Vapor compression cycle refrigeration and dehumidification device and method for large experiment module

Abstract

The invention provides a vapor compression cycle refrigeration and dehumidification device and method for a large experiment module, and belongs to the field of ocean engineering model structure tests. The problem that high efficiency and economical efficiency of humidity control are difficult to consider in the prior art is solved. A vapor compression cycle refrigeration and dehumidification method for a large experiment module comprises the following steps that when the humidity of the experiment module reaches a preset value, gas is introduced into a dehumidification bin through a vacuum pump set to be coupled with an evaporator and then discharged from the outlet end of the evaporator through the vacuum pump set; detecting the humidity d1 of the outlet end of the evaporator; detecting the humidity d2 of the outlet end of the vacuum pump set; and when d1 is larger than d2, the refrigerant circulation amount in the evaporator is increased till d1 is smaller than or equal to d2. The dehumidifying device is mainly used for dehumidifying the experiment module.

Description

Technical Field

[0001] The invention belongs to the field of marine engineering model structure testing, and in particular relates to a vapor compression cycle refrigeration and dehumidification device and method for a large experimental cabin. Background Art

[0002] In the field of marine equipment research and development, cross-media water entry and exit tests on scaled-down navigable bodies are a core experimental method for verifying their hydrodynamic performance. These tests require the air pressure within the test chamber to accurately simulate the actual marine environment. Existing technologies use vacuum pumps to regulate the chamber pressure. This causes excess water vapor, generated by evaporation of liquid water, to enter the vacuum pumps along with the airflow. Because vacuum pumps rely on lubricating oil, contact between the water vapor and the oil produces an emulsification reaction, resulting in a 40% to 60% decrease in the oil's viscosity. This increases the wear rate of the vacuum pump components by 3-5 times, leading to increased maintenance frequency and significantly increased experimental costs.

[0003] In the existing technical field, the vacuum sealed cabin dehumidification system proposed in patent CN116907201A adopts adsorbent dehumidification method, the core of which is to physically adsorb moisture in the air through adsorbent. However, this solution is not suitable for use in a volume of more than 100m 3 When using a large negative pressure cabin, the complex flow field and spatial structure within the cabin make it difficult to achieve a uniform arrangement of the adsorbent bed, resulting in insufficient effective adsorption area and a low dehumidification rate. Furthermore, when the adsorbent filling rate exceeds 60%, the airflow resistance increases by 150%, seriously affecting the efficiency of vacuuming. The negative pressure water vapor separation device disclosed in patent CN113638866 uses condensation dehumidification technology, which uses a refrigeration system to cool the humid air in the cabin to below the dew point to achieve water vapor separation. However, this solution requires maintaining a low temperature of -40°C under a high vacuum of 10 kPa, consumes extremely high energy, and is unable to cope with the continuous evaporation volume of large test cabins with a capacity of 1,000 to 10,000 cubic meters. In summary, the existing technical solutions generally suffer from a contradiction between dehumidification efficiency and energy consumption in large negative pressure cabin applications, making it difficult to achieve a balance between high efficiency and economic efficiency in humidity control. Therefore, inventing an efficient dehumidification method suitable for large experimental chambers (chamber volume 1,000 to 10,000 cubic meters) to ensure the continuous and stable operation of large experimental chambers and support the research and development of deep-sea equipment has important engineering value. Summary of the Invention

[0004] In view of this, the present invention aims to propose a vapor compression cycle refrigeration and dehumidification device and method for a large experimental chamber to solve the problem that the existing technology is difficult to balance the efficiency and economy of humidity control.

[0005] To achieve the above objectives, the present invention adopts the following technical solutions. According to one aspect of the present invention, a vapor compression cycle refrigeration and dehumidification method for a large experimental chamber is provided, comprising the following steps:

[0006] When the humidity in the experimental chamber reaches the preset value, the gas is introduced into the dehumidification chamber through the vacuum pump group and coupled with the evaporator, and then discharged from the outlet of the evaporator through the vacuum pump group;

[0007] Detect the humidity at the evaporator outlet as d1;

[0008] Detect the humidity at the outlet of the vacuum pump group to be d2;

[0009] When d1 is greater than d2, the refrigerant circulation amount in the evaporator is increased until d1 is less than or equal to d2.

[0010] Furthermore, when d1 approaches d2, the amount of refrigerant circulating in the evaporator increases.

