RU2339890C2 - Heat exchanger-modular water heater and heat exchanger element (versions) - Google Patents

Abstract

FIELD: mechanics, heating.

SUBSTANCE: in compliance with the invention, the heat exchanger-modular water heater incorporates one or two modules each comprising, at least, two heat exchanger units integrated by a diffuser to feed a cooling medium and a confuser to withdraw the medium to be cooled, primarily, a turbine hot exhaust gas. It also comprises the manifolds feeding and withdrawing the medium being heated, primarily, air, each communicating, via a tube plates fitted directly in the said manifold walls, with the multi-row bank of the four-pass heat exchanger variable standard-size pipes, the said standards sizes being calculated from the ratios covered by this invention and the aforesaid tube plates being secured by appropriated spacers. The multi-row bank can be made up of, at least, two trains of two-pass U-shape pipes integrated by the aforesaid manifolds and, at least, one bypass chamber.

EFFECT: high-efficiency heat exchanger, lower heat exchanger metal input, optimum design and spacers, higher design rigidity, simpler assembly of heat exchange pipe banks.

21 cl, 16 dwg

Description

The invention relates to a power system, and in particular, to devices for recovering heat from exhaust gases from aggregates, in particular for heating air with exhaust products from a compressor of a gas turbine installation of a gas pumping unit at compressor stations of gas mains.

Known air heater (SU No. 992920, F12L 15/04, 1983), containing located on top of one another and mounted on the lower frame blocks of heat-exchange sections, formed by vertical pipes with horizontal pipe boards, rigidly fastened together and an upper distribution box equipped with a compensator temperature changes, while the air heater is equipped with a power belt with spring supports covering the junction box, rigidly fastened with a belt in the area below its compensator, and the area above the latter interacting with its spring supports.

Also known is a regenerative air heater (SU No. 985595, F12L 15/04, 1982) containing a tube plate with a bundle of heat exchange tubes fixed in it, arranged in vertical rows, the planes of which are perpendicular to the supporting edges of the tube plate, while reducing the thermal stresses of the pipes in places where the tube bundle is fixed in the pipe boards, the pipes in rows in sections located on the side of the supporting edges of the pipe board are connected with each other and with the pipe boards by additional spacers.

The disadvantages of the above devices include their high metal consumption, due to the presence of vertical heat transfer tubes and horizontal tube boards. In the first analogue, the load from the upper distribution box is perceived through the blocks of the heat exchange sections by the lower frame, and therefore the introduction of a power belt with spring supports was required. In the second analogue, in order to reduce thermal stresses, it was necessary to introduce spacers connecting the pipes together and with the tube plate.

The closest analogue in the part of the heat exchanger itself is a regenerative air heater (RU No. 31838 U1, F23L 15/04, 08.27.2003), containing heat exchange units having bundles of bundles of heat exchange tubes, the ends of which are attached to the supply and exhaust manifolds by fastening elements air, the heat exchange tube bundle has the shape of a coil and is made single-package, while the fastening elements of the heat exchange tubes to the collectors are made in the form of separate tube plates welded directly into the wall of the corresponding collector but.

The disadvantages of the closest analogue include the fact that it does not provide high thermal efficiency, as well as the compactness of the stacking of heat transfer pipes, while ensuring strength and rigidity of the structure, as a result of which the closest analogue has an increased metal consumption.

In terms of the heat exchanger block of the heat exchanger, the closest analogue is the heat exchanger block of the regenerative air heater, including a four-way multi-row bundle of heat exchange pipes (RU No. 17600 U1, F23L 15/04, 04/10/2001), formed by installed horizontal rows of V-shaped pipes with one bend and two straight branches, each row containing two packets of V-shaped pipes located next to each other at the same level.

The disadvantage of this device is that it does not provide high heat transfer efficiency and has a high metal consumption.

The problem solved by all objects of the claimed group of inventions is to ensure the compactness of the device, increasing the efficiency of heat transfer while increasing the strength and rigidity of the structure and reducing metal consumption.

составляющем 0,56÷0,85, а отношение суммарной длины ∑L [м] труб пучка к суммарной площади ∑S_н.т.т. внешней теплообменной поверхности труб определено коэффициентом

составляющим 0,08÷0,32 [м^-1].The problem in terms of the first object of the group of inventions is solved due to the fact that the heat exchanger - block-sectional air heater according to the invention contains at least two sections, each of which contains at least two heat-exchange units, each of which includes a diffuser for supply and a confuser for removal of the cooled medium, a supply manifold and a collector for the removal of the heated medium, each of which is connected by means of separate tube plates mounted directly to the wall its collector for supplying or discharging a heated medium, with a multi-row bundle of four-way heat transfer pipes, mainly with an unequal number of pipes in rows adjacent in height, mainly horizontal, with vertical and horizontal separation from each other by means of spacer elements, each heat transfer pipe of a row made with the number of bends in different tubes of the bundle from four to six, forming four straight branches and connecting their three knees, while the number and distribution of tubes in the bundle are taken with Yuden conditions under which the volume ratio V _Cdes [m ³ ] occupied by heat transfer tubes in the block and equal to the total volume of straight branches and elbows of the beam tubes, outlined along the external contour with conditional planes touching the outer surfaces of the extreme heat transfer tubes, minus the volume of the annular medium between the branches and elbows of the bundle tubes to the total internal volume heat exchange unit V _ext. [m ³ ], limited by the bottom, top cover and end walls of the block casing, is defined in the range of values

component of 0.56 ÷ 0.85, and the ratio of the total length ∑L [m] of the bundle tubes to the total area ∑S _nt the external heat exchange surface of the pipes is determined by the coefficient

components of 0.08 ÷ 0.32 [m ^-1 ].

In each section of the heat exchanger, the heat exchange blocks can be located one above the other, and the preferred number of blocks is four, and the supply manifold and the collector of the outlet of the heated medium can be made with the possibility of connection with the pipelines of the inlet and outlet of the heated medium, which is preferably used air, including with an enriched oxygen content, while combustion products after the turbine of a gas turbine installation can be used as a cooled medium.

при этом внешняя труба каждого из рядов, имеющих большее число труб, чем в смежных с ним рядах, имеет один гиб длиной πR, образующий колено, соединяющее внутренние ветви этой трубы, а общее число гибов этой трубы равно пяти, а внутренняя труба каждого из рядов, имеющих большее число труб, чем в смежных с ним рядах, имеет два гиба длиной πR, каждый из которых образует колено, соединяющее соответствующие внутреннюю и внешнюю ветви этой трубы, а общее число гибов у этой трубы равно четырем, шаг а между продольными осями смежных труб прямолинейных ветвей составляет (1,5-2,5)d, где d - наружный диаметр теплообменной трубы, шаг b между осями смежных труб на прямолинейных участках колен составляет (1,8-2,8)d, причем в каждом ряду шаг а между продольными осями смежных труб прямолинейных ветвей меньше или больше, чем шаг b между продольными осями колен смежных труб, предпочтительно а<b, или шаг а равен шагу b, и количество теплообменных труб в смежных по высоте рядах пучка для нечетных и четных рядов может составлять соответственно m и n, где m - четное число, а n=(m-1), количество рядов труб в пучке k - предпочтительно нечетное, причем k>3, теплообменные трубы в смежных по высоте рядах могут быть размещены в шахматном порядке со смещением на (0,4÷0,6)a, [м], где a - шаг между продольными осями смежных труб на прямолинейных ветвях одного ряда [м], при этом количество труб в блоке может составлять предпочтительно 263-563 шт.The ratio of the total length "l "of rectilinear branches of the heat exchange tubes flowing in the transverse direction to the total length ∑L [m] of all heat transfer tubes of the beam can be 0.78-0.92, while the outer and inner pipes in each row of the beam can contain each of at least one bend with a length equal to πR, and the bends of the remaining pipes in all rows of the beam can be performed with a length equal to

the outer pipe of each of the rows having a larger number of pipes than in adjacent rows has one bend of length πR, forming a bend connecting the internal branches of this pipe, and the total number of bends of this pipe is five, and the inner pipe of each of the rows having a larger number of pipes than in the rows adjacent to it, has two bends of length πR, each of which forms a bend connecting the corresponding internal and external branches of this pipe, and the total number of bends at this pipe is four, the pitch and between the longitudinal axes of adjacent straight pipe Twi is (1.5-2.5) d, where d is the outer diameter of the heat exchanger pipe, the step b between the axes of adjacent pipes in the straight sections of the elbows is (1.8-2.8) d, and in each row, the step a between the longitudinal axes of adjacent pipes of rectilinear branches are smaller or larger than step b between the longitudinal axes of the elbows of adjacent pipes, preferably a <b, or step a is equal to step b, and the number of heat-exchange tubes in the height-adjacent rows of the bundle for odd and even rows can be respectively m and n, where m is an even number, and n = (m-1), the number of rows of pipes in the bundle k is preferred odd, moreover, k> 3, heat exchanging pipes in rows adjacent in height can be staggered with an offset of (0.4 ÷ 0.6) a, [m], where a is the step between the longitudinal axes of adjacent pipes on rectilinear branches of one row [m], while the number of pipes in the block can be preferably 263-563 pcs.

может содержать сопряженную с гибами прямолинейную вставку длиной, кратной 2а, где a - шаг между осями одноименных прямолинейных ветвей смежных труб ряда, или каждое колено труб всех рядов пучка, образованное двумя гибами длиной каждый, равной

может содержать сопряженную с гибами прямолинейную вставку длиной, изменяющейся у разных труб ряда от величины, равной 2a±10% [м] до величины, равной 2a (m-1)±10% [м] для рядов с большим числом труб, чем в смежных с ними по высоте рядах, а для остальных рядов до величины, равной а(2n-1)±10% [м], гдеEach pipe elbow of all rows of the bundle, formed by two bends each equal in length

may contain a rectilinear insert conjugated with bends that is a multiple of 2a, where a is the step between the axes of the same straight branches of adjacent pipes in a row, or each pipe bend of all rows of a bundle, formed by two bends each equal in length

may contain a straight insert coupled with bends, the length varying for different pipes of the row from a value equal to 2a ± 10% [m] to a value equal to 2a (m-1) ± 10% [m] for rows with a larger number of pipes than rows adjacent to them in height, and for the remaining rows to a value equal to a (2n-1) ± 10% [m], where

a is the step between the axes of the same rectilinear branches of adjacent pipes of a row [m],

m is the number of pipes in a row with a large number of pipes, mainly an even number of pipes in odd rows,

n is the number of pipes in a row with a smaller number of pipes, mainly an odd number of pipes in even rows.

