RU2778804C1 - Heat transfer increaser device and boiler containing this device - Google Patents

Abstract

FIELD: heat engineering.

SUBSTANCE: invention relates to the field of heat engineering and can be used in hot water boilers. The device for intensifying heat transfer, configured to be installed between the flat edges of adjacent heat exchanger tubes, together with said edges forms at least one labyrinth channel, having a proximal end with an inlet for combustion products, a distal end with an outlet for combustion products and at least one partition located so as to provide at least one bend of the said labyrinthine channel. Hot water boiler containing a body (10) and a heat exchanger, the pipes (7) of which have at least two non-adjacent, essentially flat faces, the first collector (3), the second collector (5). The pipes (7) are connected at one end to the first collector (3), and at the other end to the second collector (5), forming an assembly in the form of a squirrel wheel. Devices for intensifying heat transfer are installed in the gap between adjacent pipes.

EFFECT: increasing the intensity of heat transfer without making changes to the design and shape of the heat exchanger tubes, while the elements that ensure the intensification of heat transfer are easily mounted and dismantled, do not weaken the structure.

30 cl, 8 dwg

Description

FIELD OF TECHNOLOGY TO WHICH THE INVENTION RELATES

The invention relates to hot water boilers for the needs of heating and hot water supply of municipal, domestic and industrial facilities.

BACKGROUND OF THE INVENTION

Known hot water boiler containing a housing having a side wall and two closing elements that are rigidly connected to different ends of the side wall and form with it the internal space of the boiler [1]. The boiler burner [1] is located in the inner space of the body and is connected to one of the closing elements. The boiler heat exchanger [1] is located in the internal space of the housing between the side wall and the burner so that it defines the combustion chamber surrounding the burner and shields the side wall of the boiler housing from the radiant radiation of the burner. Between the heat exchanger and the side wall of the boiler body [1], a circular channel is formed for the passage of flue gases formed in the combustion chamber. The closing elements of the boiler body [1] are designed so that one of them forms an inlet manifold for supplying the heat carrier to be heated into the boiler, and the other outlet manifold for the removal of the heated heat carrier. The boiler heat exchanger [1] is formed by separate flow tubes in one direction, each of which is connected at one end to the inlet manifold, and at the other end to the outlet manifold. Each tube of the boiler heat exchanger [1] has an elongated cross section, the elongated sides of which define heat exchange surfaces located opposite each other. The boiler heat exchanger [1] is made in the form of sectors containing tubes, the heat exchange surfaces of which are predominantly parallel to each other, each tube of the sector with an elongated cross section has ends, one of which faces the burner, and the other - to the side wall of the boiler body [1]. The heat exchange surfaces of adjacent tubes in the sector form a continuous flow channel for the passage of flue gases from the combustion chamber into the specified circumferential flue gas channel formed between the heat exchanger and the side wall of the boiler body.

The disadvantages of the boiler [1] are:

1) The need to use a large number of heat exchange tubes, which leads to an increase in the cost of materials, and also increases the weight of the boiler [1].

2) The location of the tubes in sectors is necessary to bring the tubes closer to each other in order to increase the speed of the exhaust gases for better heat transfer and the ability to control the geometry of flat heat exchange tubes due to water pressure in them. This leads to the need within each sector to weld the tubes to the tube sheet very close to each other, which is very laborious and complicates the control of welds.

3) Also, a very close location of the heat exchange tubes negatively affects the life of the boiler [1]. Since the water in the pipes rises under the action of lifting forces due to heating of the water, i.e., very slowly, the slightest clogging of one of the pipes will cause a difference in the heating temperature of the neighboring pipes and, as a result, different elongation of the pipes. From different pressure on the tube plate, into which the heat exchanger pipes are welded, stress arises in the tube plate, which after a certain number of cycles leads to the formation of microcracks in it and the failure of the boiler. The distance between the pipes is calculated on the basis of appropriate well-known methods and has the minimum allowable values. The smaller the distance between adjacent pipes, the shorter the life of the boiler.

4) The need for a close location of pipes in each sector to increase heat transfer increases the resistance to the passage of burnt gases, which leads to the need to use burners of greater power. An increase in the speed of passage in a narrow gap between flat pipes can lead to a drop in pressure on the walls of these pipes and a deterioration in the contact of gas molecules with stacks of tubes (due to the Bernoulli effect).

