RU2768138C1 - Method of converting thermal energy into mechanical energy of rotational movement and device for its implementation - Google Patents

Abstract

FIELD: heat power engineering; machine building.

SUBSTANCE: group of inventions relates to heat power engineering and machine building, namely to methods and devices for conversion of thermal energy into mechanical energy. Method consists in the fact that chambers 2 are alternately heated and cooled, which are filled with heat-sensitive working medium 4, walls 5 of which are heat-conducting and have, completely or partially, the shape of a heat exchange surface, redistributing the mass of liquid in rotor 1, creating a weight unbalance of rotor 1, which causes alternate movement of chambers 2 into zones of their heating and cooling. Chambers 2 are alternately heated and cooled, which are located along the circumference of wheel-shaped rotor 1 and are interconnected through inlet/outlet valves 5 or other shutoff inlet/outlet devices with formation in aggregate of an inner annular space inside rotor 1.

EFFECT: group of inventions is aimed at increasing efficiency of thermal energy conversion.

10 cl, 1 dwg

Description

The field of technology to which the invention belongs.

The invention relates to:

- to thermal power engineering, namely, to the conversion of thermal energy into another type of energy that is converted into useful work;

- to mechanical engineering, namely to the production of devices and installations for converting thermal energy into mechanical energy, capable of operating on any source of thermal energy, incl. on different types of fuel.

State of the art

From technical thermodynamics and the practice of creating and using heat engines, it is well known that a continuous process of converting heat into work can only be carried out by supplying heat to the working fluid, which, due to heating, expands and, due to the use of part of the supplied thermal energy, being in a gaseous state, does the job. Further, if the process follows a closed cycle, the working fluid is cooled to its original temperature (for example, a steam engine according to the Carnot cycle), or, if the process is not closed, the working fluid is discharged into the environment (for example, open cycle gas turbine engines).

The expansion of the working fluid due to its heating occurs linearly and in different directions. However, for the practical use of the work of expanding the working fluid, it is necessary to turn the process of linear expansion of the working fluid into a rotational mechanical movement of the working body of a heat engine.

There is a known method of converting thermal energy into mechanical energy of rotational motion and a device for its implementation in the form of a set of technical devices, including a steam turbine (Kirillin V.A., Sychev V.V., Sheindlin A.E. Technical thermodynamics. Moscow "Energoatomizdat" 1983 ).

In this method, the thermal energy obtained from the combustion of organic fuel is supplied to the working fluid (water) in a special device - a steam generator, then the evaporated working fluid in the form of steam is fed into a steam turbine, where the potential energy of the steam is converted into the kinetic energy of the high-speed movement of the steam, which, in turn, is converted into rotational motion of the turbine rotor. The rotational movement of the working body of the turbine (rotor) is achieved by organizing a high-speed curvilinear movement of the expanding working body through the system of turbine blades. After the turbine, the steam containing the thermal energy unused in the turbine is sent to the cooler-condenser, where it is condensed to the initial state of water, which is again supplied to the steam generator by a pump.

This method and devices for its implementation (steam generator, turbine, condenser, pump) are widely used in thermal power engineering.

However, this method and the main device for its implementation, the turbine, have the problem of using it at moderate and low temperatures: when operating on wet steam with the presence of a dropping liquid, the operating mode of the turbine flow path deteriorates sharply, as a result of which the internal efficiency of the turbine decreases, and this, in turn, , leads to a decrease in the effective efficiency of the entire installation (Kirillin V.A., Sychev V.V., Sheindlin A.E. Technical thermodynamics. Moscow "Energoatomizdat" 1983, p. 314).

A significant disadvantage of this method of devices for its implementation is their complexity.

An essential feature of this analogue, which coincides with the essential features of the claimed invention, is:

- the working fluid is supplied to the heating zone in a liquid state, evaporates in the heating zone, condenses in the cooling zone, and then, again, is fed into the heating zone in a liquid state.

Also known is a method for converting thermal energy into mechanical energy of rotational motion and a device for its implementation in the form of a reciprocating external combustion engine - a Sterling engine, incl. with a two-phase working fluid (Walker G. Machines operating on the Stirling cycle. Lane from English: -M .: Energy, 1978. - 152 s, ill.).

This method of converting thermal energy into mechanical energy of the rotational movement of the working body is implemented in a single device - a Stirling piston heat engine, and is carried out with the supply of heat to the working fluid from an external source through the wall of the technical device.

With all the existing variety of designs (single-piston and multi-piston) Stirling engines, the main structural elements of the device are: a cylinder (cylinders) with a heat supply zone, a heat removal zone, a heat regenerator, a piston (pistons) reciprocating in the cylinder, a crank or another mechanism for converting the reciprocating movement of the piston into the rotational movement of the working body.

In the working cylinder with a piston, thermal energy is converted into mechanical energy of the rectilinear movement of the piston, which, by means of a crank or other similar mechanism, is converted into mechanical energy of rotation of the working body of a heat engine.

High efficiency of energy transfer from the expanding working fluid to the piston is achieved at high pressures in the cylinders of the device, which requires the use of a complex system for sealing the zone of sliding contact between the piston and the cylinder.

A complex sealing system is required (in order to prevent losses of the working fluid due to leakage from the inside of the engine to the outside) and at the exit points of the working shaft, as well as auxiliary systems and communications from the inside of the engine to the outside.

The main disadvantage of this method of converting thermal energy into mechanical energy of the rotational movement of the working body and the device for its implementation - the Stirling piston engine is the complexity and high cost (Walker G. Machines operating on the Stirling cycle. Lane from English: - M .: Energy , 1978., p. 102).

Important problems (disadvantages) for Stirling engines are seals and fatigue failures, as a result of alternating stresses arising from the presence of a reciprocating movement of the working piston (Walker G. Machines operating on the Stirling cycle. Lane from English: -M. : Energy, 1978., p. 104).

The essential features of this analogue, which coincide with the essential features of the claimed invention, are:

- alternate heating and cooling of cylinders (chambers) filled with a heat-sensitive working fluid,

- the walls of the cylinders (chambers) are made heat-conducting, and have, in whole or in part, the shape of a heat exchange surface.

Also known is a method for converting thermal energy into mechanical energy of rotational motion and a device for its implementation in the form of a rotor filled with liquid, along the periphery of which there are chambers filled with a temperature-sensitive working fluid, separated from the liquid by a flexible partition (USSR Author's certificate 1100422, class F03G 7/ 06, published 06/30/84 .; US patent No. 4121420, class 60-531, published 1978; USSR Author's certificate 1302013, class F03G 7/06, published 04/07/87).

The conversion of thermal energy into mechanical energy of rotational motion is carried out here by alternating heating and cooling of chambers filled with a temperature-sensitive working fluid located on the periphery of a hollow rotor filled with liquid (heating zone on one side of the rotor, cooling zone on the other side), which causes a redistribution of the liquid mass in rotor when the volume of the chambers changes (the volume of the chambers in the heating zone increases due to the expansion of the working fluid when it is heated, and the liquid adjacent to these chambers is squeezed out into the central cavity of the rotor; the volume of the chambers in the cooling zone decreases due to the compression of the working fluid when it is cooled, and adjacent to cooled chambers, the peripheral space of the rotor is filled with liquid coming from the central cavity of the rotor), creates a weight imbalance of the rotor, and, as a result, causes the rotation of the rotor.

The change in the volume of the chambers during heating and cooling is due to the use of a flexible partition (chamber wall) that separates the heat-sensitive working fluid from the liquid in the rotor; the volume of the chambers changes due to the deformation of the flexible partition under the influence of expansion/compression of the working fluid in the chambers.

At the same time, the very impact of the working fluid on the transferred liquid is carried out through a flexible hermetic partition that separates the working fluid in the chambers from the liquid; and the movement of liquid from the peripheral sections of the rotor, adjacent to the chambers of the heating zone, to the peripheral sections of the rotor, adjacent to the chambers of the cooling zone, does not occur directly from the chamber to the chamber, but through the cavity (cavities) located in the center of the rotor, filled with liquid.

The technical device for implementing the method is a rotor filled with liquid, along the periphery of which there are chambers filled with a temperature-sensitive working fluid, separated from the liquid in the rotor by a flexible non-heat-conducting partition. The chambers are made in the form of heat exchangers, their walls facing the heating and cooling zones are made of a material with high thermal conductivity.

In order to expand the scope (according to the USSR Author's certificate 1100422, class F03G 7/06, published on 06/30/84), the rotor of the device is equipped with suction and discharge cavities separated by a sealed partition, equipped with radial partitions dividing its cavity into sealed compartments adjacent to the chambers, equipped with valves connecting the compartment with the suction and discharge cavities.

In order to increase the efficiency of work (according to the USSR Author's certificate 1302013, cl. F03G 7/06, published on 04/07/87), the rotor of the device is equipped with a cylindrical hollow collector, divided by a diametrical heat-insulating partition into two sealed cavities, one of which is an injection cavity, hydraulically connected to the compartments adjacent to the chambers located in the heating zone, and the other - suction - with compartments adjacent to the chambers located in the cooling zone.

