Peak cooling device of direct air cooler

Abstract

A peak cooling device of a direct air cooler belongs to the related technical field of air cooler equipment, is mounted in an air cooling condenser and comprises a first nozzle group and a second nozzle group, the first nozzle group is composed of a plurality of first nozzles, and the second nozzle group is composed of a plurality of second nozzles; in the air-cooled condenser unit, the first nozzle group and the second nozzle group are arranged in a central symmetry manner by taking the axis of an axial flow fan of the air-cooled condenser unit as a symmetric line; the plurality of first nozzles of the first nozzle group are non-uniformly arranged, and the plurality of second nozzles of the second nozzle group are non-uniformly arranged. The nozzles capable of spraying water mist are arranged, and the cooling effect of the air-cooled condenser can be further improved in cooperation with an air cooling mode. Through model analysis of the rotating airflow field, the layout mode of the nozzles is designed, and the arrangement density of the nozzles corresponding to a high-wind-speed area is large, so that the uniformity degree of water mist in the rotating airflow field can be increased, and the cooling effect of the air-cooled condenser is further improved.

Description

Technical Field

[0001] The utility model relates to the technical field related to air cooler equipment, and more specifically, particularly relates to a direct air cooler peak cooling device. Background Art

[0002] The economic development of countries around the world today has made energy conservation and emission reduction an important issue. In my country, thermal power generation is dominant. Thermal power generation not only consumes energy resources, but also consumes a lot of water resources. The water shortage in Northeast, North China and Northwest my country, which are rich in coal resources, is very serious. Therefore, thermal power plants in these areas mostly use air cooling units to reduce the consumption and dependence on water resources. Air cooling units are widely used in these coal-rich and water-scarce areas.

[0003] The principle of air cooling technology is to use ambient air to directly or indirectly cool the exhaust steam of the steam turbine to condense it. Air cooling technology will become the dominant cooling technology in thermal power plants. Air cooling includes direct air cooling and indirect air cooling. There are many problems in the actual operation of direct air cooling units. Among them, the output of air cooling units is blocked and cannot be fully generated during the high temperature season in summer, which is a common problem in power plants using direct air cooling. In the summer with high temperatures, the cooling capacity of the air cooler is significantly reduced. Taking necessary summer measures to reduce the inlet air temperature of the air cooler and enhance the heat exchange effect of the air cooling radiator is one of the effective ways.

[0004] In recent years, in order to solve the problem of air-cooling system in summer, many power plants have installed water spray systems on air-cooled condensers, which can reduce the operating back pressure of air-cooled units by increasing the humidity of the air and lowering the dry bulb temperature of the air. The existing water spray system is equipped with multiple uniformly arranged nozzles. Multiple nozzles are arranged in the air-cooled condenser unit of the air-cooled unit. Between the fin tube bundle and the axial flow fan of the air-cooled condenser unit, multiple nozzles spray at high pressure to implement summer peak cooling, thereby reducing the back pressure of the air-cooled unit and reducing coal consumption. However, due to the characteristics of the axial flow fan, the wind it blows rises in a spiral, and the air is not evenly distributed in the fin tube bundle. The heat dissipation effect of different areas of the fin tube bundle varies greatly, and the existing uniform spray device cannot achieve the ideal cooling state. Utility Model Content

[0005] 1. Technical issues:

[0006] In summary, how to further improve the cooling effect of the air-cooled condenser has become an urgent problem to be solved by those skilled in the art.

[0007] (II) Technical solution:

[0008] To achieve the above-mentioned object, the utility model provides a direct air cooler peak cooling device, which is installed in an air-cooled condenser. In the utility model, the direct air cooler peak cooling device includes a nozzle unit;

[0009] The nozzle unit includes a first nozzle group and a second nozzle group, the first nozzle group is composed of a plurality of first nozzles, and the second nozzle group is composed of a plurality of second nozzles;

[0010] In the air-cooled condenser unit, the first nozzle group and the second nozzle group are centrally symmetrically arranged with the axis of the axial flow fan of the air-cooled condenser unit as a symmetry line;

[0011] The plurality of first nozzles of the first nozzle group are arranged non-uniformly, and the plurality of second nozzles of the second nozzle group are arranged non-uniformly.