5) Also, due to the sectoral arrangement of the heat exchanger tubes, unused areas appear between the sectors, in which uncooled corners are installed to keep flat heat exchange tubes from deformation due to water pressure in them. The corners used must be heat-resistant and of sufficient thickness. The disadvantage is that the area of the boiler is used inefficiently, and in the furnace space of the boiler [1] there are elements that do not contribute to heat transfer.

6) The disadvantage is also the rigid connection of the side wall to the closing elements of the boiler from below and from above [1]. Since the boiler wall [1] and the heat exchanger tubes are located along the length in the same direction and have different temperatures, due to the temperature difference in them, a different elongation occurs and when the wall and pipes are rigidly fixed, stress occurs in the boiler elements, which also negatively affect boiler service life. Also, the non-removable wall of the boiler [1] does not allow for operational inspection, cleaning and replacement of some elements of the heat exchanger.

Also known is the design of a single-pass hot water boiler, containing a housing having a side wall and two closing elements that are rigidly connected to different ends of the side wall and form with it the internal space of the boiler [2]. The boiler [2] contains a burner located in the inner space of the housing and connected to one of the closing elements, a heat exchanger located in the inner space of the housing between the side wall of the housing and the burner so that it defines the combustion chamber surrounding the burner and screens the side wall of the boiler housing from radiant burner radiation. Between the heat exchanger and the side wall of the boiler body [2], a circumferential channel is formed for the passage of flue gases formed in the combustion chamber. The closing elements of the body are designed so that one of them forms an inlet manifold for the wire of the coolant to be heated to the boiler, and the other forms an outlet manifold for removing the heated coolant from the boiler. The boiler heat exchanger [2] is formed by separate flow tubes in one direction, each of which is connected to the inlet manifold at one end and to the outlet manifold at the other end. In this case, each tube of the heat exchanger has an elongated cross section, the elongated sides of which define elongated heat exchange surfaces located opposite each other, one of which is facing the burner, and the other is facing the side wall of the boiler body. In this case, the pipes of the boiler [2] are located so that the elongated heat exchange surface of each pipe facing the burner is at least partially blocked by the adjacent pipe, and the heat exchange surface of each pipe facing the burner and the neighboring pipe overlapping it with its heat exchange surface facing the side wall of the casing form a continuous passage channel for the passage of flue gases from the combustion chamber into the specified circumferential flue gas channel formed between the heat exchanger and the side wall of the boiler body [2].

The execution of the heat exchanger from a plurality of individual pipes with an elongated cross section, as well as the presence of channels between the pipes for the passage of combustion products from the combustion chamber into the circumferential channel, can significantly increase the heat exchange surface. At the same time, the presence of such channels, which have a relatively large length in the longitudinal direction of the boiler [2], provides a connection between the combustion chamber and the circumferential flue gas channel without the need to change the direction of flue gas movement to the opposite.

Thus, the required thermal power of the boiler [2] is achieved by heating the coolant both from the burner radiation and from the convective heat of flue gases.

In addition, the use of the specified one-pass boiler system [2] reduces the internal hydraulic resistance of the heat exchanger and thus allows the use of less powerful pumps for the circulation of the coolant. This drag reduction effect is enhanced by the heat exchanger being made of multiple single-flow tubes that create a significant overall heat exchanger flow area, which allows the heat transfer medium to move faster within the heat exchanger, whereby heavier sludge particles settle by gravity in the inlet manifold, significantly reducing clogging. pipes of the heat exchanger, facilitating the cleaning of the heat exchanger and increasing the periods between maintenance.

However, the partial overlap of the heat exchange tubes with the formation of passage channels between the heat exchange surfaces of adjacent tubes leads to the fact that at the inlet to such passage channels from the side of the burner, the combustion products have a significant concentration and maximum speed of movement, and at the exit from the passage channels into the circumferential channel, the combustion products move only along that part of the heat exchange tube that is not blocked by the neighboring tube, that is, they are subjected to dispersion with a decrease in the speed of their movement. This leads to the fact that only those parts of adjacent heat exchange tubes that form passage channels for concentrated and high-speed movement of combustion products are heated to the maximum, that is, they overlap each other. The parts of each heat exchange tube that are not covered by the neighboring tube are heated to a lesser extent. In this case, for uniform heating of all the water entering the heat exchange tubes, either a longer period of time or an increase in boiler power is required.

