Refrigeration heat recovery system for refrigeration house

Abstract

The utility model discloses a refrigeration heat recovery system of a refrigeration house. The refrigeration heat recovery system of the refrigeration house comprises a refrigeration compressor unit, an evaporative condenser, a water defrosting heat recovery heat exchanger, a floor heating heat recovery heat exchanger and a refrigeration house room, and a tail end heat exchanger is arranged in the refrigeration house room. The evaporative condenser, the water defrosting heat recovery heat exchanger and the floor heating heat recovery heat exchanger are communicated with one end of the refrigeration compressor unit in parallel, and the refrigeration house is communicated with the other end of the refrigeration compressor unit through the tail end heat exchanger. The evaporative condenser, the water defrosting heat recovery heat exchanger and the terrace heating heat recovery heat exchanger are communicated with the refrigeration compressor unit in parallel, condensation heat recovery is achieved, the recovered condensation heat is used for water defrosting and terrace heating, the condensation heat recovery utilization rate of the refrigeration storage system is improved, energy consumption of a refrigeration storage is reduced, and the energy consumption of the refrigeration storage system is reduced. And external heat release is reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of cold storage refrigeration heat recovery, in particular to a cold storage refrigeration heat recovery system. Background Art

[0002] At present, the cold storage refrigeration heat recovery system generally adopts the method of connecting a heat recovery device in series between the cold storage host and the condenser to recover part of the condensation heat and produce hot water of a certain temperature for defrosting the cold storage terminal equipment. Although this system can recover the condensation heat of the cold storage system, there are two problems. First, the amount of hot water used for defrosting is very small compared to the heat exhaust of the cold storage refrigeration equipment, and a large amount of condensation heat needs to be discharged to the environment, which is very energy-inefficient. Second, when there is no defrosting, all the exhaust of the refrigeration host must pass through the heat recovery device and then to the condenser, causing resistance loss in the refrigeration system, which affects the energy efficiency of the refrigeration system. Utility Model Content

[0003] The purpose of the utility model is to overcome the deficiencies of the prior art and provide a cold storage refrigeration heat recovery system.

[0004] In order to solve the above technical problems, the present invention adopts the following technical solutions:

[0005] An embodiment of the present utility model provides a cold storage refrigeration heat recovery system, comprising: a refrigeration compressor unit, an evaporative condenser, a water defrost heat recovery heat exchanger, a floor heating heat recovery heat exchanger and a cold storage room, wherein a terminal heat exchanger is provided in the cold storage room, the evaporative condenser, the water defrost heat recovery heat exchanger and the floor heating heat recovery heat exchanger are connected in parallel to one end of the refrigeration compressor unit, and the cold storage room is connected to the other end of the refrigeration compressor unit through the terminal heat exchanger, the refrigeration compressor unit generates high-temperature exhaust gas which flows to the evaporative condenser or the water defrost heat recovery heat exchanger or the floor heating heat recovery heat exchanger to form a reflux liquid, the reflux liquid is cooled and depressurized by the refrigeration compressor unit to form a low-temperature liquid, the low-temperature liquid flows to the terminal heat exchanger for cooling the cold storage room and forming recovered gas, and the recovered gas flows to the refrigeration compressor unit.

[0006] In a specific embodiment, the defrost heat recovery heat exchanger is connected to a defrost water pool, and the defrost heat recovery heat exchanger is used to heat water in the defrost water pool.

[0007] In a specific embodiment, the floor heating heat recovery heat exchanger is connected to the cold storage floor through a heat exchange pipeline, and the floor heating heat recovery heat exchanger is used to heat the cold storage floor.

[0008] In a specific embodiment, a first solenoid valve is further provided between the refrigeration compressor unit and the water defrost heat recovery heat exchanger.

[0009] In a specific embodiment, a second solenoid valve is further provided between the refrigeration compressor unit and the floor heating heat recovery heat exchanger.

[0010] In a specific embodiment, a third solenoid valve and a pressure differential control valve are further provided between the refrigeration compressor unit and the evaporative condenser.

[0011] In a specific embodiment, a first valve and a second valve are respectively provided at both ends of the third solenoid valve+pressure differential control valve.

[0012] In a specific embodiment, a third valve connected in parallel with the first valve and the second valve is further provided between the refrigeration compressor unit and the evaporative condenser.

[0013] In a specific embodiment, a fourth valve, a fifth valve, and a sixth valve are respectively provided between the evaporative condenser, the water defrost heat recovery heat exchanger, the floor heating heat recovery heat exchanger, and the refrigeration compressor unit.

[0014] In a specific embodiment, the number of the terminal heat exchanger is at least one.

