Offshore converter station valve hall air conditioning system and design method thereof

Abstract

The application discloses a valve hall air conditioning system of a marine converter station and a design method thereof. The design method comprises the following steps: drawing an enthalpy-humidity chart, determining a summer indoor design state point parameter range in combination with the enthalpy-humidity chart; calculating a positive pressure required air volume by using a gap method, determining a fresh air volume by taking the maximum value between the positive pressure required air volume and a fresh air volume calculated at a frequency of not less than 0.5 times per hour, determining summer air conditioning parameters according to the determined fresh air volume and the summer indoor design state point parameter range, determining winter air conditioning parameters according to the determined fresh air volume and the summer air conditioning parameters, and obtaining design parameters of the valve hall air conditioning system according to the determined summer air conditioning parameters and the winter air conditioning parameters. The design method can reasonably control the temperature and humidity of the internal environment of the valve hall of the converter station, and can maintain a slight positive pressure in the valve hall, thereby providing key technical support for reasonable selection and configuration of the valve hall air conditioning system of the marine converter station.

Description

TECHNICAL FIELD

[0001] The present application relates to the offshore wind power technology field, and in particular to an offshore converter station valve hall air conditioning system and a design method thereof. BACKGROUND

[0002] With the offshore wind power in China becoming saturated, the far-sea wind power has gradually become the industry mainstream, the offshore wind turbine is large-scale, the installed capacity and the off-shore distance are expanded, and the large-scale offshore wind power output technology based on the flexible direct current transmission technology will become the hotspot of the offshore wind power development and research. The offshore converter station is a key component of the offshore wind farm and a hub of the offshore wind power access project, and the safe and reliable operation thereof is directly related to the stable operation of the entire power grid, and the valve hall air conditioning system is an important auxiliary equipment for the safe and stable operation of the offshore converter station.

[0003] The converter valve in the converter station valve hall is the core electrical equipment in the offshore wind power platform flexible direct current converter station, the heat generation of the converter valve tower is large, although the cooling water takes away most of the heat dissipation, but the converter valve still dissipates heat to the valve hall through the radiation and convection heat transfer, therefore, in order to eliminate the heat dissipated by the converter valve to the air in the valve hall, control the temperature of the valve hall within a certain range, prevent the temperature of a certain part from being too high, shorten the service life of the equipment, and even cause the electrical equipment to burn out, and in order to prevent the flashover phenomenon from occurring when the converter valve operates, the valve hall air conditioning system also needs to control the relative humidity in the valve hall within the required range. In addition, the valve hall air conditioning system also needs to send a certain amount of fresh air to maintain a certain micro-positive pressure in the valve hall, so as to prevent outdoor salt mist, dust and other external pollutants from penetrating into the valve hall through the door, hole and gap of the enclosure structure. Therefore, the temperature and humidity of the environment inside the converter station valve hall must be reasonably controlled, and a certain micro-positive pressure must be maintained. In order to achieve the above-mentioned goals, a high-efficiency and reliable valve hall air conditioning system must be configured in the offshore converter station valve hall.

[0004] The existing offshore converter station valve hall air conditioning system is not efficient and reliable, therefore, to provide a design method of the offshore converter station valve hall air conditioning system, to provide important technical support for the reasonable selection and configuration of the valve hall air conditioning system, is a key technical problem to be solved at present. SUMMARY

[0005] The purpose of the present application is to provide an offshore converter station valve hall air conditioning system and a design method thereof, to provide key technical support for the reasonable selection and configuration of the valve hall air conditioning system, and to configure a high-efficiency and reliable valve hall air conditioning system in the offshore converter station valve hall.

[0006] To achieve the above-mentioned purpose, the embodiments of the present application adopt the following technical solutions:

[0007] On the one hand, the embodiments of the present application provide a design method of an offshore converter station valve hall air conditioning system, comprising:

[0008] drawing an enthalpy psychrometric chart, determining a summer indoor design state point parameter range in combination with the enthalpy psychrometric chart;

[0009] calculating the required air volume for positive pressure by using the gap method , measuring the maximum value between the required air volume for positive pressure and the calculated fresh air volume which is not less than to determine the fresh air volume ;

[0010] determining summer air conditioning parameters according to the determined fresh air volume and the summer indoor design state point parameter range;

[0011] determining winter air conditioning parameters according to the determined air supply volume and the summer air conditioning parameters;

[0012] obtaining design parameters of the valve hall air conditioning system according to the determined summer air conditioning parameters and winter air conditioning parameters.

