Heat exchanger core

FIELD: heating systems.

SUBSTANCE: inventions are intended for heat exchange, and can be used for heating heat carriers. Heat exchanger core consists of two groups of alternating plates. The latter are connected to each other and each plate in each group is made at least in one of its surfaces at least with three platelets, each of which consists of a group of parallel channels, holes passing through the first and second group of plates for transferring fluid heat carriers to the platelets and from them, and distributing channels connecting opposite ends of each platelet in each of the plates to some of the holes related thereto. Distributing channels that are connected to each of the platelets in the plates of the first group are located so that they cross the distributing channels that are connected to some of the appropriate platelets in the plates of the second group. Heat exchanger can include at least one core. Heat exchanger can include headers connected to the core. Heat exchanger can include at least two cores. In heat exchanger the cores are attached rear side-to-rear side, and headers are connected to assembly for transferring fluid heat carriers to the cores and from them.

EFFECT: providing required thermal efficiency, and decreasing dimensions and mass of heat exchanger.

31 cl, 16 dwg

 

The technical field to which the invention relates.

This invention relates to the core of the heat exchanger of this type, which is made from a variety of connected plates with channels designed for flowing fluids (i.e. liquids and/or gases) and formed within at least some of the plates.

The level of technology

Core heat exchangers of this type, which include the present invention (see for example US 4665975), sometimes referred to as the very core of the heat exchangers with the printed circuit, were first developed by the author of the present invention in the early 1980s, and their industrial production began in 1985 Core heat exchangers printed circuit often usually created by etching (or "chemical milling") channels, with all required forms and profiles on the surface of the individual plates, as well as bundling and diffusion connection of the plates to form cores having dimensions that are required for specific applications. Although the dimensions of the plates and channels may change considerably in order to meet, for example, the requirements for different modes of operation, environment, perform certain functions and operational characteristics, the plate can usually be made of heat-resistant alloy, e.g. the stainless steel and may have the following dimensions: width 600 mm, length 1200 mm and a thickness of 1.6 mm, the Individual channels in the respective plates can usually have a semicircular cross-section and a radial depth of about 1.0 mm

To attach the hearts reservoir for supplying fluid to the respective groups of channels in the core and from these groups of channels, and depending on, for example, from functional requirements and layout of the openings of channels collectors can be connected to any two or more of the six sides and surfaces of hearts.

The design of the cores of the heat exchangers with the printed circuit, or more precisely of heat exchangers includes a core, requires coordination of a number of factors (sometimes contradictory)that in the context of the present invention include the following:

1) providing the required thermal efficiency (boundary temperature) within the allowable pressure drops;

2) the process of minimizing the size and/or mass exchanger;

3) giving appropriate form of the core and/or layout of holes for groups of channels so as to facilitate normal supply of flowing fluids using conventional pipe/coupling devices.

In search of approaches that could be used to fulfill these requirements, was recently the setting, for minimizing the area of heat transfer, which is necessary for a given case, in order to comply with certain requirements relating to the specific operation mode, you must create a channel plate having high levels of sinuosity. However, the channels, which give such a configuration along their length to receive a significant tortuosity should be made shorter than those channels that have a lower level of sinuosity that could be provided constraints on the pressure drop.

Shortening channels usually will not create serious problems in the case of heat exchangers with cross flow. However, this will lead to reduction of heat transfer/use square plates in the case of more conventional heat exchangers associated with flow or opposing flow, which will inevitably have at least some of the plate (usually from 50% to 100% of the total number of plates), actually includes channels for control flow, providing the direction of incoming flow and outgoing flow of fluid to the orthogonal passing channels for passing flow and opposite the fluid flow to and from these channels. That is, if the length of the channels for passing flow or cross flow must be reduced, the area of the plates is occupied by the channels to cross the Otok, should be increased relative to the area occupied by the channels for passing or opposing flow. This leads to the requirement that the plate had a greater ratio of length to width, when it should be saved more common relative area, and if you ask require shorter channels to logical necessity smaller plates than those usually used in the cores of the heat exchangers with the printed circuit. This, in turn, leads to difficulties associated with the supply of flowing fluids using conventional pipe/coupling devices.

The invention

In the present invention an attempt is made to resolve the above-mentioned contradictory requirements by creating a core of the heat exchanger containing the first and second sets of alternating plates, which are arranged correspondingly to movement of the first and second fluid coolant. The plates are connected to each other and each of the plates in each group is formed, at least one of its surfaces, at least three plates, each of which contains a group of parallel channels. Through the first and second groups of plates are holes to move the first and second fluid coolant to the plates and from them, and the distribution is sustained fashion channels connect the opposite ends of each plate in each of the plates with the associated one of the holes. Distribution channels that are associated with each of the plates in plates of the first group are arranged such that they intersect with the distribution channels that are associated with the respective one of the plates in the plates of the second group, resulting in each of the plates in plates of the first group will be located in the heat exchanger in close proximity to a corresponding one of the plates in the plates of the second group.

