RU2744588C1 - Method for preventing thermal deformations of rotor frame of disc high-temperature rotating regenerative heater of working fluid of power plant - Google Patents

Abstract

FIELD: heat engineering.

SUBSTANCE: invention relates to the field of heat engineering and can be used in regenerative heaters of the working fluid of gas turbine installations. The invention is a thermophysical isolation of the frame parts, carrying the main power load from a variable temperature field due to maintain a constant temperature on the heat transfer surfaces of the heat exchanger of each cell by changing the state of aggregation of a thermal storage material disposed in the cavity of each heat exchanger cell and thus maintain a constant temperature of heat exchange cells with internal channels combined in cellular structure, and the preservation of the cylindrical shape of the rotor frame of the disk high-temperature rotating heater of the working fluid of the power plant.

EFFECT: increased efficiency and efficiency of a high-temperature rotating disk regenerative heater.

1 cl, 4 dwg

Description

The field of application of the method: thermal power engineering, mainly for heating a working fluid, such as air, fuel and their mixtures in burners of heat power plants, and in mass regenerative heaters of a working fluid of gas turbine installations, by transferring heat from hot gases to air and / or fuel, for example, in microturbines, mainly as part of hybrid power plants for heat production and / or electric current generation.

The essence of the invention: a method for preventing thermal deformations of the rotor frame of a disc high-temperature rotating regenerative heater of a working fluid of a power plant is proposed, which includes control of a system for regulating temperatures and flow rates of air and gas flows in the body of a regenerative heater with inlet and outlet channels by regulating temperatures and costs of air and gas flows by means of regulation, located in the housing and in its inlet and outlet air and gas channels, made in it, respectively, with the possibility of supplying and removing air and gas flows in a countercurrent flow, and a regenerative heater rotor installed in this housing, containing a frame 1, consisting of a hot 2 and cold 3 end discs and heat exchange cells 4 with internal channels 5, combined into a cellular structure, installed in the body of the regenerative heater with the possibility of rotation and alternating passage through it, in countercurrent flow, at least one heated cold air flow and at least one cooled hot gas flow, and the hot gas flow is introduced into the rotor through the hot end disk 2 of the rotor frame 1 and is discharged through the cold end disk 3 of the frame 1 of the rotor in the form of a cooled gas flow, and the cold air flow is introduced into the rotor through the cold end disk 3 of the rotor frame 1 and removed from it through the hot end disk 2 of the rotor frame 1 in the form of a heated air flow, while the air and gas flows are separated from each other on each disk of the rotor frame 1 by means of at least one radial 6 non-contact labyrinth seal placed on the housing, and on each outer side of the hot 2 and / or cold 3 end disks are separated from the external environment by at least one located on the housing of the circumferential 7 non-contact labyrinth seal of the corresponding rotor disk, while the way m of optimal regulation of the flow rates and temperatures of the air and gas streams, the system of optimal regulation of the temperatures and the flow rates of the air and gas flows maintains close or with the minimum possible temperature difference of the air and gas flows on the corresponding parts of the rotor, respectively, at the exit from the hot end disk 2 of the frame 1 of the rotor of the heated air flow leaving through the hot end disk 2 of the frame 1, and at the outlet of the cold end disk 3 of the frame 1 of the rotor of the cooled gas flow leaving through the cold end disk 3 of the frame 1 of the rotor, in the zone of the radial labyrinth seals 6 of the rotor on the body, and the ratio of the coefficients of the linear the expansion of the materials of the hot 2 and cold 3 end disks of the frame 1 are chosen inversely proportional to the ratio of the increases in the average operating temperatures of the corresponding disks, and the cellular structure of the frame 1 of the heater rotor includes heat exchange cells 4, which are made in the form of about separate glasses 10 with external hexagonal surfaces 11 and internal surfaces 12 of channels 5, in each of which an annular cavity 13 is made between these surfaces, which is filled with a thermal storage substance 14, which is configured to change its state of aggregation from solid to liquid by melting, and when heat is removed, back by solidification, thus, reciprocating vibrational heat exchange is carried out due to the heat of melting or solidification of the thermal storage substance 14, while the hot gas stream is cooled by taking the heat of melting from it with the thermal storage substance 14, and the cold air flow heated by giving it a thermal storage substance 14 of the heat of its solidification.

A known method of compensating for the deformation of a high-temperature rotating disk heater of the working fluid of a power plant, including a system for regulating temperatures and flow rates of air and gas flows and a rotor containing a frame consisting of cold and hot end discs and heat exchange cells, installed in the heater body with the possibility of rotation and alternating passage through it in counterflow of at least one heated gas flow of air and at least one cooled gas flow, and the air flow is introduced into the rotor through the cold end disk of the rotor frame, and is removed from it through the hot end disk of the rotor frame in the form outgoing heated air flow, and the gas flow is introduced into the rotor through the hot end disk of the rotor frame and is discharged through the cold end disk of the rotor frame in the form of an outgoing cooled gas flow, while the air and gas flows are separated on the rotor from each outer side hot and cold discs by means of at least one rotor seal located on the housing (see. RF patent No. RU 2441188, applicant BALKE-DURR GMBH (DE), publ. 27.01.2012.)

The main disadvantage of the known method for compensating for the deformation of a high-temperature rotary disc heater during its operation is a complex sequence of actions when trying to create a contactless seal and maintain an optimal gap in the seal using complex temperature-controlled rod mechanisms located on all surfaces of the seals.

A known method of preventing deformation of a high-temperature rotating disk heater of a working fluid of a power plant, including a system for regulating temperatures and flow rates of air and gas flows and a rotor containing a frame consisting of cold and hot end discs and heat exchange cells, installed in the heater body with the possibility of rotation and alternating passage through it in counterflow of at least one heated gas flow of air and at least one cooled gas flow, and the air flow is introduced into the rotor through the cold end disk of the rotor frame, and is removed from it through the hot end disk of the rotor frame in the form outgoing heated air flow, and the gas flow is introduced into the rotor through the hot end disk of the rotor frame and is discharged through the cold end disk of the rotor frame in the form of an outgoing cooled gas flow, while the air and gas flows are separated on the rotor from each outer st hot and cold discs by means of at least one rotor seal located on the housing (see. patent for invention of the Russian Federation No. 2432540, applicant BALKE-DURR GMBH (DE), publ. 27.10.2011.)

The main disadvantage of the known method of compensating for the deformation of a high-temperature rotary disk heater during its operation is a complex sequence of actions when trying to create a contactless seal and maintain the removable flow rate of overflowing air and gas streams through the optimal gap in the seal by suctioning air and / or gas constituting the leak in the zone located on all surfaces of the seals, mainly in the radial direction, allowing to stabilize the temperature distribution over the surface of the frame.

A known method of preventing deformation of a high-temperature rotating disk heater of a working fluid of a power plant, including a system for regulating temperatures and flow rates of air and gas flows and a rotor containing a frame consisting of cold and hot end discs and heat exchange cells, installed in the heater body with the possibility of rotation and alternating passage through it, in countercurrent flow, of at least one heated gas stream of air and at least one cooled gas stream, and the cold air flow is introduced into the rotor through the cold end disk of the rotor frame, and is removed from it through the hot end disk of the rotor frame into in the form of a heated air flow, and the gas flow is introduced into the rotor through the hot end disk of the rotor frame and is discharged through the cold end disk of the rotor frame in the form of an outgoing cooled gas flow, while the air and gas flows are separated on the rotor from each outer Rings of hot and cold discs by means of at least one rotor seal located on the housing (see. RF patent for invention No. RU 2119127 C1, applicant Apparatus Rotemole Brandt und Kritzler GmbH (DE), publ. 20.09.1998.)

The main disadvantage of the known method of compensating for the deformation of a high-temperature rotary disk heater during its operation consists in a complex sequence of actions when trying to create a contactless seal and maintaining the separation of air and gas cavities through an optimal gap in the seal using a separating gas flow, which compensates and prevents air and gas overflows, circumferential and radial seals form sealing surfaces located in a common plane and passing into each other without backlash at the joints and with the possibility of automatically maintaining a backlash-free contact, which makes it possible to stabilize the temperature distribution over the frame surface.

There is a method of preventing deformation of a high-temperature rotating disk heater of a working fluid of a power plant, including a system for regulating temperatures and flow rates of air and gas flows and a rotor containing a frame consisting of cold and hot end disks and heat exchange cells, installed in the heater body with the possibility of rotation and alternating passage through it in counterflow of at least one heated air flow and at least one cooled gas flow, and the cold air flow is introduced into the rotor through the cold end disk of the rotor frame, and is removed from it through the hot end disk of the rotor frame in the form outgoing heated air flow, and the gas flow is introduced into the rotor through the hot end disk of the rotor frame and is discharged through the cold end disk of the rotor frame in the form of an outgoing cooled gas flow, while the air and gas flows are separated on the rotor from each outer st orons of hot and cold discs by means of at least one rotor seal located on the housing. The heater works like a conventional rotary regenerative heater. When thermal deformations of the rotor 6 occur, its warpage is eliminated by strictly fixing the rotor 6 relative to the housing 1 by means of the interaction of the ring 14 with the annular groove 13 through the anti-friction linings 15. Thus, the skew of the sealing surfaces of the rotor 6 is eliminated, which excludes the opening of the gaps between these surfaces and the seals 9 and 10 and thereby reduces the flow of heat exchanging media - air and gas (see USSR inventor's certificate No. 881517, applicant Gorky Automobile Plant (Production Association "GAZ"), publ. 11/15/1981, the text of the analogue criticism indicates the original positions from the USSR author's certificate No. 881517).

The main disadvantage of the known method for compensating for the deformation of a high-temperature rotating disk heater during its operation is that when thermal deformations of the rotor occur, its warpage is eliminated by strictly fixing the rotor relative to the body by means of the interaction of the ring with the annular groove through the anti-friction linings. Thus, the skew of the sealing surfaces of the rotor is eliminated, which, according to the applicant, excludes the opening of the gaps between these surfaces and the seals and thereby reduces the flow of heat exchanging media - air and gas. But it should be noted that the mechanical alignment of the mushroom-like shape of the heat-transferring and end surfaces of the rotor frame cannot be fully compensated, for example, due to the presence of technological gaps in the joints, their wear and the constantly changing temperature field and the spatial thermal deformations caused by it.