The problem of the second object of the group of inventions - the first embodiment of a heat exchange unit of a heat exchanger - a block-section air heater according to the invention comprises four-way multi-row bundle of heat exchange tubes consisting of four branches, laid in horizontal rows and spaced horizontally and vertically from each other, an inlet collector and a discharge collector heated medium, each of which is connected to heat exchange tubes by means of separate tube plates mounted directly directly to the wall of the corresponding manifold for supplying or discharging the heated medium, each heat transfer pipe of a row made with four, or five, or six bends of radius R, forming four straight branches and connecting three knees, while the bending sections of two pipes in each odd row have a length πR, namely, one pipe has an inner bend, the other has two external bends; for the remaining pipes of odd and even rows, the bend sections have a length πR / 2 and are joined in pairs by straight-line inserts of length N ' _i d For the outer elbows and H " _i is for the inner elbow, and the number of heat transfer tubes in the adjacent rows of the beam for odd and even rows is respectively m and n, where m is an even number and n = (m-1), the number of rows tubes in the bundle k is preferably odd, and k> 3, the heat transfer tubes in rows adjacent in height are staggered with an offset of (0.4 ÷ 0.6) a [m], where a is the step between the longitudinal axes of the straight branches adjacent tubes of one row [m], and the length N _'i and H'_'i rectilinear inserts knee i-th tube formed variables: for nech a number of heat transfer pipes varying from a value equal to 2a ± 10% [m], to a value equal to 2a (m-1) ± 10% [m], and for an even row - from a value equal to a ± 10% [m] to a value equal to a (2n-1) ± 10% [m].

составляющим (84,5-460) [м^-1], согласно второму условию отношение суммарного объема ∑V_в.c. для нагреваемой среды в трубах ветви пучка к объему V_м.с. определено коэффициентом

составляющим 0,78-1,25.The placement of pipes in the volume occupied by at least one branch of the beam can be taken subject to the conditions, according to the first of which the ratio of the total area нF _ntp the outer heat transfer surface of the pipes of this beam branch to the volume ∑V _m.c. occupied by the annular medium in the area of active heat transfer of the beam branch and equal to the volume of the beam branch along the external contour, outlined by conditional planes touching the outer surfaces of the extreme heat transfer tubes of the beam branch, minus the volume occupied by the heat transfer tubes in this beam branch, is in the range of values determined by the coefficient

components (84.5-460) [m ^-1 ], according to the second condition, the ratio of the total volume ∑V _century.c. for the heated medium in the pipes of the beam branch to the volume V _m.s. determined by the coefficient

constituting 0.78-1.25.

The parameters of each row pipe can be determined by the dependencies:

L _{i + 1} = 2l ^' _{i + 1} + 2l ^" _{i + 1} -Δ + 2H ^' _{i + 1} + H ^" _{i + 1} + 3πR, where

L _{i + 1} - scan length of the (i + 1) th row pipe [m];

l ^' _{i + 1} - the length of the outer straight branch (i + 1) of the row pipe equal

l ^' _{i + 1} = l ^' _i -b [m];

l ^" _{i + 1} is the length of the internal straight branch (i + 1) of the row pipe equal to l" _{i + 1} = l ^' _i -Δ [m];

H ^' _{i + 1} - the length of the rectilinear inserts of the outer elbows of the (i + 1) th pipe of the row, equal to H ^' _{i + 1} = H ^' _i -2a [m],

N ^" _{i + 1} - the length of the straight insert of the inner bend of the (i + 1) th pipe of the row, equal to N ^" _{i + 1} = H ^" _i + 2a [m];

a is the step between the longitudinal axes of the same rectilinear branches adjacent in a row of pipes [m];

b is the step between the longitudinal axes of the rectilinear inserts of the elbows of adjacent pipes in the row [m];

Δ is an empirical value equal to [3-12] · 10 ^-3 [m];

l ' _i , l " _i , Н' _i and Н '' _i are the corresponding parameters for the i pipe in the row, counting from the outer pipe to the inner pipe in this row, and step a is (1.5-2.5) · d , step b can be (1.8-2.8) · d, where d is the outer diameter of the heat exchanger pipe [m], the scan length L _{min of the} heat transfer pipe of the minimum length can be at least 0.75 of the scan length L _{max of the} heat transfer pipe length, while the placement of heat transfer pipes in a row can be selected subject to the condition according to which the ratio of the surface area of the heat transfer pipes is straight the linear branches of the row, perpendicular to the flow of the cooled medium, to the volume occupied by the series of heat transfer tubes and equal to the volume outlined by the conditional planes touching the outer surfaces of the heat transfer tubes of the row, taking into account the gaps between the pipes, is 0.02-0.12 [m ^{- 1} ].

The pipe row may contain an even number of pipes, preferably not less than two and not more than ten, or it may contain an odd number of pipes, preferably not less than three and not more than nine, while the pipes can be arranged along with a variable distance between the axes of the outer branches, and the smallest value of this distance at the pipe, the ends of which can be embedded in the extreme closest to each other holes of the corresponding single-level rows of holes in the pipe boards of the collectors for supplying and discharging the heated medium, preferably about air, the heat-exchange unit of the regenerative air heater, and each subsequent four-branch pipe of the row can be made covering the previous one from the outer side of the external branches and the largest value of this distance at the pipe, the ends of which can be embedded in the outermost outermost openings of the corresponding single-level rows of openings in pipe boards of the collectors for supplying and discharging the heated medium, and two internal branches of each subsequent pipe in a row with an elbow connecting them its side in the bend formed by the corresponding branches and connecting the elbow of the previous pipe in the pipe row, while the step a between the longitudinal axes of the same straight branches of adjacent pipes in the row is less than or greater than the step b between the longitudinal axes of the rectilinear inserts of the elbows of adjacent pipes in the row, preferably a <b, or step a is equal to step b, and, in addition, for each heat exchange tube of the row, the distance H between the longitudinal axes of its outer straight branches is (30-85) d; the length of the straight branches l 'and l "may be (74-145) d and (100-135) d, respectively, where d is the outer diameter of the heat exchanger pipe [m], while the number N of heat exchanger pipes in the block with an odd number of rows of k pipes in the bundle is determined by the dependence N = 0.5 (k-1) (2m-1) + m and is preferably 263-563 pcs., or the number N of heat transfer tubes in the block with an even number of rows of k tubes in the bundle is determined by the dependence N = 0 , 5k (2m-1) and is preferably 263-563 pcs.

Between the inlet and outlet of the heated medium can be fixed displacer annular medium, made in the form of a profiled panel with a flat section located between the inlets of the inlet or outlet of the heated medium, while the passage area of the inlet or collector of the outlet of the heated medium can be 0.45- 0.82 of the total flow area of the heat transfer tubes of the beam, and the heat transfer unit can be equipped with slinging devices and manholes made in the collectors odvoda and removal of the heated environment.

The task of the third object of the group of inventions - the second embodiment of the heat exchanger block of the heat exchanger - block-section air heater, according to the invention, comprises a housing, a diffuser for supply and a confuser for draining the cooled medium, a supply manifold and removal of the heated medium with tube plates and a multi-way multi-row bundle of heat-exchange pipes, forming respectively in each row an even number of straight-line multi-tubes branches, including at least two internal and two external, united by sections with bends of a radius beam predominantly constant for all pipes, or a multi-row bundle of heat transfer pipes, consisting of at least two packages of two-way U-shaped pipes, forming, within each package, two-branch, for example, horizontal rows of pipes spaced within the row and between the rows from each other, the supply manifold and the collector of the outlet of the heated medium and at least one bypass located between them Amer, and the supply manifold and the collector of the outlet of the heated medium, as well as the bypass chamber are connected to the heat exchange pipes by a common tube board or separate tube boards, at least part of which or which form part of the wall of the supply manifold and the collector of the outlet of the heated medium and the bypass cameras, with the bottom, the cover and one of the end walls of the block body made in the form of panels with a strapping of stiffeners forming flat rod systems, and the spatial frame is bl The eye is formed by a combination of flat core systems of the frameworks of these panels with intermediate racks uniting them and rigidly connected to them by the bodies of the inlet and outlet of the heated medium, which, in turn, are connected to the bottom of the block and to each other by two-ring diaphragms and a displacer of the annular medium, and parts of the cases collectors for supplying and discharging a heated medium with tube boards mounted in them and a displacer of the annular medium together form a spatially developed rigid end the wall of the casing of the block, and on the longitudinal sides of the frame is made with the possibility of fastening, respectively, elements of the diffuser and confuser for supplying and discharging the cooled medium, while for each heat transfer tube of the beam the distance H between the longitudinal axes of its external straight branches is (30-85) d; the length of the straight branches l 'and l "is respectively (95-145) d and (100-135) d, where d is the outer diameter of the heat exchanger pipe [m].

The displacer of the annular medium can be made in the form of a profiled panel with a flat section, the inner surface of which can be located between the inlet and outlet manifolds of the heated medium in the same plane as the outer plane of the tube plates, or in the form of a flat panel welded to the walls of the inlet and outlet manifolds of the heated medium so that its inner surface can be located in the same plane with the outer plane of the tube plates, while the heat exchange unit can be equipped with fixed for days and the frame of the casing of the block with spacer elements for heat transfer pipes of the outer branches of the multi-path bundle in the form of spacer grids, said heat transfer pipes being passed through the holes of the spacing grids, and subsequent rows of heat transfer pipes in the area of the inner branches can be separated by folded spacing bars that can be attached to racks installed on the bottom, and in addition, combs for at least the inner branches of It has a number of heat exchanger tubes.

The cross-sectional area of each of the collectors for supplying and discharging the heated medium can be 1.8-3.5 of the total flow area of the heat-transfer pipes in the block, while the collectors for supplying and discharging the heated medium can be made with manholes located on the bottom side block, while manhole covers can be pivotally mounted on the bodies of the inlet and outlet manifolds of the heated medium with the possibility of rotation in a plane perpendicular to the longitudinal axis of symmetry of the inlet and outlet manifolds the medium, and on the inner walls of the manifolds for supplying and discharging the heated medium, supports can be installed that form a ladder for inspection and maintenance of the manifolds for supplying and discharging the heated medium and tube plates, and the heat exchange unit can be equipped with means for attaching a diffuser for the inlet and the confuser for drainage of the cooled medium mounted on the opposite side elements of the spatial frame of the block, as well as brackets for attaching external thermal insulation.

