RU2716636C1 - Method of compensation of deformation of high-temperature rotary disc heat exchanger - Google Patents

Abstract

FIELD: heating equipment.

SUBSTANCE: invention relates to heat engineering and can be used in regenerative rotating disc heat exchangers. In the method of preventing thermal deformations of the frame of a rotating disc heat exchanger by making a cellular structure of the heat exchanger frame, where heat exchange cells are made in form of separate cups, cells are made with external hexagonal surfaces and internal channel, and end disks – from materials having different coefficients of temperature expansion, wherein ratio of coefficients of linear expansion of materials of cold and hot end discs is selected inversely proportional to ratio of increments of average operating temperatures of discs. Heat exchange cells are installed between end discs with at least one point of rigid attachment on each disc, and at least every two points of rigid attachment of cups on adjacent discs are located in diametral plane of section of their bases, located in radial and / or tangential to it plane of section of discs, passing through axis of symmetry of each shell, and the gap between the cups is selected with the possibility of their free mutual radial expansion at the maximum operating temperature. In the rotor to compensate for unavoidable thermal deformations, elastic silicone seals with siliconized pyrographite coating are additionally arranged on the outer surface of the discs on the projection of the gaps between the hexagonal cups, wherein width in circumferential direction of labyrinth seals in housing is more than any size of hexagonal cell in same direction, and speed of mutual movement of seals is greater than rate of cocurrent flow of leakages in gap between them.

EFFECT: higher efficiency of high-temperature rotary disk heat exchanger.

1 cl, 4 dwg

Description

Scope: thermal power engineering, mainly for gas turbine plants, for example, microturbines, mainly as part of a hybrid power plant for generating electric current. The inventive method of compensating thermal deformations of the frame of a rotating disk heat exchanger by manufacturing a cellular structure of the frame of the heat exchanger, where the cells are made in the form of separate glasses, and the heat exchanger disks from materials having different coefficients of thermal expansion.

A known method of compensating for the deformation of a high-temperature rotating disk heat exchanger, comprising a rotor containing a frame consisting of cold and hot end disks and heat exchanger cells, is installed in the heat exchanger housing with the possibility of rotation and alternating passage through it in countercurrent of at least one first heated gas volumetric air flow and at least one second cooled gas volumetric flow, and the incoming first air volumetric flow into the rotor through the first cold end disk of the rotor carcass, and leaves it through the second hot end disk of the rotor carcass in the form of an outgoing first heated air volume flow, and the second gas volume flow enters the rotor through the second hot end disk of the rotor carcass and leaves through the first cold the end disk of the rotor carcass in the form of an outgoing second cooled gas volumetric stream, while the first air and second gas volumetric flows are separated on the rotor from each external side of the hot and cold disks by means of at least one rotor seal located on the housing (see RF patent No. 20055960, applicant GAZ Production Association (Gorky Automobile Plant), Convention priority 26.05.1992 RU 92 5055034.

The main disadvantage of the known method of compensating for the deformation of a high-temperature rotating disk heat exchanger during its operation is the use of a frame with different stiffness and heat capacity, while the authors argue that this should lead to a convergence of temperatures of cold and hot end disks. This statement is controversial, since the stepped design of the body and the conical shape of the heat transfer elements cannot guarantee the heat transfer from gas to air through the intermediate solid heat carrier of the frame necessary for temperature equalization, because its heat capacity and transmission intensity cannot guarantee gas cooling and air heating to the same or close in temperature, because in this case the temperature difference between the gas, air and the intermediate solid coolant drops and effectively be equalizing their temperature on the end discs are dynamically over time quickly decreases and accordingly changes shape the carcass and giving it due to thermal deformations mushroom shape can not be avoided.

A known method of compensating for the deformation of a high-temperature rotating disk heat exchanger, including a system for controlling the 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, is installed in the heat exchanger body with the possibility of rotation and alternating passage through it in countercurrent at least one first heated gas volumetric flow of air and at least one second cooled gas about the volumetric flow, and the incident first air volumetric flow enters the rotor through the first cold end disk of the rotor carcass, and leaves it through the second hot end disk of the rotor carcass in the form of an outgoing first heated air volumetric flow, and the second gas volumetric flow enters the rotor through the second hot end disk of the rotor carcass and exits through the first cold end disk of the rotor carcass in the form of an outgoing second cooled gas volume flow, the first air and second gas volume The flows are separated on the rotor from each outer side of the hot and cold disks by means of at least one rotor seal located on the housing (see USSR copyright certificate No. 1345015, authors L.Ya. Eremenko and V.I. Grishin, publ. 10/15/87).

The main disadvantage of the known method of compensating for the deformation of a high-temperature rotating disk heat exchanger during its operation is the possibility of adapting the separation working seals to the mushroom-shaped frame of the rotating disk regenerator of radial seals of the gas and air flow separator, which is not very effective due to wear of the seals and the surface of hot and cold drives.

A known method of compensating for the deformation of a high-temperature rotating disk heat exchanger, including a system for controlling the 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, is installed in the heat exchanger body with the possibility of rotation and alternating passage through it in countercurrent at least one first heated gas volumetric flow of air and at least one second cooled gas about the volumetric flow, and the incident first air volumetric flow enters the rotor through the first cold end disk of the rotor carcass, and leaves it through the second hot end disk of the rotor carcass in the form of an outgoing first heated air volumetric flow, and the second gas volumetric flow enters the rotor through the second hot end disk of the rotor carcass and exits through the first cold end disk of the rotor carcass in the form of an outgoing second cooled gas volume flow, the first air and second gas volume The flows are separated on the rotor from each outer side of the hot and cold disks by means of at least one rotor seal located on the housing (see USSR copyright certificate No. 580410, inventors V.I. Grishin, V.S. Nazarenko, T.S. Dobryakov, S.Ya. Mikhailov and E.I. Socks, publ. 11/3/07).

