmetric profile, having front and rear surfaces. In the housing there are working medium supply-discharge channels. Gears are installed on hollow axes at an angle providing covering their crowns on the whole circle. Each hollow axis is fixed on one side on end cover, and on other side it is connected with part of housing located between central parts of gears. Disk of each gear is equipped with at least two shells enveloping the crown of teeth on outer and inner sides. Each section of teeth is equipped with permanent magnets. Disk of drive gear is equipped with gear transmission with shaft output from inner space of housing through seal. Through holes of hollow axes are channels of supply-and-discharge of working medium.

EFFECT: higher efficiency of machine.

23 cl, 17 dwg

Description

The invention relates to mechanical engineering, in particular to compressors for pumping gases, creating a vacuum, as well as to power elements of pneumatic drives - pneumatic motors, pneumatic compressors, and in addition, can form the basis for creating rotary internal combustion engines.

In volumetric hydraulic machines of rotary type, displacers are involved in creating a working medium flow and giving it a pressure (pressure), the principle of operation of which is either to change the interscapular volume during rotation of the rotor due to the housing architecture, or to merge several flows into the resulting one, also due to the corresponding the shape of the case and in the presence of shielding (locking) plates, or to direct displacement of the liquid, for example, by the teeth of gears.

The efficiency of the working process of the considered second type of rotary hydraulic machines largely depends on the isolation of portions of the working medium located between the blades, firstly, from each other, and secondly, in the direction of the sinuses between the rotor disks and the housing covers.

In the well-known rotary piston-radial compressor (WO 03/055551 A1 (SELEON GMBH), 07/10/2003, F04C 18/56) comprising an inlet channel, an outlet channel, a first impeller with blades, a second impeller with blades through the drive shaft is transmitted rotation, the housing, which is formed by excluding the volumes of the impeller bearings symmetrically with respect to the plane of symmetry, while the impellers are located in the housing so that the blades of the first impeller are introduced into the cavity between the blades of another impeller, and their axes are rotated The lines intersect at a point at an angle in the plane of symmetry, while one blade in the first cavity displaces a larger or smaller volume when the impeller rotates, so that the liquid is removed due to the outlet channel (11) or, thanks to the inlet channel, magnets are integrated into the impeller blades so that each blade of one impeller repels nearby blades of the other impeller, and thus power is transmitted from one impeller to another impeller without contact.

In the proposed embodiment, the transmission of torque to the second impeller is not any mechanical wear between the wheels. However, such a device can only work as a centrifugal vortex pump with a low efficiency (30-40%) when converting energy from a mechanical form to hydraulic, since there is no closure of the blades in their engagement and the working fluid flows from the high pressure zone to the zone low through an unlocked labyrinth between the blades by the reverse flow.

Also known is a rotary hydro-pneumatic machine (patent for the invention No. 2627753, publ. 11.8.2017., Bull. No. 23), adopted for the prototype, containing a housing with end caps, in the bores of which are placed the driving and driven working gears, consisting of a hollow hubs and discs with teeth placed on its periphery with an asymmetric profile, forming a ring gear, having front and back surfaces, channels for supplying and discharging working fluid, sealing elements, working gears are made bevel and each of two pairs of the same gears form axial gears with axes of rotation intersecting at one point, while two supply and exhaust channels are located on the housing in the zone of maximum overlap of the teeth of the working gears, and the other two in the zones of the beginning of tooth adhesion, the channels are located on the periphery of the housing and are equipped with locking equipment.

The considered design of a rotary hydro-pneumatic machine involves the implementation of each tooth of the driving and driven working bevel gears in the form of sections (paragraph 1.13 of the claims of the prototype), which, when engaged, form a complex maze that prevents the flow of working fluid through it. The mating surfaces of each pair of tooth parts from each section of the engaging working bevel gears are profiled with a ruled surface formed by a generatrix originating from the center of intersection of the axes of the working bevel gears, according to the kinematics of the movement of the tooth input edge as it engages when these gears rotate synchronously. Such a profile implies direct contact of the parts of the teeth, and hence the exclusion of the gap between them, which, when the bevel gears are executed accurately, prevents an arbitrary flow of the working medium through mating from one interdental space to another.

However, an uncontrolled transfer from one interdental volume to another takes place, to one degree or another, through the sinuses between the disk of the working bevel gear and the end caps of the housing (Fig. 1, element 1), since the labyrinth seal in the form of an annular protrusion on the disk with mating groove on the end cap reduces overflow, but does not exclude it at all.

A decrease in functional indicators (volumetric efficiency) of the considered rotary hydro-pneumatic machine may also occur due to the possible overflow of the working medium from the teeth into the gap:

- on a small radius of the ring gear (Fig. 1, element 2) of each of the working bevel gears between the fixed bevel housing in the housing bore and the movable ends of the teeth;

- on the largest radius of the teeth of the working bevel gears between the ends of the movable teeth and the peripheral walls of the bore of the body (Fig. 1, element 3);

- between the vertices of the movable teeth and the fixed end wall in each of the bores of the body (Fig. 1, element 4).

Moreover, these flows, with an increase in the speed of the rotary hydraulic-pneumatic machine, which takes place on gaseous media, will increase, since the pressure unevenness on both sides of the mating blades will add pressure unevenness due to the dynamic component from the influence of each rapidly rotating blade on the working medium.

During operation, the above clearances tend to increase either due to crevice cavitation when working on liquids, or due to abrasive wear when working on abrasive media, therefore, the performance of such devices will decrease:

- when they are used as pumps and compressors, the pressure and flow will fall;

- when they are used as hydraulic and pneumatic motors, the torque on the shaft and its speed will decrease, which in both cases will lead to the need to increase power consumption to achieve the required performance of a rotary hydraulic pneumatic machine.

The completion of devices with a contact seal system will significantly complicate the design as a whole, increase its cost, and reduce reliability. In addition, the high pressure drop across the seal requires a greater degree of pressing of the sliding surfaces, and this greatly increases the moment on the shaft of the rotary hydraulic-pneumatic machine due to increased friction.

Another feature of the prototype is that the inlet and outlet channels extend over almost the entire compression and expansion zone, which determines the operation of the teeth only in the area of the contactor. Thus, the suction zone from the discharge zone is separated by only one pair of mating teeth and can withstand the complete pressure drop created by the pump or by a hydraulic motor under load. Such a pressure drop with existing gaps around the rotating teeth covered by the corresponding fixed surfaces of the grooves of the housing causes high volumetric losses

Where

μ is the flow coefficient determined by the flow pattern;

ω is the cross-sectional area of the outflow circuit, m ² ;

N is the pressure of the fluid in front of the gap, m;

g - gravity acceleration, g = 9.81 m / s.

It would be advisable to distribute this differential pressure to a larger number (k) of pairs of blades. Then the total losses in the cascade of consecutive local resistances would be only

Where

k is the number of pairs of blades involved in the blockade of differential pressure.

However, the prototype of this event is not provided.

Moreover, with a partial overlap of the crowns of the working bevel gears, which is the case with the prototype, the number of tooth pairs involved in restraining the pressure drop in this case also does not correspond to the maximum possible, since the teeth outside the mesh gears make only idle on the arc outside the mesh and Do not participate in the creation and containment of pressure. In addition, the teeth that are not involved in the engagement cause non-functional, parasitic volumes, which means excessive dimensions and weight of the hydraulic machine.

The third feature of this arrangement is that in this case, a smooth compression of the liquid is not ensured at an increased rotational speed of the bevel gears, and therefore significant hydraulic losses occur proportional to the square of the flow rate.

Another feature of the presence of the zone in which the teeth are not engaged is that all the elements of the parts and the details of the rotary hydraulic-pneumatic machine during operation operate with natural frequencies. When the teeth enter from the free state into engagement, they, the teeth, also oscillate, firstly, as cantilever elements mounted on the disk, and secondly, due to vibrations of the complex shape of the disk itself as a bearing element of the teeth, and thirdly, due to vibrations of the fixed elements of the housing holding the movable, as well as due to vibrations of the moving elements themselves within the gaps of their installation.

Consequently, such an oscillating tooth occupies a much larger volume than that determined by the geometrical dimensions in statics, and when they engage with another same tooth (another working bevel gear), they mutually collide. The result of the impact is transmitted through the material of the working bevel gears to other teeth that are engaged, and also makes them tremble. Mutual collisions of the teeth engaged, cause their mutual repulsion, which causes periodic creation of a gap between them, that is, periodic depressurization of the joint.

In addition, this circumstance is additional resistance to the rotation of the working bevel gears during the phase of each tooth engagement, as well as the cause of wear of both the teeth themselves and the housing in this zone and the zone of divergence of the teeth.

Another circumstance causing a negative consequence is the presence of a housing element between the central parts of the bevel gears in the form of an axial ring suspended from the housing on a thin jumper. The small rigidity of the cantilever jumper makes it possible to oscillate this element of the casing with a large amplitude, which in turn causes an increase in volumetric losses through the gap of the casing wall - a rotating tooth, its increase due to wear from periodic impact contact, and therefore an even greater increase in volumetric losses during operation .

In addition, the small thickness of the jumper does not allow it to accommodate the supply and exhaust communications of the working environment, since on the one hand they are simply difficult to place there, and on the other hand, their targeted placement will even more reduce the rigidity and strength of such a jumper.

An increase in the thickness of the jumper can only be achieved by increasing the angle θ of the camber of the working bevel gears, and this measure will lead to a reduction in the number of teeth participating simultaneously in the engagement and an increase in the number of teeth outside the engagement.

Scientific and technological progress provides the proper level of material well-being of society, and to ensure a more intensive development of technology, the objective laws of its evolution should be taken into account. Currently, the technology is developing in two directions:

- the creation of new devices, technologies based on new physical principles of action;

- improvement of existing machines.

The first samples of new devices are most often more promising, but imperfect and prone to "childhood diseases", for the elimination of which a chronological resource is needed.

Traditional designs were also once fundamental innovations, but to a considerable extent have gone the way of improvement, therefore, they must have both high functional indicators and operational characteristics - durability, economy, reliability, weight and size characteristics, low cost, etc.

The prototype under consideration has reduced qualities of tightness, which reduces the efficiency of its working process, and this circumstance makes it necessary to achieve the required results:

- either increase the dimensions of the machine compared to its possibly more advanced version;

- either increase the speed of its rotor part - the speed of rotation of the bevel gears.

Each of these measures entails the need to increase drive power, which means in both cases an increase in the overall dimensions of the unit, and therefore, its cost and the cost of the entire machine, of which it is a part.

The imperfection of the working process will also increase operating costs, the total rise in price of which over time can be hundreds of times higher than capital costs.

Thus, the operational performance of such hydraulic machines is still low today, which leads to their insufficient efficiency and insufficient volumes of their use in industry. Since the bulky overall dimensions of these devices still limit their use in aviation and astronautics, insufficient reliability often generally excludes their use in military equipment. The low efficiency of the working process of such devices leads to low competitive ability in the sales market.

The field of use of this type of machine is very extensive: pumping, compressor equipment, actuators in hydro-pneumatic systems, manual pump-compressor equipment in gardening and farming enterprises, they can be pressure elements in the non-motorized rise of water from rivers and springs for water supply to farms and small settlements, can be used as turbines, and, both in a system with other mechanisms (ICE with supercharging), and in the form of turbines themselves in the production of electricity, the rotor is the basis s ICE, etc.

With the existing level of quality indicators, this device can be used in a small, limited part

the above segment, and when the device reaches a more perfect performance, it can occupy a more significant niche among the listed mechanisms.

