RU2339889C2 - 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 plate, with, at least, one multi-row bank of multipass heat exchange pipes, the various pipes being furnished with bends varying in number from four to six and forming four rectilinear runs combining their three bends. Note here that the spacing in, at least, one direction, within the band cross section, of a part of the pipes or within their limits, or of, at least, one bank of the pipes out coming from the medium feed manifold, or, at least, in one of the next runs in the same direction does not comply with that of the pipes or a part of them in their bank run right nearby the manifold withdrawing the medium being heated and/or in one of the previous bank runs. The unit of the heat exchange-modular air heater comprises four runs of the heat exchanger pipe multi-row four-pass bank, the said pipes being laid in horizontal rows spaced in horizontal and vertical planes, the manifolds feeding and withdrawing the medium being heated, each being connected, via separate tube plates, with heat exchanger pipes, each tube plate being mounted in the aforesaid manifold walls. Note here that the spacing in, at least, one direction, within the band cross section, of a part of the pipes or within their limits, or of, at least, one bank of the pipes out coming from the medium feed manifold, or, at least, in one of the next runs in the same direction does not comply with that of the pipes or a part of them in their bank run right nearby the manifold withdrawing the medium being heated and/or in one of the previous bank runs. In compliance with the proposed invention, the aforesaid heat exchanger unit-modular air heater comprises a carcass, a bottom, and upper and lower casing walls, a diffuser to feed the medium to be cooled and a confuser to feed the aforesaid medium, manifolds feeding and withdrawing the medium to be heated and furnished with tube plates that form, in every row, an even number of rectilinear multi-pipe banks including, at least, two inner and two outer banks integrated by constant-radius bends. Note here that the unit housing bottom, cover and one of the side walls represent panels with a reinforcement framing elements forming a flat rod systems, while the unit carcass is formed by a set of the aforesaid flat rod systems with intermediate posts inter jointing the aforesaid systems and the manifolds housings rigidly fixed thereto and, in their turn, attached to the unit bottom and inter jointed via two-ring diaphragms and a pipe medium displacer. Note that the parts of the aforesaid manifolds housings with the aforesaid tube plates and pipe medium displacer fitted therein form, when combined, the unit housing rigid face wall while the side walls allow fastening the diffuser and confuser elements. Note here also that the spacing in, at least, one direction, within the band cross section, of a part of the pipes or within their limits, or of, at least, one bank of the pipes out coming from the medium feed manifold, or, at least, in one of the next runs in the same direction does not comply with that of the pipes or a part of them in their bank run right nearby the manifold withdrawing the medium being heated and/or in one of the previous bank runs. In compliance with this invention, the aforesaid heat exchanger unit-modular air heater incorporates a multi-row heat exchanger pipe bank made up of, at least, two bundles of two-pass U-pipes forming, within one bundle, two-run horizontal rows of pipes spaced apart both in rows and between rows, manifolds of feeding and withdrawing the medium being heated and, at least one bypass chamber arranged there between. Note here that the aforesaid manifolds and the bypass chamber communicate with the heat exchanger pipes via a common tube plate or separate tube plates, at least, one part of the said plates forming a part of the aforesaid manifolds enclosure walls. Note also here that the spacing in, at least, one direction, within the band cross section, of a part of the pipes or within their limits, or of, at least, one bank of the pipes out coming from the medium feed manifold, or, at least, in one of the next runs in the same direction does not comply with that of the pipes or a part of them in their bank run right nearby the manifold withdrawing the medium being heated and/or in one of the previous bank runs.

EFFECT: higher heat exchange efficiency, lower metal intensity of regenerative air heater.

34 cl, 15 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 tubes with horizontal tube boards, rigidly fastened to each other and the 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 section above e last interacting with its spring supports.

Also known is a regenerative air heater (SU No. 985595, F12L 15/04, 1982), comprising 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, in order to reduce the thermal stresses of the tube 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 is a regenerative air heater (RU No. 31838 U1, F23L 15/04, 08/27/2003), containing heat exchange units having bundles of heat exchange tubes assembled in packages, the ends of which are fastened to the air supply and exhaust manifolds, and a bundle of heat exchange pipes has the shape of a coil and is made single-package, while the fastening elements of the heat-exchange pipes to the collectors are made in the form of separate tube plates, welded directly into the wall of the corresponding collector.

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.

A heat-exchange unit of a regenerative air heater is known, including a four-way multi-row bundle of heat-exchange tubes (RU No. 17600 U1, F23L 15/04, 04/10/2001) formed by horizontal V-shaped tubes with one bend and two straight branches, each row contains two packages of V-shaped tubes 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.

Known bundles of heat transfer tubes of regenerative air heaters (RU 2087825, 08.20.1997), the spacing elements of which are made corrugated, in the cross section having the form of continuous waves. The distance elements can also be made in the form of periodic corrugations having the form of a full wave, while the corrugations can also be gaps in the form of intermediate corrugations of lower height, located at an angle to the direction of the main distance corrugations, which usually coincides with the direction of flow heat exchanging media.

The disadvantages of this analogue is that due to this design of the spacing elements, the overall thermal efficiency of the heat exchange tube bundle is insufficient, which, all other things being equal, leads to an increase in size and an increase in metal consumption.

A close analogue is also a bundle of heat-exchange tubes of a tubular air heater (SU No. 1453122, F23L 15/04, 1989), including heat-exchange tubes fixed in tube sheets, while the intermediate tube sheets are made of corrugated strips and are designed to attach heat-exchange pipes to them in the case of supplying the line to the gaps between the pipes and shells. Wavy strips provide spatial fixation of the heat exchange tubes, while the wavy strips have supporting sections located on both sides of the strips, one on each half wave, strips for supporting contact with the supporting sections of height-adjacent wavy strips and connecting the supporting sections of two inclined sections forming the supporting elements for supporting the beam tubes.

This device has a large metal consumption and insufficiently high heat transfer efficiency due to the fact that the wavy stripes are installed vertically and for the formation of a tube sheet that acts as a spacing element, it is necessary to fasten, for example by welding, the supporting sections between themselves and with heat transfer pipes.

A known collector of a heat exchanger containing inlet and outlet pipes, a package of plates, the end of which together with the covers form the collectors (RU No. 2137076, 09/10/1999).

Known collectors supply - exhaust air regenerative air heater, which is welded into a common tube board (RU No. 17600 U1, 2001, RU No. 2176051, 11/20/2001).

The problem solved by all objects of the invention is to increase the efficiency of heat transfer while ensuring compactness, increasing the strength and rigidity of structures and reducing metal consumption.

