Modular vortex heat exchanger

Abstract

FIELD: heat engineering.SUBSTANCE: heat exchangers with recuperative heat transfer can be used in the chemical, food and related industries. A modular vortex heat exchanger containing adjacent coaxial vortex chambers formed by flat cover disks and a central horizontal flat element - a heat exchange surface, cylindrical rings clamped between the flat cover disks and the central flat element, inlet and central outlet pipes of the vortex chambers, is characterized in that it contains two or more heat exchange modules based on vortex chambers, wherein the central flat element is the base and heat exchange surface for all heat exchange modules. The inlet pipes of the vortex chambers are angular and are placed on flat cover discs at radii from 0.7 to 0.9° of the radius of the vortex chamber. The axes of the inlet pipes form an angle of 30 to 45° with the plane of the cover discs. The projections of these axes onto the cover disks are perpendicular to the radii of the vortex chambers. The lower vortex chambers, connected to each other in series by tubes, and the upper vortex chambers, connected to each other in the same way, are arranged on the base so that the first vortex chamber in the direction of movement of the hot coolant has the last vortex chamber in the direction of movement of the cold coolant, acting as an adjacent vortex chamber along the heat exchange module, and the last vortex chamber in the direction of movement of the hot coolant has the first vortex chamber in the direction of movement of the cold coolant, acting as an adjacent vortex chamber along the heat exchange module. This ensures counter-current movement of coolants. The preferred number of modular heat exchange elements is from 2 to 7. All vortex chambers of the modular elements are of the same shape and dimensions, and the diameter-to-height ratio is in the range from 5 to 20. The installation of the inlet pipes of the vortex chambers ensures that the direction of rotation of the coolant flows in all lower and all upper vortex chambers is in opposite directions. The base with the modular heat exchange elements installed can be rectangular, square, round or other in shape.EFFECT: increase in the degree of heating (cooling) of the coolant and an increase in the amount of heat transferred by the apparatus.7 cl, 6 dwg, 4 tbl

Description

[0001] This invention relates to heat engineering, specifically to heat exchangers with recuperative heat transfer, and can be used in the chemical, food, and related industries. This device is most effective at moderate to medium coolant flow rates.

[0002] A "Spiral Heat Exchanger" [1] is known, comprising a housing with a two-channel heat exchange element installed inside, inlet and outlet pipes, the cavities of which are connected with the corresponding cavities of the heat exchange element. The inlet and outlet pipes are mounted on the upper and lower flat covers of the housing. The flat covers are attached to the housing with studs. The two-channel heat exchange element of the apparatus is designed as a two-pass cylindrical spiral. Its central and peripheral parts are interconnected, while the twisted profiled cavity formed by the turns of the first pass is connected to the inlet and outlet pipes of the first coolant, and the twisted profiled cavity formed by the turns of the second pass is connected to the inlet and outlet pipes of the second coolant. Rotational movement of both coolants along helical trajectories ensures intensification of heat transfer between them.

[0003] Spiral heat exchanger [1] has the following disadvantages.

[0004] - Firstly, the device is difficult to manufacture. The device's dual-channel heat exchange element is designed as a double-threaded cylindrical coil and must be hermetically sealed to both the central pipe and the housing surface. High-quality welding to the central pipe is possible, but welding to the housing from the inside is difficult (only possible for larger devices).

[0005] - Secondly, the central pipe does not participate in the heat exchange process, since coolants do not pass through it.

[0006] Also known as a "Spiral Heat Exchanger" [2], this type of heat exchanger comprises two circuits separated by a metal wall, with spiral channels for the flow of hot and cold coolant. The heat exchanger is distinguished by its composition, consisting of two profiled panels placed on both sides of a flat metal sheet, with the channels of each circuit formed by the combined surfaces of the panel and the sheet. The channels of each circuit have a semicircular cross-section. The profiled panels and the flat sheet are fastened with bolts and nuts. The flat metal sheet serves as the heat exchange surface.

[0007] The disadvantage of this unit is the complexity of manufacturing due to the geometry of the profiled panels—special equipment is required for stamping them. Furthermore, the flat metal sheet is only partially bathed by the hot and cold coolant—the surface between the spiral channels is not involved in the heat exchange process.

