Ice pool test chamber constant temperature double shell side blowing type ice making air flow control method

Abstract

The application provides a kind of ice pool test room constant temperature double-shell side-blown type ice-making airflow control method, it is characterized in that, using the following steps: S1. start the cold air blower, set the initial air supply temperature of the cold air blower as T1, S2. adjust the secondary air supply temperature of the cold air blower, S3. after the secondary air supply of the cold air blower, test obtains the temperature difference of air supply port and return air port, when the temperature difference between indoor temperature and air supply temperature T2 is less than 0.1 DEG C, stop air supply at this time;S4. record the duration of the initial stage refrigeration, test the ice thickness, and calculate the ice volume according to the pool length and pool width;S5. the ratio of initial air supply temperature rise and average temperature rise required for initial stage ice formation, S6. remove the ice block that has been iced, carry out spray crystal operation on the ice pool, so that a very thin ice layer is formed on the surface of the ice pool;S7. start the cold air blower, obtain the air supply temperature of the third ice-making of the cold air blower.The method has higher reproducibility for model ice.

Description

Technical Field

[0001] This invention belongs to the field of marine ice environment testing technology, specifically, it relates to a method for controlling the airflow of a constant-temperature double-shell side-blowing ice-making system in an ice pool test chamber. Background Technology

[0002] For a long time, maritime transport across Eurasia has relied primarily on southern shipping routes such as the Panama Canal and the Suez Canal, which connect the Pacific and Atlantic Oceans. However, due to factors such as climate change in the Arctic region, warming of the Arctic Ocean, and the Suez Canal's recent blockages, attention has increasingly focused on Arctic shipping routes. The Arctic shipping routes consist of the Northeast Passage, with most of its route along the northern coast of Russia, and the Northwest Passage, with most of its route in the waters of the Canadian Arctic Archipelago. This route significantly shortens voyages, reduces transportation costs, and also avoids the threat of piracy.

[0003] The development of Arctic shipping routes has placed urgent technical demands on icebreakers and ice engineering structures. To address these engineering challenges related to sea ice environments, various countries have constructed ice-water pool testing facilities. Among these, the core technology of ice-water pool testing lies in how to form model ice of a certain thickness and with high flatness within a specified time and designated test area. Summary of the Invention

[0004] The present invention aims to overcome the above-mentioned defects and to provide an ice-making method that can produce model ice with a standard thickness and uniform distribution in an ice pool test area within a specified time, and has a high degree of reproducibility in producing model ice, thereby providing a more realistic and reliable sea ice test environment for icebreakers, ice engineering structures, etc.

[0005] This invention provides a constant-temperature double-shell side-blowing ice-making airflow control method for an ice pool test chamber. This method, under conditions of significant external temperature variations, utilizes a method of sequentially laterally jetting low-temperature air into the water within the insulated inner shell test chamber area to form a uniformly thick model ice layer within a specified time. The method is characterized by the following steps:

[0006] S1. Turn on the air cooler and set the initial air supply temperature of the air cooler to T1. The value of T1 is obtained based on formula (4):

[0007]

[0008] In the formula, T1 is the initial stage air supply temperature of the evaporative cooler, and λ1 is the initial stage air supply temperature coefficient. The average temperature rise caused by the ice-making airflow cooling the water body during the ice-making period;

[0009] S2. Monitor the temperature rise Δt1 at the air supply and return vents and compare it with the average temperature rise caused by the ice-making airflow supplying water during the ice-making period, thereby adjusting the secondary air supply temperature of the air cooler, which is obtained based on formula (5):

[0010] T2=λ2×T1 (5)

[0011] In the formula, T2 is the secondary air supply temperature of the evaporative cooler, and λ2 is the temperature difference coefficient between the supply air and the set temperature, based on... As long as the air is continuously supplied into the room, the indoor temperature will become closer and closer to the supply air temperature.

[0012] S3. After the air cooler supplies air for the second time, the temperature difference between the air supply outlet and the return air outlet is measured. When the difference between the return air outlet temperature and the secondary air supply temperature T2 is less than 0.1℃, the air supply is stopped.