[0011] According to another aspect of the present invention, there is provided an apparatus for a vapor compression cycle refrigeration and dehumidification method using a large experimental chamber as described above, comprising:

[0012] The dehumidification chamber has an inlet connected to the experimental chamber and an outlet connected to the inlet of the vacuum pump group;

[0013] An evaporator is arranged in the experimental chamber and coupled with the gas flowing through the dehumidification chamber;

[0014] Refrigeration system, connected to the evaporator for circulating refrigerant;

[0015] A first humidity sensor is provided at the outlet of the evaporator for detecting the humidity of the gas flowing therethrough;

[0016] A second humidity sensor is provided at the outlet of the vacuum pump assembly to detect the humidity of the gas flowing therethrough;

[0017] The controller is connected to the first humidity sensor and the second humidity sensor, and is used to collect signals from the first humidity sensor and the second humidity sensor and then control the refrigerant circulation amount of the refrigeration system.

[0018] Furthermore, both ends of the circulation flow path of the refrigeration system are connected to the coolant inlet and outlet of the evaporator respectively, and a compressor, a condenser and a throttle valve are provided on the flow path.

[0019] Furthermore, the compressor and the throttle valve are both connected to a controller.

[0020] Furthermore, the compressor is a speed-adjustable compressor, and the throttle valve is an opening-adjustable throttle valve.

[0021] Furthermore, the evaporator is provided with a water storage chamber for storing condensed water.

[0022] Furthermore, the water storage chamber is provided with a valve.

[0023] Furthermore, the vacuum pump group is provided with a plurality of vacuum pumps connected in parallel.

[0024] Compared with the prior art, the present invention has the following beneficial effects:

[0025] This method introduces the air in the experimental chamber into the dehumidification chamber for treatment through an evaporator or similar heat exchange component, monitors the humidity at the evaporator outlet d1 and the humidity at the vacuum pump group outlet d2, and adjusts the relative humidity by comparing d1 and d2. It does not need to condense and remove all the water vapor in the air. It only needs to reduce the moisture content in the air to a certain value to prevent the formation of condensed water in the vacuum pump and extend the service life of the vacuum pump. Therefore, this method can quickly and efficiently reduce the moisture content of the air in large-volume, high-vacuum, and high-humidity environments with high efficiency and low energy consumption, showing an excellent energy consumption advantage. In actual engineering applications, whether it is a simulation experimental chamber in the aerospace field or a test chamber for deep-sea equipment research and development, as long as it involves the high vacuum dehumidification needs of large experimental chambers, this method can play a key role. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] The accompanying drawings, which constitute part of the present invention, are provided to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are provided to explain the present invention and do not constitute an undue limitation of the present invention. In the accompanying drawings:

[0027] Figure 1 This is a schematic diagram of the layout of a vapor compression cycle refrigeration and dehumidification device for a large experimental chamber according to the present invention;

[0028] Figure 2 The present invention provides a flow chart of a vapor compression cycle refrigeration and dehumidification method for a large experimental chamber.

[0029] Experimental chamber 1; dehumidification chamber 2; evaporator 3; compressor 4; condenser 5; throttle valve 6; water storage chamber 7; first humidity sensor 8; second humidity sensor 9; controller 10; vacuum pump group 11. DETAILED DESCRIPTION

[0030] The following will be combined with the accompanying drawings in the embodiments of the present invention to clearly and completely explain the technical solutions in the embodiments of the present invention. It should be noted that the embodiments of the present invention and the features therein can be combined with each other in the absence of conflict, and the embodiments described are only part of the embodiments of the present invention, not all of the embodiments.

[0031] It should be noted that the descriptions of the present invention regarding directions such as "left", "right", "left side", "right side", "upper", "lower", "top", and "bottom" are all defined based on the relationship between the orientations or positions shown in the accompanying drawings. They are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the structure described must be constructed and operated in a specific orientation. Therefore, they should not be understood as limitations on the present invention. In the description of the present invention, the meaning of "plurality" is more than two, unless otherwise clearly and specifically defined.

[0032] In the description of the present invention, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood broadly. For example, they may refer to fixed connections, detachable connections, or integral connections; they may refer to direct connections, indirect connections through an intermediary, or internal communication between two components. Those skilled in the art will understand the specific meanings of these terms in the present invention based on the specific circumstances.

