Transcritical CO2 heat pump ejector performance improving device and method

Abstract

The invention provides a transcritical CO2 heat pump ejector performance improving device and method, and relates to the technical field of industrial heat pumps, the device comprises a compressor, a first gas cooler, a second gas cooler, an ejector and a CO2 pump; the compressor is used for compressing the received CO2 to a high-temperature and high-pressure supercritical state; the first gas cooler is used for performing primary heat exchange on CO2 in a supercritical state and first circulating water to obtain high-temperature water; the CO2 pump is used for pressurizing a part of CO2 after heat exchange of the second gas cooler to obtain a mainstream fluid; the ejector is used for ejecting the CO2 fluid from the first gas cooler under the expansion depressurization action of the mainstream fluid, and a confluence flow is formed after ejection and mixing and flows into the second gas cooler; and the second gas cooler is used for carrying out secondary heat exchange on the confluence flow and second circulating water to obtain medium-temperature water. Efficient and stable operation of the transcritical CO2 heat pump system is achieved, and the waste heat utilization efficiency and the heat supply energy efficiency are improved.

Description

Technical Field

[0001] This application relates to the field of industrial heat pump technology, and in particular to a device and method for improving the performance of a transcritical CO2 heat pump ejector. Background Technology

[0002] In today's petroleum and steel industries, energy consumption is high, and the production process generates a large amount of high-temperature, high-pressure industrial waste heat, including associated high-temperature wastewater. Direct discharge of this waste heat not only leads to significant energy waste but also increases greenhouse gas emissions, exacerbating global warming, and causing thermal pollution to surrounding water bodies and the atmosphere, threatening ecological security. Therefore, how to efficiently recover and utilize waste heat from petroleum processes under complex and variable operating conditions, and effectively reduce energy consumption, has become a pressing technical problem that needs to be solved for sustainable industrial development.

[0003] In existing technologies, scholars and enterprises have proposed transcritical heat pump systems using CO2 as the refrigerant, combined with ejectors to recover throttling losses, thereby improving system performance. For example, CN107642916A proposes a compression-ejection transcritical CO2 cycle combined cooling and heating system. This system integrates cooling, heating, and domestic hot water preparation by introducing ejectors and gas-liquid separators in the cooling section, thereby improving energy utilization. CN110030756B proposes a transcritical CO2 multi-temperature zone supermarket combined cooling and heating system with ejectors. By setting up high-temperature water tank groups and multiple medium-temperature evaporators, and utilizing ejectors to recover expansion energy, it meets the multi-temperature zone requirements of a supermarket environment. In addition, CN111174268B and CN114608050A both involve air-source transcritical CO2 heat pump systems, which reduce throttling losses and improve heating performance under low-temperature conditions by introducing ejectors, parallel compression, and economizer subcooling.

[0004] However, the aforementioned existing technologies are mainly geared towards multi-temperature zone cooling / heating applications in the building or supermarket sectors, focusing on improving frosting issues in low-temperature environments and enhancing overall system energy efficiency. These technical solutions are not adapted to the large amounts of high-temperature wastewater waste heat, complex operating conditions, and high-pressure operating conditions present in the petroleum industry, and cannot effectively solve the practical problems of high-temperature heat tracing requirements and multi-stage heat energy utilization in petroleum processes.

[0005] In summary, although prior art documents such as CN114608050A have disclosed transcritical CO2 heat pump systems that utilize ejectors for energy recovery and improve low-temperature operating conditions, they do not cover high-temperature waste heat recovery and graded utilization for petroleum processes, nor do they propose optimized control of flow rate and exhaust pressure based on internal and external parameters and heat demand ratio. Summary of the Invention

[0006] To address the problems in the prior art, this application provides a device and method for improving the performance of transcritical CO2 heat pump ejectors, which can solve problems such as excessive pressure ratio, excessive exhaust temperature, and poor performance of transcritical CO2 systems under low ambient temperature conditions in winter, and can realize multi-stage thermal energy utilization.