[0012] Preferably, in the direct air cooler peak cooling device provided by the present invention, the first nozzle group is arranged in parallel with the fin tube bundle on one side of the air-cooled condenser unit, and the second nozzle group is arranged in parallel with the fin tube bundle on the other side of the air-cooled condenser unit.

[0013] Preferably, in the direct air cooler peak cooling device provided by the utility model, in the air-cooled condenser, the air-cooled condenser includes an axial flow fan and a heat sink, and a rotating airflow field is formed in the air-cooled condenser by the axial flow fan. Under the rotating airflow field, the heat sink is affected by the different air flow directions and sizes, including a leeward part and a windward part;

[0014] The straight-line distance between the nozzle unit arranged corresponding to the leeward part and the heat sink is d1, and the straight-line distance between the nozzle unit arranged corresponding to the windward part and the heat sink is d2, wherein d1<d2.

[0015] Preferably, in the direct air cooler peak cooling device provided by the utility model, the rotating airflow field includes a low wind speed area and a high wind speed area according to the wind speed;

[0016] The arrangement density of the nozzle units corresponding to the low wind speed zone is less than the arrangement density of the nozzle units corresponding to the high wind speed zone.

[0017] Preferably, in the direct air cooler peak cooling device provided by the present invention, the first nozzle group includes A rows and B columns of nozzles, wherein the spacing between the nozzles in column b1 on one side is greater than the spacing between the nozzles in the other row b2; B=b1+b2.

[0018] Preferably, in the direct air cooler peak cooling device provided by the present invention, in the first nozzle group and in the blowing direction of the axial flow fan, multiple rows of nozzles close to the axial flow fan form a settlement relative to the heat sink.

[0019] Preferably, in the direct air cooler peak cooling device provided by the present invention, the spacing between the nozzles in the top row a1 is greater than the spacing between the nozzles in the other rows a2; A=a1+a2.

[0020] Preferably, in the direct air cooler peak cooling device provided by the utility model, a plurality of the nozzle units are provided, and the plurality of the nozzle units correspond one-to-one to the plurality of air-condenser units of the air-condenser.

[0021] Preferably, in the direct air cooler peak cooling device provided by the utility model, the first nozzle and the second nozzle are both 0.15 mm nozzles.

[0022] Preferably, in the direct air cooler peak cooling device provided by the present invention, the water supply pressure range of the first nozzle and the second nozzle is 4MPa-5MPa.

[0023] (III) Beneficial effects:

[0024] From the above, it can be seen that the utility model provides a direct air cooler peak cooling device, which is installed in an air-cooled condenser, and the direct air cooler peak cooling device includes a nozzle unit; the nozzle unit includes a first nozzle group and a second nozzle group, the first nozzle group is composed of a plurality of first nozzles, and the second nozzle group is composed of a plurality of second nozzles; in the air-cooled condenser unit, the first nozzle group and the second nozzle group are arranged in a centrally symmetrical manner with the axis of the axial flow fan of the air-cooled condenser unit as the symmetry line; the plurality of first nozzles of the first nozzle group are arranged non-uniformly, and the plurality of second nozzles of the second nozzle group are arranged non-uniformly.

[0025] Through the above structural design, the utility model is provided with a nozzle capable of spraying water mist, and in combination with the air cooling method, the cooling effect of the air-cooled condenser can be further improved. In addition, through the model analysis of the rotating air flow field, the utility model designs the layout of the nozzles, and the nozzles are arranged with a high density corresponding to the high wind speed area, which can increase the uniformity of the water mist in the rotating air flow field, and further improve the cooling effect of the air-cooled condenser. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] The drawings constituting part of the present application are used to provide a further understanding of the present invention. The exemplary embodiments and descriptions of the present invention are used to explain the present invention and do not constitute an improper limitation on the present invention. Among them:

[0027] Figure 1 This is the distribution diagram of atomized particle size parameters under different pressures when a 0.15mm aperture nozzle is used in the utility model;

[0028] Figure 2 is the air flow velocity distribution diagram in the rotating air flow field;

[0029] Figure 3 This is a schematic structural diagram of an air-cooled condenser unit in an embodiment of the utility model;

[0030] Figure 4 This is a schematic diagram of the distribution structure of the nozzles in the air-cooled condenser unit in the embodiment of the utility model;

[0031] Figure 5 This is a distribution layout diagram of the nozzles in the first nozzle group in an embodiment of the utility model.