[0033] Referring to the accompanying drawings, this embodiment is described. According to one aspect of the present invention, a vapor compression cycle refrigeration and dehumidification method for a large experimental chamber is provided, comprising the following steps:

[0034] When the humidity in the experimental chamber 1 reaches a preset value, the gas is introduced into the dehumidification chamber 2 and coupled with the evaporator 3 through the vacuum pump group 11, and then discharged from the outlet of the evaporator 3 through the vacuum pump group 11;

[0035] Detect the humidity at the outlet of evaporator 3 as d1;

[0036] Detect the humidity at the outlet of the vacuum pump group 11 to be d2;

[0037] When d1 is greater than d2, the refrigerant circulation amount in the evaporator 3 is increased until d1 is less than or equal to d2.

[0038] In this embodiment, when d1 approaches d2, the refrigerant circulation amount in the evaporator 3 increases, which temporarily increases power consumption, but ensures that d1 is less than or equal to d2, thus preventing condensation in the vacuum pump.

[0039] Specifically, such as Figure 1As shown, during the process of adjusting the air pressure in the experimental chamber 1, as the air pressure decreases, the water pool inside the experimental chamber 1 will produce a large amount of water vapor, forming humid air with a high humidity of >90%. The humid air enters the dehumidification chamber 2 through the vacuum pipeline and contacts the evaporator 3. The refrigerant in the evaporator 3 evaporates and absorbs heat, the temperature drops below the dew point, and the water vapor in the humid air condenses into liquid water and precipitates, reducing the moisture content in the humid air and achieving the purpose of dehumidification. As long as the moisture content d1 in the air after passing through the evaporator 3 is not greater than the moisture content d2 after the vacuum pump, it can be ensured that no condensed water will be generated in the vacuum pump group 11, thereby avoiding the mixing of lubricating oil in the vacuum pump body and the problem of catalyzing the emulsification of lubricating oil under high temperature conditions.

[0040] Compared with traditional dehumidification methods, the present invention does not need to condense and remove all the water vapor in the air, but only needs to reduce the moisture content in the air to a certain value. Therefore, the present invention can quickly and efficiently reduce the moisture content of the air in a large volume, high vacuum, and high humidity environment, showing an excellent energy consumption advantage. In actual engineering applications, whether it is a simulation laboratory cabin in the aerospace field or a test cabin for deep-sea equipment research and development, as long as it involves the high vacuum dehumidification needs of large laboratory cabins, this method can play a key role. A breakthrough innovation has been made to address the shortcomings of traditional dehumidification methods in dealing with large volume, high vacuum and high humidity complex environments. In simulation test chambers in the aviation field, the harsh vacuum and humidity conditions place extremely high demands on the stability of equipment operation. This method can accurately and efficiently control the humidity in the chamber to the ideal range, ensuring that the vacuum system is not damaged by moisture and guaranteeing the continuity and reliability of the experimental process. In other fields, such as the application of test chambers for deep-sea equipment research and development, facing the problems of condensation and high humidity in the chamber easily caused by high pressure and low temperature, this method can not only quickly eliminate excess moisture and maintain a suitable temperature and humidity balance in the chamber, but also can operate continuously and stably in a high vacuum environment, avoiding pressure fluctuations caused by the dehumidification process that interfere with the experimental progress.

[0041] According to another aspect of the present invention, there is provided an apparatus for a vapor compression cycle refrigeration and dehumidification method using the above-mentioned large-scale experimental chamber, comprising:

[0042] The inlet end of the dehumidification chamber 2 is connected to the experimental chamber 1 through a vacuum pipeline, and the outlet end is connected to the inlet end of the vacuum pump group 11 through a vacuum pipeline; the experimental chamber 1 is specifically a negative pressure experimental chamber.

[0043] Evaporator 3 is installed within the experimental chamber 1 and coupled to the gas flowing through the dehumidification chamber 2. Specifically, the evaporator 3 is placed vertically within the inlet and outlet of the dehumidification chamber 2, allowing the gas to flow through the heat exchange components of evaporator 3. The moisture in the gas condenses along the flow path of evaporator 3 and flows into the water storage chamber 7 for storage. Depending on actual needs, evaporator 3 can be replaced with another type of heat exchanger with similar functions. After a certain period of operation, the system will shut down. At this time, the valve in the water storage chamber 7 is opened to discharge the condensed water.

[0044] A refrigeration system connected to the evaporator 3 for circulating the refrigerant;

[0045] A first humidity sensor 8 is provided at the outlet of the evaporator 3 and is used to detect the humidity of the gas flowing therethrough;

[0046] The second humidity sensor 9 is provided at the outlet of the vacuum pump group 11 and is used to detect the humidity of the gas flowing therethrough;

[0047] The controller 10 is connected to both the first humidity sensor 8 and the second humidity sensor 9, and is used to collect signals from the first humidity sensor 8 and the second humidity sensor 9 and then control the refrigerant circulation amount of the refrigeration system.