[0013] S4. Record the initial cooling time, test the ice thickness, and calculate the ice volume based on the pool length and pool width;

[0014] S5. The ratio of the supply and return air temperature difference after the second adjustment of the evaporative cooler to the average temperature rise required for the initial stage of icing is obtained based on formula (6):

[0015] λ3=△t2÷(a×b×h2×ρ ice ×q ice ÷T”÷c÷m) (6)

[0016] In the formula, λ3 is the ratio of the supply and return air temperature difference after the second adjustment of the evaporative cooler to the average supply air temperature difference required for the initial stage of icing, Δt2 is the supply and return air temperature difference after the second adjustment of the evaporative cooler, h2 is the average thickness of the initial stage of icing, and T” is the cooling time in the initial stage.

[0017] S6. Remove the frozen ice blocks and perform a spray crystal-inducing operation on the ice pool to form an extremely thin (1mm-5mm) ice layer on the surface of the ice pool.

[0018] S7. Turn on the air cooler, and calculate its air supply temperature based on formula (7):

[0019]

[0020] In the formula, T3 is the air supply temperature for the third ice-making process of the evaporative cooler.

[0021] Furthermore, the present invention provides a method for controlling the airflow of a constant-temperature double-shell side-blowing ice-making system in an ice pool test chamber, characterized in that:

[0022] The above The method for obtaining it is as follows:

[0023] S1-1. Based on the required ice thickness and the length and width of the water body in the ice pool test chamber, obtain the total cooling capacity required for ice production.

[0024] S1-2. Based on the required ice-making time and the total cooling capacity needed for ice making, obtain the average cooling capacity that the ice-making airflow needs to provide within the ice-making time.

[0025] S1-3. Based on the average cooling capacity required by the ice-making gas flow during the ice-making period, obtain the average temperature rise caused by the ice-making gas flow cooling the water body.

[0026] Furthermore, the present invention provides a method for controlling the airflow of a constant-temperature double-shell side-blowing ice-making system in an ice pool test chamber, characterized in that:

[0027] The total cooling capacity required for ice making is calculated using formula (1):

[0028]

[0029] In the formula, The total cooling capacity required for ice making is given by: ρ represents the total cooling capacity required, a is the length of the water in the ice pool test chamber, b is the width of the water in the ice pool test chamber, h1 is the total ice thickness set in the experiment, and ρ represents the total cooling capacity required for ice making. ice Let q be the density of ice. ice It is the latent heat of freezing of ice.

[0030] Furthermore, the present invention provides a method for controlling the airflow of a constant-temperature double-shell side-blowing ice-making system in an ice pool test chamber, characterized in that:

[0031] The average cooling capacity required by the ice-making airflow during the above ice-making time is calculated using formula (2):

[0032]

[0033] In the formula, T' is the average cooling capacity required by the ice-making airflow during the ice-making time, and T' is the ice-making time specified in the test.

[0034] Furthermore, the present invention provides a method for controlling the airflow of a constant-temperature double-shell side-blowing ice-making system in an ice pool test chamber, characterized in that:

[0035] The average temperature rise caused by the ice-making airflow cooling the water body is calculated using formula (3):

[0036]

[0037] In the formula, Let c be the average temperature rise caused by the ice-making gas flow cooling the water body during the ice-making time, and m be the specific heat capacity of the ice-making gas flow.

[0038] Furthermore, the present invention provides a method for controlling the airflow of a constant-temperature double-shell side-blowing ice-making system in an ice pool test chamber, characterized in that:

[0039] The mass flow rate of the ice-making airflow generated by the aforementioned air cooler should ensure that the average wind speed at the 1.2m high air outlet is not less than 2.5m / s.

[0040] Furthermore, the present invention provides a method for controlling the airflow of a constant-temperature double-shell side-blowing ice-making system in an ice pool test chamber, characterized in that:

[0041] The experiment must be conducted in an environment with an external temperature of 20-25℃.

[0042] The aforementioned external space refers to the space outside the ice-making room.

[0043] Furthermore, the present invention provides a method for controlling the airflow of a constant-temperature double-shell side-blowing ice-making system in an ice pool test chamber, characterized in that:

[0044] The aforementioned air cooler uses a method of alternating forward and reverse blowing at a certain frequency to cool the ice-making area.

[0045] Furthermore, the present invention provides a method for controlling the airflow of a constant-temperature double-shell side-blowing ice-making system in an ice pool test chamber, characterized in that:

[0046] The above-mentioned constant temperature double-shell side-blowing ice-making airflow control method for ice pool test chambers is based on equipment with side-cooled airflow to the ice-making area. Attached Figure Description

[0047] Figure 1 This embodiment provides a flowchart illustrating a constant-temperature double-shell side-blowing ice-making airflow control method for an ice pool test chamber.