[0032] exist Figure 1 Middle, D 10 , D 50 and D 90 Respectively represent that the volume of particles smaller than this size accounts for 10%, 50% and 90% of the total volume of particles. (4，3) is the volume weighted average particle size, D (3，2) is the average particle size of Sauter.

[0033] exist Figure 2 In the middle, the wind speed in the corner is faster, forming a high wind speed area.

[0034] exist Figures 3 to 5 In the figure, the corresponding relationship between the component names and the reference numerals is as follows:

[0035] Axial flow fan 1, heat sink 2, nozzle 3. DETAILED DESCRIPTION

[0036] The present invention will be described in detail below with reference to the accompanying drawings and in conjunction with embodiments. Each example is provided by way of explanation of the present invention and does not limit the present invention. In fact, it will be clear to those skilled in the art that modifications and variations may be made in the present invention without departing from the scope or spirit of the present invention. For example, a feature shown or described as a part of one embodiment may be used in another embodiment to produce yet another embodiment. Therefore, it is desired that the present invention includes such modifications and variations within the scope of the appended claims and their equivalents.

[0037] In the description of the present invention, the terms "longitudinal", "lateral", "upper", "lower", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom" and the like indicate directions or positional relationships based on the directions or positional relationships shown in the accompanying drawings. They are only for the convenience of describing the present invention and do not require that the present invention must be constructed and operated in a specific direction. Therefore, they cannot be understood as limitations on the present invention. The terms "connected" and "connection" used in the present invention should be understood in a broad sense. For example, they can be fixed connections or detachable connections; they can be directly connected or indirectly connected through intermediate components. For ordinary technicians in this field, the specific meanings of the above terms can be understood according to specific circumstances.

[0038] Please refer to Figures 1 to 5 ,in, Figure 1 This is the distribution diagram of atomized particle size parameters under different pressures when a 0.15mm aperture nozzle is used in the utility model; Figure 2 is the air flow velocity distribution diagram in the rotating air flow field; Figure 3 This is a schematic structural diagram of an air-cooled condenser unit in an embodiment of the utility model; Figure 4 This is a schematic diagram of the distribution structure of the nozzles in the air-cooled condenser unit in the embodiment of the utility model; Figure 5 This is a distribution layout diagram of the nozzles in the first nozzle group in an embodiment of the utility model.

[0039] The utility model provides a direct air cooler peak cooling device. The design method of the device is as follows: comprising the following steps.

[0040] Step 1: Design a study model of the air-cooled condenser unit.

[0041] Among them, taking the air-cooled condensers in existing power plants as a reference, the air-cooled condenser unit is designed, and the research model is designed as Type A (the appearance structure of the air-cooled condenser unit is like the letter A), in which the steam distribution box is the top of A, the finned tube bundle is the two sides of A, the condensate header is the two bottom ends of A, and the axial flow fan is the horizontal side of A.

[0042] Step 2: Analyze and study the rotating airflow field of the model.

[0043] Among them, when analyzing the rotating airflow field, it includes studying the axial flow velocity of the fan outlet section of the rotating airflow field to obtain the axial flow velocity distribution law; studying the circumferential flow velocity of the fan outlet section of the rotating airflow field to obtain the circumferential flow velocity distribution law; studying the radial flow velocity of the fan outlet section of the rotating airflow field to obtain the radial flow velocity distribution law; studying the areas at different heights of the rotating airflow field to obtain the airflow distribution law; studying the velocity and pressure of the rotating airflow field on the outlet surface of the fin tube bundle to obtain the outlet surface velocity and pressure distribution law of the fin tube bundle; studying the velocity vectors of the rotating airflow field on different sections of the fan to obtain the velocity vector distribution law. After research and analysis, the conclusions are as follows:

[0044] First, the axial flow velocity distribution law is: the axial velocity of the air flow in the fan outlet section varies greatly along the radial direction, and a negative value appears in the central hub area of ​​the axial flow fan (indicating the existence of air recirculation). Along the radial direction of the blades of the axial flow fan, the flow velocity gradually increases with the increase of the radius, and gradually decreases after reaching the maximum value (the air flow is hindered to a certain extent near the wall of the axial flow fan, and a small amount of recirculation vortex will appear between the tip of the blade and the wall, weakening the axial flow of the air).