Also, in order to achieve sufficient heat transfer, it is necessary to place the pipes as close as possible relative to each other, which leads to the complexity of manufacturing the boiler and its fragility due to the small distance between the pipes, which reduces the resistance to cyclic loads of the metal of the tube sheet, to which the heat exchange pipes are welded.

Rigid fastening of the boiler wall [2] to the closing lower and upper elements also does not contribute to the durability of the boiler due to the stresses arising in the heat exchanger due to the temperature difference between the heat exchanger pipes and the side wall. Also, rigid fastening of the wall to the heat exchanger prevents quick inspection, cleaning of the boiler [2] from soot and, if necessary, repair.

These shortcomings indicate the lack of efficiency of such a design of a hot water boiler [2].

DISCLOSURE OF THE INVENTION

The terms and expressions used in this text are given the following meaning.

"Labyrinth passages" - passages for combustion products, in which the trajectory of combustion products, at least on one segment of the path from the proximal to the distal part of the channel, deviates from a straight line. Preferably, on the way from the proximal to the distal part of the channel, the combustion products change their direction at least twice and move first in one lateral direction and then in the other lateral direction.

Under the assembly in the form of a "squirrel wheel" is understood as an assembly, whose side boundaries are mainly formed by longitudinally elongated pipes - located on the periphery of the longitudinal central cavity, and the ends - by collectors located mainly in the transverse direction.

Under the "jumpers" are understood the structural elements that connect the partitions to each other into a single structure.

By "proximal" end is meant the end closest to the burner.

By "distal" end is meant the end farthest from the burner.

The technical problem of the invention is the intensification of heat transfer in boilers with heat exchange tubes located around the burner like a squirrel wheel.

The technical result consists in the fact that the intensity of heat transfer is increased due to the fact that the combustion products are directed through a labyrinth channel with a large heat exchange area (compared to pipes), without making changes to the design and shape of the pipes themselves (there is no need for profiling their surface) , while the elements that provide heat transfer intensification are easily mounted and dismantled (for example, for cleaning), do not weaken the structure (on the contrary, the overall strength of the assembly increases).

The above task is achieved due to the fact that the proposed device for intensifying heat transfer is made with the possibility of installation between the flat faces of adjacent pipes of the heat exchanger, while together with the said flat faces of neighboring pipes it forms at least one labyrinth channel for combustion products, having a proximal an end with an inlet for combustion products, a distal end with an outlet for combustion products, side walls formed by said flat faces of adjacent pipes, and at least one partition located so as to provide at least one bend of said labyrinth canal.

To ensure the mechanical strength of the device, the aforementioned partitions can be interconnected by bridges. In addition to mechanical, jumpers can partly perform a heat exchange function, especially if their cross section, the area of contact with combustion products and pipes are large enough. The shape of the jumpers can be different.

In one of the simplest embodiments, the aforementioned webs may be rods threaded through holes in the aforementioned baffles.

In an even simpler embodiment, said webs are longitudinally elongated rod-like elements molded in one piece with said webs.

In a more complex embodiment, the aforementioned bridges are groups of plate elements having a first side end intended for contact with one said pipe, a second side end located opposite said first side end and intended for contact with another said pipe, a proximal end, and a distal end located opposite said proximal end. The greater the ratio of bridges and partitions, the higher will be the strength of the device and the more important will be the contribution of bridges to heat transfer.

In a preferred embodiment, said webs are trapezoidal in plan. This form allows you to install the device in tension, sliding it between two pipes like a wedge.

The location of jumpers, including flat ones, can be different.

In one of the simplest embodiments, the aforementioned bridges are arranged parallel to each other. This option is the most suitable for the manufacture of devices by casting.

The mutual orientation of jumpers, including flat ones, and pipes can be different.

In the simplest embodiment, the dihedral angle between the aforementioned webs and the aforementioned flat faces of adjacent pipes is a right angle.