[0007] In a first aspect, this application provides a transcritical CO2 heat pump ejector performance enhancement device, comprising: a compressor, a first gas cooler, a second gas cooler, an ejector, and a CO2 pump;

[0008] The compressor is used to compress the received CO2 to a supercritical state with high temperature and high pressure and to transfer the supercritical CO2 to the first gas cooler.

[0009] The first gas cooler is used to exchange heat between the supercritical CO2 and the first circulating water to obtain high-temperature water, and to transfer the heat-exchanged CO2 fluid to the ejector inlet of the ejector.

[0010] The CO2 pump is used to pressurize a portion of the CO2 after heat exchange in the second gas cooler to obtain the mainstream fluid and to transmit the mainstream fluid to the mainstream inlet of the ejector;

[0011] The outlet of the ejector is connected to the second gas cooler. The ejector is used to eject CO2 fluid from the first gas cooler under the expansion and pressure reduction of the mainstream fluid, and form a confluence flow into the second gas cooler after injection and mixing.

[0012] The second gas cooler is used to perform secondary heat exchange between the confluence stream and the second circulating water to obtain medium-temperature water.

[0013] Furthermore, it also includes: a throttle valve and an air-source evaporator;

[0014] The throttling valve is used to throttle and reduce the pressure of another portion of CO2 after heat exchange in the second gas cooler.

[0015] The air source evaporator is used to exchange heat between the CO2 from the throttle valve and the external environment, and to transfer the resulting evaporated CO2 to the compressor.

[0016] Furthermore, it also includes: a control module, a first control valve, and a second control valve;

[0017] The control module is electrically connected to the first control valve and the second control valve; the first control valve is connected to the inlet of the throttle valve, and the second control valve is connected to the inlet of the CO2 pump.

[0018] The control module is used to control the first control valve and the second control valve according to the preset heat demand in order to distribute the flow.

[0019] Furthermore, the control module is specifically used for:

[0020] If the heat demand satisfies the first constraint model, calculate the primary heat exchange flow rate and the secondary heat exchange flow rate according to the first flow rate calculation model.

[0021] If the heat demand satisfies the second constraint model, calculate the primary heat exchange flow rate and the secondary heat exchange flow rate according to the second flow rate calculation model.

[0022] The first control valve and the second control valve are controlled according to the primary heat exchange flow rate and the secondary heat exchange flow rate.

[0023] Furthermore, the control module is also used to control the optimal exhaust pressure for a single heat exchange.

[0024] Furthermore, the high-temperature water is 120°C; the medium-temperature water is 60°C.

[0025] Secondly, this application provides a method for improving the performance of a transcritical CO2 heat pump ejector, applied to the transcritical CO2 heat pump ejector performance improvement apparatus described in any of the above embodiments, comprising:

[0026] The compressor compresses the received CO2 to a supercritical state with high temperature and high pressure and then transfers the supercritical CO2 to the first gas cooler.

[0027] The first gas cooler allows the supercritical CO2 to exchange heat with the first circulating water once to obtain high-temperature water, and then transmits the heat-exchanged CO2 fluid to the ejector inlet.

[0028] The CO2 pump pressurizes a portion of the CO2 after heat exchange in the second gas cooler to obtain the mainstream fluid and then transmits the mainstream fluid to the mainstream inlet of the ejector.

[0029] The injector, under the expansion and pressure reduction of the mainstream fluid, draws CO2 fluid from the first gas cooler, and after injection and mixing, forms a confluence flow that flows into the second gas cooler;

[0030] The second gas cooler allows the confluence stream to exchange heat with the second circulating water a second time to obtain medium-temperature water.

[0031] Furthermore, the transcritical CO2 heat pump ejector performance enhancement device also includes a throttling valve and an air source evaporator; the transcritical CO2 heat pump ejector performance enhancement method further includes:

[0032] The throttling valve reduces the pressure of another portion of CO2 after heat exchange in the second gas cooler.

[0033] The air source evaporator allows CO2 from the throttle valve to exchange heat with the external environment and transfers the resulting evaporated CO2 to the compressor.