In addition, technically advanced machines are the basis for creating on the basis of their complexes with new properties, with an expanded area of use, including in areas that are currently not traditional for people.

So, according to the objective laws of the development of technology, the next stage in the production of machines is the stage of creating robotic devices that adapt to the conditions and tasks set by supplementing the multivariate mechanical part with artificial intelligence. Therefore, it is necessary now to produce such mechanisms and devices that are characterized by variability, the possibility of reincarnation by either changing the mode of the working process, or by a slight constructive subadjustment. At the same time, their work processes must be perfect, and overall dimensions are minimal.

With respect to, for example, robotic manipulators, this device is also relevant for providing movement, since in this case the pneumatic actuator is characterized by high speed, small dimensions and weight, its constituent parts, and a free working medium - air.

Thus, at present, there is a need for a small-sized, but with the required quality indicators of a rotary volumetric machine for working on gases. The most appropriate option for its creation is to use a rotary hydro-pneumatic machine as its basis.

The aim of the invention is to increase the efficiency of a rotary volumetric machine when working on gases by increasing the volumetric efficiency.

To achieve this goal, in the well-known rotary hydro-pneumatic machine, comprising a housing with end caps, in the bores of which are placed the driving and driven working gears forming an axial gear, each working gear of which consists of a hollow hub and a disk with a crown placed on its periphery , with teeth consisting of separate sections with an asymmetric profile having front and rear surfaces, channels for supplying and discharging the working medium are formed in the housing, working gears are mounted on the hollow axes at an angle m, ensuring the overlapping of their tooth crowns on the entire circumference, each hollow axis is fixed on one side to the end cover of the housing, and on the other hand is connected to a part of the housing located between the central parts of the working gears, the disk of each working gear is equipped with at least two with shells covering the crown of teeth from the outer and inner sides, each section of the teeth is equipped with permanent magnets, the drive drive gear wheel is equipped with a gear transmission with the output of the shaft from the inner space of the housing through the seal, the through holes of the hollow axes are channels for supplying and discharging the working medium.

Wherein:

- the housing can be formed directly from the end caps, each of which has a meridional connector along the plane of the axes of rotation of the working gears;

- each of the shells of each working gear can be made in the form of a part of a hollow torus, forming in the cross section of the greatest overlap of the teeth either a closed ring, or a ring with one, or a ring with two windows;

- the surface of the shells can be made spherical with radii drawn from the center coinciding with the point of intersection of the axes of the working gears of the axial gear:

- - the surface of the shells of each of the working gears can have equal radii of the same name with an arbitrary ratio of the widths, provided the total width of the shells does not exceed the width of the ring gear;

- - the surfaces of the shells of the working gears can be mated along the entire width of the crown with a minimum radial clearance between the shells of the same name, both from the outer and the inside of the crowns, and the smaller shell of the outer pair and the larger shell of the inner pair have each section of its teeth cuts under the tooth section of another working gear;

- - one of the shells may partially cover the ring gear, and the other covers the ring gear over the entire width with a quarter sampling from the side of the ring for placing the first with a minimum radial clearance and the formation of a sealing labyrinth;

- - each of the shells limiting the gear ring can be made on one of the working gears with full or partial coverage of both crowns in the zone of minimum tooth reduction and penetration into the housing along a spherical slot with minimal radial clearances in the zone of maximum tooth reduction:

- - - on the periphery, for example, of the driving working gear, on its rear end a spherical shell may be mounted, mating with the inner surface of the shell of the driven working gear;

- - - at the rear end of the driving working gear, at radii smaller than the peripheral one or more concentric cylindrical shells that are included in the sliding interface with grooves in the housing can be installed;

- - - the shell on the inside of the crown can be made a separate part common to both working gears in the form of a spherical ring movably mating with the crowns, mounted with the possibility of rotation in the inclined groove of the housing located between the central parts of the working gears, and the formation of a zone free from overlapping them with one of the crowns in the area of maximum tooth reduction;

- - - the middle part of the housing located between the central parts of the working gears can be made either as a separate floating sphere, or a sphere belonging to one of the working gears;

- - the ends of the mating shells (both spherical and torus) can have mating protrusions and depressions, passing on the ledges of the body under these shells, forming a sealing labyrinth;

- the gear drive can be made in the form of a cylindrical gear, or a bevel gear, or a planetary gear:

- - a cylindrical gear can be connected on the largest radius of the working gear, or on its hollow hub;

- - the planetary gear can be performed with the carrier stopped, or with the sun gear stopped, or with a mechanism for changing its structure:

- - - a mechanism for changing the structure of a planetary gear may

be made in the form of electromagnetic couplings, one of which connects the housing to the carrier, and the other the hollow axis of the pinion gear with the sun gear:

- - - - the electromagnetic coupling connecting the hollow axis of the pinion gear to the sun gear can be made in the form of an annular cavity on the inside of the sun gear, with radial partitions installed in this cavity and filled with ferromagnetic powder or ferromagnetic fluid, and hollow on the inside the axis on the part of its passage section within the annular cavity installed solenoid with the ability to connect to a source of electric current;

- - - - the electromagnetic coupling connecting the carrier to the body can be made in the form of an annular cavity on the outer side of the carrier, with radial partitions installed in this cavity and filled with ferromagnetic powder or ferromagnetic fluid, and on the outside of the body within this ring cavity a solenoid is installed with the ability to connect to an electric current source;

- the gear can be placed on the outside of the housing and connected to the hollow hub of the working gear;

- when using a rotary volumetric machine as a rotary internal combustion engine, the central part of its body in the zone of maximum divergence of teeth is equipped with a nozzle to which a fuel pipe connected to the fuel tank is connected via a high pressure pump to one of two groups of nozzles on the peripheral part of the same zone a compressor is connected, and ignition devices are placed in the zone of maximum convergence of the teeth;

- - the ignition device can be made in the form of magnets placed in the end caps of the housing in the zone of maximum convergence of the teeth, and in each interdental interval of the disk of the working gear there are inductors with the ends of the conductor in its interdental space, with a gap between them;

- - - end caps, case, working gears or their separate parts can be made either of metals, or of polymers, or of ceramics, or of optically transparent material.

The proposed design measures provide the following advantages to the device.

Installation of working bevel gears at an angle

Where:

In - the width of the crown in the meridional section of the working gear;

D is the largest diameter of the working gear,

providing overlapping of their tooth crowns (Fig. 2, a shaded triangle), makes it possible to increase the number of pairs of teeth participating simultaneously in the working process, and this in turn:

- eliminates the presence of non-functional parasitic volumes, reduces the size and weight of the hydropneumatic machine;

- reduces volumetric leaks from one interdental compartment to another, since the pressure drop across the device is distributed over several stages consisting of pairs of teeth, which is very important for a pneumatic machine, since the viscosity of the gases used as a working medium is significantly lower than that of liquids and their penetration even through narrow slots is much higher;

- makes the dynamic qualities of the engagement process more favorable, firstly, due to the fact that a decrease in the angle θ due to a change in geometry provides a smoother compression of the liquid, especially at an increased rotational speed, which, according to the theory of attached masses, reduces hydraulic losses;

Secondly, in this case, the impact of one tooth on the other due to their own vibrations when entering the mesh is excluded (since in this case it does not enter), which reduces their wear and tear, and also eliminates the transmission of this blow to the body of each worker gears on engaging other teeth. Therefore, this measure also prevents periodic overflow of the working medium between the teeth repelled by trembling in each pair of mating.

These advantages provide a solution to the technical problem of expanding the arsenal of technical means that use gaseous products as a working fluid, that is, such rotary volumetric machines that operate at high compression ratios.

Reducing the camber angle θ of the working gears also eliminates the jumper to the housing element between the central parts of the working gears in the form of an axial washer and all the negative factors associated with it:

- fluctuations of the axial washer during the working process;

- its wear from collisions with oscillating teeth of the working gears;

- wear of the teeth themselves on the axial washer and an increase in the clearance of the washer - a moving tooth;

- increased volumetric losses through an increased gap due to the above reasons, as well as due to its variable value from oscillations of the axial washer;

- the difficulties of laying in the washer of the inlet and outlet communications;

However, this part of the housing itself, located between the central parts of the working gears, cannot be positioned and held in the set position in the form of an axial washer - fixing and fixing elements are necessary. It is advisable to use hollow axes as such elements on which working gears (hollow hubs) are installed.

To this end, in the proposed technical solution "each hollow axis is fixed on one side to the housing cover, and on the other hand is connected to a part of the housing (axial washer) located between the central parts of the working gears." In this case, the moment of inertia of the cross section of the tubular axis is significantly higher than that of the cantilever support of the axial washer of the prototype, therefore, the rigidity is also higher. Two supports in the form of such hollow axes form a spatial openwork design, the rigidity and strength of which is even higher, therefore, less flexibility, and hence the amplitude of the micromovement of the axial washer during vibration and its wear (Fig. 3).

This design of the Central part of the body reduces the dimensions of the rotary volumetric machine in the axial direction and thereby provides high specific indicators (in relation to weight and size) of its working process.

It is advisable to use the through holes of the hollow axes as channels for supplying and discharging the working medium. The cross sections of such channels are sufficient for this role. In the part of the housing between the central parts of the working gears, these channels continue to the required angular value for introducing the working medium into the interdental system of working gears.

The supply of each section of the teeth with permanent magnets, firstly, provides the necessary compression of their mating facial profiled surfaces, which ensures the tightness of the interdental spaces in the circumferential direction. Secondly, the magnets hold the ferromagnetic powder in the gaps between the sections of the applied magneto-liquid seal. Thirdly, when the device operates as an internal combustion engine (Fig. 16, Fig. 17), the stationary magnets in the housing and the rotating magnets of the tooth sections during interaction will create an uneven, unsteady magnetic field with high intensity gradients. This circumstance will contribute to the induction of increased EMF in the inductors (ignition).

Supplementing the disk of each working gear with at least two shells covering the crown of teeth from the outer and inner sides replaces the installation of sealing devices at the indicated places. In this case, the working medium is fenced off by an impermeable wall from overflow in non-functional directions, which is much simpler and more reliable than installing seals of various designs (Fig. 3 ... Fig. 7, Fig. 10; Fig. 11; Fig. 13; Fig. 14; Fig. 15; Fig. 16).

Moreover, the gap between the tops of the teeth and the housing has been eliminated, since the cantilever jumper holding the axial washer (part of the housing between the central parts of the operating gears) is absent due to the small angle θ.

The tightness of the mating teeth of the working bevel gears due to their sectional performance in combination with the use of magneto-liquid compositions, as well as due to the installation of sealing shells, reaches the required level for the operation of the device as rotary volumetric compressor-driven machines.

The housing in the form of two end caps, each of which has a meridional connector, makes it easier to assemble the product, since installation in this case can be carried out from each of six directions (Fig. 3 ... Fig. 7, Fig. 10; Fig. 11; Fig. 13; Fig. 14; Fig. 15).

At the same time, shells can have various designs:

- the implementation of the interdental canals in the meridional section in the form of a circle (Fig. 3), otherwise, the channels themselves in the form of tori, makes it possible, in comparison with the embodiment of the tooth profile in the form of a polygon, to more carefully seal each tooth element from the differential pressure in the circumferential direction, then there is one interdental space to separate from another. To do this, on separate sections of the tooth should wear piston rings from the pistons of the internal combustion engine of the appropriate size, which is made in one of the design options of the prototype.

However, the weak point of such a design of a rotary volumetric pneumatic machine remains the possibility of overflow of the working medium into the sinuses between the rotating disk of the working gear and the stationary case. Through these gaps (moving wall - fixed surface), the overflow of the working medium from one interdental volume to another is possible, causing volumetric losses and a decrease in the efficiency of the working process, especially on gaseous working media.