The assertion that the distribution channels that are associated with each of the plates in plates of the first group are "so overlap with the distribution channels that are associated with the respective one of the plates in the plates of the second group, means that the corresponding distribution channels "cross" each other, without cooperation between them. Thus, in the context of the invention it is assumed that the word "cross" should be understood as "pass across" each other and not "pass through" each other.

In the case defined above, the composition of the core group of plates provided in each of a large number of large plates of normal size. The length of each of the plates may be selected to provide a high level of sinuosity of parallel channels, which form a plate, and, therefore, to ensure the optimizatio area of the heat exchange plates.

The core of the heat exchanger can be made so as to provide heat exchange between the three or more fluid environments, with at least some of the plates in each group are positioned to provide the movement of more than one fluid. However, for many, if not most, cases of application of the invention, the core of the heat exchanger to provide heat transfer only between the first and second fluid coolants.

At least some of the plates in one or the other of the two groups of plates can be formed with plates on both surfaces. However, in this case will also be necessary intermediate plate for rotation with the fins of the core, to prevent contact between different fluid coolants. However, it is desirable that each of the plates in each group was formed with the plates only in one of its surfaces.

Each of the channels in the multiple channel groups, which form the plates may be formed so as to give the tortuosity (i.e. create a tortuous path for the flow of fluid through the channel. This can be achieved in various ways, one of which involves the formation of each channel so that it followed a zig-zag path. When channels are formed thus, the expression "the parallel channels" should be understood as covering the layout of the channels, in which the projected path of the channels are parallel to each other.

Although, as indicated previously, each plate will have at least three plates, each plate will normally be from three to thirty plates. In addition, the plate can be placed in two groups and in this case, on each plate, in General, can be from six to sixty plates.

The channels within each of the plates can be formed so that they pass along the length of each of the plates, and in this case, the holes will pass through the upper and lower edges of the plates. However, preferably such formation of channels that they passed transversely through the plates and the holes were made along the marginal side portions of the plates. In the case when groups of parallel channels are arranged in two rows as possible as described above, holes can be made along the length of the plates four rows. Alternatively, if you use the Central location of the holes, so as to serve the opposite of a passing group of parallel channels, the holes are made along the length of the plates three rows.

Holes can be formed in the form of slits, all slots may be generally located within the boundaries of the plates. However, in the case of holes, the cat is who are near (side or end) of the edge portions of the plates, some or all of such holes can be formed as slits for lateral entry or end of input.

Edge portion of the holes, which are the distribution channels, to connect with the plates can be located at right angles to the parallel channels that form a plate that is parallel to the ends of the plates), or in the case of round holes will be bent. However, it is desirable that each of the edge parts, which are distribution channels, is tilted relative to the plates in order to minimize the length of the edges, from which depart distribution channels.

Plates can be connected to each other through any one of a number of processes such as welding, brazing or diffusion grip.

Thus according to one variant of the invention the proposed core heat exchanger, comprising: a) first and second sets of alternating plates, which are intended respectively to move the first and second fluid coolant, and the plates are connected to each other and each of the plates in each group performed, at least one of its surfaces, at least three plates, each of which contains a group of parallel channels, (b) holes passing through the first and the second is the group of plates to move the first and second fluid coolant to the plates and from them, (C) distribution channels connecting the opposite ends of each plate in each of the plates with the associated one of the holes, with distribution channels that are associated with each of the plates in plates of the first group are arranged in such a way that overlap with the distribution channels that are associated with the respective one of the plates in the plates of the second group, whereby each of the plates in plates of the first group is providing the heat transfer near the location of the corresponding one of the plates in the plates of the second group.

Preferably, the plate is made only in one surface of each of the plates of each group.

Preferably, the plates of the first and second groups sequentially alternate.

Preferably, at least in most parts of the plates most holes are connected distribution channels with two adjacent slices.

Preferably, the holes in the opposite ends of each plate are arranged without centering.

Preferably, all of the holes pass through all of the plates of both the first and second groups of plates.

Preferably, each of the parallel channels each of the plates is designed to provide winding p is t for flowing coolant.

Preferably, each of the parallel channels is designed to follow a zig-zag path.

Preferably, the plate of each group in one of its surfaces with a number of adjacent plates from three to thirty.

Preferably, the plate consists of parallel channels by number, from twenty to forty.

Preferably, each plate in plates of the first group has a size and shape essentially the same as the size and shape of each respective plates in plates of the second group.

Preferably, each plate in plates of the first group is positioned in such a way that overlaps each corresponding record in the plates of the second group.

