A high-efficiency gradient refrigeration cycle system and a method of operating the same

Abstract

The application provides a high-efficiency gradient refrigeration cycle system and a running method thereof, comprising a heat release unit, a pressure reduction unit and a gradient refrigeration module; a temperature gradient control mechanism is arranged in the gradient refrigeration module, and the temperature gradient control mechanism is configured to gradually increase the temperature of a refrigeration working medium according to a preset curve in a heat absorption process, so as to match the temperature curve of a cooled medium and reduce heat transfer loss. The temperature gradient control mechanism is used to realize dynamic matching of the temperature curve of the refrigeration working medium and the cooled medium, and the irreversible loss in the heat transfer process is greatly reduced. A multi-stage pressure regulation structure or a variable volume closed structure is adopted, and is matched with a high-precision sensor array and an intelligent control system, so that the refrigeration working medium can be accurately heated according to the preset curve, and the controllability and stability of the refrigeration process are greatly improved, and the high-precision temperature control requirement is met.

Description

Technical Field

[0001] This invention belongs to the field of refrigeration technology, and in particular relates to a high-efficiency gradient refrigeration cycle system and its operation method. Background Technology

[0002] In traditional refrigeration systems, a large temperature difference between the refrigerant and the medium being cooled during the cooling process leads to the generation of a large amount of irreversible heat during heat transfer. This heat loss reduces the system's energy efficiency. Current technologies typically employ a single-stage refrigeration cycle, where the refrigerant absorbs heat at a constant temperature in the evaporator. This mismatch between the refrigerant's temperature profile and that of the cooled medium results in a significant heat transfer temperature difference, increasing system energy consumption. Therefore, reducing the heat loss during the heat transfer process is crucial. Improving system energy efficiency and reducing energy loss have become urgent technical problems to be solved in this field. Summary of the Invention

[0003] To overcome the shortcomings of existing technologies, the present invention aims to provide a high-efficiency gradient refrigeration cycle system and its operation method, thereby solving the problems in existing refrigeration and heat transfer processes. Problems include high energy consumption and low energy efficiency.

[0004] To solve the above problems, the technical solution adopted by the present invention is as follows:

[0005] In a first aspect, the present invention provides a high-efficiency gradient cooling cycle system, including a heat release unit, a pressure reduction unit and a gradient cooling module;

[0006] The gradient cooling module is equipped with a temperature gradient control mechanism, which is configured to gradually increase the temperature of the refrigerant according to a preset curve during heat absorption, matching the temperature curve of the medium being cooled, thereby reducing heat transfer. damage.

[0007] In some embodiments, the cooled medium forms a countercurrent heat exchange relationship with the refrigerant within the gradient refrigeration module.

[0008] In some embodiments, the gradient cooling module adopts a variable volume closed structure, including:

[0009] A volume adjustment mechanism is configured to adjust the volume of the first chamber within the gradient cooling module for accommodating the refrigerant;

[0010] A pressure monitoring device is configured to monitor the working fluid pressure in the first chamber;

[0011] A temperature sensor array is configured to detect the temperature of the refrigerant and / or the medium being cooled in the heat exchange field constructed by the gradient refrigeration module.

[0012] The temperature gradient control mechanism is configured to control the volume adjustment mechanism to make the refrigerant heat up according to a preset curve and the relationship between saturation temperature and saturation pressure based on the detection data of the pressure monitoring device and the temperature sensor array.

[0013] In some embodiments, the gradient refrigeration module adopts a multi-stage pressure regulation structure. The pressure regulation structure is used to analyze the continuous preset curve of the refrigerant in the refrigeration cycle into a discrete process consisting of multiple combinations of evaporation heat absorption and adiabatic compression. The refrigerant is controlled to operate at a temperature close to the preset curve through the multi-stage discrete process with a gradient relationship.

[0014] In some embodiments, the gradient cooling module includes at least two evaporators and also includes a number of compressors equal to the number of evaporators;

[0015] A compressor is connected after each evaporator, and an evaporator and the compressor connected thereto form an evaporative compression module. At least two evaporative compression modules are connected in series and disposed between the outlet of the pressure reduction unit and the inlet of the heat release unit.

[0016] In some embodiments, the gradient cooling module includes at least two evaporators, the pressure reduction unit is a throttling valve in the same number as the evaporators, and the heat release unit is a condenser;

[0017] The inlet end of each throttling valve is connected to the outlet end of the condenser, and the outlet end of each throttling valve is connected to an evaporator. A throttling valve and the evaporator connected thereto form a throttling evaporation module. The outlet steam of each throttling evaporation module is subjected to staged compression or coupled compression and then introduced into the inlet of the heat release unit.

[0018] In some embodiments, the throttling evaporation modules are sorted from high to low according to the pressure after throttling, and each pressure level throttling evaporation module is connected to a compressor of the corresponding pressure level.

[0019] The lowest pressure steam generated by the lowest pressure stage throttling evaporation group is connected to the compressor inlet of the lowest pressure stage through a pipeline. The steam generated by the throttling evaporation groups of other pressure stages is combined with the outlet steam of the compressor of the corresponding pressure stage of the throttling evaporation module of the next lower pressure stage, and then enters the compressor inlet of the corresponding pressure stage. The outlet steam of the highest pressure stage compressor is connected to the condenser through a pipeline.