[0008] A "Vortex Heat Exchanger" is known from work [3]; it contains two adjacent coaxial vortex chambers formed by three flat disks, the outer disks of which serve as covers, and the middle disk is the heat exchange surface, two cylindrical rings clamped between the disks, and inlet and outlet pipes located tangentially on the cylindrical rings and in the center of both covers. The diameters of both vortex chambers are the same. The chamber of the first coolant has a tangential pipe and a pipe in the center of the flat cover. The chamber of the second coolant also has a tangential pipe and a pipe in the center of the flat cover.

[0009] Two cylindrical rings with tangential connections are clamped between flat disc-shaped covers with central connections using studs. A heat exchange disk is located between the cylindrical rings. Gaskets ensure a tight seal. The unit can be made of steel or another metal. The unit has an exceptionally simple, disassemblable design.

[0010] The vortex heat exchanger [3] operates as follows.

[0011] The first (hot) coolant is fed into the tangential port of the cylindrical ring of the first vortex chamber, rotates and translates within the chamber, and exits through the central port. The second (cold) coolant is fed through the tangential port of the cylindrical ring of the second vortex chamber. It exits through the central port.

[0012] It is possible to supply a second coolant through the central nozzle; however, this operating option is less preferable. Tangential coolant supply in the chambers results in more intense fluid rotation, better vortex formation, and more intense heat exchange.

[0013] During operation, heat is transferred through the heat exchange disk from the hot to the cold coolant. The rotational and reciprocating motion of the coolants within the chambers is accompanied by vortex formation and turbulence, which significantly intensifies heat transfer. The rotational speed of the coolant in the vortex chamber determines the heat transfer rate α. To increase it, simply increase the velocity in the inlet pipe. Intensified heat transfer in both chambers leads to an increase in the overall heat transfer coefficient K realized in the device.

[0014] This device is the closest in technical essence and achieved result to the proposed technical solution.

[0015] The vortex heat exchanger [3] (prototype) is characterized by increased values ​​of heat transfer coefficients K, however, the advantages of the device are limited by a number of reasons.

[0016] Firstly, the device does not ensure sufficiently complete thermal contact between the coolants. The device's vortex chambers are hollow, and the coolants mix in all directions, including radially toward the central outlet pipe. Due to this flow arrangement, some of the coolant passes through the vortex chamber without adequate contact with the heat exchange surface F. While ideal mixing is not achieved in the vortex chamber, the extent of thermal contact is limited to a relatively small number of rotations of each microvolume of liquid (usually 3-5 revolutions) before it exits the chamber. Since the extent of thermal contact is limited, more complete heating (or cooling) of the coolant does not occur. As a result, the device's thermal efficiency is insufficiently high. when heating (cooling) the coolant.

[0017] Thermal efficiency is called the ratio of the heat flow of the apparatus under consideration Q to the ideal heat flow , which can transfer the heating coolant under ideal conditions [4, p.129], when the apparatus K = , which is only possible in theory.

[0018] Secondly, the heat exchange surface of the device The size of the disk is limited by its permissible dimensions. To increase the heat transfer surface, the diameter of the vortex chambers D must be increased. However, a disk with a larger diameter resists the pressure in the vortex chamber less effectively, and to ensure strength, it must have a greater thickness S, which is undesirable due to increased metal consumption and increased thermal resistance. A limited heat transfer surface reduces the amount of heat transferred by the device.

[0019] Thirdly, with tangential inlet ports on the cylindrical rings of the vortex chambers, connecting the vortex chambers to each other is structurally difficult and impractical, and the size of these ports is limited by the height of the chambers, which can limit the flow rate of the supplied coolant. Consequently, the thermal efficiency and thermal power of the unit are limited.

[0020] The tasks that the claimed invention is aimed at solving are to increase the thermal efficiency of the apparatus and to increase its thermal power.

[0021] The technical result of using the proposed design consists in increasing the degree of heating (cooling) of the coolant and in increasing the amount of heat transferred by the device.

