RU2686134C1 - Plate heat exchanger and the plate heat exchanger manufacturing method - Google Patents

Abstract

FIELD: heating equipment.SUBSTANCE: invention relates to the heat engineering and can be used in the art for liquid or gaseous media pre-heating, for example, as the recuperator. Plate heat exchanger contains the first section of the heat exchanger, which includes a cylindrical outer casing, one central and two peripheral separation rings, placed between the body and the rings and heat exchanger elements supported on the central separation ring, made of corrugated plates connected in pairs along their peripheral edges, at the same time, the heat exchange elements have flanges protruding beyond the peripheral edge, forming inlet and exhaust manifold windows, connected without a gap with the windows of the adjacent heat exchange elements and covered by separating rings, wherein the flanges, the central and peripheral rings form the internal heat transfer medium supply and removal manifolds, and the end parts of the heat exchanger are made in such a way as to ensure the possibility of passage between the heat exchange elements of the external coolant, at the same time, the heat exchanger is equipped with an additional section, similar in construction and located coaxially with the first section.EFFECT: reducing the mass of the heat exchanger while increasing its efficiency and reliability.24 cl, 12 dwg

Description

The invention relates to heat engineering and can be used in the technique for heating liquid or gaseous media, for example, as a recuperator.

Known plate heat exchanger (RF Patent No. 125321, IPC F28D 9/00, Plate heat exchanger with Frenkel-type heat exchange surfaces. Published on February 27, 2013) with multiple-path, cold and single-pass path, hot heat carrier, comprising a housing, supply and discharge channels for both coolants, the matrix, with Frenkel-type heat transfer surfaces, which are pairwise connected metal plates with the coplanar direction of the corrugations located on the upper and lower plates of each pair. At the same time, cold and hot coolants flow in transverse flows and the cold coolant has more than four intersecting flows with a hot coolant, which ensures high heat exchange efficiency, approaching the most efficient heat transfer with countercurrent flow of coolants.

This design does not have sufficient reliability due to the need to seal many places of the supply and removal of heat carrier with high pressure.

Also known is a plate heat exchanger and a method of manufacturing a plate heat exchanger (Patent RF №2100733, IPC F28D 9/00, B21D 53/04, Plate heat exchanger and a method of manufacturing a plate heat exchanger. Published 12/27/1997.). The heat exchanger includes a housing with devices for supplying and discharging one coolant, as well as packages of corrugated plates connected in pairs along the peripheral edges and branch pipes for supplying and discharging the second coolant, communicating with collectors formed by the flanged windows made in the plates, connecting plates with clamping elements between which The plate pack described above is installed. On the plates can be performed additional stamping, forming a straight or zigzag channels. In the manufacture of a plate heat exchanger by stamping, identical corrugated plates with peripheral edges and flanged windows are made, then the plates are rigidly connected in pairs along the peripheral edges, and the heat exchange elements formed during this process interconnect the flanges of the window plates in the adjacent elements, attach the supply and discharge pipes and place in the case. The flanging of the windows is performed with protruding 0.3-0.6 mm sections above the surface of the corrugation plates with the formation of an inclined surface between the peripheral edges and flanging of the windows with an angle at the base equal to 45 ° to 75 °. The plate pack is clamped using clamping plates and clamping elements. The peripheral edges of the plates of a given width are connected by means of roller contact welding or by argon-arc welding, or they are joined by soldering.

The disadvantages of this known heat exchanger and method of its manufacture should be attributed to the high intensity and low design efficiency. In addition, these heat exchangers have increased stresses in the plates adjacent to the clamping plates due to the large temperature difference, and the increase in the flow of heat transfer fluids here is associated with an increase in the two parameters of the heat exchanger, which is not always acceptable.