Preferably, the group of parallel channels that make up each record takes place in the transverse direction through the plate containing the record.

Preferably, the plates in each plate are parallel to each other and arranged in one row.

Preferably, the plates in each plate are parallel to each other and arranged in two parallel rows.

Preferably, each row contains between three and thirty of adjacent plates.

Preferably, each of the plates is made with six passing in the longitudinal direction of the rows of holes, the first of which is in the plate in the center, the second and third are located in the respective side edges of the plate, the fourth and fifth of which contain holes, which pass inward from the respective side edges of the plate, and the sixth of which is located at the center of the plate and intersects with the holes of the first row.

Preferably, the first and sixth rows of holes are accessible from the opposite end surfaces of the core.

Preferably, the second and third rows of holes available with one of the end surfaces of the core.

Preferably, the fourth and fifth rows are available respectively from opposite side surfaces of the core.

Preferably, the corresponding holes of the first, fourth, and fifth rows centered in the transverse direction of each plate, and the corresponding holes of the second, third, and fifth rows centered in the transverse direction of each plate.

Preferably, the first row of holes is when they are used to ensure the input stream of the first fluid coolant, the second and third rows of holes are designed when using them to ensure that the output stream of the first fluid coolant, the fourth and fifth rows of holes are used when they are used to ensure the input stream of the second fluid coolant, the sixth of radamisty is when it is used to provide an output flow of the second fluid coolant.

Preferably, each of the holes has an edge portion which is inclined with respect to related records.

Preferably, all of the plates are connected with each other by diffusion.

Preferably, all of the channels and distribution channels have essentially the same shape and dimensions of the cross section.

Preferably, each of the distribution channels is connected directly with an associated one of the channels, which forms a record.

According to another variant of the invention is proposed a heat exchanger comprising at least one above the heart.

Preferably, the heat exchanger contains a reservoir connected to the core to move the first and second fluid coolant to the core and from it.

According to other variant is proposed a heat exchanger Assembly comprising at least two above the core.

Preferably, the cores are attached to the rear side to the rear side, and the collectors are connected to the Assembly for moving the first and second fluid coolant to the core.

Preferably, the core linearly combined with lengths and orientations selected in such a way that when the core when using them undergo the deformation caused by nahrawan who eat creates a compound bend in such a way that the normal to the Central points of the end surfaces of the United hearts remain essentially collinear.

The invention will be better understood from the following description of preferred embodiments of the cores of the heat exchangers, which provide opposing the passage of the two fluids are fluids. In the description made with reference to the accompanying drawings.

Brief description of drawings

In the drawings shows the following:

figure 1 presents a schematic representation of the elementary core;

figure 2 presents two groups of three plates remote from the heart;

figure 3 presents the individual plates of the respective groups shown in figure 2;

figure 4 presents less schematic illustration of the core with a large number of wafers;

figure 5 presents two consecutive plates remote from the core according to figure 4;

figure 6 on an enlarged scale shows a part of the plates according to figure 5;

figure 7 presents a schematic representation of two successive plates for the alternative composition of the core;

on Fig presents front side of the core, which includes plate according to Fig.7;

figure 9 shows the rear side of the core according Fig;

figure 11 presents the lower end part of one of the plates remote from the core according pig and 9;

on Fig presents (in a contour image) view in perspective of the upper part of the assembled heat exchanger, which includes two core of this type, which are shown in Fig and 9, but for illustrative purposes, some collectors deleted;

on Fig schematically shows an end view of a cylindrical vessel containing eight heat exchangers, each of which contains three linearly combined core of the type indicated above;

on Fig presents a view in plan, and schematic again, one of the heat exchangers, when viewed in the direction of the arrows 12-12 in Fig when it is subject to deformation caused by exposure to heat;

on Fig and 16 presents a view similar to the view of Fig, but with different layouts Association of cores of the heat exchangers.

Detailed description of preferred embodiments of the invention

As shown in figures 1, 2, 3, the core 10 of the heat exchanger contains a wide array of plates 11 and 12, which by means of diffusion are in contact, the surface-to-surface between the end plates 13 and 14. All of the plates 11 and 12 may be made of stainless steel and have a thickness of the inu 1.6 mm

Plates 11 and 12 are trying to enter into two groups 15 and 16 of alternating plates P1P2, R3, R4---- RnPn+1while appropriate groups 15 and 16 of the plates are designed by using them to move the first and second (opposite) of fluid coolants F1and F2.

Each of the plates 11 in one of its surfaces made with many theoretically separate groups of parallel channels, which form the plates 17. Each of the plates 17 (that is, each group of parallel channels) passes transversely through the respective plate, and the opposite ends of each of the plates 17 are holes 18. In addition, the group's distribution channels 19 formed in each of the plates 11 to provide a direct passage of fluid between the respective holes 18 and the associated one of the plates 17.

