A seawater source heat pump system and control method utilizing waste cooling and waste heat.

Abstract

This invention belongs to the field of energy-related technology, and in particular relates to a seawater source heat pump system and control method that utilizes waste cooling and waste heat. By dynamically allocating the waste cooling of LNG stations, waste heat of thermal power plants, and the cold and heat resources of seawater, the system prioritizes the energy needs of condensers and vaporizers, improves the power generation efficiency of thermal power plants, reduces the primary energy consumption of LNG, and uses seawater to supplement cooling or heating when waste cooling or heat is insufficient, ensuring the continuous and stable energy supply process and the balance between supply and demand. The system has strong adaptability and high operational reliability.

Description

Technical Field

[0001] This invention belongs to the field of energy-related technology, and in particular relates to a seawater source heat pump system and control method that utilizes waste cooling and waste heat. Background Technology

[0002] The statements in this section are merely background information related to the present invention and do not necessarily constitute prior art.

[0003] During operation, LNG stations (liquefied natural gas stations) and thermal power plants generate a large amount of waste cooling and waste heat resources. The waste cooling generated during the LNG vaporization process and the waste heat discharged from the steam turbine of the thermal power plant can be rationally recovered and utilized through recovery devices. This can replace traditional energy-driven refrigeration and heating methods, reduce energy waste and carbon emissions, and has a very wide range of applications and great value.

[0004] Currently, the waste cooling and waste heat technologies of LNG terminals and power plants have been widely used due to their high efficiency and energy saving. However, in actual operation, the load fluctuations of LNG terminals and power plants will cause fluctuations in the amount of waste cooling and waste heat generated. In addition, the cooling and heating load demands of users will also change with the seasonal changes. Both of these factors restrict the overall level of recycling and utilization of waste cooling and waste heat resources of LNG terminals and power plants.

[0005] Therefore, achieving precise matching and efficient synergistic utilization of waste cooling resources from LNG terminals and waste heat resources from power plants with users' cooling and heating needs, ensuring the stable and efficient operation of the entire system, and promoting the cascade utilization of energy from LNG terminals and power plants are urgent problems that need to be solved. Summary of the Invention

[0006] To overcome the shortcomings of the prior art, the present invention provides a seawater source heat pump system and control method that utilizes waste cooling and waste heat, transforming energy that might otherwise be discarded or discharged into a stable and reliable cold and heat source, thereby achieving efficient and cyclical energy utilization.

[0007] To achieve the above objectives, the present invention adopts the following technical solution:

[0008] In a first aspect, the present invention provides a seawater source heat pump system that utilizes waste cooling and waste heat, comprising: a vaporizer, a steam turbine, a condenser, and a heat exchanger;

[0009] The vaporizer is used to convert liquefied natural gas into gaseous natural gas and output cooling capacity to provide cooling capacity for the seawater source heat pump in summer and the condenser.

[0010] The steam turbine is connected to the condenser via a pipeline and serves as the main heat source during the winter heating season.

[0011] The condenser is connected to the heat exchanger and the heat pump unit through a circulation pipeline, and is used to recover the waste heat of the turbine exhaust steam and convert it into a heat transfer fluid.

[0012] One side of the heat exchanger is connected to the vaporizer or the condenser, and the other side is connected to the seawater source and the heat pump unit. In summer, it serves as an exchanger for the waste cooling of liquefied natural gas and the cold source of seawater, and in winter, it serves as an enhancer for the waste heat of the condenser and the heat of the seawater.

[0013] Secondly, the present invention provides a control method for a seawater source heat pump system utilizing waste cooling and waste heat, comprising:

[0014] Determine whether the waste heat from the turbine exhaust meets the heat load requirements of the user and the liquefied natural gas vaporization.

[0015] If the conditions are met, the valve is switched to transfer the waste heat from the thermal power plant to the gasifier as a gasification heat source, and at the same time transfer it to the circulating water through the heat exchanger. The circulating water is then transported to the user side after passing through the heat pump unit.

[0016] If the requirements are not met, the valve opening will be dynamically adjusted to prioritize heating the vaporizer, and the seawater source heat pump will be started to extract heat from the seawater to compensate for the heat load gap in conjunction with the remaining waste heat.