[0013] In some embodiments, determining the summer indoor design state point parameter range comprises determining the temperature , relative humidity and moisture content of the valve hall indoor design state point, wherein

[0014] the temperature satisfies: ;

[0015] the relative humidity satisfies: ;

[0016] the moisture content satisfies: , which is the moisture content of the outdoor design state point.

[0017] In some embodiments, determining the summer indoor design state point parameter range further comprises narrowing the summer indoor design state point parameter range according to the selected air supply temperature difference to obtain the final valve hall summer indoor design state point parameter range.

[0018] In some embodiments, the gap method is calculated by the following formula:

[0019] ,

[0020] wherein, is the required air volume for positive pressure by using the gap method; The safety factor determined according to the air tightness of the envelope structure is 1.1-1.2; The air leakage of the envelope structure per unit length of the room when the room is at a certain pressure difference; The length of the gap of the envelope structure.

[0021] In some embodiments, the summer air conditioning parameters are determined, including determining the indoor design state point, the outdoor air design state point, the valve hall equipment heat release And the selected supply air temperature difference Determine the air conditioning supply air volume , air conditioning reheat load And air conditioning refrigeration capacity , wherein,

[0022] The air conditioning supply air volume , which is calculated by the following formula:

[0023] ,

[0024] In the formula, The valve hall equipment heat release; The humidity content of the summer indoor design state point; The air density of the supply air point;

[0025] The air conditioning reheat load , which is calculated by the following formula:

[0026] ,

[0027] In the formula, The air density of the supply air point; The specific enthalpy of the supply air point; The specific enthalpy of the dew point;

[0028] The air conditioning refrigeration capacity , which is calculated by the following formula: ,

[0029] In the formula, The fresh air volume; The specific enthalpy of the indoor design point; The specific enthalpy of the outdoor design point.

[0030] In some embodiments, the winter air conditioning parameters are determined, including determining the air conditioning supply air volume And the selected supply air temperature difference , the temperature of the winter indoor design state point Is greater than or equal to the temperature of the summer indoor design state point , and the minimum humidification amount condition is determined;

[0031] The minimum humidification amount condition meets:

[0032] ;

[0033] ;

[0034] ;

[0035] In the formula, is the relative humidity of the summer indoor design state point; is the temperature of the winter air supply point.

[0036] In some embodiments, the minimum humidification amount is determined according to the condition that the indoor is in the minimum humidity content and no humidity load and the air conditioning humidification amount ;

[0037] The air conditioning humidification amount is calculated by the following formula:

[0038] ,

[0039] In the formula, ,

[0040] In the formula, is the temperature of the winter air supply point; is the fresh air amount; is the humidity content of the winter indoor design state point; is the humidity content of the winter outdoor design state point; is the saturated water vapor partial pressure.

[0041] In some embodiments, the winter air conditioning parameters are determined, including preheating the fresh air according to the condition that the fresh air inlet exists a water pipe freeze crack of the surface cooler caused by outdoor cold air, and determining the air conditioning fresh air preheating amount which is calculated by the following formula:

[0042] ,

[0043] In the formula, is the air density of the winter air supply point; is the fresh air amount; is the temperature of the winter outdoor design state point;

[0044] and determining the air conditioning heating amount when the valve hall is shut down according to the condition that the indoor temperature of the valve hall is not lower than 10℃ when the valve hall is shut down and the winter air conditioning heat load which is calculated by the following formula: In the formula,

[0045] ，

[0046] wherein, is the air density when the valve hall indoor temperature is 10℃.

[0047] In some embodiments, the design parameters of the valve hall air conditioning system include air conditioning air supply , air conditioning refrigeration capacity , air conditioning reheat load , air conditioning humidification amount , and air conditioning heating capacity , wherein,

[0048] The air conditioning heating capacity ,

[0049] wherein, is the air conditioning fresh air preheating amount; is the air conditioning heating capacity when the valve hall is shut down.