A known method of operation and prevention of deformation of a high-temperature rotating disk heater of the working fluid of a power plant, including a system for regulating temperatures and flow rates of air and gas flows and a rotor containing a frame consisting of cold and hot end disks and heat exchange cells, installed in the heater body with the possibility of rotation and alternately passing through it in countercurrent at least one heated air flow and at least one cooled gas flow, moreover, the cold air flow is introduced into the rotor through the cold end disk of the rotor frame, and is removed from it through the hot end disk of the rotor frame in the form of an outgoing heated air flow, and the gas flow is introduced into the rotor through the hot end disk of the rotor frame and is discharged through the cold end disk of the rotor frame in the form of an outgoing cooled gas flow, while the air and gas flows are separated on the rotor from each The outer side of the hot and cold discs by means of at least one rotor seal located on the housing (see. USSR author's certificate No. SU 800579 A1, applicant Gorky Automobile Plant (Production Association "GAZ"), publ. 01/30/1981)

According to the applicant, the execution of transverse channels on the hot side of the frame, communicated by the inlet openings with the air inlet pipe, and the outlet openings with the air outlet pipe, allows cooling the frame end on the hot side, reducing the warping of the frame by leveling the temperature of the frame surface and increasing the reliability of the regenerator. But at the same time, the applicant does not take into account the possibility of mushroom-like warping of the entire rigid frame, consisting of monolithic hexagonal cells, in which heat transfer elements are installed in the form of conical inserts, which are constantly washed on one side of the radial seal by cold air heated by them, and on the other, the cells are heated by hot gases , as a result of which thermal deformations of the entire frame under their influence cannot be compensated by smaller deformations of the cooled hot disk.

There is a known method of preventing deformation of a high-temperature rotating disk heater of a working fluid of a power plant, including a system for regulating temperatures and flow rates of air and gas flows, a housing with inlet and outlet channels made in it, respectively, with the possibility of supplying and removing air and gas flows in a counterflow, and installed in it is a rotor containing a frame 1, consisting of hot 2 and cold 3 end disks and heat exchange cells 4 with internal channels 5, installed in the heater body with the possibility of rotation and alternately passing through it in countercurrent at least one heated air flow and, at least one cooled gas stream, and the hot gas stream is introduced into the rotor through the hot end disk 2 of the rotor frame and is output through the cold end disk 3 of the rotor frame 1 in the form of an outgoing cooled gas flow, and the cold air flow is introduced into the rotor black without the cold end disk 3 of the rotor frame 1, and is removed from it through the hot end disk 2 of the rotor frame 1 in the form of an outgoing heated air flow, while the air and gas flows are divided among themselves on each rotor disk by at least one radial 6 labyrinth seal located on the housing, and on each outer side of the hot 2 and cold 3 discs are separated from the external environment by at least one circumferential 7 labyrinth seal of the rotor located on the housing, and part of the frame is enclosed by a heat-shielding shell designed to create a dynamic thermal protection against overheating of the part of the frame adjacent to the rotor (see. RF patent No. RU 2296930 C1, applicants State educational institution of higher professional education Moscow State Technical University "MAMI" (RU), Federal State Unitary Enterprise Moscow Machine-Building Production Enterprise "Salut" (RU), publ. 10.04.2007.)

According to the applicants, the proposed method for cooling the frame of a rotating disk heater by taking a part of the flow with the heat of the exchanging media and directing it along the wall of the frame, in which the selected part of the flow of the hot medium is directed along the wall of the frame after pre-cooling, which will prevent washing of the frame wall by the hot medium and, therefore , provides a reduction in thermal deformations of the frame. The cooling system that implements this method consists of cooling channels located along the wall of the frame: the main one and an additional one with a guide vanes. The main channel is formed by two shells covering the heat exchange matrix, made in a U-shape with a bottom placed on the hot cheek. The inner shell is cantilevered on the hot cheek and can be made in the form of a heat-insulating wall separating the additional cooling channel from the main one. The outer shell divides the main channel into two elbows, one of which communicates with the additional channel and together with the cover, which is at the same time the bottom of the additional channel, this shell constitutes the guide vane of the system. The additional cooling channel, depending on the design features of the heat exchange matrix and the operating parameters of the heater, is formed by an internal shell and either slotted channels of the matrix, or at least one newly introduced special channel (slotted or some other), at least one , or as part of a porous matrix packing, isolated or not isolated from the main packing volume. The technical result obtained from the use of the proposed group of inventions consists in increasing the efficiency of cooling the heater frame and, accordingly, reducing its thermal deformations and stresses in it with a constructive simplification of the cooling system. But the main disadvantage of the proposed method and the cooling system of the rotary disk heater frame that implements its operation will be that the main part of the heater frame will be under the influence of uneven heating along the heat exchange cells, the temperature field of which will be uneven, which will certainly lead to mushroom-shaped thermal deformation of the frame, which it is impossible to compensate with a heat-stabilized part of the frame, separated by shells, which should lead to an unpredictable curvature of the frame shape in its inner non-heat-stabilized part during its washing with cooled hot gas or heated cold air from the side of the “hot cheek”.

There is a known method of operation and prevention of deformation of the rotor frame of a disc high-temperature rotating regenerative heater of a working medium of a power plant, which includes control of a system for regulating temperatures and flow rates of air and gas flows in the body of a regenerative heater with inlet and outlet channels made in it respectively with the possibility of supplying and removing and gas flows in a counterflow and a rotor installed in it, containing a frame 1, consisting of hot 2 and cold 3 end disks and heat exchange cells 4 with internal channels 5, combined into a cellular structure, installed in the heater body with the possibility of rotation and alternating passage through it in countercurrent flow of at least one heated air flow and at least one cooled gas flow, and the hot gas flow is introduced into the rotor through the hot end disk 2 of the rotor frame 1 and is discharged through the cold the end disk 3 of the rotor frame 1 in the form of an outgoing cooled gas flow, and the cold air flow is introduced into the rotor through the cold end disk 3 of the rotor frame 1 and is removed from it through the hot end disk 2 of the rotor frame 1 in the form of an outgoing heated air flow, while the air and the gas flows are separated on the rotor on each outer side of the hot and cold disks by at least one radial 6 and / or circumferential 7 rotor seal located on the housing, while being performed on the hot side of the frame and around the heat exchange cells of the transverse cooling channels, communicated by inlets with an air inlet pipe, and outlets with an air outlet pipe (see. RF patent No. RU 2623133 C1, applicant Federal State Budgetary Educational Institution of Higher Education "Moscow Polytechnic University" (RU), publ. 27.01.2012.)

According to the applicant, the execution of transverse cooling channels on the hot side of the frame and around the heat exchange cells, communicated by the inlet openings with the air inlet pipe, and the outlet openings with the air outlet pipe, allows to provide cooling of the frame end on the hot side and the frame with heat exchange cells, to reduce the warping of the frame due to equalization of the temperature of the surface of the hot disk and the cells of the frame and increase the reliability of the regenerator. But at the same time, the applicant does not take into account the possibility of mushroom-like warping of the entire rigid frame, consisting of monolithic hexagonal cells, in which heat transfer elements are installed in the form of conical inserts, which are constantly washed on one side by cold air heated by them, and on the other by hot gases, and at the same time heat exchange cells in the form of heat transfer packages are rigidly connected to the walls of the frame, as a result of which thermal deformations of the heat-accumulating cells of the frame under their influence cannot be compensated by smaller deformations of the cooled hot disk and the walls of the frame cells, which are rigidly connected to each other, and the cooling of the hot disk will not be able to support the frame in undeformed state, since the outer walls of the frame cells are not thermally insulated from their inner part and are rigidly connected to it, for this reason, the real state and deformations of the frame are determined by heating from the heat of the heat transfer packages and their mechanical deformation air Actions on the frame and frame deformation due to the uneven real temperature distribution over the supporting structures of the frame.

The closest technical solution is the method of operation of the specified heat exchange system and prevention of deformation of the high-temperature rotating disk heater of the working fluid of the power plant, according to RF patent No. RU 2623133 C1, which is the closest to the proposed invention in terms of the problem being solved and has the largest number of actions that coincide with the actions of the proposed invention ...

The technical task of the proposed invention is to increase the operability and efficiency of a high-temperature rotating disk regenerative heater of the working fluid of a power plant, by using a new sequence of actions and a new set of materials used to prevent thermal deformations of its cylindrical shape under the influence of a constantly dynamically changing temperature field from the effects of cold air flows and hot gas with their constant temperature change, affecting the rotor frame of the high-temperature rotating regenerative heater of the working fluid of the power plant, by thermophysical insulation of the frame parts carrying the main power loads from the variable temperature field due to maintaining a constant temperature on the heat transfer surface of each heat exchange cell due to the change in the aggregate the state of the thermal storage substance placed in cavity of each heat exchange cell and, as a result, maintaining constant temperatures of heat exchange cells with internal channels, combined into a cellular structure, and maintaining the cylindrical shape of the rotor frame of the disk high-temperature rotating heater of the working fluid of the power plant.

The technical problem posed is solved by using the structures proposed as examples of the implementation of the sequence of actions of the method, and the following technical results described below are achieved.

The technical problem is solved by the fact that the method is implemented in the following sequence of actions on the material means to prevent thermal deformations of the cylindrical shape of the rotor frame of the disk high-temperature rotating regenerative heater of the working fluid of the power plant,

Consequently, the technical problem is solved by the fact that a method for preventing thermal deformation of the rotor frame of a disc high-temperature rotating regenerative heater of a working fluid of a power plant, which includes controlling a system for regulating temperatures and flow rates of air and gas flows in a regenerative heater body with inlet and outlet channels, by regulating temperatures and flow rates of air and gas flows by means of regulation located in the housing and in its inlet and outlet air and gas channels, made in it, respectively, with the possibility of supplying and withdrawing in a countercurrent flow of air and gas flows, and a regenerative heater rotor installed in this housing, containing a frame 1 consisting of hot 2 and cold 3 end disks and heat exchange cells 4 with internal channels 5, combined into a cellular structure, installed in the body of the regenerative heater with the possibility of rotation and alternately passing through it in countercurrent at least one heated cold air flow and at least one cooled hot gas flow, and the hot gas flow is introduced into the rotor through the hot end disk 2 of the rotor frame 1 and is discharged through the cold end disk 3 of the rotor frame 1 in the form of a cooled gas flow, and the cold air flow is introduced into the rotor through the cold end disk 3 of the rotor frame 1 and removed from it through the hot end disk 2 of the rotor frame 1 in the form of a heated air flow, while the air and gas flows are divided between on each disc of the rotor frame 1 by means of at least one radial 6 non-contact labyrinth seal located on the housing, and on each outer side of the hot 2 and / or cold 3 discs are separated from the external environment by means of at least one located on the housing of the circumferential 7 non-contact labyrinth seal of the corresponding rotor disc, moreover, by optimally regulating the flow rates and temperatures of the air and gas streams, the system for optimal regulation of the temperatures and flow rates of the air and gas flows maintains close or with the minimum possible temperature difference between the air and gas flows on the corresponding parts of the rotor, respectively, at the exit from the hot end disk 2 of the rotor frame 1 heated air flow leaving through the hot end disk 2 of the frame 1, and at the outlet of the cold end disk 3 of the frame 1 of the rotor of the cooled gas flow leaving through the cold end disk 3 of the frame 1 of the rotor, in the zone of the radial labyrinth seals 6 of the rotor on the body, and the ratio of the coefficients linear expansion of the materials of the hot 2 and cold 3 end disks of the frame 1 are chosen inversely proportional to the ratio of the increases in the average operating temperatures of the corresponding disks, and the cellular structure of the frame 1 of the heater rotor includes heat exchange cells 4, which perform in the form of separate glasses 10 with external hexagonal surfaces 11 and internal surfaces 12 of channels 5, in each of which an annular cavity 13 is made between these surfaces, which is filled with a thermal storage substance 14, which is made with the possibility of changing its state of aggregation at operating temperature and heat supply solid to liquid by melting, and when heat is removed, back by solidification, thus, reciprocating vibrational heat exchange is carried out due to the heat of melting or solidification of the thermal storage substance 14, while the hot gas stream is cooled by taking the heat of its melting from it with the thermal storage the air flow is heated by giving it the heat of solidification by the thermal storage substance 14.