[0017] Thirdly, the present invention provides a control method for a seawater source heat pump system utilizing waste cooling and waste heat, comprising:

[0018] Determine whether the cooling capacity generated by liquefied natural gas vaporization meets the cooling load requirements of the power plant condenser and users;

[0019] If the conditions are met, the cold energy generated by the vaporization of liquefied natural gas is transferred to the condenser through valve control, and then transferred to the circulating refrigerant through the heat exchanger. The cold energy is then transferred to the heat pump unit through the circulating refrigerant to provide cooling services to the user side.

[0020] If this cannot be achieved, the valve opening is dynamically adjusted to prioritize cooling the condenser of the thermal power plant, and the seawater transfer pump is turned on to draw low-temperature seawater to replenish the circulating refrigerant and meet the cooling needs of the user side.

[0021] The above one or more technical solutions have the following beneficial effects:

[0022] In this invention, by dynamically allocating the waste cooling of LNG stations, the waste heat of thermal power plants, and the cold and heat resources of seawater, priority is given to ensuring the energy needs of the condenser and gasifier, improving the power generation efficiency of thermal power plants, reducing the primary energy consumption of LNG, and using seawater to supplement the cold or heat when the waste cooling or heat is insufficient, the continuous and stable energy supply process and the supply and demand balance are ensured. The system has strong adaptability and high operational reliability.

[0023] In this invention, seawater is used as the system's "natural energy battery" and ultimate guarantee. When the cooling or heating is insufficient, the cooling or heating is extracted from the seawater through seawater source heat pump technology to supplement it, ensuring the continuity and stability of energy supply and resulting in outstanding environmental benefits.

[0024] In this invention, a large amount of waste cooling generated during LNG gasification, waste heat emitted from steam turbines in thermal power plants, and vast seawater resources are integrated into a single system. Through system design and control strategies, these energy sources that might otherwise be discarded or emitted are transformed into stable and reliable cold and heat sources, achieving efficient and cyclical energy utilization.

[0025] Advantages of additional aspects of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0026] The accompanying drawings, which form part of this invention, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an improper limitation of the invention.

[0027] Figure 1 This is a block diagram of the seawater source heat pump system in Embodiment 1 of the present invention;

[0028] Figure 2 This is a control flowchart of the seawater source heat pump system in Embodiment 1 of the present invention. Detailed Implementation

[0029] It should be noted that the following detailed descriptions are exemplary and intended to provide further illustration of the invention. Unless otherwise specified, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains.

[0030] It should be noted that the terminology used herein is for the purpose of describing particular implementations only and is not intended to limit the exemplary implementations of the present invention.

[0031] Where there is no conflict, the embodiments and features in the embodiments of the present invention can be combined with each other.

[0032] Example 1

[0033] This embodiment discloses a seawater source heat pump system that utilizes waste cooling and waste heat, including: a vaporizer, a steam turbine, a condenser, and a heat exchanger;

[0034] As one of the core pieces of equipment in a liquefied natural gas (LNG) station, the vaporizer is connected to the LNG storage unit and heat exchanger via pipelines. It can convert LNG into gaseous natural gas. In this process, while meeting the natural gas supply demand, it also outputs a large amount of cooling capacity to the seawater source heat pump system. It is the core cold source for providing cooling capacity for the seawater source heat pump system in summer and for the condenser of the thermal power plant.

[0035] As the core of energy conversion in a thermal power plant, the steam turbine's exhaust end is connected to the condenser through pipelines. It is the stable and main heat source for the seawater source heat pump system in winter heating mode, and is the core heat source on the heating side of the seawater source heat pump system, realizing the recovery and utilization of waste heat from the thermal power plant.

[0036] The condenser serves as a condensation device for the exhaust steam from the steam turbine and also as a waste heat collection device for the seawater source heat pump system. It is connected to the heat exchanger and heat pump unit through a circulation pipeline to convert the exhaust steam waste heat from the steam turbine into a usable heat transfer fluid, thus completing the recovery of waste heat from the thermal power plant.