The spacer grids can be fixedly mounted in the body of the regenerative air heater, the folded spacers can have alternating supporting sections located on both sides, one on the upper and lower protrusions of the fold, for supporting contact of the corresponding lower and upper protrusions of the folded planks adjacent in height and connecting protrusions two inclined sections forming supporting elements for supporting the beam tubes, while the heat exchange tubes are spaced vertically and vertically they were mounted apart from each other to ensure a distance between the longitudinal axes of adjacent heat exchange tubes in a row of 1.5-2.3 diameters of the heat exchanger pipe, and in rows adjacent in height to ensure a distance between the longitudinal axes of the heat exchange tubes of adjacent rows of 0.6- 1.5 diameters of the heat exchanger pipe, while the heat exchanger pipes in rows adjacent in height can be staggered, the spaced folding pleats of each overlying row can be supported by their lower protrusions on the facing them in The tops of the upper protrusions of the folds of the adjoining height of the underlying spacer bar with the formation of a system of support contacts displaced in each successive row by 0.4-0.6 pipe steps in a row, and the thickness of the folded bar can be at least 0.03 of the diameter of the heat exchange pipes and the spacing elements on the external and internal branches can be located along the length of the heat exchange tubes, preferably with the same pitch, while the supporting sections on the upper and lower protrusions of the fold can be made with a supporting surface in in the form of a fragment of a cylindrical surface with a radius of not more than 35% of the diameter of the heat exchanger tube convex outward, or supporting sections on the upper and lower protrusions of the fold can be made with a flat supporting surface.

The supply manifold or the collector of the outlet of the heated medium can be made in the form of a cylindrical shell with an aperture into which the tube plate can be welded, the projection onto the end of the tube plate of a curved section of the shell forming the end of the opening can be located within the thickness of the tube plate, which can be made with through holes for the ends of the heat exchanger tubes of the heat exchanger block, the holes can be arranged in rows along the height of the tube plate with a step in the axes in a row of (1.5-2.8) · d, step ohm of rows along the height of the tube plate, which is (0.60-0.84) · d, where d is the outer diameter of the heat exchanger pipe, and with the displacement of holes in adjacent rows by (0.4 ÷ 0.6) the step size in the row, the total area of the through holes in the tube plate for the ends of the heat exchanger tubes of the heat exchange unit may be 56-85% of the total area of the tube field in the plane of the tube plate, limited by a contour formed by a set of conditional straight lines tangent to the outer edges of the outer holes in the tube plate, and the area of the pipe field can be 0.75 ÷ 0.94 of the total area of the frontal projection of the tube plate, the connection of the shell with the tube plate in the plane of the cross section of the shell can be performed in the angular range γ = 28-75 °, and the ratio of the projection area to the specified plane of the curved section of the shell, forming the end face of the opening, to the projection area on this plane of the corresponding end of the tube plate can be 0.048 ÷ 0.172, and the side edges of the tube plate can be trihedral, while one of the faces can be made with the formation in cross section the contact area contacting with the shell, and the faces adjacent to it can be made - one adjacent to the surface of the tube plate facing the collector for supplying or removing the heated medium, with a bevel that forms an angle α = (22-29) ° with the plane of the support section and the other, facing the outer surface of the tube plate, the face can be made with a bevel, forming an angle β = (25-35) ° with the plane of the supporting section.

The trihedral edges of the tube plate can be made with a width of the supporting section of at least 4.5% of the total thickness of the plate forming the tube plate, a face with a bevel α = (22-29) ° can be made with a width of 5.9-12, 5% of the total plate thickness, and a face with a bevel β = (25-35) ° can be made with a width of 79-89.6% of the total plate thickness.

The task of the fourth object of the group of inventions, the third embodiment, of a heat exchanger block of a heat exchanger of the type of a block or block section regenerative air heater according to the invention comprises a multi-row bundle of heat exchange tubes consisting of at least two packages of two-way U-shaped pipes forming within each packet two-branch, for example, horizontal rows of pipes spaced within the row and between the rows from each other, the supply manifold and the exhaust manifold heated with food and located between them at least one bypass chamber, and the supply manifold and the collector of the outlet of the heated medium, as well as the bypass chamber are connected to the heat exchange pipes by a common pipe board or separate pipe boards, at least part of which or which forms part of the wall enclosure of the inlet and outlet manifolds of the heated medium and the bypass chamber, with the total area of through holes in the tube plate or tube boards at the ends of the heat exchange tubes Nogo block is 29-85% of the overall area of the pipe pitch.

In each package, through a row, one inner pipe of the series can be made with a bend length equal to πR, and all other pipes of all rows of the package can be made with two bends each length equal to πR / 2, where R is the bend radius, which is (2, 5-6.0) d, where d is the outer diameter of the heat exchanger pipe, and can be joined in pairs by means of straight sections of various lengths.

составляющем 0,56÷0,85, а отношение суммарной длины ∑L [м] труб пучка к суммарной площади ∑S_н.т.т. внешней теплообменной поверхности труб определено коэффициентом

составляющим 0,08÷0,32 [м^-1].The number and distribution of pipes in the bundle can be taken subject to the condition under which the volume ratio V _t. [m ³ ] occupied by heat transfer tubes in the unit and equal to the total volume of straight branches and elbows of the beam tubes, outlined along the outer contour with conditional planes touching the outer surfaces of the extreme heat transfer tubes, minus the volume of the annular medium between the branches and elbows of the bundle tubes, to the total internal the volume of the heat exchange unit V _ext. [m ³ ], defined in the range of values

component of 0.56 ÷ 0.85, and the ratio of the total length ∑L [m] of the bundle tubes to the total area ∑S _nt the external heat exchange surface of the pipes is determined by the coefficient

components of 0.08 ÷ 0.32 [m ^-1 ].

In each row, the step a between the longitudinal axes of adjacent pipes of rectilinear branches is smaller or larger than the step b between the longitudinal axes of the elbows of adjacent pipes, preferably a <b, or step a may be equal to step b.

The step a between the longitudinal axes of adjacent pipes of rectilinear branches can be (1.5-2.5) d, where d is the outer diameter of the heat exchanger pipe, step b between the axes of adjacent pipes on straight sections of the elbows can be (1.8-2.8 ) d.

Preferably, air, including with an enriched oxygen content, can be used as a heated medium, while combustion products after a turbine of a gas turbine installation can be used as a cooled medium.

The technical result provided by all objects of the group of inventions is to ensure high heat transfer efficiency while reducing the metal consumption of the regenerative air heater due to the designs of the heat exchanger apparatus and its elements developed in the invention, which ensure optimal placement of various heat transfer tubes in the bundle, optimal performance of the distance elements, increased stiffness and durability of structures operating at high temperatures while simultaneously lowering reduction of metal consumption by reducing the size and metal consumption of the lattice elements for heat transfer tubes and simplifying the assembly of the bundle of heat transfer tubes.

Если указанное соотношение меньше 0,56, то это приводит к неоправданному расходу материалов и увеличению габаритов и неэффективному использованию теплоты уходящих газов сгорания, если указанное соотношение больше 0,85 - имеет место резкое снижение эффективности теплообменных процессов вследствие возрастания аэродинамического сопротивления при прохождении через перенасыщенный трубами объем теплообменного аппарата.The ratio of volume V _t [m ³ ] occupied by heat transfer tubes in the unit and equal to the total volume of straight branches and elbows of the beam tubes, outlined along the outer contour with conditional planes touching the outer surfaces of the extreme heat transfer tubes, minus the volume of the annular medium between the branches and elbows of the bundle tubes, to the total internal the volume of the heat exchange unit V _ext. [m ^-1 ] determined by the coefficient

If the specified ratio is less than 0.56, this leads to an unjustified consumption of materials and an increase in size and inefficient use of the heat of the exhaust gases, if the specified ratio is greater than 0.85, there is a sharp decrease in the efficiency of heat transfer processes due to an increase in aerodynamic drag when passing through a supersaturated pipe heat exchanger volume.

Если указанное соотношение меньше 0,08, то резко ухудшаются процессы теплообмена вследствие больших диаметров труб и недостаточной удельной площади на единицу объема подогреваемой площади, если указанное соотношение больше 0,32 - имеет место резкое возрастание аэродинамического сопротивления потока подогреваемого воздуха в трубах вследствие малого диаметра труб.The ratio of the total length ∑L [m] of the beam tubes to the total area ∑S _nt the external heat exchange surface of the pipes is determined by the coefficient

If the indicated ratio is less than 0.08, heat exchange processes are sharply worsened due to large pipe diameters and insufficient specific area per unit volume of the heated area, if the specified ratio is greater than 0.32, there is a sharp increase in the aerodynamic resistance of the heated air flow in the pipes due to the small diameter of the pipes .

The ratio of the total area ∑F _ntp the outer surface of the heat exchange tubes of the bundle branches to the scope ΣV _MS occupied by the annular medium in the area of active heat transfer of the beam branch and equal to the volume of the beam branch along the external contour, outlined by conditional planes touching the outer surfaces of the extreme heat transfer tubes of the beam branch, minus the volume occupied by the heat transfer tubes in this beam branch, is in the range of values determined by the coefficient

If the indicated ratio is less than 84.5, there is an irrational use of volume and unreasonably high material consumption and a decrease in the heat transfer efficiency due to the irrationally rarefied arrangement of the pipes in the bundle and underutilization of the heat of the exhaust gases to heat the air in the apparatus. If the indicated ratio is greater than 460, then there is a decrease in the heat transfer efficiency and an increase in energy losses due to a sharp increase in aerodynamic drag due to the supersaturation of the beam volume with pipes.

. Если указанное соотношение меньше 0,78, то имеет место снижение эффективности аппарата вследствие малой производительности - подогрева недостаточного количества воздуха на единицу объема уходящих газов сгорания. Если указанное соотношение больше 1,25, то также имеет место снижение эффективности аппарата вследствие нерационального соотношения объемов подогреваемого воздуха и охлаждаемой среды - уходящих газов сгорания.The ratio of the total volume ∑V _century.c. for the heated medium in the pipes of the beam branch to the volume V _m.s. determined by the coefficient

. If the specified ratio is less than 0.78, then there is a decrease in the efficiency of the apparatus due to low productivity - heating insufficient air per unit volume of exhaust combustion gases. If the indicated ratio is greater than 1.25, then there is also a decrease in the efficiency of the apparatus due to the irrational ratio of the volumes of heated air and the cooled medium — exhaust gases.