The main disadvantage of the known method of compensating for the deformation of a high-temperature rotating disk heat exchanger during its operation is the possibility of adapting the separating working seals to the mushroom-shaped frame of the rotating disk regenerator for side seals of the gas and air flow separator, which is not very effective due to wear of the seals and the side surface of the frame hot and cold drives.

A known method of compensating for the deformation of a high-temperature rotating disk heat exchanger, including a system for controlling the 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, is installed in the heat exchanger body with the possibility of rotation and alternating passage through it in countercurrent at least one first heated gas volumetric flow of air and at least one second cooled gas about the volumetric flow, and the incident first air volumetric flow enters the rotor through the first cold end disk of the rotor carcass, and leaves it through the second hot end disk of the rotor carcass in the form of an outgoing first heated air volumetric flow, and the second gas volumetric flow enters the rotor through the second hot end disk of the rotor carcass and exits through the first cold end disk of the rotor carcass in the form of an outgoing second cooled gas volume flow, the first air and second gas volume The flows are separated on the rotor from each outer side of the hot and cold disks by means of at least one rotor seal located on the housing (see USSR author's certificate No. 208162, applicant Podolsky Machine-Building Plant named after Sergo Ordzhonikidze, publ. 12/29/67).

The main disadvantage of the known method of compensating for the deformation of a high-temperature rotating disk heat exchanger during its operation is the possibility of adapting to the mushroom shape of the rotary disk regenerator frame and the adaptive control mechanism of the working radial seals of the gas and air flow separator, which is not very effective due to constant wear of seals and surfaces of hot and cold discs.

A known method of compensating for the deformation of a high-temperature rotating disk heat exchanger, including a system for controlling the 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, is installed in the heat exchanger body with the possibility of rotation and alternating passage through it in countercurrent at least one first heated gas volumetric flow of air and at least one second cooled gas about the volumetric flow, and the incident first air volumetric flow enters the rotor through the first cold end disk of the rotor carcass, and leaves it through the second hot end disk of the rotor carcass in the form of an outgoing first heated air volumetric flow, and the second gas volumetric flow enters the rotor through the second hot end disk of the rotor carcass and exits through the first cold end disk of the rotor carcass in the form of an outgoing second cooled gas volume flow, the first air and second gas volume The flows are separated on the rotor from each outer side of the hot and cold disks by means of at least one rotor seal located on the housing (see RF patent No.RU 2441188, applicant BALKE-DURR GMBH (DE), publ. 01/27/2012.).

The main disadvantage of the known method of compensating for the deformation of a high-temperature rotating disk heat exchanger during its operation is a complex sequence of actions when trying to create a non-contact seal and maintain an optimal clearance in the seal using temperature-controlled complex rod mechanisms located on all surfaces of the seals, which is ineffective.

A known method of compensating for the deformation of a high-temperature rotating disk heat exchanger, including a system for controlling the 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, is installed in the heat exchanger body with the possibility of rotation and alternating passage through it in countercurrent at least one first heated gas volumetric flow of air and at least one second cooled gas about the volumetric flow, and the incident first air volumetric flow enters the rotor through the first cold end disk of the rotor carcass, and leaves it through the second hot end disk of the rotor carcass in the form of an outgoing first heated air volumetric flow, and the second gas volumetric flow enters the rotor through the second hot end disk of the rotor carcass and exits through the first cold end disk of the rotor carcass in the form of an outgoing second cooled gas volume flow, the first air and second gas volume The streams are separated on the rotor from each outer side of the hot and cold disks by means of at least one rotor seal located on the housing ,, (see USSR copyright certificate No. SU 613193 A1, authors Markman Yakov Abramovich, Gerashchenko Boris Avksentievich, Borodyansky Moisei Evseevich, Ushakov Ivan Kirillovich, Vainshtein Leonid Petrovich, publ. 10/27/2011.)

The main disadvantage of the known method of compensating for the deformation of a high-temperature rotating disk heat exchanger and the mechanism used to maintain gaps in the seals during its operation is a complicated sequence of actions when trying to create an almost non-contact seal and maintain an optimal minimum clearance along the entire length of the seals using temperature-controlled complex adjustable tracking mechanisms, seals located on all surfaces, which does not allow to achieve optimum minimum minimum clearance along the entire length of the seal due to the constant uneven wear of the seal plates, this will lead to uncontrolled contact of the seal and disruption of the seal during thermal deformation of the rotor.

A known method of compensating for the deformation of a high-temperature rotating disk heat exchanger, including a system for controlling the 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, is installed in the heat exchanger body with the possibility of rotation and alternating passage through it in countercurrent at least one first heated gas volumetric flow of air and at least one second cooled gas about the volumetric flow, and the incident first air volumetric flow enters the rotor through the first cold end disk of the rotor carcass, and leaves it through the second hot end disk of the rotor carcass in the form of an outgoing first heated air volumetric flow, and the second gas volumetric flow enters the rotor through the second hot end disk of the rotor carcass and exits through the first cold end disk of the rotor carcass in the form of an outgoing second cooled gas volume flow, the first air and second gas volume The flows are separated on the rotor from each outer side of the hot and cold disks by means of at least one rotor seal located on the housing (see patent for the invention of the Russian Federation No. 2432540, the applicant BALKE-DURR GMBH (DE), publ. 10/27/2011.)

The main disadvantage of the known method of compensating for the deformation of a high-temperature rotating disk heat exchanger during its operation is the complicated sequence of actions when trying to create a non-contact seal and maintain a removable flow rate of flowing air and gas flows through the optimal clearance in the seal by aspirating the air and / or gas of the leak components in the zone located on all surfaces of the seals, mainly in the radial direction, allowing stabilization amb the temperature distribution on the surface of the frame, which is inefficient.