[0037] The heat exchanger is a key component in the seawater source heat pump system, facilitating the exchange of waste cooling and heat with seawater energy. One side of the pipe connects to the vaporizer or condenser, while the other side connects to the seawater source and the heat pump unit. In summer cooling mode, the heat exchanger acts as a cold energy exchanger between liquefied natural gas waste cooling and seawater; in winter heating mode, it acts as a heat enhancer between condenser waste heat and seawater, ensuring the high efficiency and stability of energy exchange in the seawater source heat pump system.

[0038] As an alternative implementation, the heat exchanger can be made of PPR or PERT material, which has the characteristic of being resistant to seawater corrosion.

[0039] In one specific implementation, the medium outlet pipeline of the liquefied natural gas storage unit is directly connected to the medium inlet of the vaporizer, and the medium outlet end of the vaporizer is connected to the natural gas pipeline network (NG pipeline) to realize the conversion of liquefied natural gas into gaseous natural gas; a temperature sensor T1 and a mass flow meter m1 are installed on the cold energy output pipeline of the vaporizer, and a temperature sensor T1 is installed on the cold energy inlet and outlet pipelines of the vaporizer to monitor the medium temperature and flow rate in the LNG vaporization process in real time.

[0040] The cold energy output end of the vaporizer is connected to the cold energy input end of the second heat exchanger 2 through the pipeline containing temperature sensor T1 and valve 1; the cold energy output end of the vaporizer is also connected to the cold energy input end of the condenser through the pipeline containing temperature sensor T1, valve 26, valve 10 and temperature sensor T3; thus realizing the exchange of cold energy between waste cooling and circulating refrigerant or seawater.

[0041] In one specific implementation, the main steam pipeline is connected to the steam input end of the steam turbine, and the exhaust pipeline of the steam turbine is connected to the steam inlet of the condenser. After the steam turbine completes the conversion of mechanical energy into electrical energy, it delivers the waste heat steam to the condenser. The condensate outlet of the condenser is connected to a dedicated condensate pipeline for return, completing the water circulation on the power plant side.

[0042] Temperature sensor T3 is installed on the waste heat inlet pipe of the condenser, and temperature sensor T4 and mass flow meter m2 are installed on the waste heat outlet pipe of the condenser to monitor the medium parameters of the waste heat recovery process.

[0043] The waste heat output end of the condenser is connected to the input end of the vaporizer through the pipeline containing temperature sensor T4, valve 11, and valve 9. The waste heat output end of the condenser is also connected to the heat input end of the first heat exchanger 1 through the pipeline containing temperature sensor T4 and valve 13, thereby realizing the integration of waste heat with the heat of the circulating heat medium or seawater.

[0044] In one specific implementation, the heat exchanger includes a first heat exchanger 1 and a second heat exchanger 2. The heat medium output end of the first heat exchanger 1 is connected to the heat medium input end of the evaporator through the pipelines containing valves 7 and 18. The heat medium return end of the evaporator is connected back to the heat medium inlet end of the first heat exchanger 1 through the pipelines containing valves 20 and 8, forming a heat medium circulation on the heating side. The refrigerant output end of the second heat exchanger 2 is connected to the refrigerant input end of the condenser through the pipelines containing valves 5 and 16. The refrigerant return end of the condenser is connected back to the refrigerant inlet end of the second heat exchanger through the pipelines containing valves 22 and 8, forming a refrigerant circulation on the cooling side. The evaporator and condenser form a closed loop through the refrigerant pipeline, constituting the core heat exchange unit of the seawater source heat pump unit, realizing the phase change of the refrigerant.

[0045] The outlet of water pump 1 is connected to the seawater input end of the first heat exchanger 1 through the pipeline where valve 25 and valve 13 are located. The seawater side of the first heat exchanger 1 is connected to the heat pump unit side, so that the heat of seawater can be introduced into the heat pump unit when the waste heat is insufficient.

[0046] The outlet of water pump 2 is connected to the second heat exchanger 2 through the pipeline where valve 24 is located. The seawater side of the second heat exchanger 2 is connected to the heat pump unit side, so that the cooling capacity of seawater can be introduced into the heat pump unit when the residual cooling is insufficient.