[0022] The technical result is achieved due to the fact that in a modular vortex heat exchanger, containing adjacent coaxial vortex chambers formed by flat disk covers, and a central horizontal flat element - a heat exchange surface, cylindrical rings secured between the flat disk covers and the central flat element by means of studs, containing inlet and central outlet nozzles of the vortex chambers, two or more heat exchange modules based on vortex chambers are provided. The central flat element serves as a common base and heat exchange surface for all heat exchange modules. The inlet nozzles of the vortex chambers are angular and are located on the flat disk covers at radii ranging from 0.7 to 0.9 of the vortex chamber radius. The axes of the inlet pipes form an angle β of 30 to 45° with the plane of the disk-covers, while their projection onto the disk-cover is perpendicular to the radius of the vortex chamber.Lower vortex chambers, connected sequentially by tubes, and upper vortex chambers, connected sequentially by tubes, are arranged on a base such that the first vortex chamber in the direction of hot coolant flow is adjacent to the last vortex chamber in the direction of cold coolant flow, along the heat exchange module, while the last vortex chamber in the direction of hot coolant flow is adjacent to the first vortex chamber in the direction of cold coolant flow, along the heat exchange module. This ensures countercurrent movement of the hot and cold coolants in the apparatus.

[0023] It is preferable that the number of modular heat exchange elements be between 2 and 7.

[0024] It is preferable that all vortex chambers have the same shape and size.

[0025] It is preferable that the ratio of the diameters of the vortex chambers D to their height h be in the range from 5 to 20.

[0026] It is also preferable that the placement of the inlet pipes of the vortex chambers ensures that the direction of rotation of the coolant flow in all lower vortex chambers and the direction of rotation of the coolant flow in all upper vortex chambers are in opposite directions.

[0027] The horizontal flat element—the heat exchange surface—is the base where the modular heat exchange elements are located. It can be rectangular, or, as a special case, square. The base can also be circular, or disc-shaped. Other base shapes are also possible.

[0028] Achieving a technical result.

[0029] The heating efficiency of the coolant in the claimed device is increased due to its better organized and zoned flow across the heat exchange modules. In the claimed device, two or more vortex chambers are connected in series at the top and bottom. This increases the length of thermal contact and reduces the negative impact of radial leakage of a portion of the coolant, which occurs in a single chamber. Furthermore, the heat exchange modules are connected so that the coolants flow counter-currently. This increases the heating efficiency of the cold coolant: its temperature rises more sharply. Consequently, the hot coolant cools more rapidly. As a result, the amount of heat transferred increases, simultaneously enhancing the thermal efficiency of the device, which constitutes the technical result of the claimed technical solution.

[0030] The achievement of the technical result is determined by the presence in the proposed device of a set of distinctive features stated in paragraph 1 of the invention formula.

[0031] The invention is explained by drawings.

[0032] Fig. 1 shows a general view of the apparatus in section (rectangular base).

[0033] Fig. 2 shows a view of the apparatus from above (rectangular base).

[0034] Fig. 3 - cross-section of the heat exchange module along A-A in Fig. 2 (the base and elements of the vortex chambers are made of metal).

[0035] Fig. 4 is a cross-section of the heat exchange module along A-A in Fig. 2 (the base is made of metal, and the vortex chamber elements are made of plastic).

[0036] Fig. 5 shows a view of the apparatus from above (the base is in the shape of a square).

[0037] Fig. 6 shows a view of the apparatus from above (the base is in the shape of a round disk).

[0038] The following items are indicated by the positions on the drawings:

[0039] 1,2,3,4,5 - lower swirl chambers; 6,7,8,9,10 - upper swirl chambers; 11 - lower covers - disks; 12 - upper covers - disks; 13 - base - middle flat element - heat exchange surface; 14 - cylindrical rings; 15, 15v and 16, 16v - respectively, the inlet and outlet pipes of the lower swirl chambers of the coolant T / H1; 17, 17v and 18, 18v - respectively, the inlet and outlet pipes of the upper swirl chambers of the coolant T / H2; 19 - connecting tubes of the lower swirl chambers; 20 - connecting tubes of the upper swirl chambers; 21 - gaskets; 22 - studs; 23 - nuts.