[0015] The cold storage refrigeration heat recovery system of the utility model has the following beneficial effects compared with the prior art: the evaporative condenser, the water defrosting heat recovery heat exchanger and the floor heating heat recovery heat exchanger are connected in parallel to the refrigeration compressor unit to realize condensation heat recovery, and the recovered condensation heat is used for water defrosting and floor heating, thereby improving the condensation heat recovery utilization rate of the cold storage system, reducing the energy consumption of the cold storage, and reducing the external heat release.

[0016] The present invention will be further described below with reference to the accompanying drawings and specific embodiments. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the following briefly introduces the drawings required for use in the embodiments or descriptions of the prior art. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative labor.

[0018] Figure 1 This is a block diagram of the cold storage refrigeration heat recovery system provided by the utility model;

[0019] Figure 2 This is a flow chart of the cold storage refrigeration heat recovery control method provided by the utility model.

[0020] Reference numerals:

[0021] Refrigeration compressor unit 10, evaporative condenser 20, water defrost heat recovery heat exchanger 30, floor heating heat recovery heat exchanger 40, cold storage room 50, terminal heat exchanger 60, defrost water pool 70, cold storage floor 80, first solenoid valve 90, second solenoid valve 100, third solenoid valve 110, pressure differential control valve 120, first valve 130, second valve 140, third valve 150, fourth valve 160, fifth valve 170, sixth valve 180. DETAILED DESCRIPTION

[0022] In order to make the purpose, technical solutions and advantages of the present invention more clearly understood, the present invention will be further described in detail below with reference to the accompanying drawings and specific implementation methods.

[0023] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the embodiments described are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without making creative efforts shall fall within the scope of protection of the present invention.

[0024] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise" and the like to indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present invention.

[0025] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of the technical features being referred to. Thus, a feature specified as "first" or "second" may explicitly or implicitly include one or more of such features. In the description of this utility model, "plurality" means two or more, unless otherwise specifically defined.

[0026] In this utility model, unless otherwise specified or limited, the terms "installed," "connected," "connect," "fixed," etc. should be understood in a broad sense. For example, they can refer to connection, detachable connection, or integration; mechanical connection or electrical connection; direct connection or indirect connection through an intermediate medium; internal communication between two components or interaction between two components. For those skilled in the art, the specific meanings of the above terms in this utility model can be understood according to specific circumstances.

[0027] In the present invention, unless otherwise expressly specified or limited, a first feature being "above" or "below" a second feature may include the first and second features being in direct contact, or may include the first and second features being in contact not directly but through another feature between them. Moreover, a first feature being "above," "above," and "above" a second feature may include the first feature being directly above or obliquely above the second feature, or may simply mean that the first feature is higher in level than the second feature. A first feature being "below," "below," and "below" a second feature may include the first feature being directly below or obliquely below the second feature, or may simply mean that the first feature is lower in level than the second feature.

[0028] In the description of this specification, the reference terms "one embodiment", "some embodiments", "example", "specific example", or "some examples" mean that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic expressions of the above terms should not be understood as necessarily referring to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art can combine and combine the different embodiments or examples described in this specification.

[0029] See also Figure 1As shown, the utility model discloses a specific embodiment of a cold storage refrigeration heat recovery system, comprising: a refrigeration compressor unit 10, an evaporative condenser 20, a water defrosting heat recovery heat exchanger 30, a floor heating heat recovery heat exchanger 40 and a cold storage room 50, wherein a terminal heat exchanger 60 is provided in the cold storage room 50, the evaporative condenser 20, the water defrosting heat recovery heat exchanger 30 and the floor heating heat recovery heat exchanger 40 are connected in parallel to one end of the refrigeration compressor unit 10, and the cold storage room 50 is connected to the cold storage room 50 through the terminal heat exchanger 60. The device 60 is connected to the other end of the refrigeration compressor unit 10. The refrigeration compressor unit 10 generates high-temperature exhaust gas which flows to the evaporative condenser 20 or the water defrosting heat recovery heat exchanger 30 or the floor heating heat recovery heat exchanger 40 to form a reflux liquid. The reflux liquid is cooled and depressurized by the refrigeration compressor unit 10 to form a low-temperature liquid. The low-temperature liquid flows to the terminal heat exchanger 60 for cooling the cold storage room 50 and forming a recovered gas. The recovered gas flows to the refrigeration compressor unit 10.