[0048] Figure 2 A schematic diagram of the ice-making equipment on which the method provided in this embodiment is based.

[0049] Figure 3 A schematic diagram of the ice-making equipment on which the method provided in this embodiment is based.

[0050] in,

[0051] 1. Model ice; 2. Water in the test ice pool; 3. Insulation of the test ice pool wall; 4. Outer shell insulation; 5. Inner shell insulation; 6. Constant temperature air layer; 7. Two-way air cooler; 8. Horizontal air duct for cooling airflow; 9. Ceiling of air cooler equipment; 10. Air duct guide vanes; 11. Vertical air duct for cooling airflow; 12. Jet and return air outlet; 13. Ice thickness measuring instrument; 14. Thermometer; 15. Adjustable height main flow plate; 16. Upper area of ​​the ice water pool; 17. Air conditioning in the middle area of ​​the inner and outer shell insulation; 18. Interior area of ​​the test building; 19. External envelope of the test building; 20. Floor insulation of the test ice pool; 21. Vertical flow guide plate; 22. Spray crystal guide device; 23. Air duct support column; 24. External flow guide insulation body for the column. Detailed Implementation

[0052] like Figure 1 As shown in this embodiment, a method for controlling the airflow of a constant-temperature double-shell side-blowing ice-making system in an ice pool test chamber is as follows:

[0053] Based on the experimental requirements, the ice-making thickness and ice-making time are determined. Combined with the length and width of the water body in the ice pool test chamber, the total cooling capacity required for ice making can be calculated using formula (1):

[0054]

[0055] In the formula, The total cooling capacity required for ice making is given by: ρ represents the total cooling capacity required, a is the length of the water in the ice pool test chamber, b is the width of the water in the ice pool test chamber, h1 is the total ice thickness set in the experiment, and ρ represents the total cooling capacity required for ice making. ice Let q be the density of ice. ice It is the latent heat of freezing of ice.

[0056] Based on the ice-making time required by the experiment and the total cooling capacity required for ice making, the average cooling capacity that the ice-making airflow needs to provide within the ice-making time can be calculated using formula (2):

[0057]

[0058] In the formula, T' is the average cooling capacity required by the ice-making airflow during the ice-making time, and T' is the ice-making time specified in the test.

[0059] Based on the average cooling capacity required by the ice-making airflow during the ice-making period, the average temperature rise caused by the ice-making airflow cooling the water body can be calculated using formula (3):

[0060]

[0061] In the formula, Let c be the average temperature rise caused by the ice-making gas flow cooling the water body during the ice-making time, and m be the specific heat capacity of the ice-making gas flow.

[0062] The mass flow rate of the ice-making airflow generated by the evaporative cooler should ensure that the average wind speed in the air outlet area reaches 2.5 m / s.

[0063] Depending on the width of the chilled water tank, the height of the main guide vane can be adjusted to change the height of the air vents, allowing the system to adapt to the ice-making process requirements of different chilled water tank widths within a certain range. The angle of the vertical guide vane should also be determined appropriately during the initial debugging phase in the laboratory. In this embodiment, a 20°-30° inclination towards the column is recommended, ensuring that there is also ice-making airflow in the middle area of ​​the column, guaranteeing that the entire area above the chilled water tank is uniformly blasted with ice-making airflow and forced to exchange heat.

[0064] In the initial stage, the temperature in the test chamber is room temperature. First, the air conditioner in the outer shell insulation space is turned on to make the temperature in the inner and outer insulation shell space 20℃. Then, the air cooler is turned on and the initial air supply temperature of the air cooler is set to T1. Based on experience and simulation, this patent recommends that the value of T1 can be calculated using formula (4):

[0065]

[0066] In the formula, T1 is the initial stage air supply temperature of the air cooler, and λ1 is the initial stage air supply temperature coefficient, which is recommended to be 2 to 3 in this patent.