In a more complex embodiment, the dihedral angle between the aforementioned webs and the aforementioned flat faces of adjacent pipes is different from a right angle.

The mutual orientation of the jumpers, including flat ones, and the shortest direction of movement of the combustion products can also be different.

In the simplest embodiment, the angle between the aforementioned bridges and the imaginary shortest direction of movement of the combustion products is 180 degrees.

In a more complex embodiment, the angle between the aforementioned bridges and the imaginary shortest direction of movement of the combustion products is different from 180 degrees. In the limit, this angle can reach 90 degrees.

The labyrinth shape of the channel can be provided by various techniques, for example, by varying the length and location of the partitions.

In one case, the plane of the labyrinth channels will be oriented across the axis of the pipes. For example, in one of the simplest forms of execution, one end of the aforementioned partition is flush with the side ends of the aforementioned jumpers, between which it is located, and the other end is with a gap relative to the side ends of the aforementioned jumpers, between which it is located.

Alternatively, the plane of the labyrinth channels may be oriented predominantly along the direction of the pipes. For example, in one of the preferred forms of execution, the aforementioned partitions are made in such a way that they almost completely block the lumen of the channel between the said flat edges of the pipes over its entire area, with the exception of sections made with a gap relative to the aforementioned bridges, which ensure the passage of combustion products in the proximal distal direction.

With an increase in the number of partitions, the completeness of heat extraction from combustion products increases. In this regard, it is preferable when at least two of the aforementioned partitions are located between adjacent aforementioned webs, while the aforementioned gaps of adjacent partitions are located near the opposite side ends of the aforementioned webs. Thus, the combustion products move through the labyrinth, the channels in which are formed by adjacent partitions and pipe walls, and the flow between the channels with a change in the direction of movement of the combustion products is carried out through the mentioned gaps.

The aforementioned baffles, in one of the possible embodiments, may have a width less than the distance between the aforementioned flat edges of adjacent pipes in such a way as to provide a passage for the combustion products.

The orientation of the baffles relative to the imaginary shortest direction of movement of the combustion products can be different.

In the simplest embodiment, the planes of the aforementioned baffles are oriented essentially perpendicular to the imaginary shortest direction of movement of the combustion products between the aforementioned pipes.

In a more complex embodiment, the angle between the planes of the aforementioned baffles and the imaginary shortest direction of movement of the combustion products between the aforementioned pipes may differ from a straight one. In the limiting case, this angle is 180 degrees, and in the gaps between the partitions, the combustion products will move along the labyrinth located in the plane of the pipes, mainly along the axis of the pipes.

In one particularly preferred embodiment, the device is designed to be installed between pipes under tension. This connection simplifies the design, avoids the use of any additional fasteners.

The shape of the pipes in combination with which the device can be used may vary. An important point is only the presence of two more or less flat edges, which make it possible to install devices between adjacent pipes in tension, similar to a wedge. Why is it important that the cavity of the annular space expands in the proximal-distal direction and does not have protrusions and undercuts that prevent insertion of the device.

Strictly speaking, the shape of the faces may slightly deviate from flatness, however, the stronger such a deviation is, the more difficult it is to provide a large area of contact between the device and them.

In this regard, the "flat" shape of the edges in the present description refers to a shape that provides a significant area of contact between the device and the pipe and the possibility of installation by the wedge method. Taking into account this criterion, for example, the cylindrical side surface of the pipes cannot be called “flat”, since the contact area of the part installed by the wedge method between the cylindrical pipes, even in the limiting case, will be less than half the area of the side surface of the cylinder, while if the surfaces are made flat (or congruent), the area of contact of the parts with an increase in the length of the cross section in the proximal-distal direction tends to the full area of the lateral surface.

In view of the foregoing, the more elongated the pipes are in cross section, the greater the heat exchange area can be provided using the proposed device, both by increasing the contact area between the pipes and the device, and due to the length of the labyrinth channel. In this regard, it is preferable that the aforementioned pipes have an elongated cross section. Even more preferably, when the length of the cross-section of said pipes is at least twice the width of their cross-section.

At the same time, it is desirable that the pipes be relatively thin-walled in order to ensure their slight deformation during the installation of devices and a tighter abutment. In addition, mechanical stresses in thin-walled pipes during thermal expansion do not reach critical values and are not capable of destroying the proposed devices for heat transfer intensification.