If the total area of through holes in the tube plate or tube boards for the ends of the heat exchanger tubes of the heat exchanger block is less than 29%, then there is an unjustified overspending of the material on the tube boards and a sharp decrease in the efficiency of the heat exchanger block due to insufficient block productivity, and if the indicated ratio is more than 85%, it decreases heat transfer efficiency due to the supersaturation of the block volume with pipes and the irrational ratio of the volume of the heated medium and the volume of the cooled medium - exhaust gases wounding.

The invention is illustrated by drawings, where

figure 1 shows a regenerative air heater, side view;

figure 2 is the same, a top view;

figure 3 - heat transfer unit regenerative air heater, top view;

figure 4 - heat transfer pipe, top view;

figure 5 - node a in figure 3;

figure 6 is a section bB in figure 3;

Fig.7 is a heat exchange unit of a regenerative air heater with open manhole covers, a top view;

on Fig - block regenerative air heater in a perspective view;

figure 9 is a spacing element in the form of a folded plate;

figure 10 is a section of a regenerative air heater, the main view;

figure 11 is a section of a regenerative air heater, side view;

on Fig - collector supply or removal of the heated medium, the main view;

Fig.13 is a section along BB in Fig.12;

in Fig.14 - node G in Fig.13;

in Fig.15 - node D in Fig.14;

in Fig.16 is an embodiment of a heat exchange unit with a bypass chamber, in plan.

составляющем 0,56÷0,85. Отношение суммарной длины ∑L [м] труб 9 пучка 8 к суммарной площади ∑S_н.т.т. внешней теплообменной поверхности труб 9 определено коэффициентом

составляющим 0,08÷0,32 [м^-1].The heat exchanger of a block-sectional air heater contains at least two sections 1, inside each of which at least two heat exchanger blocks 2 are placed, each of which includes a diffuser 3 for supply and a confuser 4 for removal of the cooled medium, a supply manifold 5 and the collector of the outlet 6 of the heated medium, each of which is connected by means of separate tube plates 7 mounted directly into the wall of the corresponding collector of the supply 5 or outlet 6 of the heated medium, with a multi-row beam 8 of four outlet heat transfer pipes 9, mainly with an unequal number of pipes 9 in adjacent rows 10, mainly horizontal, with vertical and horizontal separation from each other by means of spacer elements 11. Each heat transfer pipe 9 of row 10 is made with the number of bends 12, 13 different pipes 9 of the bundle 8 from four to six, forming four straight branches 14, 15 and the three elbows 16, 17, 18 connecting them. The number and distribution of pipes 9 in the bundle 8 are accepted under the condition that the volume ratio V _t. [m ³ ] occupied by heat exchange tubes 9 in block 1 and equal to the total volume of straight branches 14, 15 and elbows 16-18 of tubes 9 of bundle 8, defined along the outer contour with conditional planes touching the outer surfaces of the extreme heat exchange tubes 19, 20, minus the volume of the annular medium between the branches 14, 15 and the elbows 16-18 of the pipes 9 of the beam 8, to the total internal volume of the heat exchange unit V _ext. [m ³ ], limited by the bottom, top cover and end walls of the block casing, is defined in the range of values

component of 0.56 ÷ 0.85. The ratio of the total length ∑L [m] of pipes 9 of the beam 8 to the total area ∑S _nt the external heat exchange surface of the pipes 9 is determined by the coefficient

components of 0.08 ÷ 0.32 [m ^-1 ].

In each section 1 of the heat exchanger, the heat exchange blocks 2 are located one above the other, and the preferred number of blocks is four. The inlet collector 5 and the outlet collector 6 of the heated medium are adapted to be connected to the inlet and outlet pipelines of the heated medium, which is preferably used as air, including with an enriched oxygen content. As a cooled medium, combustion products after the turbine of a gas turbine plant are used.

. Внешняя труба 19 каждого из рядов 10, имеющих большее число труб 9, чем в смежных с ним рядах, имеет один гиб 12 длиной πR, образующий колено 17, соединяющее внутренние ветви 15 этой трубы 9, а общее число гибов 12, 13 этой трубы равно пяти. Внутренняя труба 20 каждого из рядов 10, имеющих большее число труб 9, чем в смежных с ним рядах, имеет два гиба 12 длиной πR, каждый из которых образует колено 16, 18, соединяющее соответствующие внутреннюю 15 и внешнюю 15 ветви этой трубы 9, а общее число гибов 12, 13 у этой трубы 9 равно четырем. Шаг а между продольными осями смежных труб 9 прямолинейных ветвей 14, 15 составляет (1,5-2,5)d, где d - наружный диаметр теплообменной трубы 9. Шаг b между осями смежных труб 9 на прямолинейных участках - вставках 21 колен 16-18 составляет (1,8-2,8)d. В каждом ряду 10 шаг а между продольными осями смежных труб прямолинейных ветвей 14, 15 меньше или больше, чем шаг b между продольными осями колен 16-18 смежных труб 9, предпочтительно а<b, или шаг а равен шагу b, и количество теплообменных труб 9 в смежных по высоте рядах 10 пучка 8 для нечетных и четных рядов составляет соответственно m и n, где m - четное число, а n=(m-1), количество рядов труб в пучке k - предпочтительно нечетное, причем k>3, теплообменные трубы в смежных по высоте рядах размещены в шахматном порядке со смещением на (0,4÷0,6)a [м], где а - шаг между продольными осями смежных труб на прямолинейных ветвях 14, 15 одного ряда 10 [м], при этом количество труб 9 в блоке 1 составляет предпочтительно 263-563 шт.The ratio of the total length ∑l "of the straight branches 14, 15 of the heat exchange tubes 9, streamlined in the transverse direction, to the total length ∑L [m] of all heat exchange tubes 9 of the beam 8 is 0.78-0.92. The outer 19 and inner 20 pipes each row 10 of the beam 8 each contains at least one bend 12 of length πR, and the bends 13 of the remaining pipes 9 in all rows 10 of the beam 8 are made of a length equal to

. The outer pipe 19 of each of the rows 10, having a larger number of pipes 9 than in adjacent rows, has one bend 12 of length πR, forming a bend 17 connecting the internal branches 15 of this pipe 9, and the total number of bends 12, 13 of this pipe is five. The inner pipe 20 of each of the rows 10, having a larger number of pipes 9 than in adjacent rows, has two bends 12 of length πR, each of which forms an elbow 16, 18 connecting the corresponding internal 15 and external 15 branches of this pipe 9, and the total number of bends 12, 13 in this pipe 9 is four. The step a between the longitudinal axes of adjacent pipes 9 of straight branches 14, 15 is (1.5-2.5) d, where d is the outer diameter of the heat exchange pipe 9. Step b between the axes of adjacent pipes 9 on straight sections - inserts 21 of the elbows 16- 18 is (1.8-2.8) d. In each row 10, step a between the longitudinal axes of adjacent pipes of rectilinear branches 14, 15 is smaller or larger than step b between the longitudinal axes of the elbows 16-18 of adjacent pipes 9, preferably a <b, or step a is equal to step b, and the number of heat exchange tubes 9 in adjacent rows of height 10 of bundle 8 for odd and even rows is respectively m and n, where m is an even number and n = (m-1), the number of rows of pipes in the bundle k is preferably odd, and k> 3, heat exchanging pipes in rows adjacent in height are placed in a checkerboard pattern with an offset of (0.4 ÷ 0.6) a [m], where a is the step between single axes of adjacent pipes on straight branches 14, 15 of one row 10 [m], while the number of pipes 9 in block 1 is preferably 263-563 pcs.

содержит сопряженную с гибами 13 прямолинейную вставку 21 длиной, кратной 2а, где а - шаг между осями одноименных прямолинейных ветвей 14, 15 смежных труб 9 ряда 10, или каждое колено 16-18 труб 9 всех рядов 10 пучка 8, образованное двумя гибами 13 длиной каждый, равной

, содержит сопряженную с гибами 13 прямолинейную вставку 21 длиной, изменяющейся у разных труб 9 ряда 10 от величины, равной 2а±10% [м], до величины, равной 2а(m-1)±10% [м], для рядов с большим числом труб 9, чем в смежных с ними по высоте рядах, а для остальных рядов до величины, равной а(2n-1)±10% [м], гдеEach bend of 16-18 pipes 8 of all rows 10 of the bundle 8, formed by two bends 13 each equal in length

contains a rectilinear insert 21 conjugated with bends 13, a multiple of 2a, where a is the step between the axes of the same straight branches 14, 15 of adjacent pipes 9 of row 10, or each bend of 16-18 pipes 9 of all rows 10 of bundle 8, formed by two bends 13 of length each equal

contains a rectilinear insert 21 associated with the bends 13 with a length varying for different pipes 9 of row 10 from a value of 2a ± 10% [m] to a value of 2a (m-1) ± 10% [m] for rows with a larger number of pipes 9 than in rows adjacent to them in height, and for the remaining rows up to a value equal to a (2n-1) ± 10% [m], where

a is the step between the axes of the same rectilinear branches of adjacent pipes of a row [m],

m is the number of pipes in a row with a large number of pipes, mainly an even number of pipes in odd rows,

n is the number of pipes in a row with a smaller number of pipes, mainly an odd number of pipes in even rows.

The heat exchange unit 2 according to the first embodiment of the heat exchanger — a block-sectional air heater contains four branches 14, 15, a four-way multi-row bundle 8 of heat exchange tubes 9, laid in horizontal rows 10 and spaced horizontally and vertically from each other, a supply collector 5 and a discharge collector 6 of the heated medium, each of which is connected to heat exchange tubes 9 by means of separate tube plates 7 mounted directly into the wall of the corresponding collector 5 or retraction of the heated medium. Each heat exchange tube 9 of row 10 is made with four, or five, or six bends 12, 13 of radius R, forming four straight branches 14, 15 and three knees 16-18 connecting them. The bending sections 12 for two pipes 9 in each odd row have a length πR, namely, for one pipe - on the inner elbow 17, the other - on the two outer elbows 16, 18, for the remaining pipes of odd and even rows, the bending sections 13 are length πR / 2 and articulated in pairs by means of straight inserts 14, 15 of length N ^' _i for the external elbows 16, 18 and H ^" _i for the internal elbow 17. The number of heat transfer tubes 9 in adjacent rows 10 of the bundle 8 for odd and even rows is respectively m and n, where m is an even number and n = (m-1). The number of rows of 10 pipes 9 in a bundle of 8 k is preferable odd, and moreover, k> 3, the heat transfer pipes in rows adjacent in height are staggered with an offset of (0.4 ÷ 0.6) a [m], where a is the step between the longitudinal axes of the straight branches of adjacent pipes of the same row [ m]. The lengths Н ' _i and Н ^" _{i of the} rectilinear inserts of 21 bends of the 16-18th pipe are made by variables: for an odd number of heat-exchange pipes, varying from a value of 2a ± 10% [m] to a value of 2a (m -1) ± 10% [m], and for an even row, from a value equal to a ± 10% [m], to a value equal to a (2n-1) ± 10% [m].