This method and devices for its implementation are simple, but have significant drawbacks.

The disadvantages of this method and technical device are:

- limited degree of expansion of the working fluid in the chambers, due to the presence of a flexible partition that separates the working fluid from the moving fluid, which creates a mass imbalance;

- reduced energy transfer efficiency of the expanding/contracting working fluid of the transported fluid, due to the fact that the transfer is carried out through a flexible partition, which "takes" part of the energy for bending;

- reduced efficiency of energy transfer - expanding / contracting the working fluid of the transported fluid, due to the fact that the work of expansion / contraction is performed in a group of parallel operating chambers (with respect to the transported fluid) of the heating zone, and in a group of chambers of the cooling zone, where (in each group of chambers), uneven heating/cooling inevitably arises, and, accordingly, uneven pressure developed by the working fluid in the chambers of one group, which causes unproductive movement of a certain amount of working fluid in the rotor cavity within the heating zone, as well as within the cooling zone.

- reduced efficiency of the method due to the presence of a ballast mass of liquid in the central part of the hollow rotor, which does not participate in the conversion of thermal energy into mechanical energy of the rotational movement of the rotor (does not participate in the creation of a weight unbalance of the rotor), but requires energy for rotation;

- increased mass of the device due to the presence of essentially ballast liquid in the central part of the hollow rotor, which does not participate in the conversion of thermal energy into mechanical energy (does not participate in the creation of the weight unbalance of the rotor);

- low reliability of the device due to the presence of a flexible partition through which mechanical energy is transmitted from the working fluid, and which is subjected to alternating loads with significant deformations that threaten fatigue failure; as a result, increased costs are required for diagnostics, repair and replacement of the flexible partition.

The essential features of this analogue, which coincide with the essential features of the claimed invention, are:

- alternating heating and cooling of chambers filled with a heat-sensitive working fluid;

- redistribution of the mass of liquid in the device for implementing the method, with the creation of a weight imbalance;

- a device for implementing the method, containing a rotor with chambers;

- the walls of the chambers are made of heat-conducting (made of a material with high thermal conductivity), and have the shape of a heat-exchange surface.

This set of features, inherent in the last of the above analogues (USSR Author's certificate 1100422, class F03G 7/06, published 06/30/84 .; US patent No. 4121420, class 60-531, published in 1978; USSR Author's certificate 1302013, class F03G 7/06, published 04/07/87), is closest to the set of essential features of the invention, on the basis of which this analogue is selected as a prototype.

The aim of the invention is: improving the efficiency of the method of converting thermal energy into mechanical energy of rotational motion, increasing the efficiency of the technical device for its implementation

Disclosure of the essence of the invention

In the method for converting thermal energy into mechanical energy of rotational motion, including alternate heating and cooling of chambers filled with a temperature-sensitive working fluid, redistribution of the mass of liquid in the rotor of the device to implement the method, with the creation of a weight imbalance with alternate movement of the chambers into their heating and cooling zones, the following are provided: differences:

chambers are alternately heated and cooled, which are located around the circumference of the wheel-shaped rotor, communicated with each other through inlet/outlet valves or other shut-off inlet/outlet devices to form, in the aggregate, an internal annular space inside the rotor.

In addition, the proposed method has the following differences:

- a heat-sensitive working fluid is placed in the annular space formed by the chambers in the form of a liquid in an amount less than the capacity of the annular space, which ensures the formation of a U-shaped hydraulic seal in the lower part of the annular space, and a vapor-gas medium in the upper part, above the hydraulic seal; the supply of thermal energy (i.e. heating of the chambers) and the removal of thermal energy (i.e. cooling of the chambers) are carried out in the area of location of the chambers adjacent to opposite sides of the hydraulic seal: the heating zone on one side of the hydraulic seal, the cooling zone on the other side hydraulic shutter and from above the wheel-shaped rotor to the heating zone.

- the redistributed liquid that creates the weight imbalance is the working fluid in the liquid phase, the redistribution of the mass of the liquid with the creation of the weight imbalance occurs without changing the volume of the chambers and is carried out in the form of liquid overflowing through the annular space under the influence of the pressure difference of the vapor-gas medium on opposite sides of the U-shaped hydraulic seal ,

- the working fluid in the liquid phase, moves inside the annular space of the rotor by successively flowing from chamber to chamber; the working fluid is fed into the heating zone in a liquid state, evaporates in the heating zone, condenses in the cooling zone, and then, again, is fed into the heating zone in a liquid state;

- heating / cooling is carried out with at least one closed valve between the chambers above the liquid seal in the heating zone, with open valves located in the liquid, and at least one open valve between the chambers above the hydraulic seal in the cooling zone, and in compliance with the following valve opening/closing sequences when they pass through the heating and cooling zones during the rotation of the rotor:

the valve in the heating zone, which, during the rotation of the rotor, left the hydraulic sealing liquid towards its flow in the open state, closes when, at some distance from the liquid level in the hydraulic seal, the pressure of the vapor-gas medium under the valve (i.e., from the side of the hydraulic seal) began to exceed the pressure of the medium above valve; moving further with the rotation of the rotor from the heating zone to the cooling zone, the valve remains closed and opens when the pressure of the vapor-gas medium behind the valve (i.e. in the chamber behind the valve) is lower than the pressure of the vapor-gas medium in front of the valve (i.e. in the chamber in front of him); the valve enters the oppositely flowing hydraulic sealing liquid in the open state and remains open until the spatial position of the closing point is reached - after leaving the hydraulic sealing liquid in the heating zone.

- the amount of the working fluid placed in the annular space in the form of a liquid, is selected from the condition: moreover, being concentrated in the lower part of the annular space completely overlaps the cross section of the annular space, but not more than half the capacity of the annular space;

- as a temperature-sensitive working fluid, a liquid is used in the form of water, mercury, or any substance that is in a liquid state under operating conditions and has, under these conditions, a saturated vapor pressure sufficient to create a difference in the heights of the liquid levels in a U-shaped hydraulic seal of at least the value of the diameter wheel-shaped rotor.

- after placing the working fluid in the form of a liquid in the annular space, from the volume of this space not filled with liquid, the air or nitrogen located there, or another gas inert with respect to the working fluid, is removed (for example, by vacuum or steam blowing), to the residual amount that, under operating conditions, being concentrated in the volume of the chamber adjacent to the hydraulic seal in the cooling zone, will, in combination with the pressure of the saturated steam of the working fluid, create in this chamber the pressure specified by the project.

In the device for converting thermal energy into mechanical energy of rotational motion, containing a rotor with chambers filled with a heat-sensitive working fluid, the walls of which are made heat-conductive and have, in whole or in part, the shape of a heat exchange surface, the following differences are provided:

the rotor has a wheel-shaped form, the chambers are located around the circumference of the rotor, communicated with each other through the inlet/outlet valves or other locking inlet/outlet devices to form, in the aggregate, the inner annular space of the wheel-shaped rotor.

In addition, the proposed device has the following difference:

- the number of chambers located around the circumference of the rotor - at least four.

Between the set of essential features of the claimed object and the achieved technical result in the form of increasing the efficiency of the method of converting thermal energy into mechanical energy of rotational motion and increasing the efficiency of the technical device for its implementation, there is the following causal relationship.

Namely, in terms of the method.

The set of features indicated in the claimed object indicates that in the proposed method, the conversion of thermal energy into mechanical energy of rotational motion is carried out by heating and cooling chambers located not along the periphery of a hollow rotor filled with liquid, but along the circumference of a wheel-shaped rotor that does not have liquid filled cavities. The absence of the ballast mass of liquid in the rotor cavity eliminates the energy costs present in the prototype for the rotation of the ballast mass, respectively, the efficiency of energy conversion in the proposed method, on this basis, is higher than the efficiency of the prototype.

The set of features indicated in the claimed object indicates that in the proposed method, the potential energy of pressure of the working fluid in the gas-vapor phase is transferred to the liquid (in the proposed method - to the working fluid in the liquid phase) directly, and not through a flexible partition, as in the prototype. The absence of a flexible partition eliminates the energy costs present in the prototype for bending the flexible partition, respectively, the efficiency of energy conversion in the proposed method, on this basis, is higher than the efficiency of the prototype.

The set of features indicated in the claimed object indicates that in the proposed method, the work of expanding / compressing the working fluid is not performed in the form of a limited (technical possibility of flexible partitions) changes in the volume of the chambers during their heating / cooling, but is realized in the form of a complete displacement of liquid from one cameras to another. The expansion/compression of the working fluid not limited by flexible partitions in the proposed method allows converting a larger amount of thermal energy into expansion work, respectively, the energy conversion efficiency in the proposed method, on this basis, is higher than the efficiency of the prototype.

