RU2377414C2 - Rotor-type cone-screw engine - Google Patents

Abstract

FIELD: engines and pumps.

SUBSTANCE: invention relates to engine production. Proposed engine comprises inner and outer cone-screw elements arranged at an angle to each other and having hearing, pressure and expansion sections. The latter have helical working surfaces for elements to stay in contact with each other. Number of starts of helical working surface in expansion section of whatever element equals that in expansion section. Number of starts n₂ of outer element helical working surface per unity exceeds number of starts n₁ of inner element helical working surface. Aforesaid inner and outer elements are arranged in fixed housing to rest thereupon via bearings and rotate therein in one direction. Synchronisation of the rotation of aforesaid elements is performed by gearing. Direction of helical winding in pressure section of whatever cone-screw element complies with that in expansion section. Helices of working surfaces of the inner and outer cone-screw elements are directed in opposition. Helices of working surfaces of pressure and expansion sections of said elements comprises at least one complete turn.

EFFECT: higher reliability, increased RPM, simpler design and good balancing.

34 dwg

Description

Technical field

The invention relates to mechanical engineering, mainly to engine building, namely to rotary-type heat engines with non-parallel axes, and can be used as a source of mechanical energy in vehicles and various power plants, and in partial form as a gas compressor or gas engine.

State of the art

Known gas turbine internal combustion engine, gas-dynamic type, working with the supply of heat at constant pressure and consisting of a compressor, a combustion chamber, as well as a compressor drive turbine and a power turbine. The working fluid (air) is compressed by the compressor, enters the combustion chamber, where it is heated at constant pressure due to the combustion reaction of the fuel supplied to the combustion chamber, and then, expanding and accelerating, it does the job, reporting torque and rotational movement of the compressor drive turbine and power turbine. The interaction of the working fluid with the blades of the turbines and the compressor is based on the aerodynamic phenomena that occur when gases flow around profiled surfaces. The advantages of this engine include high specific (by weight) power, compactness, complete balance, low toxicity, multi-fuel, smooth operation with no ripple in the torque, optimal appearance of external speed characteristics, high duration of service intervals. An increase in efficiency on this engine is achieved by increasing the pressure developed by the compressor, increasing the temperature of the gases at the exit of the combustion chamber, and also by partially regenerating the residual heat of the exhaust gases. The whole complex of these measures requires design complexity by the inclusion of new devices and leads to a general weighting of the structure, and in combination with the need to use the most advanced materials and technologies, it leads to a significant increase in the cost of finished products. In addition, the disadvantages of this engine include unsatisfactory operation in transient and transient modes, a relatively high specific fuel consumption, reduced to energy taken from a power turbine, a narrow operating range that provides maximum efficiency, and inapplicability in low-power installations.

In addition to the described, volumetric type discharge devices are known, such as Wankel, Zoller and Powerplus, Lysholm, Roots, Volkswagen G-shaped blowers, as well as Muano gerotor pumps.

The injection in these devices occurs due to the formation and filling with gas of volume cavities (capsules), limited by moving bodies and the body, with their subsequent isolation from the inlet tract and the displacement of gas from these capsules into the outlet pressure cavity due to the geometric reduction of the volume of the capsule enclosed between the expelling bodies. The presence of a limited number of isolated capsules during their successive opening into the injection cavity causes the appearance of pressure in the last pulsation, the degree of which can vary from one device to another and depends on their design features. Due to the preliminary compression of the capsules before opening them into the injection cavity, the Volkswagen G-Lader spiral compressor and Liskholm screw compressors are characterized by the least pressure pulsation.