[0020] The heat exchange sequence between the cooled medium and each stage of the evaporator is from the highest pressure stage evaporator to the lowest pressure stage evaporator.

[0021] In some embodiments, the outlet steam of each of the throttling evaporation modules is fed into a compressor in the form of a single gas source or multiple gas sources, and the outlet steam of the compressor is connected to the condenser through a pipeline.

[0022] In some embodiments, each of the throttling evaporation modules is connected to a corresponding compressor, and the outlet steam of each compressor is connected to a condenser via a pipe.

[0023] In some embodiments, the pressure reduction unit employs a converging nozzle structure to convert the pressure difference energy of the working fluid into kinetic energy.

[0024] In some embodiments, the gradient cooling module employs a diffuser structure, in which the low-temperature, high-speed fluid generated by the depressurization device absorbs heat and simultaneously increases pressure and temperature.

[0025] In some embodiments, a booster device is also included, which employs continuous cooling to reduce compression power consumption.

[0026] In some embodiments, a booster device is also included, which employs multi-stage cooling to reduce compression power consumption.

[0027] Secondly, the present invention provides an operating method for the above-mentioned high-efficiency gradient cooling cycle system, comprising:

[0028] Based on the temperature drop curve of the cooling medium during the cooling process, the ideal temperature rise curve of the refrigerant in the gradient refrigeration module is determined, and the ideal temperature rise curve is set as the preset curve.

[0029] Based on the characteristic curve of the refrigerant's heat absorption process, a temperature gradient control mechanism is used to control the refrigerant's pressure increase process to approach the preset curve.

[0030] In some embodiments, including:

[0031] Real-time monitoring of the state parameters of the refrigerant and / or the medium being cooled;

[0032] Based on the structural characteristics of the refrigeration cycle system, a corresponding adjustment strategy is selected to dynamically optimize the heat transfer process.

[0033] In some embodiments, including:

[0034] State parameters are acquired through a multi-parameter real-time monitoring system, and a multi-dimensional state space containing key parameters such as temperature, pressure, and flow rate is established.

[0035] Thermodynamic theory-based calculation system for each component Loss, and perform dynamic optimization;

[0036] An adaptive control algorithm is adopted to automatically adjust system parameters according to load changes and environmental conditions, so that the deviation between the actual operating curve and the preset curve is less than the set threshold.

[0037] In some embodiments, including:

[0038] Determine the pressure boosting requirement of the refrigerant from the outlet of the gradient cooling module to the inlet of the heat release unit, and determine the ideal pressure boosting process line of the refrigerant with the goal of minimizing power consumption;

[0039] Using the ideal pressure boosting process line as the target line, the pressure boosting process of the refrigerant is made close to the ideal pressure boosting process line by controlling the cooling method, cooling medium, cooling temperature and cooling flow rate of the pressure boosting device.

[0040] In some embodiments, the working fluid of the pressurizing device is steam, the inlet steam of the pressurizing device is in a saturated state, and the selected saturated steam line is the ideal pressurizing process line.

[0041] In some embodiments, the working fluid of the pressurizing device is steam, the inlet steam of the pressurizing device is in a supersaturated state, the steam superheat is set, and the steam pressurization curve with a specific steam superheat is selected as the ideal pressurization process line.

[0042] Compared with the prior art, the present invention has at least the following beneficial effects:

[0043] 1. This invention achieves dynamic matching of the temperature curves of the refrigerant and the cooled medium through a temperature gradient control mechanism, which greatly reduces irreversible losses during the heat transfer process.

[0044] 2. By adopting a multi-stage pressure regulation structure or a variable volume closed structure, combined with a high-precision sensor array and intelligent control system, the refrigerant can be precisely heated according to a preset curve, which greatly improves the controllability and stability of the refrigeration process and meets the requirements of high-precision temperature control.

[0045] The present invention will now be described in further detail with reference to the accompanying drawings and specific embodiments. Attached Figure Description

[0046] The present invention will be further described with reference to the accompanying drawings, but the embodiments in the drawings do not constitute any limitation on the present invention. For those skilled in the art, other drawings can be obtained based on the following drawings without creative effort.

[0047] Figure 1 This is a schematic diagram of the framework of a high-efficiency gradient cooling cycle system under one embodiment of this Example 1.

[0048] Figure 2This is a schematic diagram of a high-efficiency gradient cooling cycle system under another implementation method in Embodiment 3.

[0049] Figure 3 This is a schematic diagram of a high-efficiency gradient cooling cycle system under one implementation method in Example 4.

[0050] Figure 4 This is a schematic diagram of a high-efficiency gradient cooling cycle system under another implementation method in Example 4.

[0051] Figure 5 This is a schematic diagram of the framework of a high-efficiency gradient cooling cycle system under another embodiment of Example 4.