A known method of compensating for the deformation of a high-temperature rotating disk heat exchanger, including a system for controlling the 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, is installed in the heat exchanger body with the possibility of rotation and alternating passage through it in countercurrent at least one first heated gas volumetric flow of air and at least one second cooled gas about the volumetric flow, and the incident first air volumetric flow enters the rotor through the first cold end disk of the rotor carcass, and leaves it through the second hot end disk of the rotor carcass in the form of an outgoing first heated air volumetric flow, and the second gas volumetric flow enters the rotor through the second hot end disk of the rotor carcass and exits through the first cold end disk of the rotor carcass in the form of an outgoing second cooled gas volume flow, the first air and second gas volume The flows are separated on the rotor from each outer side of the hot and cold disks by means of at least one rotor seal located on the housing (see Patent for the invention of the Russian Federation No.RU 2119127 C1, Applicantbau Rotemole Brandt und Kritzler GmbH (DE), publ. 09/20/1998.)

The main disadvantage of the known method of compensating for the deformation of a high-temperature rotating disk heat exchanger during its operation is a complex sequence of actions when trying to create a non-contact seal and maintain separation of the air and gas cavities through the optimal clearance in the seal using a flow of separation gas that compensates and prevents air and gas overflow and radial seals form seal surfaces located in a common plane and without zorno turning into each other at the junction and with the ability to automatically maintain a gapless contact, allowing to stabilize the temperature distribution on the surface of the frame, which is ineffective.

A known method of compensating for the deformation of a high-temperature rotating disk heat exchanger, including a system for controlling the 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, is installed in the heat exchanger body with the possibility of rotation and alternating passage through it in countercurrent at least one first heated gas volumetric flow of air and at least one second cooled gas about the volumetric flow, and the incident first air volumetric flow enters the rotor through the first cold end disk of the rotor carcass, and leaves it through the second hot end disk of the rotor carcass in the form of an outgoing first heated air volumetric flow, and the second gas volumetric flow enters the rotor through the second hot end disk of the rotor carcass and exits through the first cold end disk of the rotor carcass in the form of an outgoing second cooled gas volume flow, the first air and second gas volume The flows are separated on the rotor from each outer side of the hot and cold disks by means of at least one rotor seal located on the housing (see USSR copyright certificate No. 881517, applicant Gorky Automobile Plant (Production Association "GAZ"), publ. 11/15/1981).

The main disadvantage of the known method of compensating for the deformation of a high-temperature rotating disk heat exchanger during its operation is that in the event of thermal deformations (see Fig. 1 of the USSR copyright certificate No. 881517) of the rotor 6, its warpage is eliminated by strict fixation of the rotor 6 relative to the housing 1 by means of ring interaction 14 with an annular groove 13 through anti-friction linings 15. This eliminates the bias of the sealing surfaces of the rotor 6, which eliminates the opening of the gaps between these surfaces and seals 9 and 10 and thereby reduces the flow of heat-exchanging media - air and gas. The mechanical alignment of the mushroom shape of the heat transfer surface of the rotor frame cannot be fully compensated, for example, due to the presence of technological gaps in the joints.

A known method of compensating for the deformation of a high-temperature rotating disk heat exchanger, including a system for controlling the 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, is installed in the heat exchanger body with the possibility of rotation and alternating passage through it in countercurrent at least one first heated gas volumetric flow of air and at least one second cooled gas about the volumetric flow, and the incident first air volumetric flow enters the rotor through the first cold end disk of the rotor carcass, and leaves it through the second hot end disk of the rotor carcass in the form of an outgoing first heated air volumetric flow, and the second gas volumetric flow enters the rotor through the second hot end disk of the rotor carcass and exits through the first cold end disk of the rotor carcass in the form of an outgoing second cooled gas volume flow, the first air and second gas volume The flows are separated on the rotor from each outer side of the hot and cold disks by means of at least one rotor seal located on the housing (see USSR copyright certificate No. SU 800579 A1, applicant Gorky Automobile Plant (Production Association GAZ), publ. 01/30/1981)

According to the applicant, the execution on the hot side of the frame of the transverse channels communicated by the inlet openings with the air inlet pipe and the output holes with the air outlet pipe allows cooling of the end face or the disk of the frame on the hot side, to reduce warpage of the frame by equalizing the temperature of the surface of the frame and to increase the reliability of operation regenerator. But at the same time, the applicant does not take into account the possibility of mushroom 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 the one hand by cold air heated by them, and on the other, by hot gases, as a result of which thermal mushroom-like deformations of the frame under their influence cannot be compensated by smaller deformations of the cooled hot disk.

A known method of compensating for the deformation of a high-temperature rotating disk heat exchanger, including a temperature and air flow control system for air and gas flows, a housing and a rotor installed in it, comprising a frame consisting of cold and hot end disks and heat-exchange cells, is installed in the heat exchanger housing with the possibility of rotation and alternating passage through it in countercurrent of at least one first heated gas volumetric air stream and at least one in of a cooled gas volume stream, the incident first air volume stream entering the rotor through the first cold end disk of the rotor carcass, and leaving it through the second hot end disk of the rotor carcass as an outgoing first heated air volume flow, and the second gas volume flow the rotor through the second hot end disk of the rotor carcass and exits through the first cold end disk of the rotor carcass in the form of an outgoing second cooled gas volumetric flow, the first air shnyj and a second gas volume flows on the rotor are separated from each outer side of the hot and cold drive via at least one rotor seal disposed on the housing (see. RF patent №RU 2623133 C1, applicant Federal State Budgetary Educational Institution of Higher Education "Moscow Polytechnic University" (RU), publ. 01/27/2012.)

