An open-type spiral-wound high-efficiency cooling system

Abstract

The present invention discloses an open-type spiral-wound high-efficiency cooling system, which includes an open-type spiral-wound condenser, a cooling circulation pump, a sprayer, a water distributor, a fan, a cooling packing layer, and a cooling water tank; the open-type spiral-wound condenser is immersed in the cooling water inside the cooling water tank, and the water distributor and the cooling circulation pump are arranged at the inner bottom of the cooling water tank; the sprayer is located above the cooling packing layer and sprays cooling water onto the surface of the cooling packing layer; the cooling packing is placed between the sprayer and the open-type spiral-wound condenser to increase the contact area between the cooling water and the air, and to make the cooling water cooled by the cooling packing layer uniformly drip onto the water surface of the cooling water tank; the fan is arranged above the sprayer to discharge the latent heat of vaporization of the cooling water and the cooling water tank vaporized into saturated water vapor to the outdoor atmosphere. The present invention has the characteristics of small volume, compact structure, and modularization, achieving the purpose of saving electricity, water, and being convenient for online cleaning.

Description

Technical Field

[0001] The present invention relates to the field of air conditioning equipment, and particularly to an open-type spiral wound high-efficiency cooling system. Background Art

[0002] In the field of refrigeration air conditioners, water-cooled air conditioners have higher refrigeration efficiency than air-cooled air conditioners, so they are the first choice for refrigeration equipment. Shell-and-tube condensers or double-pipe condensers are widely used as standard accessories for water-cooled air conditioners due to their small heat exchange volume, high heat exchange efficiency, mature technology, low cost, etc. The cooling function is realized by the way of cooling tower + shell-and-tube condenser (separated from the cooling tower).

[0003] However, there are mainly two major problems in the existing cooling system:

[0004] First, the existing water-cooled chillers share a set of cooling towers. When the refrigeration units operate at partial load, the cooling system still operates at full load, and the cooling water pumps and fans are in an overloaded operation state, resulting in waste of electric energy. Moreover, cooling water circulation is accompanied by the generation of flying water (cooling water that is not vaporized and evaporated, discharged into the atmosphere by the fan and cannot participate in the cooling cycle heat exchange), resulting in waste of water resources; since the cooling tower is on the roof and the condenser is built into the indoor refrigeration host, it causes an increase in the frictional resistance along the line formed by the extension of the cooling pipe network and thus waste of electric energy.

[0005] Second, the existing air conditioner units generally adopt shell-and-tube or double-pipe condensers. Whether it is a shell-and-tube condenser or a double-pipe condenser, there are the following problems:

[0006] 1. Scale is not easy to clean: Since the heat exchange between the refrigerant and the coolant (water) is completed in a closed shell tube, the scale formed in the shell tube must be cleaned after disassembling the shell-and-tube condenser when the machine is stopped. This causes high maintenance difficulty, large workload, and frequent maintenance, affecting production.

[0007] 2. The latent heat of vaporization decreases with the increase of pressure. The closed shell-and-tube heat exchanger or double-pipe heat exchanger is not conducive to the vaporization and evaporation of cooling water vapor, thus losing the heat exchange amount of the latent heat of vaporization and resulting in a reduction in the cooling effect.

[0008] 3. High power consumption of the cooling pump: Since the shell-and-tube condenser or double-pipe condenser has a small volume and limited heat exchange area inside the shell, when the outlet water temperature of the cooling water is constant, if the heat exchange amount is increased, it is necessary to increase the circulation amount of the cooling water flowing through the surface of the heat exchange body in the tube per unit time, and then increase the flow rate of the cooling water in the cooling pipe. Since the frictional resistance in the pipe is proportional to the square of the flow rate, an increase in the circulating power requires a higher-power cooling pump, thus increasing the power consumption. Summary of the Invention

[0009] The technical problem to be solved by the present invention is to provide an open-type spiral-wound high-efficiency cooling system, which overcomes the disadvantages of the prior art, has the characteristics of small volume, compact structure and modularization, can control the number of operating modules according to the system load demand, ensure that each module operates at its peak, realize the parallel networking operation of multiple units, and can also realize the independent operation of a single unit; an open-type spiral-wound condenser is adopted to replace the traditional shell-and-tube or double-pipe heat exchanger, reduce the cooling water flow rate, extend the residence time of the cooling water in the cooling water tank, ensure the full heat exchange between the cooling water and the refrigerant, increase the outlet temperature of the cooling water, increase the temperature difference △T between the inlet and outlet of the cooling water, and increase the heat exchange amount between the refrigerant and the cooling water; increase the temperature difference △t between the cooling water and the air, and increase the heat dissipation of the cooling water; increase the surface of the cooling filler layer and the evaporation surface of the cooling water tank, and increase the latent heat of vaporization heat dissipation of the cooling water; reduce the cooling water circulation volume, reduce the frictional resistance along the heat exchanger, and reduce the power of the cooling circulation pump, so as to achieve the purpose of power saving and water saving, and facilitate online cleaning.

[0010] To solve the above technical problems, the technical solution adopted by the present invention is as follows:

[0011] An open-type spiral-wound high-efficiency cooling system, comprising an open-type spiral-wound condenser, a cooling circulation pump, a sprayer, a water distributor, a fan, a cooling filler layer and a cooling water tank; the open-type spiral-wound condenser is immersed in the cooling water inside the cooling water tank, and the water distributor and the cooling circulation pump are arranged at the bottom inside the cooling water tank; the sprayer is located above the cooling filler layer and sprays cooling water onto the surface of the cooling filler layer; the cooling filler is placed between the sprayer and the open-type spiral-wound condenser to increase the contact area between the cooling water and the air, further reduce the temperature of the cooling water, and make the cooling water cooled by the cooling filler layer evenly drip onto the water surface of the cooling water tank; the fan is arranged above the sprayer to discharge the latent heat of vaporization of the cooling filler layer and the cooling water tank vaporized into saturated water vapor to the outdoor atmosphere;

[0012] The open spiral-wound condenser includes a refrigerant collecting box, several turns of spiral refrigerant tube windings, several layers of anchor frames, a refrigerant inlet pipe, and a refrigerant outlet pipe. The refrigerant collecting box consists of an end cover and a bottom plate. The length and width dimensions of the end cover and the bottom plate match each other, and flange plates of the same size are provided on the outside. A number of screw holes with matching sizes and positions are provided on the flange plates. A number of tube holes are formed in the middle of the bottom plate, and a box-shaped portion protrudes from the middle of the end cover. The bottom plate and the end cover are screwed and fastened together by bolts passing through the screw holes on the flange plates to form a cavity for collecting refrigerant. The refrigerant collecting box includes a steam-end collecting box and a liquid-end collecting box arranged oppositely. A collecting-box refrigerant inlet and a collecting-box refrigerant outlet are respectively provided above the side of the steam-end end cover and below the side of the liquid-end end cover. The refrigerant inlet pipe extends into the steam-end collecting box through the collecting-box refrigerant inlet to form a steam-distributing pipe. Small holes are evenly distributed along the lower edge of the steam-distributing pipe, so that refrigerant steam is evenly sprayed into the entire steam-end collecting box, ensuring that each turn of the spiral refrigerant tube winding is evenly supplied with steam, facilitating the uniform distribution of refrigerant in the tubes to achieve a full condensation and liquefaction effect. The refrigerant outlet pipe is connected to the collecting-box refrigerant outlet. A deflector plate forming a certain angle with the bottom surface is arranged at the bottom of the liquid-end collecting box, so that the condensed refrigerant liquid flows into the refrigerant outlet pipe, facilitating the liquid outflow of the refrigerant and preventing the occurrence of liquid accumulation phenomena, and improving the utilization efficiency of the refrigerant. The several layers of anchor frames are vertically fixedly connected between the bottom plates of the steam-end collecting box and the liquid-end collecting box. Each layer of the anchor frame consists of four anchor frames, and the projections of each layer of the anchor frame on the two bottom plates form two symmetrical anchor-frame rectangular structures. The anchor-frame rectangular structures formed by the projections of each layer of the anchor frame on the bottom plate are centered on the center point of the bottom plate and their sizes decrease in sequence. The several turns of spiral refrigerant tube windings are formed by several turns of spiral refrigerant tubes rotating externally tangent around the corresponding layer of anchor frames at a certain angle. Each turn of the spiral refrigerant tube consists of several spiral refrigerant tubes. Each spiral refrigerant tube consists of a straight pipe inlet section, a straight pipe outlet section at both ends and a spiral section in the middle, and a certain winding spacing is maintained between each spiral refrigerant tube. The straight pipe inlet section or the straight pipe outlet section of several spiral refrigerant tubes in each turn is connected to the tube holes on the bottom plate by energy-saving threads by the expansion tube method and is perpendicular to the bottom plate, and is axially symmetrically arranged in the length and width directions of the bottom plate with the center point of the bottom plate as the axis of symmetry. The projections of the straight pipe inlet section or the straight pipe outlet section of several spiral refrigerant tubes in each turn on the corresponding bottom plate (that is, the positions of the tube holes corresponding to this turn of the spiral refrigerant tube on the two bottom plates) form two symmetrical tube-rectangle structures. The positions of the straight pipe inlet section and the straight pipe outlet section of each spiral refrigerant tube on the tube-rectangle structure obtained by projection on the bottom plate are also axially symmetrically arranged with the center point of the bottom plate as the axis of symmetry, so as to ensure that the distance between each spiral refrigerant tube between the two bottom plates is of the same length, further ensuring the uniformity of the cooling of the refrigerant in the tubes. The rotation angles of the spiral refrigerant tube windings of adjacent two turns with respect to the corresponding layer of anchor frames are opposite, forming a microchannel group.