The use of labyrinth seals in the form of a circumferential collar in a concentric groove, which is done in the prototype, does not fully solve this problem even for liquid working environments. The use of contact seals entails the need to supplement them with a lubrication and cooling system, which significantly complicates the design, increases its cost, and reduces reliability. A more promising solution to this problem is the use of magneto-liquid seals, however, their presence, their maintenance will also lead to the complication and cost of the device.

The simplest and most appropriate solution is, as noted above, the addition of the disk of each working gear, both on the outer side of the ring gear, and with internal additional walls in the form of shells that enclose the interdental space from the sinuses.

The use of shells in the form of a part of the torus allows for complete sealing of the cross section in the region of maximum tooth alignment, especially in combination with piston rings and when using labyrinth mating at the joints. On the remaining part of the circumference of the ring gear, especially in the region of the minimum tooth alignment, these shells cover only a part of the contour of each gear working gear. In this case, the achievement of the necessary tightness will be facilitated by careful sealing of the mating of the annular end of the shell — the annular ledge of the body under this shell, for example, the coupling of the protrusion with the cavity providing the sealing maze (Fig. 3). The windows between the shells are used for placement in the case within these windows of the inlet or outlet channels.

The execution of the surfaces of the shells spherical with equal radii of the same name, drawn from the center coinciding with the point of intersection of the axes of the working gears of the axial gear, at which they are mated by ring ends and can be made with an arbitrary ratio of widths, provided the total width of the shells does not exceed the joint width of the gear rims in the zone of their maximum alignment (Fig. 4, Fig. 5, Fig. 6) ensures that they completely overlap the tooth crowns, as well as in the above case, only in the maximum th coupling teeth, the rest - the majority of the circumference of their ends are in contact with the shoulder of the housing. In this case, also the end parts of the joints, including with the body, it is advisable to perform in the form of mating protrusions and depressions forming a maze (see paragraph 12 of the claims).

To ensure the possibility of supplying and draining the working medium into the interdental spaces in the zone of maximum tooth alignment, the total width of the shells is smaller than the joint width of the gear rims in this zone by the width of the communication channels (Fig. 5).

For the convenience of placing the channels of supply and removal of the shell, the working gears are not the same, but so that their total width (together with the width of the channels) does not exceed the joint width of the gear rims in the zone of maximum tooth alignment (Fig. 6).

Such a shell design, similar to the above case, only partially blocks the working volume of the device from the space of radial gaps on the periphery, however, it seals it well from the sinuses behind the rotating disks and partially from the overflow into the end gap at a small radius of the ring gear.

The peculiarity of the spherical shell allows the meridional contour of the tooth — the body — to obtain a uniform and minimal clearance over the entire mating surface, thereby eliminating the problem points of the above construction (and prototype construction) at the intersection of the tooth contours (Fig. 3, points M, N). At these points there is a point gap, one of the walls of which (between the mating elements of the teeth) has an infinitely small thickness in the form of an edge.

- - when pairing the surfaces of the shells of the working gears along the entire width of the crown with a minimum radial clearance of the shells of the same name between them (Fig. 7), to prevent sticking of the shell and teeth it is necessary that the shell of the outer pair is smaller in diameter and larger in diameter of the inner pair had behind their teeth cuts under the teeth of another working gear (Fig. 9). The design under consideration has greater tightness in relation to the previous one, which eliminates the volumetric losses of each interdental volume from one direction, enclosed by a continuous shell, and significantly reduces them from the remaining directions.

Full sealing in this case is absent due to the presence of zones g (Fig. 9), within the contours of which the space of the movable interdental canal is in contact with the fixed housing, and therefore with the radial clearance between the working gear and the housing. In the gap, volumetric losses spread in all directions and thereby reduce the efficiency of the device.

- - the execution of one of the shells of the same name covering the ring gear partially, and the other covering the ring gear over the entire width with a quarter sampling from the side of the ring for placing the first with a minimum radial clearance and the formation of a sealing labyrinth (Fig. 10) is a hybrid of the above design options. Such a constructive variant of sealing the working space to a greater extent than the butt shape of the shells seals the working space, however, it does not completely exclude the overflow of the working medium between the body and the short shell, as well as between the body and part of the crown not covered by this shell. This option is more complicated and more expensive than butt joints (Fig. 4, Fig. 5, Fig. 6), but it is simpler and cheaper than the radial conjugation of the shells with windows in one of the teeth of the other - the working gear engaged with it (Fig. 7).

- - the implementation of large and small shells bounding the ring gear on one of the working gears with full or partial coverage of both crowns in the zone of minimum tooth reduction and penetration into the housing along a spherical slot with minimal radial clearances in the zone of maximum tooth reduction makes it possible, as completely to isolate the working space from the housing (both from the side of the inner radius of the crown and from the outside), and to ensure that part of the housing communicates with the working space, for example, for supplying communications ( Fig. 11, when performing a small shell smaller width of the crown).

In this case, during the transition of the teeth, as the working gear rotates, from the position of minimum reduction to the position of their full alignment, each tooth of the working gear not equipped with a shell, or its elements makes a small, equal to the width of the crown, axial movement along the shell of the second working gear . The speed of this movement is much lower than the peripheral speed of rotation of the teeth, approximately π × D / b times. This feature allows you to use either a reliable seal (contact (Fig. 12), magneto-fluid, etc.) between the interdental channels, that is, in the gaps between the tooth or its elements and the shell of the second working gear, or grooves on the inside of the shells for widened teeth or their elements.

For better sealing of the sinuses of the working gear, which does not have shells in this embodiment, it is also equipped with a spherical shell on the back of the gear rim, mating with the inner surface of the shell covering the rim. Between the shells, spring rings similar to piston rings in traditional ICEs or rubber flagella in grooves can be installed (Fig. 13). To enable assembly-disassembly of the device, its housing can be made integral, consisting of separate fragments along the line k h (Fig. 11).

In order to achieve additional, more reliable sealing of the sinuses of the working gear, which does not have a peripheral shell device in the structure under consideration, it is advisable to install one or several cylindrical shells included in the sliding interface with the housing grooves at smaller radii of its rear end (Fig. 11).

However, the design of the device with the supply of the working medium only in the region of the maximum divergence of the teeth (Fig. 14, Fig. 11, provided the shells are shorter than the crown width) is functional and useful only in a narrow range of practical options, for example, in the form of a rotary ICE, and then using only a self-igniting pressure mixture, or with a non-contact ignition method. This limitation is caused by the fact that rotating spherical shells prevent access through the channels in the central part of the body to the working interdental space in the zone of maximum tooth reduction, since in order to provide access to it, for example, the inner shell should be made excessively narrow. But this event will expose a considerable part of the working space in the maximum breeding zone from shielding by this shell, and the considered sealing scheme of the working space may lose all its advantages.

To reduce the openness of the working space from the shell in the zone of maximum tooth breeding while ensuring the possibility of creating a window in the zone of maximum tooth reduction will allow the shell on the inside of the crown to be a separate part common to both working gears, in the form of a spherical ring movably mating with the crowns mounted for rotation in an inclined groove (along the lines q and p of Fig. 13) of the central part of the housing located between the working gears.

With such a design of the small shell, it is an intermediate part between the fixed body and the rotating gear rims, therefore, with a more thorough sealing of the gap (Fig. 12), the inner part of the gear rim - the small shell will get the greatest mobility between the central part of the housing - the inner surface of the small shell.

This circumstance will determine the main movement of the shell along the groove (between the broken lines q and p of Fig. 13) with slight slippage in the circumferential direction relative to the teeth of the crown and axial mutual displacement less than π * D / h of the circumferential movement while providing access to the letting-off or igniting communications into the zone of maximum tooth reduction (maximum compression or deep vacuum).

The ultimate stage of development of this element with such a spherical shape of the small shell is either a moving floating sphere that is not fixed on the hollow axes (Fig. 14), or a sphere belonging to one of the working gears (Fig. 15).

The supply of the ends, as well as the mating ledges of the body, in which the ends of the shells (both spherical and torus) are located, with mating protrusions and depressions, as mentioned above, also creates additional labyrinth resistance to the possible overflow of the working medium and increases the tightness of the interdental space (Fig. 3).

Screening the working space of a rotary volumetric machine by installing various types of shells is an effective type of sealing, which makes it possible to increase the compression qualities of the rotary volumetric machine and thereby reduce its weight and size characteristics and improve the quality of the workflow, which ultimately suggests the emergence of another promising device in gas mashim arsenal.

Each of the above types of spherical shells can be used in various combinations for internal and external fencing of gear rims, taking into account the purpose of the rotary volumetric machine, types and locations of communication channels.

It should also be noted that in the proposed design of a rotary volumetric machine, the exclusion of a jumper supported by a part of the housing located between the ring gears implies increased requirements for the hollow axes that replace it, in particular in terms of the accuracy of their positioning, the reliability of their fastening, and their long stiffness.

The specified set of requirements for the device causes the rejection of direct shaft output from the housing for direct connection with the coupling and then either with the engine or with the working body. In this case, instead of the output shaft element, the following gears can be used:

- a cylindrical external gearing (Fig. 3), located in the axils of one of the working gears, depending on the ratio of diameters, can be either upward or downward in both directions of the export of movement (compressor, air motor) with a small number of reductions. Such a transmission in itself is simple in design, but in conjunction with working gears and their bearings, it degenerates into a rather serious mechanism located in the body cavity. This circumstance reduces the reliability of the mechanism as a whole and makes it difficult to carry out repair work in case of failures, due to the need to disassemble the entire device.

- the removal of the transmission mechanism from the inner space simplifies the design (Fig. 11, Fig. 13) provides easier access to the gear pair, reduces the amount of internal space by eliminating the volume occupied by the transmission. In this case, parasitic movements of the working environment are reduced.

- a cylindrical internal gearing located in the sinus of one of the working gears (Fig. 4) allows the working gears and the drive shaft to rotate in the same circumferential direction. Another feature of it is that this type of engagement causes a greater gear ratio compared to the previous design option with comparable machine dimensions. The third feature is the need to place it only inside the housing with the output of the shaft into the outer space through the seal. This feature provides less convenience when carrying out repair work.

- the bevel gear used in the rotary volumetric machine (Fig. 5), causes the engagement of the rear gear ring of one of the working gears with a high-speed gear gear. The transmission scheme under consideration is characterized by a relatively high gear ratio, since dividing diameters in this case can differ by 5-10 times, therefore, it is advisable to use it for a device operating in compressor mode.

Another feature of this transmission is the ability to rotate the entire device during settings and installation relative to the axis of the drive shaft.

- the planetary gear with the carrier stopped, also does not allow to reduce the output shaft rotation speed with respect to the working gear and recommends using the device either in the compressor mode with a high-speed engine (Fig. 6) or with a high-speed electric generator in the air or steam turbine mode.

- a planetary gear with the sun gear stopped (Fig. 7) causes a run-in of the satellites along it, and due to this a decrease in the angular velocity of the carrier in relation to the epicyclic gear. This type of transmission is less fast than when the carrier is stopped (Fig. 6) and therefore requires a low-speed engine for the compressor mode, as well as a low-speed electric generator in the air-steam turbine mode to generate electricity.