A method for preventing thermal deformations of the rotor frame of a disc high-temperature rotating regenerative heater of a working fluid of a power plant for implementing a sequence of its actions, which includes controlling a system for regulating temperatures and flow rates of air and gas flows in a body of a regenerative heater with inlet and outlet channels by regulating temperatures and flow rates gas flows by means of regulation located on the body of the regenerative heater and in its inlet and outlet air and gas channels, made in it, respectively, with the possibility of supplying and removing air and gas flows in countercurrent flow, which determines the intensity of heat exchange between air and gas flows through a high-temperature rotating disk heater of the working fluid in the corresponding unit of the heat exchanger, the body with inlet and outlet channels made in it, intended respectively, for the supply and removal of air and gas flows and their regulation (in the drawings, they are conventionally not shown with separate positions), and a regenerative heater rotor installed in it, containing a frame 1 consisting of hot 2 and cold 3 end disks and heat exchange cells 4 with internal channels 5, integrated into a cellular structure, installed in the body of the regenerative heater with the possibility of rotation and alternately passing through it in countercurrent flow of at least one heated cold air flow and at least one cooled hot gas flow, and the hot gas flow is introduced into the rotor through the hot end disk 2 of the rotor frame 1 and output through the cold end disk 3 of the rotor frame 1 in the form of a cooled gas flow, and the cold air flow is introduced into the rotor through the cold end disk 3 of the rotor frame 1 and out of it through the hot end disk 2 frame of 1 rotor in the form of a heated air stream , while the air and gas flows are separated on each disk of the rotor frame 1 by means of at least one radial contactless labyrinth seal 6 located on the body, and on each outer side of the hot 2 and / or cold 3 end disks separate the air and gas flows from the external environment by means of at least one circumferential contactless labyrinth seal 7 of the rotor located on the housing. These features completely repeat the set of actions, properties and the known technical results achieved in the prototype, which consist in leveling the temperature field along the surfaces of hot and cold disks, which can reduce the extreme values of thermal deformations by increasing the uniformity of temperature distribution over these surfaces. Improving the quality of the high-temperature rotary disc heater is also achieved by the efficient operation of radial seals and high quality separation of air and gas streams. First of all, regardless of the type and design of the seals, the quality of their work increases and is characterized by stability and the absence of changes in the gaps and shape of the mating surfaces of the rotor and seals in this process, which is determined during operation by the constancy of the working gap between the housing and the rotor, the main prerequisite for which is the constancy of the rotor shape, which should not depend on changes in the temperature field distribution over the surface of the cold and hot end disks 2 or 3 and the thermal state of the heat exchange cells 4. Usually, a radial seal 6 is placed on the body opposite each of the end disks 2 and 3, separating the air and gas flows and reducing their overflows, and a circumferential seal 7, which eliminates air and gas leaks and reduces useless uneven heating or cooling of the outer surface of the frame and body due to leaks and leaks, leading to uneven heating and thermal deformations due to this uneven heat distribution and, accordingly, the appearance of an uneven temperature field.

To reduce the deforming effect of temperature drops on the frame 1 and reduce the values of its cylindrical thermal deformations without the need to create complex conditions and structures for leveling and stabilizing the temperature field along the supporting elements of the frame structure 1, it is necessary to change and create a new structure of frame 1 and the sequence of actions during its operation leading to a decrease in deformations of the frame 1. This is achieved through the use of the following distinctive features of the proposed method.

At the same time, by optimally regulating the flow rates and temperatures of the flows, the system for optimal regulation of the temperatures and flow rates of the air and gas flows (which is not conventionally shown in the drawings) maintains close or with the minimum possible temperature difference between the air and gas flows on the corresponding parts of the rotor, respectively, at the exit from the hot end disk 2 of the frame 1 of the rotor of the heated air flow coming out through the hot end disk 2 of the frame 1, and at the outlet of the cold end disk 3 of the frame 1 of the rotor of the cooled gas flow coming out through the cold end disk 3 of the frame 1 of the rotor, in the zone of the radial 6 seals of the rotor on casing, and the radial and circumferential seals 6 and 7 of the rotor on the casing are made labyrinthine, which makes it possible to reduce the possibility of air and gas flows between air and gas flows in the contours of the frame 1 during counter-current movement of air and gas and eliminate the negative effect on the thermal state of the frame 1 air and gas leaks along the perimeter of disks 2 and 3, and on the cold part of the rotor through the cold end disk 3 of the frame 1 of the rotor, cold air flow is introduced into the rotor, while through the cold end disk 3 of the frame 1 of the rotor, the outgoing cooled gas flow is removed in the radial zone seals 6 of the rotor on the body, made labyrinthine. That allows you to create a more uniform temperature field on all surfaces of the frame 1, including hot 2 and cold 3 disks, and is obvious, since these actions are similar to the known actions in the prototype and are the development of these known actions, because at close temperatures and thermophysical properties of heat exchange cells, the heat absorbed and released back by them should create conditions for creating a field of close temperatures on the surface of hot and cold disks 2 and 3. Absolutely the same temperatures on the indicated surfaces of the disks cannot be due to the fact that heat transfer with the required intensity occurs only with a sufficient difference temperatures between air or gas and heat transfer material of each heat exchange cell 4 in the most general form, the difference between which decreases exponentially. This constancy of the temperature field is possible, for example, due to the possibility of operation of the gas turbine hybrid plant in one optimal selected mode of operation of the turbine and the operation of the system for optimal regulation of the flow rates and temperatures of the flows and its regulation of the temperatures and flow rates of the air and gas flows. The optimality criterion can be close or with a minimum possible temperature difference movement of air and gas flows on the corresponding part of the rotor, respectively, at the exit from the hot end disk 2 of the rotor frame 1 of the heated air flow and the cooled gas flow leaving the rotor through the cold end disk 3 of the rotor frame 1 into the zone of the radial 6 seals of the rotor on the body, since this will be the most efficient use of waste heat.It should be noted that improving the uniformity of temperature distribution over the hot and cold discs 2 and 3 can be properly organized by choosing the correct design, thermophysical characteristics of heat exchange cells and the time of heat exchange (contact), so for example, you can change the air heating sector and you can choose a larger one than the gas cooling sector, or create a device for changing the specified sectors in the variable process of operation, which will allow more heat to be given off to the air from the mother of the heat exchange cell, with an equal amount of heat extraction from the gas to it, due to the greater temperature difference, therefore, the higher the efficiency of their operation, so that the efficiency of heat exchange should be greater with different initial conditions, and the closer the initial and final temperatures will be surfaces of the hot 2 and cold 3 end disks, respectively, for the heated air flow and, respectively, the cooled gas flow, since the cold air flow is introduced into the rotor through the cold end disk 3 of the rotor frame 1, and is removed from it through the hot end disk 2 of the rotor frame 1 in the form outgoing heated air flow, and the gas flow is introduced into the rotor through the hot end disk 2 of the rotor frame 1 and is discharged through the cold end disk 3 of the rotor frame 1 in the form of an outgoing cooled gas flow, the more heat these flows give and receive from heat transfer cells 4 in the process reciprocating vibrational heat transfer, the closer the temperature will be air and gas temperatures in the portions of the streams passing through the hot 2 and cold 3 end discs of the frame 1. Such design changes are described below.

The most effective development of the correct design can be a type of design when heat exchange cells 4 are made in the form of glasses 10 with external hexagonal surfaces 11 and internal surfaces 12 of channels 5, in each of which an annular cavity 13 is made between these surfaces, which is filled with a thermal storage substance 14, which, when operating temperature and heat supply, it changes its state of aggregation from solid to liquid by melting, and when heat is removed, back by solidification, that is, reciprocating vibrational heat exchange is carried out due to the heat of melting or solidification of the thermal storage substance 14, while the hot gas stream is cooled by sampling from it with a thermal storage substance 14 of the heat of melting, and the cold air stream is heated by giving it the heat of its solidification by the thermal storage substance 14.

For this, the design of the heat exchange cells has been changed, so that in each of the glasses between the outer hexagonal surface and the surface of the inner channel, an annular cavity 13 is made, which is filled with a thermal storage substance 14, which, at operating temperature and heat supply, has the ability to change its state of aggregation from solid to liquid melting, and when heat is removed, back by solidification, that is, reciprocating vibrational heat exchange is carried out due to the heat of melting or solidification of the thermal storage substance 14 with a melting point and solidification in the operating temperature range of a high-temperature rotating disk heater, while the hot gas stream is cooled by taking thermal storage substance 14 of the heat of its melting, and the cold air flow is heated by giving it heat storage substance 14 of the heat of its solidification.