Pumping devices used in modern engineering can be classified as follows:

1. Gas-dynamic type:

1.1. Aerodynamic fan type:

1.1.1. Axial scapular:

1.1.2. Centrifugal:

1.2. Energy exchange (Comprex);

2. Volumetric type:

2.1. Piston;

2.2. Shibernye (Zoller, Powerplus, Shorrock, Pierburg, Bendix);

2.3. Rotary:

2.3.1. Single rotor (Wankel);

2.3.2. Two-rotor with parallel gear type rotors (Roots);

2.3.3. Two-rotor with parallel rotors of screw type (Lisholm);

2.3.4. Twin-rotor with nested rotors of screw type (Murano gerotor pumps);

2.4. Volkswagen Spiral Blowers (G-Lader).

Any pumping device can be turned into an engine, but due to design reasons, and also due to the insignificance of the developed effective working pressures, at present such constructions of rotor-type devices have not gone beyond the scope of prototypes and experimental samples, examples of commercial application are not known to the author.

In addition to the above-described devices, a rotary-wave engine of a volume type of a design is also known. (RU, patent 2155272 C1, class F02B 55/00, 53/08), comprising a rotor installed in a housing including an inlet and an outlet window, a compressor and expansion compartments, and a combustion chamber, characterized in that the inner surface of the housing is made in the form facing the vertices and lying on the same axis, a pair of screw cones like the surface of a rotor installed at an angle to the axis of the housing, and at least two support nodes, with any point on the helix of the rotor, except for the center, in which the frequency and amplitude of oscillation is zero, performed with the ability to make equal angular oscillations relative to the axial line of the housing, and in general to provide the rotor with the possibility of rotation with simultaneous planetary rolling along the inner envelope of the housing. The advantages of the described engine include:

1. The possibility of realizing the continued expansion of the working fluid, which leads to an increase in efficiency, reduces the noise level and eliminates the need for silencers.

2. Complete overall engine balance.

3. Smooth operation due to uniform torque.

Prototype

Based on the generality of the basic geometric principle of the formation and transformation of volumetric cavities (capsules), the closest to the proposed one is the Sedunov wave-rotary engine (RU, patent 2155272 C1, class F02B 55/00, 53/08). In this regard, the specified engine is selected as a prototype.

The disadvantages of this engine include the presence of a complex planetary-rolling motion of the rotor, which limits the maximum engine speed, and therefore its power, and also requires additional balancing elements (balances). In addition, to ensure the complex nature of the movement of the rotor in the support node, crosshead and pull mechanisms are used, which are spherical analogues of rodless mechanisms, patented by Frank Carey in US patent No. 441932 dated December 2, 1890 and carefully developed and developed by S. S. Balandin. Existence of excessive communication places high demands on the accuracy of manufacturing and the assembly culture of rodless devices. Even with minor manufacturing inaccuracies, excess bonds can prove to be a source of very significant stresses in the contact areas of the movable elements, which contributes to additional mechanical losses and rapid wear.

It should also be noted that the use of a crosshead support-synchronizing mechanism allows the device to be realized only with the number of winding entries n ₁ = 1 for the screw working surface of the rotor and n ₂ = 2 for the screw working surface of the housing.

The purpose of the invention

The aim of the present invention is, while maintaining all the advantages of the prototype to provide:

1. Improving reliability;

2. Increase the maximum speed;

3. Complete balancing of the engine without the participation of special mechanical elements;

4. Improving power and weight and size characteristics;

5. The implementation of the device with the number of approaches of winding the working surfaces of the conical screw elements n ₁ > 1 and n ₂ >2;

6. Simplification of engine design.

In accordance with the invention, the goals are achieved by transferring bearing functions from a fixed external conical screw element, which in the prototype acts as a housing to the third element, while the external conical screw element and the internal one are able to rotate in the bearings of the stationary third element - the housing around non-parallel axes having a common point. This arrangement of the main structural elements allows you to have only the rotational movement of the internal and external conical screw elements and thus get rid of the conical planetary-rolling motion of the rotor inside the housing in the prototype, which helps to increase the maximum speed of the working elements, and therefore increase the maximum engine power. The rotation synchronization of the conical screw elements can be provided either by a bevel gear internal gearing, or by independent mutual self-installation of the conical screw elements, the screw working surfaces of which initially have a fundamental similarity to the mentioned transmission. Elimination of the crosshead and driver synchronization mechanisms that create redundant connections allows you to get rid of spurious forces, which positively affects the reliability and durability of the engine. In the absence of a crosshead mechanism that imposes a limit on the number of windings of the screw working surfaces of the conical screw elements, it becomes possible to implement multi-start forms of screw working surfaces of the conical screw elements with a gear ratio other than 1: 2.