Similarly, each of the plates 12 is made in one of its surfaces with multiple groups of parallel channels, which form the plates 20. In this case, the plate 20 also pass transversely through the plate 12 and the holes 21 are located at opposite ends of each of the plates 20. Direct connection for the passage of fluid between the holes 21 and the respective associated layer is kami 20 provided with groups of distribution channels 22.

The group's distribution channels 19 and 22 in the respective groups of plates 11 and 12 are overlapping (as defined previously). Therefore, they are placed so that the plate 17 in the plates 11 will be providing closure and heat transfer near the location relative to the plates 20 in the plate 12, so that will ensure proper thermal contact between the fluid heat carriers F1 and F2.

Two groups of holes 18 and 21 pass through all of the plates 11, 12, 13 and 14 to provide communication with the interior of the core 10 of the two flowing fluids F1 and F2. Plate, through which the respective liquids are determined by the relevant groups of distribution channels 19 and 22. Collectors (not shown) are attached to the core for supplying a fluid coolant to the core and from it.

The layout shown in figure 1, 2, 3 with four clearly defined groups of parallel channels or plates 17 and 20 in the plates 11 and 12, respectively, is intended only to illustrate the General concept of the invention. A more realistic picture of the plates 11 and 12 are presented in figure 5.

As shown in figure 5, a separate plate 17 differ from each other only in respect of oppositely located distribution channels 19, which are connected with the respective ends of them from the plates. Similarly, the plates 20 are different from each other in respect of oppositely located distribution channels 22, which are connected with the respective ends of one of the plates.

The number of plates 17 and 20 within their respective plates 11 and 12 reduced to an absolute minimum, as shown by the location of the holes 18 and 21 so that they close distance from each other, and connecting opposite ends of each of the plates 17 and 20 with step-arranged some of the holes.

Each plate 11 and 12 has a size of 600 mm to 1200 mm, while it is made with ten-twenty plates 17 and 20, and contains approximately twenty to forty separate, parallel channels 23 in each plate. Each channel 23 may have a semicircular cross-section and a radial depth of about 1.0 mm, while the adjacent channels can be separated by a rib or strip having a width of 0.5 mm, However, it will be clear that all of these numbers and sizes can be significantly changed depending on the application the core of the heat exchanger.

As shown in Fig.6, each of the channels 23 passes through the zigzag path, and it will be clear that to the extent described here, the channels are parallel, their projected path 24 are parallel to each other.

7-9 presents the alternative is for the layout of the core, in which the plates 11 and 12 made two vertical rows of closely compacted, passing through the horizontal plates 25 and 26. Each of the plates 25 and 26 are similar to the corresponding plates 17 and 20, which are shown in figures 1, 2, 3, but in the case of the variant of the design shown in Fig.7-9, made six groups are arranged vertically holes to move the fluid of the fluids F1 and F2 to the respective plates and from them.

As shown in Fig.7-9, a fluid coolant F1served to the core 10 and the plates 25 by means of a single group of spaced vertical holes 28 and groups 29A distribution channels. The same fluid coolant moves from the core through groups 29V distribution channels and two groups of spaced vertical holes 27. Similarly, fluid coolant F2served to the core and the plates 26 by means of the two groups of spaced vertical holes 30 for lateral entry and groups 32A distribution channels and moves from the core through groups 32V distribution channels and teams located vertical hole 31.

To connect the desired number of inlet and outlet manifolds (not shown) of holes 27, 28 and 31 are as holes for end of input, while the hole is ment 30 runs as a hole for the side entrance. As in the case of the previously described embodiment of the invention, all the holes pass through all of the plates 11 and 12.

Figure 10 in an enlarged scale shows a typical implementation of the lower end part of one of the plates 11 in the embodiment of the invention according to Fig.7-9, and figure 11 similarly illustrates a lower end part of one of the plates 12.

Figure 10 is best shown (when considered together with Fig and 9)that the fluid F1comes in a hole 28 in the plate 11, is held in the corresponding group distribution channels 29A, through oppositely passing of the plate 25, through the group's distribution channels 29 and out through the openings 27. Because successive plates 11 and 12 provide movement of different fluid F1and F2and all of the holes pass through all of the plates, for maximizing the usable space of the hole and distribution channels are placed in such a manner that fluid flowing in each direction (left and right) from a single (full) holes 28, splits and exits through two spaced at vertical openings 27. Similarly, as best seen in figure 11, the fluid F2included in holes 30 in the plate 12, is held in the corresponding groups spread is lnyh channels 32A, after passing opposite plate 26, through the group's distribution channels 32V and exits through holes 31. In this case, holes and distribution channels are arranged in such a manner that fluid flowing inward from each of the single holes 30 for lateral entry, split and exits through two situated at a distance from each other vertically and located at the center of the hole 31.