According to the applicant, the execution on the hot side of the frame and around the heat-exchange cells of the transverse cooling channels communicated by the inlet openings with an air inlet pipe and the output holes with an air outlet pipe allows cooling of the end face or disk of the frame on the hot side and the frame with heat-exchange cells, to reduce warping of the frame by equalizing the surface temperature of the disk and the cells of the frame and to increase the reliability of the regenerator. But at the same time, the applicant does not take into account the possibility of mushroom 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 the one hand by cold air heated by them, and on the other hand, by hot gases and heat exchange cells in the form of heat-transferring packets are rigidly connected with the walls of the frame, as a result of which thermal deformations of the frame under their influence cannot be compensated by smaller deformations holes of the cooled hot disk and the walls of the cells of the frame, and cooling will not be able to maintain the frame in an undeformed state, since the outer walls of the cells of the frame are not thermally insulated from their inner part and are rigidly connected to it, for this reason the real state and frame deformations are determined by heating from heat transfer heat packages and their mechanical deformation effects on the frame and the deformation of the frame due to the uneven radial distribution of temperatures on the supporting structures of the frame.

The closest technical solution is the device and operation of a rotating disk regenerator, according to the patent of the Russian Federation No. RU 2623133 C1, which is closest to the invention according to the problem being solved and has the greatest number of actions coinciding with the actions according to the invention.

The technical task of the proposed invention is to increase the operability of a high-temperature rotating disk heat exchanger by using a sequence of actions and a new set of material means to prevent deformation of its shape under the influence of a constantly acting and changing temperature field acting on a rotating disk heat exchanger, that is, by maintaining the cylindrical shape of a high-temperature rotating disk heat exchanger .

When implementing the actions of the method of compensating for the deformation of a high-temperature rotating disk heat exchanger, the technical problem is solved and the following technical results are described, which are described below.

The technical problem is solved by the fact that the method is implemented in the following sequence of actions on material means to prevent deformation of the shape of a high-temperature rotating disk heat exchanger, includes a temperature and air flow control system for air and gas flows, a housing and a rotor installed in it containing a frame consisting of cold and hot end disks and heat exchange cells installed in the heat exchanger housing with the possibility of rotation and alternate passage through it in countercurrent flow of at least one first heated air volumetric stream and at least one second cooled gas volumetric stream, the incident first air volumetric stream entering the rotor through the first cold end disk of the rotor carcass, and out of it through the second hot the end disk of the rotor carcass in the form of an outgoing first heated air volumetric flow, and the second gas volumetric flow enters the rotor through the second hot end disk of the rotor carcass and exits through the first cold Ortsevo disc rotor frame to form a second outgoing cooled gas volume flow, wherein the first air and the second gas volume flows on the rotor are separated from each outer side of the hot and cold drive via at least one rotor seal disposed on the housing. These features completely repeat the totality, properties and well-known technical results achieved in the prototype, which consist in leveling the temperature field on the 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. Improving the quality of work of a high-temperature rotating disk heat exchanger is achieved by the efficient operation of seals and high quality separation of air and gas flows. First of all, regardless of the type and design of the seals, their quality of work is characterized by stability and the absence of changes in the shape of the seals in this process, which is determined during operation by the constancy of the working gap between the casing and the rotor, the main premise of which is the constancy of the shape of the rotor, which should not depend on changes in the distribution of the temperature field over the surface of the cold and hot end disks and the thermal state of the heat exchange cells. Typically, a radial seal is placed on the housing opposite each of the end disks, separating the first air and second gas flows and reducing their overflows, and a circumferential seal that eliminates air and gas leaks into the frame and the environment.

Reducing the deforming effect of temperature differences on the frame and reducing its thermal deformations of the form is impossible without creating the necessary complex conditions and structures for aligning and stabilizing the temperature field along the load-bearing elements of the frame structure, and for this it is necessary to change the frame structure and the sequence of actions leading to a decrease in deformations frame. This is achieved through the use of the following distinctive features of the proposed method.

Moreover, by regulating the flow rates and temperature of the flows, the temperature and air and gas flow rate control system maintains flows close to or with the smallest possible temperature difference at the hot part of the rotor, respectively, at the exit of the hot end disk of the rotor cage of the outgoing first heated air volumetric flow and entering the hot rotor second gas volumetric flow through the second hot end disk of the rotor frame in the area of the radial seals of the rotor on the housing, made lab and on the cold part of the rotor, through the first cold end disk of the rotor carcass, the incoming first air volume flow enters the rotor, and through the first cold end disk of the rotor carcass leaves the outgoing second cooled gas volume flow in the area of the radial and circumferential rotor seals mounted on the housing and made labyrinth. This allows you to create a more uniform temperature field on the surfaces of the hot and cold disks and is obvious, so 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 the heat exchange cells, the heat absorbed and returned back by them should create conditions for obtaining a field of close temperatures on the surface of hot and cold disks. There cannot be absolutely identical temperatures on the indicated surfaces of disks and heat transfer cells due to the fact that heat transfer with the necessary intensity occurs only with a sufficient temperature difference between air or gas and the heat transfer material of each cell. This constancy of the temperature field is possible due to the possibility of the gas turbine hybrid unit operating in one optimal selected mode of operation of the turbine and the operation of the flow rate and temperature control system and its regulation of temperature and air and gas flow rates. It should be noted that the uniformity of the temperature distribution over the hot and cold disks can be correctly organized by choosing the thermophysical characteristics of the heat exchange cells and the heat transfer (contact) time, the higher their efficiency, the closer the initial and final temperatures of the surfaces of the hot and cold disks, respectively, for the first heated volumetric air flow and, accordingly, the second cooled gas volumetric flow, since the incoming first air volumetric flow tons into the rotor through the first cold end disk of the rotor carcass, and leaves it through the second hot end disk of the rotor carcass in the form of an outgoing first heated air volume flow, and the second gas volume stream enters the rotor through the second hot end disk of the rotor carcass and exits through the first cold end disk of the rotor cage in the form of an outgoing second cooled gas volumetric flow, the more heat these flows give and receive from heat transfer cells, the closer the air and gas temperatures in parts n currents flowing through the hot and cold end discs and frame heat exchanger cell. Differences in operating temperatures of air and gases will lead to a small difference in the linear elongation of the glasses and a slight bend of the discs.