[0030] Specifically, by connecting the evaporative condenser 20, the water defrost heat recovery heat exchanger 30, and the floor heating heat recovery heat exchanger 40 in parallel with the refrigeration compressor unit 10, condensation heat recovery is achieved. The recovered condensation heat is used for defrosting and floor heating, thereby improving the cold storage system's condensation heat recovery efficiency, reducing the cold storage's energy consumption, and minimizing external heat release. Furthermore, in conventional cold storage refrigeration systems, the heat generated during the condensation process is often directly discharged into the environment, resulting in energy waste. However, by connecting the evaporative condenser 20, the water defrost heat recovery heat exchanger 30, and the floor heating heat recovery heat exchanger 40 in parallel, the high-temperature exhaust gas generated by the refrigeration compressor unit 10 can be directed to any of these three components as needed, thereby recovering and utilizing the condensation heat. Furthermore, by recovering condensation heat, the system can reduce its demand for new thermal energy. For example, in winter or cold weather, the recovered heat can be used to heat the floor, reducing reliance on external heating systems. Furthermore, the water defrost heat recovery heat exchanger 30 can also utilize the recovered heat for defrosting operations, further reducing energy consumption. In addition, since the evaporative condenser 20, the water defrost heat recovery heat exchanger 30 and the floor heating heat recovery heat exchanger 40 are connected in parallel, the system can flexibly choose which heat exchanger to use according to actual needs; for example: when the floor needs to be heated, the floor heating heat recovery heat exchanger 40 can be used first; when defrosting is required, the water defrost heat recovery heat exchanger 30 can be used first.

[0031] More specifically, the number of the terminal heat exchangers 60 is one or more, and the specific number can be set according to actual needs, which will not be elaborated in detail here.

[0032] In one embodiment, the defrost heat recovery heat exchanger 30 is connected to a defrost water pool 70 , and the defrost heat recovery heat exchanger 30 is used to heat water in the defrost water pool 70 .

[0033] Specifically, during the refrigeration process of the cold storage, the high-temperature exhaust gas generated by the compressor is usually discharged into the environment, resulting in energy waste. However, through the water defrosting heat recovery heat exchanger 30, the heat energy in this part of the high-temperature exhaust gas is recovered and used to heat the water in the defrosting water pool 70. This not only reduces energy waste, but also improves the overall energy efficiency of the system. In addition, using the recovered heat energy to heat the water in the defrosting water pool 70 can significantly reduce dependence on traditional energy sources, such as electricity or gas, which helps to reduce the operating costs of the cold storage, while reducing carbon emissions and promoting environmental protection. In addition, by heating the water in the defrosting water pool 70 through the water defrosting heat recovery heat exchanger 30, precise control of the water temperature can be achieved, which helps to maintain the temperature stability in the cold storage room 50 and improve the quality and safety of the stored items. In addition, this technology reduces the impact and wear of traditional defrosting methods on refrigeration equipment, improves the reliability and stability of the system, which helps to reduce equipment failure rates, reduce maintenance costs, and improve the overall operating efficiency of the cold storage.

[0034] In one embodiment, the floor heating heat recovery heat exchanger 40 is connected to the cold storage floor 80 through a heat exchange pipeline, and the floor heating heat recovery heat exchanger 40 is used to heat the cold storage floor 80.

[0035] Specifically, the floor heating heat recovery heat exchanger 40 utilizes the waste heat generated during the refrigeration process for heating, thereby realizing the reuse of energy. This not only reduces energy waste, but also reduces dependence on traditional energy sources, contributing to energy conservation, emission reduction and environmental protection. The internal temperature of the cold storage room 50 is usually relatively low. In a low-temperature environment, the floor is prone to frost heave. The floor heating heat recovery heat exchanger 40 utilizes the waste heat generated during the refrigeration process and transfers heat to the cold storage floor 80 through heat exchange, thereby increasing the temperature of the floor, thereby effectively preventing the floor from frost heave and maintaining the flatness and stability of the floor. In addition, in a low-temperature and high-humidity environment, the cold storage floor 80 is prone to condensation, causing the goods to become damp, moldy or deteriorate. The floor heating heat recovery heat exchanger 40 heats the floor to increase the ambient temperature inside the cold storage room 50 and reduce the relative humidity, thereby effectively preventing the occurrence of condensation and keeping the goods dry and clean. In addition, the floor heating heat recovery heat exchanger 40 can adjust the floor temperature as needed to maintain the stability of the temperature inside the cold storage room 50, which helps to reduce the impact of temperature fluctuations on the goods and improve the storage quality and safety of the goods. In addition, by heating the floor, the ambient temperature inside the cold storage room 50 is increased, the operating time of the cold storage equipment is reduced, and thus energy consumption is reduced, which is of great significance for reducing the operating costs of the cold storage and improving the economic benefits.

[0036] In one embodiment, a first solenoid valve 90 is further provided between the refrigeration compressor unit 10 and the water defrost heat recovery heat exchanger 30 .