[0052] Figure 6 This is a schematic diagram of a high-efficiency gradient cooling cycle system under one embodiment of Example 5. Detailed Implementation

[0053] The technical solution of the present invention will now be clearly and completely described with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0054] In the description of this invention, it should be noted that the terms "center," "upper," "lower," "left," "right," "vertical," "horizontal," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing the invention and for simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on the invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0055] In the description of this invention, when a specific device is described as being located between a first device and a second device, an intermediary device may or may not be present between the specific device and the first or second device. When a specific device is described as being connected to other devices, the specific device may be directly connected to the other devices without an intermediary device, or it may not be directly connected to the other devices but may have an intermediary device.

[0056] Techniques, methods, and equipment known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and equipment should be considered part of the specification.

[0057] Example 1:

[0058] Reference Figure 1 This embodiment 1 provides a high-efficiency gradient cooling cycle system, including a heat release unit 10, a pressure reduction unit 20 and a gradient cooling module 30;

[0059] The gradient cooling module 30 is equipped with a temperature gradient control mechanism. This mechanism is configured to gradually increase the temperature of the refrigerant according to a preset curve during heat absorption, matching the temperature curve of the medium being cooled, thereby reducing heat transfer. damage.

[0060] It should be noted that in a traditional refrigeration cycle, the refrigerant maintains its saturated temperature at its saturated pressure during heat exchange. Furthermore, friction losses occur along the refrigerant's path, resulting in pressure loss. Therefore, as heat exchange progresses, the actual saturated pressure of the refrigerant continuously decreases. That is, if the refrigerant's saturated pressure at the start of the evaporation process corresponds to a temperature of 8 degrees Celsius, its current saturated pressure at the end of the evaporation process corresponds to a temperature of 6 degrees Celsius, representing a 2-degree Celsius loss. However, because the temperature of the cooled medium before and after heat exchange is higher than that of the refrigerant, further loss of evaporation temperature by the refrigerant increases the temperature difference between the refrigerant and the cooled medium, thus affecting the heat exchange process. Increased heat loss and decreased efficiency; therefore, in this embodiment, during the heat absorption process of the refrigerant, a temperature gradient control mechanism is used for phase adaptation control, so that the temperature rise curve of the refrigerant matches the temperature curve of the cooled medium, reducing the temperature difference between the two. By allowing the temperature of the refrigerant to gradually increase during the heat exchange process, a better heat transfer process is achieved, thereby reducing heat loss. Reduce heat loss and improve heat transfer efficiency.

[0061] Preferably, the cooled medium and the refrigerant form a counter-current heat exchange relationship within the gradient refrigeration module 30. That is, in the heat exchange field constructed by the gradient refrigeration module 30, for example, if the temperature of the cooled medium before heat exchange is 25 degrees Celsius and after heat exchange is 15 degrees Celsius, and the temperature of the refrigerant before heat exchange is 5 degrees Celsius and after heat exchange is 15 degrees Celsius, due to the counter-current heat exchange relationship, the cooled medium at 25 degrees Celsius corresponds to the refrigerant at 15 degrees Celsius, and vice versa. It can be seen that regardless of whether the temperature difference between the cooled medium and the refrigerant is before or after heat exchange, it is controlled within 10 degrees Celsius. Essentially, during the heat exchange process, as the temperature of the refrigerant gradually increases, it can better match the cooling curve of the cooled medium, reducing the temperature difference during heat transfer. A smaller heat transfer temperature difference means smaller irreversible losses, thereby improving the thermodynamic efficiency of the system. By reducing power consumption, the system's required input power can be reduced, thus achieving energy savings.

[0062] Optionally, the temperature rise of the refrigerant is a process of dynamic matching with the temperature curve of the medium being cooled, and the temperature rise changes in a gradient.

[0063] Example 2:

[0064] As one implementation method, in this embodiment 2, the gradient cooling module 30 adopts a variable volume closed structure, including:

[0065] The volume adjustment mechanism is configured to adjust the volume of the first chamber within the gradient cooling module 30 for accommodating the refrigerant.

[0066] A pressure monitoring device is configured to monitor the working fluid pressure in the first chamber;

[0067] A temperature sensor array is configured to detect the temperature of the refrigerant and / or the medium being cooled in the heat exchange field constructed by the gradient cooling module 30.

[0068] The temperature gradient control mechanism is configured to control the volume adjustment mechanism to make the refrigerant heat up according to a preset curve and the relationship between saturation temperature and saturation pressure based on the detection data of the pressure monitoring device and the temperature sensor array.

[0069] In actual operation, the volume adjustment mechanism can dynamically adjust the volume of the refrigerant in the first chamber based on real-time data from the pressure monitoring device and temperature sensor array. By changing the volume, the pressure and temperature of the refrigerant are adjusted to ensure stable heating of the refrigerant according to a preset heating curve, while maintaining the correspondence between saturation temperature and saturation pressure. Specifically, when the pressure monitoring device detects a change in refrigerant pressure, the system automatically adjusts the temperature gradient control mechanism to optimize the heating path of the refrigerant, thereby improving cooling efficiency. The key benefit of this technical solution is that it achieves precise control of the refrigerant state, effectively reduces energy loss, and improves the system's adaptability and efficiency.