[0045] Second, the circumferential velocity distribution law is: starting from the center point of the axial flow fan, gradually increasing along the radial direction, starting to fluctuate radially near the root of the axial flow fan blade, until it rapidly increases near the top of the axial flow fan blade. This reflects that the axial flow fan blade has a certain degree of twist in the design, and the good aerodynamic performance makes the circumferential velocity and radius not a simple positive correlation, which also reflects the complex and changeable characteristics of the flow field inside the air-cooled condenser unit.

[0046] Third, the radial flow velocity distribution law is: the radial flow velocity first increases along the radial direction, and then begins to decrease at the connection between the blade and the hub (this is the result of the combined influence of the connection between the blade and the hub of the axial flow fan and the aerodynamic performance of the blade profile at the root of the blade), and then gradually increases in the radial direction (the rotating axial flow fan causes the airflow to be affected by centrifugal force, and the airflow as a whole has an outward flow trend, and the magnitude of the centrifugal force is proportional to the radius), and decreases near the top of the blade of the axial flow fan (the blade tip is weakened due to the constraint of the wall), reflecting that the radial velocity at the outlet of the axial flow fan is not zero and cannot be ignored.

[0047] Fourth, the law of air flow distribution is: as the height increases, due to the influence of the resistance of the fin tube bundle, the overall air flow velocity gradually decreases, while the radial flow velocity gradually increases, and the radial flow velocity increases with the increase of the radius (this law is the same for cross-sections at different heights of the air-cooled condenser unit. During the process of air flow rising, although the flow field area decreases, the phenomenon of the gradual increase of air flow velocity along the radial position has not changed).

[0048] Fifth, the velocity and pressure distribution law of the outlet surface is: the velocity distribution generally shows that one side is relatively large and the other side is relatively small. This is because when the axial flow fan rotates clockwise, the air is a clockwise rotating vortex, and the fin tube bundles on both sides hinder the airflow, causing a large amount of air to flow to the diagonal of the fin tube bundle. At the same time, since the air needs to change its flow direction when it flows into the flow channel of the fin tube bundle, the angle between the air flow direction and the flow channel direction is related to the energy loss of the air flowing through the flow channel. These two reasons make the velocity distribution on the outlet surface generally show that half is relatively large and the other half is relatively small; the pressure gradually increases along the steam flow direction (the steam flow direction is from the steam distribution box to the condensate manifold), which corresponds to the pressure distribution near the fin tube bundle in the air-cooled condenser unit.

[0049] Sixth, the velocity vector distribution law is: the air flow velocity gradually increases from the center of the fan to the edge of the fan (due to the rotation of the blades of the axial flow fan, the air moves upward in a spiral form after passing through the axial flow fan, and the air flow velocity gradually increases from the center of the axial flow fan to the edge of the axial flow fan), and an air mass with high density and speed is formed at the edge of the fan under the action of centrifugal force, and a vortex is formed above the hub.

[0050] Comprehensive analysis shows that the air velocity distribution on the outlet plane of the axial flow fan is extremely uneven. As the complex airflow rises in the air-cooled condenser unit, it is bound to affect the heat dissipation effect of the fin tube bundle.

[0051] Step 3: Perform parameter study on the nozzle required for spike cooling.

[0052] As shown in the figure, when conducting parameter research, the pressure range is set between 2 and 10 MPa, and nozzles with apertures of 0.15 mm, 0.3 mm, 0.5 mm, and 0.8 mm are selected as test nozzles, respectively. The particle size data of nozzle atomization under different pressures are measured at a distance of 300 mm from the nozzle outlet (where D10, D50, and D90 represent the volume of particles smaller than this particle size, which accounts for 10%, 50%, and 90% of the total particle volume, respectively; D(4,3) is the volume-weighted average particle size; and D(3,2) is the Sauter average particle size).

[0053] Please refer to Figure 1 , Figure 1 This is a distribution diagram of atomized particle size parameters under different pressures when a 0.15 mm aperture nozzle is used in the utility model.

[0054] From the research results, it can be found that when a nozzle with an aperture of 0.15mm is selected, the spray particle size produced by the nozzle is negatively correlated with the increase of pressure, that is, the atomized particle size will continue to decrease. At the same time, when the spray pressure is greater than 6MPa, the change of the spray particle size with the increase of pressure is significantly reduced. When a nozzle with an aperture of 0.15mm is selected, when the spray pressure is 4MPa, it can be observed that 90% of the atomized particle size is below 20μm. Therefore, in order to reduce the operating cost and achieve the design purpose of the spray particle size below 20μm, the utility model can achieve the purpose by using a pressure of 4.5MPa.