[0050] In another aspect, the embodiments of the present application provide a valve hall air conditioning system of an offshore converter station, which is configured and selected by using the design parameters obtained by the design method of the valve hall air conditioning system of the offshore converter station provided by any of the foregoing embodiments.

[0051] The present application has the following beneficial effects:

[0052] The design method of the valve hall air conditioning system of the offshore converter station provided by the embodiments of the present application can control the temperature and humidity of the internal environment of the valve body of the offshore converter station within a reasonable range, and can also maintain a certain micro-positive pressure, which can provide key technical support for the reasonable selection and configuration of the valve hall air conditioning system of the offshore wind power converter station, and can configure an efficient and reliable valve hall air conditioning system for the valve hall of the offshore converter station. At the same time, the design method greatly improves the standardization design and batch design efficiency of the valve hall air conditioning system of the offshore wind power converter station. BRIEF DESCRIPTION OF DRAWINGS

[0053] Figure 1 FIG. 1 is a flowchart of the design method of the valve hall air conditioning system of the offshore converter station in the embodiments of the present application;

[0054] Figure 2 FIG. 2 is a schematic diagram of the indoor state point range in the embodiments of the present application;

[0055] Figure 3 Fig. 6 is a schematic diagram of the indoor state point range selected by the air supply temperature difference in the embodiment of the present application;

[0056] Figure 4 Fig. 7 is a schematic diagram of the air handling process in summer in the embodiment of the present application;

[0057] Figure 5 Fig. 8 is a schematic diagram of the air handling process in winter in the embodiment of the present application. DETAILED DESCRIPTION

[0058] The technical solutions of the present application will be further described below by the specific embodiments. Those skilled in the art can easily understand other advantages and effects of the present application from the content disclosed in the present specification.

[0059] It should be noted that the embodiments in the present application and the features in the embodiments can be combined with each other without conflict. The present application will be described in detail below with reference to the accompanying drawings and in combination with the embodiments. In order to enable those skilled in the art to better understand the present application scheme, the technical solutions in the embodiments of the present application will be described clearly and completely below in combination with the drawings of the embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, but not all the embodiments. Based on the embodiments of the present application, all other embodiments obtained by those skilled in the art without creative labor should belong to the protection scope of the present application.

[0060] It should be noted that the terms "first", "second" and the like in the specification and claims of the present application and the above-mentioned drawings are used to distinguish similar objects, and do not necessarily indicate a specific order or a chronological sequence. In addition, the terms "include", "contain" or any other variants thereof are intended to cover non-exclusive inclusion, so that the processes, articles or devices including a series of elements not only include those elements, but also include other elements not explicitly listed or inherent to such processes, articles or devices. Without more limitations, the element defined by the statement "including a" does not exclude the presence of other identical elements in the process, article or device including the element; for example, a process, method, system, product or device including a series of steps or units does not necessarily limit to those steps or units clearly listed, but can include other steps or units not clearly listed or inherent to these processes, methods, products or devices.

[0061] In the embodiments of this application, the words "exemplary" or "for example" are used to indicate that they are examples, illustrations, or descriptions. Any embodiment or design that is described as "exemplary" or "for example" in the embodiments of this application should not be construed as being more preferred or advantageous than other embodiments or design; rather, the use of the words "exemplary" or "for example" is intended to present the relevant concepts in a specific manner.

[0062] Offshore converter stations are the core hubs connecting offshore wind farms and onshore power grids. They undertake the key functions of power collection, voltage conversion and power control, and their operational safety and reliability directly affect the stability of the entire power transmission system.

[0063] The valve hall of the converter station, as the core area, houses critical electrical equipment such as converter valve towers, valve control equipment, and cooling systems. Among these, the converter valves are the core electrical equipment in the offshore wind power platform's flexible DC converter station. The converter valve towers generate a significant amount of heat. Although cooling water removes most of the heat, the converter valves still dissipate heat into the valve hall through radiation and convection. Therefore, to eliminate the heat dissipated from the converter valves into the valve hall air and maintain the valve hall temperature within a certain range to prevent overheating in any part, which could shorten the equipment's lifespan or even cause electrical equipment burnout, and to ensure that flashover does not occur during converter valve operation, the valve hall air conditioning system also needs to control the relative humidity within the valve hall within the required range. Furthermore, the valve hall air conditioning system needs to supply a certain amount of fresh air to maintain a slight positive pressure within the valve hall, preventing external pollutants such as outdoor salt spray and dust from seeping into the valve hall through doors, openings, and gaps in the enclosure structure. Therefore, it is necessary to implement reasonable temperature and humidity control and maintain a slight positive pressure within the offshore converter station's valve hall environment.