[0070] Alternatively, as another implementation, the gradient cooling module 30 adopts a multi-stage pressure regulation structure. The pressure regulation structure is used to analyze the continuous preset curve of the refrigerant in the refrigeration cycle into a discrete process consisting of multiple combinations of evaporation heat absorption and adiabatic compression. Through the multi-stage discrete process with a gradient relationship, the refrigerant is controlled to operate at a temperature close to the preset curve.

[0071] This implementation employs a multi-stage pressure control structure, analyzing the continuous preset temperature rise curve of the refrigerant in the refrigeration cycle into multiple discrete processes combining evaporation and heat absorption with adiabatic compression. Specifically, the refrigerant undergoes evaporation and heat absorption processes and compression processes at each stage, with these multiple discrete processes combining into a gradual temperature rise process. Each evaporation and compression stage corresponds to specific pressure and temperature changes, making the refrigerant's temperature rise process closer to the ideal preset curve. This multi-stage discrete control scheme can optimize the refrigerant's temperature rise path at different stages, thereby improving heat exchange efficiency, avoiding overcooling or temperature fluctuations common in traditional refrigeration methods, and thus reducing energy waste.

[0072] Example 3:

[0073] Reference Figure 2 In this embodiment 3, the gradient cooling module 30 includes at least two evaporators and also includes a compressor in the same number as the evaporators;

[0074] A compressor is connected after each evaporator, and an evaporator and the compressor connected thereto form an evaporation compression module 40. At least two evaporation compression modules 40 are connected in series and placed between the outlet of the pressure reduction unit 20 and the inlet of the heat release unit 10.

[0075] Each evaporator cools the medium through evaporation and heat absorption, allowing the refrigerant to absorb heat and evaporate. The compressor then compresses the evaporated gas to increase its energy density. This combined structure of evaporation and compression modules 40 allows the refrigerant to release its cooling and heat absorption capacity in multiple stages. Furthermore, the series module configuration further optimizes refrigeration efficiency, ensuring uniform and stable temperature rise of the refrigerant during heat exchange. Each evaporation and compression module 40 can be adjusted based on the difference between the actual and ideal temperature rise curves of the refrigerant, improving the overall system's heat exchange efficiency and reducing compression power consumption and the energy required for refrigeration.

[0076] Optionally, the compressor in this embodiment is a variable displacement compressor or a twin-screw compressor. The variable displacement compressor can adjust its volume according to changes in the state of the working fluid (such as changes in the ratio of gaseous to liquid states), so that it can effectively handle mixtures of liquid and gaseous working fluids during intake. The twin-screw compressor achieves compression through rotating screws, has high volumetric efficiency and compression efficiency, and can effectively handle gas mixtures containing liquid working fluids. Both variable displacement compressors and twin-screw compressors can precisely control the temperature rise during compression, avoiding changes in the properties of the working fluid and energy loss caused by excessively high temperatures during compression. This is crucial for improving the efficiency of the overall refrigeration system. Such compressors can achieve efficient compression and temperature rise of the gas-liquid two-phase refrigerant, thereby improving the performance and energy efficiency of the entire high-efficiency gradient refrigeration cycle system.

[0077] Example 4:

[0078] In this embodiment 4, the gradient cooling module 30 includes at least two evaporators, the pressure reduction unit 20 is a throttling valve with the same number as the evaporators, and the heat release unit 10 is a condenser.

[0079] The inlet end of each throttling valve is connected to the outlet end of the condenser, and the outlet end of each throttling valve is connected to an evaporator. A throttling evaporation module 50 is formed by combining a throttling valve and the evaporator connected thereto. The outlet steam of each throttling evaporation module 50 is compressed in stages or coupled and then introduced into the inlet of the heat release unit 10.

[0080] In practice, the throttling valve is used to regulate the flow and pressure of the refrigerant, converting the high-pressure refrigerant into low-pressure vapor. Each evaporator absorbs heat and lowers its temperature through the vapor after passing through the throttling valve. Optionally, the throttling valve is an electronic expansion valve. The opening degree of the electronic expansion valve corresponding to different throttling evaporation modules 50 is different, thus creating different pressure drops. The gradient change in pressure after throttling forms a saturated evaporation temperature with a gradient heat exchange effect. This design can minimize the energy loss in the heat exchange process. By optimizing the temperature control effect of each stage through a multi-stage pressure distribution system, the cooling effect of each evaporator is maximized, thereby improving the overall refrigeration efficiency.

[0081] Reference Figure 3 As one implementation method, a staged compression method is adopted. Specifically, the throttling evaporation modules 50 are sorted from high to low pressure after throttling, and each pressure level throttling evaporation module 50 is connected to a compressor of the corresponding pressure level.

[0082] like Figure 3 As shown, there are three stages of throttling evaporation modules 50 from top to bottom. The top stage has the lowest pressure, the middle stage has the next highest pressure, and the bottom stage has the highest pressure. The lowest pressure steam generated by the throttling evaporation module of the lowest pressure stage is connected to the compressor inlet of the lowest pressure stage through a pipe. The compressor of the lowest pressure stage is the first compression stage. The steam generated by the throttling evaporation modules of other pressure stages is combined with the outlet steam of the compressor of the corresponding pressure stage of the throttling evaporation module 50 of the next lower pressure stage, and then enters the compressor inlet of the corresponding pressure stage. The outlet steam of the compressor of the highest pressure stage is connected to the condenser through a pipe. In essence, the steam corresponding to the lowest pressure stage is first compressed and heated, then combined with the steam corresponding to the middle pressure stage for compression and heating, and finally combined with the steam corresponding to the highest pressure stage for compression and heating, forming a staged compression.