In order to achieve the object of the invention, a rotary cone-screw engine comprising angled inner and outer cone-screw elements, each of which has a heating section, as well as a discharge and expansion section, having screw working surfaces with which the elements are in contact with each other along lines closed in space, forming a series of helical vesicular cavities isolated from each other, the volume and position of which change with a working change in the relative position elements, the number of entries of the screw working surface in the discharge section of any of the elements is equal to the number of entries of the screw working surface in its expansion section, the number of entries n _{2 of the} screw working surface of the outer element is one greater than the number of entries n _{1 of the} screw working surface of the inner element, characterized in that the inner and outer conical screw elements are located in a fixed housing, rely on it through bearings and have the ability to make interconnected e one-way rotation, synchronization of rotation of the conical screw elements is carried out by means of a gear transmission, the direction of winding the screw working surface in the discharge section of any of the conical screw elements coincides with the direction of winding the screw working surface in its expansion section, the winding of screw working surfaces of the inner and outer conical screw elements coincide in direction, spherical sections of screw work surfaces having a common central point, representing constitute, scaled and rotated around the axes of the corresponding conical screw elements, winding the screw working surface of the discharge section of the external conical screw element contains at least one full revolution, winding the screw working surface of the expansion section of the outer conical screw element contains at least one full revolution .

Thus, the proposed changes in layout and kinematics greatly simplify the design of the engine as a whole. At the same time, the basic geometric principle of the formation of volumetric cavities (capsules) that serves to transform the parameters of the working fluid is preserved.

Description of illustrations

Graphic explanations of the design principles and principles of the proposed mechanism are presented in the illustrations:

Figure 1. Engine housing (front view).

Figure 2. Engine housing (rear view).

Figure 3. Engine housing section AA (left view).

Figure 4. Engine housing (isometric view).

Figure 5. External conical screw element of the engine (front view).

6. External conical screw element of the engine (rear view).

7. External cone-screw element of the engine - section (left view).

Fig. 8. External conical screw element of the engine (left view).

Fig.9. The outer cone-screw element of the engine is dissected (isometric view).

Figure 10. Internal conical screw element of the engine (front view).

11. Internal conical screw element of the engine (rear view).

Fig. 12. The internal conical screw element of the engine is a section (left view).

Fig.13. Internal conical screw element of the engine (left view).

Fig.14. Internal conical screw element of the engine (isometric view).

Fig.15. General view of the engine (front view).

Fig.16. General view of the engine (rear view).

Fig.17. General view of the engine (left view).

Fig. 18. General view of the engine (isometric view).

Fig.19. Engine cross section without internal conical screw element (left view).

Fig.20. Cross-section of an engine with a non-dissected internal conical screw element (left view).

Fig.21. Engine cross section (left view).

Fig.22. Generators (front view).

Fig.23. Generators (left view).

Fig.24. Generators (top view).

Fig.25. Generators (isometric view).

Fig.26. A helical vesicular cavity in contact with the screw working surface of the internal conical screw element (right view).

Fig.27. Helical vesicular cavity (right side view).

Fig.28. A helical bubble-shaped cavity in contact with a screw working surface of an internal conical screw element (top view).

Fig.29. Helical vesicular cavity (top view).

Fig.30. A helical bubble-shaped cavity in contact with a screw working surface of an internal conical screw element (front view).