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 one or more sections, each of which includes at least two heat exchangers, combined by a diffuser for supply and a confuser to drain the cooled medium, mainly outgoing from a turbine of hot gases, blocks with collectors for supplying and discharging a heated medium, preferably air, each of which is connected by means of tube plates to at least one multi-row bundle of multi-pass heat transfer tubes with the number of bends for different bundle tubes from four to six, forming four straight branches and connecting them three elbows, while at least in one direction in the cross section of the bundle the pitch of at least part of the tubes and / or within a part of the length of the pipes, at least in the beam branch directly extending from the collector for supplying the heated medium, and / or, at least in one of the branches following the heated medium, made mismatched with the pipe pitch and / or parts the length of the pipes in the same direction in the cross section in the beam branch, directly suitable for the collector of the outlet of the heated medium, and / or in at least one of the previous beam branches.

The pitch of the pipes in the row, at least on a part of the width of the beam branch directly extending from the collector of the supply of the heated medium, may exceed the pitch of at least part of the pipes in the row of the branch of the beam directly approaching the collector of the outlet of the heated medium.

The step of the pipes in the row, at least on a part of the width of the beam branch directly extending from the collector for supplying the heated medium, may be less than the step of at least part of the pipes in the row of the branch of the beam directly approaching the collector for removing the heated medium.

The step of at least part of the bundle tubes can be made variable in at least one direction of the cross section of the bundle branch, for example, within the branch of a row of bundle tubes and / or between at least part of the rows of tubes along the height of the bundle.

The internal branches or parts thereof, at least part of the rows of bundle pipes can be made non-parallel to the external branches within the corresponding rows, and the gaps between the branches, at least part of the rows of bundle pipes can be made with a variable width along the length of the branches, for example wedge-shaped tapering and / or wedge-shaped expanding.

The ratio of the unequal steps of adjacent pipes can be taken to be different by at least 5% from the value of the smaller of them.

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 block 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 ], 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 the products of combustion after the turbine of a gas turbine installation were used as a cooled medium.

, при этом внешняя труба этой части рядов, имеющих большее число труб, чем в смежных с ними таких рядах, имеет один гиб длиной πR, образующий колено, соединяющее внутренние ветви этой трубы, общее число гибов этой трубы равно пяти, а внутренняя труба каждого из таких рядов, имеющих большее число труб, чем в смежных с ними таких 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 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)а, [м], при этом количество труб в блоке составляет предпочтительно 263-563 шт.The ratio of the total length ∑l '' of straight branches, at least part of the heat exchange tubes streamlined in the transverse direction, to their total length ∑L [m] in the bundle can be 0.78-0.92, while the outer and inner tubes at least in part of the rows of the beam each may contain at least one bend with a length equal to πR, and the bends of the remaining pipes in these rows of the beam can be made with a length equal to

while the outer pipe of this part 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, the total number of bends of this pipe is five, and the inner pipe of each of such rows, having a larger number of pipes than in adjacent rows, 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 of this pipe is four, step ″ a ″ Between longitudinal axes adjacent pipes of straight branches is (1.5-2.5) d, where d is the outer diameter of the heat transfer 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 In a 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 the step ″ a ″ is equal to the step ″ b ″, and the number of heat-exchanging pipes in adjacent the height of the 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 in the rows of pipes in the bundle k is preferably 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], while the number of pipes in the block is preferably 263-563 pcs.

, может содержать сопряженную с гибами прямолинейную вставку длиной, кратной 2а, где а - 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 2а±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 of the row, or each pipe bend of all rows of the 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 large number of pipes 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 problem in terms of the second object of the group of inventions is solved due to the fact that the heat exchanger block of the heat exchanger — block-sectional air heater according to the invention comprises 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, a supply collector and a collector for removal of the heated medium, each of which is connected to heat exchange pipes by means of separate tube boards mounted directly directly into the wall of the corresponding manifold for supplying or discharging the heated medium, and at least in one direction in the cross section of the beam, the step of at least part of the pipes and / or within part of the length of the pipes, at least in the beam branch, directly outgoing from the collector of supply of the heated medium, and / or, at least in one of the branches following the heated medium, is made at least partially not coinciding with the pitch of at least part of the pipes and / or within part of the length of the pipes at least in the same n directional in cross section, at least in the beam branch, directly approaching the collector of the outlet of the heated medium, and / or at least in one of the previous beam branches.

The pitch of the pipes in the row, at least on a part of the width of the beam branch directly extending from the collector of the supply of the heated medium, may exceed the pitch of at least part of the pipes in the row of the branch of the beam directly approaching the collector of the outlet of the heated medium.

The step of the pipes in the row, at least on a part of the width of the beam branch directly extending from the collector for supplying the heated medium, may be less than the step of at least part of the pipes in the row of the branch of the beam directly approaching the collector for removing the heated medium.

The step of at least part of the bundle tubes can be made variable in at least one direction of the cross section of the bundle branch, for example, within the branch of a row of bundle tubes and / or between at least part of the rows of tubes along the height of the bundle.

The internal branches of at least part of the rows of bundle pipes can be made non-parallel to the external branches within the corresponding rows, and the gaps between the branches of at least part of the rows of bundle pipes can be made with a variable width along the length of the branches, for example, tapered / or wedge-shaped expanding.

The ratio of the unequal steps of adjacent pipes can be taken to be different by at least 5% from the value of the smaller of them.

At least part of the heat exchange tubes, at least part of the rows, can be made with four, five, or six bends of radius R, forming four straight branches and connecting them to three knees, while the bending sections of two pipes in each odd of these rows can have a length πR, namely: one pipe has an inner bend, the other has two external bends, for the remaining pipes of such odd and even rows, the sections of the bend have a length of πR / 2 and are joined in pairs by straight inserts of length H ' _i - for external knees and H '' _i - for the inner elbow, and the number of heat transfer tubes in such 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 such rows of tubes in the bundle k is preferably odd moreover, k> 3, heat-exchange pipes in such 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 the rectilinear branches of adjacent pipes of one row, [m], while the lengths H ' _i and H'' _{i of the} straight inserts of the elbows of the i-th pipe can be performed temporary: for an odd row of heat exchange tubes 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].

[м^-1], 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 pipes in the volume occupied by at least one branch of the beam can be made subject to the conditions, according to the first of which the ratio of the total area is ∑F _n.p.p. 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

[m ^-1], 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.

The number N of heat transfer tubes in the block with an odd number of rows of k tubes in the bundle can be determined by the dependence N = 0.5 (k-1) (2m-1) + m and preferably be 263-563 pcs., Or the number N of heat transfer tubes in block with an even number of rows of k pipes 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 outlet of the heated medium collector is 0.45-0 82 of the total flow area of the beam heat-transfer tubes, moreover, the heat-exchange unit can be equipped with slinging devices and manholes made in the headers and the removal of the heated medium.