[0083] The heat exchange sequence between the cooled medium and each stage of the evaporator is from the highest pressure stage evaporator to the lowest pressure stage evaporator. The flow direction of the cooled medium differs from the compression direction of the refrigerant. The compression direction of the refrigerant is from low to high, while the flow direction of the cooled medium is from high to low.

[0084] The outlet steam of each throttling evaporation module 50 is arranged in descending order of pressure level and is compressed step by step by compressors of different pressure levels. Each compressor is responsible for compressing the steam generated by the throttling evaporation module 50 connected to it, ensuring that the steam maintains a high energy density when entering the next stage. When the steam is compressed step by step between pressure levels, the energy conversion is more efficient, avoiding energy waste caused by uneven compression. This design can achieve more precise compression control, ensuring stable temperature and pressure changes of the refrigerant, and effectively improving the efficiency and stability of the entire system.

[0085] Reference Figure 4 As another implementation method, coupled compression is employed. Specifically, the outlet vapor from each throttling evaporator module is fed into a compressor in the form of a single or multiple gas sources. The outlet vapor of the compressor is connected to the condenser through a pipeline. By using a single compressor to compress multiple gas sources, the compressor's operating efficiency is improved, and unnecessary compression devices in the system are reduced. This centralized compression method simplifies the system structure, improves compression efficiency, reduces equipment size and cost, and ensures that the system's cooling effect is not affected.

[0086] Reference Figure 5 As another implementation method, a staged compression approach is adopted. Specifically, each throttling evaporation module is connected to a corresponding compressor. The outlet steam of each compressor is connected to the condenser via a pipeline. Each compressor can be individually controlled, compressing and heating the steam at the outlet of each throttling evaporation module. The required compression and heating process for each throttling evaporation module can be adjusted individually to achieve a relatively consistent refrigerant exhaust state at the condenser inlet. A dedicated compressor handles the steam generated by each module. The outlet steam of each compressor is connected to the condenser via a pipeline, ensuring that the cooling capacity of each throttling evaporation module is maximized. This method optimizes the performance of each module while improving the system's adaptability, enabling it to handle more types of load changes and ensuring efficient operation under different working conditions.

[0087] Example 5:

[0088] Reference Figure 6 In this embodiment 5, the pressure reduction unit adopts a tapered nozzle structure 21 to convert the pressure difference energy of the working fluid into kinetic energy. Specifically, the tapered nozzle design accelerates the fluid through a gradually narrowing channel, thereby enabling the working fluid to flow at high speed during the pressure reduction process and enhancing heat exchange efficiency. This design not only optimizes the flow characteristics of the working fluid but also improves its heat absorption capacity, thereby reducing overall energy consumption and improving the heat transfer performance of the system.

[0089] Preferably, the gradient refrigeration module employs a diffuser structure 31, in which the low-temperature, high-speed fluid, processed by the pressure-reducing device, is introduced. Through diffusion, the working fluid absorbs heat while simultaneously increasing its temperature. A key feature of this structure is its ability to absorb external heat and increase its pressure as the working fluid transitions from a low-speed flow to a high-pressure, appropriately temperatured gas. This structure not only effectively absorbs the fluid's kinetic energy and raises the temperature of the refrigerant, but also improves the overall system's refrigeration efficiency and reduces system power consumption.

[0090] Optionally, the system also includes a booster unit 60, which employs continuous cooling to reduce compression power consumption. In practice, the continuous cooling process reduces the compressor load and minimizes energy loss during compression. Continuous cooling effectively controls the temperature of the working fluid during the boosting process, preventing energy waste due to overheating and ultimately improving the overall system's energy efficiency and operational stability.

[0091] Optionally, the system also includes a booster unit 60, which employs multi-stage cooling to reduce compression power consumption. Each stage of the cooling system precisely controls the cooling temperature and flow rate to ensure stable temperature changes of the working fluid during the multi-stage cooling process, ultimately achieving the ideal boost pressure state. This multi-stage cooling not only effectively reduces energy loss but also improves the overall stability and efficiency of the system, making it particularly suitable for refrigeration needs under high loads or long-term operation.

[0092] Example 6:

[0093] In this embodiment 6, an operating method for the above-mentioned high-efficiency gradient cooling cycle system is provided, including:

[0094] Based on the temperature drop curve of the cooling medium during the cooling process, the ideal temperature rise curve of the refrigerant in the gradient refrigeration module 30 is determined, and the ideal temperature rise curve is set as the preset curve.