[0013] The open type spiral wound condenser can be replaced by a second open type spiral wound condenser (or called a header type open type spiral wound condenser), which has the same structure as the open type spiral wound condenser, including several turns of spiral refrigerant tube windings and several layers of anchor frames, but the end cover of the refrigerant collection box of the open type spiral wound condenser is cancelled and its bottom plate is retained. The bottom plate is divided into a steam end bottom plate and a liquid end bottom plate. A refrigerant steam inlet system and a refrigerant liquid outlet system are also added. The refrigerant steam inlet system includes a refrigerant steam main pipe located above the outer side of the steam end bottom plate, a steam branch pipe interconnected with each other below the main pipe, and several steam inlet pipe bundles. The several steam inlet pipe bundles The other end of the pipe is connected with the straight tube inlet section of the spiral refrigerant tube through the several tube holes on the bottom plate of the steam end. The several steam inlet tube bundles are kept of equal length and equal distance, so that the refrigerant is evenly distributed in each tube, so that each tube exchanges heat evenly and the condensation effect is optimal; the refrigerant liquid outlet system includes a refrigerant liquid main pipe located below the outer side of the liquid end bottom plate, a liquid branch pipe and several liquid outlet pipes interconnected above the refrigerant, the other ends of the several liquid outlet pipes are connected with the several tube holes on the bottom plate of the liquid end, and each of the several liquid outlet pipes maintains a certain downward inclined angle with the straight tube outlet section of the several spiral refrigerant tubes, so as to facilitate the outflow of the refrigerant after condensation and effectively prevent the deposition of liquid refrigerant.

[0014] Compared with the open type spiral wound condenser, the second open type spiral wound condenser omits the end cover of the refrigerant manifold box, and replaces the refrigerant manifold box, refrigerant inlet pipe and refrigerant outlet pipe with the steam end bottom plate, liquid end bottom plate, refrigerant steam inlet system and refrigerant liquid outlet system, and has the characteristics of simple structure and low cost.

[0015] Preferably, the water distributor adopts an H-type same-path multi-stage water distributor, including a water distributor main pipe, multi-stage water distribution pipes and a plurality of water distribution heads that are interconnected. Each lower-level water distribution pipe is vertically connected to the upper-level water distribution pipe to form a multi-stage H-shape, and the plurality of water distribution heads are distributed at both ends of the last-level water distribution pipe, so that the various water distribution heads are finally presented on the same horizontal plane, and each adjacent water distribution head is arranged equidistantly, thereby forming a uniform water distribution head array; the other end of the water distributor main pipe is connected to the cooling circulation pump, and the cooling water that has been heated by heat exchange in the cooling water tank passes through the evenly distributed water distribution heads, enters the multi-stage water distribution pipes, the water distributor main pipe, and finally enters the cooling pump and the sprinkler through the cooling pump guide pipe to enter the next cooling cycle.

[0016] The use of an H-shaped parallel multi-stage water distributor can make the low-temperature cooling water cooled on the surface of the cooling water tank move horizontally downward at a uniform speed in the vertical direction, just like a "piston" formed by the side wall of the water tank; through the setting of the H-shaped parallel multi-stage water distributor, it can effectively prevent the disordered heat exchange between the cooling water and the refrigerant tubes, avoid the situation of incomplete backflow caused by the high flow rate in the inlet area of the circulation pump and the low flow rate in the far end area of the inlet of the circulation pump in the state without a water distributor; ensure that the low-temperature cooling water passes through the "micro-channel" group formed by the reverse winding of the upper and lower two turns of spiral refrigerant tube windings from top to bottom and exchanges heat layer by layer with the refrigerant tubes, forming water layers with different gradients of the same temperature flowing downward along the vertical direction through each layer of tubes, thereby improving the cooling effect of the cooling water. The setting of the H-shaped parallel multi-stage water distributor is a necessary guarantee for the realization of the function of the heat exchanger, and realizes the efficient heat exchange of the heat exchanger.

[0017] For the open-type spiral-wound condenser in the above form, since the spiral refrigerant tube windings of adjacent two turns rotate in opposite directions, a certain angle is formed between the upper and lower two turns of tubes, and countless micro-channels are formed on the vertical plane of the open-type spiral-wound condenser. And because the surface of each tube is arc-shaped, the micro-channel is a non-planar structure, continuously changing the flow direction and flow rate of water, enhancing the disturbance of the cooling water, forming turbulent flow and chaotic flow, and further improving the heat transfer coefficient; it can not only ensure the full heat exchange between the refrigerant in the spiral refrigerant tubes and the cooling water in the cooling water tank, but also enable a part of the latent heat of vaporization generated by the heat exchange between the refrigerant and the cooling water to be released through the water surface of the cooling water tank, thus achieving an effect that cannot be achieved by a shell-and-tube heat exchanger. Utilizing the latent heat of vaporization of water improves the heat transfer amount per unit of water, thereby making the heat exchange efficiency higher than that of a shell-and-tube heat exchanger; and the open-type spiral-wound condenser is more convenient for cleaning and maintenance.

[0018] Preferably, the anchor frame and the refrigerant collecting box adopt the process of welding carbon steel and then performing hot-dip galvanizing to prevent and delay oxidation in high-temperature and high-humidity environments.

[0019] Preferably, the spiral tubes are made of inner-threaded copper tubes with a wall thickness of 8-15 μm and a diameter of 10-15 mm, or other metal materials such as titanium alloy, aluminum alloy, and stainless steel; the straight tube inlet section and the straight tube outlet section of each tube are arranged horizontally in parallel, and the spiral section forms the same angle ∠χ with the anchor frame and the winding pitch is 1 cm or more, which is convenient for cleaning; while ensuring easy cleaning, maintaining the minimum winding pitch can increase the tube density in the cross-section and is conducive to full heat exchange.

[0020] Preferably, the refrigerant collecting box is made of carbon steel plate with a thickness of 15 mm or more; the bottom plate of the refrigerant collecting box punches out tube holes according to the tube diameter by a machine tool, and the diameter of the tube holes is consistent with the outer diameter of the tubes. The tubes are connected to the bottom plate of the refrigerant collecting box by the method of expanding tubes or welding; the whole is treated with a hot-dip galvanizing process to make an anti-corrosion coating.