The problem regarding the third object in the group of inventions is solved due to the fact that the heat exchanger block of the heat exchanger - block-sectional air heater according to the invention comprises a housing, a diffuser for supply and a confuser for draining the cooled medium, consisting of a spatial frame, bottom, top cover and end walls, collectors for supplying and discharging a heated medium with tube plates and a multi-way multi-row bundle of heat-exchange tubes, forming, in each row, an even number of straight-line multi-tubes, respectively branches, including at least two internal and two external, connected by sections with bends of a radius beam predominantly constant for all pipes, while the bottom, cover and one of the end walls of the block body are made in the form of panels with a binding from stiffeners forming flat rod systems, and the spatial frame of the block is formed by a combination of flat rod systems of the frameworks of these panels with intermediate racks connecting them and rigidly connected to them by the bodies of the supply and exhaust manifolds 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 housings of the manifolds for supplying and discharging the heated medium with tube boards and the displacer of the annular medium mounted in them together form a spatially developed rigid end wall block housing, and on the longitudinal sides of the frame is made with the possibility of mounting, respectively, the elements of the diffuser and confuser for supplying and discharging the cooled medium, while at least in one direction in the cross section of the beam, the step of at least part of the pipes and / or within part of the length of the pipes, at least in the branch of the beam directly extending from the collector for supplying a heated medium, and / or at least , in one of the branches following the heated medium, it is made at least partially not coincident with the pitch of at least part of the pipes and / or within part of the length of the pipes, at least in the same direction in cross section, at least in a branch of the beam that directly approaches to the collector of the outlet of the heated medium, and / or, at least, in one of the previous branches of the beam.

The pitch of the pipes in the row, at least on a part of the width of the beam branch directly extending from the collector of the supply of the heated medium, may exceed the pitch of at least part of the pipes in the row of the branch of the beam directly approaching the collector of the outlet of the heated medium.

The step of the pipes in the row, at least on a part of the width of the beam branch directly extending from the collector for supplying the heated medium, may be less than the step of at least part of the pipes in the row of the branch of the beam directly approaching the collector for removing the heated medium.

The step of at least part of the bundle tubes can be made variable in at least one direction of the cross section of the bundle branch, for example, within the branch of a row of bundle tubes and / or between at least part of the rows of tubes along the height of the bundle.

The internal branches, or at least parts of them, at least part of the rows of bundle pipes can be made non-parallel to the external branches within the corresponding rows, and the gaps between the branches, at least part of the rows of bundle pipes can be made with a variable width the length of the branches, for example wedge-shaped tapering and / or wedge-shaped expanding.

The ratio of the unequal steps of adjacent pipes can be taken to be different by at least 5% from the value of the smaller of them.

The annular displacer can be 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 inlet and outlet manifolds of the heated medium so that its inner surface is located in the same plane with the outer plane of the tube plates, while the heat exchange unit can be equipped with fixed to the bottom and frame of the housing with distance elements for heat transfer tubes of the outer branches of the beam in the form of distance gratings, said heat exchange tubes being passed through the openings of the distance gratings, and subsequent rows of heat transfer tubes in the area of internal branches can be separated by fold-in distance strips that are attached to racks mounted on the bottom, and in addition, combs for at least the inner branches of the lower row of heat transfer tubes can be fixed to the bottom of the housing.

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 are pivotally mounted on the bodies of the headers for supplying and discharging the heated medium with the possibility of rotation in a plane perpendicular to the longitudinal axis of symmetry of the headers for supplying and discharging the heated medium dy, and on the inner walls of the collectors for supplying and discharging the heated medium, supports are installed that form a ladder for inspection and maintenance of the collectors for supplying and discharging the heated medium and tube plates.

The heat exchanger block of the heat exchanger can be equipped with means for attaching a diffuser for supplying and a confuser for draining 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 task in part of the fourth object of the group of inventions is solved due to the fact that the heat exchanger block of the heat exchanger - block-sectional air heater according to the invention 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, 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, p at least one bypass chamber, wherein 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 form part of the wall of the supply and collector manifold walls the removal of the heated medium and the bypass chamber, and at least in one direction in the cross section of the beam step, at least part of the pipe and / or within part of the length of the pipe, at least the beam of the beam directly departing from the manifold for supplying the heated medium and / or the bypass chamber, and / or, at least in one of the branches following the heated medium, is made at least partially not coinciding with the step of at least part pipes and / or within a part of the length of the pipes, at least in the same direction in the cross section, at least in the beam branch, directly approaching the collector of the outlet of the heated medium and / or the bypass chamber, and / or at least , in one of the previous beam branches.

The step of the pipes in the row, at least on the part of the width of the beam branch directly extending from the collector for supplying the heated medium and / or from the bypass chamber, may exceed the step of at least part of the pipes in the row of the branch of the beam directly approaching the collector of the heated outlet medium and / or to the bypass chamber.

The step of the pipes in the row, at least on the part of the width of the beam branch, directly departing from the collector for supplying the heated medium and / or from the bypass chamber, may be less than the step of at least part of the pipes in the row of the branch of the beam directly approaching the outlet collector heated medium and / or to the bypass chamber.

The step of at least part of the bundle tubes can be made variable in at least one direction of the cross section of the bundle branch, for example, within the branch of a row of bundle tubes and / or between at least part of the rows of tubes along the height of the bundle.

The ratio of the unequal steps of adjacent pipes can be taken to be different by at least 5% from the value of the smaller of them.

The technical result provided by all objects of the invention is to increase the heat transfer efficiency due to the optimal arrangement of pipes in the bundle developed in the invention, providing uniform heat transfer, while reducing the metal consumption of the regenerative air heater and its structural elements by reducing the size and metal consumption of the lattice elements for heat exchange pipes.

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;

on Fig - an embodiment of a heat exchange unit with a bypass chamber, in plan.

A heat exchanger - a block-sectional air heater contains one or more sections 1, each of which includes at least two heat exchangers, combined by a diffuser 2 for supply and a confuser 3 for removal of the cooled medium, mainly hot gases leaving the turbine, blocks 4 with supply headers 5 and exhaust 6 of the heated medium, preferably air, each of which is connected by means of tube plates 7 with at least one multi-row bundle 8 of multi-pass heat transfer tubes 9 with the number of bends 10, 11 for different pipes b 9 of bundle 8 from four to six, forming four straight branches 12, 13 and three knees 14, 15, 16 connecting them. At least in one direction in the cross section of bundle 8, step of at least part of pipes 9 and / or within part of the length of the pipes 9, at least in the branch of the beam 8, directly extending from the collector for supplying 5 heated medium, and / or, at least in one of the branches following the heated medium, made non-coincident with the pipe pitch 9 and / or part of the length of the pipes 9 in the same direction in cross section in the branch of the bundle 8, suitable for the heated medium outlet manifold 6 and / or in at least one of the previous branches 13 of the beam 8.