[0047] In one specific implementation, the low-temperature water output end of the condenser is connected to the user-side cooling water supply port through the pipeline where valve 23 is located, and the user-side cooling water return port is connected back to the condenser's return water input end through the pipeline where valve 17 is located, forming a cooling water circulation; the high-temperature water output end of the evaporator is connected to the user-side heating water supply port through the pipeline where valve 21 is located, and the user-side heating water return port is connected back to the evaporator's return water input end through the pipeline where valve 19 is located, forming a hot water circulation.

[0048] Based on the waste cooling and waste heat conditions of the LNG station and the thermal power plant, as well as the users' heating and cooling load requirements, two operating modes are set up: waste heat heating (including seawater supplemental heating) and waste cooling (including seawater supplemental cooling).

[0049] In the waste heat heating mode (including seawater supplemental heating), the system controller calculates data from temperature sensors and mass flow meters to determine whether the waste heat from the turbine exhaust can meet the heat load required by users and LNG vaporization. If it does, the control system switches valves to enter the waste heat heating mode, where the waste heat generated by the power plant is transported through pipelines to the vaporizer as a vaporization heat source; simultaneously, it is transferred to the circulating water through a heat exchanger, and the circulating water is then upgraded by a heat pump unit before being transported to indoor heat dissipation devices to meet the user's heat load requirements. If it is determined that the requirements are not met, the valve opening is dynamically adjusted to prioritize heating the vaporizer, and the excess waste heat is used in conjunction with seawater for heating. Based on the utilization of waste heat, a seawater source heat pump is started to extract heat from the seawater to make up for the load gap.

[0050] The waste cooling mode (including seawater make-up cooling) determines whether the cooling capacity generated by LNG vaporization meets the cooling load requirements of the power plant condenser and building users. If it does, the system switches to waste cooling mode via valve control. In this mode, the LNG's cooling energy is piped to the condenser and simultaneously transferred to the heat exchanger, which then delivers the cooling energy to the seawater source heat pump to provide cooling for the indoor environment, meeting the building users' cooling load needs. If the LNG's cooling energy is insufficient, the system switches to waste cooling + seawater make-up cooling mode. This involves dynamically adjusting valve openings to prioritize cooling the power plant condenser. Excess waste cooling is combined with seawater for cooling. Simultaneously, the system activates the seawater transfer pump to extract low-temperature seawater, extracting cooling capacity to replenish the circulating refrigerant and meet the building's cooling requirements.

[0051] In this embodiment, during the cooling season, when the LNG terminal has sufficient waste cooling supply, the system can stably output cooling capacity to meet the heat release from the power plant condenser and the building cooling needs. When the LNG terminal has insufficient waste cooling capacity, the waste cooling is prioritized to supply the power plant condenser to improve its power generation efficiency. Then, seawater is coupled through a heat exchanger to extract cooling capacity for the seawater source heat pump unit, providing cooling capacity for building users and ensuring the continuous stability and rational energy utilization of the cooling process. During the heating season, when the power plant has sufficient waste heat supply, the system can stably output heat to ensure the vaporization of the vaporizer and the heating needs of building users. If the waste heat supply is insufficient, the waste heat is prioritized to supply the vaporizer, reducing the supply of LNG primary energy (such as natural gas). Then, seawater is coupled through a heat exchanger to extract heat for the seawater source heat pump unit, providing heat for building users, ultimately achieving efficient load adaptation and stable and reliable operation of the heating process.

[0052] Example 2

[0053] The purpose of this embodiment is to provide a control method for a seawater source heat pump system that utilizes waste cooling and waste heat, including:

[0054] Determine whether the waste heat from the turbine exhaust meets the heat load requirements of the user and the liquefied natural gas vaporization.

[0055] If the conditions are met, the valve is switched to transfer the waste heat from the thermal power plant to the gasifier as a gasification heat source, and at the same time transfer it to the circulating water through the heat exchanger. The circulating water is then transported to the user side after passing through the heat pump unit.

[0056] If the requirements are not met, the valve opening will be dynamically adjusted to prioritize heating the vaporizer, and the seawater source heat pump will be started to extract heat from the seawater to compensate for the heat load gap in conjunction with the remaining waste heat.