Fig.31. Helical vesicular cavity (front view).

Fig. 32. A helical vesicular cavity in contact with a screw working surface of an internal conical screw element (isometric view).

Fig. 33. Helical vesicular cavity (isometric view).

Fig. 34. Indicator diagram.

Designations in illustrations

1. Housing assembly.

2. The upper body element.

3. The lower housing element.

4. The front hub.

5. The rear hub.

6. The conical screw element is external.

7. The discharge section of the outer conical screw element.

8. The expansion section of the outer conical screw element.

9. The heating section of the outer conical screw element with thermal insulation.

10. The front disc cover assembly of the outer conical screw element.

11. Disc cover rear outer conical screw element.

12. The front bearing of the outer conical screw element.

13. The rear bearing of the outer conical screw element.

14. The gear of the outer conical screw element is synchronizing.

15. The conical screw element is internal.

16. The discharge section of the internal conical screw element.

17. The expansion section of the internal conical screw element.

18. The heating section of the internal conical screw element with thermal insulation.

19. The gear of the internal conical screw element synchronizing.

20. The axis of the internal conical screw element assembly.

21. The front bearing of the inner conical screw element.

22. The rear bearing of the inner conical screw element.

23. The initial cone of the outer conical screw element.

24. The initial cone of the internal conical screw element.

25. The initial circumference of the outer conical screw element.

26. The initial circumference of the inner conical screw element.

27. Generating an external conical screw element.

28. Generating an internal conical screw element.

29. Point of contact of generators.

30. The shape of a helical vesicular cavity.

31. The line of contact of the working surfaces.

Description of the invention

The engine consists of two conical screw elements. The inner conical screw element 15 (Fig. 20) is located inside the outer conical screw element 6 (Fig. 19), rotating in bearings 21, 22, 12, 13 (Fig. 3) of the housing 1 assembly (Fig. 4), around axes intersecting at a certain angle at a central point. Cone-screw elements form with each other a series of helical vesicular cavities 30, Fig. 33. The helical vesicular cavities are locked between the screw working surfaces and sealed along the space-tightened contact lines 31 of the screw working surfaces of the conical screw elements. Screw working surfaces have a mutually bending geometric shape, that is, they are in constant contact with any interconnected rotation of the conical screw elements. The outer conical screw element consists of three sections: discharge 7, expansion 8 and heating 9 connecting them (Figure 7). The internal conical screw element also consists of three sections: discharge 16, expansion 17 and heating 18 connecting them (Fig.13). When the engine is running, the cone-screw elements rotate around their axes and, like screws, screw the gaseous working fluid bubbles with their screw working surfaces in the discharge part of the engine. Next, the working fluid enters the space enclosed between the heating sections of the cone-screw elements, forming a heating chamber, after heating in which it does work, making up between the screw working surfaces of the expansion sections of the cone-screw elements. When a gaseous working fluid is screwed between the screw working surfaces of the discharge sections of the cone-screw elements, the compression occurs due to the reduction in the geometric dimensions of the screw-like vesicular cavities (capsules) enclosed between the cone-screw elements, according to three dimensions in space. When the screw-like vesicular cavities are unscrewed between the expansion sections of the cone-screw elements, the working fluid expands in them. The helical working surfaces of the expansion sections of the conical screw elements are subjected to the pressure of gases enclosed in helical bubble-shaped cavities. The resulting gas pressure forces on the screw working surfaces, intersecting with the axes of the corresponding conical screw elements, cause the formation of torques on the latter. Some of the moments are communicated to the injection sections to overcome the reaction forces of the compressible gas, another part does the work by transmitting rotation through the transmission to an external consumer of mechanical energy. The rotation synchronization of the conical screw elements is carried out by bevel gears: internal gear gear 14 (Fig. 7) and gear 19 (Fig. 13). A synchronization mechanism is required to prevent direct contact between the helical working surfaces of the conical screw elements, which can contribute to intensive wear.