The step of the pipes 9 in the row, at least on a part of the width of the branch of the beam 8, directly extending from the collector of the supply 5 of the heated medium, exceeds the step of at least the part of the pipes 9 in the row of the branch of the beam 8, directly approaching the collector of the outlet 6 of the heated medium .

The pitch of the pipes 9 in the row, at least on the part of the width of the branch of the beam 8, directly extending from the collector of the supply 5 of the heated medium, is less than the step of at least the part of the pipes 9 in the row of the branch of the beam 8, directly matching the collector of the outlet 6 of the heated medium .

At least the pitch of the part of the pipes 9 of the bundle 8 is made variable in at least one cross-sectional direction of the branch 12 of the bundle 8, for example, within the branch 12 of the row of pipes 9 of the bundle 8 and / or between at least part of the rows of pipes 9 along the height of the beam 8.

The internal branches 12 or their parts, at least part of the rows of pipes 9 of the bundle 8 are made non-parallel to the external branches 13 within the corresponding rows, and the gaps between the branches 12, 13 of at least part of the rows of pipes 9 of the bundle 8 are made with a variable width along the length of the branches, for example wedge-shaped tapering and / or wedge-shaped expanding.

The ratio of the unequal steps of adjacent pipes 9 is accepted to differ by at least 5% from the value of the smaller of them.

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

составляющим 0,08÷0,32 [м^-1].The number and distribution of pipes 9 in the bundle 8 are taken in compliance with the conditions under which the volume ratio V _t. [m ³ ] occupied by heat exchange tubes 9 in the block and equal to the total volume of straight branches 12, 13 and elbows 14, 15 of tube 9 of bundle 8, defined along the outer contour with conditional planes touching the outer surfaces of the extreme heat exchange tubes 9, minus the volume of the annular medium between the branches 12, 13 and the elbows 14, 15 of the pipes 9 of the bundle 8, to the total internal volume of the heat exchange unit 4 V _ext. [m ³ ], limited by the bottom, top cover and end walls of the block casing, is 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 9 is determined by the coefficient

components of 0.08 ÷ 0.32 [m ^-1 ].

In each of its sections 1, the heat exchange blocks 4 are located one above the other, and the preferred number of blocks 4 is four. The inlet manifold 5 and the outlet manifold 6 of the heated medium are adapted to be connected to the inlet and outlet pipelines of the heated medium, which preferably uses air, including oxygen enriched, while the products of combustion after the turbine of a gas turbine are used as a cooled medium.

. Внешняя труба 17 этой части рядов, имеющих большее число труб 9, чем в смежных с ними таких рядах, имеет один гиб 10 длиной πR, образующий колено 16, соединяющее внутренние ветви этой трубы 17, общее число гибов 10 этой трубы 17 равно пяти, а внутренняя труба 18 каждого из таких рядов, имеющих большее число труб 9, чем в смежных с ними таких рядах, имеет два гиба 11 длиной πR, каждый из которых образует колено 14, 16, соединяющее соответствующие внутреннюю 12 и внешнюю 13 ветви этой трубы 18, а общее число гибов 11 у этой трубы 18 равно четырем, шаг ″а″ между продольными осями смежных труб 9 прямолинейных ветвей 12, 13 составляет (1,5-2,5)d, где d - наружный диаметр теплообменной трубы 9, шаг ″b″ между осями смежных труб 9 на прямолинейных участках колен 14, 15, 16 составляет (1,8-2,8)d. В каждом ряду шаг ″а″ между продольными осями смежных труб 9 прямолинейных ветвей меньше или больше, чем шаг ″b″ между продольными осями колен 14, 15, 16 смежных труб 9, предпочтительно а<b, или шаг ″а″ равен шагу ″b″, и количество теплообменных труб 9 в смежных по высоте рядах пучка 8 для нечетных и четных рядов составляет соответственно m и n, где m - четное число, а n=(m-1), количество рядов труб 9 в пучке 8 k - предпочтительно нечетное, причем k>3, теплообменные трубы 9 в смежных по высоте рядах размещены в шахматном порядке со смещением на (0,4÷0,6)a, [м], при этом количество труб 9 в блоке составляет предпочтительно 263-563 шт.The ratio of the total length ∑l '' of straight branches, at least part of the heat exchange tubes 9, streamlined in the transverse direction, to their total length ∑L [m] in the beam 8 is 0.78-0.92. The outer 17 and inner 18 pipes, at least in part of the rows of the bundle 8 each contain at least one bend 10, 11 of a length equal to πR, and bends 10, 11 of the remaining pipes 9 in these rows of the bundle 8 are made with a length equal to

. The outer pipe 17 of this part of the rows, having a larger number of pipes 9 than in adjacent rows, has one bend 10 of length πR, forming a bend 16 connecting the internal branches of this pipe 17, the total number of bends 10 of this pipe 17 is five, and the inner pipe 18 of each of these rows, having a larger number of pipes 9 than in adjacent rows, has two bends 11 of length πR, each of which forms an elbow 14, 16 connecting the corresponding internal 12 and external 13 branches of this pipe 18, and the total number of bends 11 of this pipe 18 is four, the step ″ a ″ between the longitudinal the axes of adjacent pipes 9 of straight branches 12, 13 is (1.5-2.5) d, where d is the outer diameter of the heat exchange pipe 9, the step ″ b ″ between the axes of adjacent pipes 9 on the straight sections of the elbows 14, 15, 16 is (1.8-2.8) d. In each row, the step ″ a ″ between the longitudinal axes of adjacent pipes 9 of straight branches is smaller or larger than the step ″ b ″ between the longitudinal axes of elbows 14, 15, 16 of adjacent pipes 9, preferably a <b, or step ″ a ″ is equal to step ″ b ″, and the number of heat transfer pipes 9 in the rows of the beam 8 adjacent to the height 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 9 in the beam 8 k is preferably odd, and k> 3, the heat transfer tubes 9 in rows adjacent in height are staggered with an offset of (0.4 ÷ 0.6) a, [m], at the number of pipes 9 in the block is preferably 263-563 pcs.