- a planetary gear with a variable structure due to, for example, the alternative inclusion of electromagnetic couplings allows you to transfer the device to each of the above modes of its operation (Fig. 10, Fig. 16). In this case, the mechanism of changing the structure of the planetary gear can be made in the form of electromagnetic couplings, one of which connects the housing to the carrier, and the other the hollow axis of the pinion gear with the sun gear:

- - the electromagnetic coupling connecting the carrier to the body can be made in the form of an annular cavity on the outside of the carrier, with radial partitions installed in this cavity and filled with ferromagnetic powder or ferromagnetic fluid, and a solenoid is installed on the outside of the body within this ring cavity with the ability to connect to an electric current source;

Therefore, if you want to stop the carrier, the power is supplied to an external coil, which creates a magnetic field inside the space it covers. If the magnetic field is static, then it acts on the ferro-powder located in the torus pocket, causing its immobility, which also inhibits the carrier itself. It is advisable to use ferro-powder in an oil medium, which makes it possible to obtain not only two discrete “stop” modes - “rotation”, but also intermediate modes, due to changes in the magnetic field strength, as well as off-band modes, due to the creation of a vortex magnetic field by a coil in each of the district directions.

- - the electromagnetic coupling connecting the hollow axis of the pinion gear with the sun gear can be made in the form of an annular cavity on the inside of the sun gear, with radial baffles installed in this cavity and filled with ferromagnetic powder or ferromagnetic fluid, and on the inside of the hollow axis a solenoid is installed within the annular cavity with the ability to connect to an electric current source;

Thus, it is possible to control the behavior of the sun gear using a torus coil inside its hollow axis and the ferromagnetic fluid of the second of the pockets in the hub of the sun gear.

To coordinate the movements of the gears on the output shaft, one of which is connected to the carrier, and the other to the sun gear, they are installed on overrunning, or on electromagnetic couplings.

The combination of control functions on the carrier and the sun gear (both in the mode of simple stop and movement in each of the two circumferential directions) allows you to work in a wide range of gear ratios and use such a device, for example, to create a motor wheel.

Moreover, the proposed device can operate, for example, as a compressor, only from the power supplied to the solenoids, that is, in the form of a monoblock structure without a direct drive from a separate engine to the input shaft.

The placement of gears from the outside of the housing of the proposed device by connecting them to the hollow shaft of the working gear (Fig. 15) allows you to develop a variety of created designs and find among them the most rational for the technological task to use a rotary volumetric machine.

The addition of the rotary volumetric machine ignition device in the zone of maximum convergence of the teeth of the working gears, a fuel tank, a pump, a fuel pipe of one of the nozzles in the zone of maximum divergence of the teeth, and the other - a compressor (Fig. 16, Fig. 17) allows you to use the proposed device as a rotary engine internal combustion engine (ICE).

In this case, the compressor ventilates the interdental spaces from the combustion products from previous cycles and fills them under excess pressure with clean air. The fuel pump delivers flammable liquid (gasoline, ether, gas oil, diesel fuel, etc.) from the fuel tank through the fuel line into the interdental spaces filled with air.

At the same time, spraying it by volume, compression due to the rotation of the working gears produces a fuel charge. At the time of the highest degree of compaction (in the zone of maximum convergence of the teeth of the working gears), the ignition device ignites the fuel charge, accompanied by an increase in volume due to the production of combustion products and an increase in temperature in each interdental volume. As a result, the pressure rises and a circumferential force appears on each working gear, exceeding the circumferential force from the need to compress the fuel charge.

The difference in moments from the need to compress the fuel charge and the moment from the combustion of this charge makes it possible to connect to the device any payload (within the generated power), that is, use it as a rotary ICE.

In this case, the compression part of the device operates as a compressor, and its expanding part (as it rotates) in the form of a pneumatic motor.

In order to increase the efficiency In this case, the rotary volumetric machine in the internal combustion engine mode due to the preservation of high tightness of the interdental volumes, the ignition device can be made non-contact, in the form of a coil in each interdental volume rotating together with the working gear between the magnets mounted on the housing.

In addition to the stationary magnets in the housing, in addition, there are also rotating magnets of the tooth sections, which, when interacting, will create an uneven, unsteady magnetic field with high tension gradients

Therefore, the rotation of each coil in an uneven and unsteady magnetic field from the magnets fixed on the body and movable in the tooth sections creates an EMF in each turn-loop of the coil, which is multiplied by the number of turns and grows with increasing speed of rotation of the working gears. At the output ends of each coil installed with the required gap between each other, a potential difference is created sufficient for the occurrence of a spark discharge. The spark ignites the fuel charge and thereby first starts the process, and then supports it, since the described cycle occurs with each interdental volume. This sequence of strokes ensures continuous rotation of the working gears.

At the same time, to obtain the required magnetic field strength, the elements of the device or their parts can be made of non-metals (polymers, ceramics, glass, etc.), which increases the magnetic permeability of the area of functioning of the magnets and thereby the stability of the working process.

Thus, the totality of the claimed features allows you to more significantly expand the arsenal of technical equipment based on a rotary volumetric machine, even to the point of using it as an internal combustion engine.

The invention is illustrated by the following drawings:

FIG. 1. Problem areas of the design of the prototype for the tightness of the interdental working volumes.

FIG. 2. The design scheme of the condition for pairing all the teeth of the working gears.

FIG. 3. A constructive embodiment of the shells of the working gears in the form of a torus, a drive in the form of an internal cylindrical gear of an external gearing and a housing formed by covers with a meridional connector.

FIG. 4. A variant of identical execution of spherical shells end-to-end at working gears, a drive in the form of an internal cylindrical gear of internal gearing and a housing formed by covers with a meridional connector.

FIG. 5. A variant of the same design of spherical shells with windows and channels in the housing, as well as a drive in the form of a tapered mesh and a housing formed by covers with a meridional connector.

FIG. 6. A variant of unequal execution of spherical shells end-to-end at working gears, a drive in the form of an internal planetary gear with a carrier stopped, and a housing formed by covers with a meridional connector.

FIG. 7. An embodiment of spherical shells mating with a minimum radial clearance, an actuator in the form of an internal planetary gear with a stopped sun gear and a housing formed by covers with a meridional connector.

FIG. 8. A radial section of an embodiment of spherical shells mating with a minimum radial clearance. Section AA Fig. 7.

FIG. 9. A cylindrical section of an embodiment of spherical shells mating with a minimum radial clearance. Section BB FIG. 8.

FIG. 10. An embodiment of spherical shells, one of which partially covers the toothed ring, and the other covers the toothed ring along the entire width with a quarter selection from the side of the ring for placing the first with a minimum radial clearance and the formation of a sealing labyrinth, as well as a planetary gear drive with variable structure from electromagnetic couplings and a housing formed by covers with a meridional connector.

FIG. 11. An embodiment of spherical shells with full coverage of the crowns of both working gears in the zone of minimum tooth reduction and penetration into the housing along a spherical slot with a minimum radial clearance in the zone of maximum tooth reduction, as well as a drive in the form of an external cylindrical gear of an external gearing and a housing formed by covers with meridional connector.

FIG. 12. Radial cut along the teeth of the working gear. Section BB of FIG. eleven.

FIG. 13. An embodiment of the inner spherical shell common for both working gears and located in the peripheral channel of the middle part of the housing located between the working gears, as well as a drive in the form of an external cylindrical gear of an external gearing and a housing formed by covers with a meridional connector.

FIG. 14. An embodiment of the inner central part of the body in the form of a floating sphere.

FIG. 15. Case design without a separate inner central part.

FIG. 16. A design variant of a rotary internal combustion engine (ICE) based on a rotary volumetric machine with a body and two covers.

FIG. 17. Scheme of the nature of the distribution of ticks along the length of the working volume of the rotary engine. Section GG of FIG. 16.

The rotary volumetric machine (Fig. 16) contains a housing 1 with end caps 2 and 3, in the bores 4, 5 of which are placed the driving 6 and driven 7 working gears forming an axial gear, each working gear of which consists of a hollow hub 8, 9 and a disk 10, 11 with teeth 14 located on its periphery in the form of crowns 12, 13, consisting of separate sections 15 (Fig. 8, Fig. 9, Fig. 18) with an asymmetric profile having a front 16 and a back 17 surface. In the housing 1, channels for supplying and discharging 18, 19 of the working medium are formed, working gears 6, 7 are mounted on the hollow axes 20, 21 at an angle θ (Fig. 2), which ensures overlapping of their crowns 12, 13 of the teeth 14 over the entire circumference. Each hollow axis 20, 21 is fixed on one side to the end cap 2 or 3 of the housing 1 (Fig. 16), and on the other hand is connected to a part 22 of the housing 1 (axial washer) located between the central parts of the working gears 6, 7. Disk 10 of the driving gear 6 is provided with at least two shells 23, 24, covering the crown 12 of the teeth 14 from the outer and inner sides. The disk 11 of the driven working gear 7 is also provided with at least two shells 25, 26, covering the crown 13 of the teeth 14 from the outer and inner sides. The disk 10 of the driving working gear 6 is equipped with a gear 27 with the output of the shaft 28 from the inner space of the end cover 3 through the seal 29. The through holes 30, 31 of the hollow axes 20, 21 are the channels for supplying the outlet of the working medium. The cross sections of such channels 30, 31 are sufficient for this role. In the axial washer 22, these channels continue to the required angular value for introducing the working medium into the interdental system of working gears 6, 7.

Wherein:

- the device body can be formed directly from the end caps themselves 34, 35, each of which has a meridional connector along the plane of the axes of rotation of the working gears (Fig. 3, Fig. 4, Fig. 5, Fig. 6, Fig. 7, Fig. 10, Fig. 11, Fig. 13, Fig. 14, Fig. 15);

- each of the shells 23, 24, 25, 26 of the working gears 6, 7 can be made in the form of a part of a hollow torus, forming in the cross section of the largest tooth overlap either a closed ring (Fig. 3), or a ring with one, or a ring with two windows;

- the surfaces of the shells 23, 24, 25, 26 can be made spherical with radii drawn from the center coinciding with the point 0 of intersection of the axes of the working gears 6, 7 of the axial gear (Fig. 4, Fig. 5, Fig. 6, Fig. 7 , Fig. 10, Fig. 11, Fig. 13, Fig. 14, Fig. 15, Fig. 16);

Moreover:

- - the surfaces of the shells 23, 24, 25, 26 of each of the working gears 6, 7 can have equal radii of the same name and are made with an arbitrary ratio of the widths, provided the total width of the shells 23, 24, 25, 26 does not exceed the width of each of the ring gears 12 , 13;

- - the surfaces of the shells in pairs 23-25, 24-26 of the working gears 6, 7 are mated across the entire width of the crown 12 or 13 with a minimum radial clearance, both the outer 23-25 and the inner 24-26 shells are interconnected, and the smaller the diameter of the shell 25 of the outer pair, and the larger in diameter 26 of the inner pair, have behind their teeth 15 slots for the teeth of another working gear (Fig. 7, Fig. 8, Fig. 9);

- - one of the shells of the same name 23 (26) partially covers the ring gear 12, and the other 25 (24) covers the ring gear over the entire width with a quarter selection from the side of the ring for placing the first with a minimum radial clearance and a sealing labyrinth (Fig. 10, Fig . 16);

- - each of the spherical shells 36, 37, limiting the ring gear, is made on one of the working gears (7) with full or partial coverage of both crowns 12, 13 in the zone of minimal tooth reduction and penetration into the body of the cover 35 along the spherical slot 38 and 39 with minimal radial clearances in the zone of maximum tooth alignment (Fig. 11, Fig. 13, Fig. 14, Fig. 15):

- - - on the periphery, for example, of the driving working gear 6, a spherical shell 40 is mounted on its rear end, mating with the inner surface of the shell 36 of the driven working gear (Fig. 11, Fig. 13, Fig. 14, Fig. 15);