[0021] Preferably, the bolts adopt a hot-dip galvanizing process for carbon steel of 8 mm or above, or are made of the same material as the refrigerant collection box; an anti-leakage cushion layer is attached between the flange plates on the end cover and the bottom plate and fastened with bolts.

[0022] Preferably, the main water distribution pipe, multi-stage branch water pipes and several water distribution heads of the H-type parallel-flow multi-stage water distributor can adopt galvanized steel pipes, PUC pipes, PE and other metal pipes, plastic pipes, etc.

[0023] Beneficial effects: The present invention has the characteristics of small volume, compact structure and modularization. The number of operating modules can be controlled according to the system load demand to ensure that each module operates at its peak. It can realize the parallel networking operation of multiple units or the independent operation of a single unit; an open spiral-wound condenser is adopted to replace the traditional shell-and-tube or double-pipe heat exchanger, which can reduce the cooling water flow rate, extend the residence time of the cooling water in the cooling water tank, ensure sufficient heat exchange between the cooling water and the refrigerant, increase the outlet temperature of the cooling water, increase the temperature difference △T between the inlet and outlet of the cooling water, and increase the heat exchange amount between the refrigerant and the cooling water; increase the temperature difference △t between the cooling water and the air, and increase the heat dissipation of the cooling water; increase the surface of the cooling filler layer and the evaporation surface of the cooling water tank to increase the latent heat of vaporization heat dissipation of the cooling water; reduce the cooling water circulation volume, reduce the frictional resistance along the heat exchanger, and reduce the power of the cooling circulation pump, achieving the purpose of saving electricity and water, and facilitating on-line cleaning.

[0024] Specifically, the following problems are solved:

[0025] First, the problems of high energy consumption of the cooling circulation pump and waste of cooling water in the cooling system:

[0026] 1. Miniaturize and modularize the cooling tower so that a central air-conditioning refrigeration system consists of multiple micro-cooling modules. The number of operating modules can be controlled according to the system load demand to ensure that each module operates at its peak. It can realize the parallel networking operation of multiple units or the independent operation of a single unit; the cooling pump built in the cooling tower is synchronized with the cooling module and starts and stops according to the refrigeration system load, avoiding the waste of circulating pump electric energy caused by the full-load operation of the traditional single large cooling tower when the whole refrigeration system is under partial load. In addition, since the cooling pump is built in the micro-cooling module, it avoids the excessive length of the cooling pipe network caused by the separation of the traditional cooling tower and the refrigeration host, and thus the increase in frictional resistance along the way, the increase in power of the circulating pump due to the increase in head, and the waste of electric energy.

[0027] 2. Since the forced circulation of the fan is inevitable to ensure the heat exchange effect between the cooling water and the air during the operation of the cooling tower, the phenomenon of "water splash" that is not vaporized and evaporated for heat exchange but is carried into the air by the fan will occur. Moreover, the higher the wind speed, the more serious the "water splash" is, resulting in a waste of water resources. After modularizing the cooling tower, each module can operate independently according to the load of the refrigeration system, and the number of started modules can fundamentally solve the "water splash" phenomenon and achieve the purpose of water conservation. Since the fan runs synchronously with the module, the power consumption of the fan is also saved at the same time.

[0028] Second, solve the following problems of traditional shell-and-tube or double-pipe condensers:

[0029] 1. Solve the problem that the scale of traditional shell-and-tube or double-pipe condensers is not easy to clean: This patent adopts an open condenser, which exposes the inner tubes of the traditional shell-and-tube condenser completely in the open water tank, facilitating the cleaning of scale and ensuring maintenance and cleaning under the condition of non-stop operation.

[0030] 2. Reduce the frictional resistance along the heat exchanger: By adopting an open cooling method, there is no shell-side fluid resistance of the traditional shell-and-tube heat exchanger. The self-gravity flow of the cooling water can completely overcome the resistance of the tube bundle to the water. Compared with a shell-and-tube (double-pipe) heat exchanger with the same heat exchange power, the power consumption is low. Thus, the power of the cooling circulation pump is reduced to achieve the purpose of power saving.

[0031] 3. Reduce the cooling water circulation volume: The heat exchange between the cooling water and the refrigerant is divided into two parts: Qf = Q1 + Q2. Among them, Q1 is the convective heat exchange process between water and refrigerant. In this part, the heat energy of the refrigerant is directly transferred to the cooling water, and the absorbed heat exists in the cooling water in the form of sensible heat; the other Q2 is the part that is vaporized into saturated water vapor. The heat of the refrigerant forms steam through heat exchange with the cooling water and is discharged into the atmosphere by the exhaust fan in the form of latent heat. Since the heat exchange between the cooling water and the refrigerant in the shell-and-tube (double-pipe) heat exchanger is carried out in a high-pressure closed shell tube, it is not conducive to the vaporization and evaporation of water. This heat exchanger adopts an open form, and the cooling water is exposed to the air for heat exchange under normal pressure, which is conducive to the vaporization and evaporation of water. Therefore, the latent heat exchange amount Q2 is larger, that is, the vaporization amount of the cooling water increases. When the total heat exchange amount Qf is a fixed value, if the latent heat exchange amount Q2 of the cooling water increases, the sensible heat exchange amount Q1 of the cooling water will decrease accordingly. Therefore, a smaller cooling water circulation volume can meet the heat exchange requirements. Thus, the cooling water circulation volume is reduced.

[0032] 4. Improve the cooling efficiency: As known from the thermodynamic formula, Q absorption = V flow rate * S cross-sectional area * ρ density * ΔT temperature difference * C specific heat capacity; where V flow rate * S cross-sectional area, i.e., the flow rate, is a constant value, ρ density and C specific heat capacity are constants. Due to the increase in the cross-sectional area S cross-sectional area of the open water tank, the cooling water flow rate V flow rate decreases, and then the residence time of the cooling water in the water tank is prolonged, and the temperature T2 of the water leaving the water tank increases, that is, the temperature difference ΔT between the inlet and outlet of the cooling water is increased. The increase in Q absorption means that the heat exchange amount between the refrigerant and the cooling water increases; when the outlet temperature of the cooling water increases, the temperature difference Δt between it and the air increases, thereby improving the heat transfer efficiency between the cooling water and the air. Through the entire heat exchange process of refrigerant → cooling water → air, the heat of the refrigerant is transferred to the air. According to the law of conservation of energy: Q release = Q absorption, and the process of the refrigerant releasing heat is the process of the cooling water absorbing heat. The decrease in the flow rate increases the temperature difference ΔT between the inlet and outlet of the cooling water and improves the cooling efficiency. Description of the Drawings

[0033] Figure 1 It is a schematic structural view of the open-type spiral-wound high-efficiency cooling system of the present invention.

[0034] Figure 2 It is an overall assembly top view of the open-type spiral-wound condenser of the present invention.

[0035] Figure 3 It is a front view of the steam end collecting box of the open-type spiral-wound condenser of the present invention.

[0036] Figure 4 It is a front view of the liquid end collecting box of the open-type spiral-wound condenser of the present invention.

[0037] Figure 5 It is a right side view of the end cover of the steam end collecting box of the open-type spiral-wound condenser of the present invention.

[0038] Figure 6 It is a left side view of the end cover of the liquid end collecting box of the open-type spiral-wound condenser of the present invention.

[0039] Figure 7 It is a side top view of the end cover of the steam end collecting box.

[0040] Figure 8 It is a side top view of the end cover of the liquid end collecting box.

[0041] Figure 9 It is a right side internal cross-sectional view of the end cover of the steam end collecting box of the present invention.

[0042] Figure 10 It is a right side internal cross-sectional view of the end cover of the liquid end collecting box of the present invention.

[0043] Figure 11 It is a schematic diagram of the positional layout (left view or right view) of the anchor frame and the straight pipe section of the spiral refrigerant pipe in the present invention projected on the bottom plate.

[0044] Figure 12 It is a right view schematic diagram of the positional distribution of the straight pipe inlet section of the spiral refrigerant pipe in the present invention on the steam end bottom plate of the steam end collecting box (taking the first turn of the spiral refrigerant pipe as an example).