, содержит сопряженную с гибами 10, 11 прямолинейную вставку 19 длиной, кратной 2а, где а - шаг между осями одноименных прямолинейных ветвей 12, 13 смежных труб 9 ряда, или каждое колено 14, 15, 16 труб 9 всех рядов пучка 8, образованное двумя гибами 10, 11 длиной каждый, равной

, содержит сопряженную с гибами 10, 11 прямолинейную вставку 19 длиной, изменяющейся у разных труб 9 ряда 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 elbow 14, 15, 16 pipes 9 of all rows of the bundle 8, formed by two bends 10, 11 each equal in length

contains a rectilinear insert 19 conjugated with bends 10, 11 and a multiple of 2a, where a is the step between the axes of the same straight branches 12, 13 of adjacent pipes of the 9th row, or each elbow 14, 15, 16 of pipes 9 of all rows of the bundle 8, formed by two bends 10, 11 each equal in length

contains a rectilinear insert 19 associated with bends 10, 11, with a length varying in different pipes of the 9th row from a value equal to 2a ± 10% [m] to a value equal to 2a (m-1) ± 10% [m] for rows with large by the number of pipes 9, than in rows adjacent to them in height, and for the remaining rows to a value equal to a (2n-1) ± 10% [m], where

a - step between the axes of the same straight branches 12, 13 of adjacent pipes of the 9th row, [m],

m is the number of pipes 9 in a row with a large number of pipes 9, mainly an even number of pipes 9 in odd rows,

n is the number of pipes 9 in a row with a smaller number of pipes 9, mainly an odd number of pipes 9 in even rows.

The heat exchange unit according to the second embodiment contains four branches of a four-way multi-row bundle 8 of heat exchange tubes 9 stacked in horizontal rows and spaced horizontally and vertically from each other, a supply manifold 5 and a collector for exhaust 6 of the heated medium, each of which is connected to the heat exchange tubes 9 by means of individual tube plates 7 mounted directly into the wall of the corresponding collector of the supply 5 or exhaust 6 of the heated medium, and at least in one alignment in the cross section of the beam 8, the step of at least part of the pipes 9 and / or within part of the length of the pipes 9, at least in the branch of the beam 8, directly extending from the collector for supplying 5 heated medium, and / or at least , in one of the branches 12, 13 subsequent along the heated medium, is made at least partially not coinciding with the pitch of at least part of the pipes 9 and / or within part of the length of the pipes 9, at least in the same direction in cross section, at least in the branch of the beam 8, directly approaching the collector from water 6 of the heated medium, and / or, at least in one of the previous branches of the beam 8.

The step of the pipes 9 in the row, at least on a part of the width of the branch of the beam 8, directly extending from the collector of the supply 5 of the heated medium, exceeds the step of at least the part of the pipes 9 in the row of the branch of the beam 8, directly approaching the collector of the outlet 6 of the heated medium .

The pitch of the pipes 9 in the row, at least on the part of the width of the branch of the beam 8, directly extending from the collector of the supply 5 of the heated medium, is less than the step of at least the part of the pipes 9 in the row of the branch of the beam 8, directly matching the collector of the outlet 6 of the heated medium .

The step of at least part of the pipes 9 of the bundle 8 is made variable in at least one cross-sectional direction of the branch of the bundle 8, for example, within the branches of a series of pipes 9 of the bundle 8 and / or between at least part of the rows of pipes 9 beam height 8.

The inner branches 12, at least part of the rows of pipes 9 of the beam 8 are made non-parallel to the external branches 13 within the corresponding rows, and the gaps between the branches 13, at least part of the rows of pipes 9 of the beam 8 are made with a variable width along the length of the branches 13, for example, tapered tapered and / or tapered expanded.

The ratio of the unequal steps of adjacent pipes 9 is accepted to differ by at least 5% from the value of the smaller of them.

At least a part of the heat transfer tubes 9, at least part of the rows, are made with four, five, or six bends 10, 11 of radius R, forming four straight branches 12, 13 and three knees 14, 15, 16. connecting them for two pipes, 9 in each odd of these rows have a length πR, namely: for one pipe 9, on the inner elbow 15, the other on two external elbows 14, 16, for the remaining pipes 9 of such odd and even rows, the bend sections have πR / 2 length and articulated in pairs by means of rectilinear inserts 19 of length H ' _i for the outer elbows 14, 16 and H'' _i - for the inner bend 15, and the number of heat transfer tubes 9 in adjacent rows of such a 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 such rows of pipes 9 in a beam 8 k is preferably odd, and k> 3, the heat transfer pipes 9 in adjacent rows of such 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 rectilinear branches 12, 13 of adjacent tubes 9 of one row, [m], and the length N _'i and H'_'i rectilinear knee inserts 19 i-th tube 9 are change by: for an odd row of heat exchange tubes 8 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 9 ветви пучка 8 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 of the beam 8 is taken subject to the conditions, according to the first of which the ratio of the total area ∑F _ntp the outer heat-exchange surface of the pipes 9 of this branch of the beam 8 to the volume ∑V _m.c. occupied by the annular medium in the area of active heat transfer of the beam branch 8 and equal to the volume of the beam branch 8 along the external contour defined by the conditional planes touching the outer surfaces of the extreme heat exchange tubes 9 of the beam branch 8, minus the volume occupied by the heat exchange tubes 9 in this beam branch 8 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 a heated medium in pipes 9 of a beam branch 8 to a volume of V _m.s. determined by the coefficient

constituting 0.78-1.25.

The number N of heat transfer tubes 9 in the block with an odd number of rows of k pipes 9 in the bundle 8 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 9 in a block with an even number of rows of k pipes 9 in a bundle 8 is determined by the dependence N = 0.5k (2m-1) and is preferably 263-563 pcs.

Between the collectors of the inlet 5 and the outlet 6 of the heated medium is fixed displacer 20 annular medium, made in the form of a profiled panel with a flat section 21 located between the collectors of the inlet 5 or 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, and the heat exchange unit is equipped with sling devices 22 and manholes made in the inlet 5 and exhaust manifolds 6 heated medium.

The heat exchange unit according to the third embodiment comprises a housing 27, a bottom 24, a top cover 25 and end walls 26, a housing 27, a diffuser 2 for supply and a confuser 3 for removal of the cooled medium, collectors for supply 5 and removal 6 of the heated medium with tube boards 7 and a multi-way multi-row bundle 8 of heat-exchange tubes 9, forming, respectively, in each row, an even number of straight multi-tube branches 12, 13, including at least two internal 12 and two external 13, connected by sections with bends 10, 11 predominantly of a radius 8 beam that is substantially constant for all pipes 9, with the bottom 24, the cover 25, and one of the end walls 26 of the block body 27 made in the form of panels with strapping elements of stiffness forming flat rod systems 28, and the spatial frame 23 of the block is formed by a set of flat the core systems 28 of the frameworks of these panels with the intermediate racks 29 connecting them and the collector bodies of the supply 5 and the outlet 6 of the heated medium rigidly connected to them, which, in turn, are connected to the bottom 24 of the unit and to each other a two-ring diaphragms and displacer 20 of the annular medium, and parts of the housings of the inlet 5 and outlet 6 of the heated medium with tube boards 7 mounted in them and the annular displacer 20 together form a spatially developed rigid end wall 26 of the block housing 27, and along the longitudinal sides of the frame 23 made with the possibility of mounting respectively the elements of the diffuser 2 and confuser 3 for supplying and discharging the cooled medium, while at least in one direction in the cross section of the beam 8 step, at least heres, parts of pipes 9 and / or within part of the length of pipes 9, at least in the branch of the beam 8, directly extending from the collector for supplying 5 heated medium, and / or at least in one of the branches following the heated medium made at least partially not coincident with the pitch of at least part of the pipes 9 and / or within part of the length of the pipes 9, at least in the same direction in cross section, at least in the branch of the beam 8, directly suitable for the outlet manifold 6 of the heated medium, and / or in at least one of previous branches of the bundle 8.