The set of features indicated in the claimed object indicates that in the proposed method, the work of expansion / contraction of the working fluid is performed not in a group of parallel operating (with respect to the moving fluid) chambers of the heating zone, but in a group of chambers of the cooling zone, where (in each group chambers), uneven heating / cooling inevitably occurs, causing unproductive movement of the working fluid in the rotor cavity within the heating zone, as well as within the cooling zone, but takes place in sequentially located chambers, which eliminates unproductive movement of the liquid, but ensures its purposeful movement along the annular space strictly from the chambers of the heating zone to the chambers of the cooling zone. Accordingly, the efficiency of energy conversion in the proposed method, on this basis, is higher than the efficiency of the prototype.

The set of features indicated in the claimed object indicates that in the proposed method, the work of expansion / compression of the working fluid is converted into mechanical energy of the rotational motion of the rotor, which does not have a ballast mass of liquid in the central part of the hollow rotor, which does not participate in the conversion of thermal energy into mechanical energy rotational movement of the rotor (does not participate in the creation of the weight unbalance of the rotor), but requires energy for rotation. Accordingly, the efficiency of energy conversion in the proposed method, on this basis, is higher than the efficiency of the prototype.

Namely, in terms of the device.

The set of features indicated in the claimed object indicates that in the proposed technical device, unlike the prototype, the rotor with working chambers located along its perimeter does not have a cavity in the central part filled with a liquid that does not participate in energy conversion (not involved in creating weight unbalance of the rotor), but increasing the mass of the technical device in working condition. For this reason, the working mass of the proposed technical device is less than the mass of the prototype, respectively, the efficiency of the proposed device is higher than the efficiency of the prototype.

The set of features indicated in the claimed object indicates that in the proposed technical device, namely in the chambers, unlike the prototype, there are no flexible partitions (through which mechanical energy is transmitted from the working fluid in the prototype), which are subjected to alternating loads during operation with significant deformations that pose a threat of fatigue failure, and therefore require increased costs for diagnostics, repair, and replacement. Due to this circumstance, the claimed technical device bears lower risks of fatigue failure than the prototype, does not require, like the prototype, increased costs for diagnostics, repair, replacement, and therefore, the efficiency of the proposed device is higher than the efficiency of the prototype.

Brief description of the drawings

The technical essence and principle of operation of the proposed method and device for its implementation are illustrated by the following drawing (illustrating figure), which shows a device for implementing the method, in working condition; in section (section along the rotor, - perpendicular to the axis of rotation).

The numbers on the figure indicate the following elements of the technical device, as well as the heating and cooling zones of the chambers:

1 - rotor;

2 - cameras;

3 - valves or other shut-off inlet / outlet devices between the chambers;

4 - working fluid in the liquid phase;

5 - chamber wall;

6 - chamber heating zone;

7 - chamber cooling zone.

Bold arrows in the figure indicate: the direction of rotation of the rotor, and the direction of fluid flow through the inner annular space of the wheel-shaped rotor.

The inscription "Open" shows the valves between the chambers that are in the open state. The inscription "Closed" indicates the valve is closed.

Implementation of the invention

The explanatory figure shows a device for implementing the method in the operating state - when heat is supplied to the working fluid in the heating zone and heat is removed from the working fluid in the cooling zone.

The device contains a wheel-shaped rotor 1, with chambers 2 located around the circumference of the rotor 1, which communicate with each other through the inlet/outlet valves or other locking inlet/outlet devices 3, and which, in aggregate, form the inner annular space of the wheel-shaped rotor 1.

In the annular space formed by the chambers, a working fluid is placed in the liquid phase 4, for example, water or mercury, etc. in such an amount that the liquid concentrated in the lower part of the annular space completely covers the annular space section, but not more than half of the annular space capacity.

With such filling of the inner annular space with a liquid working fluid, a U-shaped hydraulic seal is formed in the lower part of the annular space, and in the upper part - above the hydraulic seal (in chambers not filled with liquid), a vapor-gas medium is formed, consisting of liquid vapor (thermosensitive working fluid in the vapor-gas phase ) and the residual content of air or gas contained inside the chambers before they were filled with a heat-sensitive working fluid.

The walls of the chambers 5 are made heat-conducting and have, in whole or in part, the shape of a heat exchange surface.

Valves or other locking devices through which the chambers are connected into a single annular space are designed to allow the passage of the internal medium in one direction and block the movement of the medium in the opposite direction (for example, as a check valve).

The device works as follows.

With at least one closed valve 3 between the chambers 2 above the water seal in the heating zone, with open valves 3 located in the liquid and above the liquid in the chamber of the cooling zone, the working fluid is heated inside the chamber 2 in the heating zone, and the working fluid is cooled in the chambers 2 in the cooling zone.

When heated, in chamber 2, located in the heating zone, the working fluid evaporates from the liquid (passes from the liquid phase into the gaseous phase both directly from the surface of the hydraulic seal level and from the surface of the inner walls of the chamber wetted with liquid), the pressure of the vapor-gas phase in the volume between the level liquid in the hydraulic seal and the closed valve 3 above the hydraulic seal increases, and the hydraulic seal liquid is squeezed out down the chamber. And further along the annular space into the chamber of the cooling zone.

In the cooling zone in the chambers 2, the gaseous working fluid condenses due to cooling, as a result of which the pressure in the chambers 2 decreases and the hydraulic sealing liquid is sucked into the chamber 2, the cooling zone.

The movement of the mass of fluid (the working fluid in the liquid phase) 4 inside the rotor 1, - from the chamber of the heating zone to the chamber of the cooling zone, leads to the appearance of a difference in the levels of the liquid in the hydraulic seal, as a result of which there is a weight imbalance of the rotor 1, and it, the rotor 1, rotates .

When the rotor 1 rotates, new chambers 2 enter the heating and cooling zones, and the process is repeated.

The continuity of the rotation process is ensured

by opening/closing the corresponding valves between the chambers, while maintaining the above state: valve 3 between the chambers above the water seal in the heating zone is closed, the valves located in the liquid and above the liquid in the chamber of the cooling zone are open.

Opening / closing of the corresponding valves between the chambers during the rotation of the rotor is carried out from an external drive (electric drive, pneumatic drive) at the signal of pressure sensors, if the device is equipped with such valves of a known design and sensors of a known design, or under the influence of a differential pressure of the medium naturally occurring in the annular space of the rotor during the rotation of the rotor, if the device is equipped with check valves of a known design.

To ensure the required performance of a technical device, it must be prepared, in accordance with the distinctive position of the proposed method for converting thermal energy into mechanical energy of rotational motion:

- after placing the working fluid in the form of a liquid in the annular space, from the volume of this space not filled with liquid, the air or nitrogen located there, or another gas inert with respect to the working fluid, is removed (for example, by vacuum or steam blowing), to the residual amount that, under operating conditions, being concentrated in the volume of the chamber adjacent to the hydraulic seal in the cooling zone, will, in combination with the pressure of the saturated steam of the working fluid, create in this chamber the pressure specified by the project.

The need to remove nitrogen, or another gas inert with respect to the working fluid, from the annular space arises when the air in the technical device was previously replaced with nitrogen, or another gas inert with respect to the working fluid. Such a replacement is necessary if a working fluid (for example, mercury) is used in a technical device that is not resistant to the chemical action of oxygen in the air.

Replacing an oxidizing environment with an inert one, in order to eliminate the negative chemical effect of atmospheric oxygen on substances used inside a technical device, is well known to specialists from the state of the art, and is not a new procedure.

The preparation itself in the form of removing air or nitrogen, or another gas inert with respect to the working fluid, from the annular space of the rotor is necessary due to the fact that the chambers filled with the vapor-gas medium in the heating zone, moving during the rotation of the rotor from the heating zone to the cooling zone is carried into the cooling zone and the vapors of the working fluid, which, when condensed, provide a reduction in pressure in the chambers of the cooling zone, but also the air / gas initially present in the annular space of the rotor. Which does not condense in the cooling zone, but, accumulating in the chamber adjacent to the hydraulic seal in the cooling zone, creates an increased pressure in this chamber, preventing the movement of the hydraulic barrier fluid and, accordingly, preventing the creation of rotor unbalance.

Another condition for ensuring the required performance of the technical device, which is indicated in the distinguishing features of the invention, is:

- the number of chambers located around the circumference of the rotor - at least four.

This constructive difference is based on the fact that, in accordance with the claimed method, there should be at least one chamber in the heating zone with a high pressure of the medium, where the working fluid expands and from where the hydraulic barrier liquid is squeezed out; there must be at least one chamber in the cooling zone with a low pressure of the medium, where the working fluid is compressed and where the hydraulic barrier fluid is drawn; there should be a part of the annular space between them at the bottom to accommodate the fluid that creates the water seal. But, there must be at least one more chamber in the cooling zone, in the upper part of the annular space between the high pressure chamber, from where the sealing fluid is squeezed out, and the low pressure chamber, where the sealing fluid is drawn in. Which, leaving during the rotation of the rotor from the heating zone with a high pressure of the vapor-gas medium with closed valves, in the process of moving through the cooling zone, provides a decrease in the pressure of the vapor-gas medium inside the chamber to a level close to the pressure in the chamber of the cooling zone, which draws in the hydraulic barrier liquid. That ensures the exclusion of pressure surges in the chambers of the cooling zone, when the valve is opened, approaching the water seal in the cooling zone. And thus ensures the smooth movement of the hydraulic barrier fluid and, accordingly, the smooth rotation of the rotor.