Despite the layout similarity of a cone-screw engine with a conventional gas turbine engine, its working process is closer to the working process of a piston engine. The steady state indicator diagram shown in FIG. 34 will be slightly different from that for a reciprocating engine. This diagram can be conditionally divided into five sections. The first section is described by line AB and shows the process of forming a helical vesicular cavity and filling it with a working fluid. The pressure in the first section P _{AB is} slightly less than atmospheric P _atm due to the resistance exerted by the filtering elements of the intake tract. At the moment to which point B corresponds (Fig. 34), when the helical vesicular cavity is fully formed, has acquired the volume V of the _EP and is hermetically isolated (closed), the second section of the indicator diagram begins, which is described by the curved line BC, on which the worker pre-compresses body in a decreasing helical vesicular cavity of the discharge part of the engine. At the moment to which point C corresponds (Fig. 34), when the helical vesicular cavity opens into the heating chamber and has a volume V _SJ and pressure P _C , the third section begins, described by line C-C'-D. In the third section, the working fluid is extruded from the screw-shaped bubble-shaped cavity of the engine’s discharge part into the heating chamber and, at the same time, the spiral-shaped bubble-shaped cavity is formed and filled with the working medium in the expansion part of the engine, therefore, the volume in the third section of the indicator diagram can be considered constant, while pressure will experience ripple. These pulsations are due to the fact that when the screw-like bubble-shaped cavity of the injection part of the engine communicates with the heating chamber, it contains a working fluid that has not yet been warmed up, therefore its pressure P _{C is} less than the pressure P _{D of the} already heated working fluid in the heating chamber. Part of the gases from the heating chamber rushes into the spiral-like vesicular cavity, and their pressures are equalized to a certain pressure P _{C '} . As the gases squeezed out from the screw-like vesicular cavity of the engine’s injection part are heated up, the pressure rises to the value of P _D when the formation of the next screw-like vesicular cavity between the screw working surfaces of the expansion sections of the cone-screw elements and its hermetic isolation (closure) occurs, as well as opening into the heating chamber of the next helical vesicular cavity from the discharge part of the engine. A very important feature of the engine is that when implementing multi-helical helical working surfaces with a heating section in simultaneous communication, but in different phases, there are several screw-like bubble-shaped cavities of the discharge part of the engine and several spiral-like bubble-shaped cavities of the expansion part. At the moment to which point D corresponds (Fig. 34), when the helical vesicular cavity of the engine expansion part is completely formed and hermetically isolated (closed) from the heating chamber, the fourth section begins, which is described by the line DE of the indicator diagram (Fig. 34). In this section, the working gases enclosed inside the expanding helical bubble-shaped cavity of the engine’s expansion part perform mechanical work by exerting pressure on the walls of the expansion sections of the cone-screw elements and giving off a certain part of the energy previously communicated to them. Theoretically, the expansion can be carried out completely, that is, to atmospheric pressure, and then almost all the energy of the working fluid available for extraction in the form of work will be used, however, for layout reasons, the implementation of full expansion seems difficult, so you can limit yourself to incomplete continued expansion. At the moment that corresponds to point E of the indicator diagram, when the volume of the expanding screw-like vesicular cavity becomes equal to V _SP , it is opened into the exhaust system of the engine, the pressure in it drops sharply to almost atmospheric, which is reflected by the fifth section EF of the indicator diagram. Very significant is the condition V _SAT> V _VI, which provides the operating cycle engine-expansion, and consequently an increase of the thermodynamic cycle efficiency. After opening, the helical vesicular cavity, having disbanded and decreasing in volume to zero, displaces the remaining exhaust gases into the engine exhaust system under pressure P _FG , which is slightly higher than atmospheric P _atm , due to the resistance exerted by the exhaust path, which is reflected in the sixth section of the FG indicator diagrams. The work of one portion of gas passing through the engine in steady state is determined by the difference between the large and small areas enclosed inside a closed loop figure described by the lines of the ABCDEFGA indicator diagram (Fig. 34).