[0064] To achieve the above objectives, one aspect of this application is to provide a design method for an air conditioning system in the valve hall of an offshore converter station. Figure 1 This is a schematic diagram illustrating the design method of the air conditioning system in the valve hall of an offshore converter station, as described in this application. Figure 1 As shown, in some embodiments, the design method specifically includes the following steps:

[0065] S100. Draw an enthalpy-humidity diagram and determine the range of indoor design state point parameters for summer based on the enthalpy-humidity diagram.

[0066] According to the following formula:

[0067] (1)

[0068] In the formula, Relative humidity; This refers to the partial pressure of water vapor, measured in Pa. This is the partial pressure of saturated water vapor, expressed in Pa.

[0069] (2)

[0070] (3)

[0071] wherein, is the moisture content, in g / kg.

[0072] (4)

[0073] wherein, ; ; ; ; ; ; .

[0074] (5)

[0075] wherein, ; ; ; ; ; .

[0076] (6)

[0077] wherein, is the specific enthalpy, in kJ / kg.

[0078] (7)

[0079] wherein, is the air density, in kg / m3. .

[0080] (8)

[0081] In this step, for large space valve hall with large heat release, there is no wet load in the valve hall, and the air conditioning adopts full air air conditioning system for cooling.

[0082] First, the design temperature (℃), relative humidity (%) of the indoor air design state point of the valve hall in summer, moisture content (g / kg) and specific enthalpy (kJ / kg) of the valve hall in summer are determined, and the temperature , relative humidity , moisture content and specific enthalpy of the outdoor air design state point are setAnd in order to prevent the valve hall from dewing, the fresh air needs to be dehumidified, then there are:

[0083] (9)

[0084] And in the actual application scene, when the valve hall air conditioner supply air dew point temperature is lower than the chilled water temperature of the cooling coil, the valve hall air conditioner completely loses the condensing effect. According to the operation experience, when the dew point temperature of the valve hall air conditioner inlet air and the chilled water temperature of the cooling coil are different by 2℃, the dehumidification performance of the valve hall air conditioner will be greatly reduced, and the chilled water design return water temperature of the air conditioning cooling coil is 12℃. Therefore, in order to ensure the dehumidification effect, the air conditioning supply air dew point temperature should not be lower than 16℃, that is, the extreme dew point temperature can be 16℃.

[0085] According to the above, let the air conditioning supply air dew point air parameters be temperature , relative humidity (the relative humidity of the air conditioning machine dew point can be 90%, that is ), moisture content and specific enthalpy , then there are:

[0086] (10)

[0087] (11)

[0088] (12)

[0089] At the same time, according to the "Design Standard of Flexible DC Transmission Converter Station" GB / T 51381-2019 and "Design Specification of Offshore Flexible DC Converter Station" NBT11403-2023, the valve hall temperature and humidity are controlled according to , , then there are:

[0090] (13)

[0091] (14)

[0092] Because the relative humidity of the valve hall is required to be , in order to avoid the local relative humidity of the valve hall being greater than 60%, therefore the relative humidity of the air conditioning supply air is designed to be not greater than 60%, then there are:

[0093] (15)

[0094] (16)

[0095] In the formula, is the relative humidity of the supply air point; The moisture content at the air supply point is expressed in g / kg.

[0096] From the aforementioned equations (1)-(16), we can obtain:

[0097] (17)

[0098] (18)

[0099] (19)

[0100] Based on the aforementioned equations (1)-(6), enthalpy-humidity diagrams can be drawn, and combined with equations (17)-(19), the following can be obtained: Figure 2 The enthalpy-humidity diagram shown. Figure 2 This is a schematic diagram of the range of indoor status points in an embodiment of this application. Figure 2 The shaded area in the diagram represents the parameter range for the interior design status points. It is understandable that... Figure 2 The shaded area in the figure represents the feasible range of the interior design state points for the marine valve hall.