The above restriction on filling the annular space "no more than half the capacity of the annular space" is dictated by the fact that if this restriction is not observed, in the annular space of the rotor from the side of the heating zone in any modes, even at the maximum liquid level in the hydraulic seal from the side of the cooling zone, there will be there is an excessive amount of, in fact, ballast liquid, which will oppose the rotation of the rotor.

The use of the invention allows the conversion of thermal energy into mechanical energy of the rotary motion of the rotor.

The possibility of carrying out the claimed invention is shown by the following examples 1,2,3. As well as the test results of a model of a heat-and-power gravitational wheel (example 4).

Example 1

Technical device. Construction, design parameters.

The wheel-shaped rotor, with an outer diameter of 5 m, with 6 chambers with an inner diameter of 0.3 m, communicating with each other through shut-off inlet / outlet devices (valves).

Shut-off inlet/outlet devices (valves) are of a well-known design; they are brought into the appropriate position by an electric drive from an external source, according to a signal from pressure sensors before and after the valve.

The internal volume of one chamber is 0.17 m3. The total volume (capacity) of the inner annulus formed by the chambers is 1.02 m3. The inner annular space is filled with a liquid working fluid - water by 45% of the total capacity. Residual volume of liquid-free annulus (55% of capacity) 0.56 m3. The volume of water (the working fluid in the liquid phase) forming a water seal in the lower part of the annulus is 0.46 m3, and the mass (taking into account the water density of 1000 kg/m3) is 460 kg. Including: the volume of liquid required to completely cover the section of the annular space at the bottom of the annular space 0.15 m3, weight - 150 kg; the volume of liquid in the hydraulic seal is above the level at which the liquid completely blocked the cross section of the annular space 0.46-0.15=0.31 m3, weight - 310 kg.

The maximum unbalance of the rotor, achievable under the condition of complete concentration of this amount of liquid (0.31 m3, weight - 310 kg) on one side of the hydraulic seal, above the level of complete overlapping of the section of the annular space below by the liquid, is 310 kg.

The maximum height difference of liquid levels in the hydraulic seal, when this amount of liquid (0.31 m3, weight - 310 kg) is concentrated on one side of the hydraulic seal (in accordance with the geometry of the annular space) is -4 m.

Accordingly, the design pressure drop between the chambers of the heating and cooling zone required to provide the specified height difference of liquid levels in the hydraulic seal is -4 m of water column, or, in the SI system, 39.24 kPa.

Inside the annular space before the water was placed in it, there was air. After water is placed in the annular space and a hydraulic seal is formed in the lower part of the annular space, a vapor-air medium is self-formed above the hydraulic seal.

The design working pressure of the steam-air medium in the chamber of the cooling zone is 101.3 kPa (taken equal to atmospheric pressure).

Design pressure of saturated water vapor in the chamber of the heating zone (higher than the design pressure in the chamber of the cooling zone by the value of the design pressure difference between the chambers) 101.3+39.24=140.54 kPa.

The design temperature of the working fluid in the heating zone chamber, providing this (140.24 kPa) saturated steam pressure in the heating zone chamber, according to known data (Pavlov K.F., Romankov P.G., Noskov A.A. Examples and tasks for Course of Processes and Apparatuses of Chemical Technology Textbook for High Schools/Edited by Corresponding Member of the Academy of Sciences of the USSR PG Romankov, L.: Chemistry, - 1987, p. -382 K.

The design temperature of the working fluid in the chamber of the cooling zone adjacent to the hydraulic seal (accepted taking into account the characteristics of the cooler), +40 C, or, in degrees Kelvin, 313 K.

The pressure of saturated water vapor at this temperature, according to known data (Pavlov K.F., Romankov P.G., Noskov A.A. Examples and tasks in the course of processes and apparatuses of chemical technology. Textbook for universities / Ed. Chl. Correspondent of the Academy of Sciences of the USSR P.G. Romankova, L.:, Chemistry, -1987, p. 549) 7.4 kPa.

With a design pressure in the cooling zone chamber of 101.3 kPa, and a pressure of the working fluid - saturated water vapor in it of 7.4 kPa, the design partial air pressure in the cooling zone chamber: 101.3 kPa - 7.4 kPa = 93.9 kPa.

The design volume fraction of air in the chamber adjacent to the hydraulic seal in the cooling zone (numerically equal to the ratio of the partial air pressure to the total pressure in the chamber): 93.9 kPa / 101.3 kPa = 0.927.

The design amount (mass) of air in the chamber adjacent to the hydraulic seal in the cooling zone (calculated through the density of air under operating conditions in the chamber, - 1.13 kg / m3, the volume of the chamber, - 0.17 m3, and the volume fraction of air in the chamber, - 0.927) 0.178 kg.

This value is also the design amount of air that needs to be left in the annular space of the rotor. And which, under operating conditions, being concentrated in the chamber adjacent to the hydraulic seal in the cooling zone, will, in combination with the pressure of the saturated steam of the working fluid, create a design working pressure of 101.3 kPa in this chamber.

Preparation of a technical device for work.

Before starting work (after placing the working fluid in the form of water into the annular space), from the volume of the annular space free from liquid (0.56 m3), which is initially under pressure equal to atmospheric pressure - 101.3 kPa, is removed by connecting to an external vacuum lines (by vacuum) the air there. Air is evacuated by vacuum until the residual pressure in the liquid-free annulus is 24.8 kPa.

It is at such a residual pressure that the residual amount of air in the annulus will be calculated as 0.178 kg (calculated through the density of air in a vacuum space - 0.317 kg / m3 and the volume of space - 0.56 m3), which corresponds to the required design residual amount of air in the annulus .

Operation of a technical device. Technical indicators

The valves between the chambers of the annular space are brought into working position: the valve 3 between the chambers above the hydraulic seal in the heating zone is closed, the valves 3 located in the liquid and above the liquid in the chamber of the cooling zone are open.

The heaters in the heating zone and coolers in the cooling zone are switched on.

When heated, in chamber 2 located in the heating zone, the working fluid evaporates from the liquid, the pressure of the vapor-gas phase in the volume between the liquid level in the hydraulic seal and the closed valve 3 above the hydraulic seal increases (from the initial, set

evacuation), as a result of which the hydraulic sealing liquid is squeezed down the chamber, and further into the chamber of the cooling zone.

The pressure in the cooling zone chamber, initially low, set by vacuuming, increases due to the compression of the vapor-air medium by the hydraulic barrier liquid (liquid phase) squeezed out of the heating zone chamber.

The movement of the mass of liquid 4 inside the rotor leads to the emergence of a weight imbalance of the rotor 1, and it, the rotor 1, starts to rotate.

The continuity of the rotation process is ensured

by opening/closing the corresponding valves between the chambers, while maintaining the above state: valve 3 between the chambers above the water seal in the heating zone is closed, valves 3 located in the liquid and above the liquid in the chamber of the cooling zone are open.

At the beginning of the rotation process, when the pressure of the medium in the annular space, and, incl. in the cooling zone chamber, due to pre-evacuation, is initially low, and the counterpressure from the side of the cooling zone chamber is small, the design pressure drop required to create an unbalance of the rotor between the chambers of the heating and cooling zone (4 m of water column, or, in the SI system, 39.24 kPa.) is created at a relatively low total pressure in the annular space of the rotor. Further, during the rotation of the rotor, when chambers moved from the heating zone with increased pressure and with the content of non-condensable air enter the cooling zone, the counterpressure in the chamber of the cooling zone increases. The increased back pressure from the side of the chamber of the cooling zone is overcome by a corresponding increase in pressure in the chamber of the heating zone, provided by the supply of heat to the working fluid in the heating zone.

With the complete transfer of all residual air into the chamber of the cooling zone, the process stabilizes at the design parameters: pressure in the chamber of the cooling zone is 101.3 kPa, pressure in the chamber of the heating zone at maximum load (with a maximum height difference of liquid levels in the hydraulic seal = 4 m), design, - 140.54 kPa; the temperature of the working fluid in the cooling zone is 40 C, in the heating zone 109 C.

The maximum unbalance of the rotor, while - 310 kg.

In accordance with the geometry of the wheel-shaped rotor, the center of gravity of the fluid that creates the unbalance of the rotor, with the specified parameters, is located at a distance of 2 m horizontally from the center of the rotor.

Torque on the rotor axis, determined through the product of the force on the shoulder (distance from the axis of rotation to the vertical of gravity): 310 kg * 2 m = 620 kg * m.