составляющим (84,5-460) [м^-1], согласно второму условию отношение суммарного объема ∑V_в.с. для нагреваемой среды в трубах ветви пучка к объему V_м.с определено коэффициентом

составляющим 0,78-1,25.The placement of the pipes 9 in the volume occupied by at least one branch 14 or 15 of the bundle 8 is accepted subject to the conditions, according to the first of which the ratio of the total area is нF _ntp the outer surface of the heat exchange tubes 9 of the branch 14 or 15 of the beam 8 to the scope ΣV _MS occupied by the annular medium in the area of active heat transfer of the branch 14 or 15 of the beam 8 and equal to the volume of the branch 14 or 15 of the beam 8 along the external contour outlined by the conditional planes touching the outer surfaces of the extreme heat transfer tubes 19, 20 of the branch 14 or 15 of the beam 8, minus the volume occupied by the heat exchange tubes 9 in this branch 14 or 15 of the beam 8 is in the range of values determined by the coefficient

components (84,5-460) [m ^-1], the second condition the ratio of the total volume _VS ΣV for the heated medium in the pipes of the beam branch to the volume V _{m.s is} determined by the coefficient

constituting 0.78-1.25.

The parameters of each pipe 9 of row 10 are determined by the dependencies:

L _{i + 1} = 2l ^' _{i + 1} + 2l ^'' _{i + 1} -Δ + 2H ^' _{i + 1} + H ^'' _{i + 1} + 3πR, where

L _{i + 1} - scan length of the (i + 1) th row pipe [m];

l ^' _{i + 1} is the length of the outer rectilinear branch of the 14 (i + 1) th pipe of the row, equal to l' _{i + 1} = l ' _i -b [m];

l ^" _{i + 1} - the length of the inner straight branch of the 15 (i + 1) -th pipe of the row, equal to l ^" _{i + 1} = l ^' _i -Δ [m];

H ^' _{i + 1} - the length of the rectilinear inserts 21 of the outer elbows of the 16th, 18th (i + 1) th pipe of the row, equal to H ^' _{i + 1} = H ^' _i -2a [m];

H " _{i + 1} - the length of the straight insert of the inner bend of the (i + 1) th pipe of the row, equal to H ^" _{i + 1} = H _i ^" + 2a [m];

a - step between the longitudinal axes of the same straight branches adjacent in the row of pipes [m];

b is the step between the longitudinal axes of the rectilinear inserts of the elbows of adjacent pipes in the row [m];

Δ is an empirical value equal to [3-12] · 10 ^-3 [m];

l ^' _i , l ^" _i , Н ^' _i and H ^" _i are the corresponding parameters for the i pipe in the row, counting from the outer pipe to the inner pipe in this row, and step a is (1.5-2.5) · d, step b is (1.8-2.8) · d, where d is the outer diameter of the heat exchanger pipe [m], the scan length L _{min of the} heat transfer pipe of the minimum length is at least 0.75 of the scan length L _{max of the} heat transfer pipe, this placement of the heat transfer pipes 9 in a row 10 is selected subject to the condition according to which the ratio of the internal surface area of the heat transfer pipes 9 on straight branches 1 4, 15 rows located perpendicular to the flow of the cooled medium, to the volume occupied by the series of heat transfer pipes, and equal to the volume outlined by the conditional planes touching the outer surfaces of the heat transfer pipes 9 of row 10, taking into account the gaps between the pipes, is 0.02-0.12 [m ^-1 ].

The pipe row 10 contains an even number of pipes 9, preferably at least two and no more than ten, or it contains an odd number of pipes 9, preferably at least three and no more than nine, while the pipes are arranged in a row with a variable distance between the axes of the outer branches 14, 15. The smallest value of this distance is for the pipe, the ends of which are sealed in the extreme closest to each other holes of the corresponding single-level rows of holes in the pipe boards 7 of the supply manifold 5 and exhaust 6 of the heated medium, preferably air, heat exchange unit 2 regenerative air heaters. Each subsequent four-branch pipe 9 of row 10 is made covering the previous one from the outer side of the outer branches 14 and the largest value of this distance is at the pipe 9, the ends of which are sealed in the outermost most distant from each other holes of the corresponding sibling rows of holes in the pipe boards 7 of the supply 5 and outlet 6 collectors heated medium. Two internal branches 14 of each subsequent pipe in a row with the elbow 17 connecting them are placed on the outside in a bend formed by the respective branches 15 and connecting the elbow 17 of the previous pipe in the pipe row. The step a between the longitudinal axes of the straight lines of the same name 14, 15 adjacent pipes in a row is less than or greater than step b between the longitudinal axes of the straight inserts 21 of the elbows 16-18 adjacent pipes in a row, preferably a <b, or step a is equal to step b, and , in addition, for each heat transfer tube of a series, the distance H between the longitudinal axes of its external straight branches is (30-85) d; the length of the straight branches l 'and l "is respectively (74-145) d and (100-135) d, where d is the outer diameter of the heat transfer pipe [m]. The number N of heat transfer pipes 9 in block 2 with an odd number of rows of k pipes in the bundle is determined by the dependence N = 0.5 (k-1) (2m-1) + m, or the number N of heat transfer tubes in the block with an even number of rows of k tubes in the bundle is determined by the dependence N = 0.5k (2m-1).

Between the collectors of the inlet 5 and the outlet 6 of the heated medium, a displacer 22 of the annular medium is fixed, made in the form of a profiled panel with a flat section 23 located between the collectors of the inlet 5 and the outlet 6 of the heated medium. The cross-sectional area of the supply manifold 5 or the exhaust manifold 6 of the heated medium is 0.45-0.82 of the total cross-sectional area of the heat exchange tubes 9 of the beam 8. The heat exchange unit 2 is equipped with sling devices 24 and manholes (not shown), made in the collectors of the supply 5 and exhaust 6 of the heated medium.

The heat exchange unit 2 according to the second embodiment comprises a housing 29 consisting of a space frame 25, a bottom 26, an upper cover 27 and end walls 28, a supply diffuser 3 and a confuser 4 for draining the cooled medium, supply manifolds 5 and outlet 6 of the heated medium with tube sheets 7 and a multi-way multi-row bundle 8 of heat-exchange tubes 9, forming respectively in each row 10 an even number of straight-line multi-tube branches 14, 15, including at least two internal 15 and two external 14 connected by sections with bends 12, 13 is predominantly constant for all pipes 9 beam 8 radius. The bottom 26, the cover 27, and one of the end walls 28 of the housing 29 of the block 2 are made in the form of panels with a strapping of stiffeners forming flat rod systems 30. The spatial frame 25 of the block 2 is formed by a combination of flat rod systems 30 of the frames of these panels with intermediate racks connecting them 31 and the collector bodies of the supply 5 and the removal 6 of the heated medium that are rigidly connected with them. The collectors of the inlet 5 and outlet 6 of the heated medium, in turn, are connected to the bottom 26 of block 2 and to each other by double-ring diaphragms and a displacer 22 of the annular medium. Parts of the bodies of the manifolds for supplying 5 and venting 6 of the heated medium with tube plates 7 mounted in them and the annular displacer 22 together form a spatially developed rigid end wall 32 of the housing 29 of block 2. Along the longitudinal sides of the frame 25 are adapted to mount respectively the elements of the diffuser 3 for supply and confuser 4 for the removal of the cooled medium. For each heat exchange tube 9 of the beam 8, the distance H between the longitudinal axes of its outer straight branches 14, 15 is (30-85) d; the length of the straight branches l 'and l "is respectively (95-145) d and (100-135) d, where d is the outer diameter of the heat exchanger pipe [m].

The displacer 22 of the annular medium is made in the form of a profiled panel with a flat section 23, the inner surface of which is located between the collectors of the inlet 5 and the outlet 6 of the heated medium in the same plane as the outer plane of the tube plates 7, or in the form of a flat panel welded to the walls of the inlet manifolds 5 and of the outlet 6 of the heated medium so that its inner surface is located in the same plane as the outer plane of the tube plates 7. The heat exchange unit 2 is provided with a distance fixed to the bottom 26 and frame 25 of the housing 29 of the housing 29 the ruling elements 11 for heat transfer tubes 9 of the outer branches of the beam 14 in the form of spacing grids. Said heat exchange tubes are passed through the openings of the distance grids. Subsequent rows of heat transfer pipes 9 in the area of the internal branches 15 are separated by folded spacers 33 that are attached to struts mounted on the bottom 26. Combs 34 are fixed on the bottom 26 of the housing 29 for at least the internal branches 15 of the lower row of heat transfer pipes 9.

The cross-sectional area of each of the collectors for supplying 5 and exhaust 6 of the heated medium is 1.8-3.5 of the total flow area of heat-transfer pipes 9 in block 2. The collectors for supplying 5 and exhaust 6 of the heated medium are made with manholes located on the side bottoms 26 of block 2. Covers 35 of manholes are pivotally mounted on the bodies of the supply manifold 5 and the outlet 6 of the heated medium with the possibility of rotation in a plane perpendicular to the longitudinal axis of symmetry of the supply manifold 5 and the outlet 6 of the heated medium. On the inner walls of the manifolds for supply 5 and exhaust 6 of the cooled medium, supports are formed that form a ladder for inspection and maintenance of the manifolds for supply 5 and exhaust 6 of the heated medium and tube plates 7.

The heat exchange unit 2 is equipped with means for attaching a diffuser 3 for supply and a confuser 4 for draining the cooled medium mounted on the opposite side elements of the spatial frame 25 of unit 2, as well as brackets for attaching external thermal insulation.