Closest to the proposed invention to the technical essence is a known plate heat exchanger of the heat exchanger of a gas turbine unit (US Patent No. 7,065,873 published 06/27/2006 - prototype) containing a cylindrical outer case, internal separating rings placed between them and resting on the central internal separating ring, identical heat exchangers elements in the form of envelopes made of pairs of ribbed plates connected in pairs along the peripheral edges of the ribbed plates. The high-pressure internal coolant supply and discharge connections are formed here by a set of structural elements including strips supported on the separating rings. There is also known a method of manufacturing this plate heat exchanger, which includes the gradual cutting and assembly of structural elements, with an indication of the places of welding, including the welding of the strips.

The disadvantages of this design and method of its manufacture include a large number of structural elements and welds, which adversely affects the tightness and strength of the heat exchanger. In addition, the use in the area of the pipes for supplying and discharging the coolant of the strips with their argon-arc welding increases the metal consumption and the cost of the product, as well as reduces its effectiveness due to blocking of the nozzle window bores. An increase in the flow rate of the hot (external) coolant here is associated with an increase in the diameter of the heat exchanger, and an increase in the internal, cold coolant — with the length of the heat exchanger, which is not always acceptable in gas turbine structures. In an attempt to preserve the length of the heat exchanger, in such cases, the number of transverse flows is reduced, which leads to a decrease in the efficiency of the heat exchanger. A photo of a view of the heat transfer fluid inlet of the Capstone C-30 heat exchanger (as in the prototype) is shown in FIG. one.

The problem to which the claimed invention is directed, is the elimination of the above disadvantages of the prototype. In addition, the claimed invention solves the problem of reducing the cost and optimizing the mass-dimensional characteristics of a gas turbine installation, using a standard (spent, existing) envelope of the heat exchanger.

The technical result consists in the implementation of a highly efficient heat exchanger increased flow of coolants with limitations of size, reducing the mass of the heat exchanger, its cost, while increasing its efficiency and reliability by providing tightness and strength of the heat exchanger, as well as increasing performance by increasing air flow (coolant) through heat exchanger.

The technical result is achieved due to the fact that the plate heat exchanger contains the first section of the heat exchanger, which includes a cylindrical outer casing, one central and two peripheral separating rings placed between the casing and the rings and heat exchanger elements made from pairs connected along peripheral edges corrugated plates, while the heat exchange elements have flanges protruding beyond the peripheral edge, forming inlet and outlet The collector windows are connected without gap with the windows of adjacent heat exchange elements and covered by separating rings, and the flanges, the central and peripheral rings form the collectors for supplying and discharging the internal heat carrier, and the end parts of the heat exchanger are designed to allow the external heat carrier to pass between the heat exchange elements, in addition, the heat exchanger contains an additional section of the heat exchanger, made similar to the first section, and the section of the heat exchanger CENI disposed in the heat exchanger so as to provide parallel internal coolant flow to the first and further heat exchanger section, and also provide them parallel external coolant supply.

The heat exchange elements are adjacent to each other along the enveloping surfaces of the corrugations and have a ruled surface with an involute guide.

Corrugated plates consist of at least two vortex matrices connected by a longitudinal smooth channel and separated by internal partitions.

Partitions of each heat exchange element are made by stamping plates and interconnected.

With the number of matrices equal to more than two, the partitions and longitudinal smooth channels are arranged in a checkerboard pattern.

The adjacent corrugations of the matrices of each plate of the heat exchange element are located at an angle of 20 ° -90 ° to each other.

The width of the edges and partitions at the joints is from 20 plate thickness.

The width of the edge and the partition at the joints is preferably from 20 to 40 plate thicknesses.

Along the peripheral edges near the smooth channels, partitions connected to the heat exchange elements are installed.

Involute guides of the ruled surfaces of the heat exchange elements of the first and additional sections have different directions.

The elements are connected by welding or soldering.

The additional section of the heat exchanger is located coaxially with the first section from its outer side, and the central and both peripheral separation rings of the additional section are made in one piece with the cylindrical outer case of the first section of the heat exchanger, and the outer case of the first section of the internal heat exchanger has channels configured to provide supply and discharge internal coolant to the intake and exhaust manifolds of the additional section.

The elements are connected by welding or soldering.