[0034] Furthermore, the transcritical CO2 heat pump ejector performance enhancement device further includes a control module, a first control valve, and a second control valve; the transcritical CO2 heat pump ejector performance enhancement method further includes:

[0035] The control module controls the first control valve and the second control valve according to the preset heat demand to distribute the flow.

[0036] Furthermore, the control module controls the first control valve and the second control valve according to a preset heat demand, including:

[0037] If the heat demand satisfies the first constraint model, calculate the primary heat exchange flow rate and the secondary heat exchange flow rate according to the first flow rate calculation model.

[0038] If the heat demand satisfies the second constraint model, calculate the primary heat exchange flow rate and the secondary heat exchange flow rate according to the second flow rate calculation model.

[0039] The first control valve and the second control valve are controlled according to the primary heat exchange flow rate and the secondary heat exchange flow rate.

[0040] Furthermore, it also includes:

[0041] The control module regulates the optimal exhaust pressure for a single heat exchange.

[0042] Thirdly, this application provides a computer device, including a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the processor executes the computer program to implement the method described in any of the above embodiments.

[0043] Fourthly, this application provides a computer-readable storage medium storing a computer program that, when executed by a processor, implements the methods described in any of the above embodiments.

[0044] Fifthly, this application provides a computer program product, which includes a computer program that, when executed by a processor, implements the method described in any of the above embodiments.

[0045] This application provides a device and method for improving the performance of a transcritical CO2 heat pump ejector. The device includes: a compressor, a first gas cooler, a second gas cooler, an ejector, and a CO2 pump. The compressor is used to compress received CO2 to a supercritical state at high temperature and high pressure and transfer the supercritical CO2 to the first gas cooler. The first gas cooler is used to perform a primary heat exchange between the supercritical CO2 and first circulating water to obtain high-temperature water, and to transfer the heat-exchanged CO2 fluid to the ejector's inlet. The CO2 pump is used to pressurize a portion of the CO2 after heat exchange in the second gas cooler to obtain a mainstream fluid and to transfer the mainstream fluid to the ejector's mains inlet. The ejector's outlet is connected to the second gas cooler. The ejector is used to eject CO2 fluid from the first gas cooler under the expansion and pressure reduction effect of the mainstream fluid, and after jet mixing, form a confluence flow into the second gas cooler. The second gas cooler is used to perform a secondary heat exchange between the confluence flow and second circulating water to obtain medium-temperature water. The transcritical CO2 heat pump ejector performance enhancement device and method provided in this application realize the efficient and stable operation of the transcritical CO2 heat pump system and improve the waste heat utilization efficiency and heating energy efficiency.

[0046] This application solves the problem of performance degradation caused by excessive system pressure ratio and excessive exhaust temperature at low ambient temperatures by introducing an ejector into the transcritical CO2 cycle process, thus achieving efficient and stable operation of the system in winter conditions. By coupling the ejector circuit with the conventional throttling circuit, hot water of different temperature levels can be output simultaneously, realizing precise distribution and flexible supply of heat energy. Under the premise of ensuring stable operation, the waste heat of different temperature levels is fully utilized, significantly improving the overall energy efficiency of the transcritical CO2 heat pump system. Attached Figure Description

[0047] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0048] Figure 1 This is a schematic diagram of the structure of a transcritical CO2 heat pump ejector performance enhancement device provided in an embodiment of this application;

[0049] Figure 2 This is a schematic diagram of the structure of a transcritical CO2 heat pump ejector performance enhancement device provided in an embodiment of this application;

[0050] Figure 3This is a schematic flowchart of a method for improving the performance of a transcritical CO2 heat pump ejector provided in an embodiment of this application;

[0051] Figure 4 This is a schematic flowchart of a method for improving the performance of a transcritical CO2 heat pump ejector provided in an embodiment of this application;

[0052] Figure 5 This is a schematic flowchart of a method for improving the performance of a transcritical CO2 heat pump ejector provided in an embodiment of this application;

[0053] Figure 6 This is a schematic diagram of the physical structure of an electronic device provided in an embodiment of this application. Detailed Implementation

[0054] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the embodiments of this application will be further described in detail below with reference to the accompanying drawings. Here, the illustrative embodiments and their descriptions are used to explain this application, but are not intended to limit this application. It should be noted that, unless otherwise specified, the embodiments and features in the embodiments of this application can be arbitrarily combined with each other.