[0040] The modular vortex heat exchanger (Fig. 1) has a disassemblable design. The apparatus contains adjacent coaxial vortex chambers formed by flat disks - covers 11, 12, and a middle horizontal flat element - heat exchange surface 13, cylindrical rings 14, fixed between the flat disks - covers and the middle flat element by means of studs 22. It contains inlet 15, 17, 15v, 17v and central outlet pipes 16, 18, 16v, 18v of the vortex chambers. The apparatus is characterized in that it contains two or more heat exchange modules based on vortex chambers. The heat exchanger shown in Figs. 1, 2 has five heat exchange modules, which are formed by vortex chambers 1 and 10, 2 and 9, 3 and 8, 4 and 7, 5 and 6, respectively. The middle flat element 13 is the common base for the assembly and the heat exchange surface for these heat exchange modules.The inlet pipes 15,17, 15v,17v of the vortex chambers are angular and are placed on flat-disc covers 11,12 at radii R. в , making up from 0.7 to 0.9 of the radius of the vortex chamber. The axes of the inlet pipes 15, 17, 15v, 17v make an angle β of 30 to 45° with the plane of the cover disks, while their projections onto the cover disk are perpendicular to the radius of the vortex chamber. Pipes 15, 17, 15v, 17v are cut into the covers 11 and 12 of the vortex chambers, as shown in Figs. 3 and 4. The inner parts of the pipes are recessed inside the vortex chambers. Pipes 15, 17, 15v, 17v and pipes 16, 18, 16v, 18v are secured to the covers 11 and 12 by welding or glue.

[0041] Placement of inlet pipes on radius R в = (0.7 ÷ 0.9) R,

[0042] where R=D / 2 is dictated by the following. A value less than 0.7 indicates worse flow swirl conditions in the vortex chamber and the outlet pipe is too close to the inlet. A value greater than 0.9 makes installation more difficult.

[0043] The placement of inlet nozzles at an angle β between 30 and 45° is determined by the following. If β is less than 30°, installation and fastening of the nozzle is more difficult. If β is greater than 45°, the flow swirl conditions in the vortex chamber are worse, as the tangential component of the inlet flow velocity vector decreases.

[0044] The hot coolant T / H1 enters the unit via pipe 15v, and its outlet via pipe 16v. The cold coolant T / H2 enters the unit via pipe 17v, and its outlet via pipe 18v.

[0045] The vortex chambers of the hot coolant (H / H1) 1-5 and the vortex chambers of the cold coolant (H / H2) 6-10 are connected in series (Fig. 1, 2). The lower vortex chambers are connected to each other by tubes 19. The upper vortex chambers are connected to each other by tubes 20. The vortex chambers on the base 13 are arranged and connected so that the first vortex chamber 1 in the direction of movement of the hot coolant has the last vortex chamber 10 in the direction of movement of the cold coolant as an adjacent vortex chamber along the heat exchange module, and the last vortex chamber 5 in the direction of movement of the hot coolant has the first vortex chamber 6 in the direction of movement of the cold coolant as an adjacent vortex chamber along the heat exchange module. This ensures countercurrent movement of the hot (H / H1) and cold (H / H2) coolants through the heat exchange modules of the apparatus. This increases the length of the thermal contact T / H1 and T / H2, and also ensures the maximum value of the driving force of the heat exchange process.

[0046] Various quantity and placement of modular elements on a flat element - base 13 is possible.

[0047] It is preferable that the number of modular heat exchange elements in the apparatus is from 2 to 7. Thus, in Fig. 1, 2 the number of modular elements is 5. In Fig. 5 their number is 4. In Fig. 6 their number is 7. The range from 2 to 7 is determined by the fact that one modular element will not ensure the achievement of the technical result, and the number of modules more than seven will lead to an increase in hydraulic resistance.

[0048] It is preferable that all vortex chambers of the modular heat exchange elements have the same shape and dimensions D and h (see Figs. 3 and 4).

[0049] For modular heat exchange elements, it is preferable that the ratio of the diameters D of the vortex chambers to their height h be in the range from 5 to 20.

[0050] It is preferable that the installation of inlet pipes 15v and 15 of all lower vortex chambers and inlet pipes 17v and 17 of all upper vortex chambers in the device ensures the direction of rotation of the coolant flows - in opposite directions.

[0051] The horizontal flat element 13—the heat exchange surface—the base, where the modular heat exchange elements are located, may alternatively have a rectangular shape (see Figs. 1, 2). As a special case of this, the base may have a square shape (see Fig. 5). Alternatively, the base may have the shape of a round disk (see Fig. 6). The base 13 may also have a different shape.

[0052] The material of element 13 must be steel, copper, brass or other metal with high thermal conductivity.

[0053] Both cylindrical rings 14 of each heat exchange module are installed on the base 13 coaxially at the top and bottom (see Figs. 3 and 4).