[0101] For example, determining the range of parameters for the summer indoor design state may further include based on a defined supply air temperature difference. This further narrows down the parameter range of the indoor design status points, and obtains the final parameter range of the summer indoor design status points for the valve hall. Figure 3 This is a schematic diagram of the indoor state point range based on the selected supply air temperature difference in this embodiment of the application. The final summer indoor design state point parameter range of the valve hall is as follows: Figure 3 The shaded area is shown.

[0102] According to Article 8.4.9 of the "Code for Design of Heating, Ventilation and Air Conditioning of Industrial Buildings" (GB50019-2015), the air supply temperature difference of the air conditioner shall be selected according to Table 1 below.

[0103]

[0104] According to Article 3.1.1 of the "Design Method for Heating, Ventilation and Air Conditioning Systems on Offshore Platforms" (Q / HS3008-2016), the outdoor air design parameters shall be selected according to Table 2 below.

[0105]

[0106] S200, Calculate the required air volume for positive pressure using the gap method. Measure the required air volume for positive pressure. and not less than The maximum value among the calculated fresh air volumes is used to determine the fresh air volume. .

[0107] In the embodiments of the present application, in order to prevent outdoor salt spray, dust and other external pollutants from penetrating into the valve hall through the door, hole and gap of the enclosure structure, the air conditioning system also needs to send a certain amount of fresh air to maintain a certain micro-positive pressure in the valve hall. The required air volume for positive pressure is calculated by the gap method , which takes into account both the air tightness of the room enclosure structure and the air volume required to maintain a certain positive pressure value indoors .

[0108] The gap method is calculated by the following formula:

[0109] (20)

[0110] In the formula, is the required air volume for positive pressure by the gap method, with the unit being ;

[0111] is a safety factor determined according to the air tightness of the enclosure structure, which can be in the range of 1.1-1.2;

[0112] is the air leakage volume of the enclosure structure per unit length of the gap when the room is at a certain pressure difference, with the unit being ;

[0113] is the gap length of the enclosure structure, with the unit being m.

[0114] According to the Clean Workshop Design Specification GB50073-2013, the air leakage per unit length of the gap is shown in Table 3.

[0115] Since the rooms of the offshore converter station are all windowless rooms, and the doors are all airtight doors, the air leakage per unit length of the gap can be taken as the value of the airtight door in Table 3.

[0116]

[0117] In the embodiments of the present application, considering the post-accident ventilation requirement of specified in the Flexible DC Power Transmission Converter Station Design Standard GB / T 51381-2019 specification, the fresh air sent by the air conditioning unit is used as the post-disaster ventilation system, a mechanical air intake and natural air exhaust system is adopted, the holes in the valve hall are reduced, and the fresh air volume is designed to be not less than calculated. Therefore, the fresh air volume is taken as the maximum value between the air volume required for positive pressure and the fresh air volume calculated by not less than , and the fresh air volume is determined.

[0118] S300, determine the summer air conditioning parameters according to the determined fresh air volume and the summer indoor design state point parameter range.

[0119] According to the determined indoor design state points (including temperature , relative humidity ), outdoor air design state points (including temperature , relative humidity ), valve hall equipment heat release Q and selected air supply temperature difference , the air conditioning air supply volume , air conditioning reheat load and air conditioning refrigeration capacity are determined, and the following is obtained:

[0120] (21)

[0121] And according to the foregoing (6)-(8), the air conditioning air supply volume is obtained:

[0122] (22)

[0123] In the formula, is the valve hall equipment heat release, with the unit of kW; is the humidity content of the indoor design state point in summer, with the unit of g / kg; is the air density of the air supply point, with the unit of .

[0124] The air conditioning reheat load (23) is obtained:

[0125] In the formula, is the air density of the air supply point, with the unit of ; it is the specific enthalpy of the air supply point; it is the specific enthalpy of the dew point.

[0126] The air conditioning refrigeration capacity (24) is obtained:

[0127] In the formula, is the fresh air volume, with the unit of ; is the specific enthalpy of the indoor design point; is the specific enthalpy of the outdoor design point.

[0128] S400, according to the determined air conditioning air supply volume and summer air conditioning parameters, winter air conditioning parameters are determined.