- - - between the shells 36 and 40, spring rings 41 are installed, similar to the piston of traditional ICEs, or rubber flagella 42 in the grooves (Fig. 11, Fig. 13, Fig. 14, Fig. 15);

- - - at the rear end of the driving working gear, at radii smaller than the peripheral one or more concentric cylindrical shells 43 are inserted, which are included in the sliding interface with grooves 44 in the case of the end cover 3 (Fig. 11);

- - - the shell on the inside of the crown is made in the form of a separate part 45 common to both working gears in the form of a spherical ring movably mating with the crowns, mounted for rotation in an inclined groove 46 of the housing part 22 located between the central parts of the working gears 6, 7, and the formation of zone 47, free from overlapping the crown in the direction of the maximum information of the teeth (Fig. 13);

- - - the middle part 22 of the housing located between the central

parts of the working gears 6, 7, made in the form of a separate floating sphere 48, or a sphere belonging to one of the working gears 6 or 7 (Fig. 14, Fig. 15);

- - the ends of the mating shells (both spherical and torus) have mating protrusions 49 and depressions 50, passing to the ledges of the housing under these shells, forming a sealing labyrinth (Fig. 3), and each section 15 of the tooth 14 can be equipped with a contact seal 51 ( Fig. 11, Fig. 12, Fig. 17);

In this case, the working gears 6, 7 are installed on the hollow axles 20, 21 through the bearings 52;

- the gear train can be made in the form of a cylindrical gear (Fig. 3, Fig. 4), or a bevel gear (Fig. 5), or a planetary gear (Fig. 6, Fig. 7, Fig. 10, Fig. 16):

- - a cylindrical gear can also be connected at the largest radius (Fig. 4) of the working gear 6, or on its hollow hub 8 can have the following versions:

- - - a cylindrical external gearing (Fig. 3), located in the axils of the driving gear 6, includes a ring gear 55 on the hollow hub 8 that engages with the gear 56 mounted on the output shaft 28. The shaft 28 is mounted in bearings 57 and sealed from the outer space by a seal 29;

- - - a cylindrical internal gearing (Fig. 4), located in the axils of the driving working gear 6, includes a ring gear 58 at the largest radius of the disk 10 forming an epicyclic gear and engaging with the gear 56 mounted also on the output shaft 28. Shaft 28 is installed in bearings 57 and sealed from the outer space by a seal 29 similar to the above case;

- - a cylindrical gear transmission can be placed on the outside of the end cover 3 (or 35) and connected to the hollow hub 8 of the working gear 6 (Fig. 11, Fig. 13, Fig. 14, Fig. 15). In this case, the hollow hub 8 of the driving working gear 6 is elongated, due to which the ring gear 55 is shifted from the sealed working space to a more distant distance than in previous versions. Owing to this constructive measure, the drive gear 56, together with the shaft 28, also moves away from the sealing zone. In this case, one end of the shaft 28 is fixed in the housing of the cover 35, and to ensure the necessary rigidity of holding the shaft, its second end is placed in an additional housing part of the earring 59, screwed onto the hollow axis 20 (Fig. 11). In the constructions of FIG. 14, FIG. 15, an additional mounting is provided for the earring to the cover body 35.

Design Options FIG. 13, FIG. 15 provide for the implementation of the reciprocal gear for the ring gear 55 in the node mated to the proposed device.

- - bevel gear (Fig. 5), also located in the axils of the driving working gear 6, includes a gear ring 60 at the largest radius of the disk 10 forming a bevel gear and engaged with the gear 61 mounted on the output shaft 62. The shaft 62 is installed in bearings 57 and sealed from the outside with a seal 29;

- - the planetary gear is made with the carrier stopped (Fig. 6), or with the sun gear stopped (Fig. 7), or with a mechanism for changing its structure (Fig. 10, Fig. 16):

- - - - the planetary gear with the carrier stopped (Fig. 6) in the rotary volumetric machine is located in the axils of the driving working gear 6 and contains an epicyclic crown 58 on the periphery of the rear of the driving working gear 6, freely rotating on the hollow axis 20, the sun gear 65, kinematically connected through a ring gear 66 with a gear wheel 67 fixed to the shaft 28. A satellite 68 is mounted on the same shaft 28 with the possibility of free rotation on it. Other satellites 68 are mounted on rotating axles 69. The axles 69 and the shaft 28 are mounted in bearings 70, the shaft 28 being protected from external contaminants by a seal 29 located in the cover 71. The cover body 35 performs the function of a stopped carrier;

- - - - the planetary gear with the sun gear stopped (Fig. 7) in the rotary volumetric machine includes the sun gear 65 proper, which is fixedly connected to the cover body 35 through the hollow shank 72, covering the concentrically hollow axis 20. The carrier of this structural embodiment of the transmission is made in the form cage 73, rotatably mounted on the shank 72. The carrier has a gear ring 74 and axles 69 with satellites 68. The axles 69 in the holes of the carrier carrier 73 are mounted through bearings 70, and its gear ring 74 is connected to the gear 75, fixed oh on the shaft 28 having a seal 29. The gear 75 may be closed by a removable casing 76;

- - - - planetary gear with the possibility of changing its structure

(Fig. 10, Fig. 16) is a combination of the two above-described structural variants of planetary gears, converted into one using the mechanism of structural change. The mechanism of structural change allows you to get two different gear ratios (when the carrier is stopped and when the sun gear is stopped) in the presence of the same mechanical part. An additional condition for the implementation of this function is the installation of gears 67 and 75 on the output shaft 28 using overrunning (or electromagnetic) couplings 77, 78;

- - - the mechanism of changing the planetary gear structure is made in the form of electromagnetic couplings, one of which connects the cover body 3 to the carrier 73, and the other hollow axis 20 of the pinion gear 6 with the sun gear 65 (Fig. 10, Fig. 16).

When this ferromagnetic powder, or ferromagnetic fluid 80 is placed in the grooves 81, 82, made concentric with inductive coils 83, 84 and provided with partitions 85, 86.

Thus, the electromagnetic coupling connecting the hollow axis 20 of the pinion gear 6 with the sun gear 65 is made in the form of an annular cavity 82 on the inside of the sun gear 65, with radial baffles 85 installed in this cavity and filled with ferromagnetic powder or ferromagnetic fluid 80, and on the inner side of the hollow axis 20 within the annular cavity 82, a solenoid 84 is installed with the possibility of connecting to an electric current source;

The electromagnetic coupling connecting the carrier 73 with the body of the end cap 3 is made in the form of an annular cavity 81 on the outer side of the carrier, with radial partitions 86 installed in this cavity and filled with ferromagnetic powder or ferromagnetic fluid 80, and on the outside of the case within this ring cavity installed solenoid 83 with the ability to connect to a source of electric current;

The above design can be the basis for the creation and development of a rotary internal combustion engine (in this case, the principle of reversibility of volumetric rotary machines is implemented). To operate the device as an internal combustion engine, a pipe 87 connected to the fuel tank 88 and the throttle 89 through the high-pressure pump 90 is connected to the pipe 18 located in the central part of the housing and located in the zone of maximum divergence of the tooth crowns 12, 13 through the hole 31 of the hollow shaft 21. A compressor 91 is connected to one of the two nozzles 18 or 19 on the peripheral part of the same zone, and ignition devices are placed in the zone of maximum convergence of the teeth. The ignition device is made in the form of magnets 92, 93 located in the end caps 2, 3 of the housing 1 (or the housing of the caps 34, 35) in the zone of maximum convergence of the teeth (Fig. 17), magnets 94, located in the sections 15 of the teeth 14 of the working gears 6 , 7, and in each interdental interval of the disks 10, 11 of the working gears 6.7, inductors 95 are placed with the output of the ends of the conductor in each interdental space with a gap between them.

Lids 2, 3, housing 1, or housing of covers 34, 35, working gears 6, 7, or their separate parts are made either of metals, or of polymers, or of ceramics, or of optically transparent material.

The device operates as follows:

one). When executing shells 23, 24 and 25, 26 in the form of a part of the torus, forming a ring in the form of a circle in the section of the zone of maximum convergence of the teeth.

When the shaft 28 rotates, a gear 56 fixed on it rotates, which rotates the ring gear 55 mounted on the hollow hub 8 of the working gear 6. Each individual section 15 of the teeth 14 (Fig. 8, Fig. 9, Fig. 17) of the driving working gear 6 engages with the front surfaces 16 (Fig. 9) of the same sections 15 of the teeth 14 of the driven working gear 7 forming tight volumes in the circumferential direction between the teeth due to the contact of the front surfaces and duplication of the mating of the front surfaces 16 in each section 15 of the tooth 14 with constant compression from pic oyannyh magnets 94 arranged in the sections 15 of teeth 14 working gears 6, 7.

Due to the fact that in radial directions these volumes are partially covered by shells 23, 24, 25, 26 and housing 1 (Fig. 16) or covers 34, 35 (Fig. 3) with a minimum radial clearance mating with each section 15 of tooth 14 is provided complete tightness of interdental volumes.

On the diverging tooth section 14 in the interdental space as the working gears 6, 7 rotate, a vacuum pressure (vacuum) is created, due to which the working medium enters the interdental spaces from the source (storage, atmosphere) through channel 21 further 18 and then as the workers rotate gears 6 and 7 in a converging section, the working medium is crimped due to the fact that the cross section of the torus interdental space decreases from almost two areas of the circle to one in the zone of maximum tooth reduction 14. The degree of compression Attack in this case can be further adjusted by the thickness of the extreme sections 15 of the engaging groups of sections (see the description of the prototype).

Due to the acquired excess pressure, the elastic working medium is removed through the channel 19, placed with an offset from the point of greatest alignment of the teeth 14 (crowns 12, 13) of the working gears 6, 7.

In this case, the sectional execution of the teeth, the presence of the shells significantly increases the sealing of the interdental volumes, and to prevent overflow on the back of the shells in their annular ends there are labyrinths in the form of mating protrusions and depressions, which have a further continuation in the ledge of the body parts (covers 34, 35 )

2). When performing shells 23; 25; 24; 26 spherical (Fig. 4).

In this case, the rotation of the shaft 28 in the bearings 57 and the seal 29, the gear 56, rigidly mounted on the shaft 28, leads to rotation in the same direction of the epicyclic ring 58 located on the back of the working gear 6, therefore, the working gear 6 itself rotates. The teeth 14 of the working gear 6 through their sections 15 with the front surfaces 16 drive the working gear 7, acting on the same front surfaces 16 of the same sections 15 of the same teeth 14 of this driven working gear 7. In this case, the mating of the front surfaces 16 work sneeze gears 6 and 7, as well as their Poggi due to the interaction of permanent magnets 94 in the sections of the teeth provides a full and continuous contact rib section 15 on the front ruled mating surface 16 that provides a sealing interface. For a greater degree and reliability of sealing, the teeth 14 are divided into sections 15 - several sections more carefully seal the joint in the circumferential direction. Thus, the workflow is completely similar to the above case (Fig. 3), with the exception of replacing the external gear transmission with an internal one. The spherical shells of the case under consideration also provide sealing similarly to torus ones and can also be equipped with mating protrusions 49 and depressions 50 (Fig. 3).

The gaseous working medium can be entered into the device through one of the channels 18 in the peripheral part of the body part 35 (cover), or in the same way as above, sequentially through the channels 31, 18. The output after crimping is also made through the channels 19 and then the hole 30 axis 20.

It should also indicate the advantages of the options considered, consisting in the gradual compression of a portion of the gas in the interdental canal, captured in the area of maximum divergence of the teeth. Therefore, at each pair of teeth 14 of the working gears 6, 7, the pressure drop is minimal, therefore, the possible overflow through each pair is also minimal.