[0037] Specifically, the first solenoid valve 90 automatically opens or closes based on the operating status of the refrigeration compressor unit 10 and the needs of the defrost heat recovery heat exchanger 30. This intelligent regulation ensures efficient and accurate heat recovery. Furthermore, when the refrigeration compressor unit 10 is operating, the high-temperature exhaust gas generated can flow through the open first solenoid valve 90 into the defrost heat recovery heat exchanger 30, transferring heat energy to the defrost water pool 70. When heat recovery is no longer needed or the temperature of the defrost water pool 70 has reached a preset value, the first solenoid valve 90 automatically closes, preventing excessive heat energy from entering the defrost water pool 70 and wasting energy. In addition, the automatic control of the first solenoid valve 90 can prevent the water defrost heat recovery heat exchanger 30 from overheating, thereby protecting the equipment from damage. When the temperature of the defrost water pool 70 is too high, the first solenoid valve 90 will automatically close, cutting off the inflow of high-temperature exhaust gas, ensuring the safe operation of the system. The automatic control of the first solenoid valve 90 can also prevent the refrigeration compressor unit 10 from operating under abnormal conditions. For example, when the water defrost heat recovery heat exchanger 30 fails, the solenoid valve will close to prevent the high-temperature exhaust gas from continuing to flow in, thereby protecting the normal operation of the compressor unit. In addition, through the precise control of the first solenoid valve 90, efficient recovery and utilization of thermal energy is achieved, reducing energy waste, which helps to reduce the operating costs of the cold storage, while reducing carbon emissions and promoting environmental protection. In addition, because the first solenoid valve 90 can intelligently adjust the recovery of thermal energy, the energy consumption of the system can be adjusted according to actual needs, which helps to reduce the overall energy consumption of the system and improve energy utilization efficiency.

[0038] In one embodiment, a second solenoid valve 100 is further provided between the refrigeration compressor unit 10 and the floor heating heat recovery heat exchanger 40 .

[0039] Specifically, the second solenoid valve 100 can precisely control the flow of high-temperature exhaust gas generated by the refrigeration compressor unit 10 to the floor heating heat recovery heat exchanger 40. When the refrigeration compressor unit 10 is running, the high-temperature exhaust gas can flow into the floor heating heat recovery heat exchanger 40 through the open second solenoid valve 100, transferring heat energy to the cold storage floor 80. This precise control ensures the efficiency and accuracy of heat energy recovery and avoids energy waste. In addition, through the adjustment of the second solenoid valve 100, it is possible to precisely control the heat input to the floor heating heat recovery heat exchanger 40, thereby maintaining the temperature stability of the cold storage floor 80. This helps to reduce the impact of temperature fluctuations on the internal environment of the cold storage room 50 and improve the quality and safety of stored items. In addition, the second solenoid valve 100 also serves as a protection system. When the floor heating heat recovery heat exchanger 40 fails or the temperature is too high, the second solenoid valve 100 will automatically close, cutting off the flow of high-temperature exhaust gas and preventing damage to the equipment. This helps to extend the service life of the equipment and reduce maintenance costs. In addition, automatic control of the second solenoid valve 100 prevents overheating of the floor heating heat recovery heat exchanger 40, thereby avoiding potential safety hazards and ensuring that the system operates under safe and stable conditions. Furthermore, precise control of the second solenoid valve 100 enables efficient recovery and utilization of thermal energy, which helps reduce the operating costs of the cold storage while also reducing carbon emissions and promoting environmental protection. Furthermore, based on the needs of floor heating, the second solenoid valve 100 can intelligently adjust the system's energy consumption. When the floor temperature reaches a preset value, the solenoid valve automatically closes, reducing unnecessary energy consumption. This intelligent regulation helps improve energy efficiency and reduce overall energy consumption. Furthermore, precise control of the second solenoid valve 100 enables the floor heating heat recovery heat exchanger 40 to operate under more suitable conditions, improving equipment utilization and performance. Furthermore, by precisely controlling the operation of the floor heating heat recovery heat exchanger 40, downtime caused by equipment failure or maintenance can be reduced, which helps improve the overall operational efficiency of the cold storage and ensure the continuity and stability of stored items.

[0040] In one embodiment, a third solenoid valve 110 and a pressure difference control valve 120 are further provided between the refrigeration compressor unit 10 and the evaporative condenser 20 .

[0041] Specifically, when it is detected that the first solenoid valve 90 and the second solenoid valve 100 are closed at the same time, the third solenoid valve 110 is opened to allow all high-temperature exhaust gas to pass through the evaporative condenser 20 for heat dissipation; when any one of the first solenoid valve 90 and the second solenoid valve 100 is in the open state, the third solenoid valve 110 will be in the closed state, and the airflow of the high-temperature exhaust gas is adjusted by the setting value of the pressure difference control valve 120 to adjust the heat recovery amount. The pressure difference of the pressure difference control valve 120 is adjustable within the range of 0-c. When designing the system, the pressure drops of the three heat exchangers, the evaporative condenser 20, the water defrosting heat recovery heat exchanger 30, and the floor heating heat recovery heat exchanger 40, are fully calculated. At the same time, the value of c is adjusted in time according to on-site debugging to ensure that the exhaust gas flow passes through the heat recovery heat exchanger first, and the excess heat is dissipated through the evaporative condenser 20 for heat dissipation.