[0048] In this embodiment, both ends of the circulation flow path of the refrigeration system are connected to the coolant inlet and outlet of the evaporator 3 respectively, and a compressor 4, a condenser 5 and a throttle valve 6 are provided on the flow path.

[0049] In this embodiment, the compressor 4 and throttle valve 6 are both connected to a controller 10. The compressor 4 is a speed-adjustable compressor, and the throttle valve 6 is an opening-adjustable throttle valve. The controller can control the speed of the compressor 4 and the opening of the throttle valve 6, thereby adjusting the refrigerant circulation rate based on the difference between d1 and d2, ensuring that the ideal operating conditions are quickly achieved. Furthermore, if the humidity rises after stabilizing, the controller can ensure that d1 is less than or equal to d2, thereby preventing the vacuum pump assembly 11 from being affected by condensation.

[0050] In this embodiment, the evaporator 3 is provided with a water storage chamber 7 for storing condensed water. The actual location of the water storage chamber 7 and the flow path connecting the condensed water to the evaporator 3 can be arranged appropriately according to actual conditions. The water storage chamber 7 is provided with a valve. The valve can be a manual valve or an electronically controlled valve, depending on the actual situation, to drain water during shutdown. Other drainage methods are also possible, but they must not affect the normal operation of the entire device.

[0051] In this embodiment, the vacuum pump group 11 is provided with several vacuum pumps connected in parallel, which can increase the adjustable margin and the stability of the system. When an individual vacuum pump fails, it will not affect the overall use.

[0052] For dehumidification and refrigerant circulation methods, such as Figure 2 As shown, when high-humidity air (humidity >90%) enters the evaporator 3 in the dehumidification chamber 2, the low-temperature, low-pressure liquid refrigerant (evaporation temperature -5°C, corresponding pressure 0.4 MPa) absorbs heat through evaporation, lowering the air temperature to below the dew point (25°C), causing the water vapor to condense into liquid water. This water vapor is stored in the water storage chamber 7 and then discharged through the drain port after the vacuum pump assembly 11 is shut down. The vaporized low-temperature, low-pressure gaseous refrigerant is compressed by the compressor 4 into a high-temperature, high-pressure gas (evaporation temperature 80°C, corresponding pressure 1.8 MPa). It then enters the condenser to release latent heat and, under certain conditions, condenses into high-pressure liquid refrigerant. The liquid refrigerant undergoes adiabatically expanding through the throttle valve 6 before re-entering the evaporator 3, forming a closed cycle. Humidity sensors monitor the moisture content at the evaporator outlet d1 and the vacuum pump outlet d2. Controller 10 (not shown; the actual location can be adjusted accordingly) dynamically adjusts the throttle valve 6 opening and compressor 4 speed after comparison. When d1 approaches d2, the throttle valve opening is reduced to lower the evaporation temperature, the compressor 4 speed is increased to increase the refrigerant circulation rate, and the condenser 5 is activated to enhance dehumidification, ensuring that d1 ≤ d2. These two factors are collaboratively optimized through a PID control algorithm to prevent condensation in the vacuum pump and achieve continuously adjustable dehumidification capacity. This significantly improves energy efficiency compared to traditional solutions, making it particularly suitable for humidity control in specialized environments such as aerospace simulation chambers and deep-sea laboratories.

[0053] Provide a set of specific working condition data:

[0054] 1. The vacuum pump unit is fully open, and the flow rate of a single unit is 3500m 3 / h, when maintaining pressure, turn on two vacuum pumps;

[0055] 2. Negative pressure test chamber 1, volume 8300m 3 , the pool surface area is 1500m 2 , gas leakage rate <0.05vol% / h;

[0056] 3. The initial air dry-bulb temperature in the negative pressure test chamber 1 is 35°C, and the initial wet-bulb temperature is 30°C;

[0057] 4. Initial air pressure 100kPa;

[0058] 5. Water surface temperature 30℃;

[0059] 6. The temperature after vacuum pump is 45℃;

[0060] 7. Air-water convection heat transfer coefficient 10W / (m 2 K);

[0061] 8. Evaporation is calculated according to ASHRAE handbook.