3). When the transmission is conical, and the shells are shorter (Fig. 5), the working process occurs similarly to the above cases - the shaft 62 in the bearings 27 and the seal 29 rotates the bevel gear 61 and it transfers the circumferential movement to the working gear 6, then through the teeth 14 of the working gear 7. Subsequent operation occurs in the same way as the above cases (Fig. 3, Fig. 4) except that the shell 23; 25; 24; 26 in this case are narrower and in the region of maximum convergence of the teeth 14 they (the shells) do not contact the labyrinth seals formed by the mating protrusion 49 and the cavity 50 (Fig. 3.) The contact of the mating surface at the end of each shell will be carried out only with ledges in the case details 34, 35, or in the housing 1 (Fig. 16). This fact may be the reason for even greater sealing of interdental volumes in radial directions.

In addition, in these gaps, it is possible to bring on the communication housing at the point of maximum convergence of the teeth (channels 18, 19 of Fig. 5).

The joint rotation of the working gears 6 and 7 in the region of the maximum divergence of the teeth fills the interdental volumes through the input channels (not shown in Fig. 5) with a working medium, then they are crimped as they rotate along the channels of the maximum teeth 14 through the channels 18 or 19 under pressure medium leaves the device.

four). When performing a planetary gear with the carrier stopped (Fig. 6), and a spherical shell on only one working gear (7), nothing fundamentally changes either. The shaft 28, mounted in bearings 70 and seal 29, rotates the gear 67. The gear 67 rotates the crown 66 of the hub of the sun gear 65. The sun gear 65, mounted on the hollow axis 20 acts on the satellites 68, mounted on the axes 69 and the continuation of the shaft 28 used in this section as an axis. In this case, the satellites 68 transmit rotation to the epicyclic ring 58 (in Fig. 4) of the working gear 6. The working gear 6, interacting with the sections 15 of the teeth 14 and with the same sections 15 of the teeth 14 of the driven working gear, 7 transmits rotation to it. The tightness of the engagement is ensured, both due to the sectional design of the teeth 14, and due to their preload from the interaction of the permanent magnets 94 integrated into these sections 15.

The joint rotation of the working gears 6 and 7 in the region of the maximum divergence of the teeth fills the interdental volumes through the input channels 19 with a working medium, then, as they rotate, they are crimped due to the mutual inclination of the axes of rotation and in the region of the maximum reduction of the teeth 14 through the channels 18, or through one of them under pressure, it is either discharged into the atmosphere (in the operating mode the pump vacuum), or supplied to the network (in the compressor operating mode).

The widths of the shells 24, 25 can be equal to the width of the ring gear 13, then the peripheral outlet holes must be made either before or after the point of maximum information of the teeth. If the width of the shells 24, 25 will be less than the width of the crown 13, then in the arrays of the body parts 22 and 35, you can place the outlet channels 18 (both central and peripheral) at the point of maximum tooth reduction.

5). The drive from the engine to the leading working gear in this case is also carried out through a transmission, in this case a planetary gear with the sun gear stopped.

When performing a planetary gear (Fig. 7) with the sun gear 65 stopped and shells along the entire width of the crown with a minimum radial clearance of the shells of the same name, when the smaller diameter shell 25 of the outer pair (Fig. 7) and large 26 (Fig. 8, Fig. .9) according to the diameter, the shell of the inner pair has behind its sections 15 teeth 14 slots under the section 15 of the teeth 14 of the other working gear 7. In this case, the gear ratio to the above types of gears changes and the degree of sealing of the interdental volumes increases.

In this device, when the shaft 28 is rotated, the gear 75 fixed on it rotates, which drives the ring gear 74 and the carrier 73 itself. The satellites 68 mounted on the carrier 73 are rotatable on the axles 69 installed in the bearings 70 and run around the gear ring stationary the sun gear 65 rotates in the same direction the crown 58 of the epicyclic gear and then the working gear 6 itself.

The rotation of the working gear 6, as well as the above cases, through the interaction of the sections 15 of the teeth 14 rotates the working gear 7, located at an angle 0 to the leading 6. The relative inclination of the axes of rotation of the working gears 6 and 7 causes a change in the distance between the disks 10, 11 in the axial direction with their joint rotation.

When the interdental volume is in the zone of maximum divergence of the teeth (Fig. 7), the working medium is supplied to it through the channel 31 of the hollow axis 21, then the channel 18. As the working gears 6 and 7 rotate, the height of the interdental volume in the axial direction decreases, and of course its volume. The elastic working medium is crimped, its pressure rises.

To prevent volumetric leaks, mating shells 23, 25 (Fig. 7), 24, 26 (Fig. 8) are provided in the design, which cover the interdental volumes in radial directions. In this case, there is a sealing of two mating shells 23, 25 with low relative mobility and intensively moving shells 24, 26 (Fig. 8) with a fixed body 1 (Fig. 17), or covers 34, 35 (Fig. 7). To prevent sticking of the sections 15 of the teeth 14 of the working gear 6 with the inner shells 25 (Fig. 7) and 26 (Fig. 8) of the working gear 7, cuts are made in front of the sections 15 of the teeth 14 (Fig. 8 and Fig. 9). These cuts to a small extent reduce the tightness due to zones g (Fig. 9) of the inactive junction of the mating shells.

In the zone of maximum compression of the interdental volumes, the working medium is displaced through the channel 19 and then the hole 30 of the hollow axis 20 into the atmosphere or pneumatic system. It should be noted that in FIG. 7, this type of pairing is shown only on the outer shells 23 and 24.

6). Performing planetary gears with the possibility of changing the structure, and one of the shells covering the gear ring partially and the other covering the gear ring along the entire width with a quarter selection from the crown side for placing the first one with a minimum radial clearance and the formation of a sealing labyrinth, allows you to change the speed of rotation of the working gears 6, 7, that is, to change the supply and pressure of the supercharger, moreover, to ensure a higher degree of tightness of the interdental space (Fig. 10).

In this case, two discrete options are possible, with the alternative inclusion of coils 83 and 84.

When the coil 83 is connected to a direct current source, the ferromagnetic powder 80 (or magnetorheological liquid) is held by the magnetic field and creates the structure of the delatant liquid, which keeps the ribs 86 of carrier 73 stationary. Further, the rotation of the shaft 28 of the freewheel clutch 77 rotates the gear 67, which in turn rotates the sun gear 65 through its gear ring 66. The sun gear 65 itself rotates the satellites 68 mounted on the stationary axes 69 of the stopped carrier 73 through bearings 70. The rotation of the satellites 68 is relatively motionless axes 69 and carrier 73 rotates the epicyclic ring 58 connected to the working gear 6, which rotates in the same direction.

Gear 75 in this case remains stationary, since it, like gear 67, is mounted on overrunning clutch 78 with the opposite direction of torque transmission.

With an alternative connection of the coil 84 to the direct current source, the ferromagnetic powder 80 of the magnetoreagic liquid is held by a magnetic field and also creates the structure of the delatant liquid, which keeps the ribs 85, and hence the sun gear stationary.

Further, the rotation of the shaft 28 (in the opposite direction relative to the above case) disables the freewheel clutch 77 and, through the other freewheel clutch 78, transmits the rotation to the gear 75 and then to the ring gear 74 of the carrier 73. In this case, the axles 69 move along the circumference together with the rotating carrier 73 forcing by rolling on the stationary sun gear 65, the satellites 68 rotate. As a result, the satellites 68 rotate the working gear 6 through the epicyclic rim 58, moreover, at a speed of the speed of the satellite’s own rotation at 68 and the speed of their rolling around the sun gear 65.

With a decrease in the supply voltage on the coils 85 and 84, the links held by each of them:

- or drove 73;

- or sun gear 65 (shank 72)

will partially slip in the direction of the reaction, which will lead to a change in the gear ratio in both cases.

When AC is applied, it creates a vortex magnetic field around the coils 83 or 84, which due to the ribs 85 or 86 and the magnetic material of the powder 80 will forcefully drive either the carrier 73 or the shank 72 of the sun gear 65 (which means the sun gear itself) in motion against the direction of the load.

This circumstance will increase the gear ratio of the gear planetary gear. In the last two cases, this planetary gear becomes a differential, in which two input motions are either added up or subtracted at the output.

However, in the case under consideration, using overrunning clutches 77, 78, only a part of the above possibilities can be realized. For a more complete use of the resources of this drive design (in accordance with the above narrative), overrunning clutches 77, 78 can also be replaced by electromagnetic ones.

The functioning of the working body of the device, including two axially mounted working gears 6, 7 and the housing is similar to the above structural options. However, the specified design of the shells (Fig. 10) even more increases the tightness of each interdental space in the radial directions due to the fact that the short shell is mated with a cut in the form of a quarter (in the cross section of the maximum information of the teeth). At other angular values of the input of the short shell, the quarter is much smaller, therefore, the locking ability of this pair decreases as the interdental volume approaches the zone of maximum divergence of the teeth. This event is nevertheless advisable, since the distribution of the degree of compaction along the circumference of the body corresponds to the distribution of pressure values in the interdental volumes by their location, and the “quarter” mating, which forms the labyrinth, satisfactorily closes the interdental volume, especially if there is an additional pair of protrusions 49 and depressions 50 on the annular ends of the shells 6, 7.

7). Performing large 36 and small 37 shells bounding the gear ring 13 on one of the working gears 7 with full or partial coverage of both crowns 12, 13 in the zone of minimum tooth reduction and penetration into the housing 35 along the spherical slot 38, 39 with minimal radial clearances in the zone of maximum information of the teeth 14 makes it possible to completely fence off the working space from the parts 34, 35 of the body (both from the side of the inner radius of the crown and from the outside), and to ensure communication of the part of the body with the working space, for example For the supply of communications 18, 19 (Fig. 11, when performing a small shell 37 of a smaller width of the crown 13). Removing the transmission mechanism from the inner space simplifies the design (Fig. 11, Fig. 13) provides easier access to the gear pair, reduces the amount of internal space by eliminating the amount occupied by the transmission. In this case, parasitic movements of the working environment are reduced.

In this case, when the shaft 28 is rotated, placed in the coaxial openings of the cover housing 35 and the additional housing part, the earring 59 rotates the gear 56 fixed thereon. The gear 56 rotates the ring gear 55, with it the hollow hub 8, then the drive gear 10 10, consequently, the working gear 6 itself.

The rotation of the working gear 6, as well as the above cases, through the interaction of the sections 15 of the teeth 14 rotates the working gear 7, located at an angle θ to the drive 6. The relative inclination of the axes of rotation of the working gears 6 and 7 causes a change in the distance between the disks 10, 11 in the axial direction with their joint rotation.

When the interdental volume is in the zone of maximum divergence of the teeth (Fig. 11), a working medium is supplied to it through the channel 30 of the hollow axis 20, then the channel 19 (provided the inner shell is narrower than the crown width). As the working gears 6 and 7 rotate, the height of the interdental volume in the axial direction decreases, and of course its volume. The elastic working medium is crimped, its pressure rises, and then through the channel 18, brought to the area of maximum convergence of the teeth, it leaves the device.