[0045] Figure 13 It is a right view schematic diagram of the positional distribution of the straight pipe outlet section of the spiral refrigerant pipe in the present invention on the liquid end bottom plate of the liquid end collecting box (taking the first turn of the spiral refrigerant pipe as an example).

[0046] Figure 14 It is a side view of the positional distribution of the refrigerant collecting box and the anchor frame in the present invention.

[0047] Figure 15 It is a side top view of the positional distribution of the refrigerant collecting box and the anchor frame in the present invention.

[0048] Figure 16 It is a schematic diagram of the structure of each anchor frame in the present invention.

[0049] Figure 17 It is a partial enlarged schematic diagram of the connection between the anchor frame and the bottom plate of the refrigerant collecting box in the present invention.

[0050] Figure 18 It is a side view of the first turn of the spiral refrigerant pipe winding in the present invention.

[0051] Figure 19 It is a side top view of the first turn of the spiral refrigerant pipe winding in the present invention.

[0052] Figure 20 is Figure 19 A partial enlarged schematic diagram of one end of the steam end collecting box in

[0053] Figure 21 It is a side view of the second turn of the spiral refrigerant pipe winding in the present invention.

[0054] Figure 22 It is a side top view of the second turn of the spiral refrigerant pipe winding in the present invention.

[0055] Figure 23 It is a side view of the third turn of the spiral refrigerant pipe winding in the present invention.

[0056] Figure 24 It is a side top view of the third turn of the spiral refrigerant pipe winding in the present invention.

[0057] Figure 25 It is a side view of the fourth turn of the spiral refrigerant pipe winding in the present invention.

[0058] Figure 26 It is the top view of the side of the fourth turn of the spiral refrigerant tube winding in the present invention.

[0059] Figure 27 It is the Y-axis point array diagram of the projection of the anchor frame and the spiral refrigerant tube on the bottom plate in the present invention.

[0060] Figure 28 It is the X-axis point array diagram of the projection of the anchor frame and the spiral refrigerant tube on the bottom plate in the present invention.

[0061] Figure 29 It is the front view of the refrigerant vapor inlet system on the side of the steam end bottom plate of the second open-type spiral-wound condenser in the present invention.

[0062] Figure 30 It is the rear view of the refrigerant liquid outlet system on the side of the liquid end bottom plate of the second open-type spiral-wound condenser in the present invention.

[0063] Figure 31 It is the schematic top view structure of the H-type parallel multi-stage water distributor in the present invention.

[0064] Wherein: R3, open-type spiral-wound condenser; 30a, end cover; 30b, bottom plate; 30-1, steam end collecting box; 30-2, liquid end collecting box; 30a-1, steam end cover; 30a-2, liquid end cover; 30b-1, steam end bottom plate; 30b-2, liquid end bottom plate; 31, refrigerant inlet pipe; 32, refrigerant outlet pipe; 31a, air distribution pipe; 31b, main refrigerant vapor pipe; 31c, steam branch pipe; 31d, steam inlet tube bundle; 32a, guide plate; 32b, main refrigerant liquid pipe; 32c, liquid branch pipe; 32d, liquid outlet pipe; 33, anchor frame; 33-1, anchor frame fixing section; 33-2, anchor frame supporting section; 33.1, first layer anchor frame; 33.2, second layer anchor frame; 33.3, third layer anchor frame; 33.4, fourth layer anchor frame; 34, spiral refrigerant tube; 34-1, straight pipe inlet section; 34-2, straight pipe outlet section; 34-3, spiral section; 34.1, first turn of spiral refrigerant tube winding; 34.2, second turn of spiral refrigerant tube winding; 34.3, third turn of spiral refrigerant tube winding; 34.4, fourth turn of spiral refrigerant tube winding; 300, flange plate; 301, screw hole; 302, tube hole; 303, box-shaped part; 306, collecting box refrigerant inlet; 307, collecting box refrigerant outlet; 308, bolt; 330, anchor frame rectangular structure; 340, tube rectangular structure.

[0065] O, center point of the bottom plate; D, diameter of the anchor frame; d, diameter of the spiral refrigerant tube row; H, layer spacing of adjacent turns of tube rows in the y-axis direction; L, tube distance of adjacent straight tube sections of the same turn of horizontal tube rows in the x-axis direction; l, spacing of the side wings of different turns of tube rows in the x-axis direction; S, total height of the same turn of tube rows in the y-axis direction; s, spacing of the anchor frame in the y-axis direction of the central layer (the fourth layer); E, spacing of the side wings of the same turn of tube rows in the y-axis direction; M, total distance of the straight tube sections of the same turn of horizontal tube rows in the x-axis direction; m, spacing of adjacent turns of tube rows in the y-axis direction in the x-axis direction; b, adjacent winding spacing of the same turn of tube rows; R, diameter of the support section of the anchor frame; r, diameter of the fixed section of the anchor frame;

[0066] C1, cooling circulation pump; C2, sprayer; C3, water distributor; C4, fan; C5, cooling packing layer; C6, cooling water tank; C300, main water pipe of the water distributor; C301, primary sub-water pipe; C302, secondary sub-water pipe; C303, tertiary sub-water pipe; C304, quaternary sub-water pipe; C305, quinary sub-water pipe; C306, senary sub-water pipe; C307, water head. Detailed implementation mode

[0067] The present invention will be further described in detail below with reference to the accompanying drawings and the detailed implementation mode.

[0068] As Figure 1 shown, an open-type spiral-wound high-efficiency cooling system includes an open-type spiral-wound condenser R3, a cooling circulation pump C1, a sprayer C2, a water distributor C3, a fan C4, a cooling packing layer C5, and a cooling water tank C6; the open-type spiral-wound condenser R3 is immersed in the cooling water inside the cooling water tank C6, and the water distributor C3 and the cooling circulation pump C1 are arranged at the inner bottom of the cooling water tank C6; the sprayer C2 is located above the cooling packing layer C5 and sprays cooling water onto the surface of the cooling packing layer C5; the cooling packing layer C5 is placed between the sprayer C2 and the open-type spiral-wound condenser R3 to increase the contact area between the cooling water and the air, further reduce the temperature of the cooling water, and make the cooling water cooled by the cooling packing layer C5 uniformly drip onto the water surface of the cooling water tank C6; the fan C4 is arranged above the sprayer C2 to discharge the latent heat of vaporization of the cooling packing layer C5 and the cooling water tank C6 vaporized into saturated water vapor to the outdoor atmosphere;

[0069] As Figures 2 - 13, the open spiral-wound condenser R3 includes a refrigerant collecting box, several turns of spiral refrigerant tube windings, several layers of anchor frames, a refrigerant inlet pipe 31, and a refrigerant outlet pipe 32. The refrigerant collecting box is composed of an end cover 30a and a bottom plate 30b. The length and width dimensions of the end cover 30a and the bottom plate 30b match each other, and flange plates 300 of the same size are provided on the outside. A number of screw holes 301 with matching sizes and positions are provided on the flange plates 300. A number of tube holes 302 are opened in the middle of the bottom plate 30b. A box-shaped portion 303 protrudes in the middle of the end cover 30a. The bottom plate 30b and the end cover 30a are screwed and fastened together by bolts 308 passing through the screw holes 301 on the flange plates 300 to form a cavity for collecting refrigerant. The refrigerant collecting box includes a steam-end collecting box 30-1 and a liquid-end collecting box 30-2 arranged oppositely. A collecting-box refrigerant inlet 306 and a collecting-box refrigerant outlet 307 are respectively provided above the side of the steam-end end cover 30a-2 and below the side of the liquid-end end cover 30a-2. The refrigerant inlet pipe 31 extends into the steam-end collecting box 30-1 through the collecting-box refrigerant inlet 306 to form a steam-distributing pipe 31a. Small holes are evenly distributed along the lower edge of the steam-distributing pipe 31a, so that the refrigerant steam is evenly sprayed into the entire steam-end collecting box 30-1, ensuring that each turn of the spiral refrigerant tube winding is evenly supplied with steam, facilitating the uniform distribution of the refrigerant in the tubes to achieve a full condensation and liquefaction effect. The refrigerant outlet pipe 32 is connected to the collecting-box refrigerant outlet 307. A guide plate 32a forming a certain angle with the bottom surface is provided at the bottom of the liquid-end collecting box 30-2, so that the condensed refrigerant liquid converges to the refrigerant outlet pipe, facilitating the liquid outflow of the refrigerant and preventing the occurrence of liquid accumulation phenomenon, and improving the utilization efficiency of the refrigerant;

[0070] Among them, it should be particularly noted that:

[0071] Figure 11 is a schematic diagram of the positional layout of the anchor frame and the straight pipe section of the spiral refrigerant tube in the present invention projected on the bottom plate. Since the projections of the anchor frame and the straight pipe section of the spiral refrigerant tube on the bottom plate are axially symmetrically distributed with the center point O of the bottom plate as the axis, therefore, whether it is a left view or a right view, it is Figure 11 the presented figure.