The step of the pipes 9 in the row, at least on a part of the width of the branch of the beam 8, directly extending from the collector of the supply 5 of the heated medium, exceeds the step of at least the part of the pipes 9 in the row of the branch of the beam 8, directly approaching the collector of the outlet 6 of the heated medium .

The pitch of the pipes 9 in the row, at least on the part of the width of the branch of the beam 8, directly extending from the collector of the supply 5 of the heated medium, is less than the step of at least the part of the pipes 9 in the row of the branch of the beam 8, directly matching the collector of the outlet 6 of the heated medium .

The step of at least part of the pipes 9 of the bundle 8 is made variable in at least one cross-sectional direction of the branch of the bundle 8, for example, within the branches of a series of pipes 9 of the bundle and / or between at least part of the rows of pipes 9 along beam height 8.

The internal branches 12, or at least part of them, at least part of the rows of pipes 9 of the beam 8 are made non-parallel to the external branches 13 within the corresponding rows, and the gaps between the branches 12, 13, at least part of the rows of pipes 9 of the beam 8 are made with a variable width along the length of the branches 12, 13, for example, wedge-shaped tapering and / or wedge-shaped expanding.

The ratio of the unequal steps of adjacent pipes 9 is accepted to differ by at least 5% from the value of the smaller of them.

The displacer 20 of the annular medium is made in the form of a profiled panel with a flat section 21, 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 collectors of the inlet 5 and outlet 6 of the heated medium so that its inner surface is located in the same plane with the outer plane of the tube plates 7. The heat exchange unit is provided with a spacer mounted on the bottom 24 and frame 23 of the housing 27 of the unit elements 30 for heat exchange tubes 9 of the outer branches 13 of the beam 8 in the form of spacing grids, said heat exchanging tubes 9 being passed through the openings of the spacing grids, and the subsequent rows of heat exchanging tubes 9 in the area of the inner branches 12 are separated by folding spacers 31 that are attached to the uprights 19 mounted on the bottom 24, and in addition, combs 32 are fixed on the bottom 24 of the housing 27 for at least the inner branches 12 of the lower row of heat transfer tubes 9.

The cross-sectional area of each of the collectors of the inlet 5 and outlet 6 of the heated medium is 1.8-3.5 of the total flow area of the heat-transfer pipes 9 in the block. The manifolds for supplying 5 and outlet 6 of the heated medium are made with manholes located on the bottom side of the block 24, while the covers 33 for manholes are pivotally mounted on the bodies of the manifolds for supplying 5 and outlet 6 of the heated medium with the possibility of rotation in a plane perpendicular to the longitudinal axis of symmetry collectors for supply 5 and exhaust 6 of the heated medium, and supports are installed on the inner walls of collectors for supply 5 and exhaust 6 of the heated medium, forming a ladder for inspection and maintenance of collectors for supply 5 and exhaust 6 heated medium and tube sheets 7.

The heat exchange unit is equipped with means for attaching a diffuser 2 for supply and a confuser 3 for draining the cooled medium, mounted on the opposite side elements of the spatial frame 23 of the unit, as well as brackets for attaching external thermal insulation.

The heat exchange unit according to the fourth embodiment comprises a multi-row bundle 8 of heat exchange pipes 9, consisting of at least two packages of two-way U-shaped pipes 34, 35, forming two-branch pipes, for example, horizontal rows of pipes 34, 35, spaced within each package 36 within the row and between the 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 37, and the collector of the supply 5 and the collector of the outlet 6 of the heated medium, as well as bypass The chamber chamber 37 is connected to heat exchange tubes 9 by a common tube board 7 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 37, at least at least in one direction in the cross section of the beam 8, the step of at least part of the pipes 9 and / or within the part of the length of the pipes 9, at least in the branch of the beam 8, directly extending from the collector for supplying 5 heated medium and / or bypass cameras s 37, and / or, at least in one of the branches following the heated medium, is made at least partially not coinciding with the pitch of at least part of the pipes 9 and / or within part of the length of the pipes 9, at least in the same direction in the cross section, at least in the branch of the beam 8, directly approaching the collector of the outlet 5 of the heated medium and / or the bypass chamber 37, and / or in at least one of the previous branches of the beam 8 .

The step of the pipes 9 in the row, at least on a part of the width of the branch of the beam 8, directly extending from the collector for supplying 5 heated medium and / or from the bypass chamber 37, exceeds the step of at least part of the pipes 9 in the row of the branch of the beam 8, directly suitable to the collector of the outlet 6 of the heated medium and / or to the bypass chamber 37.

The step of the pipes 9 in the row, at least on a part of the width of the branch of the beam 8, directly extending from the collector for supplying 5 heated medium and / or from the bypass chamber 37, is less than the step of at least part of the pipes 9 in the row of the branch of the beam 8, directly suitable to the collector of the outlet 6 of the heated medium and / or to the bypass chamber 37.

The step of at least part of the pipes 9 of the bundle 8 is made variable in at least one cross-sectional direction of the branch of the bundle 8, for example, within the branches of a series of pipes 9 of the bundle 8 and / or between at least part of the rows of pipes 9 beam height 8.

The ratio of the unequal steps of adjacent pipes 9 is accepted to differ by at least 5% from the value of the smaller of them.