[0129] In practical application scenarios, the heat generated by the valve hall equipment increases with the decrease of indoor temperature, while the heat dissipation of the enclosure structure in winter is considered as a design margin. Therefore, if the indoor design temperature is reduced, the heat generated by the valve hall equipment will increase, and the selected air supply temperature difference has been determined by the summer operating condition. According to the aforementioned formula (22), the air conditioning supply air volume will increase, but the air conditioning supply air volume has been determined by the summer operating condition.

[0130] Therefore, the temperature of the winter indoor design state point is greater than or equal to the temperature of the summer indoor design state point , and the minimum humidification amount is determined, then:

[0131] (25)

[0132] (26)

[0133] (27)

[0134] In the formula, is the relative humidity of the winter indoor design state point; is the temperature of the winter air supply point.

[0135] Since there is no humidity load in the room, according to formulas (1) and (2), the relative humidity is constant, the lower the temperature, the lower the moisture content, so the state point has the minimum humidification amount of fresh air. Thus, the minimum humidification amount and the air conditioning humidification amount 。

[0136] Then, the aforementioned formulas (1)-(4), (25), (26) can obtain the minimum humidification amount :

[0137] (28)

[0138] In the formula, is the saturated water vapor pressure.

[0139] Then, according to the known winter outdoor air state parameters (including temperature , relative humidity , moisture content and specific enthalpy ） , the air conditioning humidification amount can be obtained:

[0140] (29)

[0141] In the formula, temperature of the winter indoor design state point, in ℃; new air volume, in m3 / s ; humidity of the winter indoor design state point, in g / kg humidity of the winter outdoor design state point, in g / kg.

[0142] Meanwhile, to avoid the water pipe of the surface cooler from being frozen and cracked due to the cold outdoor wind at the new air inlet, the new air needs to be preheated, and the new air can be preheated to 5℃. Therefore, according to the working condition that the water pipe of the surface cooler at the new air inlet is frozen and cracked due to the cold outdoor wind, the new air is preheated, and the air conditioning new air preheating amount is determined.

[0143] (30)

[0144] In the formula, air density of the winter indoor design state point, in kg / m3 ; new air volume, in m3 / s ; temperature of the winter outdoor design state point, in ℃.

[0145] In the actual application scenario, when the valve hall is shut down, the indoor temperature of the valve hall needs to be ensured to be not lower than 10℃. Therefore, according to the working condition that the indoor temperature of the valve hall is not lower than 10℃ when the valve hall is shut down and the winter air conditioning heat load , the air conditioning heating amount of the valve hall when the valve hall is shut down is determined.

[0146] (31)

[0147] In the formula, new air volume, in m3 / s ; temperature of the winter outdoor design point, in ℃; air density of the valve hall indoor temperature being 10℃, in kg / m3 .

[0148] S500, according to the determined summer air conditioning parameters and winter air conditioning parameters, the design parameters of the valve hall air conditioning system are obtained.

[0149] According to the new air volume , summer air conditioning parameters and winter air conditioning parameters determined as described above, the final design parameters of the valve hall air conditioning system can be obtained, which can include air conditioning air supply ( ), air conditioning refrigerating capacity (kW), and air conditioning reheating load (kW), air conditioning humidification amount (kg / h) and air conditioning heating amount (kW), wherein,

[0150] ;

[0151] ;

[0152] ;

[0153] ;

[0154] ;

[0155] In the formula, is the air conditioning fresh air preheating amount; is the air conditioning heating amount when the valve hall is shut down.

[0156] The design method provided by the embodiments of the present application determines the summer indoor design state point parameter range through the psychrometric chart, and determines the fresh air amount by using the gap method. Moreover, the summer air conditioning parameters are determined according to the determined fresh air amount and the summer indoor design state point parameter range. Meanwhile, the winter air conditioning parameters are determined according to the determined fresh air amount and the summer air conditioning parameters, and the final valve hall air conditioning system design parameters are obtained according to the determined summer air conditioning parameters and the winter air conditioning parameters. By using the design method of the present application, the temperature and humidity in the valve body of the offshore converter station can be controlled in a reasonable range, and a certain micro-positive pressure can be maintained, which can provide key technical support for the reasonable selection and configuration of the valve hall air conditioning system of the offshore converter station.