All of the holes 18, 21, 27, 28, 30 and 31 have edge parts 33 and 34 (shown on figure 10 and 11), which are distribution channels that are inclined relative to their associated plates so as to maximize the length of the edges, from which depart distribution channels.

In the case of the above layouts core heat transfer fluid will be directed into the core, and through it in such a way as to provide a practically uniform temperature distribution along the longitudinal axis of the core. Thus, the present invention allows to avoid or at least reduce, the stress created by bending, which is characteristic of a well-known heat exchangers. Such bending occurs due to the presence of a temperature gradient and leads to different thermal expansion along the length of the core. In addition, in the case of the composition of cores that show is on 7-9, two of the core 10 can be attached to the front side (or rear side), which is somewhat schematically shown in Fig, and separated by barriers 35. This may be placed a single collector device (not shown) for supplying a fluid coolant F1to the Central zone 36 layout with two hearts and to move the fluid F1from the sides 37 of the layout with two hearts. In addition, the reservoir 38 can be easily attached to the four side layout with two hearts for supplying the fluid F2to appropriate plates of the two hearts, and the reservoir 39 may be connected to the rear sides of the two hearts to move the fluid F2from the device with two hearts.

Passing through the vertical design, which is shown in Fig, contains only one layout, which can be performed invention, however, it provides the usual four or six pages with two hearts around a common vertical axis. In addition, in the construction shown in Fig can be performed changes. For example, in each of the holes 28 and 31 may be located Central wall or jumper (not shown), and some of the edge (end) of the plates in the core, which passes fluid can be formed with approximately half the number of plates, forming the channels, when the rest of the plates in the core serves to provide equalization of heat flow between the plates in the core.

As another possible layout many of cores 10 can be combined linearly (i.e. next to each other), as schematically shown in Fig, and many heat exchangers 40, is designed, can be placed inside a cylindrical tank 41. As shown, the assembled core and the reservoir are in the longitudinal direction.

A potential problem with the device, which was presented on Fig, is that when it is subjected to normal operating heat, there is a tendency to bend each of the heat exchangers 40 (banana shaped) so that the extreme end surface of the assembled core will be displaced from their normal parallel position relative to each other. This creates problems relating to capacity and/or connections.

However, it should be noted that these problems can be solved by combining the core 40A and 40B having a different length, and by the orientation of the core relative to each other in such a way that will create compound curves and normal to the Central points of the end surfaces of these United Serdtsev who will remain essentially collinear. On Fig, 15 and 16 shows three examples of the combined layouts that can be obtained using for this purpose four core 40A-40D of the heat exchanger. In these examples, the cores 40A-40D uses the same design plates; core 40A has the same length as the core of the 40S, the core 40B has the same length as the core of the 40D, and the core 40A and 40C are half the length of the core 40B and 40D; core 40A differs from the core 40C and the core 40B differs from the core 40D only the orientation and direction of flow of a fluid coolant.

1. The core of the heat exchanger containing:
a) first and second sets of alternating plates, which are intended respectively to move the first and second fluid coolant, and the plates are connected to each other and each of the plates in each group performed, at least one of its surfaces, at least three plates, each of which contains a group of parallel channels,
b) holes passing through the first and second groups of plates to move the first and second fluid coolant to the plates and from them,
c) distribution channels connecting the opposite ends of each plate in each of the plates with the associated one of the holes, with distribution channels that link the Ana with each of the plates in plates of the first group, are arranged in such a way that overlap with the distribution channels that are associated with the respective one of the plates in the plates of the second group, whereby each of the plates in plates of the first group is providing the heat transfer near the location of the corresponding one of the plates in the plates of the second group.

2. The core of the heat exchanger according to claim 1, in which the plate is made only in one surface of each of the plates of each group.

3. The core of the heat exchanger according to claim 2, in which the plates of the first and second groups sequentially alternate.

4. The core of the heat exchanger according to claim 2, in which, at least in most parts of the plates most holes are connected distribution channels with two adjacent slices.

5. The core of the heat exchanger according to claim 1, in which holes located at opposite ends of each plate are arranged without centering.

6. The core of the heat exchanger according to claim 1, in which all of the holes pass through all of the plates of both the first and second groups of plates.

7. The core of the heat exchanger according to claim 1, in which each of the parallel channels each of the plates is designed to provide a tortuous path for fluid coolant.

8. The core of the heat exchanger according to claim 7, in which the each of the parallel channels are thus to follow a zig-zag path.

9. The core of the heat exchanger according to claim 1, in which each plate of each group in one of its surfaces with a number of adjacent plates from three to thirty.

10. The core of the heat exchanger according to claim 1, in which each record consists of parallel channels by number, from twenty to forty.