In the rotor to compensate for these inevitable thermal deformations, elastic silicone seals coated with siliconized pyrographite are additionally installed, located on the outer surface of the disks according to the projection of the gaps between the hexagonal cups, and the width in the circumferential direction of the labyrinth seals in the housing is larger than any size of the hexagonal cell in the same direction, and the speed of the mutual movement of the seals is greater than the speed of the satellite flow of overflows in the gap between them. The preservation of elasticity of silicone and its heat resistance and stabilization of properties are determined by deepening into the colder part of the disks and the heat-dissipating and thermostabilizing ability of the inner hexagonal surface of the glasses adjacent to it. In case of urgent need, the internal gaps between the glasses can be further cooled by known means and methods. It should be noted that the inner channel of each glass can be filled with any heat-accumulating composition, and its density and porosity is determined by the optimal ratio of aerohydraulic resistance and heat-absorbing properties of the material of the filler composition. In this case, parasitic pore volumes can be selected from the condition of minimal mutual transfer of air and gas. If necessary, these spaces under the labyrinth seals can be purged with inert gas, air or gas, which will prevent air or gas from entering the adjacent stream. A satellite gas stream that moves in the direction of the moving part of the rotor.

The ratio of the linear expansion coefficients of the materials of the cold and hot end disks is chosen inversely proportional to the growth rate of the average working temperatures of the disks, the heat exchange cells being made in the form of cups with external hexagonal surfaces and an internal channel and installed between the end disks with at least one fixed point each disk, every two points of hard mounting of glasses on adjacent disks are located in the diametrical plane of the cross section of their bases, the plane of the disk cross section lying in the radial and / or tangential plane to it passing through the axis of symmetry of each glass, and the gap between the glasses is selected with the possibility of their mutual mutual radial expansion at maximum operating temperature. These features make it possible to obtain a new property with the same temperature distributions (as in the analogues and prototype) of the temperatures on the surfaces of the hot or cold disks — the same linear expansion of the disks, for example, for a hot disk at a high working temperature due to the small coefficient of linear expansion of its material, we can obtain its small linear elongation and relatively large linear expansion of the cold disk with a higher coefficient of linear expansion of the material at a lower working temperature us to obtain a predetermined linear expansion. With the right choice of the linear expansion coefficients of the materials of the cold and hot end disks, corresponding to an inversely proportional ratio of the growth of the average working temperature of the disks, their absolute linear increase in size at the calculated or selected working temperatures will be almost the same, and the overall mushroom-like deformations of the frame will be minimal, i.e. the initial cylindrical the shape of the frame will not change. By increasing the average operating temperature of the disks, the differences of the corresponding absolute operating temperatures are selected minus the absolute initial temperature of the inoperative initial state of the frame.

If the heat-exchange cells are made in the form of cups with external hexagonal surfaces and an internal channel and are installed between end disks with at least one hard-mount point on each disc, and at least every two hard-mount points of the cups on adjacent disks are located the diametrical plane of the cross section of their bases, located in the radial and / or tangential to it plane of the cross section of the corresponding disk, passing through the axis of symmetry of each glass, this eliminates the effect of thermal deformations of the cells on the end disks at a very significant temperature difference along the length of each cell, since the end surfaces of the glasses of the heat-exchange cells in contact with the corresponding disk have the possibility of free linear expansion and this does not cause deformation of the disks. The location of the points of rigid attachment of the glasses of the heat-exchange cells on adjacent disks in the diametrical plane of the section of their bases located in the radial plane of the section of the disks, that is, in the plane passing through the axis of their rotation in the radial direction, allows to achieve a minimum temperature difference between these points, since these points at the same time begin to be exposed to the corresponding flow of air or gas and will be at close temperature conditions throughout the entire heat exchange process on even if they reside on the same disk. The location of the points of rigid attachment of the glasses of heat-exchange cells on adjacent disks in the diametrical plane of the cross section of their bases, located tangential to the radial plane of the cross section of the disks, allows you to achieve a given temperature difference between these points, since these points are located in close or identical conditions of exposure to the corresponding air flow or gas for the selected inner surface of the channel in the glass of each heat-exchange cell and will be in close temperature differential conditions during the entire heat transfer process, because the part of the air or gas stream located in the specified channel of the heat exchange cell will have almost the same temperature distribution along the channel length and linear elongation along the channel axis, as a result of which the deformation of the shape of each cell separately and all cells together does not can lead to a change in the cylindrical shape of the frame, and will only cause its extension and / or a corresponding rotation in the tangential direction of the points of rigid fastening of one end disk relates flax other. The deformations of the position and bending of the disks due to changes in the length of the heat exchange cells will not be significant, since the gradient of the temperature distribution along the length of the glasses will not change sign, and the average temperature of the outer hexagonal surface of the glasses of the heat transfer cells of the frame due to the massiveness of the heat exchange part of the glasses and a limited cycle time heat transfer will vary slightly, and temperature differences on the working surface of the inner channels of the glasses will lead to both direct () and reverse) (barrel-shaped changes in their walls, which with a sufficient mass of the glass will slightly affect its working length.

In this case, the movement of air and gas flows with similar temperatures in the area of the radial seals of the rotor of the rotating disk heat exchanger on the casing and the performance of the radial and circumferential seals are labyrinth, under the above conditions, it is possible to achieve a minimum clearance and a high effective non-contact seal. In the rotor to compensate for the inevitable thermal bending deformations of the disks, elastic silicone seals with a coating of siliconized pyrographite are additionally installed, located on the outer surface of the disks according to the projection of the gaps between the hexagonal cups, and the width in the circumferential direction of the labyrinth seals in the housing is greater than any size of the silicone seal of the hexagonal cell in this the same direction, and the speed of the mutual movement of the seals is greater than the speed of the satellite flow of overflows in the gap between them.