To prevent volumetric leaks or their significant reduction, the design includes a large 36 and a small 37 shell, limiting the gear ring 13, on one of the working gears 7 with full or partial coverage of both crowns 12, 13 in the zone of minimal tooth reduction and penetration into the housing 35 along spherical slots 38, 39 with minimal radial clearances to the zone of maximum tooth reduction. In this case, the sections 15 of the teeth 14 of the working gear 7 are made integrally with the large 36 and small 37 shells, therefore, leaks are excluded. Sections 15 of the teeth 14 of the working gear 6 are in movable conjugation with the shells 36, 37 of the working gear 7. In this case, when the teeth 14 move, as the working gears 6, 7 rotate, from the position of minimum information to the position of their full alignment of section 15 of each tooth 14 the working gear 6, not equipped with a shell, makes a small, equal to the width of the rim, axial movement along the shells 36, 37 of the second working gear 7. The speed of this movement is much lower than the peripheral speed of rotation of the teeth 14, approximately π × D / b times, which call It is necessary to use a reliable contact seal 51 (Fig. 11, Fig. 12) between the interdental channels, i.e. in the gaps between the tooth 14 or its elements 15 and the sides 36, 37 of the second working gear 37 (or grooves on the inside of the sides for widened teeth or their elements).

For better sealing of the sinuses of the working gear 6, which does not have shells in this embodiment, it is also equipped with a spherical shell 40 mating with the inner surface of the shell 36 covering the crown 12 from the back of the ring gear 12. Spring rings 41 can be installed between the rings 36, 40 similar to piston ones in traditional ICEs or rubber flagella 42 in grooves (Fig. 13).

Spherical cuts 38, 39 in this case with spherical shells 36, 37 placed in them with minimal radial gaps are additional sealing elements, especially in the positions of the interdental canal in the region of maximum compression (the region of maximum tooth convergence).

To achieve additional more reliable sealing of the sinuses of the working gear 6, which does not have a peripheral shell in the structure under consideration, from the working interdental volume, it is advisable to install one or several cylindrical shells 43 included in the sliding interface with the grooves 44 of the body part 35 at smaller radii of its rear end face. (Fig. 11). An additional labyrinth will increase even more hydraulic resistance to overflow in centripetal directions.

8). However, the design of the device with the supply of the working medium only in the region of the maximum divergence of the teeth (Fig. 14, Fig. 11, provided the shells are shorter than the crown width) is functional and useful only in a narrow range of practical options, for example, in the form of a rotary ICE, and then using only a self-igniting pressure mixture, or with a non-contact ignition method. This limitation is caused by the fact that rotating spherical shells prevent access through the channels in the central part of the body to the working interdental space in the zone of maximum tooth reduction, since in order to provide access to it, for example, the inner shell should be made excessively narrow. But this event will expose a considerable part of the working space in the zone of maximum discrepancy from shielding this shell, and the considered sealing scheme of the working space may lose all its advantages.

To overcome this drawback, the shell on the inner side of the crown is made common to both crowns in the form of a spherical ring movably mating with the crowns, mounted with the possibility of rotation in the inclined groove of the housing part located between the central parts of the working gears, and the formation of a zone free from overlapping of the crown in direction of maximum tooth reduction.

In such an embodiment of the rotary volumetric machine (Fig. 13), the working medium enters the hole 31, then the hole 18 in the region of the maximum divergence of the teeth and fills the interdental space. As the working gears 6 and 7 rotate due to the reduction of the interdental volume from the reduction of its size in the axial direction, the pressure increases in it and when each such interdental volume reaches the position corresponding to the maximum convergence of the teeth, the compressed working medium leaves the interdental volume through the channel 19 and then the hole thirty.

The sealing system for the largest shell is similar to the above structural embodiment (Fig. 11). The small-shell sealing system is provided by a spherical ring 45 rotating in the annular groove 47. This spherical ring 45 rotates with the ring gears 12, 13 when sliding in the stationary groove 47. At the ends of the ring 45 it is limited by the walls p and q of the groove 47. The minimum radial the gap between the bottom of the groove 47 and the inner surface of the ring 45, as well as filling it with grease, provide sufficient sealing of the interdental volumes in the circumferential and radial directions. The tight fit and grease of the inner surfaces of the gears 12, 13 to the outer surface of the spherical ring 45 also prevents volumetric losses between the interdental spaces in the circumferential direction. Between the sections of the teeth 15 and the outer surfaces of the spherical ring 45 there is a sliding in the axial direction, however, it is insignificant in comparison with the prevented circumferential. An additional coupling density is provided by the contact seal 51 (Fig. 11). In the resulting gaps in the peripheral Central part of the housing 22 from the spherical ring 45 summed communications 18, 19.

To actuate the working gears 6,7, the drive is made from the gears of the motor shaft (not shown in Fig.) To the gear ring 55 of the hollow shaft 8 mounted on the hollow axis 20 through bearings 52. Further transmission of rotation from the working gear 6 to the working gear 7 is carried out due to the interaction of their sections of the 15 teeth 14. The front and rear surfaces of the sections of the teeth are in contact, and their profile is made from the condition of constant contact when the gears are rotated together, and their clamp is carried out due to the interaction tinuous magnets 94 integrated into each section 15 of the teeth 14.

9). In the constructive embodiment, providing (Fig. 4) the execution of the middle part of the housing located between the Central regions of the working gears 6, 7, in the form of a movable part 48, but also spherical in shape can reduce idling power (mechanical friction loss).

The transmission of mechanical motion in this design occurs with a complete analogy to case 7 (Fig. 11): shaft 28 - gear 56 - ring gear 55 - hollow shank 8 - disk 10 - working gear 6. Due to the fact that the spherical shape has become mobile, communications in this case, it is possible to connect only from the outer side of the crown 12. The width of the shell 36 is reduced to provide windows to the working space of the gears 6, 7 (interdental volumes). Through one of these windows, and previously through the opening 18 of the housing part 35, the working medium is supplied into the interdental spaces of the gear rims 12, 13. As the gear 6 rotates, the gear sections 15 of the teeth 14 rotate and the gear gear 7 rotates. Each interdental volume during transition in the region of the maximum information of the teeth of the working gears 6 and 7 are crimped with increasing pressure of the working medium, due to which it leaves the mouth through the window between the shell 36 and the disk 10 and then through the outlet in the body part 35 (not shown in Fig. 14) oystvo.

The considered scheme for sealing the interdental volumes is slightly inferior to the previous structural options (Fig. 11, Fig. 13) on the periphery, however, it has advantages in reducing friction of the sections 15 of the teeth 14 on the inner diameter of the crowns 12, 13. This gain is achieved by reducing their relative movements, since the central part 48 rotates in the circumferential direction together with the working gears 6, 7.

10). Another option for the rolling execution of the central part 48 is to manufacture it together with one of the working gears (in this case 7). This design, although with a moving middle part (Fig. 15), still allows you to lay in it a communication channel 19, passing further into the outlet openings 30 and 31 in the hollow axes 20 and 21.

The output channel 19 in the structure under consideration is formed by meridional grooves in the spherical central part located in each of the interdental spaces and a radial groove at the end of the stationary hollow axis 20 located in the zone of maximum tooth reduction. Due to the fracture of the axes of rotation of the working gears 6 and 7, each of the rotating meridional interdental grooves is aligned with the stationary end groove on the fixed axis 20 only in the zone of maximum tooth reduction, ensuring in this case the discharge of the indicated volume (in the compressor mode) or its filling (in the mode vacuum pump) with a working medium.

Another channel 18 (for example, in the supply quality) is formed by a radial hole 0 in the spherical ring 36 in each interdental volume and a coaxial hole in the body part 35, connected with a groove in the region of the maximum divergence of teeth, which is connected with the circumference relative to the axis of rotation of the working gear 6.

In this case, the coincidence of the hole ∅ with the circumferential groove in the housing 35 ensures that the interdental space of the working gears 6, 7 is filled with the working medium. With the circumferential movement of the interdental space into the region of maximum tooth reduction, the working medium is compressed and leaves this space due to the pressure difference through the channel 19, formed by the coincidence of the meridional grooves of the central sphere with the radial groove at the end of the axis 20. Next, the working medium enters the hole 30 of the hollow axis 20 and (or) the hole 31 of the hollow axis 21 and leaves the device. The drive operates identically to the above cases (Fig. 11, Fig. 13, Fig. 14).

eleven). To convert the source device (Fig. 16, Fig. 17) into an internal combustion engine, the following measures should be taken in it:

- in the region of the maximum divergence of the teeth on the periphery of the housing 1 (Fig. 16, Fig. 17) along the circumferential direction there are a number of holes 19, one group of these holes is inclined at an acute angle to the outer surface of the ring gears in the meridional plane, and the subsequent group of holes along the way rotation of the working gears 6, 7 at an obtuse angle;

- - to the second in the direction of rotation of the working gears 6, 7, a group of holes 19 is connected to the compressor 91;

- - in the area of the maximum divergence of the teeth to the small diameter of the ring gears in the central housing element 22 located between the central parts of the working gears 6, 7, a feed channel 18 is connected, connected to the hole 31 of the hollow axis 21, and then to the compressor 90 and the capacity of 88 s liquid fuel and a valve 89, regulating the ratio of air and fuel in the supply path;

- in the area of maximum convergence of the teeth in the lids 2 and 3 (Fig. 16), either constant or electromagnets are installed;

- in the disks 10, 11 between the teeth 14 are wired coils of wire with leads that extend into the interdental space with the formation of a gap between them.

Rotary volumetric machine as an internal combustion engine operates as follows:

Upon reaching after the previous working cycle the interdental space of the first group of holes 19 in the region of maximum tooth divergence, part of the combustion products leaves the interdental volume due to excess pressure. With the further movement of the working gears 6, 7, the interdental space overlaps the second group of holes 19, through which the ventilation stream from the compressor 91 under additional overpressure, entering tangentially, displaces the remaining smoke. The tangential entry and exit of flows reduces their mixing and contributes to a more complete and organized displacement of combustion products.

The compressor 90 through a pipe 87 is continuously sucked from the atmosphere and pumps air into the hole 31. In this case, the air flow can be controlled either by the frequency of the compressor cycles, or by a valve 89, and hydrocarbon liquid (or dusty solid or gaseous) fuel enters into this air stream and mixes with it. From the hole 31, the fuel-air mixture through the channel 18 enters the interdental space of the gears 12, 13, limited in the circumferential direction by the engaging sections 15 of the teeth 14, in the radial shells 23, 24, 25, 26, in the axial disks 10, 11 of the working gears 6 , 7.

In the course of further rotation of the working gears 6, 7, a second pair of interacting teeth 14 of the interdental space passes through the first group of openings 19 and the compressor 91 supplies atmospheric air (or other gas) through the second group of openings 19 to the already closed volume under increased pressure (Fig. 17). At the same time, the fuel charge is also supplied to the closed interdental volume through channels 18, 31 from the compressor 90.

Further rotation of the working gears 6, 7 moves the interdental volume from the region of maximum divergence of the teeth 14 (and their sections 15) to the region of their maximum convergence with a decrease in its volume by reducing the size in the axial direction.

The decrease in volume can increase the pressure of the fuel mixture in the interdental volume to the desired degree of compression due to the addition of teeth with tidal displacers (see prototype). Together with the interdental volume, the inductor 95 rotates. When the inductor 95 enters the magnetic field of the magnets 92, 93 placed either in the covers 2, 3, or in the halves of the housing 34, 35 in the sector of the minimum axial size, an EMF is induced in each of the turns, creating at the ends of the open winding voltage [see KABARDIN O.F. Physics, References, Moscow, Education, 1991, p. 196-197]

U = 2 n V V l,

Where

n is the number of turns of wire in the coil;

V is the linear velocity of the coil entering the magnetic field, m / s;

B - magnetic field induction from permanent stationary magnets 92, 93, T;

L is the length of the moving conductor within the magnetic field (l ≈ half the length of the coil loop, m).