[0095] Based on the characteristic curve of the refrigerant's heat absorption process, a temperature gradient control mechanism is used to control the refrigerant's pressure rise process to approach the ideal pressure rise process line, which corresponds to a preset curve. Since the preset curve and the ideal pressure rise process line have a unique correspondence during the refrigerant's heat absorption process, according to the one-to-one correspondence between saturation pressure and saturation temperature, controlling the refrigerant's pressure rise process to approach the preset curve is equivalent to controlling the refrigerant's pressure rise process to approach the ideal pressure rise process line.

[0096] In actual operation, users generally have a target temperature, such as the current room temperature of 35 degrees and need to adjust it to 25 degrees. There is a temperature difference of 10 degrees in between, which means that a temperature drop curve will be formed during the cooling process of the cooling medium. Based on the ideal heat transfer temperature difference of 8 degrees, the ideal temperature rise curve of the refrigerant in the gradient cooling module 30 can be determined. For example, the refrigerant is 17 degrees before heat exchange and 27 degrees after heat exchange. The curve of the refrigerant rising from 17 degrees to 27 degrees is set as the preset curve.

[0097] Then, based on the heat absorption characteristics of the refrigerant, since there is a one-to-one correspondence between saturation pressure and saturation temperature under saturated conditions, an ideal pressure rise process curve is determined. The correspondence between the ideal pressure rise process curve and the preset curve is established. By precisely controlling the temperature, pressure, and flow rate at each stage, it is ensured that the refrigerant can rise in the optimal way during the heat absorption process, thus perfectly matching the cooling process of the cooled medium. In actual operation, a temperature sensor array and a real-time data monitoring system are used to track the temperature changes of the cooling medium. At the same time, the flow state, pressure, and flow rate of the refrigerant in the gradient refrigeration module 30 are adjusted to ensure that the heating process of the refrigerant matches the set ideal curve. By adjusting the temperature gradient and the working state of the compression device in real time through the control system, the heating process is dynamically adjusted, and the system operating state is adjusted in real time to maximize refrigeration efficiency, reduce energy waste, and improve the overall refrigeration effect.

[0098] Specifically, including:

[0099] Real-time monitoring of the state parameters of the refrigerant and / or the medium being cooled; as the system load changes, the heat absorption capacity of the refrigerant will also change, so dynamic adjustment is needed to ensure optimal heat transfer. Changes in environmental conditions (such as outdoor temperature, humidity, etc.) will also affect the system operation; therefore, adopting real-time monitoring and dynamic optimization strategies can enable the system to maintain optimal performance under various changing conditions.

[0100] Based on the structural characteristics of the refrigeration cycle system, a corresponding adjustment strategy is selected to dynamically optimize the heat transfer process.

[0101] The system monitors the state parameters of the refrigerant and the cooled medium in real time through a multi-dimensional state space and selects appropriate adjustment strategies based on system characteristics. During implementation, the system adjusts the operating parameters of each component based on real-time data and uses a thermodynamic model to calculate energy loss. Based on this information, the control system automatically adjusts parameters such as refrigerant flow rate, pressure, and volume to optimize the heat exchange process, ensuring that parameters such as temperature and pressure are always within the optimal operating range. This improves cooling efficiency and effectively addresses operational changes under different loads and environmental conditions.

[0102] Furthermore, including:

[0103] State parameters are acquired through a multi-parameter real-time monitoring system, and a multi-dimensional state space containing key parameters such as temperature, pressure, and flow rate is established.

[0104] Thermodynamic theory-based calculation system for each component Loss, and perform dynamic optimization;

[0105] An adaptive control algorithm is adopted to automatically adjust system parameters according to load changes and environmental conditions, so that the deviation between the actual operating curve and the preset curve is less than the set threshold.

[0106] By monitoring the state parameters of the system in real time through a multi-dimensional state space, and combining thermodynamic theory to calculate the energy loss of each link, dynamic optimization is performed. The control system first collects data from various sensors (such as temperature, pressure, flow rate, etc.), and then calculates the energy loss of each link based on thermodynamics. Through adaptive control algorithms, the system can automatically adjust according to load changes and environmental conditions, thereby reducing the deviation from the preset curve, improving the stability and efficiency of operation, and ensuring that the system can maintain high-efficiency operation under different loads.

[0107] Furthermore, including:

[0108] Determine the pressure boosting requirement of the refrigerant from the outlet of the gradient cooling module 30 to the inlet of the heat release unit 10, and determine the ideal pressure boosting process line of the refrigerant with the goal of minimizing power consumption;

[0109] Using the ideal pressure boosting process line as the target line, the pressure boosting process of the refrigerant is made close to the ideal pressure boosting process line by controlling the cooling method, cooling medium, cooling temperature and cooling flow rate of the pressure boosting device 60.

[0110] During the compression process, the refrigerant experiences energy loss; therefore, employing an ideal pressure ramp-up process curve can minimize this loss. By setting an ideal pressure ramp-up curve, the system can more precisely control the refrigerant's temperature rise, ensuring maximum compressor efficiency and reducing power consumption. In implementation, the pressure ramp-up device 60 first calculates the ideal pressure ramp-up process curve based on the refrigerant's initial state (e.g., vapor saturation). Then, the control system optimizes the refrigerant's pressure ramp-up process by adjusting the temperature, flow rate, and cooling method of the cooling medium, ensuring the process closely approximates this ideal pressure ramp-up curve.