The developed power can be determined through the product of the force and the speed of its movement.

The speed of rotation of the rotor is predetermined by the speed of movement of the liquid through the annular space inside it, under the influence of the pressure difference on different sides of the hydraulic seal.

The rate of pressure movement of the liquid can be taken on the basis of the values of the velocities taken in the calculation of industrial pressure pipelines (Pavlov K.F., Romankov P.G., Noskov A.A. Examples and tasks in the course of processes and apparatuses of chemical technology. Textbook for universities / Under the editorship of Corresponding Member of the Academy of Sciences of the USSR P. G. Romankov, L.:, Chemistry, - 1987, p. 17), within 0.5-2.5 m / s.

When the speed of the fluid flow through the annular space inside the rotor is equal to 0.5 m/s, the linear speed of rotation of the rotor, respectively, will be 0.5 m/s.

At such a speed of rotation of the rotor, the developed power (calculated through the product of the gravity force of the unbalance and the speed of its movement) is estimated by the value: 310 kg * 0.5 m / s = 155 kg * m / s. Or, in SI: 1.519 kW

The thermal efficiency of the thermal energy conversion cycle, calculated by the well-known formula (Kirillin V.A., Sychev V.V., Sheindlin A.E. Technical thermodynamics. Moscow "Energoatomizdat" 1983, p. 54), through the ratio of temperatures of the working fluid (temperature difference between hot and cold working fluid, in degrees Kelvin, divided by the temperature of the hot working fluid, in degrees Kelvin):

Efficiency=(382-313)/382=0.18 or 18%

Transfer of the mechanical energy of the rotation of the rotor to the working body of the energy consumer can be carried out by placing the rotor on the shaft, in the center of rotation of the rotor, with the connection of this shaft to the shaft of the energy consumer.

Example 2

Technical device. Construction, design parameters.

Wheel-shaped rotor, outer diameter 10 m, with 6 chambers, inner diameter 0.5 m, communicating with each other through shut-off inlet/outlet devices (valves).

Shutoff inlet / outlet devices - check valves of known design (normally closed), are brought into the appropriate position by the pressure drop across the valve, which naturally occurs in the process of heating / cooling the working fluid; the differential required to drive the valves is negligible compared to the operating pressure differential between the chambers in the heating and cooling zone in this example; in this connection, in the form of losses in the creation of a working level difference in the hydraulic seal, it is not taken into account.

The internal volume of one chamber is 0.973 m3. The total volume (capacity) of the inner annulus formed by the chambers is 5.84 m3. The inner annular space is filled with a liquid working fluid - mercury - 45% of the total capacity. Residual liquid-free annular space (55% of capacity) 3.212 m3. The volume of mercury (working fluid in the liquid phase), which forms a water seal in the lower part of the annular space, is 2.628 m3, and the mass (taking into account the density of mercury is 13600 kg/m3) is 35740 kg. Including: the volume of liquid required to completely cover the section of the annular space at the bottom of the annular space 0.88 m3, weight - 11970 kg; the volume of liquid in the hydraulic seal is above the level at which the liquid completely blocked the cross section of the annular space 1.748 m3, weight - 23770 kg.

The maximum unbalance of the rotor, achievable under the condition of full concentration of this amount of liquid on one side of the hydraulic seal, above the level of complete overlapping of the section of the annular space below by the liquid, is 23770 kg.

The maximum height difference of the liquid levels in the hydraulic seal, in this case (in accordance with the geometry of the annular space in the example under consideration) is 8.1 m.

Accordingly, the design pressure drop between the chambers of the heating and cooling zone required to provide the specified height difference of liquid levels in the hydraulic seal is 8.1 m of mercury or in the SI system, 1079 kPa.

Nitrogen was present inside the annular space before mercury was placed in it. After mercury was placed in the annular space and a water seal was formed at the bottom, a vapor-gas medium (nitrogen + mercury vapor) was self-formed above the water seal.

The design working pressure of the vapor-gas medium in the chamber of the cooling zone is 101.3 kPa (taken equal to atmospheric pressure).

Design pressure of saturated mercury vapor in the chamber of the heating zone (higher than the design pressure in the chamber of the cooling zone by the value of the design pressure difference between the chambers) 101.3 kPa + 1079 kPa = 1180.3 kPa.

The design temperature of the working fluid (mercury) in the heating zone chamber, providing this (1180.3 kPa) saturated steam pressure in the heating zone chamber, according to known data (Volkov. A.I., Zharsky. I.M. Big chemical reference book. - M: Soviet school, 2005, p. 424) 532 C, or, in degrees Kelvin, - 805 K.

The design temperature of the working fluid in the chamber of the cooling zone adjacent to the hydraulic seal (accepted taking into account the properties of mercury vapor and the characteristics of the cooler), +100 C, or, in degrees Kelvin, 373 K.

The pressure of saturated mercury vapor at this temperature, according to known data (Volkov. A.I., Zharsky. I.M. Big chemical reference book. - M: Soviet school, 2005, p. 424) 0.037 kPa.

With a design pressure in the cooling zone chamber of 101.3 kPa, and a pressure of the working fluid - saturated mercury vapor in it 0.037 kPa, the design partial pressure of nitrogen in the cooling zone chamber adjacent to the hydraulic seal: 101.3 kPa - 0.037 kPa =. 101.26 kPa

The design volume fraction of nitrogen in the chamber adjacent to the hydraulic seal in the cooling zone (numerically equal to the ratio of the partial pressure of nitrogen to the total pressure in the chamber): 101.26 kPa / 101.3 kPa = 0.9996.

The design amount (mass) of nitrogen in the chamber adjacent to the hydraulic seal in the cooling zone (calculated through the density of nitrogen under operating conditions in the chamber, - 0.915 kg / m3, the volume of the chamber, - 0.973 m3, and the volume fraction of nitrogen in the chamber, - 0.9996 ), 0.89 kg.

This value is also the design amount of nitrogen that must be left in the annular space of the rotor. And which, under operating conditions, being concentrated in the chamber adjacent to the hydraulic seal in the cooling zone, will, in combination with the pressure of the saturated steam of the working fluid, create a design working pressure of 101.3 kPa in this chamber.

Preparation of a technical device for work.

Before starting work (after placing the working fluid in the form of mercury into the annular space), the volume of the annular space free from liquid (3.212 m3), which is initially under pressure equal to atmospheric pressure, is removed by connecting to an external vacuum line (by vacuuming) the nitrogen located there . Nitrogen is pumped out with vacuum until the residual pressure in the liquid-free annulus is 22.7 kPa.

It is at such a residual pressure that the residual amount of nitrogen in the annular space will be calculated by the value (calculated through the density of nitrogen in a vacuum space, - 0.28 kg / m3, and the volume of space - 3.212 m3) 0.89 kg, which corresponds to the required design residual the amount of nitrogen in the annulus.

Operation of a technical device.

Technical indicators

Due to the fact that the technical device is equipped with shut-off inlet / outlet devices in the form of check valves of a known design, which are closed in the normal position and brought to the open position by a pressure drop across the valves naturally occurring during the process of heating / cooling the working fluid, special preparation - valve actuation in working position is not required.

The heaters in the heating zone and coolers in the cooling zone are switched on.

When heated, in chamber 2 located in the heating zone, with the check valve 3 closed above the hydraulic seal, the working fluid evaporates from the liquid, the pressure of the gas-vapor medium in the volume between the liquid level in the hydraulic seal and the closed valve above the hydraulic seal increases (from the initial one set by vacuuming). When the pressure rises to the level of opening of the check valves, the valves 3 in the liquid open and the hydraulic sealing liquid is squeezed out down the chamber, and further into the chamber of the cooling zone.

The pressure in the cooling zone chamber, initially low, set by vacuuming, increases due to the compression of the gas-vapor medium by the hydraulic sealing liquid (liquid phase) squeezed out of the heating zone chamber. The increased pressure opens the valve above the liquid in the chamber of the cooling zone.

The movement of the fluid mass inside the rotor leads to the appearance of a weight imbalance of the rotor, and it, the rotor, begins to rotate.

The continuity of the rotation process is ensured by opening / closing the corresponding valves between the chambers, maintaining the above state: valve 3 between the chambers above the hydraulic seal in the heating zone is closed, valves 3 located in the liquid and above the liquid in the chamber of the cooling zone are open.

At the beginning of the rotation process, when the pressure of the medium in the annular space, and, incl. in the chambers of the cooling zone, due to pre-evacuation, initially low, and the back pressure from the side of the chamber of the cooling zone is small, the design pressure drop required to create an unbalance of the rotor between the chambers of the heating and cooling zone (8.1 mHg, or, in the SI system 1079 kPa ) is created at a relatively low total pressure in the annulus of the rotor. Further, during the rotation of the rotor, when chambers moved from the heating zone with increased pressure and with the content of non-condensable nitrogen enter the cooling zone, the back pressure in the cooling zone chamber increases. The increased back pressure from the side of the cooling zone chamber is overcome by a corresponding increase in pressure in the heating zone chamber provided by the supply of heat to the working fluid in the heating zone.