In a preferred embodiment, the longitudinal axes of the aforementioned pipes are substantially parallel.

Even more preferably, the tubes and headers of the heat exchanger are arranged in a squirrel-like arrangement.

The device can be made of various metals and alloys, but aluminum and its alloys are preferred, which have a higher thermal conductivity compared to austenitic or carbon steels, which are used to make heat exchanger pipes and do not corrode in the environment of combustion products.

In the most preferred embodiment, the device is one-piece. In this case, the manufacturing process is easily scalable and requires a minimum number of operations and manual labor.

The use of the device makes it possible to create boilers with fewer heat exchange tubes and/or with a smaller thickness, while the tubes can be evenly spaced over the entire area, and sufficient distance can be provided between them to increase the life of the boiler (too frequent arrangement of tubes, which is necessary to achieve comparable thermal efficiency leads to a reduction in the gaps between the pipes, weakening the tube sheet, increasing the length of the joints between pipes and headers).

In yet another aspect, the invention relates to a hot water boiler comprising:

body (10) and

stainless steel heat exchanger;

said heat exchanger comprises:

pipes (7) having at least two non-adjacent, essentially flat faces,

first collector (3),

the second collector (5);

said pipes (7) are connected at one end to said first manifold (3), and at their other end to said second manifold (5), forming an assembly in the form of a squirrel wheel,

in the gap between adjacent pipes, the above-described devices for intensifying heat transfer are installed.

The boiler described above at least partially eliminates the shortcomings of known boilers [1] and [2].

In one particularly preferred form of execution, the aforementioned tubes are oriented vertically.

In one of the preferred forms of execution, the headers of the aforementioned boiler are in the form of a closed or open ring or shell, or are composite of annular sectors interconnected by additional headers.

In another preferred form of execution, the continuation of the planes of the faces of the aforementioned adjacent pipes converge into a line essentially coinciding with the longitudinal axis of the boiler (similar to the boiler [1]).

In an alternative form of execution, the continuation of the planes of the faces of the above-mentioned adjacent pipes are not parallel to each other and converge into a line located at a distance from the longitudinal axis of the boiler (similar to the boiler [2]).

The above-mentioned body (10) may include a shell made removable. Preferably, one end of said shell is rigidly fixed relative to one of the said manifolds, and the other end is slidable relative to the other manifold in the longitudinal direction. This reduces the stress in the structure during thermal expansion of the pipes, simplifies inspection, cleaning the boiler from soot and, if necessary, repairs.

The construction and principle of operation will be illustrated below by means of schematic drawings of some specific embodiments and their more detailed description.

BRIEF DESCRIPTION OF THE FIGURES OF THE DRAWINGS

In FIG. 1 shows the boiler in a perspective view of the boiler, front view.

In FIG. 2 shows a front view of the boiler.

In FIG. 3 is a perspective view showing a schematic section of the boiler with the heat exchanger casing removed.

In FIG. 4 shows section A-A.

In FIG. 5 shows section B-B.

In FIG. 6 shows view B.

In FIG. 7 Axonometry of an element of the intensification device with ribs and baffles.

In FIG. 8 Axonometric view of the heat exchanger tube.

IMPLEMENTATION OF THE INVENTION

As shown in FIG. 1-6, the proposed heat exchanger consists of an upper (5) and lower (3) collectors, having a generally annular shape. The collectors are formed by a tube sheet (17), an inner shell (15), an outer shell (16) and a flat cover (14). The heat-exchange tubes (7) oblong in cross-section in the boiler are welded to the tube sheets of the collectors (17) in such a way that the tubes are arranged in a circle around the furnace at a distance from each other. The long axis of the cross section of the pipes lies on imaginary radial rays emanating from the center of the circle. The pipes have the same elongated cross section and are located at the same distance from the center of the circle. Their lateral surfaces are essentially flat, with a slight slope, allowing the expansion of the annulus in the proximal-distal direction. Heat transfer intensification devices (13) are installed in the formed gaps between the tubes. These devices are made of aluminum or its alloys and have lintels and/or baffles pressed tightly against the pipe walls. The devices are installed in such a way that the walls of the pipes are slightly deformed. The devices are held in the annular spaces due to the friction force, which only increases with thermal expansion.