[0111] In one implementation, the working fluid of the booster device 60 is steam, and the steam at the inlet of the booster device 60 is in a saturated state. The saturated steam line is selected as the ideal boosting process line. Under saturated steam conditions, the temperature and pressure of the steam are stable. Selecting the saturated steam line as the boosting process line ensures stable steam heating, reduces energy loss, and maintains efficient compressor operation. In actual operation, the booster device 60 sets the boosting process line according to the saturated state of the working fluid steam and controls the cooling system accordingly to ensure that the steam remains in an ideal state throughout the boosting process.

[0112] In another implementation, the working fluid of the booster device 60 is steam. The steam at the inlet of the booster device 60 is in a supersaturated state. The steam superheat is set, and a steam boosting curve with a specific steam superheat is selected as the ideal boosting process curve. Supersaturated steam has higher thermal energy and can perform heat exchange more efficiently. During the boosting process, selecting a boosting curve with a specific superheat can further optimize the compression process and improve the compressor's operating efficiency. In practice, the control system sets the superheat according to the initial state of the working fluid and selects a suitable boosting curve. By adjusting the cooling temperature and flow rate, the boosting process of the working fluid conforms to the set ideal boosting curve, thereby achieving optimal energy efficiency.

[0113] It should be noted that the booster device in the above embodiments also includes a compressor, which will not be distinguished here.

[0114] In summary, compared with the prior art, the above embodiments have at least the following technical advantages:

[0115] High heat exchange efficiency: This system utilizes a temperature gradient control mechanism within the gradient cooling module 30 to ensure that the refrigerant gradually heats up according to a preset curve during heat absorption, precisely matching the temperature change of the cooled medium. The counter-current heat exchange design ensures a larger heat exchange area and a smaller temperature difference, thereby significantly improving the overall heat exchange efficiency.

[0116] Dynamically optimized operation capability: This system can monitor the state parameters of the refrigerant and the cooled medium in real time, and dynamically optimize the heat transfer process based on this data. Compared with traditional systems, this method improves the system's adaptability and response speed, ensuring that the system can still operate stably and efficiently under the influence of load changes and environmental condition fluctuations.

[0117] Reduced energy consumption: By setting ideal temperature rise and pressure rise curves, the system can optimize the compression and cooling processes, reducing unnecessary energy consumption. Simultaneously, the use of saturated and supersaturated steam further improves compression efficiency and reduces system power consumption.

[0118] Innovation of multi-stage pressure regulation structure: The multi-stage pressure regulation structure decomposes the heating process of the refrigerant into multiple discrete processes of evaporation heat absorption and adiabatic compression, thereby achieving fine control and avoiding the problems of temperature fluctuation and energy loss in traditional refrigeration methods.

[0119] The above embodiments are merely preferred embodiments of the present invention and should not be construed as limiting the scope of protection of the present invention. Any non-substantial changes and substitutions made by those skilled in the art based on the present invention shall fall within the scope of protection claimed by the present invention.

Claims

1. A high-efficiency gradient cooling cycle system, characterized in that, Includes a heat release unit, a step-down unit, and a gradient cooling module; The gradient cooling module is equipped with a temperature gradient control mechanism, which is configured to gradually increase the temperature of the refrigerant according to a preset curve during the heat absorption process, matching the temperature curve of the medium being cooled, so as to reduce heat transfer loss. Based on the temperature drop curve of the cooling medium during the cooling process, the ideal temperature rise curve of the refrigerant in the gradient refrigeration module is determined, and the ideal temperature rise curve is set as the reference target of the preset curve.

2. The high-efficiency gradient cooling cycle system as described in claim 1, characterized in that, The cooled medium forms a countercurrent heat exchange relationship with the refrigerant within the gradient refrigeration module.

3. A high-efficiency gradient cooling cycle system as described in claim 1 or 2, characterized in that, The gradient cooling module adopts a variable volume closed structure, including: A volume adjustment mechanism is configured to adjust the volume of the first chamber within the gradient cooling module for accommodating the refrigerant; A pressure monitoring device is configured to monitor the working fluid pressure in the first chamber; A temperature sensor array is configured to detect the temperature of the refrigerant and / or the medium being cooled in the heat exchange field constructed by the gradient refrigeration module. The temperature gradient control mechanism is configured to control the volume adjustment mechanism to make the refrigerant heat up according to a preset curve and the relationship between saturation temperature and saturation pressure based on the detection data of the pressure monitoring device and the temperature sensor array.

4. A high-efficiency gradient cooling cycle system as described in claim 1 or 2, characterized in that, The gradient refrigeration module adopts a multi-stage pressure regulation structure. The pressure regulation structure is used to analyze the continuous preset curve of the refrigerant in the refrigeration cycle into a discrete process consisting of multiple combinations of evaporation heat absorption and adiabatic compression. Through the multi-stage discrete process with a gradient relationship, the refrigerant is controlled to operate at a temperature close to the preset curve.