[0054] The upper and lower swirl chamber elements are secured to base 13 using studs 22 and nuts 23. Gaskets 21 (made of rubber, fluoroplastic, paronite, etc.) ensure the swirl chambers are sealed. The number of studs must ensure the airtightness of the apparatus's swirl chambers.

[0055] The material of rings 14 and cover discs 11, 12 in Fig. 3 is metal. In this case, rings 14 can be either separate or welded to base 13, forming a single element. In this case, the number of gaskets 21 is halved.

[0056] The material of rings 14 and cover discs 11, 12 in Fig. 4 is plastic. In this case, rings 14 and cover discs 11, 12 can be manufactured either separately or as a single part (e.g., by casting or 3D printing). In this case, the device's manufacture is significantly simplified, and the number of gaskets 21 is also halved.

[0057] The choice of materials for the manufacture of apparatus elements depends on the customer's requirements and production capabilities.

[0058] The apparatus operates as follows (see Fig. 1, 2). The first (hot) coolant T / H1 is fed into the inlet corner pipe 15c of the lower vortex chamber 1. Upon entering, it is reflected from the surface of the base 13 and performs a rotational motion inside the space of chamber 1. The coolant T / H1 washes the heat exchange surface 13, transferring heat through it to the coolant T / H2, located in chamber 10. Then T / H1 is removed from chamber 1 through the central pipe 16 and through the tube 19 enters chamber 2. The process is repeated in chambers 2, 3, 4 and 5. After passing the lower chambers, T / H1 is removed from the apparatus through pipe 16c.

[0059] The second (cold) heat transfer fluid T / H2 is fed into the apparatus through the inlet angular pipe 17c of the upper vortex chamber 6. Upon entering, it is reflected from the surface of the base 13 and rotates within the space of chamber 6. The heat transfer fluid T / H2 washes the heat exchange surface 13, accepting the heat from the heat transfer fluid T / H1. T / H2 is then discharged from chamber 6 and through pipe 18 and tube 20 into chamber 7. The process is repeated in chambers 7, 8, 9 and 10. After passing through the upper chambers, T / H2 is discharged from the apparatus through pipe 18c. This is how heat is transferred from T / H1 to T / H2 in the apparatus.

[0060] Heat exchange occurs under zonal heat exchange conditions across heat exchange modules, which increases the thermal efficiency of the unit. The counter-flow of T / H1 and T / H2 provides a high driving force for the process. The movement of the coolants in the chambers is rotational and reciprocating, with vortex formation, ensuring the destruction of the wall boundary layer and high heat transfer rates.

[0061] Tests were conducted to confirm the efficiency of the heat exchange module of the proposed apparatus with angular inlet nozzles. The experimental module consisted of two coaxial vortex chambers separated by a heat exchange disk (S = 3 mm). The diameter of both chambers was D = 305 mm with a chamber height of h = 30 mm. The design of the module corresponds to Fig. 3, but it also has tangential inlet nozzles on rings 14. These allow coolant to be introduced through the rings of the upper and lower chambers at a radius of R. в= 114 mm tangentially. Two main inlet pipes are welded at an angle of β = 45° on the upper and lower cover discs (R в =114 mm.). The device is made of 12X18H10T steel. The elements of the heat exchange module are connected with M10 studs.

[0062] The experiments were carried out on a test bench, which included: the heat exchange module under study, a hot water tank with a heating element, a centrifugal pump, hot and cold water rotameters, and digital devices for measuring the temperatures and pressures of the coolant at the inlet and outlet of the module.

[0063] The setup provided hot water circulation. It was fed into the lower vortex chamber. Cold water was fed into the upper vortex chamber from the water supply. The coolant flow rates were regulated by valves and measured with rotameters.

[0064] The experimental module was placed horizontally. The upper chamber's design was completely identical to the lower chamber's.

[0065] During the experiments, the heat transfer coefficients K and the hydraulic resistance of the vortex chamber ΔP were determined. The hydraulic resistance ΔP of the lower vortex chamber was determined using digital instrument readings.

[0066] The experiments on the heat exchange module were carried out in series: in series A - with the supply of coolants through tangential inlet pipes on the rings of the upper and lower vortex chambers; in series B - with the supply of coolants through inlet pipes welded at an angle of β = 45° on the upper and lower cover disks

[0067] During the experiments, the hot water flow rate was varied from 0.646 to 2.723 m 3 / h; cold water consumption - from 0.749 to 1.404 m 3 / h. The initial water temperature in the experiments was: for hot water - 45÷47°C, for cold water - 9÷12°C. The results of some of the experiments are presented in Tables 1 and 2.