The gaps between the external hexagonal walls of the glasses of the frame of the rotating disk heat exchanger, which are selected from the condition of providing free mutual radial expansion relative to the axis of symmetry of each glass relative to the others at its maximum working temperature without mutual contact and the possibility of deformation, this design eliminates deformation from uneven heating surfaces of disks and massive parts of glasses.

The proposal is illustrated by drawings, which show:

In FIG. 1 shows a partial section through the frame of a heat exchanger along one heat exchanger cell, along labyrinth seals on the housing and along silicone seals on the rotor, which are shown conditionally on one side of the rotor;

In FIG. 2 is a schematic isometric view of a heat exchanger frame with a set of non-contact seals in a casing and a partial section.

In FIG. Figure 3 shows the location of the silicone seals along the projections of the gaps between the hexagonal surfaces of the glasses.

In FIG. 4 shows a diagram of a hybrid power plant for generating electric current and an approximate temperature distribution of air and gas flows in it.

The device of a high-temperature rotating disk heat exchanger that implements the method includes (see Fig. 1 and 2) a frame 5 consisting of hot 2 and cold 3 disks and heat-exchange cells in the form of glasses 4 with external hexagonal surfaces and an internal channel, points 1 of rigid attachment to the disks of the glasses 4 heat transfer cells, shown conditionally radial 6 and circumferential 7 non-contact labyrinth seal on the housing. In FIG. 2, the gas flow is shown blackened by an arrow, and the air flow from the side of the hot disk 2 by the white arrow. The glasses 4 of the frame 5 are rigidly fixed to the disks 2 and 3 at the hard points 1 with the possibility of formation of gaps 10 between them, which are selected from the condition of free mutual radial from their axis (possibly symmetrical) the expansion of the glasses 4, since the magnitude of the displacement of the glass relative to the axis depends on the places of rigid fastening of the glass. So, for example, with a radially pairwise rigid attachment of the cup to each disk, due to the difference in the coefficients of linear expansion of the cups and disks, the shape of the cup will be ovalized and local deformation will change the shape of the holes in the disks, and the disks will not change their general shape, because with a sufficient length under the influence of the shape of the disks, it can bend slightly, without significantly affecting the cylindrical shape of the entire frame 5. The location of at least two points 1 of the fastening of the glasses 4 heat transfer cells nuts on adjacent disks 2 and 3 in the diametrical plane of the cross section of their bases, located in the tangential plane of the cross section of the disks, i.e. in the plane perpendicular to the radial plane of the section, it is possible to achieve a minimum 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 of the channel of the glass 4 of each heat transfer cell and will be in relatively close temperature conditions for of the entire heat transfer process, because part of the air flow or gas located in the specified inner channel of the cup 4 of the heat exchange cell will have almost the same temperature distribution along the channel length, as a result of which thermal deformations of the linear sizes and shapes of each individual cell separately and of all cells together will not lead to a change in the shape of the frame, but will only cause linear elongation and / or corresponding rotation of one end disk relative to the other. Obviously, the mutual real displacement of the glasses and disks depends on the points of their rigid attachment, changes in the distribution of the temperature field and the magnitude of thermal deformations, determined by the coefficient of temperature linear expansion of the material of the glass and the corresponding disk.

The method of compensating for the deformation of the shape of a high-temperature rotating disk heat exchanger for a hybrid power plant is implemented using the specified device of a high-temperature rotating disk heat exchanger in the following sequence of operations during its operation and reaches the indicated technical results and solving the technical problem.

In FIG. 4 shows a hybrid microturbine installation and an approximate temperature distribution therein. A high-temperature rotating disk heat exchanger is designed for a hybrid power plant, used mainly as part of a hybrid power plant for generating electric current, usually including a temperature and air flow rate control system that works as follows: after starting and operating mode through the air filter, air enters the compressor, where it is precompressed and enters the recuperator or usually for microturbine plants regenerated in the form of an incident first air volumetric flow that enters the rotor of the regenerative heat exchanger from its cold side 8 through the first cold end disk of the rotor frame, and leaves it through the second hot end disk of the rotor frame to its hot side 9 in the form of an outgoing first heated air the volume flow that enters the microturbine engine, the temperature of the gases at its outlet is controlled by the control system according to the temperature sensor, for example, by changing the flow rate necessary to the amount of fuel in the combustion chamber. After that, the second gas volume stream enters from the hot side 9 into the rotor of the regenerative heat exchanger through the second hot end disk of the rotor frame and exits through the first cold end disk of the rotor frame on the cold side 8 in the form of an outgoing second cooled gas volume stream.

This implements a method of compensating for the deformation of the shape of a high-temperature rotating disk heat exchanger for a hybrid power plant, used mainly as part of a hybrid power plant for generating electric current, usually including a temperature and air flow rate control system, gas flow, a housing and a rotor containing a frame 5 consisting of cold 3 and hot 2 end disks, heat exchange cells in the form of glasses 4 with external hexagonal surfaces the internal channel and points 1 of their rigid attachment to the disks, installed in the heat exchanger housing with the possibility of rotation and alternating passage through it in countercurrent flow of at least one first heated air volume stream and at least one second cooled gas volume stream, the oncoming first air volume flow enters the rotor through the first cold end disk 3 of the rotor frame, and leaves it through the second hot end disk 2 of the rotor frame in the form of an outgoing first heated air volume stream, and the second gas volume stream enters the rotor through the second hot end disk 2 of the rotor frame and exits through the first cold end disk 3 of the rotor frame in the form of an outgoing second cooled gas volume stream, while the first air and second gas volume flows on the rotor from each outer side of the hot and cold disks by means of at least one radial 6 and circumferential 7 rotor seals placed on the housing (which in FIG. 1 and 2 not shown). These features completely repeat the totality, properties and well-known technical results achieved in the prototype, which consist in leveling the temperature field to maintain a flat shape on 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 extremes on the frame and to reduce the values of its thermal deformations without the need to create a complex cooling structure and conditions for leveling and stabilizing the temperature field along the supporting elements of the frame structure, it is necessary to change the frame design and the consequent actions with it, leading to a decrease in the frame deformations. This is achieved through the use of the following distinctive features of the proposed method.