The technical result is also achieved due to the method of manufacturing a plate heat exchanger, which consists in the fact that the outer and inner corrugated plates of the heat exchanger section are made by stamping, and then connected in pairs along peripheral edges, and the heat exchange elements formed during this are connected to each other using an outer cylindrical body, two peripheral and one central separating rings, with flanging in each heat exchanger element forming accelerating and outgoing windows, in such a way that they protrude beyond the peripheral edge of the plates along the internal diameter of the heat exchanger, and the ends of the central ring, as well as one end of the peripheral rings, are performed with a profile that repeats the external profile of the outlet windows into which the heat exchange elements are alternately inserted, and then the heat exchange elements are interconnected and with the rings; in this case, an additional section of the heat exchanger is installed in the heat exchanger in such a way as to ensure parallel supply of the heated heat the carrier in the first and additional sections of the heat exchanger, as well as parallel supply of external heat carrier to the first and additional sections of the heat exchanger.

The difference between the outer and inner diameters of the separating rings at the joints with the inlet and outlet windows is from 2.0 to 2.2 mm.

The flanges protrude beyond the peripheral edge by an amount of 0.95-1.05 times the difference between the outer and inner diameters of the separating rings at the junction points with the inlet and outlet ports.

Each heat exchange element is mounted on the central separation ring in such a way that the peripheral edge touches the cylindrical surface of the separation ring.

Corrugated plates perform having at least two vortex matrices connected by a longitudinal smooth channel and separated by internal partitions.

External partitions connected to heat exchange elements are installed along the peripheral edges near the smooth channels.

External partitions are made by stamping a metal sheet.

The internal partitions of each heat exchange element are made by stamping and interconnected.

At least one of the compounds is carried out by welding.

The connection of the corrugated plates of at least one heat exchange element is carried out using the contact roller welding.

An additional section of the heat exchanger is installed coaxially with the first section from its outer side, and the central and both peripheral separating rings of the additional section, as well as the cylindrical outer case of the first section of the heat exchanger are made as one piece having channels adapted to ensure the supply and removal of the internal heat carrier to the inlet and exhaust manifolds additional section.

The invention is illustrated in the figures, in which:

in fig. 1 shows a view of the coolant supply pipe for the Capstone C-30 heat exchanger;

in fig. 2 shows a general view of the first section of the heat exchanger, with a partially opened outer cylindrical body;

in fig. 3 shows internal separating rings with partially installed heat exchange elements - envelopes;

in fig. 4 shows a heat exchange element - an envelope;

in fig. 5 shows external partitions;

in fig. 6 shows a heat exchange element with coolant flow patterns;

in fig. 7 shows the angle at the top of the crossing of the corrugations;

in fig. 8 shows element B of FIG. 6;

in fig. 9 shows element A of FIG. 3;

in fig. 10 shows item B of FIG. four;

in fig. 11 shows a cross-section of a gas turbine engine with an additional heat exchanger section;

in fig. 12 shows a general view of the heat exchanger sections, with different directions of involute guides of the ruled surfaces of the heat exchange elements of the first and additional sections.

The heat exchanger (Fig. 2) consists of two sections: the first and additional. In this case, each section consists of a cylindrical outer housing 1, heat exchange elements 2, central 3 and peripheral 4, 5 separating rings (Fig. 3). The heat exchange elements 2 are made of lower 6 and upper 7 corrugated plates (Fig. 4). The ruled surface with the involute guide plates 6, 7 has a stamped relief and consists of a peripheral edge 8, a corrugation 9, 10 of the vortex matrix, transverse bridges 11 internal partitions, longitudinal smooth channels 12 and flanges 13, 14, as well as collector ports 15, 16.