[0072] Figure 12This is a right view schematic diagram of the position distribution of the straight pipe inlet section of the spiral refrigerant tube in the present invention on the steam end bottom plate of the steam end collecting box (taking the first turn of the spiral refrigerant tube as an example), that is, the position distribution diagram of the straight pipe inlet section 34-1 of the spiral refrigerant tube on the steam end bottom plate 30b-1 seen from the external right side perspective of the steam end collecting box 30-1. For the convenience of narration and illustration, we take the first turn of the spiral refrigerant tube winding 34.1 as an example, and only draw the position of the straight pipe inlet section 34-1 of the first turn of the spiral refrigerant tube on the steam end bottom plate 30b-1, and number the positions of the straight pipe inlet section 34-1 of the first turn of the spiral refrigerant tube winding 34.1 on the steam end bottom plate 30b-1 in the counterclockwise direction, from 1 to 26. Among them, the position of the straight pipe inlet section of the spiral refrigerant tube in the upper right corner is 1, the position of the straight pipe inlet section of the spiral refrigerant tube in the upper left corner is 9, the lower left corner is 14, and the lower right corner is 22; the positions of the straight pipe inlet sections of the above 26 first turn of the spiral refrigerant tube windings on the steam end bottom plate form a largest tube rectangular structure 340.

[0073] Similarly, Figure 13 This is a right view schematic diagram of the position distribution of the straight pipe outlet section of the spiral refrigerant tube in the present invention on the liquid end bottom plate 30b-2 of the liquid end collecting box 30-2 (taking the first turn of the spiral refrigerant tube winding 34.1 as an example), which is the position distribution diagram of the straight pipe outlet section 34-2 of the spiral refrigerant tube seen from the right side perspective of the liquid end collecting box 30-2 on the liquid end bottom plate 30b-2. We still take the first turn of the spiral refrigerant tube winding 34.1 as an example and only draw the position of the straight pipe outlet section 34-2 of the first turn of the spiral refrigerant tube on the liquid end bottom plate 30b-2. Since each spiral refrigerant tube 34 rotates and winds along the corresponding layer of the anchor 33, its straight pipe inlet section 34-1 must be connected to the corresponding straight pipe outlet section 34-2 after passing through the spiral section 34-3, and the position of the corresponding straight pipe outlet section 34-2 on the liquid end bottom plate 30b-2 (that is, in Figure 13 the position), and the position of its straight pipe inlet section 34-1 in Figure 12 the position, is axisymmetric with respect to the center point O of the bottom plate. Specifically, we also number the position of the straight pipe outlet section 34-2 corresponding to the straight pipe inlet section 34-1. The position of the straight pipe outlet section 34-2 corresponding to the straight pipe inlet section 34-1 at position 1 is denoted as 1′, the position of the straight pipe outlet section 34-2 corresponding to the straight pipe inlet section 34-1 at position 2 is denoted as 2′, and so on, from 1′ to 26′. It forms another largest tube rectangular structure 340 in Figure 13 it, where the position of the straight pipe outlet section of the spiral refrigerant tube in the lower left corner is 1′, the position of the straight pipe outlet section of the spiral refrigerant tube in the lower right corner is 9′, the upper right corner is 14′, and the upper left corner is 22′. It can be seen that if Figure 12 andFigure 13 If the column tube rectangular structures 340 in are overlapped, then the position 1' of the straight tube inlet section 34-1 at position 1 and its corresponding straight tube outlet section 34-2 are axisymmetric with respect to the center point O of the bottom plate. The position 2' of the straight tube inlet section 34-1 at position 2 and its corresponding straight tube outlet section 34-2 are also axisymmetric, and so on. The positions of each straight tube inlet section 34-1 and its corresponding straight tube outlet section 34-2 are axisymmetric in the column tube rectangular structure 340. Such a design can ensure that the distances between every spiral refrigerant tube 34 between the two bottom plates 30b are of the same path, further ensuring the uniformity of the cooling of the refrigerant in the tubes.

[0074] Figures 14 - 26 It is a side view, a side top view, and a partial enlarged schematic diagram of some positions of the refrigerant collection box and the anchor frame position distribution of the present invention, as well as the first to fourth turn spiral refrigerant tube windings. It can be seen that the several layers of anchor frames are vertically fixedly connected between the bottom plates 30b of the steam end collection box 30-1 and the liquid end collection box 30-2. Each layer of the anchor frame is composed of four anchor frames 33, and the projections of each layer of the anchor frame on the two bottom plates form two symmetric anchor frame rectangular structures 330. The anchor frame rectangular structures formed by the projections of each layer of the anchor frame on the bottom plate are centered on the center point O of the bottom plate and their sizes decrease in sequence; the several turns of spiral refrigerant tube windings are formed by several turns of spiral refrigerant tubes 34 rotating externally tangent around the corresponding layer of the anchor frame 33 at a certain angle. Each turn of the spiral refrigerant tube 34 is composed of several spiral refrigerant tubes 34. Each spiral refrigerant tube 34 is composed of a straight tube inlet section 34-1 and a straight tube outlet section 34-2 at both ends and a spiral section 34-3 in the middle, and a certain winding pitch b is maintained between each spiral refrigerant tube 34; the straight tube inlet section 34-1 or the straight tube outlet section 34-2 of the several spiral refrigerant tubes 34 in each turn is connected to the tube holes 302 on the bottom plate 30b by an energy-saving thread in an expansion tube method and is perpendicular to the bottom plate 30b, and is axisymmetrically arranged with respect to the center point O of the bottom plate 30b in the length and width directions of the bottom plate 30b. The projections of the straight tube inlet section 34-1 or the straight tube outlet section 34-2 of the several spiral refrigerant tubes 34 in each turn on the corresponding bottom plate 30b (that is, the positions of the tube holes 302 corresponding to this turn of the spiral refrigerant tube 34 on the two bottom plates 30b) form two symmetric column tube rectangular structures 340. The positions of the straight tube inlet section 34-1 and the straight tube outlet section 34-2 of each spiral refrigerant tube 34 on the column tube rectangular structure 340 obtained by the projection of the bottom plate are also axisymmetric with respect to the center point O of the bottom plate, so as to ensure that the distances between every spiral refrigerant tube 34 between the two bottom plates 30b are of the same path, further ensuring the uniformity of the cooling of the refrigerant in the tubes; the rotation angles of the spiral refrigerant tube windings of the adjacent two turns and the corresponding layer of the anchor frame are opposite, forming a microchannel group.