[0057] This also includes: determining whether the cooling capacity generated by liquefied natural gas vaporization meets the cooling load requirements of the power plant condenser and users;

[0058] If the conditions are met, the cold energy generated by the vaporization of liquefied natural gas is transferred to the condenser through valve control, and then transferred to the circulating refrigerant through the heat exchanger. The cold energy is then transferred to the heat pump unit through the circulating refrigerant to provide cooling services to the user side.

[0059] If this cannot be achieved, the valve opening will be dynamically adjusted to prioritize cooling the condenser of the power plant. A seawater transfer pump will be activated to draw low-temperature seawater and replenish the circulating refrigerant to meet the user's cooling needs.

[0060] like Figure 2 As shown, the heating and cooling control method of seawater source heat pump utilizing waste heat and cold is as follows:

[0061] (I) Summer Cooling Mode:

[0062] Step 1: Initialize the system controller; all valves and water pumps are in standby mode; monitor the outdoor ambient temperature in real time. T w Steam turbine operating power P LNG vaporizer inlet and outlet flow rates m 1 and inlet / outlet temperature T 1. T 2. Valve opening degree K v1 .

[0063] Step 2: Calculate the building's cooling load Q 0= f 1( T w ) α，α It is a constant, determined experimentally.

[0064] Step 3: Calculate the cooling load of the condenserQ 1= f 2( P )× k 冷 + β，β It is a constant, determined experimentally.

[0065] Step 4: Based on the inlet and outlet flow rates of the vaporizer m 1 and temperature T 1. T 2. Calculate the actual waste cooling capacity generated by LNG vaporization. Q 2= cm 1( T 1 T 2).

[0066] Step 5: Calculate the valve opening. K v1 = f v ( G 1)+ k 1, among which, ; k 1 is the basic opening offset, determined experimentally.

[0067] Step 6: Based on the building's cooling load Q 0, condenser cooling capacity Q 1. Cooling capacity generated by LNG vaporization Q 2 and valve opening degree K v1 ,when ,(in, i >1. This needs to be based on the water source heat pump unit. EER Confirmed, in this embodiment i =1.1), which is the residual cooling sufficient mode. The cooling capacity is provided to the condenser by regulating the valve, and at the same time, the cooling capacity is supplied to the heat exchanger for heat exchange. The low temperature medium enters the condenser, where the refrigerant undergoes condensation and releases heat. The low temperature medium absorbs heat and rises in temperature, and then returns to the heat exchanger to participate in the circulation, completing the heat transfer and discharge. At the same time, the return water from the user side enters the evaporator. The refrigerant in the evaporator absorbs the heat of the return water through the evaporation process, which lowers the temperature of the return water. Finally, the low temperature water is supplied to the user to meet the cooling demand.

[0068] Specifically, control valves 1, 3, 5, 6, 16, 19, 21, and 22 supply cooling capacity to building users to meet their cooling needs, while control valves 10 and 26 supply cooling capacity to the condenser to meet the heat release requirements of the power plant condenser. Water pumps 1 and 2 and other valves are all in the closed state.

[0069] when This indicates insufficient residual cooling, according to Kv1 Adjust the valve opening to prioritize supplying cooling energy to the condenser. Extract seawater cooling energy by controlling the valve and corresponding water pump, and then supply the cooling energy to users through heat exchangers and heat pump units.

[0070] Specifically, according to K v1 Control valves 10 and 26 prioritize supplying residual cooling to the power plant condenser; water pump 2 is activated to extract cooling from seawater, enabling the excess residual cooling and seawater to work together to provide cooling to building users through control valves 1, 2, 3, 4, 5, 6, 16, 19, 21, 22, and 24. Water pump 1 and all other valves are in the closed state.

[0071] (II) Winter Heating Mode:

[0072] Step 1: Real-time monitoring of outdoor ambient temperature T w Actual flow rate of LNG M Condenser inlet and outlet flow rates m 2 and inlet / outlet temperatures T 3, T 4. Valve opening degree K v2 .

[0073] Step 2: Based on the outdoor temperature T w Calculate the building's heat load Q 3= f 1( T w )+ c, c It is a constant, determined experimentally.