Separating rings 3, 4, 5 have grooves 17, 18, 19 and 20 (Fig. 3). There are also collectors for the inlet 21 and outlet of the internal and external 24 coolants of the heat exchange element 2 (Fig. 2), external partitions 25, 26 (Fig. 5) and retaining rings 27 (Fig. 2). The directions of flow of heat carriers (Fig. 6) and the crossing angle of the corrugations 9, 10 of the lower 6 and upper 7 plates (Fig. 7) are shown, the external partitions 25, 26 (Fig. 5) are shown, their installation locations are 28, 29 (Fig. 3 and 6) and defining dimensions (Fig. 6, 7, 8, 9). The involute guides of the ruled surfaces of the heat exchange elements 2, 34 of the first and additional sections may have the same or different direction (Fig. 12), which is caused by ensuring the direction of exhaust gas flow.

The lower 6 and upper 7 corrugated plates adjoin each other along the circumflex surfaces of the corrugations 9, 10 (Fig. 4, 7) and are rigidly fastened together, for example, by welding or soldering along the peripheral edges 8 and the lintels of the internal partitions 11. In this case, The assembled heat exchange element 2 of the flange 13, 14 forms the collector windows of the inlet 15 and outlet 16 of the internal coolant (Fig. 4, 10), and inside the heat exchange element 2, along with the corrugations 9, 10 and smooth longitudinal channels 12, channels are formed for the internal coolant to flow. Heat exchange elements 2 are located between the outer casing 1 and the separation rings 3, 4 and 5 (Fig. 2, 3). In this case, the heat exchange elements 2 end of the peripheral edges 8 are based on the Central separating ring 3, adjacent to each other on the flanging 13, 14 of the collector windows 15, 16, which, together with adjacent grooves 17, 18, 19 and 20, peripheral 4, 5 and the central 3 separation rings form the collectors for the inlet 21 and the internal heat transfer (Figs. 2, 3, 4). Between the heat exchange elements 2, in the area of the peripheral edges 8 on the side of the outer casing 1 and the central separating ring 3, external partitions 25, 26 are installed at the points 28, 29 of the formed longitudinal smooth channels 12. The internal heat transfer fluid is supplied to the inlet manifold 21, from where it goes through the collector windows the inlet 15 passes inside the heat exchange element 2, where it moves, as shown in FIG. 6, on the vortex matrix formed by the corrugations 9, 10 of the lower 6 and the upper 7 plates. For a uniform flow of the internal coolant from one to another vortex matrix, which are formed between the internal partitions 11 arranged in a checkerboard pattern, in the area of the overflow windows, made in the form of gaps between the partitions 11 and the peripheral edge 8, the longitudinal smooth channels 12 are formed by punching. the top of the crossing of the corrugations 9, 10 plates 6, 7, as shown in FIG. 6, ranges from 20 ° to 90 °. After the vortex matrices, the internal coolant, in the course of the flow, passes through the collector window of outlet 16 to the collector of the internal coolant outlet. For the external heat carrier, a channel of the vortex matrix is formed between adjacent heat exchanging elements 2. At the same time, the inlet collectors (not shown) and the external heat transfer outlet 24 are formed by the outer case 1 and the peripheral separation rings 5 and 4, respectively. To eliminate the overflow of the external coolant along the peripheral edges 8, in places 28 and 29 external partitions 25, 26 are installed.

In order to improve the performance of the heat exchanger, its sections are located in such a way as to ensure the possibility of parallel supply of external coolant. In particular, this can be achieved by locating the additional section coaxially of the first section from its outside. To reduce the mass of the heat exchanger, the central 3 and peripheral 4, 5 separation rings of the additional section can be made in one piece with the cylindrical outer case 1 of the first section of the heat exchanger. In this case, the outer casing 1 of the first section of the heat exchanger is performed in such a way as to ensure the possibility of supply and removal of the internal coolant to the collectors of the supply 35 and discharge 36 of the internal coolant of the additional section. In particular, it is possible to perform the first section of the channels in the outer casing 1, which are connected with the help of tubes 33 and windows 32 that direct the flow of the internal heat carrier. 8, bridges of internal partitions 11 and flanges 13, 14 of collector windows 15, 16. A cylindrical outer case 1 with separation rings 3, 4 and 5 is manufactured. At the same time, separation rings 3, 4 and 5 are made once itsey outer and inner diameters at the connection points with the eyelet 13, 14 of the collector boxes 15, 16 equal _to δ 2 mm to 2.2 mm (FIG. 9) and the flange returns ends 13, 14 in the plates 6, 7 is performed for the protrusion the end of the peripheral edge on the value of Δ equal to 0.95-1.05 from the value of δ _to (Fig. 8). Themselves joined the ends of the central separation ring 3 and the peripheral separation rings 4, 5 perform figured with grooves 17, 18, 19 and 20 (Fig. 3, 9), which mirror the profile of the peripheral edge 8 and flanging 13, 14, collector windows 15, 16 (Fig. 7).