[0062] According to measurements and calculations, as the vacuum pump draws air, the air pressure gradually decreases from 100kPa to 10kPa, which takes about 70 minutes. The corresponding air temperature gradually decreases from 35°C to 20.2°C. As the air pressure decreases, the water vapor evaporated from the surface of the experimental chamber 1 enters the air, and the air density decreases from 1.15kg / m 3 Gradually reduce to 0.11kg / m 3 The relative humidity of the air increased to 96%; the air moisture content gradually increased from 22g / kg to 182g / kg, and the air enthalpy gradually increased from 100kJ / kg to 480kJ / kg. The humid air entered the evaporator 3 in the dehumidification chamber 2 and was cooled to 20.2°C (below the dew point of 25°C) at an evaporation temperature of -5°C (0.4MPa). The condensed water was temporarily stored in the water storage chamber 7. When the humidity sensor detected that the evaporator outlet moisture content d1 approached the vacuum pump outlet threshold d2, the control system activated the throttle valve 6 opening, increased the compressor 4 speed, and activated the condenser's three-stage speed regulation. Using the PID algorithm, the evaporation temperature was maintained at -5±0.3°C and the compressor discharge pressure at 1.8±0.05MPa. At this point, in this large negative pressure test chamber, the air moisture content after the evaporator dropped to 58g / kg, lower than the 65g / kg after the vacuum pump. No condensate was generated in the vacuum pump unit, indicating a good dehumidification effect.

[0063] In the above description, the sensors, controllers and control programs that may be involved are all existing technologies and will not be described in detail.

[0064] The embodiments of the present invention disclosed above are intended only to illustrate the present invention. The embodiments do not describe all details in detail, nor do they limit the present invention to the specific embodiments described. Numerous modifications and variations are possible based on the contents of this specification. These embodiments are selected and described in detail in this specification to better explain the principles and practical applications of the present invention, thereby enabling those skilled in the art to better understand and utilize the present invention.

Claims

1. A vapor compression cycle refrigeration and dehumidification method for a large negative pressure test chamber, characterized in that: The following steps are involved: When the humidity of the experimental chamber (1) reaches a preset value, the gas is introduced into the dehumidification chamber (2) through the vacuum pump group (11), coupled with the evaporator (3), and then discharged from the outlet of the evaporator (3) through the vacuum pump group (11); Detecting the humidity at the outlet of the evaporator (3) as d1; Detecting the humidity at the outlet of the vacuum pump group (11) as d2; When d1 is greater than d2, the refrigerant circulation amount in the evaporator (3) is increased until d1 is less than or equal to d2.

2. The vapor compression cycle refrigeration and dehumidification method for a large negative pressure test chamber according to claim 1, characterized in that: When d1 approaches d2, the amount of refrigerant circulating in the evaporator (3) increases.

3. A device using the vapor compression cycle refrigeration and dehumidification method of a large negative pressure test chamber as claimed in claim 1 or 2, characterized in that: include: The dehumidification chamber (2) has an inlet end connected to the experimental chamber (1) and an outlet end connected to an inlet end of a vacuum pump assembly (11); An evaporator (3) is disposed in the experimental chamber (1) and is coupled with the gas flowing through the dehumidification chamber (2); a refrigeration system connected to the evaporator (3) for circulating a refrigerant; A first humidity sensor (8) is provided at the outlet of the evaporator (3) and is used to detect the humidity of the gas flowing therethrough; A second humidity sensor (9) is provided at the outlet of the vacuum pump assembly (11) for detecting the humidity of the gas flowing therethrough; The controller (10) is connected to the first humidity sensor (8) and the second humidity sensor (9) and is used to collect signals from the first humidity sensor (8) and the second humidity sensor (9) and control the refrigerant circulation amount of the refrigeration system after comparing the signals.

4. The device according to claim 3, characterized in that: The two ends of the circulation flow path of the refrigeration system are respectively connected to the coolant inlet and outlet of the evaporator (3), and a compressor (4), a condenser (5) and a throttle valve (6) are provided on the flow path.

5. The device according to claim 4, characterized in that: The compressor (4) and the throttle valve (6) are both connected to a controller (10).

6. The device according to claim 4, characterized in that: The compressor (4) is a speed-adjustable compressor, and the throttle valve (6) is an opening-adjustable throttle valve.

7. The device according to claim 3, characterized in that: The evaporator (3) is provided with a water storage chamber (7) for storing condensed water.

8. The device according to claim 6, characterized in that: The water storage chamber (7) is provided with a valve.

9. The device according to claim 4, 5, 6 or 7, characterized in that: The vacuum pump group (11) is provided with a plurality of vacuum pumps connected in parallel.

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