[0157] Meanwhile, the design method provided by the embodiments of the present application greatly improves the standardization design and batch design efficiency of the valve hall air conditioning system of the offshore wind power converter station, and provides key technical support for the rapid development of the industry.

[0158] On the other hand, the embodiments of the present application provide an offshore converter station valve hall air conditioning system. The offshore converter station valve hall air conditioning system is selected and configured by using the design parameters obtained by the design method of the offshore converter station valve hall air conditioning system provided by any of the preceding embodiments.

[0159] The offshore converter station valve hall air conditioning system provided by the embodiments of the present application can effectively eliminate the heat emitted by the converter valve and other equipment to ensure that the valve hall temperature is moderate and in a safe operating range. Moreover, the humidity can be controlled in a reasonable range to prevent condensation and flashover phenomenon. Meanwhile, the valve hall can maintain a certain micro-positive pressure through the fresh air system, which can effectively prevent outdoor salt mist, dust and other external pollutants from penetrating into the valve hall through the door, hole and gap of the enclosure structure.

[0160] The valve hall air conditioning system of the offshore converter station is very suitable for the offshore high humidity, high salt fog and strong corrosion and other harsh environments, and has the ability of high efficiency, reliability and long-term stable operation.

[0161] Embodiment one

[0162] In this embodiment, the valve hall equipment heat release of a certain offshore wind power offshore converter station in the Yellow Sea is taken as an example, and the known heat release is shown in Table 4 as follows.

[0163]

[0164] In this embodiment, the selected air supply temperature difference is 7℃, and the indoor state point selected for design is temperature 35℃ and relative humidity 40%.

[0165] According to Table 4, the valve hall equipment heat release is 540kW, the known heat load during winter shutdown is 250kW, the room volume is 52000 m3, and the fresh air volume is calculated as 26000 m3 according to the air change number.

[0166] Figure 4 The summer air treatment process in this embodiment is shown in FIG. 6, and the summer air treatment process according to the design method provided in this embodiment is shown in FIG. 6. Figure 4 Figure 4 The summer state point parameters in Table 5 are shown as follows.

[0167]

[0168] According to the summer air treatment process, the design parameters of the summer air conditioning system can be obtained as follows:

[0169] The air supply volume ;

[0170] The fresh air volume ;

[0171] The total cooling capacity of the unit ;

[0172] The indoor cooling load ;

[0173] The fresh air load ;

[0174] The reheating cooling load .

[0175] Figure 5 The winter air treatment process in this embodiment is shown in FIG. 7, and the winter air treatment process according to the design method provided in this embodiment is shown in FIG. 7. Figure 5 Figure 5 ​​​The parameters of each state point in winter are shown in Table 6.

[0176]

[0177] According to the air handling process in winter, the air conditioning humidification amount ,

[0178] .

[0179] In order to avoid the water pipe of the surface cooler from being frozen and cracked due to the cold outdoor air at the fresh air inlet, the fresh air is preheated to 5℃, and the air conditioning fresh air preheating amount ,

[0180] .

[0181] According to the working condition that the indoor temperature of the valve hall is not lower than 10℃ when the valve hall is shut down and the air conditioning heat load in winter, the air conditioning heating amount ,

[0182] .

[0183] According to the air handling process in summer and the air handling process in winter, the design parameters of the valve hall air conditioning system are as follows:

[0184] The air conditioning supply air amount ;

[0185] The fresh air amount ;

[0186] The air conditioning refrigeration amount ;

[0187] The air conditioning heating amount ;

[0188] The air conditioning humidification amount .

[0189] The above description is only a specific embodiment of the present application, but the protection scope of the present application is not limited thereto, and any modification, change or equivalent replacement made by the skilled in the art without departing from the technical concept of the present application, all the obtained embodiments belong to the protection scope of the claims of the present application.