[0074] Step 3: Based on the actual LNG flow rate M Calculate the heat required for the vaporizer. Q 4= f 3( M )× k 热 + d, in, k 热 The heat of vaporization coefficient, d It is a constant, determined experimentally.

[0075] Step 4: Based on the condenser inlet and outlet flow rates m 2 and temperature T 3, T 4. Calculate the actual waste heat. Q 5= cm 2( T 4 T 3).

[0076] Step 5: Calculate the valve opening. K v2 = f v ( G 2)+ k 2, of which, , k 2 is the basic opening offset, which is determined experimentally.

[0077] Step 6: Based on the building's required heat load Q 3. Heat load required for the vaporizer Q 4. Actual waste heat of the condenser Q 5 and valve opening K v2 ,when ( e <1. It is necessary to determine the experimental seawater source heat pump unit. COP Confirmed, in this embodiment e =0.9), then it is in the waste heat sufficient mode. The corresponding valves are adjusted to supply waste heat to the vaporizer and allow it to enter the heat exchanger for heat exchange. The high-temperature medium after heat exchange travels through pipes to the evaporator, where the refrigerant evaporates and absorbs heat, changing the high-temperature medium to a low-temperature medium, which then returns to the heat exchanger to participate in the cycle. The return water from the building users enters the condenser side, where the refrigerant condenses and releases heat, raising the temperature of the low-temperature return water to provide heat for the building users. Specifically, valves 7, 8, 13, 14, 17, 18, 20, and 23 are adjusted to provide heat to the building users, while valves 9 and 11 are adjusted to provide heat to the vaporizer. Water pumps 1 and 2, and other valves, are all in the closed state.

[0078] when This indicates insufficient residual heat mode, according to K v2 The valve opening is adjusted to prioritize supplying waste heat to the gasifier, and then the corresponding water pumps and valves are activated to extract heat from seawater to provide heating for users. Specifically, according to... K v2 Control valves 9 and 11 prioritize supplying waste heat to the vaporizer to meet LNG vaporization needs. Start water pump 1 to extract heat from seawater. Control valves 7, 8, 12, 13, 14, 15, 17, 18, 20, 23, and 25 to achieve the synergistic supply of excess waste heat and seawater to building users for heating. Water pump 2 and other valves are all in the closed state.

[0079] In further embodiments, the following is also provided:

[0080] An electronic device includes a memory and a processor, as well as computer instructions stored in the memory and running on the processor. When executed by the processor, the computer instructions perform the method described in Embodiment 1. For brevity, further details are omitted here.

[0081] It should be understood that in this embodiment, the processor can be a central processing unit (CPU), or it can be other general-purpose processors, digital signal processors (DSPs), application-specific integrated circuits (ASICs), programmable gate arrays (FPGAs), or other programmable logic devices, discrete gate or transistor logic devices, discrete hardware components, etc. The general-purpose processor can be a microprocessor or any conventional processor, etc.

[0082] Memory may include read-only memory and random access memory, and provides instructions and data to the processor. A portion of memory may also include non-volatile random access memory. For example, memory may also store information about the device type.

[0083] A computer-readable storage medium for storing computer instructions, which, when executed by a processor, perform the method described in Embodiment 1.

[0084] The method in Embodiment 1 can be directly implemented by a hardware processor, or implemented by a combination of hardware and software modules within the processor. The software modules can reside in readily available storage media in the art, such as random access memory, flash memory, read-only memory, programmable read-only memory, electrically erasable programmable memory, or registers. This storage medium is located in memory; the processor reads information from the memory and, in conjunction with its hardware, completes the steps of the above method. To avoid repetition, a detailed description is not provided here.

[0085] A computer program product includes a computer program that, when executed by a processor, implements the method described in Embodiment 1.

[0086] The present invention also provides at least one computer program product tangibly stored on a non-transitory computer-readable storage medium. The computer program product includes computer-executable instructions, such as instructions included in program modules, which execute in a device on a target real or virtual processor to perform the processes / methods described above. Typically, program modules include routines, programs, libraries, objects, classes, components, data structures, etc., that perform specific tasks or implement specific abstract data types. In various embodiments, the functionality of program modules can be combined or divided among program modules as needed. The machine-executable instructions for the program modules can execute within a local or distributed device. In a distributed device, the program modules can reside in both local and remote storage media.