5. The high-efficiency gradient cooling cycle system as described in claim 4, characterized in that, The gradient cooling module includes at least two evaporators and also includes a number of compressors equal to the number of evaporators; A compressor is connected after each evaporator, and an evaporator and the compressor connected thereto form an evaporative compression module. At least two evaporative compression modules are connected in series and disposed between the outlet of the pressure reduction unit and the inlet of the heat release unit.

6. The high-efficiency gradient cooling cycle system as described in claim 4, characterized in that, The gradient cooling module includes at least two evaporators, the pressure reduction unit is a throttling valve with the same number of evaporators, and the heat release unit is a condenser; The inlet end of each throttling valve is connected to the outlet end of the condenser, and the outlet end of each throttling valve is connected to an evaporator. A throttling valve and the evaporator connected thereto form a throttling evaporation module. The outlet steam of each throttling evaporation module is subjected to staged compression or coupled compression and then introduced into the inlet of the heat release unit.

7. The high-efficiency gradient cooling cycle system as described in claim 6, characterized in that, The throttling evaporation modules are sorted from high to low pressure after throttling, and each pressure level throttling evaporation module is connected to a compressor of the corresponding pressure level. The lowest pressure steam generated by the lowest pressure stage throttling evaporation group is connected to the compressor inlet of the lowest pressure stage through a pipeline. The steam generated by the throttling evaporation groups of other pressure stages is combined with the outlet steam of the compressor of the corresponding pressure stage of the throttling evaporation module of the next lower pressure stage, and then enters the compressor inlet of the corresponding pressure stage. The outlet steam of the highest pressure stage compressor is connected to the condenser through a pipeline. The heat exchange sequence between the cooled medium and each stage of the evaporator is from the highest pressure stage evaporator to the lowest pressure stage evaporator.

8. The high-efficiency gradient cooling cycle system as described in claim 6, characterized in that, The outlet steam of each of the throttling evaporation modules is fed into a compressor in the form of a single gas source or multiple gas sources, and the outlet steam of the compressor is connected to the condenser through a pipeline.

9. The high-efficiency gradient cooling cycle system as described in claim 6, characterized in that, Each of the throttling evaporation modules is connected to a corresponding compressor, and the outlet steam of each compressor is connected to the condenser through a pipe.

10. A high-efficiency gradient cooling cycle system as described in claim 1 or 2, characterized in that, The pressure reduction unit adopts a converging nozzle structure to convert the pressure difference energy of the working fluid into kinetic energy.

11. The high-efficiency gradient cooling cycle system as described in claim 10, characterized in that, The gradient cooling module adopts a diffuser structure, in which the low-temperature high-speed fluid generated by the depressurization unit absorbs heat and simultaneously increases pressure and temperature.

12. The high-efficiency gradient cooling cycle system as described in claim 11, characterized in that, It also includes a booster unit, which employs continuous cooling to reduce compression power consumption.

13. The high-efficiency gradient cooling cycle system as described in claim 11, characterized in that, It also includes a booster unit, which employs multi-stage cooling to reduce compression power consumption.

14. A method for operating a high-efficiency gradient refrigeration cycle system as described in any one of claims 1 to 13, characterized in that, include: Based on the temperature drop curve of the cooling medium during the cooling process, the ideal temperature rise curve of the refrigerant in the gradient refrigeration module is determined, and the ideal temperature rise curve is set as the preset curve. Based on the characteristic curve of the refrigerant's heat absorption process, a temperature gradient control mechanism is used to control the refrigerant's pressure increase process to approach the preset curve.

15. The operating method as described in claim 14, characterized in that, include: Real-time monitoring of the state parameters of the refrigerant and / or the medium being cooled; Based on the structural characteristics of the refrigeration cycle system, a corresponding adjustment strategy is selected to dynamically optimize the heat transfer process.

16. The operating method as described in claim 15, characterized in that, include: State parameters are acquired through a multi-parameter real-time monitoring system, and a multi-dimensional state space containing key parameters such as temperature, pressure, and flow rate is established. The losses of each component of the system are calculated based on thermodynamic theory, and dynamic optimization is performed. An adaptive control algorithm is adopted to automatically adjust system parameters according to load changes and environmental conditions, so that the deviation between the actual operating curve and the preset curve is less than the set threshold.

17. The operating method as described in claim 15, characterized in that, include: Determine the pressure boosting requirement of the refrigerant from the outlet of the gradient cooling module to the inlet of the heat release unit, and determine the ideal pressure boosting process line of the refrigerant with the goal of minimizing power consumption; Using the ideal pressure boosting process line as the target line, the pressure boosting process of the refrigerant is made close to the ideal pressure boosting process line by controlling the cooling method, cooling medium, cooling temperature and cooling flow rate of the pressure boosting device.

18. The operating method as described in claim 17, characterized in that, The working fluid of the pressure boosting device is steam, and the steam at the inlet of the pressure boosting device is in a saturated state. The saturated steam line is selected as the ideal pressure boosting process line.

19. The operating method as described in claim 17, characterized in that, The working fluid of the pressurization device is steam. The steam at the inlet of the pressurization device is in a supersaturated state. The steam superheat is set, and the steam pressurization curve with a specific steam superheat is selected as the ideal pressurization process line.

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