As a result, an electrical voltage and an electric discharge are created at the output contacts. Moreover, first the first half of the loop of the inductor 95 enters the magnetic field and, as the induction increases, by approaching it to the permanent magnets 92, 93, an electric current of one direction is organized in it. After overcoming the zone of maximum induction by this part of the inductor 95, an inductive electric current of the opposite direction is created in it. It is advisable to carry out coils of such dimensions that they would ensure the entry of the second part of the circuit after the full exit of the magnetic field of the permanent magnets 92, 93 of the first part of the circuit. That is, the electric current in this case is alternating.

Moreover, the above group of stationary magnets 92, 93 works in combination with movable magnets 94, mounted on the mating blades 12, 13 for their mutual pressing in order to seal.

The interaction of the fields of fixed and movable magnets causes a deep non-uniformity of induction (tension), which greatly increases the local value of the inductance of the total magnetic field and its gradient, which means the voltage at the ends of the open winding (≈ 1000 V) and the guarantee of electric discharge due to intense ionization of the gas mixture.

The process of intense ionization of a gas mixture under the influence of a constant or alternating electric field occurs when it reaches a certain critical value of intensity. In this case, the “seed” free electron, under the action of the field, gains energy sufficient to ionize the atom, and, further involving more and more new generations of electrons in the ionization of the gas mixture, and this generates an electron avalanche, creating a spark.

A spark from an electric discharge ignites the fuel charge in the interdental space, increases its volume from fuel combustion and raises the temperature of the gas, which, in turn, multiplies pressure.

After overcoming the “bottom dead center” the interdental volume acquires a configuration when the projection of the surface area of the first gear pair in the circumferential direction becomes larger than the similar characteristic of the next pair of engaging teeth (see prototype). The difference in area in the product of the pressure in the interdental volume gives the circumferential force and moment on the shank 8 of the working gear 6.

Thus, in each interdental space, circumferential moments are created on the gear teeth 12 and 13. The pressure in the interdental spaces decreases as they approach the “top dead center” due to an increase in the volume of this space, which means that the contribution to the resulting circumferential moment of each interdental volume different.

The total circumferential moment drives the working gears 6, 7, and is also transmitted to the epicyclic crown.

Further, the nature of the transmission of motion is determined by the configuration of the planetary gear:

- adjustment of the planetary gear with carrier 73 stopped (when the solenoid 83 is turned on). In this case, the axles of the satellites 69 in the circumferential direction are stationary, the satellites 68 themselves rotate relative to the axes fixed in the bearings 70 and transmit the motion to the ring gear 65 of the sun gear. Together with the sun gear, the gear 66 rotates at the same angular speed and then the gear 67, which, when its overrunning clutch 77 is activated, rotates the shaft 28 in the same direction as the ring gears 12, 13. In this case, the gear 75 is not connected with the shaft 28 , since its overrunning clutch 78 in this direction does not transmit a moment.

- setting the planetary gear with the stopped sun gear 65 (when the solenoid 84 is turned on) involves rolling the satellite 68 along the stationary gear ring of the sun gear 65 from the rotation of the epicyclic gear ring 58 of the working gear 6.

In this case, the carrier 73 will rotate in the same direction as the working gear 6 (ring gears 12, 13), but more slowly. The carrier also has a gear ring 74 that rotates the gear 75, and this gear 75 rotates the shaft 28 in the direction opposite to the direction of rotation of the gear rims 12, 13. Gear 67 in this case is not connected with the shaft 28, since its freewheel 77 In this direction does not transmit the moment.

It should be noted that the use of couplings 83, 84 is possible in the incomplete locking mode, which allows you to change the gear ratio of the gearbox continuously in a smaller direction.

The mode of creating a vortex field by the solenoids 83, 84 translates the planetary gear into the differential gearbox, which allows both lowering and increasing the rotation frequency of the output shaft 28. Moreover, with the joint regulation of the motion of the epicyclic and sun gear, additional capabilities can be achieved.

The proposed technical solution is progressive and timely for the development of designs of hybrid drives (for example, in the automotive industry), involving the rotation of the power of hydrocarbon and electrical origin with the most appropriate implementation of each of these types according to the operating conditions.

Moreover, the compactness of the proposed device makes it possible to use it in the form of motor wheels for cars, which also allows you to increase the usable volume of the car, increase its reliability by duplicating the drive by installing it on each wheel, and increase the efficiency of these cars due to the increased gearbox. d. this type of power plant.

In addition, the compactness and low weight of the installation suggests its use in non-traditional fields of application, for example, in the active chassis of aircraft, which can significantly reduce the energy consumption of the take-off stages of flights and reduce fuel costs.

The most appropriate use of the proposed device is their use in small-sized robotic transport systems - drones due to their compactness and efficiency of the work process. In this case, the duration of flights, sailing, moving on land can be significantly increased.

With a systematic approach to the design and manufacture of rotary volumetric machines, it is possible to significantly reduce the cost of manufacturing these devices for various purposes - vacuum pumps, compressors, liquid ring pumps, rotary internal combustion engines, power units of milking machines, etc., and also reduce costs even more to production by creating standardized series, unifying groups of parts. The low cost of the object in question contributes to the expansion of its scope - medicine, food production, life, oil and gas sector, etc.

A significant resource for the intensification of the production of such products containing parts with complex geometry is the rapidly developing technology of 3D printing on machine printers, and around the clock and without human presence.

As a result, we can also assume that, as a result of the general development of industry, the demand for the products offered is indicated by the need to improve existing technological processes and products, as well as by the need to create new technologies and products, including on new operating principles. More advanced devices in this case are more relevant than ever.

Claims (23)

1. Rotary volumetric machine, comprising a housing with end caps, in the bores of which are driving and driven working gears forming an axial gear, each working gear of which consists of a hollow hub and a disk with teeth consisting of a crown in the form of a crown, consisting of separate sections with an asymmetric profile having front and rear surfaces, channels for supplying and discharging the working medium are formed in the housing, characterized in that the working gears are mounted on the hollow axes at an angle that provides overlap they have tooth crowns on the entire circumference, each hollow axis is fixed on one side to the end cover of the housing, and on the other hand is connected to a part of the housing located between the central parts of the working gears, the disk of each working gear is equipped with at least two shells covering a crown of teeth from the outer and inner sides, each section of the teeth is equipped with permanent magnets, the drive drive gear wheel is equipped with a gear transmission with the shaft output from the inside of the housing through the seal, through hole axes are hollow channels approach-retraction operating environment. 2. Rotary volumetric machine according to claim 1, characterized in that the housing is formed directly from the end caps, each of which has a meridional connector along the plane of the axes of rotation of the working gears. 3. The rotary volumetric machine according to claim 1, characterized in that each of the shells of each working gear is made in the form of a part of a hollow torus, forming in the cross section of the largest tooth overlap either a closed ring, or a ring with one, or a ring with two windows. 4. The rotary volumetric machine according to claim 1, characterized in that the surfaces of the shells are made spherical with radii drawn from the center coinciding with the point of intersection of the axes of the axial gears. 5. The rotary volumetric machine according to claim 1, characterized in that the gear transmission is made in the form of a cylindrical gear, or a bevel gear, or a planetary gear. 6. The rotary volumetric machine according to claim 1, characterized in that the gear transmission is placed on the outside and connected to the hollow hub of the working gear. 7. The rotary volumetric machine according to claim 1, characterized in that when using the rotary volumetric machine as a rotary internal combustion engine, the central part of its body in the zone of maximum divergence of teeth is equipped with a nozzle to which a fuel pipe is connected, connected to the fuel tank through a high pressure pump , a compressor is connected to one of two groups of nozzles on the peripheral part of the same zone, and ignition devices are placed in the zone of maximum tooth convergence. 8. The rotary volumetric machine according to claim 4, characterized in that the surfaces of the shells of each of the working gears have equal radii of the same name and are made with an arbitrary ratio of widths, provided that the total width of the shells does not exceed the width of the ring gear. 9. The rotary volumetric machine according to claim 4, characterized in that the surfaces of the shells of the working gears are mated along the entire width of the crown with a minimum radial clearance of the shells of the same name with each other, both on the outer and inner sides of the crowns, and the smaller diameter outer shell pairs, and a large diameter shell of the inner pair have slots for each section of their teeth under the tooth section of another working gear. 10. The rotary volumetric machine according to claim 4, characterized in that one of the shells partially covers the ring gear, and the other covers the ring gear along the entire width with a quarter sampling from the side of the ring for placing the first with a minimum radial clearance and the formation of a sealing labyrinth. 11. The rotary volumetric machine according to claim 4, characterized in that each of the shells limiting the gear ring is made on one of the working gears with full or partial coverage of both crowns in the zone of minimal tooth reduction and penetration into the housing along a spherical slot with minimal radial gaps in the zone of maximum tooth reduction. 12. Rotary volumetric machine according to any one of paragraphs. 1, 3, 4, characterized in that the ends of the mating shells have mating protrusions and depressions, passing on the ledges of the housing under these shells, forming a sealing labyrinth. 13. The rotary volumetric machine according to claim 5, characterized in that the cylindrical gear is connected at the largest radius of the working gear, or at its hollow hub. 14. Rotary volumetric machine according to claim 5, characterized in that the planetary gear is made with the carrier stopped, or with the sun gear stopped, or with a mechanism for changing its structure. 15. The rotary volumetric machine according to claim 7, characterized in that the ignition device is made in the form of magnets placed in the end caps of the housing in the zone of maximum convergence of the teeth, and in each interdental interval of the disk of the working gear there are inductors with the output of the ends of the conductor into its interdental space, with a gap between them. 16. The rotary volumetric machine according to claim 11, characterized in that on the periphery of the driving working gear, on its rear end there is a spherical shell mating with the inner surface of the shell of the driven working gear. 17. The rotary volumetric machine according to claim 11, characterized in that at the rear end of the driving working gear, at radii smaller than the peripheral one or more concentric cylindrical shells are installed, which are included in the sliding interface with grooves in the housing. 18. The rotary volumetric machine according to claim 11, characterized in that the shell on the inside of the crown is made up of a separate part common to the crowns of both working gears in the form of a spherical ring movably mating with the crowns mounted for rotation in the inclined groove of the housing located between the central parts of the working gears, and the formation of a zone free from overlapping one of the crowns in the area of maximum tooth reduction. 19. The rotary volumetric machine according to claim 11, characterized in that the middle part of the housing located between the central parts of the working gears is either a separate floating sphere or a sphere belonging to one of the working gears. 20. The rotary volumetric machine according to claim 14, characterized in that the mechanism for changing the structure of the planetary gear is made in the form of electromagnetic couplings, one of which connects the housing to the carrier, and the other the hollow axis of the working gear with the sun gear. 21. The rotary volumetric machine according to claim 15, characterized in that the end caps, housing, working gears or their individual parts are made either of metals, or of polymers, or of ceramics, or of an optically transparent material. 22. The rotary volumetric machine according to claim 20, characterized in that the electromagnetic coupling connecting the hollow axis of the pinion gear to the sun gear is made in the form of an annular cavity on the inside of the sun gear, with radial baffles installed in this cavity and filled with ferromagnetic powder, or ferromagnetic fluid, and on the inside of the hollow axis on the part of its bore within the annular cavity, a solenoid is installed with the ability to connect to an electric current source. 23. The rotary volumetric machine according to claim 20, characterized in that the electromagnetic coupling connecting the carrier to the body is made in the form of an annular cavity on the outer side of the carrier, with radial partitions installed in this cavity and filled with ferromagnetic powder or ferromagnetic fluid, and the outer side of the housing within this annular cavity is installed a solenoid with the ability to connect to a source of electric current.

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