In the process of manufacturing each section of the heat exchanger by stamping, the lower 6 and upper 7 corrugated plates are made, which differ in the direction of the corrugations 9, 10 and the linear surface with an involute guide.

The bottom 6 and top 7 plates are rigidly fastened together, for example, by welding or soldering with the help of roller contact welding along the peripheral edges 8 and bridges of the internal partitions 11. At the same time, since using contact welding, the width of the weld will be at least 6 plate thicknesses then the width of the peripheral edge 8 and the web of the internal partition 11 should be 20-40 plate thicknesses σ. This is done in order to save material and ensure the tightness and strength of the sections of the heat exchanger in particular and the heat exchanger as a whole. So, in the case of using a sheet with a thickness of 0.2 mm, the width of the peripheral edge 8 and lintel 11 should be from 4 to 8 mm.

On the upper plate 7 of the heat exchange element 2 in the area of the peripheral edges 8 from the outer case 1 and the central separation ring 3, in the places 28, 29 of the formed longitudinal smooth channels 12 external partitions 25 and 26 are fixed, equal in height, width and thickness to the peripheral edge , the width of the two heights of the stamping and the thickness of the corrugated plate, respectively.

Partitions 25, 26 are manufactured by stamping into a given shape and size of a metal sheet, and are rigidly fixed to the top 7 plate of the heat exchange element 2, for example, by welding.

Formed heat exchange elements 2 are located between the rings 3, 4 and 5, the grooves 17, 18, 19 and 20 are inserted. In this case, the heat exchange elements 2 with the ends of the peripheral edges 8 rest on the central separating ring 3, and the flanges 13, 14 connect with the peripheral edges 8 with rings 3, 4, 5 grooves 17, 18, 19 and 20. This connection can also be carried out by welding. In addition, the ends of flanging 13, 14 of adjacent heat exchange elements 2 of collector windows 15, 16 can be connected by welding. After completing the complete set of heat exchange elements 2 with external partitions 25, 26, a cylindrical outer case 1 is put on the assembled set. For convenience, before installing the outer the housing 1, the outside of the heat exchange elements 2 is covered by retaining rings 27 (Fig. 2), preventing the separation of the upper 7 and lower 6 plates.

The heat exchanger operates as follows. For example, consider it as a heat exchanger for a gas turbine engine (GTE) used to recover exhaust heat. The heated coolant, for example, air from the compressor 30 of the CCD, is supplied to the collector 21 for supplying the internal coolant of the first section and through the air flow guides of the window 32 through the tubes 33 to the collector 35 for supplying the additional section and through the corresponding collector windows 15 flows into sections, where the air, moving along the vortex matrix formed by extruded corrugations 9, 10 of the plates 6, 7, is heated by heat transmitted through the plates 6, 7 of the engine exhaust gases coming from the tour Bins 31 to collectors for supplying external coolant and move to the collectors of the outlet 24 of the external coolant on a vortex matrix formed by corrugations 9, 10 adjacent heat exchange elements 2.