With the complete transfer of all residual nitrogen to the cooling zone chamber adjacent to the hydraulic seal, the process stabilizes at the design parameters: the pressure in the cooling zone chamber adjacent to the hydraulic seal is 101.3 kPa, the pressure in the heating zone chamber at maximum load (at the maximum height difference of liquid levels in the hydraulic seal = 8.1 m Hg) design, - 1180.3 kPa; the temperature of the working fluid in the cooling zone is 100 C, in the heating zone 532 C.

The maximum unbalance of the rotor, while - 23770 kg.

In accordance with the geometry of the wheel-shaped rotor, the center of gravity of the fluid that creates the unbalance of the rotor, with the specified parameters, is located at a distance of 4.02 m horizontally from the center of the rotor.

Torque on the rotor axis, determined through the product of the force on the shoulder (distance from the axis of rotation to the vertical of gravity): 23770 kg * 4.0 2 m = 95555 kg * m.

The developed power can be determined through the product of force times the speed of movement.

The speed of rotation of the rotor is predetermined by the speed of movement of the liquid through the annular space inside it, under the influence of the pressure difference on different sides of the hydraulic seal.

The rate of pressure movement of the liquid can be taken on the basis of the values of the velocities taken in the calculation of industrial pressure pipelines (Pavlov K.F., Romankov P.G., Noskov A.A. Examples and tasks in the course of processes and apparatuses of chemical technology. Textbook for universities / Under the editorship of Corresponding Member of the Academy of Sciences of the USSR P. G. Romankov, L.:, Chemistry, - 1987, p. 17), within 0.5-2.5 m / s.

When the speed of the fluid flow through the annular space inside the rotor is equal to 0.5 m/s, the linear speed of rotation of the rotor, respectively, will be 0.5 m/s.

At such a rotor speed, the developed power is estimated by the value: 23770 kg * 0.5 m / s = 11885 kg * m / s. Or, in SI: 116.5 kW,

The thermal efficiency of the thermal energy conversion cycle, calculated by the well-known formula (Kirillin V.A., Sychev V.V., Sheindlin A.E. Technical thermodynamics. Moscow "Energoatomizdat" 1983, p. 54), through the ratio of temperatures of the working fluid (temperature difference between hot and cold working fluid, in degrees Kelvin, divided by the temperature of the hot working fluid, in degrees Kelvin):

Efficiency=(805- 373)/805=0, 53 or 53%

Transfer of the mechanical energy of rotation of the rotor to the working body of the energy consumer can be carried out by placing the rotor on the support rollers, with the connection of the drive roller to the shaft of the energy consumer.

Example 3

Technical device. Construction, design parameters.

The wheel-shaped rotor, with an outer diameter of 1.5 m, with 6 chambers with an inner diameter of 0.05 m, communicating with each other through shut-off inlet / outlet devices (valves).

Shutoff inlet / outlet devices between the chambers - check valves of a known design (normally closed), are brought into the appropriate position by a pressure drop across the valve naturally occurring in the process of heating / cooling the working fluid; differential required to drive (open) the valve - 50 mm w.st.

The internal volume of one chamber is 0.00148 m3 = 1.48 liters. The total volume (capacity) of the inner annular space formed by the chambers is 0.0088 m3 = 8.8 liters. The inner annular space is filled with a liquid working fluid - water by 40% of the total capacity. Residual volume of liquid-free annulus (60% of capacity) 0.0053 m3 = 5.3 liters. The volume of water (the working fluid in the liquid phase) forming a water seal in the lower part of the annulus is 0.0035 m3 = 3.5 l, the mass (taking into account the water density of 1000 kg/m3) is 3.5 kg. Including: the volume of liquid required to completely cover the section of the annular space at the bottom of the annular space 1.1 l, weight - 1.1 kg; the volume of liquid in the hydraulic seal is above the level at which the liquid completely blocked the cross section of the annular space 2.4 l, weight - 2.4 kg.

The maximum unbalance of the rotor, achievable under the condition of complete concentration of this amount of liquid (2.4 l, weight - 2.4 kg) on one side of the hydraulic seal, is above the level at which the liquid completely overlaps the section of the annular space below with the liquid - 2.4 kg.

The maximum height difference of liquid levels in the hydraulic seal, while (in accordance with the geometry of the annular space) - 0.98 m (980 mm).

The design pressure drop between the chambers of the heating and cooling zone, required for the operation of the technical device, is the sum of this level difference, which ensures the unbalance of the rotor, and the differential required to drive (open) five valves (four in the liquid and one above the liquid in the cooling zone chamber) . Taking into account the required pressure drop across each valve of 50 mm w.st., the design pressure drop between the chambers of the heating and cooling zone is calculated as: 980 mm + 50 mm * 5 = 1230 mm w.st. Or in the SI system 12.05 kPa.

Inside the annular space before the water was placed in it, there was air. After water is placed in the annular space and a hydraulic seal is formed at the bottom, a vapor-air medium is self-formed above the hydraulic seal.

The design working pressure of the steam-air medium in the chamber of the cooling zone is 101.3 kPa (taken equal to atmospheric pressure).

Design pressure of saturated water vapor in the chamber of the heating zone (higher than the design pressure in the chamber of the cooling zone by the value of the design pressure drop between the chambers) 101.3+12.05 kPa=113.35 kPa.

The design temperature of the working fluid in the heating zone chamber, providing this (113.35 kPa) saturated steam pressure in the heating zone chamber, according to known data (Pavlov K.F., Romankov P.G., Noskov A.A. Examples and tasks for Course of Processes and Apparatuses of Chemical Technology Textbook for High Schools/Edited by Corresponding Member of the Academy of Sciences of the USSR PG Romankov, L.: Chemistry, - 1987, p. 548) 104 C, or, in degrees Kelvin, -384 K..

The design temperature of the working fluid in the chamber of the cooling zone adjacent to the hydraulic seal (accepted taking into account the characteristics of the cooler), +50 C, or, in degrees Kelvin, 323 K.

The pressure of saturated water vapor at this temperature, according to known data (Pavlov K.F., Romankov P.G., Noskov A.A. Examples and tasks in the course of processes and apparatuses of chemical technology. Textbook for universities / Ed. Chl. Correspondent of the Academy of Sciences of the USSR P.G. Romankova, L.:, Chemistry, -1987, p. 549), 12.3 kPa.

With a design pressure in the cooling zone chamber of 101.3 kPa, and a pressure of the working fluid - saturated water vapor in it 12.3 kPa., Design partial air pressure in the cooling zone chamber: 101.3 kPa - 12.3 kPa = 89 kPa.

The design volume fraction of air in the chamber adjacent to the hydraulic seal in the cooling zone (numerically equal to the ratio of the partial air pressure to the total pressure in the chamber): 89 kPa / 101.3 kPa = 0.878.

The design amount (mass) of air in the chamber adjacent to the hydraulic seal in the cooling zone (calculated through the density of air under operating conditions in the chamber, - 1.09 kg / m3, the volume of the chamber, - 0.00148 m3, and the volume fraction of air in the chamber, - 0.878) 0.0014 kg = 1.4 g.

This value is also the design amount of air that needs to be left in the annular space of the rotor. And which, under operating conditions, being concentrated in the chamber adjacent to the hydraulic seal in the cooling zone, will, in combination with the pressure of the saturated steam of the working fluid, create a design working pressure of 101.3 kPa in this chamber.

Preparation of a technical device for work.

Before starting work (after placing the working fluid in the form of water into the annular space), from the volume of the annular space free from liquid (0.0053 m3 = 5.3 l), which is initially under pressure equal to atmospheric pressure - 101.3 kPa, is removed, by connecting to an external vacuum line (vacuuming) the air present there. Air is evacuated by vacuum until the residual pressure in the liquid-free annulus is 20.6 kPa.

It is at such a residual pressure that the residual amount of air in the annular space will be calculated as 0.0014 kg = 1.4 g (calculated through the air density in a vacuum space - 0.264 kg / m3 and the volume of space - 0.0053 m3) which corresponds to the required design residual air in the annulus.

Operation of a technical device. Technical indicators

Due to the fact that the technical device is equipped with shut-off inlet / outlet devices in the form of check valves of a known design, which are closed in the normal position and brought to the open position by a pressure drop across the valves naturally occurring during the process of heating / cooling the working fluid, special preparation - valve actuation in working position is not required.

The heaters in the heating zone and coolers in the cooling zone are switched on.

When heated, in chamber 2 located in the heating zone, with the check valve above the hydraulic seal closed, the working fluid evaporates from the liquid, the pressure of the vapor-gas phase in the volume between the liquid level in the hydraulic seal and the closed valve 3 above the hydraulic seal increases (from the initial one set by vacuuming). When the pressure rises to the level of opening of the check valves, the valves 3 in the liquid open and the hydraulic sealing liquid is squeezed out down the chamber, and further into the chamber of the cooling zone.