The casing (10) of the boiler is made removable in the form of a shell with flares outwards. Holes for fastening with bolts are made in the flanges of the casing (10). The casing (10) is put on the heat exchanger from above. As it lowers, it rests on the plane of the lower collector cover protruding beyond the outer shell (3), in which holes are made for fixing the lower flanging of the casing to the lower part of the heat exchanger. In the upper part of the casing (10), the flanging and the plane of the upper part of the upper collector (5) protruding beyond the outer shell are located at the same level and are interconnected by plates with bolt holes that press the gasket located on the upper part of the flanging of the casing and the protruding plane of the upper part upper manifold (5). Both flanges are sealed with top and bottom manifolds with silicone sealant or gaskets. With linear elongation, the heat exchanger shell compensates for stresses due to straight sections of flanges that work like an "accordion".

A supply pipe (4) and a pipe for removing air from the heat exchanger are welded into the chamber of the upper collector (5). A return pipe (2) and a pipe for draining water are welded into the chamber of the lower collector (3).

A burner with a fan (1) is installed on the cover of the upper collector (5). The burner part (18) of the burner itself is located in the furnace space formed by elongated pipes (7) and devices (13) made of aluminum or its alloys installed between them, and also from above by the upper manifold (5), and from below by the lower manifold (3). Non-combustible heat insulation (19) is installed in the lower manifold (3) in the inner space of the inner shell.

Boiler with devices (13) works as follows:

The gas burns in the burner (1, 18) with the formation of heat in the form of radiant energy and flue gases. The radiant energy is transferred to the tube sheets (17) of the lower (3) and upper (5) collectors and to the heat exchange tubes (7) located in the inner part of the furnace. Then the burnt gases enter devices (13) made of aluminum or its alloys, in which the burnt gases, moving from the proximal to the distal end of the labyrinth channels along a zigzag trajectory, transfer heat to the heat exchange tubes and the device (13), and those, in turn, to the heat exchange tubes . Leaving the labyrinth channels at the distal ends of the devices (13), the combustion products move into the space (8) between the casing (10) of the heat exchanger and the part of the heat exchange tubes external from the furnace, while in the process of movement, they give off heat as much as possible directly to the walls of the heat exchange tubes and the ribs of the elements, which , due to contact with the walls of the tubes, they also transfer their heat to the coolant. The use of devices (13) significantly increases the heat transfer from the combustion products to the coolant, due to the high thermal conductivity of aluminum and its alloys, by increasing the heat transfer area and slowing down the rate of passage of the combustion products flow through the annulus.

Then the combustion products are removed into the chimney (10). The condensate from the burnt gases is removed through the condensate removal pipe at the bottom of the boiler.

The coolant (water) comes from the consumer through the branch pipe (2) in the lower manifold (3), then enters the lower manifold (3) and then into the elongated heat exchange tubes (7), where it gradually heats up from the radiant energy of the burnt gases falling on the pipe body and due to the zigzag movement in the labyrinth channels of the devices (13), and the transfer of heat from the partitions and jumpers of the devices (13), it rises to the upper collector (5) from where it is supplied to the consumer through the supply pipe.

Devices (13) are easily mounted in the annular spaces and dismantled for cleaning, reinforce the structure. Thanks to the devices (13), the intensity of heat transfer is increased.

LIST OF SOURCES

1. RF patent No. 2725918.

2. RF patent for invention No. 2625367.

Claims (38)