The shaping of helical working surfaces of cone-helical elements is based on the conceptual apparatus of the theory of gears, taken from the section of shaping of bevel gears, which considers the so-called "initial cones", which are used for modeling conical gears and in constructing tooth geometry. The initial cone 23 of the outer conical screw element and the initial cone 24 of the internal conical screw element are shown in FIG. The tangent rolling of the initial cones is considered to occur without slipping. The sets of points that belong to the initial cones and are equidistant from the vertex common for the cones (center point) are two “initial circles” 25 and 26 that are in contact, lying in different planes, the radii of which are proportional to the gear ratio of the bevel gear. Geometric constructions of the generatrix sections of the teeth of the curves are carried out from these initial circles using methods of spherical geometry. The author has developed a mathematical algorithm for the parametric description of spherical curves forming the working surfaces of conical screw elements. The algorithm is very extensive, therefore, in the description of the invention can only be set out the basic concepts and principles of construction of the generatrices 27 and 28 (Fig.22) and screw working surfaces.

The set of points of helical working surfaces equidistant from the central point has the form of two spherical curves of a petal shape (hereinafter referred to as helical working surfaces of conical screw elements or simply forming 27 and 28). Generators 27 and 28 lying on the same spherical surface centered at a central point have the following features:

1. Generators are closed within one revolution on the surface of the sphere around the axis corresponding to the conical screw element.

2. Generators have angular periodicity (the number of periods per revolution is equal to the number of petals).

3. One period is formed by alternating concave and convex sections.

4. The generatrices of the screw working surfaces of the conical screw elements in the same spherical section are mutually bending, that is, they are in constant contact at points 29 with each other, but do not intersect with each other.

5. Generators do not intersect with themselves.

6. The number of petals of the outer generatrix is equal to the number n ₂ entries of the screw working surface of the outer conical screw element and is one more than that of the generatrix of the inner one, the number of petals of which is equal to the number n _{1 of} inputs of the screw working surface of the inner conical screw element.

7. The generators of the cone-screw elements in the same spherical section are constructed using spherical geometry methods from the initial circles 25 and 26, corresponding to the diameters D ₁ and D ₂ in the ratio n ₁ : n ₂ .

8. The inner generatrix cuts off several isolated closed flaps (areas) of the spherical surface in the outer one, limited by the parts of the generators enclosed between the points 29 of their mutual contact (Fig. 22) for any interconnected rotation of the conical screw elements.

Screw working surfaces are obtained by extracting the generating curves with continuous and monotonous rotation and scaling along the axes of their corresponding conical screw elements. The formation of helical work surfaces is subject to the following principles:

1. With a continuous change in the selected direction of the removal of R (equal to the radius of the secant sphere), the generators experience continuous transformations of homothety (similarity), proportional to the value of the removal of R, which is in this case. an argument.

2. With a continuous change in the argument R, the generators monotonously rotate in the same direction from the starting position by angles whose increments Δϕ ₁ for the inner conical screw element and Δϕ ₂ for the outer are in the ratio Δϕ ₂ = (n ₁ / n ₃ ) Δϕ ₁ .

3. With a continuous change in the argument R, the generators can change shape only by changing the ratio between the angular portions of the concavity and convexity of the petals, but the number of petals always remains constant.

4. One closed helical bubble-shaped cavity of form 30 (Fig. 27) can be formed only within one full revolution of winding the screw working surface of the outer conical screw element, while winding the screw working surface of the inner conical screw element includes n ₂ / n ₁ revolutions .