[0067] Monitor the temperature rise Δt1 at the air supply and return vents and compare it with the average temperature rise caused by the ice-making airflow supplying water during the ice-making period, so as to adjust the secondary air supply temperature of the air cooler. It can be calculated using formula (5):

[0068] T2=λ2×T1 (5)

[0069] In the formula, T2 is the secondary air supply temperature of the evaporative cooler, and λ2 is the temperature difference coefficient between the supply air and the set temperature, which can be calculated according to... calculate.

[0070] After the evaporative air cooler delivers air for the second time, the temperature difference between the supply air outlet and the return air outlet is measured. When the difference between the indoor temperature and the supply air temperature T2 is less than 0.1℃, the air supply is stopped, the initial cooling time is recorded, and then the ice thickness is measured. The ice volume is calculated based on the pool length and pool width. The ratio of the initial supply air temperature rise to the average temperature rise required for the initial ice formation can be calculated using formula (6):

[0071] λ3=△t2÷(a×b×h2×ρ ice ×q ice ÷T”÷c÷m) (6)

[0072] In the formula, λ3 is the ratio of the supply and return air temperature difference after the second adjustment of the air cooler to the average supply air temperature difference required for the initial stage of icing, h2 is the average thickness of the initial stage of icing, and T” is the cooling time in the initial stage.

[0073] Remove the frozen ice. Perform a spray crystallization operation on the ice pool to form an extremely thin ice layer on the surface of the ice pool. Then turn on the cold air blower, and the air supply temperature can be calculated using formula (7):

[0074]

[0075] In the formula, T3 is the air supply temperature for the third ice-making process of the evaporative cooler.

[0076] Maintain the temperature of the middle area between the inner and outer shell insulation, and blow air in the forward direction for half an hour, then blow air in the reverse direction for half an hour, until the ice thickness reaches the thickness specified in the test.

[0077] The above method is applicable to experimental systems with side-blowing airflow.

[0078] The above method is preferably carried out in a test system with external environmental control equipment outside the ice-making chamber.

[0079] In this embodiment, an experimental system that can be used in this method is also provided. However, it should be noted that this experimental system is not the only corresponding experimental system. Any system that meets the side blowing conditions can be used in accordance with the method of this embodiment.

[0080] The experimental system proposed in this embodiment is as follows: Figure 2 and 3 As shown, it can be installed in any indoor or outdoor environment, and it consists of a double-layer structure consisting of an ice pool body and an outer shell.

[0081] In this embodiment, the main body of the ice pool has a convex inner space with the convex part facing downwards;

[0082] The walls of the main body of the ice pool (such as the floor 20, inner shell 5, etc.) are all insulated structures;

[0083] The lower part of the interior space is the ice pool. During the process of cold air ice making, water body 2 is located in the lower part, and model ice 1 is gradually generated in the upper part.

[0084] The ice pool body has a pool wall insulation layer 3. The pool wall insulation layer 3 can be made or covered by traditional insulation materials such as insulation cotton, or it can be embedded with various electronically controlled insulation elements with refrigeration functions commonly used in this field.

[0085] An ice thickness measuring instrument 13 is installed inside the ice pool or at the opening of the ice pool.

[0086] The upper part 16 of the aforementioned ice pool body is equipped with an air-cooling component;

[0087] The air-cooled assembly includes a cold air emitter (bidirectional air cooler) 7, a fluid channel (horizontal duct for cooling airflow) 8, and a main directional mechanism (adjustable height main flow plate) 15;

[0088] The cold air emission device 7 is installed directly above the ice pool, at the top of the ice pool body. Generally, in order to ensure the stability of the installation structure, the lower part of the cold air emission device 7, or its installation position, has a cold air fan ceiling 9 for the structural installation of the equipment.

[0089] In addition, a temperature measuring instrument 14 is installed on the ceiling corresponding to the position of the wind emission device 7;

[0090] The fluid channel 8 is symmetrical and connects to the air outlets on both sides of the cold air emission device 7, thereby achieving the effect of cold air output.

[0091] At the end of the fluid channel 8, namely the inlet and outlet of the cold air (when one end does not release cold air, it is the return air inlet to ensure the circulation of air volume), a main directional mechanism 15 is installed.

[0092] The fluid channel 8 has a supporting structure (air duct support column) 23;

[0093] The outer surface of the support structure 23 has a thermal insulation structure (external flow insulation body) 24, such as thermal insulation cotton covering.

[0094] On the exterior surface of the support structure 23, above the main steering mechanism 15, a vertical backflow plate 21 is also installed.