[0068] Heat transfer coefficients K (W / (m 2 ⋅K)) was determined from the basic heat transfer equation based on the amount of heat , which received cold water:

[0069] K = , (1)

[0070] where F is the heat exchange surface of the device;

[0071] - average temperature difference of coolants.

[0072] Table 1. Dependence of the heat transfer coefficient (K) on the flow rate of the hot coolant at the flow rate of the cold V х = 1.068 m 3 / h

[0073] Parameters Consumption of hot coolant Vg, m3 / h Experiments Indicator 0,646 1,122 1,622 2,159 Series A (tangential inlet ports) Kt (W / (m2⋅K) / %) 1270 / 100 1464 / 100 1560 / 100 1617 / 100 Series B (angled inlet fittings) Ku (W / (m2⋅K) / %) 1222 / 96,2 1407 / 96,1 1562 / 100 1667 / 103

[0074] Table 2. Dependence of the heat transfer coefficient (K) on the flow rate of the hot coolant with the flow rate of the cold V х = 1.404 m 3 / h

[0075] Parameters Consumption of hot coolant Vg, m3 / h Experiments Indicator 0,646 1,122 1,622 2,159 Series A (tangential inlet ports) Kt (W / (m2⋅K) / %) 1240 / 100 1498 / 100 1697 / 100 1829 / 100 Series B (angled inlet fittings) Ku (W / (m2⋅K) / %) 1305 / 105,2 1555 / 103,8 1684 / 99,2 1759 / 96,2

[0076] Tables 1 and 2 show that the heat transfer coefficients K are quite high. Furthermore, the use of angular inlet nozzles in vortex chambers with an angle of β = 45° allows the heat transfer coefficient K to be maintained at the same level as with tangential coolant flow.

[0077] Data on the influence of the coolant inlet option on the hydraulic resistance of the vortex chamber ΔP are given in Table 3. Resistances ΔP т (tangential inlet pipes) and ΔP у (angled inlet pipes) are averaged: each is determined by three values.

[0078] Table 3. Dependence of the hydraulic resistance of the vortex chamber (ΔP) on the flow rate of the hot coolant

[0079] Indicator Consumption of hot coolant Vg, m3 / h 0,646 1,122 1,622 2,159 2,723 ΔPт (kPa / %) 8,37 / 100 24,17 / 100 49,77 / 100 87,1 / 100 138,2 / 100 ΔPу (kPa / %) 9,17 / 109,6 23,87 / 98,8 47,97 / 96,4 82,13 / 94,3 128,8 / 93,2

[0080] From Table 3 it can be seen that ΔP of the vortex chamber in the case of the device with angular inlet pipes ΔP уin most of the studied range it has advantages - it is somewhat less than the hydraulic resistance of the tangential inlet pipes ΔP т .

[0081] The heat transfer and ΔP resistance test data confirmed the feasibility and feasibility of using angular inlet nozzles in vortex chambers. In the case of a device comprising N modules, this simplifies the layout and connection of the vortex chambers.

[0082] Next, it is necessary to confirm the increase in thermal efficiency with an increase in the number of heat exchange modules. We present the calculation results. The initial data for these calculations were the flow rates and inlet temperatures T / H1 and T / H2, which were used in the experiment on a heat exchange module with a diameter of 305 mm and N = 1. Hot water flow rate - V г = 1.622 m 3 / h. Cold water consumption - V х = 1.404 m 3 / h. Thermal efficiency calculations were performed when heating, temperatures and the amount of heat transferred for the case when the number of heat exchange modules with angular inlet pipes N = 2, 3 and 4. The calculation results are given in Table 4.

[0083] Thermal efficiency function when heated, it was calculated using formula (2) [4]:

[0084] (2)

[0085] Here And - temperature of the cold coolant T / H2 at the inlet and outlet of the apparatus; And - temperature of the hot coolant T / H1 at the inlet and outlet of the apparatus.