At the same time, by regulating the flow rates and flow temperatures, the temperature and flow control system of air and gas flows (not shown in Fig. 4), flows near or with a minimum temperature difference are maintained on the hot part of the rotor at the exit from the hot side 9 of the outgoing first heated air volume flow and the second gas volume stream entering the rotor through the second hot end disk of the rotor carcass in the area of the radial seals of the rotor on the housing, made of labyrinths, and from the cold side 8 its oncoming first cold air volumetric flow and the cooled second gas volumetric flow leaving the rotor through the second cold end disk of the rotor cage in the area of the rotor radial seals on the casing, made labyrinth.

In the rotor to compensate for the inevitable thermal deformation of the disks, elastic silicone seals 11 coated with siliconized pyrographite, shown in FIG. 1 and 3 by conventionally thickened lines placed on the outer surface of the disks according to the projection of the gaps 10 between the hexagonal cups 4, and the width in the circumferential direction of the labyrinth seals in the housing is greater than any size of the hexagonal cell of the silicone seal in the same direction (Fig. 1 is conventionally shown), and the speed of the mutual movement of the seals is greater than the speed of the satellite flow of flows in the gap between them, that is, the removal of gas or air into the gaps between the sealing surfaces will be minimal, since the main ear and / or gas will be under a purge cup inner channel 4. If desired, cleaning and purging of the cells from the working gas and air, for example, an inert gas, it is possible to arrange further by known means, which prevents their mutual penetration in the neighboring streams. The preservation of the elasticity of silicone and its heat resistance and stability of properties are determined by penetration into the colder part of the disks and the heat-dissipating and thermostabilizing ability of the inner hexagonal surface of the glasses adjacent to it. In case of urgent need, the internal gaps between the glasses can be further cooled. It should be noted that the internal channel can be filled with any heat-accumulating composition, and its density and porosity is determined by the optimal ratio of aerohydraulic resistance and heat-absorbing properties of the material of the filler composition. In this case, parasitic pore volumes can be selected from the condition of minimal mutual transfer of air and gas. If necessary, these spaces can be purged with an inert gas, air or gas, which will prevent air from entering the gas and vice versa.

Systems for controlling the 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 the well-known methods and using well-known technical means to create a more uniform temperature field on the surfaces of the hot and cold disk, which is obvious, because these actions are similar to the known actions in the prototype and are the development of these known actions. This is possible due to the standard operation of the gas turbine hybrid installation in one optimal selected operating mode of the microturbine engine. It should be noted that the uniformity of the temperature distribution across the hot and cold disks can be properly organized by choosing the thermophysical characteristics of the heat exchange cells and the heat transfer (contact) time, the higher their efficiency, the closer the initial and final temperatures of the surfaces of hot 2 and cold 3 disks respectively, for the first heated air volumetric flow and, accordingly, the second cooled gas volumetric flow, since the incident first air volumetric flow enters the rotor through the first cold end disk 3 of the rotor frame, and leaves it through the second hot end disk 2 of the rotor frame in the form of an outgoing first heated air volumetric flow, and the second gas volume stream enters the rotor through the second hot end disk 2 of the rotor frame and leaves through the first cold end disk 3 of the rotor carcass in the form of an outgoing second cooled gas volumetric flow, as a result of which these flows, the more they give off and receive heat from the heat transfer cells, and accordingly e are the temperature and gas in parts fluxes passing respectively through the hot 2 and cold 3 end frame wheels.

With the right choice of the ratio of linear expansion coefficients of materials of cold 3 and hot 2 end disks, which is selected inversely proportional to the ratio of the growth of average working temperatures of the disks, moreover, the heat transfer cells are made in the form of cups 4, each of which has an external hexagonal surface and an internal channel, and is installed between end disks with at least one hard mount point 1 on each drive, and at least every two hard mount points 1 glasses 4 on adjacent disk disposed in a diametrical section plane of their bases arranged in a radial and / or tangential thereto sectional plane disks, passing through the axis of symmetry of each cup, and the gap between the glasses are selected to allow their free relative expansion at the maximum operating temperature. These features make it possible to obtain the same linear expansions at the same (as in the analogues and prototype) temperatures on the surfaces of the hot and cold disks, correspondingly small for a higher working temperature of the hot disk, i.e., at high working temperature due to the small coefficient of linear expansion of its material, it will be obtained relatively small linear expansion (changes in linear size) and at a lower operating temperature, a relatively large linear expansion of the cold disk with more sokim linear expansion coefficient material that result from exposure to various temperature values will lead to almost the same linear expansion of the hot and cold respectively, to drive them to the selected or calculated operating temperature. With the right choice of the linear expansion coefficients of the materials of the cold and hot end disks, they are inversely proportional to the ratio of the growths of the average working temperatures of the disks, their absolute linear increase in sizes at the design temperatures obtained by the results of thermophysical calculations, or experimentally selected workers will be almost the same, and the general mushroom-like deformations the shape of the frame will be minimal, so that the initial cylindrical shape of the frame will hardly change.

Although it is obvious that due to working heating and thermal expansion, the overall overall dimensions of the frame 5 of the rotor and the shape of its disks will change.