[0095] Within the fluid channel 23, at a corner position, there is a rectifier mechanism (duct rectifier guide vane) 10.

[0096] The main direction of the outlet of the mechanism 15 is directly opposite the ice pool, that is, the location of the model ice.

[0097] The main steering mechanism 15 is a height-adjustable structure. This height-adjustable structure can adopt a conventional flip-plate structure, sliding structure, or similar structure. Its up-and-down movement can be controlled by a switch at the front end of the equipment, a manual handle, or an electronic control.

[0098] The outlet position of the main guiding mechanism 23 is equipped with a thermometer 15.

[0099] The main body of the ice pool has a shell 4 on its exterior;

[0100] The casing 4 is also an insulation structure;

[0101] An air layer 6 exists between the shell 4 and the main body of the ice pool;

[0102] A temperature regulation mechanism (air conditioning in the middle area of ​​the inner and outer shell insulation) 17 is also installed between the shell 4 and the ice pool body.

[0103] The function and effect of this specific embodiment:

[0104] In this embodiment, an outer shell insulation layer is first installed inside the outer envelope of the test building, with a constant temperature air layer of a certain thickness inside the outer shell insulation layer, and then an inner shell insulation layer is installed.

[0105] The inner shell is insulated and contains a vertical air duct for cooling airflow. There is one such air duct on each side of the ice pool test chamber. Above the vertical air duct is the ceiling of the air cooler equipment. The air cooler is located in the upper middle part of the ceiling space. The air cooler can output air in both directions and has horizontal air ducts and guide vanes on both sides.

[0106] The lower part of the vertical air duct is a jet and return air outlet, with a main flow guide plate installed below the outlet. Due to the large span of the lateral vertical air duct in the large ice pool test chamber, a duct support column is required. To improve the uniformity of the cooling airflow outside the column, two vertical guide plates are installed on both sides of the column, above the main flow guide plate.

[0107] In addition, a guide insulation element is installed outside the column to further increase the air velocity in this area. The cooling airflow passes laterally through an adjustable-height air jet over the upper part of the ice water pool, and then flows back into the ceiling space through a vertical air duct on the other side.

[0108] The spray crystal-attracting device is located above the ice water pool, and an ice thickness measuring instrument is also installed above the pool. Temperature gauges are installed at the air supply and return vents on both sides and near the ceiling in the upper part of the ice water pool. Insulation measures are also installed on the outside of the ice water pool walls.

[0109] When using the above method, first turn on the air conditioner in the middle area of ​​the inner and outer shell insulation of the above equipment to maintain a constant temperature air layer in the double-shell insulation structure, ensuring that the experimental ice-making process is kept within a controllable range by external ambient temperature disturbances. For the experimental ice pool, start the water cooling system, circulating the water in the ice pool until it approaches the freezing temperature.

[0110] Furthermore, the height of the main flow plate can be adjusted according to different track heights. This invention recommends that the height of the main flow plate should be such that its extension line is higher than the track, to ensure that the jet of cold air is not blocked by the track, so that the system can adapt to the ice-making process requirements of different track heights of the ice water pool within a certain range.

[0111] The angle of the vertical guide plate should also be determined during the initial debugging stage in the laboratory. In this embodiment, it is recommended to tilt the column at a 20°-30° angle so that there is also ice-making airflow in the middle area of ​​the column, ensuring that the entire ice water pool can be blown by a uniform ice-making airflow and forced to exchange heat.