In addition to crystalline and metallic materials with a narrow melting - solidification temperature range, it is possible to use amorphous substances with a wider temperature difference necessary for intensifying the initial heat transfer by obtaining a larger temperature difference between cold air or hot gas and a heat exchange cell, corresponding to the above requirements, the temperature range of the aggregate state change. Also, the execution of heat exchange cells 4 in the form of glasses 10 with external hexagonal surfaces 11 and with internal surfaces 12 of channels 5, in each of which between the external hexagonal surface 11 and the internal surface 12 of the channel 5 there is an annular cavity 13 filled with a thermal storage substance 14, which, when working temperature range and heat supply changes its state of aggregation from solid to liquid by melting, and when heat is removed, back by solidification, that is, reciprocating vibrational heat exchange is carried out due to the heat of melting or solidification of the thermal storage substance 14 in the operating temperature range of a high-temperature rotary disk heater, this is allows you to constantly maintain the maximum possible difference between gas or air and the inner surface of 12 channels 5 glasses 10 heat storage cells 4, since the temperature of the inner surface 12 cannot rise rapidly due to constant heat dissipation yes or heat supply with the participation of thermal storage substance 14 when its state of aggregation changes. This phenomenon also increases the efficiency of heat transfer in both directions of heat transfer, both from the cooled gas to each heat storage cell 4 and to the heated air from the heat storage cell 4, in addition to crystalline and metallic materials having a narrow melting-solidification temperature range, it is possible to use their mixtures, alloys or amorphous substances with the necessary corresponding to the above requirements, the temperature range of the change in the state of aggregation. In this case, the thermal storage substance allows maintaining the temperature of the inner surface 12 of the channel 5 of each heat exchange cell practically constant, it is obvious that this can be done taking into account the creation of the necessary temperature difference on the wall of the inner surface 12 of the channel 5 by creating a sufficient temperature head for the supply or removal of heat by changing the aggregate state of the thermal storage substance 14. The thinner the wall of the inner channel 5 and the higher its thermal conductivity, the lower the required temperature head required to transfer the amount of heat per unit time, that is, the higher the rate of its transfer. At the same time, the stiffness of the glass must be maintained by the required design strength, rigidity and shape stability of the hexagonal surface 11 and the end surfaces of each glass 10, which are less involved in alternating reciprocating vibrational heat exchange, but by maintaining a constant temperature (by their thermophysical thermal insulation due to thermal change the aggregate state of the intermediate heat transfer and thermal storage substance 14) the materials of the hex 11 and the end surfaces of the glasses 10 of the heat exchange cells 4, that is, the entire mass of materials and all surfaces involved in heat exchange of each glass 10 allows increasing the shape and size stability of each of the glasses 10 and reducing them influence on the thermal deformations of the frame 1. Thus, the thermal deformations of the external hexagonal surfaces 11 of the heat exchange cells 4 are reduced by increasing the constancy of the temperatures indicated, bearing the main power loads of the design active elements of heat exchange cells 4 by their thermophysical thermal insulation, that is, stabilization of the temperature field and maintaining the uniformity of the temperature field on the hexagonal surfaces 11 of the bearing structural elements of the glasses 10 of the heat exchange cells 4 when changing the operating modes of the power plant due to the elimination of the alternating thermal vibrational effect on the bearing structural elements, that is, parts adjacent to the hexagonal surfaces 11 during the heating and cooling of the heat exchange cells 4 by smoothing temperature fluctuations due to the absorption of the thermal storage substance 14 during its melting of excess heat from the hot gas and the return to cold air of the heat that is lacking for it by the thermal storage substance 14 when it solidifies.

When 14 complex compositions are used as a thermal storage substance, consisting of crystalline, metallic substances, their mixtures, alloys or substances with amorphous properties at the end of the half-cycle of heat exchange, the final heating temperature will rise above the average melting point of this substance, while heat exchange will occur with a reduced intensity , besides this, and due to the fact that the gas temperature will also drop significantly, for this reason this period of heat exchange cannot be decisive either in terms of the amount of heat transferred, or in terms of time and its intensity. But the beginning of the next half-cycle of heat transfer to the hot gas flow will occur at a large temperature difference, at which the heat of melting is cooled by the amorphous thermal storage substance taking the heat from the gas flow, will begin with a larger temperature difference between the cold air and the heated inner surface of the channel, which should sharply accelerate the heat transfer and heat transfer at the initial stage, both in time and in the amount of heat transferred per unit of time, which should also sharply increase the intensity of heat transfer by giving the heat of solidification to the cold air flow by a thermally accumulating amorphous substance, which will decrease by the end of the half-cycle due to a decrease temperature difference due to air heating and supercooling of the thermal storage substance below the average melting point of the amorphous substance, thus, on a new half-cycle, the temperature difference between the hot gas and the cooled amorphous thermal storage substance m will be larger and the cycle will repeat. In addition, mixtures or alloys, etc. can be used as a thermal storage substance. with the required properties. Obviously, the optimality and efficiency of the specified heat transfer process is calculated or selected empirically, based on the properties of the corresponding thermal storage substance, taking into account both thermal and thermophysical characteristics.

It should be noted that all known and new actions and work of new design features and design features that implement a method for preventing deformation of a high-temperature rotating disk regenerative heater of the working fluid of a power plant create conditions for a mutual increase in the quantitative indicators of heat transfer of reciprocating vibrational heat transfer, that is, increase the efficiency of the method.

The ratio of the coefficients of linear expansion of the materials of the hot 2 and cold 3 end disks is preferably chosen inversely proportional to the ratio of the increments in the average operating temperatures of the corresponding disks 2 and 3, since it is easier to manufacture them than to thermally insulate from the action of hot gases and cold air or to stabilize their operating temperatures, and heat exchange cells 4 are made in the form of glasses 10 with external hexagonal surfaces 11 and internal surfaces 12 of channels 5, in each of which an annular cavity 13 is made between these surfaces, filled with a thermal storage substance 14 at operating temperature and heat supply changing its state of aggregation from solid to liquid by removing the heat of its melting from the hot gas by the thermal storage substance 14, and by removing the heat - back by giving the heat of its solidification to the cold air by the thermal storage substance 14, that is, the return vibrational heat exchange carried out They are generated due to the heat of melting or solidification of the thermal storage substance 14, while the working gas is cooled by taking the heat of melting from it with the thermal storage substance 14, and the cold air is heated by giving it the heat of solidification by the thermal storage substance 14 and installed between the end discs 2 and 3 s, at least at least one point of rigid attachment 8 on each disc, every two points of rigid attachment of 8 glasses 10 on adjacent discs 2 and 3 are located in the diametrical plane of the section of their bases, located in the radial and / or tangential plane of the section of discs 2 or 3, passing through the axis of symmetry of each glass 10, and the gap between the glasses 10 is selected with the possibility of their free mutual radial expansion at the maximum operating temperature. These features allow, with the same distributions (as in analogs and the prototype) of temperatures on the surfaces of hot 2 or cold 3 disks, to obtain a new property - the same absolute linear expansion, that is, for correctly selected linear expansion coefficients for hot disk 2 at a high operating temperature due to low the linear expansion coefficient of its material will be the smaller possible absolute linear expansion for a high operating temperature and a relatively larger linear expansion of the cold disk 3 with a higher linear expansion coefficient of the material at a lower operating temperature. With the correct choice of the coefficients of linear expansion of the materials of the cold and hot end disks 2 and 3, corresponding to the inversely proportional ratio of increases in the average operating temperatures of disks 2 and 3, their absolute linear increases in size at the calculated or selected operating temperatures will be practically the same, and the general mushroom-like deformations of the frame 1 will be minimal, that is, the initial cylindrical shape of the frame 1 will not change. By increasing the average operating temperatures of the disks 2 and 3, the differences of the corresponding absolute operating temperatures minus the absolute initial temperature of the inoperative initial state of the frame 1 are selected, that is, in the inoperative state, cooled down to the initial ambient temperature selected by the manufacturer. Maintaining a constant temperature (by thermally changing the state of aggregation of the thermo-storage substance, that is, by stabilizing the temperature, by absorbing heat by the thermo-storage substance, as a result of which thermophysical thermal insulation will be carried out) of the load-bearing hexagonal surfaces 11 of each glass 10, with this phenomenon, the heat exchange process that occurs allows the temperature stability to be increased not only the external hex 11, but also its end surfaces, to reduce the change in their shape and size for each of the glasses 10 and to reduce their influence on the thermal deformation of the frame 1.

If the heat exchange cells 4 are made in the form of glasses 10 with external hexagonal surfaces 11 and an internal channel 5, in each of which an annular cavity 13 is made between these surfaces, filled with a thermal storage substance 14 at an operating temperature and heat supply changing its state of aggregation from solid to liquid melting, and when heat is removed - back by solidification, that is, the return vibrational heat exchange is carried out due to the heat of melting or solidification of the thermo-accumulating substance 14, while the working gas is cooled by taking the heat of melting from it with the thermo-accumulating substance 14, and the cold air is heated by giving it back substance 14 of the heat of solidification and is installed between the end discs 2 and 3 with the preferred possibility of limiting heat transfer between the cups and the discs, with at least one point 8 of rigid attachment on each disc 2 or 3, and at least every two points 8 of rigid on the attachment of the glasses on adjacent disks 2 or 3 are placed in the diametrical plane of the section of their bases, located in the radial and / or tangential to it the plane of the section corresponding to the disks 2 or 3, passing through the axis of symmetry of each glass 10, then this is achieved by eliminating the effect of thermal deformations cells 4 on the end discs 2 and 3 with a very significant temperature difference along the length of each cell 4, since the end surfaces in contact with the corresponding disc 2 or 3 have the possibility of free linear expansion and this does not cause deformation of the discs 2 and 3. The location of the points 8 of the rigid fastening the glasses 10 heat exchange cells 4 on adjacent disks 2 or 3 in the diametrical plane of the section of their bases, located in the radial plane of the section of the disks 2 or 3, that is, in the plane passing through the axis of their rotation in the radial direction, makes it possible to achieve a minimum temperature difference between the indicated dots. The location of the points 8 of the rigid attachment of the glasses 10 of the heat exchange cells 4 on the adjacent disks 2 or 3 in the diametrical plane of the section of their bases, located in the tangential to the radial plane of the cross section of the disks 2 or 3, makes it possible to achieve a given temperature difference between the indicated points, since these points are located in close or the same conditions of exposure to the corresponding air or gas flow for the selected inner surface 12 of the channel 5 in the glass 10 of each heat exchange cell 4 and will be in similar temperature conditions during the entire heat exchange process, because part of the air or gas flow in the specified channel 5 of the heat exchange cell 4 will have practically the same temperature distribution along the length of channel 5 and linear elongation along the axis of channel 5, as a result of which deformations of the shape of each cell 4 separately and of all cells 4 together will not be able to lead to a change in the shape of the frame 1, but will only cause it elongation and / or acc. The resulting rotation in the tangential direction of the points 8 of the rigid attachment of one end disk 2 or 3 relative to the other. Deformations of the position of the disks 2 or 3 due to the change in the length of the heat exchange cells 4 will be insignificant, since the temperature distribution gradient along the length of the glasses 10 will not change sign due to the thermophysical thermal insulation of the hexagonal parts 11 of the glasses 10 carrying the main loads, and the average temperature of the outer hexagonal surface 11 glasses 10 heat transfer cells 4 of the frame 1 due to the massiveness of the heat exchange part of the glasses 10 will change slightly, and temperature drops on the working surface of the internal channels of the glasses will lead to direct () or reverse) (barrel-shaped changes in the walls of their internal surfaces 12 channels 5, which with a sufficient mass of the glass 10 will slightly affect its working length.