Claims

1. A method for designing an air conditioning system for a valve hall of a marine converter station, characterized in that, Comprise: Draw the enthalpy humidity chart, determine the summer indoor design state point parameter range in combination with the enthalpy humidity chart; The required air volume for positive pressure is calculated by using the gap method The maximum value between the required air volume for positive pressure and the calculated fresh air volume is determined as the fresh air volume ; determining the fresh air amount according to the determined new air amount and the summer indoor design state point parameter range, determine a summer air conditioning parameter; determining a winter air conditioning parameter according to the determined air conditioning supply air volume and the summer air conditioning parameter; determining the winter air conditioning parameter, including determining the air conditioning supply air volume and the selected supply air temperature difference so that the temperature of the winter indoor design state point is greater than or equal to the temperature of the summer indoor design state point and determining the minimum humidification amount condition; The minimum humidification amount working condition meets: ； ； ； wherein is the relative humidity of the indoor design state point in winter; is the temperature of the supply air point in winter; According to the determined summer air conditioning parameter and winter air conditioning parameter, the design parameter of the valve hall air conditioning system is acquired.

2. The offshore converter station valve hall air conditioning system design method of claim 1, characterized in that, determining the summer indoor design state point parameter range, including determining the temperature , relative humidity and moisture content of the valve hall indoor design state point, wherein, The temperature Satisfies: ; the relative humidity satisfies: ; The moisture content Satisfies: , is the moisture content of the outdoor design state point.

3. The offshore converter station valve hall air conditioning system design method of claim 1, wherein, determining the summer indoor design state point parameter range further comprises narrowing the summer indoor design state point parameter range according to the selected supply air temperature difference , and obtaining a final valve hall summer indoor design state point parameter range.

4. The offshore converter station valve hall air conditioning system design method of claim 1, wherein, The gap method is calculated by the following formula: ， In the formula, Q is the required air volume for positive pressure by the gap method; K is a safety factor determined according to the air tightness of the enclosure, and the value range is 1.1-1.2; Q is the leakage air volume of the unit length gap of the enclosure when the room is at a certain pressure difference; L is the gap length of the enclosure.

5. The offshore converter station valve hall air conditioning system design method of claim 1, wherein, determining the summer air conditioning parameter, including determining the air conditioning supply air volume , air conditioning reheat load and air conditioning refrigeration capacity according to the determined indoor design state point, outdoor air design state point, valve hall equipment heat generation and selected supply air temperature difference , wherein, The air conditioning supply air volume which is calculated by the following equation: ， wherein is the heat generated by the valve hall equipment; is the humidity ratio of the indoor design state point in summer; is the air density of the supply air point; The air conditioning reheat load which is calculated by the equation: ， wherein is the air density at the supply point; is the specific enthalpy at the supply point; is the specific enthalpy at the dew point; The air conditioner refrigerating capacity which is calculated by the following equation: ， In the formula, is the fresh air volume; is the specific enthalpy of the indoor design point; is the specific enthalpy of the outdoor design point.

6. The offshore converter station valve hall air conditioning system design method of claim 1, wherein, According to the indoor condition of minimum moisture content and no moisture load, the minimum moisture content is determined and air conditioning humidification amount ; The air conditioning humidification amount which is calculated by the following equation: ， wherein , wherein is the air density at the winter air supply point; is the fresh air volume; is the humidity ratio at the winter indoor design state point; is the humidity ratio at the winter outdoor design state point; is the saturated water vapor partial pressure.

7. The offshore converter station valve hall air conditioning system design method of claim 1, wherein, The winter air conditioning parameter is determined, including preheating the fresh air according to the working condition that the outdoor cold air causes the water pipe of the surface cooler to be frozen and cracked, and determining the preheating amount of the fresh air which is calculated by the following formula: ， wherein is the air density at the winter air supply point; is the fresh air volume; is the temperature at the winter outdoor design state point; And according to the condition that the indoor temperature of the valve hall is not lower than 10℃ when the valve hall is shut down and the air conditioning heat load in winter , the air conditioning heating capacity when the valve hall is shut down is determined , which is calculated by the following formula: ， In the formula, is the air density at 10°C in the valve hall room.

8. The offshore converter station valve hall air conditioning system design method of claim 1, wherein, The design parameters of the valve hall air conditioning system include air conditioning supply air volume , air conditioning refrigerating capacity , air conditioning reheat load , air conditioning humidification amount , and air conditioning heating capacity , wherein, The air conditioner heating capacity , In the formula, For air conditioning fresh air preheating capacity; For valve hall shutdown air conditioning heating capacity.

9. A valve hall air conditioning system for a marine converter station, characterized by The design parameter acquired by the offshore converter station valve hall air conditioning system design method of any one of claims 1-8 is used for selection and configuration.

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