[0042] That is to say, when the first solenoid valve 90 and the second solenoid valve 100 are closed at the same time, it means that the water defrosting heat recovery heat exchanger 30 and the floor heating heat recovery heat exchanger 40 do not require additional heat energy. At this time, the third solenoid valve 110 is opened, and all high-temperature exhaust gas will directly pass through the evaporative condenser 20 for heat dissipation. However, in actual operation, since the first solenoid valve 90 and the second solenoid valve 100 are usually not completely closed at the same time (because there may be a need for heat recovery), this scenario is more of a backup or special situation processing mechanism. Under normal circumstances, when any one of the first solenoid valve 90 and the second solenoid valve 100 is in the open state, it indicates that at least one heat recovery heat exchanger requires heat energy. At this time, the third solenoid valve 110 is closed, and the airflow of the high-temperature exhaust gas is adjusted by the pressure differential control valve 120 to adjust the heat recovery amount. This design ensures the maximization of heat energy recovery and reduces unnecessary heat energy waste. In addition, the pressure differential control valve 120 can adjust the flow rate of high-temperature exhaust gas according to the set pressure differential range (0-c), thereby accurately controlling the heat recovery amount. When designing the system, the pressure drops of the three heat exchangers, namely the evaporative condenser 20, the water defrosting heat recovery heat exchanger 30, and the floor heating heat recovery heat exchanger 40, have been fully calculated, and the value of c has been adjusted in time according to the on-site debugging conditions. This precise adjustment ensures that the exhaust airflow can first recover heat energy through the heat recovery heat exchanger, while the excess heat is dissipated through the evaporative condenser 20.

[0043] More specifically, the coordinated control of the third solenoid valve 110 and the differential pressure control valve 120 effectively prevents the refrigeration compressor unit 10 from overheating due to the inability to dissipate the high-temperature exhaust gas in a timely manner. When the heat recovery heat exchanger requires heat energy, the third solenoid valve 110 closes, ensuring that the high-temperature exhaust gas passes through the heat recovery heat exchanger first. When the heat recovery demand decreases or disappears, the third solenoid valve 110 opens, and all high-temperature exhaust gas is dissipated through the evaporative condenser 20. This design ensures that the system maintains a stable operating state under all circumstances. Furthermore, precise adjustment of the differential pressure control valve 120 can prevent damage to the system due to excessively high or low pressure. By setting an appropriate differential pressure range, the internal pressure of the system can be maintained within a safe range, thereby protecting the various components of the system from damage. Furthermore, the coordinated control of the third solenoid valve 110 and the differential pressure control valve 120 achieves efficient recovery and utilization of heat energy. This design reduces energy waste and lowers the operating costs of the cold storage, while also helping to reduce carbon emissions and promote environmental protection. Based on changes in heat recovery requirements and system status, the third solenoid valve 110 and the pressure differential control valve 120 intelligently adjust the system's energy consumption. This intelligent regulation helps improve energy efficiency and reduce overall energy consumption. Furthermore, through the coordinated control of the third solenoid valve 110 and the pressure differential control valve 120, the system can flexibly respond to different operating conditions and requirements. Whether in high-temperature and high-humidity environments or low-temperature and low-humidity environments, the system can intelligently adjust to actual needs, ensuring system stability and efficiency.

[0044] More specifically, during the system design phase, it is first necessary to calculate the pressure drops of the three heat exchangers, namely the evaporative condenser 20, the water defrosting heat recovery heat exchanger 30, and the floor heating heat recovery heat exchanger 40. This is usually accomplished by using a heat exchanger pressure drop calculation formula (such as the Darcy-Weiserbach formula), which takes into account factors such as pipe length, diameter, medium flow rate, friction coefficient, and medium density. Through these calculations, the pressure drop value of each heat exchanger under different operating conditions can be obtained, providing basic data for the subsequent setting of the differential pressure control valve 120. After calculating the pressure drop of each heat exchanger, it is necessary to comprehensively consider the pressure drop balance of the entire system, which includes determining the pressure drop of the pipeline between the outlet of the refrigeration compressor unit 10 and each heat exchanger, as well as the pressure drop of the connecting pipeline between each heat exchanger. By balancing these pressure drops, it is possible to ensure that the pressure distribution within the system is reasonable and avoid damage to the system caused by excessively high or low local pressure. During the system design phase, it is also necessary to determine the set value c of the pressure differential control valve 120 based on the calculated pressure drop values ​​of each heat exchanger and the pressure distribution within the system. This set value c should be able to ensure that when the high-temperature exhaust gas flow passes through the heat recovery heat exchanger, the heat recovery demand can be met first, while ensuring that excess heat can be dissipated through the evaporative condenser 20.