Maintaining a constant temperature (by means of a thermal change in the state of aggregation of a thermal storage substance) can lead by maintaining a constant temperature of the end surfaces of the glasses 10 and to an increase in the temperature stability of disks 2 or 3 (this is in a hypothetically possible case of making them from the same materials) by means of a reciprocal vibrational flow of heat superheated or supercooled surface of the discs to the thermal storage substance 14 in the cavity 13 of each glass 10 and vice versa. To improve the flow of this process, the contacting end surfaces of the nozzles 10 and discs 2 or 3 can be connected to each other, for example, by soldering with a heat-conducting easily deformable material. Increasing the temperature stability of both disks 2 and 3 and of each glass 10 of each heat exchange cell 4 separately makes it possible to increase the shape and size stability of each of the glasses 10 and to reduce their effect on thermal deformations of the entire frame 1.

At the same time, the movement of air and gas streams with close temperatures in the area of the radial seals of the rotor of the rotary disk heater on the casing and the design of these seals 6 and 7 labyrinthine, under the above conditions, allows you to achieve a minimum gap and a high effective contactless seal by maintaining the flat shape of discs 2 or 3 ...

The execution of gaps between the outer hexagonal surfaces 11 of the walls of the glasses 10 of the frame 1 of the rotating disk heater, which are selected from the condition of the possibility of providing free mutual radial expansion relative to the axis of symmetry or point 8 of rigid attachment of each glass 10 relative to other glasses 10 at their maximum operating temperature without their mutual contact and the appearance of the possibility of deformation, such an implementation will exclude deformations from uneven heating of the surfaces of the disks 2 and 3 and the massive part of the glasses 10.

All of the above features allow achieving the following technical results:

1. Radial 6 and circumferential seals 7 of the rotor, installed on the body and made labyrinthine, which makes it possible to reduce the possibility of air and gas flow between the air and gas circuits during the rotation of the rotor frame 1 (with countercurrent movement of air and gas) and eliminate their negative influence on them shape when the thermal state of the frame changes and its thermal deformation due to the constant maintenance of the flat shape of disks 2 and 3.

2. Cold 3 and hot 2 end disks are made of materials, the ratio of linear expansion coefficients of which is chosen inversely proportional to the ratio of increases in average operating temperatures of the disks, which makes it possible to eliminate the mutual unevenness of thermal expansion of the disks under the influence of different operating temperatures on the cold 3 and hot 2 end disks.

3. Maintaining a constant temperature of each glass 10 (by thermally changing the state of aggregation of the thermal storage substance 14, in which the working gas is cooled by extracting the heat of melting from it with the thermal storage substance 14, and the cold air is heated by giving it the heat of solidification from the thermal storage substance 14) makes it possible to increase the stability of the shape and the size of each of the glasses 10 and reduce their effect on thermal deformations of the frame 1 with an additional positive effect on the shape of the frame of all the following phenomena and factors.

4. On cold 3 and hot 2 discs, the uniformity of the temperature field, respectively, the stability of the shape and their linear dimensions will be maintained automatically due to heat transfer and alternating heating and cooling of discs, glasses 10 of heat exchange cells 4.

5. Parallel and synchronous change in linear dimensions and maintenance of the shape and mutual dimensions of disks 2 and 3 will lead to a decrease in bending deformations of glasses 10, due to the constancy of the mutual radial distance of their rigid attachment points 8 from the axis of rotation on the corresponding part of disks 2 and 3.

6. Execution of heat exchange cells 4 in the form of glasses 10 with external hexagonal surfaces 11 and with internal surfaces 12 of channels 5 and installing them between end discs 2 and 3, with at least one point 8 of rigid attachment on each disc 2 or 3, and , at least the location of each two points 8 of the rigid attachment of the glasses 10 on adjacent disks 2 or 3, in the diametrical plane of the section of the bases of the glasses 10, the location of these points in the radial and / or tangential plane of the section of the disks 2 or 3 passing through the axis symmetry of each glass 10, will reduce the impact of thermal deformations of disks 2 and 3 on the shape of the frame 1 of the rotor.

7. The location of the points 8 of rigid attachment of the glasses 10 heat exchange cells 4 on adjacent discs 2 and 3 in the area of the inner surface 12 of the channels 5 of the glasses 10 allows to reduce thermal deformations of the glasses 10, since the temperature of the hexagonal bearing parts adjacent to the outer hexagonal surface 11 is kept constant for by changing the state of aggregation of the thermal storage substance 14 in the annular cavity 13 of the cup 10. And at the same time, each cup 10 can also be rigidly attached to the disk 2 or 3 along the entire perimeter of the channel 5, the inner surface of which can change its shape due to giving it less rigidity than have a carrier hex, and the ability to change the shape.

8. The choice of the size of the gap between the glasses 10 from the condition of achieving the possibility of their free expansion at the maximum operating temperature makes it possible to exclude the influence of uneven heating along the length of the channel 5 and the corresponding uneven linear in the radial direction expansion of the outer hexagonal surfaces 11 of the walls of the glass 10, and to exclude the influence of the resulting for this its mushroom-shaped glass 10 on the shape of the frame 1 of the heater.

9. In each of the glasses 10, between the outer hexagonal surface 11 and the inner surface 12 of the channel 5, an annular cavity 13 is made, filled with a thermal storage substance 14, which, at operating temperature and heat supply, changes its state of aggregation from solid to liquid by taking its heat from the hot gas melting, and when the heat of its solidification is removed back to the cold air flow, that is, with a melting and solidification point in the operating temperature range of a high-temperature rotating disk heater, while the working gas is cooled by taking the melting heat from it with a thermal storage substance, and cold air is heated by recoil he thermoaccumulating substance 14 of the heat of solidification. This allows you to align the temperature field on the supporting structures adjacent to the hexagonal surfaces of 11 glasses 10. In addition to crystalline and metallic materials with a narrow temperature range of melting - solidification, it is possible to use complex compositions of crystalline, metallic substances, their mixtures, alloys or substances with amorphous properties of substances with the necessary temperature range corresponding to the above requirements for the change in the state of aggregation.

10. On cold 3 and hot 2 disks, the uniformity of the temperature field can be maintained automatically due to optimal heat transfer from cold air and hot gas and alternate heating - cooling of disks 2 and 3, including due to the reciprocating oscillatory heat flow with the participation of glasses 10 heat exchange cells 4 For this reason, discs 2 and 3 can be made with lower structural strength and material consumption by using less heat-resistant materials.

11. Execution of heat exchange cells 4 in the form of glasses 10 with external hexagonal surfaces 11 and with internal surfaces 12 of channels 5, in each of which an annular cavity 13 is made between the external hexagonal surface 11 and the internal surface 12 of the channel 5, filled with a thermal storage substance 14, which, when operating temperature and heat supply, it changes its state of aggregation from solid to liquid by absorbing the heat of its melting, and when heat is removed back by giving off the heat of its solidification, that is, with a melting and solidification point in the operating temperature range of a high-temperature rotating disk heater, this allows you to maintain the maximum a possible difference between hot gas or cold air and the inner surface 12 of the channel 5 of the cups 10 of heat storage cells 4 throughout the entire length of the inner surface 12 of the channel 5, since its temperature cannot rise rapidly due to constant heat removal or heat through doda with the participation of thermal storage substance 14 when changing its state of aggregation. This phenomenon also increases the efficiency of heat transfer in both directions of heat transfer, both from the cooled gas to each heat storage cell, and to the heated air from the heat storage cell, while the working gas is cooled by extracting the melting heat from it by the thermal storage substance 14, and the cold air is heated by recoil he thermoaccumulating substance 14 of the heat of solidification. In addition to crystalline and metallic materials with a narrow temperature range of melting - solidification, it is possible to use amorphous and other substances with the necessary temperature range of the change in the aggregate state corresponding to the above requirements.

12. It should be noted that the use of amorphous thermal storage substances makes it possible to intensify heat transfer at the initial stage of each direction of heat transfer, because the final heating temperature of the thermal storage amorphous substance will be higher than the crystalline one, which will increase the thermal head and temperature difference at the initial stage of heat transfer, and upon cooling the final temperature of the thermally accumulating amorphous substance will be correspondingly lower, which will also increase the thermal head and temperature difference at the initial stage of heat exchange, which intensifies the heat transfer in the exchange cycle.

13. The location of at least two points 8 of rigid attachment of the glasses 10 of the heat exchange cells 4 on the adjacent discs 2 and 3 in the diametrical plane of the section of the bases of the glasses 4 of the heat exchange cells, located in the tangential plane of the section of the discs 2 and 3, i.e. in the plane perpendicular to the radial plane of the section, allows you to achieve a minimum temperature difference between the indicated points, since these points are located in close or identical conditions of exposure to air or gas for the selected working surface of each heat exchange cell 4 and will be in relatively close temperature conditions throughout the entire process heat exchange, because part of the air or gas flow in the specified channel 5 of the heat exchange cell 4 will have practically the same temperature distribution along the length of its internal channel 5, as a result of which thermal deformations of the linear dimensions and shape of each cell 4 separately and all cells 4 together will not will lead to a change in the cylindrical shape of the frame 1, but will only cause them to be centrally symmetric relative to the axis of rotation of the frame 1, a corresponding rotation of one end disk 2 or 3 relative to the other.

14. The largest barrel shape to compensate for the change in the volume of the thermal storage substance with a change in temperature and state of aggregation can be created by changing the shape on the thinnest inner cylindrical wall adjacent to the inner surface 12 of the channel 5.

15. The higher the uniformity of the distribution of air and gas temperatures over the disks, the less linear, along the axes of the channels 5 of the cups 10, changes in their length and the less the flexural mushroom-like deformation of the disk parts arising from uneven heating on the gas and air parts of the heater. And accordingly, it is possible to maintain a smaller gap in the labyrinth seals and reduce the flow between air and gas flows. In this case, the small unevenness of the dimensions of the indicated parts of the heater frame can be additionally compensated for by changing and adapting the shape of the elastic surface of the labyrinth seals.

16. In addition, the hexagonal shape of the surface 11 of the cups 10 makes it possible to increase the rigidity and resistance to shape-changing deformation of each individual thermal storage heat exchange cell 4 and each cup 10.