[0055] Step 4: Based on the rotating airflow field and parameter research, the nozzle layout rules are obtained, modeling and analysis are performed to obtain the nozzle layout and spray particle size.

[0056] Comprehensively considering steps two and three, the nozzle arrangement rule is obtained. Specifically, under the rotating airflow field, the direction and size of air flow in different parts of the same fin tube bundle are different, which can be roughly divided into the leeward part and the windward part. The ability of the air in the two parts to carry water droplets is very different. When arranging the nozzles, the influence of the rotating airflow field should be fully considered. When arranging the nozzles in the leeward part, due to its low entrainment capacity, it should be as close to the fin tube bundle as possible to avoid insufficient air entrainment capacity, causing water droplets to fall directly to the ground and waste water resources; when arranging the nozzles in the windward part, due to the strong entrainment capacity of this part of the air, the nozzle can be moved away from the fin tube bundle, which can increase the coverage of the spray and make the water mist thin and uniform.

[0057] When conducting modeling analysis, the SolidWorks modeling tool was used, the Realizable k-ε model was adopted, multiple reference systems were selected around the axial fan blades to handle the rotating area, the porous medium model was used to handle the fin tube bundle, and the DPM model was used for nozzle spray setting.

[0058] When conducting modeling analysis, a comparative analysis was used to obtain the optimal solution. Specifically, taking 10000mm×10000mm as the bearing area of ​​the finned tube bundle, the uniformly arranged nozzles and the non-uniformly arranged nozzles were compared, and the injection particle size of 40 microns and the injection particle size of 20 microns were selected for analysis to obtain the nozzle arrangement and injection particle size.

[0059] The analysis is as follows: The non-uniform arrangement of nozzles has a certain enhancement effect and can enhance the effect of spray cooling. Most of the 20-micron droplets can evaporate before reaching the heat exchanger. Only in the upper part, where the nozzles are too close to the fin tube bundle, there will be droplets passing through the fin tube bundle, so the upper nozzles can be arranged downward. The droplet diameter doubles, and the droplet residence time increases by more than 4 times. From the perspective of uniform nozzle arrangement, the use of 40-micron droplets will cause a large number of droplets to not evaporate before contacting the fin tube bundle, and the non-uniform nozzle arrangement (moving some of the upper nozzles downward) is conducive to improving this situation.

[0060] Comprehensive analysis shows that the non-uniform arrangement of nozzles has a better effect on the temperature drop of the air-cooled condenser unit. Specifically, on the bearing surface of 10000mm×10000mm on both sides, there are 49 nozzles on each side, a total of 98 nozzles, which are densely arranged in the area with higher flow rate, and the nozzles are arranged downward at the top. Specifically, the multiple nozzles of the nozzle group on each side are distributed in 7 rows and 7 columns, from the first row to the seventh row from top to bottom, and from the first column to the seventh column from left to right. From the first row to the third row, the spacing between adjacent rows is 1400mm, and from the third row to the seventh row, the spacing between adjacent rows is 950mm; from the first column to the third column, the spacing between adjacent columns is 600mm, and from the third column to the seventh column, the spacing between adjacent columns is 1500mm.

[0061] As shown in the figure, the utility model also provides a direct air cooler peak cooling device. In one embodiment of the utility model, the direct air cooler peak cooling device is installed in an air-cooled condenser, and includes a plurality of nozzle units, and the plurality of nozzle units correspond one to one to the plurality of air-cooled condenser units of the air-cooled condenser. Each nozzle unit includes a first nozzle group and a second nozzle group; in the air-cooled condenser unit, the first nozzle group and the second nozzle group are symmetrically arranged; the plurality of first nozzles of the first nozzle group are non-uniformly arranged, and the plurality of second nozzles of the second nozzle group are non-uniformly arranged.

[0062] Furthermore, in the present embodiment, the first nozzle group is arranged in parallel with the fin tube bundle on one side of the air-conditioning condenser unit, and the second nozzle group is arranged in parallel with the fin tube bundle on the other side of the air-conditioning condenser unit; the first nozzle group includes A rows and B columns of nozzles 3, wherein the spacing between the nozzles 3 in the top a1 row is greater than the spacing between the nozzles 3 in other a2 rows, and the spacing between the nozzles 3 in the b1 column on one side is greater than the spacing between the nozzles 3 in other b2 rows, wherein: A=a1+a2, B=b1+b2.