[0086] Table 4. Thermal calculation results

[0087] Number of heat exchange modules N , °C , °C , °C , °C Transferred heat, W 1 (experience) 47,1 44,9 11,5 14,0 4080 0,07023 / 100 2 (calculation) 47,1 42,79 11,5 16,19 7655 0,1317 / 187 3 (calculation) 47,1 41,00 11,5 18,13 10820 0,1862 / 265 4 (calculation) 47,1 39,42 11,5 19,85 13630 0,2346 / 334

[0088] Thermal efficiency for the heat exchange module, obtained during the experiment (N = 1) according to formula (2) was = 0.07023 (taken as 100%).

[0089] From the data in Table 4 it can be seen that the degree of heating of the cold coolant increases, the thermal efficiency increases, and the amount of heat transferred by the device also increases ( ).

[0090] Change in thermal efficiency modular heat exchanger with an increase in the number of modules: at N = 2 - growth by 1.87 times; for N = 3 – by 2.65 times; for N = 4 – by 3.34 times.

[0091] Thus, the data given in Table 4 confirm the achievement of the technical result.

[0092] List of references

[0093] 1. Russian Federation Patent 2687669 C1, IPC F28D1 / 047, Spiral Heat Exchanger / Malevanny M.V., Barakov A.V., Dubanin V.Yu., Stogney V.G., Chernichenko V.V. - published 15.05.2019, Bulletin No. 14.

[0094] 2. Utility model for Russian Federation patent 117596 U1, IPC F28D 9 / 04, Spiral heat exchanger / Botashev A.Yu., Malsugenov R.S. - published 06 / 27 / 2012, Bulletin No. 18.

[0095] 3. Popov A.S., Kosyrev V.M. Development of a test bench for studying a vortex heat exchanger. In the collection “Science. Technology. Production-2014: abstracts of reports of the International scientific and technical conference of students, graduate students and young scientists” / editorial board: Evdokimova N.G. et al. - Ufa: RIC USPTU, 2014. - 98 p.

[0096] ISBN 978-5-7831-1181-5 P. 36-37. - Prototype.

[0097] 4. Bazhan P.I. et al. Handbook of heat exchange apparatus / P.I. Bazhan, G.E. Kanevets, V.M. Seliverstov. - M.: Mechanical Engineering. 1989.- 367 p.

Claims

1. A modular vortex heat exchanger comprising adjacent coaxial vortex chambers formed by flat cover disks and a central horizontal flat element - a heat exchange surface, cylindrical rings clamped between the flat cover disks and the central flat element, inlet and central outlet nozzles of the vortex chambers, characterized in that the apparatus contains two or more heat exchange modules based on vortex chambers, wherein the central flat element is a common base and heat exchange surface for all heat exchange modules; the inlet nozzles of the vortex chambers are of an angular design and are located on the flat cover disks at radii ranging from 0.7 to 0.9 of the radius of the vortex chamber; the axes of the inlet nozzles make an angle of 30 to 45° with the plane of the cover disks, while their projections onto the cover disk are perpendicular to the radius of the vortex chamber;the lower vortex chambers, connected to each other by tubes in series, and the upper vortex chambers, connected to each other by tubes in series, are arranged on the base so that the first vortex chamber in the direction of movement of the hot coolant has, as an adjacent vortex chamber along the heat exchange module, the last vortex chamber in the direction of movement of the cold coolant, and the last vortex chamber in the direction of movement of the hot coolant has, as an adjacent vortex chamber along the heat exchange module, the first vortex chamber in the direction of movement of the cold coolant, which ensures counter-current movement of the coolants.

2. A modular vortex heat exchanger according to paragraph 1, characterized in that the number of modular heat exchange elements is from 2 to 7.

3. A modular vortex heat exchanger according to paragraph 1, characterized in that all vortex chambers of the modular heat exchange elements have the same shape and dimensions.

4. A modular vortex heat exchanger according to paragraph 1, characterized in that the ratio of the diameters of the vortex chambers to their height is in the range from 5 to 20.

5. A modular vortex heat exchanger according to paragraph 1, characterized in that the installation of the inlet pipes of all lower and all upper vortex chambers ensures the direction of rotation of the coolant flows in all lower and all upper vortex chambers in opposite directions.

6. A modular vortex heat exchanger according to paragraph 1, characterized in that the heat exchange surface - a horizontal flat element - a base where the modular heat exchange elements are located, has a rectangular shape.

7. A modular vortex heat exchanger according to paragraph 1, characterized in that the heat exchange surface - a horizontal flat element - the base where the modular heat exchange elements are located has the shape of a round disk.

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