[0087] The computer program code used to implement the methods of the present invention may be written in one or more programming languages. This computer program code may be provided to a processor of a general-purpose computer, a special-purpose computer, or other programmable data processing device, such that when executed by the computer or other programmable data processing device, the program code causes the functions / operations specified in the flowcharts and / or block diagrams to be implemented. The program code may be executed entirely on a computer, partially on a computer, as a stand-alone software package, partially on a computer and partially on a remote computer, or entirely on a remote computer or server.

[0088] In the context of this invention, computer program code or related data may be carried by any suitable carrier to enable a device, apparatus, or processor to perform the various processes and operations described above. Examples of carriers include signals, computer-readable media, and the like. Examples of signals may include electrical, optical, radio, sound, or other forms of propagation signals, such as carrier waves, infrared signals, etc.

[0089] Those skilled in the art will recognize that the units and algorithm steps described in conjunction with the embodiments herein can be implemented in electronic hardware or a combination of computer software and electronic hardware. Whether these functions are implemented in hardware or software depends on the specific application and design constraints of the technical solution. Those skilled in the art can use different methods to implement the described functions for each specific application, but such implementation should not be considered beyond the scope of this application.

[0090] While the specific embodiments of the present invention have been described above in conjunction with the accompanying drawings, this is not intended to limit the scope of protection of the present invention. Those skilled in the art should understand that various modifications or variations that can be made by those skilled in the art without creative effort based on the technical solutions of the present invention are still within the scope of protection of the present invention.

Claims

1. A seawater source heat pump system utilizing residual cold and heat, characterized by, include: Gasifier, steam turbine, condenser, heat exchanger; The vaporizer is used to convert liquefied natural gas into gaseous natural gas and output cooling capacity to provide cooling capacity for the seawater source heat pump in summer and the condenser. The steam turbine is connected to the condenser via a pipeline and serves as the main heat source during the winter heating season. The condenser is connected to the heat exchanger and heat pump unit through a circulation pipe, and is used to recover the waste heat of the turbine exhaust steam and convert it into a heat transfer fluid. One side of the heat exchanger is connected to the vaporizer or the condenser, and the other side is connected to the seawater source and the heat pump unit. In summer, it serves as an exchanger between the waste cooling of liquefied natural gas and the cold source of seawater, and in winter, it serves as an enhancer between the waste heat of the condenser and the heat of the seawater. Determine whether the waste heat from the turbine exhaust meets the heat load requirements of the user and liquefied natural gas vaporization. If it does, switch the valves to transfer the waste heat from the power plant to the vaporizer as a vaporization heat source, and transfer it to the circulating water through a heat exchanger. The circulating water is then transported to the user side after passing through the heat pump unit. If it does not meet the requirements, dynamically adjust the valve opening to prioritize heat supply to the vaporizer and start the seawater source heat pump to extract heat from the seawater, working together with the remaining waste heat to make up for the heat load gap. Determine whether the cooling capacity generated by liquefied natural gas vaporization meets the cooling load requirements of the power plant condenser and users; if so, control the valve to transfer the cooling energy generated by liquefied natural gas vaporization to the condenser, and at the same time transfer it to the circulating refrigerant through the heat exchanger, and then transfer the cooling energy to the heat pump unit through the circulating refrigerant to provide cooling services to the user side. If this cannot be achieved, the valve opening is dynamically adjusted to prioritize cooling the condenser of the thermal power plant, and the seawater transfer pump is turned on to draw low-temperature seawater to replenish the circulating refrigerant and meet the cooling needs of the user side.

2. A seawater source heat pump system utilizing waste cooling and waste heat as described in claim 1, characterized in that, The cold energy output end of the vaporizer is connected to the heat exchanger and the condenser via pipelines; the waste heat output end of the condenser is connected to the input end of the vaporizer and the heat exchanger via pipelines.

3. A seawater source heat pump system utilizing waste cooling and waste heat as described in claim 1, characterized in that, The heat pump unit includes a condenser and an evaporator; the condenser and the evaporator form a circulation through refrigerant piping.