[0063] The direct air cooler peak cooling device provided by the utility model is installed in an air condenser, and the air condenser includes an axial flow fan 1 and a heat sink 2. The heat sink 2 is provided with two groups, and the two groups of heat sinks 2 are symmetrically arranged about the blowing axis of the axial flow fan 1. The heat sink 2 is inclined and forms an "A"-shaped structure with the axial flow fan 1. The direct air cooler peak cooling device provided by the utility model is used in conjunction with the air condenser, mainly to provide water mist while realizing air cooling of the heat sink 2 to further improve the heat dissipation effect of the heat sink 2.

[0064] In the utility model, the direct air cooler peak cooling device includes a nozzle unit, which refers to the general term for all nozzles 3 used in conjunction with an air-cooled condenser. When there are multiple air-cooled condensers, each air-cooled condenser is correspondingly provided with a nozzle unit (the nozzle unit does not refer to one nozzle 3, but a nozzle group composed of multiple nozzles 3 arranged and installed according to the design).

[0065] Specifically, the nozzle unit includes a first nozzle group and a second nozzle group (dividing the multiple nozzles 3 constituting the nozzle unit into two groups), the first nozzle group is composed of multiple first nozzles, and the second nozzle group is composed of multiple second nozzles. In the present utility model, the nozzle 3 used by the first nozzle and the second nozzle has the same structure and type. The present utility model is divided into the first nozzle and the second nozzle only for the convenience of structural description. Further, the first nozzle and the second nozzle are both 0.15mm nozzles 3, and the water supply pressure range of the first nozzle and the second nozzle is 4MPa-5MPa. After many experiments by the designers, it was found through research that when a nozzle 3 with an aperture of 0.15mm is selected, as the pressure increases, the spray particle size generated by the nozzle 3 is negatively correlated, that is, the atomized particle size will continue to decrease. At the same time, when the spray pressure is greater than 6MPa, the change of the spray particle size with the increase of pressure is significantly reduced. When a nozzle 3 with an aperture of 0.15mm is selected, when the spray pressure is 4MPa, it can be observed that 90% of the atomized particle size is below 20μm. Therefore, in order to reduce the operating cost and realize the design purpose of the spray particle size being below 20 μm, the utility model can achieve the purpose by using a pressure of 4.5 MPa.

[0066] In the air-cooled condenser unit, with the axis of the axial flow fan 1 of the air-cooled condenser unit (under ideal conditions, the rotating airflow field formed by the axial flow fan 1 is a conical airflow, which is coaxial with the fan hub axis of the axial flow fan 1, and the axis used in the discussion of the present invention is this axis) as the symmetry line, the first nozzle group and the second nozzle group are arranged in a centrally symmetrical manner.

[0067] Please refer to Figure 2 , Figure 2 This is the air flow velocity distribution diagram in the rotating air flow field.

[0068] According to the analysis of the rotating airflow field, the airflow velocities in the rotating airflow field are different. According to the airflow velocities in the rotating airflow field, the utility model designs the nozzle 3 as follows: the multiple first nozzles of the first nozzle group are arranged unevenly, and the multiple second nozzles of the second nozzle group are arranged unevenly. The setting density is larger in the area with faster speed, and the setting density is reduced in the area with slower speed, that is, the rotating airflow field includes a low wind speed zone and a high wind speed zone according to the wind speed, and the setting density of the nozzle unit corresponding to the low wind speed zone is less than the setting density of the nozzle unit corresponding to the high wind speed zone.

[0069] The nozzle 3 is arranged on the inner side of the heat sink 2 and has the following structural relationship with the fin-tube bundle constituting the heat sink 2: the first nozzle group is arranged parallel to the fin-tube bundle on one side of the air-cooled condenser unit, and the second nozzle group is arranged parallel to the fin-tube bundle on the other side of the air-cooled condenser unit. In this embodiment, all the nozzles 3 constituting the first nozzle group are located in the same plane, and all the nozzles 3 constituting the second nozzle group are located in the same plane.