[0075] Figures 27 - 28 The figure shows the y-axis point array diagram and x-axis point array diagram of the anchor frame and the spiral refrigerant tube in the present invention projected on the bottom plate. N is the total number of turns of the tube; n is the number of turns to which a certain tube belongs; D is the diameter of the anchor frame; d is the diameter of the tube; H is the layer spacing in the y-axis direction between adjacent turns of the tube; L is the tube spacing in the x-axis direction between adjacent straight tube segments of the horizontal tubes in the same turn; l is the stagger spacing in the x-axis direction between different turns of the tube; S is the total height of the tubes in the y-axis direction in the same turn; s is the spacing of the anchor frame in the y-axis direction of the central layer (the fourth layer in this embodiment); E is the spacing of the side wings of the tubes in the y-axis direction in the same turn; M is the total distance of the straight tube segments of the horizontal tubes in the x-axis direction in the same turn; m is the distance in the x-axis direction between adjacent tubes in the same turn in the y-axis; b is the winding spacing between adjacent tubes in the same turn; R is the diameter of the support section of the anchor frame; r is the diameter of the fixed section of the anchor frame; λ is the number of equal parts on the vertical side of the side wing; O is the origin (center point); β is the number of tubes in the X-axis direction; k is the number of equal parts of the tubes in the X-axis direction (except for adjacent tubes in the same turn in the y-axis).

[0076] Each point on the bottom plate, including the screw hole 301, the anchor frame point (the connection point of the fixed section of the anchor frame on the bottom plate), and the tube hole 302, presents a central symmetric layout with 0 as the origin. The distance between the centers of adjacent anchor frame layers is equal to the layer spacing in the y-axis direction between adjacent turns of the tube, both being H, and the distance is the sum of the tube diameter d and the anchor frame diameter D, that is, H = D + d. The anchor frame should have sufficient strength to ensure that it does not deform when the tube is wound, and the diameter D of the winding section of the anchor frame determines the layer spacing. The diameter D of the anchor frame should be greater than the diameter d of the tube, that is, D > d; the lower side of the outer wall of the straight tube segment of the same turn of the tube is tangent to the upper side of the outer wall of the same layer of the anchor frame in the x-axis direction, and the inner side of the outer wall of the same turn of the tube is tangent to the outer side of the wall of the same layer of the anchor frame in the y-axis perpendicular direction; the outer walls of adjacent tubes are tangent to the outer wall of the anchor frame; the distance Sn of the tubes in the y-axis direction in the same turn is the sum of the center anchor tube spacing s and the difference between the sum of the diameters d of all tubes in the y-axis direction of each turn and the tube diameter d and the anchor frame diameter D, that is, Sn = (s - d) + 2H(N - n + 1) = (s - d) + 2(D + d)(N - n + 1), where 0 ≤ s. When the anchor frame diameter D, the tube diameter d, and the number of turns N are determined, the s spacing determines the height of the total height S of the tubes in the y-axis direction in the same turn. In this case, the y-axis spacing S1 of the first turn of the tube = (s - d) + 8(D + d), the y-axis spacing S2 of the second turn of the tube = (s - d) + 6(D + d), the y-axis spacing S3 of the third turn of the tube = (s - d) + 4(D + d), the y-axis spacing S4 of the fourth turn of the tube = (s - d) + 2(D + d); the side wing spacing E of the tubes in the same turn is equally distributed, and adjacent winding layers are arranged in parallel. The spacing En between the tubes in the same winding layer = Sn / λn. In this case, the side wing spacing E1 of the first turn of the tube = S1 / λ1, the side wing spacing E2 of the second turn of the tube = S2 / λ2, the side wing spacing E3 of the third turn of the tube = S3 / λ3, the side wing spacing E4 of the fourth turn of the tube = S4 / λ4, and En ≥ D + d / 2.

[0077] In the x-axis (horizontal) direction, the straight pipe sections of each turn and each column of tubes are arranged at equal distances between adjacent turns (except for the adjacent columns of tubes at the central axis). L is the pipe distance in the x-axis direction between adjacent straight pipe sections of the horizontal columns of the same turn. The distance between adjacent columns at the central axis is mn, and mn = 2Ln = 2L[1 - (n - 1) / N]. In this example, for the first turn, m1 = 2L; for the second turn, m2 = 3 / 2L; for the third turn, m3 = L; for the fourth turn, m4 = 1 / 2L. The total pipe distance of the columns in the x-axis direction is Mn, and Mn = L*[k - 2(n - 1) / N]. In this case, for the first turn of the columns, the total length M1 in the X-axis direction = kL; for the second turn of the columns, the total length M2 in the X-axis direction = L(k - 1 / 2); for the third turn of the columns, the total length M3 in the X-axis direction = L(k - 1); for the fourth turn of the columns, the total length M4 in the X-axis direction = L(k - 3 / 2). The vertical columns on the side wings of each turn of the columns are arranged in an equally divided and staggered manner from the outside to the inside. The distance between the projections of the adjacent straight pipe sections on the x-axis is equal, and the distance is l', which is the ratio of the pipe distance L in the x-axis direction between adjacent straight pipe sections of the horizontal columns of the same turn to the number of layers N. On the premise of ensuring winding, maintaining the minimum staggered distance l' can ensure that each layer has the largest horizontal cross-section and increase the heat exchange effect. In this case, l' = L / 4; the distance ln in the x-axis direction between the side wings of different turns of the columns = L[1 - (n - 1) / N], and L ≥ Nd. In this case, l1 = L; l2 = 3 / 4L; l3 = 1 / 2L; l4 = 1 / 4L.

[0078] The total distance M in the x-axis direction of the straight pipe sections of the horizontal columns of the same turn > the total height S in the y-axis direction of the columns of the same turn, ensuring that the open-type spiral-wound condenser R3 has a larger evaporation surface A in the cross-section.

[0079] The heat exchange area of the open-type spiral-wound condenser R3 is calculated as follows:

[0080] The first step is to calculate the heat exchange quantity:

[0081] Given that the heat exchange quantity of the condenser is Qr, the heat consumed by the compressor is Qw, and the refrigerating capacity is Qc. According to the law of conservation of energy, we have:

[0082] Qr = Qw + Qc

[0083] The second step is to calculate the heat transfer area:

[0084] Given the thermal conductivity K, Tr is the average temperature of the hotter medium, and △t is the average temperature of the less hot medium. From the heat transfer formula, the heat exchange area is A. We get:

[0085] A = Qr / K(Tr - △t)

[0086] The third step is to calculate the length of the tubes:

[0087] Given the heat exchange area A and the tube diameter d. From the area formula, the total length L of each tube winding is obtained:

[0088] L = A / dπ

[0089] The number of tube rows, the number of winding turns, and the winding pitch are adjusted according to the installation space, cross-sectional size, etc. The actual total length is not less than the designed length L.

[0090] Summary:

[0091] This kind of structure is smaller in volume, higher in winding density than the parallel tube in-line type or spiral circular winding type heat exchanger, and can obtain a longer extension length on the same axis, increasing the tube pass, increasing the heat transfer area A of a single tube row, and obtaining more heat transfer quantity Qr = A * K(Tr - △t):

[0092] The x-axis spacing M is greater than the y-axis spacing S, increasing the cross-sectional area of the condenser, ensuring that the cooling water tank has a larger evaporation area and facilitating the vaporization and evaporation of the cooling water; the smaller staggered layer spacing l' between each turn of tube rows not only ensures the uniform distribution of each layer of flank columns but also ensures that the cross-section of each winding layer is the largest, increasing the winding amount, increasing the total heat transfer area A, and obtaining more heat transfer quantity; Qr = A * K(Tr - △t);

[0093] While ensuring cleaning, maintaining the minimum tube row winding pitch b can increase the tube row density, making the microchannels formed by the upper and lower staggered layers smaller and the heat transfer more sufficient;

[0094] Adjacent turns of tube rows present a reverse winding structure, and the upper and lower layers of tube bundles form a baffle, increasing the disturbance of water, continuously changing the fluid flow direction and velocity, and can reach turbulence at a very low Reynolds number (Re < 100), improving the heat transfer coefficient K and obtaining more heat transfer quantity; Qr = A * K(Tr - △t);

[0095] The anchor frame spacing between adjacent layers is designed at an equal distance H from the tube row layer spacing between adjacent layers. After each layer of tube rows is wound, the adjacent windings and the anchor frame form a structure without spacing, making the entire condenser form a tight integrated structure and enhancing the overall strength of the condenser;

[0096] In summary: The open-type spiral winding condenser R3 has a compact structure, small volume, high heat transfer efficiency, and is easy to maintain.