For the outer branches 14 of the beam 8, the distance elements 11, providing horizontal and vertical spacing of the heat exchange tubes 9, and their spatial fixation, are formed by a separator 36 with holes for the passage of pipes 9, made with the possibility of fixing in the housing of the regenerative air heater 1. For the internal branches of the 15 beam 8 pipes 9 spacing elements 11 are made in the form of folded spacers 33 having alternating supporting sections 37 located on both sides of the plates, one at the upper and lower heights upah creases for supporting contact the respective lower and upper protrusions of adjacent adjustment folded strips 33 and connecting the two ledges inclined portion 38 forming the supporting elements for supporting the tube bundle. Heat transfer tubes 9 are spaced vertically and horizontally from each other to ensure a distance between the longitudinal axes of adjacent heat transfer tubes in a row of 1.5-2.3 diameters of heat transfer tube 9. In rows 10 adjacent to each other in height, providing a distance between the longitudinal axes heat transfer pipes 9 adjacent rows, comprising 0.6-1.5 diameter of the heat transfer pipe 9.

The heat exchange tubes 9 in staggered rows are staggered, the distal folded elements 11 of each overlying row are supported by their lower protrusions on the vertices of the upper protrusions of the folds of the folds of the adjacent vertically adjacent distant element 11, facing them, with the formation of a system of support contacts displaced in each subsequent the height of the row is 0.4-0.6 steps of the pipes 9 in the row 10. The thickness of the folded strip 33 is not less than 0.03 of the diameter of the heat transfer pipes 9, and the distance elements 11 on the external 14 and internal 15 yours are located along the length of the heat exchange tubes 9, preferably with the same pitch. The set of folded spacing elements 11 forms a prefabricated, at least in the cross section of the branch 14, 15 spatial carrier grid, at least for the corresponding branch 14, 15 of the beam 8 with the longitudinal and transverse steps of its constituent elements corresponding to the longitudinal and transverse steps of the heat exchange pipes 9 bundle 8.

In each row, the step a between the longitudinal axes of adjacent pipes of the rectilinear branches 14, 15 is less than or greater than the step b between the longitudinal axes of adjacent pipes in the straight section 21 of the elbow 16-18, preferably a <b, or step a is equal to step b. The bend sections 12 for two pipes in each odd row have a length πR, namely, for one pipe - on the inner elbow 17, the other - on the two outer elbows 16, 18, for the remaining pipes of odd and even rows, the bend sections 13 have a length πR / 2 and articulated in pairs by means of straight sections 21 of various lengths.

The supporting sections 37 on the upper and lower protrusions of the fold are made with a supporting surface in the form of a fragment of a cylindrical surface with a radius of not more than 35% of the diameter of the heat exchange pipe 9 facing outward, or the supporting sections 37 on the upper and lower protrusions of the fold are made with a flat supporting surface.

The inlet collector 5 or the outlet manifold 6 for the heated medium of a heat exchanger of the block or block-sectional regenerative air heater type is made in the form of a cylindrical shell 39 with an aperture in which a tube board 7 is projected. A projection onto the end of the tube board 7 of a curved section of the shell 39 forming the end of the opening located within the thickness of the tube plate 7. The tube plate 7 is made with through holes 40 for the ends of the heat transfer tubes 9 of the heat exchange unit 2. The holes 40 are arranged in rows along the height of the tube oh board 7 with a step in the axes in a row of (1.5-2.8) · d, step rows along the height of the tube 7, component (0.60-0.84) · d, where d is the outer diameter of the heat exchange pipes 9, and with the displacement of the holes 41 in adjacent rows by (0.4 ÷ 0.6) the step size in a row.

The total area of the through holes 40 in the tube plate 7 for the ends of the heat exchanger tubes 9 of the heat exchange unit 2 is 56-85% of the total area of the tube field in the plane of the tube plate 7, limited by a contour formed by a set of conditional straight lines tangent to the outer edges of the extreme holes 40 in the tube plate 7, and the area of the tube field is 0.75 ÷ 0.94 of the total frontal area of the projection of the tube plate.

The connection of the shell 39 with the tube plate 7 in the plane of the cross section of the shell is made in the angular range γ = 28-75 °, and the ratio of the projection area to the specified plane of the curved section of the shell 39 forming the end face of the opening to the projection area on this plane of the corresponding end of the tube plate is 0.048 ÷ 0.172.

The lateral edges of the tube plate 7 are trihedral, while one of the faces 41 is formed in cross-section to form a support section in contact with the shell 39, and the edges adjacent to it are made one 42 adjacent to the surface of the tube plate 7 facing the supply manifold 5 or of the outlet 6 of the heated medium, with a bevel forming an angle α = (22-29) ° with the plane of the supporting section, and the other 43 facing the outer surface of the tube plate 7, the face is made with a bevel forming an angle β = (25 with the plane of the supporting section) -35) °.

The trihedral edges of the tube plate 7 are made with a width of the supporting portion of at least 4.5% of the total thickness of the plate forming the tube plate 7, face 42 with a bevel α = (22-29) ° is made of a width of 5.9-12.5 % of the total thickness of the plate, and face 43 with a bevel β = (25-35) ° is made with a width of 79-89.6% of the total thickness of the plate.

The heat exchange unit 2 may comprise a multi-row bundle of heat exchange tubes consisting of at least two packages of two-way U-shaped pipes 45, 46, forming within each package 44 two-branch pipes, for example, horizontal rows of pipes 45, 46 spaced within a row and between the rows from each other, the inlet collector 5 and the outlet manifold 6 of the heated medium and at least one bypass chamber 47 located between them, the inlet manifold 5 and the outlet manifold 6 of the heated medium, as well as the bypass chamber 47 are connected to by exchange tubes 45 with a common tube board 48 or separate tube boards 7, at least part of which or of which forms part of the wall enclosure of the supply manifold 5 and the exhaust manifold 6 of the heated medium and the bypass chamber 47.

The heat exchange unit according to the third embodiment comprises a multi-row bundle of heat exchange pipes, consisting of at least two packages 44 of two-way U-shaped pipes 45, 46, forming two-branch pipes, for example, horizontal rows of pipes 45, 46 spaced within row and between rows from each other, the supply manifold 5 and the collector of the outlet 6 of the heated medium and located between them at least one bypass chamber 47, and the collector of the supply 5 and the collector of the outlet 6 of the heated medium, as well as bypass The chamber 47 is connected to the heat exchange pipes 45 by a common pipe board 48 or separate pipe boards 7, at least part of which or which forms part of the wall enclosure of the supply manifold 5 and the exhaust manifold 6 of the heated medium and the bypass chamber 46. The total area of the through holes in the tube plate 48 or tube plates 7 under the ends of the heat exchange tubes 45, 46 of the heat exchange unit 2 is 29-85% of the total area of the tube field.

In each package 44, through a row, one inner pipe 45 of a row is made with a bend length equal to πR, and all other pipes 46 of all rows of a package 44 are made with two bends each with a length equal to πR / 2, where R is the bend radius, which is (2, 5-6.0) d, where d is the outer diameter of the heat exchanger pipe 45, 46, and coupled in pairs by means of straight sections of different lengths.

составляющем 0,56-0,85, а отношение суммарной длины ∑L [м] труб пучка к суммарной площади ∑S_н.т.т. внешней теплообменной поверхности труб 45, 46 определено коэффициентом

составляющим 0,08-0,32 [м^-1].The number and distribution of pipes 45, 46 in the bundle are taken subject to the condition under which the volume ratio V _t. [m ³ ] occupied by heat exchange tubes 45, 46 in block 2 and equal to the total volume of straight branches 50 and elbows 51 of tube 45, 46 of the bundle, defined along the outer contour with conditional planes touching the outer surfaces of the outer heat exchanger tubes 46, minus the volume of the annulus between the branches 50 and the elbows 51 of the tubes 45, 46 of the bundle, to the total internal volume of the heat exchange unit 2 V _ext. [m ³ ], defined in the range of values

constituting 0.56-0.85, and the ratio of the total length ∑L [m] of the beam pipes to the total area ∑S _nt the external heat exchange surface of the pipes 45, 46 is determined by the coefficient

constituting 0.08-0.32 [m ^-1 ].

In each row, the step a between the longitudinal axes 52 of the adjacent pipes 45, 46 of the straight branches 50 is smaller or larger than the step b between the longitudinal axes of the elbows 51 of the adjacent pipes 45, 46, preferably a <b, or the step a is equal to step b.

The step a between the longitudinal axes of adjacent pipes 45, 46 of straight branches 50 can be (1.5-2.5) d, where d is the outer diameter of the heat exchange pipe 45, 46, and step b between the axes of adjacent pipes 45, 46 in straight sections 49 elbows 51 is (1.8-2.8) d.

Preferably, air, including with an enriched oxygen content, can be used as the heated medium, while the products of combustion after the turbine of the gas turbine installation are used as the cooled medium.

The regenerative air heater is as follows.

The air intended for the combustion of a gas turbine plant enters a compressor in which it is compressed, and then it is supplied through a supply pipe through a manifold for supplying a heated medium and a tube board to the heat transfer pipes of the heat exchange blocks of each section. The air temperature after the compressor is about 200 ° C.

Combustion products of the above composition from a gas turbine turbine through a diffuser adjacent to the housings of the heat exchange units enter the section unit and wash the heat exchange pipes with heated air. The supply of combustion products to the heat exchange units is countercurrent with the direction of movement of the heated air, that is, the combustion products enter the heat exchange unit from the location of the collector of the outlet of the heated medium. At the entrance to the heat exchange unit, the combustion products have a temperature of 520-550 ° C.

Passing through the heat exchanging pipes of the blocks, the air is heated by the combustion products to a temperature of 440-450 ° C and through the pipe board it enters the collector of the outlet of the heated medium, from which it is supplied through the pipeline to the inlet of the gas turbine combustion chamber.

Combustion products are discharged into the atmosphere through a confuser adjacent to the bodies of the heat exchange units.