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 (34)

1. A heat exchanger is a block-sectional air heater, characterized in that it contains one or more sections, each of which includes at least two heat exchangers, combined with a diffuser for supply and a confuser for the removal of the cooled medium, mainly hot gases leaving the turbine, blocks with collectors for supplying and discharging a heated medium, preferably air, each of which is connected by means of tube plates to at least one multi-row bundle of multi-pass heat transfer tubes with the number m bends for different tubes of the bundle from four to six, forming four straight branches and connecting them three knees, while at least in one direction in the cross section of the bundle step, at least part of the pipe and / or within part of the length pipes, at least in the branch of the beam directly extending from the manifold for supplying the heated medium and / or at least in one of the branches following the heated medium, is made not coincident with the pipe pitch and / or part of the pipe length in the same direction in cross section in the beam branch Directly to the collector of a suitable heated medium outlet and / or at least one of the preceding beam branches. 2. The heat exchanger according to claim 1, characterized in that the step of the pipes in the row, at least part of the width of the branch of the beam directly extending from the collector for supplying the heated medium, exceeds the step of at least part of the pipes in the row of the branch of the beam, directly suitable for the collector of the outlet of the heated medium. 3. The heat exchanger according to claim 1, characterized in that the step of the pipes in the row, at least on the part of the width of the branch of the beam directly extending from the collector for supplying the heated medium, is less than the step of at least part of the pipes in the row of the branch of the beam, directly suitable for the collector of the outlet of the heated medium. 4. The heat exchanger according to claim 1, characterized in that the step of at least a portion of the bundle tubes is made variable in at least one direction of the cross section of the bundle branch, for example, within a branch of a row of bundle tubes and / or between, at least part of the rows of pipes along the height of the beam. 5. The heat exchanger according to claim 1, characterized in that the internal branches or parts thereof, at least part of the rows of bundle pipes are made non-parallel to the external branches within the corresponding rows, and the gaps between the branches, at least part of the bundle rows of pipes with a variable width along the length of the branches, for example, wedge-shaped tapering and / or wedge-shaped expanding. 6. The heat exchanger according to claim 1, characterized in that the ratio of unequal steps of adjacent pipes is accepted to be different by at least 5% from the value of the smaller of them. 7. The heat exchanger according to claim 1, characterized in that the number and distribution of pipes in the bundle are adopted subject to a condition under which 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 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 ], 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 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 ]. 8. 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 as 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. 9. The heat exchanger according to claim 1, characterized in that the ratio of the total length Σl "of straight branches, at least part of the heat exchange pipes streamlined in the transverse direction, to their total length ΣL [m] in the beam is 0.78-0 , 92, while the outer and inner pipes, at least in part of the rows of the bundle, each contain at least one bend of length equal to πR, and the bends of the remaining pipes in these rows of the bundle are made of length equal to

the outer pipe of this part 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, the total number of bends of this pipe is five, and the inner pipe of each of these rows having a larger number of pipes than in adjacent rows 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 of this pipe is four, step ″ a ″ between the longitudinal axes of adjacent tr ub of rectilinear branches is (1.5-2.5) d, where d is the outer diameter of the heat transfer pipe, the step ″ b ″ between the axes of adjacent pipes in the straight sections of the elbows is (1.8-2, S) d, and in each In a 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 the step ″ a ″ is equal to the step ″ b ″, and the number of heat-exchanging pipes in adjacent the height of the 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 pipe poisons in the bundle k is preferably odd, with k> 3, the heat exchange pipes in rows adjacent in height are staggered with an offset of (0.4-0.6) a [m], while the number of pipes in the block is preferably 263 -563 pcs. 10. The heat exchanger according to claim 9, 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 with 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, the length varying for different pipes of the row from a value equal to 1a ± 10% [m] to a value equal to 1a (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 (2m-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. 11. The heat exchanger block of the heat exchanger - block-sectional air heater, characterized in that it contains four branches of a four-way multi-row bundle of heat exchanger tubes arranged in horizontal rows and spaced horizontally and vertically from each other, a supply manifold and a collector for removal 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 heated medium, and at least in one direction in the cross section of the beam, the step of at least part of the pipes and / or within part of the length of the pipes, at least in the branch of the beam directly extending from the manifold supply of the heated medium, and / or, at least in one of the branches following the heated medium, made at least partially not coinciding with the pitch of at least part of the pipes and / or within part of the length of the pipes, at least the same direction in the cross section, at least in the beam branch, n mediocre suitable outlet to a collector of the heated medium and / or at least one of the preceding beam branches. 12. The heat exchange unit of the heat exchanger according to claim 11, characterized in that the step of the pipes in the row, at least part of the width of the beam branch directly extending from the collector for supplying the heated medium, exceeds the step of at least part of the pipes in the row of branches beam, directly suitable for the collector of the outlet of the heated medium. 13. The heat exchange unit of the heat exchanger according to claim 11, characterized in that the step of the pipes in the row, at least on the part of the width of the beam branch directly extending from the collector for supplying the heated medium, is less than the step of at least part of the pipes in the row of the branch beam, directly suitable for the collector of the outlet of the heated medium. 14. The heat exchange unit of the heat exchanger according to claim 11, characterized in that the step of at least part of the bundle tubes is made variable in at least one direction of the cross section of the bundle branch, for example, within the branch of a row of bundle tubes and / or between at least part of the rows of pipes along the height of the beam. 15. The heat exchange unit of the heat exchanger according to claim 11, characterized in that the internal branches of at least part of the rows of bundle tubes are made parallel to the outer branches within the respective rows, and the gaps between the branches of at least part of the rows of bundle tubes this variable width along the length of the branches, for example, wedge-shaped tapering and / or wedge-shaped expanding. 16. The heat exchange unit of the heat exchanger according to claim 11, characterized in that the ratio of unequal steps of adjacent pipes is accepted to be different by at least 5% from the value of the smaller of them. 17. The heat exchange unit of the heat exchanger according to claim 11, characterized in that at least part of the heat exchange pipes, at least part of the rows are made with four, or five, or six bends of radius R, forming four straight branches and connecting them three bends, while the bend sections of two pipes in each odd of these rows have a length πR, namely, one pipe has an inner bend and the other has two external bends; for the remaining pipes of such odd and even rows, the bend sections have a length πR / 1 and articulated in pairs by rectilinear inserts of length H ' _i for the outer elbows and H " _i for the inner elbow, and the number of heat transfer tubes in such adjacent rows of the bundle for odd and even rows is m and n, respectively, where m is an even number and n = (m -1), the number of such rows of pipes in the bundle k is preferably odd, and k> 3, the heat transfer pipes in adjacent rows of such heights are placed in a checkerboard pattern with an offset of (0.4-0.6) a [m], where and - the step between the longitudinal axes of the rectilinear branches of adjacent pipes of the same row, [m], while the lengths H ' _i and H " _{i are} straight The elbow of the i-th pipe bends are made by variables: for an odd number of heat-exchange 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 (1n-1) ± 10% [m]. 18. The heat exchange unit according to claim 17, 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 heat exchange surface of the pipes of this beam branch to the volume ΣV _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