The mutual flow of the heated internal coolant — air and heat exhaust gases — is cross-flow, as shown in FIG. 4. Moreover, the direction of transverse movement of air also alternates with a counter (reverse) current with a turn of 180 degrees. The flow of air from one vortex matrix to another - reverse flow occurs through the collector window with adjacent longitudinal smooth channels 12 formed by forgings. The air outlet from the heat exchange element 2 is carried out through the collector windows 16. Subsequently, the heated air from the heat exchanger, through the collector of the internal heat carrier (not shown), is supplied to the GTE combustion chamber for further heating during fuel combustion.

The use of the vortex matrix formed by the corrugations 9, 10 of the plates 6, 7 and adjacent heat exchange elements 2 with angles α from 20 ° to 90 ° at the top of the crossing of the corrugations 9, 10, as shown in Fig.6, allows exhaust gases to be pumped into the vortex matrix and air with low hydraulic resistance and high heat transfer efficiency. At the same time, the formation of overflow channels with adjacent longitudinal smooth channels 12 between the vortex matrices of the internal heat carrier provides the most uniform filling of the internal heat carrier of the vortex matrices during the flow of the heat carrier according to the “cross countercurrent” scheme. The method of forming heat exchange elements 2, fixing them with grooves 17, 18, 19 and 20 of central 3 and peripheral 4, 5 internal separating rings and connecting flanges 13, 14 of adjacent heat exchange elements 2 of collector windows 15, 16 with each other by welding ensure sufficient rigidity of the structure and use internal coolant with high pressure. The use of two separate sections, the location of which provides the possibility of parallel supply of external heat carrier to them, allows to increase the performance of the heat exchanger by increasing the flow of air passing through it while maintaining its strength. If only one larger section is used, an increase in productivity is possible, but this inevitably leads to a decrease in the strength and reliability of the heat exchanger. In addition, the use of two separate sections, installed coaxially, allows to reduce the diameter of the heat exchanger approximately two times compared with a heat exchanger having one section, designed for the same capacity as the heat exchanger having two sections. Thus, the use of two separate sections allows you to reduce the mass of the heat exchanger and the installation containing such a heat exchanger, as a whole. In this case, the ratio of the flow of the heated coolant passing in the first section and in the additional section may be in the ratio of 3 to 7.

Laying of heat exchange elements 2 in involute, together with external partitions 25, 26, maintains the flow of external coolant along the heat transfer surface with different thermal expansions of structural elements, excluding parasitic flow of coolant along the peripheral edges 8.

The specified ranges of values are due to the fact that when going beyond the minimum value, the reliability of connections decreases, and going beyond the maximum value is not justified in terms of increasing dimensions.

Dimensions within the ranges are chosen, for example, on the basis of the required safety factor of the joints, depending on the pressure of the heat transfer media.

Claims (24)