[0045] After the system is installed, preliminary commissioning is required. This includes checking the installation of various components, the tightness of connecting pipes, and the initial setting of the differential pressure control valve 120. During this initial commissioning process, the set value c of the differential pressure control valve 120 can be manually adjusted to observe pressure changes within the system, the heat recovery efficiency of each heat exchanger, and the heat dissipation efficiency of the evaporative condenser 20. Based on the results of the initial commissioning, the set value c of the differential pressure control valve 120 can be optimized. This includes adjusting the set value c based on actual site conditions to ensure that the system maintains stable operation under different operating conditions. Optimization also needs to consider factors such as the system's energy efficiency ratio, heat recovery efficiency, and operating costs to achieve optimal overall system performance. During system operation, the inlet and outlet pressures of each heat exchanger and the actual operating status of the differential pressure control valve 120 need to be monitored in real time. If the pressure distribution within the system is found to be unreasonable or the heat recovery effect is unsatisfactory, the set value c of the differential pressure control valve 120 can be adjusted promptly to ensure system stability and efficiency.

[0046] In one embodiment, a first valve 130 and a second valve 140 are respectively provided at both ends of the third solenoid valve 110 + the pressure difference control valve 120 .

[0047] Specifically, when a fault occurs in the third solenoid valve 110 and the pressure differential control valve 120, closing the first valve 130 and the second valve 140 allows for maintenance of the third solenoid valve 110 and the pressure differential control valve 120, quickly isolating the faulty area from the entire system. This prevents the faulty component from interfering with and impacting the rest of the system, ensuring the normal operation of the remaining system. After isolating the faulty area, technicians can safely and conveniently perform maintenance on the third solenoid valve 110 and the pressure differential control valve 120 without shutting down the entire system or performing extensive disassembly, thereby reducing the difficulty and time cost of maintenance. Furthermore, by promptly closing the first valve 130 and the second valve 140, the fault condition of the faulty component can be effectively prevented from spreading to the entire system, thereby avoiding serious consequences such as system downtime, equipment damage, or safety accidents caused by the spread of the fault. Furthermore, by keeping the first valve 130 and the second valve 140 closed during fault isolation and maintenance, the stability and reliability of the remaining system can be ensured, helping to maintain the normal operation of the system and minimizing the impact on production or operations.

[0048] In one embodiment, a third valve 150 connected in parallel to the first valve 130 and the second valve 140 is further provided between the refrigeration compressor unit 10 and the evaporative condenser 20 .

[0049] Specifically, when the third solenoid valve 110 + the pressure differential control valve 120 fails, the first valve 130 and the second valve 140 are closed, the third valve 150 is opened, and the system operates normally. The third solenoid valve 110 + the pressure differential control valve 120 can also be inspected and repaired. That is to say, in the cold storage refrigeration heat recovery system, when a third valve 150 is connected in parallel between the refrigeration compressor unit 10 and the evaporative condenser 20 in addition to the third solenoid valve 110 + the pressure differential control valve 120 combination, this design brings additional flexibility and reliability. When the third solenoid valve 110 or the pressure differential control valve 120 fails, by closing the first valve 130 and the second valve 140, the faulty component can be quickly isolated from the rest of the system. At the same time, the third valve 150 is opened as a bypass channel to allow the system to continue operating, thereby avoiding the entire system shutdown caused by the failure of a single component. After isolating the fault, technicians can safely and conveniently perform maintenance on the third solenoid valve 110 and the pressure differential control valve 120. Because the system continues to operate through the third valve 150, the maintenance work will not interfere with or impact the operation of the entire system. Furthermore, by opening the third valve 150 as a bypass channel, the system can continue to operate during a failure of the third solenoid valve 110 or the pressure differential control valve 120. This helps maintain system continuity and stability and reduces the impact on production or operations. This design improves the overall reliability of the system. Even if a key component fails, the system can continue to operate through the bypass channel, thereby reducing the risk of downtime caused by the failure.

[0050] In one embodiment, a fourth valve 160 , a fifth valve 170 , and a sixth valve 180 are respectively provided between the evaporative condenser 20 , the water defrosting heat recovery heat exchanger 30 , the floor heating heat recovery heat exchanger 40 and the refrigeration compressor unit 10 .