4. A seawater source heat pump system utilizing waste cooling and waste heat as described in claim 3, characterized in that, The heat exchanger includes a first heat exchanger and a second heat exchanger. The heat medium output end of the first heat exchanger is connected to the heat medium input end of the evaporator, and the heat medium return end of the evaporator is connected back to the heat medium inlet end of the first heat exchanger, forming a heat medium circulation on the heating side. The cold medium output end of the second heat exchanger is connected to the cold medium input end of the condenser, and the cold medium return end pipe of the condenser is connected back to the cold medium inlet end of the second heat exchanger, forming a cold medium circulation on the cooling side.

5. A seawater source heat pump system utilizing waste cooling and waste heat as described in claim 1, characterized in that, The heat exchanger includes a first heat exchanger and a second heat exchanger. The outlet of the first water pump is connected to the seawater input end of the first heat exchanger. The seawater side of the first heat exchanger is connected to the heat pump unit side, so that the heat of the seawater can be introduced into the heat pump unit when the waste heat is insufficient. The outlet of the second water pump is connected to the second heat exchanger, and the seawater side of the second heat exchanger is connected to the heat pump unit side, so that the cooling capacity of the seawater can be introduced into the heat pump unit when the residual cooling is insufficient.

6. A seawater source heat pump system utilizing waste cooling and waste heat as described in claim 3 or 4, characterized in that, The low-temperature water output end of the condenser is connected to the user-side cooling water supply port, and the user-side cooling water return port is connected back to the condenser's return water input end, forming a cooling water circulation; the high-temperature water output end of the evaporator is connected to the user-side heating water supply port, and the user-side heating water return port is connected back to the evaporator's return water input end, forming a hot water circulation.

7. A seawater source heat pump system utilizing waste cooling and waste heat as described in claim 1, characterized in that, It also includes a temperature sensor, a mass flow meter, and a valve. The temperature sensor and mass flow meter are used to monitor the temperature and flow rate data of the medium, respectively, and the valve is used to regulate the delivery path of the medium.

8. A seawater source heat pump system utilizing waste cooling and waste heat as described in claim 1, characterized in that, The steam input end of the steam turbine is connected to the main steam, and the exhaust end of the steam turbine is connected to the steam inlet of the condenser. After the steam turbine completes the conversion of mechanical energy and electrical energy, it delivers the waste heat steam to the condenser. The condensate outlet of the condenser is connected to the condensate pipeline for return, completing the water circulation on the thermal power plant side.

9. A control method for a seawater source heat pump system utilizing waste cooling and waste heat, comprising a seawater source heat pump system utilizing waste cooling and waste heat as described in any one of claims 1-8, characterized in that, include: Determine whether the waste heat from the turbine exhaust meets the heat load requirements of the user and the liquefied natural gas vaporization. If the conditions are met, the valve is switched to transfer the waste heat from the thermal power plant to the gasifier as a gasification heat source, and at the same time transfer it to the circulating water through the heat exchanger. The circulating water is then transported to the user side after passing through the heat pump unit. If the requirements are not met, the valve opening will be dynamically adjusted to prioritize heating the vaporizer, and the seawater source heat pump will be started to extract heat from the seawater to compensate for the heat load gap in conjunction with the remaining waste heat.

10. A control method for a seawater source heat pump system utilizing waste cooling and waste heat, comprising a seawater source heat pump system utilizing waste cooling and waste heat as described in any one of claims 1-8, characterized in that, include: Determine whether the cooling capacity generated by liquefied natural gas vaporization meets the cooling load requirements of the power plant condenser and users; If the conditions are met, the cold energy generated by the vaporization of liquefied natural gas is transferred to the condenser through valve control, and then transferred to the circulating refrigerant through the heat exchanger. The cold energy is then transferred to the heat pump unit through the circulating refrigerant to provide cooling services to the user side. If this cannot be achieved, the valve opening is dynamically adjusted to prioritize cooling the condenser of the thermal power plant, and the seawater transfer pump is turned on to draw low-temperature seawater to replenish the circulating refrigerant and meet the cooling needs of the user side.

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