The pressure in the cooling zone chamber, initially low, set by vacuuming, increases due to the compression of the vapor-air medium by the hydraulic sealing liquid (liquid phase) squeezed out of the heating zone chamber.

The movement of the mass of liquid 4 inside the rotor leads to the appearance of a weight imbalance of the rotor 1, and it, the rotor 1, starts to rotate.

The continuity of the rotation process is ensured

by opening/closing the corresponding valves between the chambers, while maintaining the above state: valve 3 between the chambers above the water seal in the heating zone is closed, valves 3 located in the liquid and above the liquid in the chamber of the cooling zone are open.

With the complete transfer of all residual air into the chamber of the cooling zone, the process stabilizes at the design parameters: pressure in the chamber of the cooling zone 101.3 kPa, pressure in the chamber of the heating zone at maximum load (with a maximum height difference of liquid levels in the hydraulic seal = 0.98 m = 980 mm, and the sum of the pressure drops on the check valves is 250 mm w.st.), design, - 113.35 kPa; the temperature of the working fluid in the cooling zone is 50 C, in the heating zone 104 C.

The maximum unbalance of the rotor, while - 2.4 kg.

In accordance with the geometry of the wheel-shaped rotor, the center of gravity of the liquid that creates the unbalance of the rotor, with the specified parameters, is located at a distance of 0.6 m horizontally from the center of the rotor.

Torque on the rotor axis, determined through the product of the force on the shoulder (distance from the axis of rotation to the vertical of gravity): 2.4 kg * 0.6 m = 1.44 kg * m.

The developed power can be determined through the product of the force and the speed of its movement.

The speed of rotation of the rotor is predetermined by the speed of movement of the liquid through the annular space inside it, under the influence of the pressure difference on different sides of the hydraulic seal.

In turn, the pressure difference is ensured by maintaining the previously mentioned temperatures of the working fluid: in the cooling zone 50 C, in the heating zone 104 C.

At the same time, the greatest difficulty is to ensure the required temperature of the working fluid in the cold zone, because this temperature is provided by cooling the previously heated working fluid with a cold coolant, which, for the design of the technical device considered in this example, is usually used as atmospheric air.

In our example, it is assumed that the cooling of the working fluid is carried out by natural convection of atmospheric air during its free movement along the heat exchange surface in the cooling zone.

Under the following given conditions:

- atmospheric air temperature 15С;

- the temperature of the chamber wall in the cooling zone is 45 C (close to the temperature of the working fluid inside the chamber);

The heat exchange surface in the cooling zone (at least 2 chambers) is increased against the geometric surface of these 2 chambers, due to the use of small fins, and is F = 0.534 m2.

The heat transfer coefficient for the conditions of free air movement can be taken on the basis of known data (Pavlov K.F., Romankov P.G., Noskov A.A. Examples and tasks in the course of processes and apparatuses of chemical technology. Textbook for universities / Ed. Corresponding Member of the Academy of Sciences of the USSR P. G. Romankova, L.:, Chemistry, - 1987, p. 171), within 3-9 W / (m2 * deg).

With the value of the heat transfer coefficient a = 5 W / (m2 * deg), with the temperature difference between the wall and the cooling air dT = 45 C -15 C = 30 C, and with the value of the heat exchange surface F = 0.534 m2, the amount of heat removed in the cold the heat zone is calculated by the value (the product of the heat transfer coefficient, temperature difference and heat exchange surface): Qhz \u003d a * dT * F \u003d 5 W / (m2 * deg) * 30 C * 0.534 m2 \u003d 80.1 J / s \u003d 80, 1 W.

The heat removed leads to the condensation of water vapor in the chambers of the cooling zone.

The heat of condensation / vaporization of water, at an operating temperature of 50C, according to known data (Pavlov K.F., Romankov P.G., Noskov A.A. Examples and tasks in the course of processes and apparatuses of chemical technology. Textbook for universities / Ed. Corresponding Member of the Academy of Sciences of the USSR P.G. Romankova, L.:, Chemistry, - 1987, p. 548) is calculated as 2380 kJ / kg

By dividing the value of the removed heat, by the value of the heat of condensation / vaporization, the rate of water condensation in the cooling zone is found:

80.1 J/s: 2380,000 J/kg = 0.0336 * 10 ^-3 kg/s = 0.0336 g/s

The chamber leaving the heating zone into the cooling zone, at a temperature of 104 C and a pressure of 113.35 kPa, contains 0.97 g of water vapor (it is found by the product of the vapor density, under operating conditions in the chamber, -0.66 kg / m3 and the volume chambers, - 0.00148 m3).

By dividing the rate of condensation of the working fluid (water) in the cooling zone 0.0336 g / s by the amount of vaporous working fluid formed in the chamber of the heating zone 0.97 g, the number of chambers leaving the heating zone to the cooling zone per unit time is calculated: 0.0336 g/s: 0.97 g/camera = 0.034 cameras per second.

With the number of chambers in the technical device 6, one complete revolution of the rotor is completed in time 6: 0.034 = 176 sec.

With a total length of the chambers (length of the perimeter of the rotor) of 4.55 m, the linear speed of rotation of the rotor is calculated by the value: 4.55 m: 176 sec = 0.025 m/s

At such a rotor speed, the developed power is estimated by the value (the product of the unbalance force, by the speed of movement): 2.4 kg * 0.025 m / s = 0.06 kg * m / s. Or, in SI: 0.59 W.

The thermal efficiency of the thermal energy conversion cycle, calculated by the well-known formula (Kirillin V.A., Sychev V.V., Sheindlin A.E. Technical thermodynamics. Moscow "Energoatomizdat" 1983, p. 54), through the ratio of temperatures of the working fluid (temperature difference between hot and cold working fluid, in degrees Kelvin, divided by the temperature of the hot working fluid, in degrees Kelvin):

Efficiency \u003d (377-323) / 377 \u003d 0.14 or 14%

The transfer of the mechanical energy of the rotor rotation to the working body of the energy consumer can be carried out by placing the rotor on the shaft, in the center of rotation of the rotor, with the connection of this shaft to the shaft of the energy consumer.

Testing the layout of a technical device (example 4).

Layout technical device. Construction, design parameters.

The layout is assembled on the basis of a bicycle wheel with a diameter of 0.64 m. For the manufacture of chambers, flexible metal water pipes (bellows) DN = 32 mm are used. Spring check valves for water are used as shut-off inlet/outlet devices between the chambers.

Model design: a wheel-shaped rotor with an outer diameter of 0.7 m, with 6 chambers with an inner diameter of 0.032 m, communicating with each other through shut-off inlet/outlet devices (valves).

Shut-off inlet/outlet devices between the chambers - check valves of a known design (normally closed), are brought into the open position by a pressure drop across the valve naturally occurring in the process of heating/cooling the working fluid; difference required to drive (open) the valve - 50 mm w.st.

The internal volume of one chamber is 0.000245 m3 = 0.245 l. The total volume (capacity) of the inner annulus formed by the chambers is 0.00147 m3 = 1.47 l. The inner annular space is filled with a liquid working fluid - water by 30% of the total capacity. Residual volume of liquid-free annular space (70% of capacity) 0.00102 m3 = 1.02 l. The volume of water (the working fluid in the liquid phase) forming a water seal in the lower part of the annular space is 0.00045 m3 = 0.45 l, weight (taking into account the water density of 1000 kg/m3) - 0.45 kg.

Design maximum rotor unbalance 270 g.

The design maximum height difference of liquid levels in the hydraulic seal, while (in accordance with the geometry of the annular space) - 0.3 m = 300 mm.

The design pressure drop between the chambers of the heating and cooling zone, with such a height difference, and, taking into account the required pressure drop on each valve of 50 mm w.st, is calculated as: 500 mm. Or in the SI system 4.9 kPa.

Inside the annular space before the water was placed in it, there was air. The design working pressure of the steam-air medium in the chamber of the cooling zone is 101.3 kPa (taken equal to atmospheric pressure).

Design pressure of saturated water vapor in the chamber of the heating zone (higher than the design pressure in the chamber of the cooling zone by the value of the design pressure difference between the chambers) 101.3 + 4.9 kPa = 106.2 kPa.

The design temperature of the working fluid in the heating zone chamber, providing this (106.2 kPa) saturated steam pressure in the heating zone chamber, according to known data (Pavlov K.F., Romankov P.G., Noskov A.A. Examples and tasks for Course of Processes and Apparatuses of Chemical Technology Textbook for High Schools/Edited by Corresponding Member of the Academy of Sciences of the USSR PG Romankov, L.: Chemistry, - 1987, p. 548) 101 C, or, in degrees Kelvin -374 K..

The design temperature of the working fluid in the chamber of the cooling zone adjacent to the hydraulic seal (accepted taking into account the characteristics of the cooler - ambient air), +50 C, or, in degrees Kelvin, 323 K.