17. For a rigid structure of the nozzle 10, the inner cavity 13 can be filled with the thermal storage substance 14 not completely, that is, with the possibility of its volumetric expansion.

18. The change in volume when the aggregate state of the thermal storage substance 14 changes in the annular cavity 13 of the cup 10 can be compensated for by deforming the thin cylindrical wall of the channel 5 of the cup 10 by giving it a straight () or reverse) (barrel-shaped change in the cylindrical inner walls.

19. At the same time, the thermal storage substance allows maintaining the surface temperature of the inner channel of each heat exchange cell practically constant, obviously taking into account the creation of the necessary temperature difference by creating a sufficient temperature head of heat supply to change the state of aggregation of the thermal storage substance. The thinner the wall of the inner channel 5 is, the less the required temperature head will be. The stiffness of the nozzle 10 should be maintained by the required design strength, rigidity and stability of the part of the nozzle 10 adjacent to the surface 11 of the hexagonal shape and the end surfaces of each nozzle 10, which are less involved in reciprocating vibrational heat exchange.

The method can be implemented in a variety of constructs using all the actions of the method. The most preferred field of technology is a device for heating air and fuel in burners of thermal power plants.

The proposal is illustrated by drawings, which show:

FIG. 1 shows a preferred design for implementing the method in the form of a partially presented diagram of a power plant with a burner device using a high-temperature rotating disk regenerative heater of a working medium of a power plant located therein, designed for heating air, evaporating and heating liquid or gaseous fuel;

FIG. 2 shows a partial section of the frame of the high-temperature rotating disk regenerative heater of the working fluid of the power plant along adjacent closely spaced heat exchange cells;

FIG. 3 is a schematic perspective view of the rotor frame of a high-temperature rotating disk regenerative heater of a working fluid of a power plant with a complex of seals and a partial section;

FIG. 4 partially shows a diagram of a micro-turbine hybrid power plant for generating electric current with a high-temperature rotating disk regenerative heater of the working medium of the power plant and an approximate distribution of temperatures of the air and gas flows in it along the regenerative heater of the working medium.

The method of preventing thermal deformation of the cylindrical shape of the frame 1 of the rotor of the disk high-temperature rotating heater of the working fluid of the power plant, in all modifications of its design for a hybrid power plant, is implemented using the specified device of the high-temperature rotating disk heater in the following sequence of actions and achieves the specified technical results and solutions supplied by the technical tasks.

FIG. 1 shows a preferred design for implementing a method for preventing thermal deformations of the rotor frame of a disc high-temperature rotating regenerative heater of a working fluid of a power plant from the preferred area of use as part of a burner device, determined by the above properties and technical results achieved to the greatest extent when using the proposed structure of a high-temperature disc rotor frame a rotating regenerative heater of a working fluid of a power plant, for example, in the form of a partially presented diagram of an installation with a burner device and with a disc high-temperature rotating regenerative heater of a working fluid of a power plant located in it, intended in this case for heating additional air, evaporating liquid and / or heating gaseous fuel. The technical results and this predominant area of use will be determined by the previously indicated properties and the technical advantages achieved by the regenerative heater of the working fluid and the technical results inherent in these properties, which consist in increased reliability determined by maintaining the cylindrical shape of the frame 1 of the rotor of the regenerative heater under varying operating modes of the installation and thermal loads on it and in its high specific indicators, such as heat transfer per unit volume or mass of the frame 1 of the rotor of a rotating disk regenerative heater of the working fluid of a power plant, since the amount of heat transfer of the reciprocating vibrational heat exchange and the intensity of heat transfer in a separate heat exchange cell when the aggregate state of matter changes reciprocating vibrational heat transfer is much higher than the heat transfer of heating - cooling in a heat exchange cell of the same mass. Thus, it is possible to obtain the minimum dimensions of the burner and the regenerative heater in it with high operational reliability.

The burner device accommodates a disc high-temperature rotating structure of a regenerative heater of a working fluid of a power plant, which implements the method, which includes (see Figs. 1, 2 and 3) a frame 1, consisting of hot 2 and cold 3 end disks and heat exchange cells 4 with internal channels 5, in the form of cups 10 with external hexagonal surfaces 11 and surface 12 of the inner channel 5, points 8 of rigid attachment to the disks 2 and 3 of cups 10 of heat exchange cells 4, shown conventionally radial 6 and circumferential 7 contactless labyrinth seal. FIG. 2 conventionally shows the gas flow with a blackened arrow, and the white arrow shows the air flow from the side of the hot disk 2. Glasses 10 are rigidly fixed on disks 2 and 3 at rigid attachment points 8 with the possibility of forming gaps 9 between them, which are selected from the condition of free mutual radial from the axis at points 8 of expansion of glasses 10, since the magnitude of the displacement of the glass 10 relative to the axis depends on the points 8 of the rigid attachment of each glass 10. For example, with radial pairwise rigid attachment of the glass 10 to each disk, due to the difference in the coefficients of linear expansion of the glasses and discs, there will be ovalization of the shape of the glass 10 and local deformation of the change in the shape of the holes occur, and the disks 2 and 3 will not change their general shape, because with a sufficient length of the glass 10, it can bend slightly under the influence of the shaping of disks 2 and 3, without significantly affecting the cylindrical shape of the entire frame 1. The most preferred is the location of at least two points 8 gesture fastening the glasses 10 heat exchange cells 4 on adjacent discs 2 and 3 in the diametrical plane of the section of the bases of the glasses 10, located in the plane perpendicular to the discs 2 and 3, allows you to achieve a minimum change in the shape of the glasses 10, since these points are located in close or identical conditions of protection from exposure to cold air or hot gas relative to the inner surface 12 of the channel 5 of the cup 10 of each heat exchange cell 4 and will be in relatively close temperature conditions throughout the entire heat exchange process, because the outer hexagonal part adjacent to the hexagonal surface 11 of the cup 10 of each heat exchange cell 4 will be thermophysically insulated from the alternating flow of cold air or hot gas located in the specified internal channel 5 of the glass 10 of the heat exchange cell 4 and will have practically the same temperature distribution along the length of the hexagonal surface 11 of the glass 10, as a result of which thermal certain deformations of the linear dimensions and shape of each individual cell 4 separately and of all cells 4 together will not lead to a change in the shape of the frame 1, but will only cause a linear elongation of the glass 10. It is obvious that the mutual real displacement and deformation of the glasses 10 depends on the points 8 of their rigid attachment , the values of the coefficients of thermal expansion of disks 2 and 3 and nozzles 10 and their deformations, determined by the coefficient of linear thermal expansion of the material of the disks with a pairwise arrangement of pairs of points 8 of rigid attachment of the nozzle 10 on each disk.

The burner device 17 includes a branch pipe for supplying primary air (not shown in Fig. 1), a branch pipe 15 for supplying cold additional air from the cold side 18 of the regenerative heater of the working fluid; the working medium of the power plant, inside of which the air is heated from the heat of the heat exchange cells 4, while liquid and / or gaseous fuel can also be evaporated and heated, which is mixed with additional air in the form of vapors, comes out from the side of the hot disk 2 and through the pipe 16 for supplying hot additional air enters the burner device 17, mixes with the primary air, ignites, and from the hot side 19 enters again through the hot disk 2 into the heat exchange cells 4, heating them and reducing the temperature of the working fluid in front of the main fuel atomizer (shown conditionally by the dotted line on the cold side 18) of the burner 17, which makes it possible to effectively vaporize liquid and / or heat gaseous fuel and create optimal conditions for mixing primary air and a portion of the mixture of additional fuel with air prepared for ignition and preparation for efficient combustion of the main fuel in the flow of the main portion of the primary air, that is, ignition and combustion of the main portion of the fuel-air mixture. Adjusting the flow rate of additional air and additional amount of fuel allows you to achieve optimal conditions for the evaporation of the liquid part of the fuel and / or heating the gaseous (or gaseous liquid) fuel and subsequent heating of the primary air together with a portion of the main fuel over the entire range of primary air flow rates. Means of said regulation of the flow rates of additional air, additional fuel, as well as their relationship with the flow rate of primary air and the size of the portion of the main fuel are well known, very diverse, and therefore cannot be expediently considered in detail within the scope of this proposed invention.

Such a preferable use, that is, in a heat and power plant inside its burner, made with a disc high-temperature rotating regenerative heater of the working fluid, is due to the properties inherent in the proposed design of the heater based on such properties, in addition to the above, such as self-regulation of heat exchange, high reliability, performance, high specific indicators of heat transfer of heat exchange cells and accelerated heat transfer in them.

Since, due to its small dimensions, it is difficult and unreasonable to build in the means of automatic regulation of the control system for the supply of additional air and the changing conditions of combustion of an additional portion of fuel in order to further equalize the temperature field on the disks of the rotor frame of the heater used for preheating the primary air since this process does not require particularly precise regulation, then self-regulation of the process will be sufficient, achieved by maintaining a stable temperature of additional air and an additional portion of fuel at the stage of their combustion when changing in a wide range of their costs, since the heat release from the combustion of a larger portion of additional air and additional fuel will be larger and sufficient for the necessary heating. At the same time, the design of the heater must be compact, reliable and efficient in a wide range of additional air and fuel flow rates. All these properties and the associated technical results achieved are inherent in the proposed structure of the frame of the high-temperature rotating disk regenerative heater of the working fluid of the power plant.

In each of the glasses 10 (see Figs. 2 and 3) between the outer hexagonal surface 11 and the inner surface 12 of the channel 5, an annular cavity 13 is made, inside of which there is a thermal storage substance 14, which is configured to change its aggregate at the operating temperature and when heat is supplied. state from solid to liquid by melting, and when heat is removed, back by solidification, thus each heat exchange cell 4 is made with the possibility of reciprocating vibrational heat exchange by changing the state of aggregation of the thermal storage substance 14 with the possibility of extracting heat from the working gas due to the heat of its melting, and when the thermal storage substance 14 solidifies, cold air is heated, while the heat exchange cells 4 are installed between the end discs 2 and 3 with the possibility of rigid attachment to the discs 2 and 3 at the rigid attachment points 8. Such a design of the heat exchange cells 4 makes it possible to increase the efficiency of heat exchange, since the stable temperature of the inner surface 12 of the channel 5 of each heat exchange cell 4 makes it possible to increase the temperature difference between it and gas or air and to increase the heat head during heat transfer, which accelerates the heat exchange process. In addition to crystalline and metallic materials with a narrow melting - solidification temperature range, it is possible to use amorphous substances with the necessary temperature range of the change in the aggregate state corresponding to the above requirements.