Claims

1. A method for controlling the airflow of a constant-temperature double-shell side-blowing ice-making system in an ice pool test chamber, characterized in that, The following steps are to be taken: S1. Turn on the air cooler and set the initial air supply temperature of the air cooler to T1, wherein the value of T1 is obtained based on formula (4): In the formula, T1 is the initial stage air supply temperature of the evaporative cooler, and λ1 is the initial stage air supply temperature coefficient. The average temperature rise caused by the ice-making airflow cooling the water body during the ice-making period; S2. Monitor the temperature rise Δt1 at the air supply and return vents and compare it with the average temperature rise caused by the ice-making airflow supplying water during the ice-making period, thereby adjusting the secondary air supply temperature of the air cooler, which is obtained based on formula (5): T2=λ2×T1 (5) In the formula, T2 is the secondary air supply temperature of the evaporative cooler, and λ2 is the temperature difference coefficient between the supply air and the set temperature, based on... get; S3. After the air cooler supplies air for the second time, the temperature difference between the air supply outlet and the return air outlet is measured. When the difference between the return air outlet temperature and the secondary air supply temperature T2 is less than 0.1℃, the air supply is stopped. S4. Record the initial cooling time, test the ice thickness, and calculate the ice volume based on the pool length and pool width; S5. The ratio of the supply and return air temperature difference after the second adjustment of the evaporative cooler to the average temperature rise required for the initial stage of icing is obtained based on formula (6): λ3=△t2÷(a×b×h2×ρ ice ×q ice (6) In the formula, λ3 is the ratio of the supply and return air temperature difference after the second adjustment of the evaporative cooler to the average supply air temperature difference required for the initial stage of icing, Δt2 is the supply and return air temperature difference after the second adjustment of the evaporative cooler, h2 is the average thickness of the initial stage of icing, and T” is the cooling time in the initial stage. S6. Remove the frozen ice blocks and perform a spray crystal-inducing operation on the ice pool to form an extremely thin ice layer on the surface of the ice pool; S7. Turn on the air cooler, and calculate its air supply temperature based on formula (7): In the formula, T3 is the air supply temperature for the third ice-making process of the evaporative cooler.

2. The method for controlling the airflow of a constant-temperature double-shell side-blowing ice-making system in an ice pool test chamber as described in claim 1, characterized in that: The The method for obtaining it is as follows: S1-1. Based on the required ice thickness and the length and width of the water body in the ice pool test chamber, obtain the total cooling capacity required for ice production. S1-2. Based on the required ice-making time and the total cooling capacity needed for ice making, obtain the average cooling capacity that the ice-making airflow needs to provide within the ice-making time. S1-3. Based on the average cooling capacity required by the ice-making gas flow during the ice-making period, obtain the average temperature rise caused by the ice-making gas flow cooling the water body.

3. The method for controlling the airflow of a constant-temperature double-shell side-blowing ice-making system in an ice pool test chamber as described in claim 2, characterized in that: The total cooling capacity required for ice making is calculated using formula (1): In the formula, The total cooling capacity required for ice making is given by: ρ represents the total cooling capacity required, a is the length of the water in the ice pool test chamber, b is the width of the water in the ice pool test chamber, h1 is the total ice thickness set in the experiment, and ρ represents the total cooling capacity required for ice making. ice Let q be the density of ice. ice It is the latent heat of freezing of ice.

4. The method for controlling the airflow of a constant-temperature double-shell side-blowing ice-making system in an ice pool test chamber as described in claim 2, characterized in that: The average cooling capacity required by the ice-making airflow during the ice-making time is calculated using formula (2): In the formula, T' is the average cooling capacity required by the ice-making airflow during the ice-making time, and T' is the ice-making time specified in the test.

5. The method for controlling the airflow of a constant-temperature double-shell side-blowing ice-making system in an ice pool test chamber as described in claim 2, characterized in that: The average temperature rise caused by the ice-making airflow cooling the water body is calculated using formula (3): In the formula, Let c be the average temperature rise caused by the ice-making gas flow cooling the water body during the ice-making time, and m be the specific heat capacity of the ice-making gas flow.

6. The method for controlling the airflow of a constant-temperature double-shell side-blowing ice-making system in an ice pool test chamber as described in claim 1, characterized in that: The mass flow rate of the ice-making airflow generated by the air cooler should ensure that the average wind speed at the 1.2m high air outlet is not less than 2.5m / s.

7. The method for controlling the airflow of a constant-temperature double-shell side-blowing ice-making system in an ice pool test chamber as described in claim 1, characterized in that: The experiment must be conducted in an environment with an external temperature of 20-25℃. The external space refers to the space outside the ice-making room.

8. The method for controlling the airflow of a constant-temperature double-shell side-blowing ice-making system in an ice pool test chamber as described in claim 1, characterized in that: The air cooler purifies the ice-making area by alternating forward and reverse purging at a certain frequency.

9. The method for controlling the airflow of a constant-temperature double-shell side-blowing ice-making system in an ice pool test chamber as described in claim 1, characterized in that: The method for controlling the airflow of a constant-temperature double-shell side-blowing ice-making system in an ice pool test chamber is based on a side-cooled air-cooled device for the ice-making area.

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