84,5-460 components [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. 19. The heat exchange unit of the heat exchanger according to claim 17, characterized in that the number N of heat exchange tubes in the block with an odd number of rows of k tubes 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 exchange tubes in the block with an even number of rows k of pipes in the bundle is determined by the dependence N = 0.5k (2m-1) and is preferably 263-563 pcs. 20. The heat exchange unit of the heat exchanger according to claim 11, characterized in that between the collectors of the inlet and outlet 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 inlet or outlet of the heated medium, while the passage area the inlet collector or the collector of the outlet of the heated medium is 0.45-0.82 of the total flow area of the beam heat exchange tubes, and the heat exchange unit is equipped with slings and hatches and-lazami made in the reservoirs supply and discharge of heated medium. 21. The heat exchanger block of the heat exchanger is a block-sectional air heater, characterized in that it comprises a housing, a housing, a bottom, an upper cover and end walls, a diffuser for supplying and a confuser for draining the cooled medium, collectors for supplying and discharging the heated medium with pipe planks and a multi-way multi-row bundle of heat-exchange tubes, forming respectively in each row an even number of straight-line multi-tube branches, including at least two internal and two external x, united by sections with bends of a radius beam predominantly constant for all pipes, the bottom, the cover, and one of the end walls of the block body made in the form of panels with strapping elements of stiffness forming flat rod systems, and the spatial frame of the block is formed by a combination of flat rod systems frameworks of said panels with intermediate racks uniting them and rigidly connected bodies of collectors for supplying and discharging a heated medium, which, in turn, are connected to the bottom of the block and between each other with double-ring diaphragms and a displacer of the annular medium, and parts of the bodies of the collectors for supplying and discharging 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 the longitudinal sides the frame is made with the possibility of mounting, respectively, elements of a diffuser and a confuser for supplying and discharging a cooled medium, in this case, at least in one direction in the cross section of the beam, a step at least part of the pipes and / or within part of the length of the pipes, at least in the beam branch, directly extending from the collector for supplying the heated medium, and / or, at least in one of the branches following the heated medium, at least partially inconsistent with the pitch of at least part of the pipes and / or within part of the length of the pipes, at least in the same direction in the cross section, at least in the beam branch, directly approaching the collector of the heated outlet environment and / or at least in one of p previous beam branches. 22. The heat exchange unit of the heat exchanger according to item 21, wherein the step of the pipes in the row, at least part of the width of the branch of the beam directly extending from the collector for supplying the heated medium, exceeds the step of at least part of the pipes in the row of branches beam, directly suitable for the collector of the outlet of the heated medium. 23. The heat exchange unit of the heat exchanger according to item 21, characterized in that the step of the pipes in the row, at least part of the width of the branch of the beam directly extending from the collector for supplying a heated medium, is less than the step of at least part of the pipes in the row of branches beam, directly suitable for the collector of the outlet of the heated medium. 24. The heat exchange unit of the heat exchanger according to item 21, wherein the step of at least part of the bundle tubes is made variable in at least one direction of the cross section of the bundle branch, for example, within a branch of a row of bundle tubes and / or between at least part of the rows of pipes along the height of the beam. 25. The heat exchange unit of the heat exchanger according to item 21, characterized in that the internal branches or at least parts thereof, at least part of the rows of bundle pipes are made non-parallel to the external branches within the respective rows, and the gaps between the branches, at least at least, parts of the rows of bundle tubes are made of variable width along the length of the branches, for example, wedge-shaped tapering and / or wedge-shaped expanding. 26. The heat exchange unit of the heat exchanger according to claim 21, characterized in that the ratio of unequal steps of adjacent pipes is accepted to be different by at least 5% from the value of the smaller of them. 27. The heat exchange unit of the heat exchanger according to item 21, characterized in that the displacer 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 of the heated medium in the same plane with the outer plane of the tube plates or in the form of a flat a panel welded to the walls of the manifolds 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 to is equipped with spacing elements fixed to the bottom and frame of the block body for heat exchange tubes of the outer beam branches in the form of spacing grids, said heat exchanging tubes being passed through the openings of the spacing grids, and subsequent rows of heat exchanging tubes in the area of the inner branches are separated by folded spacing bars that are attached to racks mounted on the bottom, and in addition, combs are fixed on the bottom of the housing for at least the internal branches of the lower row of heat transfer pipes Ub 28. The heat exchange unit of the heat exchanger according to item 21, wherein the cross-sectional area of each of the inlet and outlet collectors of the heated medium is 1.8-3.5 of the total passage area of the heat-exchange pipes in the block, while the inlet and outlet collectors of the heated medium are made with hatches-manholes located on the side of the bottom of the unit, while the covers of manholes-manholes are pivotally mounted on the bodies of the collectors for supplying and discharging the heated medium with the possibility of rotation in a plane perpendicular to the longitudinal symmetry of the manifolds for supplying and discharging the heated medium, and supports are installed on the inner walls of the manifolds for supplying and discharging the heated medium, forming a ladder for inspection and maintenance of collectors for supplying and discharging the heated medium and tube plates. 29. The heat exchange unit of the heat exchanger according to item 21, characterized in that it is equipped with means for attaching a diffuser for supplying and a confuser for draining 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. 30. 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, 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 plate 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 chamber, and at least in at least one direction in the cross section of the beam, the pitch of at least a portion of the pipes and / or within a portion of the length of the pipes, at least in a branch of the beam directly extending from the heating supply manifold the medium, and / or the bypass chamber, and / or, at least in one of the branches following along the medium to be heated, made at least partially not coinciding with the pitch of at least part of the pipes and / or within part of the length of the pipes, at least in the same direction in the cross section, at least in the beam branch, directly suitable for the collector of the outlet of the heated medium and / or the bypass chamber, and / or in at least one of the previous branches beam. 31. The heat exchange unit of the heat exchanger according to claim 30, characterized in that the step of the pipes in the row, at least on a part of the width of the beam branch directly extending from the collector for supplying the heated medium and / or from the bypass chamber, exceeds a step of at least , parts of the pipes in a row of the beam branch, directly suitable to the collector of the outlet of the heated medium and / or to the bypass chamber. 32. The heat exchanger block of the heat exchanger according to claim 30, characterized in that the pipe pitch in the row, at least in part of the width of the beam branch, directly extending from the manifold for supplying the heated medium and / or from the bypass chamber, is less than the step, at least , parts of the pipes in a row of the beam branch, directly suitable to the collector of the outlet of the heated medium and / or to the bypass chamber. 33. The heat exchange unit of the heat exchanger according to claim 30, wherein the step of at least a portion of the bundle tubes is made variable in at least one direction of the cross section of the bundle branch, for example, within a branch of a row of bundle tubes and / or between at least part of the rows of pipes along the height of the beam. 34. The heat exchange unit of the heat exchanger according to claim 30, characterized in that the ratio of unequal steps of adjacent pipes is accepted to differ by at least 5% from the value of the smaller of them.

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