In order to optimally use the space and keep the angle of inclination of the winding stream constant over the entire shaping of the screw working surface, for the angle ϕ of rotation of the generatrix from the starting position, it is necessary to satisfy the condition dϕ / dR · R = const, which reflects the need to reduce the winding pitch proportional to the decrease of the argument R. Integration of this expression gives the logarithmic dependence of the angle of rotation of the generatrix of the corresponding conical screw element on the argument R. Dependencies ut have the form ϕ ₂ = Log _Knar (R) + ϕ ₀₂ and ϕ ₁ = Log _Kvn (R) + ϕ ₀₁ , where K _nar and K _ext are some interrelated coefficients that determine the required angles of inclination of the winding streams of screw working surfaces. A parametric description of the change in removal and the corresponding rotation angles of the generators can be described by equations; ϕ ₂ (t) = ϕ ₀₂ + 2 · π · t, ϕ ₁ (t) = ϕ ₀₁ + 2 · π · t · n ₂ / n ₁ , R (t) = R ₀ · (k) ^ t, where ϕ ₁ is the angle of rotation of the generatrix of the internal conical screw element, ϕ ₂ is the angle of rotation of the generatrix of the external conical screw element, ϕ ₀₁ is the initial angle of rotation of the generatrix of the internal conical screw element, ϕ ₀₂ is the initial angle of rotation of the generatrix of the external conical screw element , R ₀ is the initial radius of the sphere carrying the generatrix (removal), k is the coefficient of reduction of the removal corresponding to one full revolution of the generatrix of the outer conical screw element, t is the parameter, with corresponding to the number of full revolutions of the generatrix of the outer conical screw element. The dependences of the rotation angles can be rewritten in the form: ϕ ₂ (t) = ϕ ₀₂ + k ₂ · t, ϕ ₁ (t) = ϕ ₀₁ + k ₁ · t, where k ₂ is the coefficient of rotation of the generatrix of the helical working surface of the outer element, k ₁ - the coefficient of rotation of the generatrix of the screw working surface of the inner conical screw element. k ₁₂ = 2 · π · n ₂ / n ₁ , k ₂ = 2 · π and thus k ₁ and k ₂ are related by the relation k ₁ / k ₂ = n ₂ / n ₁ or k ₁ = k ₂ · n ₂ / n ₁ .

Heat can be supplied to the gaseous working fluid in the heating part of the engine in various ways. This can be the burning of fuel mixed with air in the combustion chamber, and the radiant supply of heat from solar concentrators to internal heat exchangers, and the use of nuclear decay energy in replaceable heat cassettes. With any options for supplying heat, it is possible to increase the specific power of the device by raising the pressure of the working fluid circulating through it, in the first case due to turbocharging, in the second and third - by increasing the pressure in a closed gas circuit.

Claims (1)

A rotary cone-screw engine, containing inside and outside cone-screw elements located at an angle to each other, each of which has a heating section, as well as a discharge and expansion section, having screw working surfaces by which the elements contact each other in a closed space lines, forming a series of helical vesicular cavities isolated from each other, the volume and position of which change with a working change in the relative position of the elements, the number of visits of wines the working surface in the discharge section of any of the elements is equal to the number of entries of the screw working surface in its expansion section, the number of entries n _{2 of the} screw working surface of the outer element is one greater than the number of entries n _{1 of the} screw working surface of the inner element, characterized in that the inner and outer cone - screw elements are located in a fixed housing, rely on it through bearings and have the ability to make interconnected one-way rotation, sync the rotation of the conical screw elements is carried out by means of a gear transmission, the direction of winding the screw working surface in the discharge section of any of the conical screw elements coincides with the direction of winding the screw working surface in its expansion section, the winding of the screw working surfaces of the inner and outer conical screw elements coincide direction, spherical sections of helical work surfaces having a common central point, are generators, scaler When wound and rotated around the axes of the corresponding conical screw elements, the winding of the screw working surface of the discharge section of the external conical screw element contains at least one full revolution, the winding of the screw working surface of the expansion section of the outer conical screw element contains at least one full revolution.

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