[0070] In another embodiment of the utility model, in an air-cooled condenser, the air-cooled condenser includes an axial flow fan 1 and a heat sink 2, and a rotating airflow field is formed in the air-cooled condenser by the axial flow fan 1. Under the rotating airflow field, the heat sink 2 is affected by the different air flow directions and sizes, including a leeward part and a windward part; the straight-line distance between the nozzle unit corresponding to the leeward part and the heat sink 2 is d1, and the straight-line distance between the nozzle unit corresponding to the windward part and the heat sink 2 is d2, wherein d1<d2. In this embodiment, the nozzle 3 is not arranged in the same plane, but is higher or lower relative to the heat sink 2 (reflected in the distance between the nozzle unit and the heat sink 2).

[0071] In the present utility model, the arrangement position of the nozzle 3 in the air-cooled condenser has a great influence on the cooling effect of the spray humidification system. Through the position optimization research of nozzles 3 with various apertures in the three-dimensional direction, it is found that: in the z direction, the farther the nozzle 3 is from the radiator (the vertical distance from the radiator), the better the cooling effect of the spray humidification system, but because the nozzle 3 is symmetrically arranged, it is necessary to pay attention to that the spacing between the nozzles 3 on the left and right sides cannot be too small, otherwise it will affect the evaporation of droplets and thus affect the cooling effect; in the y direction (horizontal direction), under the condition that the height of the nozzle 3 is not too low, the farther the nozzle 3 is from the radiator, the better the cooling effect, otherwise the droplets will fall on the unit floor and cause waste; in the x direction (depth direction), the spacing between the nozzles 3 cannot be too large or too small. If the spacing is too large, the droplets of the outermost nozzle 3 will fall to the periphery of the fan circular surface, and the buoyancy of the fan will be reduced and fall to the ground. If the spacing is too small, it will affect the evaporation of droplets.

[0072] Specifically, the first nozzle group includes A rows and B columns of nozzles 3, wherein the spacing between the nozzles 3 in the b1 column on one side is greater than the spacing between the nozzles 3 in the other b2 rows, B=b1+b2. In the present utility model, two heat sinks 2 are arranged on the left and right to form two oblique sides of the "A" shape, and the front and back of the "A" shape are assumed to be a closed structure, so the entire air-cooled condenser will form a shape similar to a pyramid. In the internal space of the air-cooled condenser, the air flow speed at the corner position is faster, and the multi-column nozzle 3 of the first nozzle group near the corner is arranged with a higher density (reflected in that the spacing between the multi-column nozzles 3 near the angle becomes smaller).

[0073] Since the second nozzle group is centrally symmetrical with the first nozzle group, please refer to the structural design of the first nozzle group mentioned above, and the structure of the second nozzle group will not be described in detail here.

[0074] In addition, in the first nozzle group, and in the blowing direction of the axial flow fan 1, the multiple rows of nozzles 3 close to the axial flow fan 1 form a settlement relative to the heat sink 2 (sedimentation refers to a drop in the height direction. From a macroscopic point of view, the setting density of the nozzles 3 in the settled part increases and the setting height decreases). Specifically, the spacing between the top a1 row of nozzles 3 is greater than the spacing between the other a2 rows of nozzles 3, A=a1+a2. The water mist formed by the nozzle 3 spraying water mist will be affected by the setting height of the nozzle 3. If the nozzle 3 is set lower, the overall height of the water mist will decrease. If the nozzle 3 is set higher, the overall height of the water mist will increase. Similarly, the setting height of the nozzles 3 in each row will also affect the height of the water mist formed in that row. In the utility model, the spacing between the multiple rows of nozzles 3 in the lower layer is reduced.

[0075] In the present invention, there are two main types of water mist sprayed by the nozzle 3, namely, 20 micron droplet water mist and 40 micron droplet water mist. For 20 micron droplets, when the axial flow fan 1 is running at normal power, most of the water mist can evaporate before reaching the heat exchanger. Only for the upper part, where the nozzle 3 is too close to the radiator (heat sink 2), there will be droplets passing through the radiator (heat sink 2). Therefore, in the actual process, the present invention considers the idea of ​​arranging the upper nozzle 3 downward. In order to increase the runoff time of the water mist inside the air-cooled condenser, the present invention considers adjusting the position of the nozzle 3 and arranging the nozzle 3 more at the bottom.