[0051] Specifically, during normal operation, the first valve 130, the second valve 140, the fourth valve 160, the fifth valve 170 and the sixth valve 180 are in a fully open state, and the third valve 150 is in a closed state. When the third solenoid valve 110 + the pressure differential control valve 120 fails, the first valve 130 and the second valve 140 are closed, and the third valve 150 is opened. The system operates normally, and the third solenoid valve 110 + the pressure differential control valve 120 is repaired; when the water defrost heat recovery heat exchanger 30 or the floor heating heat recovery heat exchanger 40 or the evaporative condenser 20 needs to be repaired, the solenoid valve or valve in front of the corresponding equipment is closed for maintenance.

[0052] That is, when the system is operating normally, the first valve 130, the second valve 140, the fourth valve 160, the fifth valve 170, and the sixth valve 180 are all in the fully open state, which ensures the smooth flow of refrigerant (i.e., coolant) in the system while achieving efficient heat recovery and heat dissipation management. At this time, the third valve 150 is in the closed state, avoiding unnecessary bypass flow, thereby ensuring the stability and efficiency of the system. When the third solenoid valve 110 or the pressure differential control valve 120 fails, by closing the first valve 130 and the second valve 140, the faulty area can be quickly isolated from the entire system. At the same time, opening the third valve 150 as a bypass channel allows the system to continue operating, thereby avoiding the entire system shutdown caused by the failure of a single component. During this period, technicians can safely and conveniently inspect and repair the third solenoid valve 110 and the pressure differential control valve 120. When the water defrost heat recovery exchanger 30, the floor heating heat recovery exchanger 40, or the evaporative condenser 20 requires maintenance, simply close the solenoid valve or valve in front of the corresponding device (i.e., the fourth valve 160, the fifth valve 170, or the sixth valve 180). This ensures the safety and convenience of maintenance work while avoiding interference and impact on the entire system. Furthermore, by controlling the on / off status of each valve, technicians can flexibly adjust the system configuration according to actual conditions, which helps achieve more efficient heat recovery and heat dissipation management, thereby improving the overall performance and energy efficiency of the system.

[0053] Specifically, the refrigeration compressor unit 10, the evaporative condenser 20, the water defrosting heat recovery heat exchanger 30 and the floor heating heat recovery heat exchanger 40 all adopt existing public technologies, which will not be elaborated in detail here.

[0054] See also Figure 2 As shown, the embodiment of the present invention provides a cold storage refrigeration heat recovery control method, comprising the following steps:

[0055] S1, collect the temperature of the defrosting pool 70 and the cold storage floor 80 respectively to obtain T 水池 and T 地坪 ;

[0056] Specifically, a first temperature probe is set in the defrosting pool 70, and the value T of the first temperature probe is collected. 水池 , set a second temperature probe in the heating layer of the cold storage (i.e. the cold storage floor 80), and collect the value T of the second temperature probe 地坪 , respectively, to monitor the defrost pool 70 and the underground heating layer in real time.

[0057] S2, read the set T 冲霜目标 and T 地坪目标 , and compare T 水池 With T 冲霜目标 , and T地坪 With T 地坪目标 size;

[0058] Specifically, by reading the preset defrost water temperature control value T 冲霜目标 And floor heating temperature control value T 地坪目标 , and then determine the subsequent working mode by comparing the sizes.

[0059] S3, when T 水池 <T 冲霜目标 When T 水池 ≥T 冲霜目标 +a, close the first solenoid valve 90; when T 地坪 <T 地坪目标 When T 地坪 ≥T 地坪目标 When +b, the second solenoid valve 100 is closed;

[0060] Specifically, when T 水池 <T 冲霜目标 When T 水池 ≥T 冲霜目标 +a, close the first electromagnetic valve 90 and the circulating water pump of the water defrosting heat recovery heat exchanger 30. 地坪 <T 地坪目标 When T 地坪 ≥T 地坪目标 When the voltage is +b, the second electromagnetic valve 100 is closed, and the circulating water pump of the floor heating heat recovery heat exchanger 40 is turned off.

[0061] S4 , if the first solenoid valve 90 and the second solenoid valve 100 are closed at the same time, the third solenoid valve 110 is opened, and the high-temperature exhaust gas is cooled through the evaporative condenser 20 .

[0062] Specifically, when it is detected that the first solenoid valve 90 and the second solenoid valve 100 are closed at the same time, the third solenoid valve 110 is opened to allow all high-temperature exhaust gas to pass through the evaporative condenser 20 for heat dissipation; when any one of the first solenoid valve 90 and the second solenoid valve 100 is in the open state, the third solenoid valve 110 will be in the closed state, and the airflow of the high-temperature exhaust gas is adjusted by the setting value of the pressure difference control valve 120 to adjust the heat recovery amount. The pressure difference of the pressure difference control valve 120 is adjustable within the range of 0-c to ensure that the exhaust gas flow passes through the heat recovery heat exchanger first, and the excess heat is dissipated through the evaporative condenser 20 for heat dissipation.