In addition, due to the presence in each of the glasses 10 between the hexagonal surface 11 and the inner surface 12 of the channel 5 of an annular cavity 13, inside which a thermal storage substance 14 is located, which is capable of changing its state of aggregation from solid to liquid at the operating temperature, when heat is supplied. , and when heat is removed - back, then such a design of each heat exchange cell 4 with heat storage substance 14 in the annular cavity 13 allows stabilizing the temperature of the outer wall adjacent to the hexagonal surface 11 and bearing the main loads of each cell 4 and creating an insurmountable obstacle on the way the oscillatory process of heat flow, that is, in this case, the thermal storage substance 14 performs the function of thermophysical thermal insulation of the hexagonal surface 11 from the reciprocating oscillatory process of heat flow from the inner channel 5 within the limits of the possibility of heat absorption during melting or heat transfer with it on solidification, outside these limits, the usual heat transfer process will obviously take place.

In addition, the hexagonal shape of the outer surface 11 of each glass 10 makes it possible to increase the rigidity and resistance to shape-changing deformation of each individual thermal storage heat exchange cell 4 and compactly arrange all heat exchange cells 4 with the ability to control their free thermal expansion by creating a guaranteed gap between them, and, if necessary, changing the shape ...

Cold and hot end disks 2 and 3 are made of materials, the ratio of the linear expansion coefficients of which is inversely proportional to the ratio of increases in the average operating temperatures of the disks, which makes it possible to eliminate the mutual unevenness of thermal expansion of the disks under the influence of different operating temperatures, thus, when heated to operating temperatures and under conditions of return vibrational heat transfer, the effect of which on the end disks cannot be eliminated, the so-called mushroom-shaped deformation of the frame is reduced, in a wide range of changes in the consumption of additional air and additional fuel, especially if it is necessary to completely evaporate it to improve the combustion conditions. At the same time, the uneven deformation of individual mutually opposing parts of the end disks 2 and 3 under the influence of the corresponding incoming and hot gases and cold air, including before and after heat exchange, since the properties of the materials of the disks specified in clause 2 reduce their relative thermal deformation under conditions reciprocating vibrational heat exchange, since the temperature differences between the hot and cold parts of the end discs 2 and 3, which are under the influence of the correspondingly cooled hot gas flow from the burned additional fuel and the heated cold flow of additional air will be correspondingly proportional, thus the thermal deformations of these opposite parts end disks 2 and 3 will be proportional or almost equal, which will reduce the overall mushroom deformation of the entire frame 1, even taking into account the dynamics of the heat exchange process. Synchronous thermal deformations of parts of disks 2 and 3 under the simultaneous influence of temperature-variable air and gas flows cannot lead to excessive internal stresses in these disks, since they will change their dimensions in proportion to the temperature on their surface, that is, parts of the disks that are under the influence there will be slightly more hot gas than cold parts exposed to cold air, but the general ovalized cylindricity of these disks will not disrupt the overall performance of the frame 1, since when calculating and manufacturing the frame disks as a whole, the radial clearances between it and the body must obviously be chosen more than possible working thermal deformations of the frame, and the surfaces of the body, coupled with the end discs 2 and 3 with installed radial 6 and circumferential 7 seals, are made with the necessary unchanging clearances. For this reason, discs 2 and 3 can be made with lower structural strength and material consumption. It should be noted that the plane-parallelism of the hot and cold parts of each of the disks 2 and 3 will be preserved, since these parts will synchronously change their dimensions, which will increase the performance of the heater and its seals due to the preservation of the flat shape of their surfaces, which are adjacent to radial 6 and 7 circumferential seals installed on the body, that is, the gap between the seals and the discs will be within the design working clearances, which will not interfere with their performance.

Maintaining a constant temperature (by means of a thermal change in the state of aggregation of the thermal storage substance) of the walls bearing the main force loads adjacent to the outer hexagonal surfaces 11 of each glass 10 makes it possible to increase the stability of the shape and dimensions of each of the glasses 10, both at the location of the cold disk 3 and in the place the location of the hot disk 2 and reduce their deforming effect on the thermal deformations of the entire frame 1, since the walls carrying the main force loads adjacent to the hexagonal surfaces 11 of the heat exchange cells 4 will be at a relatively stable temperature as a result of thermophysical thermal insulation. By preserving the cylindrical shape of the frame and maintaining the constancy of the size and shape of its hexagonal parts carrying the main mechanical loads, a high-temperature rotating disk heater of the power plant due to stabilization of the temperature field of the supporting structural elements of the frame 1 and eliminating the possibility of the deforming effect of an uneven change in the temperature distribution field on the specified frame during reciprocal vibrational heat exchange in heat exchange cells 4 by increasing the constancy of the temperatures of the supporting structural elements by means of their thermophysical thermal insulation, that is, stabilizing the temperature field and maintaining the uniformity of the temperature field on the hexagonal surfaces of the supporting structural elements when changing the operating modes of the power plant due to the elimination of alternating thermal vibrational effects on the bearing hexagonal parts when heating and cooling heat exchange cells by smoothing the temperature fluctuations due to the absorption of the heat accumulating substance during its melting of excess heat from the hot gas and the return to cold air of the heat that is lacking for it by the thermal storage substance when it solidifies. In addition, a rather narrow range of melting - solidification of the thermal storage substance will stabilize the temperature of heating cold additional air and evaporation of additional liquid fuel, as a result of which the combustion conditions of the fuel-air mixture formed in this way will be predictable (standard, obtained in different ways, both calculated and experimental), permanent and effective. It is obvious that the stock (mass) of the thermal storage substance inside the cavities of the heat exchange cells of the frame should be selected with a margin for heating and evaporation of additional fuel in all operating modes of the high-temperature rotating disk regenerative heater of the working fluid in the burner of the power plant

A parallel and synchronous change in the linear dimensions and maintenance of the shape and mutual dimensions of the opposing parts of the disks will lead to a decrease in bending deformations of the glasses, due to the constancy of the synchronous mutual radial change in the distance of their attachment points from the axis of rotation on the corresponding part of the disks.

A high-temperature rotating disk regenerative heater of a working fluid of a power plant to prevent deformation of its frame during operation of a hybrid power plant or power plant is implemented using the above device of a high-temperature rotating disk regenerative heater of a working fluid of a power plant in the following sequence of actions and achieves the specified technical results and solution of the technical problem ...

FIG. 4 shows a hybrid microturbine plant and an approximate temperature distribution in it. A high-temperature rotary disk heater used for a hybrid power plant, intended primarily for use as part of a microturbine hybrid power plant for generating electric current, usually including a system for regulating temperatures and air and gas flows, operates as follows: after starting and reaching the operating mode through air filter air enters the compressor, where it is pre-compressed and enters a regenerator or a conventional regenerator similar in purpose to a microturbine installation in the form of a cold air stream, which is introduced into the rotor of a rotating regenerative heater from its cold side 15 through the cold end disk 3 of the rotor frame 1 , and removed from it through the hot end disk 2 of the rotor frame 1 to its hot side 16 in the form of an outgoing heated air flow, which enters the microturbine engine, the temperature of the gases at its outlet is controlled is controlled by the control system according to the readings of the temperature sensor, for example, by changing the supply of the required amount of fuel to the combustion chamber. After that, the gas flow is introduced from the hot side 16 into the rotor of the regenerative heater through the hot end disk of the rotor frame and is discharged through the cold end disk 3 of the rotor frame 1 on the cold side 15 in the form of an outgoing cooled gas flow.

In this case, the sequence of actions during the operation of the disk high-temperature rotating regenerative heater of the working fluid of the power plant implements a method for preventing thermal deformation of the shape of the rotor frame of the disk high-temperature rotating regenerative heater of the working fluid for a hybrid power plant, intended for use mainly as part of a hybrid power plant for generating electric current, usually including a system for regulating temperatures and flow rates of air and gas flows, a housing and a rotor installed in it, containing a frame 1 consisting of cold 3 and hot 2 end disks, heat exchange cells 4 in the form of glasses 10 with external hexagonal surfaces 11 and with a channel 5 and its inner surface 12 and their points 8 of rigid attachment to disks 2 and 3, installed in the heater body with the possibility of rotation and alternately passing through it in a counterflow, at least one heated air flow and at least one cooled gas flow, and the cold air flow is introduced into the rotor through the cold end disk 3 of the rotor frame 1, and is removed from it through the hot end disk 2 of the rotor frame 1 in the form of an outgoing heated air flow, and the hot gas flow is introduced into the rotor through the hot end disk 2 of the rotor frame 1 and is discharged through the cold end disk 3 of the rotor frame 1 in the form of an outgoing cooled gas flow, while the air and gas flows are separated on the rotor from each other and from each the outer side of the hot and cold discs by means of at least one radial 6 and one circumferential 7 rotor seals located on the housing (which in Fig. 1 and 2 not shown). These features completely repeat the totality, properties and the known technical results achieved in the prototype, which consist in leveling the temperature field to maintain a flat shape along the contact surfaces of hot and cold disks, which can reduce the extreme values of thermal deformations and increase the uniformity of their distribution over these surfaces.

To reduce the deforming effect of temperature drops on the frame 1 and reduce the magnitude of its thermal deformations without the need to create a complex cooling structure or conditions for leveling and stabilizing the temperature field along the load-bearing elements of the frame structure 1, it is necessary to change the structure of frame 1 and the sequence of actions with it, leading to a decrease in deformations frame 1. This is achieved through the use of the following distinctive features of the proposed method.

At the same time, by optimally regulating the flow rates and temperatures of the flows, the system for optimal regulation of temperatures and flow rates of the air and gas flows (not shown in Fig. 3) is maintained by regulating the heat content in the hot gas so that they are close or with the minimum possible temperature difference between the air and gas flows on the corresponding parts of the rotor, respectively, at the exit from the hot end disk 2 of the frame 1 of the rotor of the heated air flow coming out through the hot end disk 2 of the frame 1, and at the exit from the cold end disk 3 of the frame 1 of the rotor of the cooled gas flow leaving through the cold end disk 3 of the rotor frame 1, in the area of the radial seals 6 of the rotor on the body, made labyrinthine, and from the cold side 15 of the incoming incoming cold air flow and leaving the rotor of the cooled gas flow through the cold end disk 3 of the frame 1 of the rotor in the area of the radial 6 seals of the rotor on the body, executed l abyrinthine. Systems for optimal control of temperatures and flow rates of air and gas flows are diverse and consist of well-known control devices, which cannot be the subject of the proposed invention. This allows using well-known methods and well-known technical means to create a more uniform temperature field over the surfaces of the hot and cold disk, which is obvious, since these actions are similar to known actions in the prototype and are a development of these known actions. This is possible due to the normal operation of the gas turbine hybrid plant in one optimum selected mode of operation of the microturbine engine. It should be noted that the uniformity of temperature distribution over hot 2 and cold 3 discs can be properly organized by the optimal choice of the structure of the frame 1, heat exchange cells 4, their thermophysical and heat transfer characteristics and the time of heat transfer (contact), the higher their efficiency, the closer there will be the initial and final temperatures of the surfaces of the hot 2 and cold 3 disks, respectively, for the heated air flow and, respectively, the cooled gas flow, since the cold air flow is introduced into the rotor through the cold end disk 3 of the rotor frame, and removed from it through the hot end disk 2 of the frame 1 rotor in the form of an outgoing heated air flow, and the gas flow is introduced into the rotor through the hot end disk 2 of the rotor frame 1 and is discharged through the cold end disk 3 of the rotor frame 1 in the form of an outgoing cooled gas flow, as a result of which these flows, the more they give and receive heat from heat transfer cells, and the closer the air and gas temperatures will be in the parts of the flows passing through the hot 2 and cold 3 end disks of the frame 1, respectively.