Claims (21)

1. A heat exchanger is a block-sectional air heater, characterized in that it contains at least two sections, each of which contains at least two heat exchange units, each of which includes a diffuser for supply and a confuser for removal of the cooled the medium, the supply manifold and the collector of the outlet of the heated medium, each of which is connected by means of separate tube plates mounted directly into the wall of the corresponding collector of the inlet or outlet of the heated medium, with multiple rows a bundle of four-way heat transfer pipes, mainly with an unequal number of pipes in rows adjacent in height, mainly horizontal, with vertical and horizontal separation from each other by means of spacer elements, each heat transfer pipe of a row made with a number of bends for different bundle pipes from four to six forming four rectilinear branches and connecting their three knees, the number and distribution of pipes in the bundle are taken under the condition that the volume ratio V _t. [m ³ ] occupied by heat transfer tubes in the block and equal to the total volume of straight branches and elbows of the beam tubes, outlined along the external contour with conditional planes touching the outer surfaces of the extreme heat transfer tubes, minus the volume of the annular medium between the branches and elbows of the bundle tubes to the total internal volume heat exchange unit V _{ext. bl ··} [m ³ ], limited by the bottom, top cover and end walls of the unit casing, is determined in the range of values

component of 0.56-0.85, and the ratio of the total length ΣL [m] of the tube tubes to the total area ΣS _nt the external heat exchange surface of the pipes is determined by the coefficient

constituting 0.08-0.32 [m ^-1 ]. 2. The heat exchanger according to claim 1, characterized in that in each of its sections the heat exchange blocks are located one above the other, and the preferred number of blocks is four, and the supply manifold and the collector of the outlet of the heated medium are made with the possibility of connection with the pipelines of supply and removal of the heated medium , which is preferably used air, including with an enriched oxygen content, while the products of combustion after the turbine of a gas turbine plant are used as a cooled medium. 3. The heat exchanger according to claim 1, characterized in that the ratio of the total length ΣL "of rectilinear branches of heat exchange pipes streamlined in the transverse direction to the total length ΣL [m] of all heat transfer tubes of the beam is 0.78-0.92, wherein the outer and inner pipes in each row of the bundle each contain at least one bend of length equal to πR, and the bends of the remaining pipes in all rows of the bundle are made of length equal to

the outer pipe of each of the rows having a larger number of pipes than in the rows adjacent to it has one bend of length πR forming a bend connecting the internal branches of this pipe, and the total number of bends of this pipe is five, and the inner pipe of each of the rows having a larger number of pipes than in rows adjacent to it, has two bends of length πR, each of which forms an elbow connecting the corresponding internal and external branches of this pipe, and the total number of bends at this pipe is four, the pitch and between the longitudinal axes of adjacent straight pipe Twi is (1.5-2.5) d, where d is the outer diameter of the heat exchanger pipe, the step ″ b ″ between the axes of adjacent pipes on the straight sections of the elbows is (1.8-2.8) d, and in each row the step ″ A ″ between the longitudinal axes of adjacent pipes of rectilinear branches is smaller or larger than the step ″ b ″ between the longitudinal axes of the elbows of adjacent pipes, preferably a <b, or step a is equal to the step ″ b ″, and the number of heat-exchange tubes in the rows of bundles adjacent in height for odd and even rows is respectively m and n, where m is an even number, an = (m-1), the number of rows of pipes in the bundle k is pre respectfully odd, and k> 3, the heat transfer pipes in rows adjacent in height are staggered with an offset of (0.4-0.6) a [m], where a is the step between the longitudinal axes of adjacent pipes on the straight branches of one row [m], while the number of pipes in the block is preferably 263-563 pcs. 4. The heat exchanger according to claim 1, characterized in that each pipe elbow of all rows of the bundle, formed by two bends each equal in length

contains a straight insert coupled to bends, a length multiple of 2a, where a is the step between the axes of the same straight branches of adjacent pipes in a row, or each pipe bend of all rows of a bundle, formed by two bends each equal in length

contains a straight insert coupled with bends, with a length varying in different pipes of the row from a value equal to 2a ± 10% [m] to a value equal to 2a (m-1) ± 10% [m] for rows with a larger number of pipes than in adjacent with them in row height, and for the remaining rows to a value equal to a (2n-1) ± 10% [m], where a is the step between the axes of the same rectilinear branches of adjacent pipes of the row, [m], m is the number of pipes in a row with a large number of pipes, mainly an even number of pipes in odd rows, n is the number of pipes in a row with a smaller number of pipes, mainly an odd number of pipes in even rows. 5. The heat exchanger block of the heat exchanger - block-sectional air heater, characterized in that it contains four-way multi-row bundle of heat exchanger tubes consisting of four branches, laid in horizontal rows and spaced horizontally and vertically from each other, the supply manifold and the collector of the outlet of the heated medium, each of which is connected to heat exchange pipes by means of separate tube plates mounted directly into the wall of the corresponding inlet or outlet manifold heating medium, each heat transfer tube of a row made with four, or five, or six bends of radius R, forming four straight branches and connecting them three knees, while the bending sections of two pipes in each odd row have a length πR, namely, one the pipes are on the inner bend, the other has two outer bends, for the remaining pipes of odd and even rows, the sections of the bend are πR / 2 in length, and are joined in pairs by straight inserts of length N ' _i for the outer bends and H " _i for the inner bend , and the amount of heat The number of pipes in adjacent rows of the bundle for odd and even rows is respectively m and n, where m is an even number and n = (m-1), the number of rows of pipes in the bundle k is preferably odd, and k> 3, heat exchange the pipes in rows adjacent in height are placed in a checkerboard pattern with an offset of (0.4-0.6) a [m], where a is the step between the longitudinal axes of the rectilinear branches of adjacent pipes of the same row, [m], with the length N ' _i and Н " _{i of the} straight insertions of the knees of the i-th pipe are made variables: for an odd number of heat-exchange pipes changing from a value equal to 2a ± 10%, [m], to a value equal to 2a (m-1) ± 10% [m] and for an even row - from a value equal to a ± 10% [m], to a value equal to a (2n-1) ± 10% [m]. 6. The heat exchange unit according to claim 5, characterized in that the placement of the pipes in the volume occupied by at least one branch of the beam is made subject to the conditions, according to the first of which the ratio of the total area ΣF _ntp the outer surface of the heat exchange tubes of the bundle branches to the scope ΣV _MS occupied by the annular medium in the area of active heat transfer of the beam branch and equal to the volume of the beam branch along the external contour, outlined by conditional planes touching the outer surfaces of the extreme heat transfer tubes of the beam branch, minus the volume occupied by the heat transfer tubes in this beam branch, is in the range of values determined by the coefficient

components (84,5-460) [m ^-1], the second condition the ratio of the total volume _VS ΣV for the heated medium in the pipes of the beam branch to the volume V _m.s. determined by the coefficient