1. Device for intensifying heat transfer, made with the possibility of installation between the flat edges of adjacent tubes of the heat exchanger, characterized in that, together with the mentioned flat edges of adjacent tubes, it forms at least one labyrinth channel for combustion products, having a proximal end with an inlet for combustion products , a distal end with an outlet for combustion products, side walls formed by said flat faces of adjacent pipes, and at least one partition located so as to provide at least one bend of the said labyrinth channel. 2. The device according to claim. 1, characterized in that it additionally contains jumpers connecting the said partitions to each other. 3. The device according to claim 2, characterized in that the aforementioned bridges are rods threaded through the holes in the aforementioned partitions. 4. The device according to claim 2, characterized in that the aforementioned bridges are longitudinally elongated rod-shaped elements cast in one piece with the aforementioned partitions. 5. The device according to claim 2, characterized in that the aforementioned jumpers are groups of plate elements having a first side end intended for contact with one said pipe, a second side end located opposite said first side end and intended for contact with the other mentioned pipe, the proximal end and the distal end located opposite the mentioned proximal end. 6. Device according to claim 5, characterized in that said bridges are trapezoidal in plan. 7. The device according to claim 5, characterized in that in it the aforementioned jumpers are located parallel to each other. 8. The device according to claim 5, characterized in that the dihedral angle between the aforementioned bridges and the aforementioned flat faces of adjacent pipes is a right angle. 9. The device according to claim 5, characterized in that the dihedral angle between the aforementioned bridges and the aforementioned flat faces of adjacent pipes differs from the right angle. 10. The device according to claim 5, characterized in that in it the angle between the aforementioned jumpers and the imaginary shortest direction of movement of the combustion products is 180°. 11. The device according to claim 5, characterized in that in it the angle between the aforementioned jumpers and the imaginary shortest direction of movement of the combustion products differs from 180°. 12. The device according to claim 5, characterized in that one end of the aforementioned partition is flush with the side ends of the aforementioned jumpers, between which it is located, and the other end is with a gap relative to the side ends of the aforementioned jumpers, between which it is located. 13. The device according to claim 5, in which the aforementioned partitions are made in such a way that they almost completely block the lumen of the channel between the said flat edges of the pipes and the aforementioned jumpers over its entire area, with the exception of sections made with a gap relative to the aforementioned jumpers, ensuring the passage of products combustion in the proximal-distal direction. 14. The device according to claim 12, characterized in that at least two of the aforementioned partitions are located between adjacent aforementioned bridges, while the aforementioned gaps of adjacent partitions are located near the opposite side ends of the aforementioned bridges. 15. Apparatus according to claim 1, characterized in that said baffles have a width less than the distance between said flat edges of adjacent tubes, so as to provide passage for combustion products. 16. The device according to claim. 1, characterized in that in it the planes of the aforementioned partitions are oriented essentially perpendicular to the imaginary shortest direction of movement of the combustion products between the aforementioned pipes. 17. The device according to claim. 1, characterized in that in it the angle between the planes of the aforementioned partitions and the imaginary shortest direction of movement of the combustion products between the aforementioned pipes differs from a straight one. 18. Device according to claim 1, characterized in that said pipes have an elongated cross section. 19. The device according to claim 1, characterized in that the length of the cross section of said pipes is at least twice the width of their cross section. 20. The device according to claim. 1, characterized in that the longitudinal axes of the aforementioned pipes are essentially parallel. 21. The device according to claim. 1, characterized in that it is designed to be installed in tension. 22. The device according to claim. 1, characterized in that it is designed to intensify heat transfer in heat exchangers with pipes and collectors in the form of a squirrel wheel. 23. The device according to claim 1, characterized in that it is made of aluminum or an aluminum alloy. 24. The device according to claim. 1, characterized in that it is one-piece. 25. Hot water boiler, containing: body (10) and stainless steel heat exchanger; said heat exchanger comprises: pipes (7) having at least two non-adjacent, essentially flat faces, first collector (3), the second collector (5); said pipes (7) are connected at one end to said first manifold (3), and at their other end to said second manifold (5), forming an assembly in the form of a squirrel wheel, devices according to any one of paragraphs are installed in the gap between adjacent pipes. 1-24. 26. The boiler according to claim 25, characterized in that the collectors in it are in the form of a closed or open ring or shell, or are composed of annular sectors interconnected by additional collectors. 27. The boiler according to claim 25, characterized in that in it the continuations of the planes of the faces of the aforementioned adjacent pipes converge into a line substantially coinciding with the longitudinal axis of the boiler. 28. The boiler according to claim 25, characterized in that the continuation of the planes of the faces of the above-mentioned adjacent pipes are not parallel to each other and converge into a line located at a distance from the longitudinal axis of the boiler. 29. The boiler according to claim 25, characterized in that the pipes in it are oriented vertically. 30. Boiler according to claim 25, characterized in that the aforementioned body (10) includes a removable shell.

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