With the correct choice of the ratio of the coefficients of linear expansion of the materials of the cold 3 and hot 2 end disks, which is chosen inversely proportional to the ratio of the increases in the average operating temperatures of the disks 2 and 3, while the heat exchange cells 4 are made in the form of glasses 10, each of which has an external hexagonal surface 11 and the inner channel 5 and is installed between the end discs 2 and 3, with at least one point 8 of the rigid attachment on each disc 2 or 3, and at least every two points 8 of the rigid attachment of the glasses 10 on adjacent discs 2 or 3 are located in the diametrical plane of the section of their bases, located in the radial and / or tangential plane of the section of disks 2 and 3 to it, passing through the axis of symmetry of each glass 10, and the gap between the glasses 10 is selected with the possibility of their free mutual expansion at the maximum operating temperature. These features allow at the same (as in analogs and prototype) temperatures on the surfaces of hot 2 and cold 3 disks to obtain the same linear expansion, respectively small for a higher operating temperature of the hot disk 2, that is, at a high operating temperature due to the small coefficient of linear expansion of its material with obtaining a relatively small linear expansion (change in the linear size) and at a lower operating temperature, obtain a relatively large linear expansion of the cold disk 3 with a higher coefficient of linear expansion of the material of the glasses 10, which, as a result of the effect of different temperatures, will lead to almost the same linear expansion of the hot 2 and cold 3 discs respectively for their selected or calculated operating temperatures. With the correct choice of the coefficients of linear expansion of the materials of the cold 3 and hot 2 end disks inversely proportional to the ratio of the increments in the average operating temperatures of the disks, their absolute linear increases in size at the calculated temperatures obtained from the results of the thermophysical calculation, or the workers selected experimentally, will be practically the same, and the general the mushroom-like deformations of the shape of the framework 1 will be minimal, so that the original cylindrical shape of the framework will not change.

Although it is obvious that in this case, in comparison with the cold state, due to the working heating and thermal expansion, the overall dimensions of the rotor frame 5 will change.

The previously described design features to improve the efficiency of heat transfer and to prevent thermal deformations of the rotor frame of the disk high-temperature rotating regenerative heater of the working fluid of the power plant can be attributed to the fact that the heat exchange cells 4 of the frame 1 of the rotor are made in the form of glasses 10 with external hexagonal surfaces 11 and channel 5 s inner surface 12 and installed between hot 2 and cold 3 end disks, with at least one point 8 of rigid attachment on each disc 2 or 3, and at least every two points 8 of rigid attachment of glasses 10 on adjacent discs 2 and 3 positioned in the diametrical plane of the section of their bases, located in the radial plane of the section of the disks 2 or 3, and passing through the axis of symmetry of each glass 10, then this is achieved by eliminating the effect of thermal deformations of the heat exchange cells 4, made in the form of glasses 10, on the end disks 2 and 3 even with very a significant temperature difference along the length of each glass 10 of the heat exchange cell, since the end surfaces of the glasses 10 in contact with the corresponding disc 2 or 3 have the possibility of free linear expansion and this does not cause deformation of the discs 2 and 3. The location of the points 8 of the rigid attachment of the glasses 10 of the heat exchange cells 4 on adjacent disks 2 and 3 in the diametrical plane of the section of their bases, located in the radial plane of the section passing through the axis of rotation of disks 2 or 3 in the radial direction, it allows to achieve a minimum temperature difference between the indicated points, since these points of disks 2 or 3 are behind the radial arrangement of the radial 6 seals 7 of the rotor simultaneously begin to be exposed to cold air or hot gas and will be in similar temperature conditions throughout the entire heat exchange process, even if they are made in pairs on each disc 2 or 3, they will be on one disc. The location of the points 8 of rigid attachment of the glasses 10 of the heat exchange cells 4 on the adjacent discs 2 or 3 in the diametrical plane of the section of their bases, located in the tangential plane of the section of the discs 2 and 3, i.e. in the plane perpendicular to the radial plane of its cross-section in one direction, preferably centrally symmetric, allows you to achieve a minimum linear elongation due to the presence of a temperature difference between these points, since these points are located in close or identical conditions of exposure to air or gas for the selected inner surface 12 of each heat exchange cell 4 and will be in relatively close temperature conditions throughout the entire heat exchange process, because part of the air or gas flow located in the specified channel of the heat exchange cell will have, taking into account the passing heat exchange with the thermal storage substance 14, practically the same temperature distribution over the inner surface 12 and along the length of the channel 5, as a result of which thermal deformations of the linear dimensions and shape of each cell 4 separately and of all cells together will not lead to a change in the shape of the frame 1 with a mushroom-like deformation, but will only cause the corresponding rotation of one end disk 2 or 3 relative to the other.

The hexagonal shape of the outer surface 11 of the cups 10 is chosen to simplify the selection and control of the gaps between them and their "tight packing" (distribution over the cross section of the end disks 2 and 3 of the frame 1).

At the same time, the movement of air and gas streams with close temperatures in the area of the radial seals 6 of the rotor of a rotary disk heater, located on the housing, and making these seals labyrinthine, under the above conditions, allows achieving a minimum gap and effective contactless seal, which should improve the quality of their work.

The execution of all gaps 9 between the outer hexagonal surfaces 11 of the glasses of the frame 1 of the rotating disk heater on each of the six outer edges of each outer hexagonal surface 11 of each glass 10 can be the same or calculated at the point 8 of the rigid attachment of the glass 10. The gaps 9 between the glasses 10 in any case are selected from the condition of the possibility of ensuring free mutual radial expansion of each glass 10 in the direction of the selected face and still possible rotation around the axis of the glass 10 or point 8 of its rigid attachment, relative to other glasses 10 of the frame 1 deformed in the same way at its maximum operating temperature without the possibility of them mutual contact and / or the possibility of deformation of the shape of the frame 1.

To reduce possible overflows of air and gas through the technological installation gaps between the nozzles 10 and the disks 2 and 3 into the gap 9, the end surfaces of the nozzles 10 and the disks 2 and 3 can be sealed to each other by any known method using known means and known heat-resistant sealing compounds, allowing carry out mutual linear normal and tangential displacements of the specified parts within the selected or calculated clearances.

Based on the above, the following can be stated.

The technical problem posed is solved by technical means and can be used in the proposed form in the national economy, therefore, the proposal meets the criterion of the invention "industrial applicability".

The proposal differs from the known method of operation, therefore, meets the criterion of the invention "novelty".

The proposal, when performing all known and new actions of the method, allows to achieve new, previously unknown technical results, therefore, meets the criterion of the invention "inventive step".

Claims (1)

A method for preventing thermal deformations of the rotor frame of a disc high-temperature rotating regenerative heater of a working fluid of a power plant, which includes control of a system for regulating temperatures and flow rates of air and gas flows in a body of a regenerative heater with inlet and outlet channels by controlling temperatures and flow rates of air and gas flows by means of control located in the housing and in its inlet and outlet air and gas channels, made in it, respectively, with the possibility of supplying and withdrawing in a countercurrent flow of air and gas flows, and a regenerative heater rotor installed in this housing, containing a frame 1 consisting of hot 2 and cold 3 end discs and heat exchange cells 4 with internal channels 5, combined into a cellular structure, installed in the body of the regenerative heater with the possibility of rotation and alternately passing through it in counterflow along of at least one heated cold air stream and at least one cooled hot gas stream, and the hot gas stream is introduced into the rotor through the hot end disk 2 of the rotor frame 1 and is discharged through the cold end disk 3 of the rotor frame 1 in the form of a cooled gas stream, and the cold the air flow is introduced into the rotor through the cold end disk 3 of the rotor frame 1 and is discharged from it through the hot end disk 2 of the rotor frame 1 in the form of a heated air flow, while the air and gas flows are divided among themselves on each disk of the rotor frame 1 by at least one radial contactless labyrinth seal 6, placed on the body, and on each outer side of the hot 2 and / or cold 3 end disks separate the air and gas flows from the external environment by means of at least one circumferential contactless labyrinth seal 7 located on the body opposite the corresponding disk rotor, characterized by , that by optimally regulating the flow rates and temperatures of the air and gas flows by the system of optimal regulation of the temperatures and flow rates of the air and gas flows, close or with the minimum possible temperature difference of the air and gas flows on the corresponding parts of the rotor, respectively, at the exit from the hot end disk 2 of the rotor frame 1 of the heated air flow leaving through the hot end disk 3 of the frame 1, and at the exit from the cold end disk 3 of the frame 1 of the rotor of the cooled gas flow leaving through the cold end disk 3 of the frame 1 of the rotor in the zone of the radial labyrinth seals 6 of the rotor on the body, and the ratio of the coefficients of the linear the expansion of the materials of the hot 2 and cold 3 end disks of the frame 1 are chosen inversely proportional to the ratio of the increases in the average operating temperatures of the corresponding disks, and the cellular structure of the frame 1 of the heater rotor includes heat exchange cells 4, which are performed in in the form of separate glasses 10 with external hexagonal surfaces 11 and internal surfaces 12 of channels 5, in each of which an annular cavity 13 is made between these surfaces, which is filled with a thermal storage substance 14, which is configured to change its state of aggregation from a solid into liquid by melting, and when heat is removed, back by solidification, thus, reciprocating vibrational heat exchange is carried out due to the heat of melting or solidification of the thermal storage substance 14, while the hot gas stream is cooled by taking the heat of its melting from the thermal storage substance 14, and the cold air the stream is heated by giving it the heat of its solidification by the thermal storage substance 14.

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