[0097] Figures 29 - 30As shown, the open type spiral wound condenser R3 can be replaced by a second open type spiral wound condenser R3a (or called a header type open type spiral wound condenser), which has the same structure as the open type spiral wound condenser R3, including several turns of spiral refrigerant tube windings and several layers of anchor frames, but the end cover 30a of the refrigerant manifold of the open type spiral wound condenser R3 is cancelled and its bottom plate 30b is retained, the bottom plate 30b is divided into a steam end bottom plate 30b-1 and a liquid end bottom plate 30b-2; a refrigerant steam inlet system and a refrigerant liquid outlet system are also added, the refrigerant steam inlet system includes a refrigerant steam main pipe 31b located above the outer side of the steam end bottom plate 30b-1, a steam branch pipe 31c and several steam inlet pipe bundles 31d interconnected thereunder, the several steam inlet pipe bundles 31d The other end of the plurality of liquid outlet pipes 32d is connected with the straight tube inlet sections 341 of the plurality of spiral refrigerant tubes 34 through the plurality of tube holes 302 on the steam end bottom plate 30b-1. The plurality of steam inlet tube bundles 31d maintain equal length and equal distance, so that the refrigerant is evenly distributed in each tube, so that each tube exchanges heat evenly and achieves the best condensation effect; the refrigerant liquid outlet system includes a refrigerant liquid main pipe 32b located below the outer side of the liquid end bottom plate 30b-2 and a liquid branch pipe 32c and a plurality of liquid outlet pipes 32d interconnected above it. The other ends of the plurality of liquid outlet pipes 32d are connected with the plurality of tube holes 302 on the liquid end bottom plate 30b-2. Each plurality of liquid outlet pipes 32d maintains a certain downward inclined angle with the straight tube outlet sections 342 of the plurality of spiral refrigerant tubes 34, so as to facilitate the outflow of the refrigerant after condensation and effectively prevent the deposition of liquid refrigerant.

[0098] Compared with the open type spiral wound condenser, the second open type spiral wound condenser omits the end cover of the refrigerant manifold box, and replaces the refrigerant manifold box, refrigerant inlet pipe and refrigerant outlet pipe with the steam end bottom plate, liquid end bottom plate, refrigerant steam inlet system and refrigerant liquid outlet system, and has the characteristics of simple structure and low cost.

[0099] Figure 31 As shown, the water distributor adopts an H-type same-path multi-stage water distributor, including a water distributor main pipe, multi-stage water distribution pipes and a plurality of water distribution heads that are interconnected. Each lower-level water distribution pipe is vertically connected to the upper-level water distribution pipe to form a multi-stage H-shape, and a plurality of water distribution heads are distributed at both ends of the last-level water distribution pipe, so that each water distribution head is finally presented on the same horizontal plane, and each adjacent water distribution head is arranged equidistantly, thereby forming a uniform water distribution head array; the other end of the water distributor main pipe is connected to the cooling circulation pump, and the cooling water that has been heated by heat exchange in the cooling water tank passes through the evenly distributed water distribution heads, enters the multi-stage water distribution pipes, the water distributor main pipe, and finally enters the cooling pump and the sprinkler through the cooling pump guide pipe to enter the next cooling cycle.

[0100] The use of an H-shaped same-way multi-stage water distributor can make the low-temperature cooling water cooled on the surface of the cooling water tank move uniformly horizontally downward in the vertical direction, just like a "piston" formed by the side wall of the water tank; through the setting of the H-shaped same-way multi-stage water distributor, it can effectively prevent the disordered heat exchange between the cooling water and the refrigerant tubes, avoid the situation of incomplete backflow caused by the high flow rate in the inlet area of the circulation pump and the low flow rate in the far end area of the inlet of the circulation pump in the state without a water distributor; ensure that the low-temperature cooling water passes through the "micro-channel" group formed by the reverse winding of the upper and lower two turns of spiral refrigerant tube windings from top to bottom and exchanges heat layer by layer with the refrigerant tubes, forming water layers with different gradients of the same temperature flowing downward vertically through each layer of tubes, thereby improving the cooling effect of the cooling water. The setting of the H-shaped same-way multi-stage water distributor is a necessary guarantee for the realization of the functions of the heat exchanger, and realizes the efficient heat exchange of the heat exchanger.

[0101] For the open-type spiral-wound condenser in the above form, since the spiral refrigerant tube windings of adjacent two turns rotate in opposite directions, a certain angle is formed between the upper and lower two turns of tubes, and countless micro-channels are formed on the vertical plane of the open-type spiral-wound condenser. And because the surface of each tube is arc-shaped, the micro-channel is of a non-planar structure, constantly changing the flow direction and flow rate of water, enhancing the disturbance of the cooling water, forming turbulent flow and chaotic flow, and further improving the heat transfer coefficient; not only can ensure the full heat exchange between the refrigerant in the spiral refrigerant tubes and the cooling water in the cooling water tank, but also can make a part of the latent heat of vaporization generated by the heat exchange between the refrigerant and the cooling water be released through the water surface of the cooling water tank, thus achieving an effect that cannot be achieved by a shell-and-tube heat exchanger, using the latent heat of vaporization of water to increase the heat exchange amount per unit of water, so that the heat exchange efficiency is higher than that of a shell-and-tube heat exchanger; and the open-type spiral-wound condenser is more convenient for cleaning and maintenance.

[0102] Preferably, the anchor frame and the refrigerant collection box adopt the process of welding carbon steel and then performing hot-dip galvanizing to prevent and delay oxidation in high-temperature and high-humidity environments.

[0103] Preferably, the spiral refrigerant tubes are made of inner-threaded copper tubes with a wall thickness of 8-15 um and a diameter of 10-15 mm, or other metal materials such as titanium alloy, aluminum alloy, and stainless steel; the straight tube inlet section and the straight tube outlet section of each tube are arranged horizontally in parallel, and the spiral section forms the same angle ∠χ with the anchor frame, and the winding pitch is 1 cm or more, which is convenient for cleaning; while ensuring easy cleaning, maintaining the minimum winding pitch can increase the tube density on the cross section and is conducive to full heat exchange.

[0104] Preferably, the refrigerant collection box is made of carbon steel plate with a thickness of 15 mm or more; the bottom plate of the refrigerant collection box punches out tube holes according to the tube diameter by a machine tool, and the diameter of the tube holes is consistent with the outer diameter of the tubes. The tubes are connected to the bottom plate of the refrigerant collection box by the method of expanding tubes or welding; the whole is treated with a hot-dip galvanizing process to make an anti-corrosion coating.

[0105] Preferably, the bolts adopt a hot-dip galvanized process for carbon steel of 8 mm or above, or are made of the same material as the refrigerant collection box; an anti-leakage cushion layer is attached between the flange plates on the end cover and the bottom plate and fastened by bolts.

[0106] Preferably, the main water distribution pipe, multi-stage branch water pipes and several water distribution heads of the H-shaped parallel-flow multi-stage water distributor can adopt galvanized steel pipes, PUC pipes, PE and other metal pipes, plastic pipes, etc.

[0107] Although the embodiments of the present invention are described in the specification, these embodiments are only for reference and should not limit the protection scope of the present invention. All omissions, substitutions and changes made within the scope not departing from the gist of the present invention should be included in the protection scope of the present invention.