[0063] More specifically, T冲霜目标 is the target control value of the defrost water temperature. The defrost water temperature of each refrigeration system is different and can be set through the touch screen. a is the defrost water temperature control accuracy constant. The value of each refrigeration system is different and can be set through the touch screen.

[0064] T 地坪目标 The target temperature of the floor heating layer is usually controlled at 1-2°C. This value can be set through the touch screen. b is the temperature control accuracy constant of the floor heating layer. The value is different for each cooling system and can be set through the touch screen.

[0065] c is the pressure drop range of the pressure differential control valve 120. This value varies for different types of valves from different manufacturers. This value also varies for different refrigeration systems and needs to be adjusted and set according to the needs of on-site commissioning.

[0066] The cold storage refrigeration heat recovery control method collects the actual temperature (T 水池 and T 地坪 ) and the preset target temperature (T 冲霜目标 and T 地坪目标 ) is compared, and it can automatically determine when the first solenoid valve 90 and the second solenoid valve 100 need to be opened or closed. When the temperature of the defrost water pool 70 or the cold storage floor 80 is lower than the target temperature, the first solenoid valve 90 or the second solenoid valve 100 is opened respectively, and the high-temperature exhaust gas generated by the refrigeration compressor unit 10 is used to heat the defrost water pool 70 or the cold storage floor 80; when the first solenoid valve 90 and the second solenoid valve 100 are closed at the same time, that is, when the temperatures of the defrost water pool 70 and the cold storage floor 80 reach or exceed the target temperature, the third solenoid valve 110 is automatically opened, and the high-temperature exhaust gas is dissipated through the evaporative condenser 20, that is, the automatic control method is adopted to realize energy recovery on demand, and realize automatic switching and stable operation between the heat recovery device and the condenser.

[0067] The above embodiments are preferred implementation schemes of the present invention. In addition, the present invention can also be implemented in other ways. Any obvious replacement without departing from the concept of the present technical solution is within the scope of protection of the present invention.

Claims

1. A cold storage refrigeration heat recovery system, characterized in that: include: A refrigeration compressor unit, an evaporative condenser, a water defrost heat recovery heat exchanger, a floor heating heat recovery heat exchanger and a cold storage room. A terminal heat exchanger is provided in the cold storage room. The evaporative condenser, the water defrost heat recovery heat exchanger and the floor heating heat recovery heat exchanger are connected in parallel to one end of the refrigeration compressor unit. The cold storage room is connected to the other end of the refrigeration compressor unit through the terminal heat exchanger. The refrigeration compressor unit generates high-temperature exhaust gas which flows to the evaporative condenser or the water defrost heat recovery heat exchanger or the floor heating heat recovery heat exchanger to form a reflux liquid. The reflux liquid is cooled and depressurized by the refrigeration compressor unit to form a low-temperature liquid. The low-temperature liquid flows to the terminal heat exchanger for cooling the cold storage room and forming recovered gas. The recovered gas flows to the refrigeration compressor unit.

2. The cold storage refrigeration heat recovery system according to claim 1, characterized in that: The water defrost heat recovery heat exchanger is connected to a defrost water pool, and the water defrost heat recovery heat exchanger is used to heat the water in the defrost water pool.

3. The cold storage refrigeration heat recovery system according to claim 1, characterized in that: The floor heating heat recovery heat exchanger is connected to the cold storage floor through a heat exchange pipeline, and the floor heating heat recovery heat exchanger is used to heat the cold storage floor.

4. The cold storage refrigeration heat recovery system according to claim 1, characterized in that: A first solenoid valve is further provided between the refrigeration compressor unit and the water defrost heat recovery heat exchanger.

5. The cold storage refrigeration heat recovery system according to claim 1, characterized in that: A second solenoid valve is also provided between the refrigeration compressor unit and the floor heating heat recovery heat exchanger.

6. The cold storage refrigeration heat recovery system according to claim 1, characterized in that: A third solenoid valve and a pressure difference control valve are further provided between the refrigeration compressor unit and the evaporative condenser.

7. The cold storage refrigeration heat recovery system according to claim 6, characterized in that: The first valve and the second valve are respectively provided at both ends of the third solenoid valve+pressure differential control valve.

8. The cold storage refrigeration heat recovery system according to claim 7, characterized in that: A third valve connected in parallel to the first valve and the second valve is further provided between the refrigeration compressor unit and the evaporative condenser.

9. The cold storage refrigeration heat recovery system according to claim 1, characterized in that: A fourth valve, a fifth valve and a sixth valve are respectively provided between the evaporative condenser, the water defrosting heat recovery heat exchanger and the floor heating heat recovery heat exchanger and the refrigeration compressor unit.

10. The cold storage refrigeration heat recovery system according to claim 1, characterized in that: The number of the terminal heat exchanger is at least one.

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