11. The core of the heat exchanger according to claim 1, in which each record in the plates of the first group has a size and shape essentially the same as the size and shape of each respective plates in plates of the second group.

12. The core of the heat exchanger according to claim 11, in which each record in the plates of the first group is positioned in such a way that overlaps each corresponding record in the plates of the second group.

13. The core of the heat exchanger according to claim 1, in which the group of parallel channels that make up each record takes place in the transverse direction through the plate containing the record.

14. The core of the heat exchanger according to claim 1, in which the plates in each plate are parallel to each other and arranged in one row.

15. The core of the heat exchanger according to claim 1, in which the plates in each plate are parallel to each other and arranged in two parallel rows.

16. The core of the heat exchanger 15 in which each row of sod is rgit between three and thirty of adjacent plates.

17. The core of the heat exchanger 15 in which each of the plates is made with six passing in the longitudinal direction of the rows of holes, the first of which is in the plate in the center, the second and third are located in the respective side edges of the plate, the fourth and fifth of which contain holes, which pass inward from the respective side edges of the plate, and the sixth of which is located at the center of the plate and intersects with the holes of the first row.

18. The core of the heat exchanger 17 in which the first and sixth rows of holes are accessible from the opposite end surfaces of the core.

19. The core of the heat exchanger 17 in which the second and third rows of holes available with one of the end surfaces of the core.

20. The core of the heat exchanger 17 in which the fourth and fifth rows are available respectively from opposite side surfaces of the core.

21. The core of the heat exchanger 17 in which the corresponding holes of the first, fourth, and fifth rows centered in the transverse direction of each plate, and the corresponding holes of the second, third, and fifth rows centered in the transverse direction of each plate.

22. The core of the heat exchanger 17 in which:
the first row of holes is when you use them to about the level of the input stream of the first fluid coolant,
the second and third rows of holes are designed when using them to ensure that the output stream of the first fluid coolant,
the fourth and fifth rows of holes are used when they are used to ensure the input stream of the second fluid coolant,
a sixth row of holes is when it is used to provide an output flow of the second fluid coolant.

23. The core of the heat exchanger according to claim 1, in which each of the holes has an edge portion which is inclined with respect to related records.

24. The core of the heat exchanger according to claim 1, in which all the plates are connected with each other by diffusion.

25. The core of the heat exchanger according to claim 1, in which all of the channels and distribution channels have essentially the same shape and dimensions of the cross section.

26. The core of the heat exchanger on A.25, in which each of the distribution channels is connected directly with an associated one of the channels, which forms a record.

27. The heat exchanger includes at least one core according to any one of the preceding paragraphs.

28. Heat exchanger according to item 27, comprising a reservoir connected to the core to move the first and second fluid coolant to the core and from it.

29. The heat exchanger Assembly, in the with in themselves, at least two core according to any one of claims 1 to 26.

30. The heat exchanger Assembly according to clause 29, in which the core is fastened to the back of the rear side, and the collectors are connected to the Assembly for moving the first and second fluid coolant to the core.

31. The heat exchanger Assembly according to clause 29, in which the core combined linearly, with lengths and orientations selected in such a way that, when the core of their use are subjected to deformation caused by heat generated compound bend in such a way that the normal to the Central points of the end surfaces of the United hearts remain essentially collinear.



 

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EFFECT: improved efficiency of operation of heat exchanger.

2 cl, 7 dwg

FIELD: agriculture: heat engineering equipment for poultry and stock-rearing.

SUBSTANCE: the invention is dealt with the field of agricultural heat engineering equipment ensuring a heat transfer from one heat-exchanger to another in presence of aggressive corrosion-influencing components in one of them. The equipment may be used in the gas-air ventilation facilities of heat recovery in poultry and stock-rearing farms. The method of production of a cross-running heat exchanger out of a polymeric material containing a package made out of polymeric cellular plates bound to each other and encased in a box ensuring an inlet and an outlet of warm and cool air streams. At that the cellular plates located in one direction in a package are bound to each other by a two-sided polymeric adhesive tape through gaskets made out of the same polymer and placed along the surface and perpendicularly to directions of cells in a plate, are kept till full polymerization of the joints with following formation of the package on all its corners with metal angle sections into a rigid metal framework. At that in one of the vertical sides of the angle section they drill some bores ensuring a free running of a liquid. Then using a sliding fit the package is inserted in the guides made out of the angle sections and mounted perpendicularly to the corners of the air-distributive box so, that the bores of the lower corner of the package meet the bores of a lateral wall of a guide. The package is fixed in the guides formed by the metal angle sections. The bores of the lower angle section of a guide should be located opposite to the bores drilled-in in the lower wall of the air channel of the box placed above a draining container. The invention ensures the necessary tightness of the channels linking the heat exchangers, possibility to use the heat exchangers at low temperatures and also to increase the cost efficiency of the polymeric material cutting.