[0076] As can be seen from the above, the utility model provides a direct air cooler peak cooling design method. In the direct air cooler peak cooling design method, the utility model includes the following steps: step one, design a research model of an air-cooled condenser unit; step two, analyze the rotating airflow field of the research model; step three, perform parameter research on the nozzles required for peak cooling; step four, based on the rotating airflow field and the parameter research, obtain the nozzle arrangement law, model and analyze, and obtain the nozzle arrangement mode and injection particle size. In addition, the utility model also provides a direct air cooler peak cooling device, which is installed in an air-cooled condenser. The direct air cooler peak cooling device includes: a plurality of nozzle units, and the plurality of nozzle units correspond to the plurality of air-cooled condenser units of the air-cooled condenser one by one; each of the nozzle units includes a first nozzle group and a second nozzle group; in the air-cooled condenser unit, the axis of the axial flow fan of the air-cooled condenser unit is used as the symmetry line, and the first nozzle group and the second nozzle group are centrally symmetrically arranged; the plurality of first nozzles of the first nozzle group are arranged uniformly or non-uniformly, and the plurality of second nozzles of the second nozzle group are arranged non-uniformly. The utility model is provided with a nozzle capable of spraying water mist, and in combination with an air cooling method, the cooling effect of the air-cooled condenser can be further improved. In addition, through the model analysis of the rotating air flow field, the utility model designs the layout of the nozzles, and the nozzles are arranged with a high density corresponding to the high wind speed area, which can increase the uniformity of the water mist in the rotating air flow field, and further improve the cooling effect of the air-cooled condenser.

[0077] The above are only preferred embodiments of the present invention and are not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A direct air cooler peak cooling device, installed in an air condenser, characterized in that: including a nozzle unit; The nozzle unit includes a first nozzle group and a second nozzle group, the first nozzle group is composed of a plurality of first nozzles, and the second nozzle group is composed of a plurality of second nozzles; In the air-cooled condenser unit, the first nozzle group and the second nozzle group are centrally symmetrically arranged with the axis of the axial flow fan of the air-cooled condenser unit as a symmetry line; The plurality of first nozzles of the first nozzle group are arranged non-uniformly, and the plurality of second nozzles of the second nozzle group are arranged non-uniformly.

2. The direct air cooler peak cooling device according to claim 1, characterized in that: The first nozzle group is arranged in parallel with the fin tube bundle on one side of the air-to-condenser unit, and the second nozzle group is arranged in parallel with the fin tube bundle on the other side of the air-to-condenser unit.

3. The direct air cooler peak cooling device according to claim 1, characterized in that: In the air-to-air condenser, the air-to-air condenser includes an axial flow fan and a heat sink, and the axial flow fan forms a rotating airflow field in the air-to-air condenser. Under the rotating airflow field, the heat sink is affected by the different air flow directions and sizes, including a leeward part and a windward part; The straight-line distance between the nozzle unit arranged corresponding to the leeward part and the heat sink is d1, and the straight-line distance between the nozzle unit arranged corresponding to the windward part and the heat sink is d2, wherein d1<d2.

4. The direct air cooler peak cooling device according to claim 3, characterized in that: The rotating airflow field includes a low wind speed area and a high wind speed area according to the wind speed; The arrangement density of the nozzle units corresponding to the low wind speed zone is less than the arrangement density of the nozzle units corresponding to the high wind speed zone.

5. The direct air cooler peak cooling device according to claim 4, characterized in that: The first nozzle group includes A rows and B columns of nozzles, wherein the spacing between the nozzles in column b1 on one side is greater than the spacing between the nozzles in the other row b2; B=b1+b2.

6. The direct air cooler peak cooling device according to claim 4, characterized in that: In the first nozzle group and in the blowing direction of the axial flow fan, a plurality of rows of nozzles close to the axial flow fan are sunken relative to the heat dissipation plate.

7. The direct air cooler peak cooling device according to claim 6, characterized in that: in, The spacing between the nozzles in the top a1 row is larger than the spacing between the nozzles in the other a2 rows; A=a1+a2.

8. The direct air cooler peak cooling device according to claim 1, characterized in that: A plurality of the nozzle units are provided, and the plurality of the nozzle units correspond one-to-one to the plurality of air-cooled condenser units of the air-cooled condenser.

9. The direct air cooler peak cooling device according to claim 1, characterized in that: The first nozzle and the second nozzle are both 0.15 mm nozzles.

10. The direct air cooler peak cooling device according to claim 9, characterized in that: The water supply pressure range of the first nozzle and the second nozzle is 4 MPa-5 MPa.

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