constituting 0.78-1.25. 7. The heat exchange unit according to claim 5, characterized in that the parameters of each row pipe are determined by the dependencies L _{i + 1} = 2l ' _{i + 1} + 2l'' _{i + 1} -Δ + 2H' _{i + 1} + H '' _{i + 1} + 3πR, where L _{i + 1} - scan length of the (i + 1) th row pipe [m]; l ' _{i + 1} is the length of the outer straight branch (i + 1) of the row pipe equal to l' _{i + 1} = l ' _i -b [m]; l " _{i + 1} is the length of the internal straight branch (i + 1) of the row pipe equal to l" _{i + 1} = l ' _i -Δ [m]; H ' _{i + 1} - the length of the rectilinear inserts of the outer elbows of the (i + 1) th pipe of the row, equal to H' _{i + 1} = H ' _i -2a [m], H " _{i + 1} - the length of the straight insert of the inner bend of the (i + 1) th pipe of the row, equal to N" _{i + 1} = H " _i + 2a [m]; a - step between the longitudinal axes of the same straight branches adjacent in the row of pipes [m]; b is the step between the longitudinal axes of the rectilinear inserts of the elbows of adjacent pipes in the row [m]; Δ is an empirical value equal to [3-12] · 10 ^-3 [m]; l ' _i , l " _i , H' _i and H" _i are the corresponding parameters for the ″ i ″ pipe in the row, counting from the outer pipe to the inner pipe in this row, and the step ″ a ″ is (1.5-2.5 ) · D, the step ″ b ″ is (1.8-2.8) · d, where d is the outer diameter of the heat exchanger pipe [m], the reamer length L _{min of the} heat exchanger pipe of the minimum length is not less than 0.75 reamer length L _max heat-transfer pipes of maximum length, while the placement of heat-exchange pipes in a row is selected subject to the condition according to which the ratio of the internal surface area of heat-transfer pipes on straight branches rows located perpendicular to the flow of the cooled medium, to the volume occupied by the series of heat transfer pipes, and equal to the volume outlined by the conditional planes touching the outer surfaces of the heat transfer pipes of the series, taking into account the gaps between the pipes, is 0.02-0.12 [m ^-1 ]. 8. The heat exchange unit according to claim 5, characterized in that the pipe row contains an even number of pipes, preferably not less than two and not more than ten, or it contains an odd number of pipes, preferably not less than three and not more than nine, wherein the pipes are located in along with a variable distance between the axes of the outer branches, the smallest value of this distance at the pipe, the ends of which are embedded in the holes closest to each other of the corresponding single-level rows of holes in the pipe boards of the headers for supplying and discharging the heated medium, etc. preferably air, the heat-exchange unit of the regenerative air heater, and each subsequent four-branch pipe of the row is made covering the previous one from the outer side of the external branches and the largest value of this distance at the pipe, the ends of which are embedded in the most extreme openings of the corresponding single-level rows of holes in the pipe boards of the supply manifolds and removal of the heated medium, and two internal branches of each subsequent pipe in a row with the elbow connecting them are placed on the outside in the bend formed by the corresponding branches and connecting the elbow of the previous pipe in the pipe row, the step ″ a ″ between the longitudinal axes of the same straight branches of adjacent pipes in the row is less than or greater than the step ″ b ″ between the longitudinal axes of the rectilinear inserts of the bends of adjacent pipes in a row, preferably a <b, or the step ″ a ″ is equal to the step ″ b ″, and, in addition, for each heat transfer tube of the row, the distance H between the longitudinal axes of its outer straight branches is (30-85) d; the length of the straight branches l 'and l "is respectively (74-145) d and (100-135) d, where d is the outer diameter of the heat exchanger pipe [m], while the number N of heat exchanger pipes in the block with an odd number of rows k of pipes in the bundle is determined by the dependence N = 0.5 (k-1) (2m-1) + m, or the number N of heat transfer tubes in the block with an even number of rows of k tubes in the bundle is determined by the dependence N = 0.5k (2m-1). 9. The heat exchange unit according to claim 5, characterized in that between the collectors of the supply and removal of the heated medium is fixed a displacer of the annular medium, made in the form of a profiled panel with a flat section located between the collectors of the supply or removal of the heated medium, while the passage area of the supply collector or the collector of the outlet of the heated medium is 0.45-0.82 of the total passage area of the heat transfer tubes of the beam, and the heat transfer unit is equipped with sling devices and manholes, data in the collectors of the inlet and outlet of the heated medium. 10. A heat exchanger block of a heat exchanger of the type of a block or block-section regenerative air heater, characterized in that it comprises a housing, a diffuser for supplying and discharging a cooled medium, manifolds for supplying and discharging a heated one consisting of a spatial frame, bottom, top cover and end walls media with tube plates and a multi-way multi-row bundle of heat transfer pipes, forming respectively in each row an even number of straight multi-tube branches, including at least Here, two internal and two external, connected by sections with bends of a beam of radius, which is predominantly constant for all pipes, or a multi-row bundle of heat exchange pipes, consisting of at least two packages of two-way U-shaped pipes forming double-branch pipes within each package, for example, horizontal rows of pipes spaced within the row and between the rows from each other, the supply manifold and the collector of the outlet of the heated medium and at least one bypass chamber located between them, the supply manifold and the collector of the outlet of the heated medium, as well as the bypass chamber, are connected to the heat exchange pipes by a common tube plate or separate tube boards, at least part of which or which forms part of the wall enclosure of the collector of the supply and collector of the outlet of the heated medium and the bypass chamber, while the cover and one of the end walls of the block body are made in the form of panels with a strapping of stiffeners forming flat rod systems, and the spatial frame of the block is formed by a set of plane x the core systems of the frameworks of these panels with intermediate racks uniting them and rigidly connected to them the bodies of the inlet and outlet of the heated medium, which, in turn, are connected to the bottom of the block and to each other by double-ring diaphragms and a displacer of the annular medium, and parts of the bodies of the supply and the removal of the heated medium with tube boards mounted in them and a displacer of the annular medium together form a spatially developed rigid end wall of the block casing, and along Aulnay side frame configured to mount the diffuser elements, respectively, and the converging tube for supplying and discharging the cooling medium, wherein each heat exchanger tube bundle distance H between the longitudinal axes of its external rectilinear branches is (30-85) d; the length of the straight branches l 'and l "is respectively (95-145) d and (100-135) d, where d is the outer diameter of the heat exchanger pipe [m]. 11. The heat exchange unit according to claim 10, characterized in that the displacer of the annular medium is made in the form of a profiled panel with a flat section, the inner surface of which is located between the inlet and outlet collectors of the heated medium in the same plane as the outer plane of the tube plates or in the form of a flat panel, welded to the walls of the collectors for supplying and discharging the heated medium so that its inner surface is located in the same plane as the outer plane of the tube plates, while the heat exchange unit is equipped with fixed on the bottom and the frame of the block body with spacer elements for heat transfer pipes of the outer branches of the multi-path bundle in the form of spacer grids, said heat transfer pipes being passed through the holes of the spacing grids, and subsequent rows of heat transfer pipes in the area of the inner branches are separated by folded spacing bars that are attached to the uprights, mounted on the bottom, and in addition, combs are fixed on the bottom of the body for at least the inner branches of the lower row of heat transfer pipes. 12. The heat exchange unit according to claim 10, characterized in that the cross-sectional area of each of the collectors for supplying and discharging the heated medium is 1.8-3.5 of the total passage area of the heat-transfer pipes in the block, while the collectors for supplying and discharging the heated medium made with manholes located on the bottom side of the unit, while manhole covers are pivotally mounted on the bodies of the inlet and outlet of the heated medium with the possibility of rotation in a plane perpendicular to the longitudinal axis of symmetry of the collectors inlet and outlet of the heated medium, and on the inner walls of the collectors of the inlet and outlet of the heated medium there are supports forming a ladder for inspection and maintenance of the collectors of the inlet and outlet of the heated medium and tube plates, and the heat exchange unit is equipped with means for attaching a diffuser for the inlet and the confuser for the outlet cooling medium mounted on opposite side elements of the spatial frame of the block, as well as brackets for attaching external thermal insulation. 13. The heat exchange unit according to claim 11, characterized in that the spacer grids are mounted so that they can be fixed in the regenerative air heater body, the folded spacer bars have alternating supporting sections located on both sides, one on the upper and lower ridges of the fold, for supporting contact of the corresponding lower and the upper protrusions of the folded planks adjacent in height and the two protruding sections connecting the protrusions, forming supporting elements for supporting the beam tubes, while the heat exchange tubes di are vertically and horizontally danced from each other to ensure a distance between the longitudinal axes of adjacent heat exchange tubes in a row of 1.5-2.3 diameters of the heat exchanger pipe, and in rows adjacent in height to ensure a distance between the longitudinal axes of the heat exchange tubes of adjacent rows, constituting 0.6-1.5 diameters of the heat exchanger tube, while the heat exchanger tubes in rows adjacent in height are staggered, the distal folded planks of each overlying row are supported by their lower protrusions on the front the vertices of the upper protrusions of the folds of the adjoining height of the underlying spacing strip with the formation of a system of support contacts displaced in each successive row by 0.4-0.6 pipe spacing in the row, and the thickness of the folded strip is at least 0.03 diameter heat-exchange pipes, and the distance elements on the external and internal branches are located along the length of the heat-exchange pipes, preferably with the same pitch, while the supporting sections on the upper and lower protrusions of the fold are made with a supporting surface in the form of a fragment ilindricheskoy radius surface, is not more than 35% of the diameter of the heat exchange tubes, outwardly facing convexity, or the support portions at upper and lower ledges formed folds with the flat supporting surface. 14. The heat exchange unit according to claim 10, characterized in that the supply manifold or the collector of the outlet of the heated medium is made in the form of a cylindrical shell with an aperture into which the tube plate is welded, the projection onto the end of the tube plate of a curved section of the shell forming the end face of the opening is located in within the thickness of the tube plate, which is made with through holes for the ends of the heat exchanger tubes of the heat exchange unit, the holes being arranged in rows along the height of the tube plate with a step in the axes in a row of (1.5-2.8) · d, step p the height of the tube plate, constituting (0.60-0.84) · d, where d is the outer diameter of the heat exchanger pipe, and with the displacement of holes in adjacent rows by (0.4-0.6) the step size in a row, at the total area of the through holes in the tube plate for the ends of the heat exchanger tubes of the heat exchange unit is 56-85% of the total area of the tube field in the plane of the tube plate, limited by the contour formed by a set of conditional straight lines tangent to the outer edges of the outer holes in the tube plate, and the area pipe field is 0.75-0.94 of the total the area of the frontal projection of the tube plate, the connection of the shell with the tube plate in the plane of the cross section of the shell is made in the angular range γ = 28-75 °, and the ratio of the projection area to the specified plane of the curved section of the shell forming the end face of the opening to the projection area on this plane of the corresponding end face the tube plate is 0.0480.172, and the lateral edges of the tube plate are trihedral, while one of the faces is made with the formation in cross section of a support section in contact with the shell, and approximately The faces sticking to it are made - one adjacent to the surface of the tube plate facing the collector for supplying or discharging the heated medium with a bevel that forms an angle α = 22-29 ° with the plane of the supporting section, and the other face facing the outer surface of the tube plate is made with bevel, forming an angle β = 25-35 ° with the plane of the supporting section. 15. The heat exchange unit according to 14, characterized in that the trihedral edges of the tube plate are made with a width of the support section of at least 4.5% of the total thickness of the plate forming the tube plate, a face with a bevel α = 22-29 ° is made wide, constituting 5.9-12.5% of the total plate thickness, and a face with a bevel β = 25-35 ° is made with a width of 79-89.6% of the total plate thickness. 16. The heat exchanger block of the heat exchanger - block-sectional air heater, characterized in that it contains a multi-row bundle of heat exchange pipes, consisting of at least two packages of two-way U-shaped pipes, forming within each package two-branch pipes, for example, horizontal rows of pipes spaced within the row and between the rows from each other, the supply manifold and the collector of the outlet of the heated medium and located between them at least one bypass chamber, and the supply manifold and the collector of the outlet of the heated medium, as well as the bypass chamber, are connected to the heat exchange pipes by a common tube board or separate tube boards, at least part of which or which form part of the wall enclosure of the collector of the supply and collector of the outlet of the heated medium and the bypass chamber, with the total area through holes in the tube plate or tube boards under the ends of the heat exchanger tubes of the heat exchange unit is 29-85% of the total area of the pipe field. 17. The heat exchange unit according to clause 16, characterized in that in each packet through the row one inner tube of the row is made with a bend of πR length, and all other pipes of all rows of the packet are made with two bends of each length equal to πR / 2, where R is the bending radius of (2.5-6.0) d, where d is the outer diameter of the heat exchanger pipe, and are joined in pairs by straight sections of different lengths. 18. The heat exchange unit according to clause 16, characterized in that the number and distribution of pipes in the bundle are taken in compliance with the condition under which the volume ratio V _t. [m ³ ] occupied by heat transfer tubes in the unit and equal to the total volume of straight branches and elbows of the beam tubes, outlined along the outer contour with conditional planes touching the outer surfaces of the extreme heat transfer tubes, minus the volume of the annular medium between the branches and elbows of the bundle tubes, to the total internal volume of the heat exchange unit V _{ext. bl ··} [m ³ ], determined in the range of values

component of 0.56-0.85, and the ratio of the total length ΣL [m] of the tube tubes to the total area ΣS _nt the external heat exchange surface of the pipes is determined by the coefficient

constituting 0.08-0.32 [m ^-1 ]. 19. The heat exchange unit according to clause 16, characterized in that in each row the step “a” between the longitudinal axes of adjacent pipes of rectilinear branches is less than or greater than the step ″ b ″ between the longitudinal axes of the elbows of adjacent pipes, preferably a <b, or step ″ A ″ is equal to the step ″ b ″. 20. The heat exchange unit according to clause 16, wherein the step ″ a ″ between the longitudinal axes of adjacent pipes of straight branches is (1.5-2.5) d, where d is the outer diameter of the heat exchange pipe, step ″ b ″ between the axes adjacent pipes in straight sections of the elbows is (1.8-2.8) d. 21. The heat exchange unit according to clause 16, characterized in that preferably air is used as a heated medium, including with an enriched oxygen content, while combustion products after a turbine of a gas turbine installation are used as a cooled medium.

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