EFFECT: the invention ensures the necessary tightness of the channels linking the heat exchangers, possibility to use the heat exchangers at low temperatures and increased the cost efficiency of the polymeric material cutting.

2 dwg

The invention relates to heat-exchange equipment, implements the exchange of thermal energy between the two working environments through the wall, and can be used in ventilation systems and air conditioning for the heat exchange between the supply air and exhaust air

The invention relates to shipbuilding, and directly to the ship exchangers for heating of supply air

The heat exchanger // 2052757
The invention relates to a surface gas-liquid or gas-air heat exchangers, such as a regenerator for gas turbine engines

The heat exchanger // 2047076
The invention relates to a heating engineer, and in particular to heat exchangers, such as radiators, cooling systems of internal combustion engines
The invention relates to heat exchangers in which the channels for the coolant is formed by a plate separating the two media, i.e

FIELD: agriculture: heat engineering equipment for poultry and stock-rearing.

SUBSTANCE: the invention is dealt with the field of agricultural heat engineering equipment ensuring a heat transfer from one heat-exchanger to another in presence of aggressive corrosion-influencing components in one of them. The equipment may be used in the gas-air ventilation facilities of heat recovery in poultry and stock-rearing farms. The method of production of a cross-running heat exchanger out of a polymeric material containing a package made out of polymeric cellular plates bound to each other and encased in a box ensuring an inlet and an outlet of warm and cool air streams. At that the cellular plates located in one direction in a package are bound to each other by a two-sided polymeric adhesive tape through gaskets made out of the same polymer and placed along the surface and perpendicularly to directions of cells in a plate, are kept till full polymerization of the joints with following formation of the package on all its corners with metal angle sections into a rigid metal framework. At that in one of the vertical sides of the angle section they drill some bores ensuring a free running of a liquid. Then using a sliding fit the package is inserted in the guides made out of the angle sections and mounted perpendicularly to the corners of the air-distributive box so, that the bores of the lower corner of the package meet the bores of a lateral wall of a guide. The package is fixed in the guides formed by the metal angle sections. The bores of the lower angle section of a guide should be located opposite to the bores drilled-in in the lower wall of the air channel of the box placed above a draining container. The invention ensures the necessary tightness of the channels linking the heat exchangers, possibility to use the heat exchangers at low temperatures and also to increase the cost efficiency of the polymeric material cutting.

EFFECT: the invention ensures the necessary tightness of the channels linking the heat exchangers, possibility to use the heat exchangers at low temperatures and increased the cost efficiency of the polymeric material cutting.

2 dwg

FIELD: gas turbine construction.

SUBSTANCE: matrix can be used in heat exchangers of heat regeneration heat system's exchanger, as well as for warming up (cooling down) gas or liquid in different heat-sing installations. Matrix of ring-shaped lamellar heat exchanger has heat-exchange members formed by lamellar plates with corrugated parts and openings of collectors, which are connected by means of lugs of internal and external diameters of plates or by means of lugs of collectors. Corrugated parts and collectors are limited by internal and external diameters of ring-shaped plate, or by lines being equidistant to them, and by frontal planes being parallel to axis of symmetry of corrugated parts. Axes of symmetry of any part and of collectors pass through center of plate. Angles between frontal planes of distributing and gathering collectors are equal to each other. Vertexes of angles are disposed at concentric circles having the same or different radiuses. Area of distributing collector relates to gathering collector is directly proportional to relation of corresponding radiuses of vertexes of angles and belongs to 0,4-0,8 interval.

EFFECT: improved efficiency of operation of heat exchanger.

2 cl, 7 dwg

FIELD: mechanical engineering; air conditioning and ventilation.

SUBSTANCE: invention relates to heat exchange devices used in air conditioning and ventilating plants, namely, to methods of evaporating cooling to dew point and to plate devices for evaporative cooling. According to invention, plates of plate device are made so that channels and perforation to pass from dry side to wet side can be at least partially wetted with evaporating liquid. Chute is provided made in part of plates which temporarily holds evaporating liquid in contact with wick material on surface of wet side of plate. Evaporating liquid flows along chute through perforation for liquid into following chute. When chute of plate from wet side is from above, perforation for liquid is on side forming reservoir for wetting opposite wick materials. When flow move along dry side, heat is conveyed to plate. In proposed method several heat transfer plates are used. Said plates have wet and dry sides and they form chutes. Plates are wetted form wet sides with evaporating liquid and they pass separately two flows, namely, working and product ones through dry sides. Flow of working gas passes along dry side and gets through perforation into channels on wet side which is cooled owing to evaporation, thermal conductivity of plate and its heat radiation.

EFFECT: provision of more effective air flow and heat transfer owing to evaporative cooling with intermediate coolant.