It should be noted that a slight unevenness in the elongation of the glasses along the gas and air parts of the disks will lead to their slight bending and the appearance in the zone of radial seals of an uneven wedge-shaped gap, which can lead to dynamic suction of the working fluid from one side and its tangent transfer to the other side, to prevent this, it is advisable to install additional elastic silicone seals, and to reduce their wear, it is necessary to cover their friction surfaces highly An anti-friction coating, for example, siliconized pyrographite, which has a low coefficient of friction and high wear and heat resistance. Even if it is placed on a hot disk, then siliconized pyrographite, both thermally and chemically resistant, will work normally, and the elasticity of the silicone will ensure its necessary displacement in the gap. The silicone elastic element will not overheat, since it will be in the body of the disk opposite the massive parts of the glasses and with the possibility of organizing its cooling through the removal of excess heat by blowing refrigerant part of the disk through the projection of the gap in the gap between the glasses.

If the heat-exchange cells are made in the form of cups 4 with external hexagonal surfaces and an internal channel and are installed between end disks 2 and 3, with at least one hard-mount point on each disc, and at least every two points 1 of hard-mount cups 4 on adjacent disks are placed in the diametrical plane of the cross section of their bases, located in the radial and / or tangential plane plane of the cross section of the disks and passing through the axis of symmetry of each glass, this eliminates the effect of the thermal deformation of heat-exchange cells made in the form of cups 4 onto the end disks at a very significant temperature difference along the length of each cup 4 of the heat-exchange cell, since the end surfaces of the cups 4 in contact with the corresponding disc have the possibility of free linear expansion and this does not cause deformation of the disks . The location of the points of rigid attachment of the glasses of heat-exchange cells on adjacent disks in the diametrical plane of the cross section of their bases, located in the radial plane of the cross section of the disks, i.e. in the plane passing through the axis of rotation of the disk in the radial direction, it allows to achieve a minimum temperature difference between these points, since these points simultaneously begin to be exposed to air or gas and will be at close temperature conditions during the entire heat transfer process, even if they are on the same drive. The location of the points of rigid attachment of glasses of heat-exchange cells on adjacent disks in the diametrical plane of the cross section of their bases, located in the tangential plane of the cross section of the disks, i.e. in the plane perpendicular to the radial plane of its cross section in one direction, it allows to achieve minimal linear elongation due to the 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 of each heat exchange cell and will be in relatively close temperature conditions during the entire heat transfer process, because part of the air flow or gas in the specified channel is heat oobmennoy cell will have almost the same temperature distribution along the channel, whereby thermal deformation of the linear dimensions and shape of each cell individually, and all the cells together does not lead to a change in the frame shape to obtain mushroom deformation, and cause a corresponding rotation of one of the end disc relative to the other.

The hexagonal shape of the outer surface of the glasses 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 of the frame).

In this case, the movement of air and gas flows with similar temperatures in the area of the radial seals of the rotor of the rotating disk heat exchanger on the casing and the performance of their seals are labyrinth, under the above conditions, it is possible to achieve a minimum clearance and effective non-contact sealing.

The performance of all the gaps 10 between the outer hexagonal surfaces of the cups 4 of the frame 5 of the rotating disk heat exchanger along each of the six outer faces of each cup can be the same or calculated by the point of rigid fastening of the cup 4. The gaps 10 are in any case chosen from the condition of ensuring free mutual radial expansion of each cup in the direction of the selected face and still possible rotation around the axis of the cup or the point of its rigid attachment, relatively mutually deformed by the same all other glasses of the frame at its maximum working temperature without the possibility of their mutual contact and / or the possibility of deformation of the shape of the frame.

To reduce the possible flow of air and gas through the technological installation gaps between the cups 4 and the disks 2 and 3, the gaps can be sealed by any known method using known means and known heat-resistant sealing compounds, allowing mutual linear normal and tangential displacements of these parts within the selected or calculated clearances.

Based on the foregoing, we can state the following.

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

The proposal has differences from the known method of work, therefore, meets the criteria of the invention of "novelty."

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

Claims (1)

A method of compensating for the deformation of a high-temperature rotating disk heat exchanger, including a temperature and air flow control system for air and gas flows, a housing and a rotor installed in it, comprising a frame consisting of cold and hot end disks and heat exchange cells, mounted in the heat exchanger housing with the possibility of rotation and alternating passage through it in countercurrent of at least one first heated air volumetric flow and at least one second cooling gas volume flow, and the incident first air volume flow enters the rotor through the first cold end disk of the rotor frame, and leaves it through the second hot end disk of the rotor frame in the form of an outgoing first heated air volume stream, and the second gas volume stream enters the rotor through the hot end disk of the rotor cage and exits through the first cold end disk in the form of an outgoing second cooled gas volumetric stream, the first air and second gas volumetric stream separated on the rotor from each outer side of the hot and cold disks by means of at least one rotor seal located on the housing, characterized in that by controlling the flow and temperature the temperature and air flow control systems maintain close or minimal temperature differences flows on the hot part of the rotor at the outlet of the outgoing first heated air volume stream and the second gas volume stream entering the rotor through the second hot end dis the rotor cage in the area of radial and circumferential heat exchanger seals made in labyrinths and located in the housing, and in the rotor there are additionally installed silicone silicone seals with a coating of siliconized pyrographite placed on the outer surface of the disks according to the projection of the gaps between the hexagonal cups, the width in the circumferential direction of the labyrinth seals the housing is larger than any size of the hexagonal cell of the silicone seal in the same direction, and the speed of mutual movement of the seals is greater the velocity of the satellite flow of the flows in the gap between them, and the ratio of the linear expansion coefficients of the materials of the cold and hot end disks is chosen inversely proportional to the ratio of the growths of the average working temperatures of the disks, the heat exchange cells being made in the form of cups with external hexagonal surfaces and internal channels and installed between the end disks, at least one point of hard mounting on each disk, and at least every two points of hard mounting of glasses on neighboring disks are placed in the diametrical plane of the cross section of their bases located in a radial and / or tangential plane plane of the cross section of the disks passing through the axis of symmetry of each glass, and the gap between the glasses is chosen with the possibility of their mutual mutual radial expansion at maximum operating temperature, and the gaps between the ends of the glasses and discs are sealed with heat-resistant elastic compounds.

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