Claims

1. An open-type spiral-wound high-efficiency cooling system, characterized in that, It includes an open-type spiral-wound condenser, a cooling circulation pump, a sprayer, a water distributor, a fan, a cooling packing layer, and a cooling water tank; the open-type spiral-wound condenser is immersed in the cooling water inside the cooling water tank, and the water distributor and the cooling circulation pump are arranged at the inner bottom of the cooling water tank; the sprayer is located above the cooling packing layer and sprays cooling water onto the surface of the cooling packing layer; the cooling packing is placed between the sprayer and the open-type spiral-wound condenser to increase the contact area between the cooling water and the air, further reduce the temperature of the cooling water, and make the cooling water cooled by the cooling packing layer evenly drip onto the water surface of the cooling water tank; the fan is arranged above the sprayer to discharge the latent heat of vaporization of the saturated water vapor vaporized in the cooling packing layer and the cooling water tank to the outdoor atmosphere; The open-type spiral wound condenser includes a refrigerant collection box, several turns of spiral refrigerant tube windings, several layers of anchor frames, a refrigerant inlet pipe, and a refrigerant outlet pipe. The refrigerant collection box is composed of an end cover and a bottom plate. The length and width dimensions of the end cover and the bottom plate match each other, and flange plates of the same size are provided on the outside. A number of screw holes with matching sizes and positions are provided on the flange plates. A number of tube holes are opened in the middle of the bottom plate, and a box-shaped part protrudes in the middle of the end cover. The bottom plate and the end cover are screwed and fastened together by bolts passing through the screw holes on the flange plates, forming a cavity for refrigerant collection. The refrigerant collection box includes a steam-end collection box and a liquid-end collection box arranged oppositely. A collection box refrigerant inlet and a collection box refrigerant outlet are respectively provided above the side of the steam-end end cover and below the side of the liquid-end end cover. The refrigerant inlet pipe extends into the steam-end collection box through the collection box refrigerant inlet to form a steam distribution pipe. Small holes are evenly distributed along the lower edge of the steam distribution pipe, so that the refrigerant steam is evenly sprayed into the entire steam-end collection box, ensuring that each turn of the spiral refrigerant tube winding is evenly supplied with steam, facilitating the uniform distribution of the refrigerant in the tubes to achieve a full condensation and liquefaction effect. The refrigerant outlet pipe is connected to the collection box refrigerant outlet. A deflector plate forming a certain angle with the bottom surface is arranged at the bottom of the liquid-end collection box, so that the condensed refrigerant liquid flows into the refrigerant outlet pipe, facilitating the liquid outflow of the refrigerant and preventing the occurrence of liquid accumulation, and improving the utilization efficiency of the refrigerant. The several layers of anchor frames are vertically and fixedly connected between the bottom plates of the steam-end collection box and the liquid-end collection box. Each layer of anchor frame is composed of four anchor frames, and the projections of each layer of anchor frames on the two bottom plates form two symmetrical anchor frame rectangular structures. The anchor frame rectangular structures formed by the projections of each layer of anchor frames on the bottom plate are centered on the center point of the bottom plate and their sizes decrease in sequence. The several turns of spiral refrigerant tube windings are formed by several turns of spiral refrigerant tubes rotating externally tangent around the corresponding layer of anchor frames at a certain angle. Each turn of the spiral refrigerant tube is composed of several spiral refrigerant tubes. Each spiral refrigerant tube is composed of a straight pipe inlet section, a straight pipe outlet section at both ends and a spiral section in the middle, and a certain winding distance is maintained between each spiral refrigerant tube. The straight pipe inlet section or the straight pipe outlet section of the several spiral refrigerant tubes in each turn is connected to the tube holes on the bottom plate by energy-saving threads by the expansion tube method and is perpendicular to the bottom plate, and is axially symmetrically arranged on the bottom plate in the length and width directions with the center point of the bottom plate as the axis. The projections of the straight pipe inlet sections or the straight pipe outlet sections of the several spiral refrigerant tubes in each turn on the corresponding bottom plate form two symmetrical tube rectangular structures. The positions of the straight pipe inlet sections and the straight pipe outlet sections of each spiral refrigerant tube on the tube rectangular structures projected on the bottom plate are also axially symmetrically arranged with the center point of the bottom plate as the axis, so as to ensure that the distance between each spiral refrigerant tube between the two bottom plates is of the same path, and further ensure the uniformity of the cooling of the refrigerant in the tubes. The rotation angles of the spiral refrigerant tube windings of adjacent two turns with respect to the corresponding layer of anchor frames are opposite, forming a microchannel group; The spiral refrigerant tube is made of a copper tube, a titanium alloy tube, an aluminum alloy tube, or a stainless steel tube; The anchor frame adopts the process of welding carbon steel and then hot-dip galvanizing.

2. The open-type spiral winding high-efficiency cooling system according to claim 1, characterized in that, The open-type spiral-wound condenser is replaced by a second open-type spiral-wound condenser, which has several turns of spiral refrigerant tube windings and several layers of anchor frames with the same structure as the open-type spiral-wound condenser, but the end cover of the refrigerant collection box of the open-type spiral-wound condenser is cancelled, and its bottom plate is retained. The bottom plate is divided into a steam-end bottom plate and a liquid-end bottom plate; a refrigerant steam inlet system and a refrigerant liquid outlet system are also added. The refrigerant steam inlet system includes a refrigerant steam main pipe located above the outside of the steam-end bottom plate and steam branch pipes and several steam inlet tube bundles that are interconnected below it. The other ends of the several steam inlet tube bundles are connected to the straight pipe inlet sections of several spiral refrigerant tubes through several tube holes on the steam-end bottom plate. The several steam inlet tube bundles are of equal length and equal path, facilitating the uniform distribution of the refrigerant in each tube and enabling uniform heat exchange in each tube; the refrigerant liquid outlet system includes a refrigerant liquid main pipe located below the outside of the liquid-end bottom plate and liquid branch pipes and several liquid outlet pipes that are interconnected above it. The other ends of the several liquid outlet pipes are connected to several tube holes on the liquid-end bottom plate. Each of the several liquid outlet pipes forms a certain downward inclination angle with the straight pipe outlet section of several spiral refrigerant tubes, facilitating the outflow of the condensed refrigerant and effectively preventing the deposition of liquid refrigerant.

3. The open-type spiral winding high-efficiency cooling system according to claim 1 or 2, characterized in that, The water distributor adopts an H-type parallel multi-stage water distributor, which includes a water distributor main pipe, multi-stage branch pipes and several water heads that are interconnected. Each lower-level branch pipe of each stage is vertically connected to its upper-level branch pipe to form a multi-stage H-type. Several water heads are distributed at both ends of the last-stage branch pipe, finally enabling each water head to be on the same horizontal plane, and each adjacent water head to be arranged at equal intervals; the other end of the water distributor main pipe is connected to the cooling circulation pump. The cooling water heated through heat exchange in the cooling water tank enters the multi-stage branch pipes and the water distributor main pipe through the uniformly distributed water heads, and finally enters the cooling pump and the sprayer through the cooling pump guide pipe to enter the next cooling cycle.

4. The open-type spiral winding high-efficiency cooling system according to claim 1, characterized in that The refrigerant collection box adopts the process of welding carbon steel and then hot-dip galvanizing to prevent and delay oxidation in high-temperature and high-humidity environments.

5. The open-type spiral winding high-efficiency cooling system according to claim 1, characterized in that, The spiral refrigerant tubes adopt inner-thread tubes with a pipe wall thickness of 8-15 μm and a diameter of 10-15 mm; the straight pipe inlet sections and straight pipe outlet sections of each tube are arranged horizontally and parallel, and the spiral section forms the same angle with the anchor frame and the winding pitch is 1 cm or more.

6. The open-type spiral winding high-efficiency cooling system according to claim 4, wherein The refrigerant collection box adopts a carbon steel plate material with a thickness of 15 mm or more; the bottom plate of the refrigerant collection box punches out tube holes according to the tube diameter by a machine tool. The diameter of the tube holes is consistent with the outer diameter of the tubes. The tubes are connected to the bottom plate of the refrigerant collection box by the expansion tube method or the welding method; the whole is treated with an anti-corrosion coating by the hot-dip galvanizing process.

7. The open-type spiral winding high-efficiency cooling system according to claim 4, wherein, The bolts adopt the process of hot-dip galvanizing of carbon steel with a diameter of 8 mm or more, or are consistent with the material of the refrigerant collection box; an anti-leakage cushion is attached between the flange plates on the end cover and the bottom plate and fastened by bolts.

8. The open-type spiral winding high-efficiency cooling system according to claim 3, characterized in that The water distributor main pipe, multi-stage branch pipes and several water heads of the H-type parallel multi-stage water distributor adopt metal pipes or plastic pipes.

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