Heat exchanger // 2334929

FIELD: heating.

SUBSTANCE: invention is referred to thermal engineering and may be used in district heating systems for heating service water. Heat exchanger contains primary circuit channel located between inlet and outlet connections, secondary circuit channel located between supply pipeline assembly and return pipeline assembly, heat-conducting device between primary circuit channel and secondary circuit channel, and temperature sensor. Temperature sensor is located between secondary circuit channels close to connection with return pipeline. Besides, temperature sensor contacts with heat-conducting device or situates at small distance from it.

EFFECT: space saving in heat exchanger when temperature is measured and good results are achieved.

7 cl, 5 dwg

Heat exchanger core // 2357170

FIELD: heating systems.

SUBSTANCE: inventions are intended for heat exchange, and can be used for heating heat carriers. Heat exchanger core consists of two groups of alternating plates. The latter are connected to each other and each plate in each group is made at least in one of its surfaces at least with three platelets, each of which consists of a group of parallel channels, holes passing through the first and second group of plates for transferring fluid heat carriers to the platelets and from them, and distributing channels connecting opposite ends of each platelet in each of the plates to some of the holes related thereto. Distributing channels that are connected to each of the platelets in the plates of the first group are located so that they cross the distributing channels that are connected to some of the appropriate platelets in the plates of the second group. Heat exchanger can include at least one core. Heat exchanger can include headers connected to the core. Heat exchanger can include at least two cores. In heat exchanger the cores are attached rear side-to-rear side, and headers are connected to assembly for transferring fluid heat carriers to the cores and from them.

EFFECT: providing required thermal efficiency, and decreasing dimensions and mass of heat exchanger.

31 cl, 16 dwg

FIELD: heating.

SUBSTANCE: invention is of relevance for operation of apparatus for air cooling of gas and is to be utilised in power engineering industry. The proposed method of the heat exchanger apparatus fabrication envisages the following activities: fabrication of finned heat exchange tubes, a framework, at least a single apparatus section with lateral walls and beams joining them together, gas inlet and outlet chambers; packing the section with a bundle of finned one-way-flow heat exchange tubes; fabrication of a manifold for gas supply and removal, a support structure and their assembly. The section walls are represented by channel bars with shelves turned towards the tubes and are equipped with fairing displacers forming the U-bar reinforcement ribs. One of the methods of the apparatus heat exchanger section fabrication envisages positioning an optimal number of tubes within the section in accordance with the dependence specified within the framework of the invention concept. An alternative method envisages assembly of the section elements on a holding frame designed within the framework of the invention concept. A third method envisages assembly of the elements in a specific sequence combined with performance of hydraulic pressure testing. The method of fabrication of the apparatus chamber for gas inlet or outlet envisages manufacture of the chamber elements and their assembly in a sequence developed within the framework of the invention concept. The method of fabrication of the gas delivery and removal manifold envisages manufacture of the manifold body sections and their assembly with the help of the tool tab designed within the framework of the invention concept. Method of hydraulic pressure testing of the apparatus sections envisages mounting the section to be tested on the hydraulic test bench designed within the framework of the invention concept with the pressure increase and drop modes as per the dependence given. Method of the manifold hydraulic pressure testing envisages it being mounted on the hydraulic test bench or a loft with the help of support structures designed within the framework of the invention concept.

EFFECT: enhanced effectiveness and precision of assembly of the apparatus and elements thereof combined with reduction of labour and material consumption, reduction of hydraulic losses occurring in the apparatus as well as technological simplification of the hydraulic pressure testing of heat exchanger sections and manifolds of the apparatus for air cooling of gas, improved effectiveness and reduced labour intensity of their performance.

25 cl, 30 dwg

FIELD: heating.

SUBSTANCE: proposed multi use plate of the plate heat exchanger contains the following: the extreme and middle parts, lying in the first plane; the rib, mating these parts, the middle of which lies in the second plane parallel to the first; the first and the second pairs from the first and the second holes same in size on the opposite sides of the middle part. These pairs of holes are positioned mirror-wise relatively to the transverse axis, passing in the first or the second plane equidistantly between the pairs of holes; at that the first and the second hole in each of these pairs of holes are formed in the sections of the middle part, lying respectively in the first and the second planes; the entire space of the middle part between the sections with holes is occupied by alternating recesses and protruberances, at that the recesses bottom and the protuberances tops are lying respectively in the first and the second planes. The package assembly of such plates consists in consequent plates packing one by one with the similar planes with the rotation of each even or each odd plate by 180 relatively to the transverse axis, after that provide the plates welding in the contact places of their similar planes. The turbulizing elements can be placed in some of the forming cells, that allows to change the hydro-gasdynamic and heat-mass exchange characteristics of the working channels.

EFFECT: operating means range expansion.

8 cl, 3 dwg

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