The pressure of saturated water vapor at this temperature, according to known data (Pavlov K.F., Romankov P.G., Noskov A.A. Examples and tasks in the course of processes and apparatuses of chemical technology. Textbook for universities / Ed. Chl. Correspondent of the Academy of Sciences of the USSR P. G. Romankova, L .: Chemistry, -1987, p. 549), 12.3 kPa.

With a design pressure in the cooling zone chamber of 101.3 kPa, and a pressure of the working fluid - saturated water vapor in it of 12.3 kPa, the design partial air pressure in the cooling zone chamber: 101.3 kPa - 12.3 kPa = 89 kPa.

The design volume fraction of air in the chamber adjacent to the hydraulic seal in the cooling zone (numerically equal to the ratio of the partial air pressure to the total pressure in the chamber): 89 kPa / 101.3 kPa = 0.878.

The design amount (mass) of air in the chamber adjacent to the hydraulic seal in the cooling zone (calculated through the density of air under operating conditions in the chamber, - 1.09 kg / m3, the volume of the chamber, - 0.000245 m3, and the volume fraction of air in the chamber, - 0.878) 0.00023 kg = 0.23 g.

This value is also the design amount of air that needs to be left in the annular space of the rotor. And which, under operating conditions, being concentrated in the chamber adjacent to the hydraulic seal in the cooling zone, will, in combination with the pressure of the saturated steam of the working fluid, create a design working pressure of 101.3 kPa in this chamber.

Before starting work (after placing the working fluid in the form of water in the annular space), from the liquid-free volume of the annular space 0.00102 m3 = 1.02 l. initially under pressure equal to atmospheric pressure - 101.3 kPa, it is necessary to remove the air located there. Air must be pumped out to a residual pressure in the liquid-free annular space of 17.5 kPa

It is at such a residual pressure that the residual amount of air in the annular space will be calculated as 0.00023 kg \u003d 0.23 g (calculated through the density of air in a vacuum space - 0.225 kg / m3 and the volume of space - 0.00102 m3) which corresponds to required design residual air quantity in the annulus.

Preparation of a technical device for work.

The removal of air from the liquid-free annular space was carried out by purging the annular space with steam. Which was developed inside the annular space, due to the fire heating of the lower section of the rotor filled with water, near the water seal level.

For heating, the flame of a household gas burner was used. Heating was carried out from the side of the cooling zone in case of depressurization of the annular space of the rotor (for air release) above the hydraulic seal in the heating zone. The air displaced from the annular space (partially with water vapor) exited through the place of depressurization into the surrounding space. Fire heating was carried out until the entire upper part of the rotor was completely heated, and was stopped when the temperature of the chamber wall at the place of depressurization reached 80°C.

The residual pressure in the annular space and the residual amount of air were not measured.

Operation of a technical device. Technical indicators

Due to the fact that the technical device is equipped with shut-off inlet / outlet devices in the form of check valves of a known design, which are closed in the normal position and brought to the open position by a pressure drop across the valves naturally occurring during the process of heating / cooling the working fluid, special preparation - valve actuation in working position is not required.

The flame of a household gas burner was used as a heater when testing the model.

Ambient air was used as a coolant. Cooling was carried out in two versions:

- without artificial blowing (due to natural air movement);

- when blowing the cooling zone with a domestic fan.

The layout tests were carried out indoors at an internal temperature of 25C.

During testing of the layout, the temperature of the working fluid in the chambers of the heating zone and in the chambers of the cooling zone was not measured.

Test results:

45 seconds after turning on the gas burner (beginning of heat supply in the heating zone), the rotor began to rotate slowly.

When operating in conditions without artificial blowing of the cooling zone (with cooling due to natural air convection), the rotor made 2 complete revolutions in 32 minutes. Linear speed of rotation of the rotor (perimeter length divided by the time of one complete revolution) 0.0022 m/s.

When operating in conditions of blowing the cooling zone with a domestic fan, the rotor made 2 complete revolutions in 23 minutes. Linear speed of rotation of the rotor (perimeter length divided by the time of one complete revolution) 0.003 m/s.

Despite the fact that in the tests of the layout, very small values of the rotor speed were recorded, the tests unequivocally confirmed the possibility of implementing the claimed invention. In particular, they confirmed the possibility of using check valves as shut-off inlet / outlet devices between the chambers driven by the pressure drop across the valves naturally occurring in the process of heating / cooling the working fluid.

Claims (10)

1. A method for converting thermal energy into mechanical energy of rotational motion by heating and subsequent cooling of the working fluid, which consists in the fact that alternately heat and cool chambers that are filled with a heat-sensitive working fluid, the walls of which are made heat-conductive and have, in whole or in part, the shape of a heat exchange surface , redistribute the mass of fluid in the rotor, create a weight imbalance of the rotor, which causes the alternate movement of the chambers into the zones of their heating and cooling, characterized in that they alternately heat and cool the chambers, which are located around the circumference of the wheel-shaped rotor and communicate with each other through the inlet / outlet valves or other locking inlet/outlet devices with the formation in the aggregate of the internal annular space inside the rotor. 2. The method according to claim 1, characterized in that the heat-sensitive working fluid is placed in the annular space formed by the chambers in the form of a liquid, in an amount less than the capacity of the annular space, which ensures the formation of a U-shaped hydraulic seal in the lower part of the annular space, and in the upper part above the hydraulic seal - a vapor-gas medium, the supply of thermal energy and the removal of thermal energy are carried out in the area of the chambers adjacent to opposite sides of the hydraulic seal, while the heating zone is on one side of the hydraulic seal, the cooling zone is on the other side of the hydraulic seal and on top of the wheel-shaped rotor to the heating zone . 3. The method according to p. 2, characterized in that the redistributed fluid that creates the weight imbalance is the working fluid in the liquid phase, the redistribution of the mass of the liquid with the creation of the weight imbalance occurs without changing the volume of the chambers and is carried out in the form of fluid flow over the annular space under the action of the difference pressure of the gas-vapor medium on opposite sides of the U-shaped hydraulic seal. 4. The method according to claim 1, characterized in that the working fluid in the liquid phase moves inside the annular space of the rotor by sequentially flowing from chamber to chamber, the working fluid is supplied to the heating zone in a liquid state, evaporates in the heating zone, condenses in the cooling zone and then it is again fed into the heating zone in the liquid state. 5. The method according to p. 2, characterized in that heating / cooling is carried out with at least one closed valve between the chambers above the hydraulic seal in the heating zone, with open valves located in the liquid, and at least one open valve between the chambers above the hydraulic seal in the cooling zone, and subject to the following sequence of opening/closing of the valves as they pass through the heating and cooling zones during the rotation of the rotor: the valve in the heating zone, which, during the rotation of the rotor, left the hydraulic sealing fluid against its flow in the open state, closes when some distance from the liquid level in the hydraulic seal, the pressure of the vapor-gas medium under the valve began to exceed the pressure of the medium above the valve, moving further with the rotation of the rotor from the heating zone to the cooling zone, the valve remains closed and opens when the pressure of the vapor-gas medium behind the valve becomes lower than the pressure of the vapor-gas medium in front valve, the valve enters the current towards the hydro barrier fluid in the open state and remains open until the spatial position of the closing point is reached after exiting the barrier fluid in the heating zone. 6. The method according to claim 1 or 2, characterized in that the amount of the working fluid placed in the annular space in the form of a liquid is selected from the condition: moreover, that, being concentrated in the lower part of the annular space, it completely covers the cross section of the annular space, but not more than half the capacity of the annulus. 7. The method according to claim 1 or 2, characterized in that a liquid is used as a heat-sensitive working fluid in the form of water, mercury, or any substance that is in a liquid state under operating conditions and has, under these conditions, a saturated vapor pressure sufficient to create a difference the heights of the liquid levels in the U-shaped hydraulic seal are not less than the diameter of the wheel-shaped rotor. 8. The method according to p. 2, characterized in that after placing the working fluid in the form of a liquid in the annular space, the air, or nitrogen, or another gas inert with respect to the working fluid, is removed from the volume of this space that is not filled with liquid, up to the residual amount that, under operating conditions, being concentrated in the volume of the chamber adjacent to the hydraulic seal in the cooling zone, will, together with the pressure of the saturated steam of the working fluid, create in this chamber such a pressure of the vapor-gas medium that is specified by the project. 9. A device for implementing the method according to claim 1, containing a rotor with chambers filled with a heat-sensitive working fluid, the walls of which are made heat-conductive and have, in whole or in part, the shape of a heat exchange surface, characterized in that the rotor has a wheel-shaped shape, the chambers are located around the circumference of the rotor , are communicated with each other through inlet/outlet valves or other inlet/outlet locking devices to form together the inner annular space of the wheel-shaped rotor. 10. The device according to claim 9, characterized in that the number of chambers located around the circumference of the rotor is at least four.

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