1. A plate heat exchanger containing the first section of the heat exchanger, which includes a cylindrical outer casing, one central and two peripheral separation rings, placed between the casing and the rings and heat exchanger elements, which are made of pairs of corrugated plates connected in pairs along the peripheral edges of the corrugated plates, differing in that the heat exchange elements have flanges protruding beyond the peripheral edge, forming inlet and exhaust manifold windows, are connected without a gap with windows of adjacent heat exchange elements and covered by separating rings, the flanges, the central and peripheral rings form the collectors for supplying and discharging the internal heat carrier, and the end parts of the heat exchanger are made in such a way as to ensure the passage between the heat exchange elements of the external heat carrier, in addition, the heat exchanger contains additional section of the heat exchanger, made similar to the first section, and the section of the heat exchanger are located in the heat exchanger ike in such a way as to ensure parallel supply of the internal coolant to the first and additional sections of the heat exchanger, as well as to ensure parallel supply of the external coolant to them. 2. The heat exchanger according to claim 1, characterized in that the heat exchange elements are adjacent to each other along the enveloping surfaces of the corrugations and have a ruled surface with an involute guide. 3. The heat exchanger according to claim 1, characterized in that the corrugated plates consist of at least two vortex matrices connected by a longitudinal smooth channel and separated by internal partitions. 4. The heat exchanger according to claim 3, characterized in that the partitions of each heat exchange element are made by stamping plates and interconnected. 5. The heat exchanger according to claim 4, characterized in that when the number of matrices equal to more than two, the partitions and longitudinal smooth channels are arranged in a staggered pattern. 6. The heat exchanger according to claim 3, characterized in that adjacent corrugations of the matrices of each plate of the heat exchange element are located at an angle of 20-90 ° to each other. 7. The heat exchanger according to claim 3, characterized in that the width of the edge and the partition at the joints is 20 times the thickness of the plate. 8. A heat exchanger according to claim 1, characterized in that the width of the edge and the partition in the joints is preferably from 20 to 40 plate thicknesses. 9. The heat exchanger according to claim 3, characterized in that partitions connected to the heat exchange elements are installed along the peripheral edges near the smooth channels. 10. Heat exchanger according to claim 2, characterized in that the involute guides of the ruled surfaces of the heat exchange elements of the first and additional sections have a different direction. 11. Heat exchanger according to any one of the preceding paragraphs, characterized in that the connection of the elements is made by welding or soldering. 12. The heat exchanger according to any one of paragraphs. 1-10, characterized in that the additional section of the heat exchanger is located coaxially with the first section from its outer side, and the central and both peripheral separation rings of the additional section are made in one piece with the cylindrical outer case of the first section of the heat exchanger, and the outer case of the first section of the internal heat exchanger has channels , made with the possibility of supplying and discharging the internal coolant to the inlet and exhaust manifolds of the additional section. 13. The heat exchanger according to claim 12, characterized in that the connection of the elements is made by welding or soldering. 14. A method of manufacturing a plate heat exchanger, which consists in the fact that the outer and inner corrugated plates of the heat exchanger section are made by stamping and then connected in pairs along peripheral edges, and the heat exchange elements formed during this are connected to each other using an outer cylindrical body, two peripheral and one central separating rings, characterized in that flanges are made in each heat exchange element, forming inlet and outlet windows, thus, They protrude beyond the peripheral edge of the plates along the internal diameter of the heat exchanger, and the ends of the central ring, as well as one end of the peripheral rings, are made with a profile that repeats the external profile of the exhaust ports, into which heat exchange elements are alternately inserted, and then the heat exchange elements are interconnected and rings, while in the heat exchanger install an additional section of the heat exchanger in such a way as to ensure parallel flow of the heated coolant in the first and additional seconds heat exchanger, as well as parallel supply of external coolant to the first and additional sections of the heat exchanger. 15. The method according to p. 14, characterized in that the difference between the outer and inner diameters of the separating rings at the points of connection with the inlet and exhaust ports is from 2.0 to 2.2 mm. 16. The method according to p. 15, characterized in that the flanges protrude beyond the peripheral edge by an amount of 0.95-1.05 from the difference between the outer and inner diameters of the separating rings at the junction points with the inlet and exhaust ports. 17. The method according to p. 14, characterized in that each heat exchange element is installed on the Central separation ring so that the peripheral edge in contact with the cylindrical surface of the separation ring. 18. The method according to p. 14, characterized in that the corrugated plates perform having at least two vortex matrices connected by a longitudinal smooth channel and separated by means of internal partitions. 19. The method according to p. 18, characterized in that along the peripheral edges near the smooth channels establish external partitions connected to the heat exchange elements. 20. The method according to p. 19, characterized in that the external partitions are made by stamping a metal sheet. 21. The method according to p. 18, characterized in that the internal partitions of each heat exchange element is made by stamping and interconnected. 22. A method according to any one of claims. 14-21, characterized in that at least one of the compounds is carried out by welding. 23. The method according to p. 22, characterized in that the connection of the corrugated plates of at least one heat exchange element is carried out using the contact roller welding. 24. The method according to p. 14, characterized in that the additional section of the heat exchanger is installed coaxially with the first section from its outer side, and the central and both peripheral separation rings of the additional section, as well as the cylindrical outer case of the first section of the heat exchanger are made as one piece with channels , made with the possibility of supplying and discharging the internal coolant to the inlet and exhaust manifolds of the additional section.

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