[0055] This application combines internal and external system parameters and the heat demand ratio of the staged cycle to regulate the flow rate, and at the same time optimizes the system's optimal exhaust pressure, thereby achieving the effect of rationally planning the system pressure ratio and improving system performance.

[0056] Figure 1 This is a schematic diagram of the structure of a transcritical CO2 heat pump ejector performance enhancement device provided in an embodiment of this application, as shown below. Figure 1 As shown, the transcritical CO2 heat pump ejector performance enhancement device provided in this application includes: a compressor 1, a first gas cooler 2, a second gas cooler 3, an ejector 4, and a CO2 pump 5;

[0057] The compressor 1 is used to compress the received CO2 to a supercritical state with high temperature and high pressure and to transfer the supercritical CO2 to the first gas cooler 2.

[0058] The first gas cooler 2 is used to exchange heat between the supercritical CO2 and the first circulating water to obtain high-temperature water, and to transfer the heat-exchanged CO2 fluid to the ejector inlet of the ejector 4.

[0059] The CO2 pump 5 is used to pressurize a portion of the CO2 after heat exchange in the second gas cooler 3 to obtain the mainstream fluid and to transmit the mainstream fluid to the mainstream inlet of the ejector 4;

[0060] The outlet of the ejector 4 is connected to the second gas cooler 3. The ejector 4 is used to eject CO2 fluid from the first gas cooler 2 under the expansion and pressure reduction of the mainstream fluid, and form a confluence flow into the second gas cooler 3 after injection and mixing.

[0061] The second gas cooler 3 is used to perform secondary heat exchange between the converging stream and the second circulating water to obtain medium-temperature water.

[0062] Specifically, compressor 1 is located at the front end of the primary heat exchanger to compress the low-temperature, low-pressure CO2 working fluid, bringing it to a supercritical state with high temperature and high pressure. Through this process, the enthalpy of the CO2 working fluid increases significantly, providing sufficient energy for subsequent heat exchange and injection processes.

[0063] The first gas cooler 2 is installed between the outlet of compressor 1 and the inlet of ejector 4, with CO2 working fluid and first circulating water on its two sides, respectively, for heat exchange. The high-temperature, high-pressure supercritical CO2 fluid output from compressor 1 releases heat in the first gas cooler 2, heating the first circulating water and forming high-temperature water. Simultaneously, its own temperature decreases, and it continues to flow as CO2 fluid towards the inlet of ejector 4. This arrangement ensures a stable high-temperature heat source during system operation, meeting the high-temperature heat tracing requirements of petroleum processes.

[0064] The CO2 pump is connected between the outlet of the second gas cooler 3 and the main flow inlet of the ejector 4. It is used to repressurize part of the CO2 fluid after heat exchange in the second gas cooler 3, making it a high-pressure main flow fluid, and then deliver it to the main flow inlet of the ejector 4.

[0065] The ejector 4 comprises a mains inlet, an ejector inlet, and an outlet, with its outlet connected to the second gas cooler 3. The ejector 4 generates an ejector effect through the expansion and depressurization of the high-pressure mains fluid, thereby introducing CO2 fluid from the outlet of the first gas cooler 2 and mixing it with the mains fluid. The two fluids are thoroughly mixed inside the ejector 4 and pressurized by the diffuser section, ultimately forming a stable converging flow that is output to the second gas cooler 3.

[0066] The second gas cooler 3 is connected to the outlet of the ejector 4 and is used to further cool and exchange heat between the CO2 working medium in the confluence stream and the second circulating water. Through the heat exchange process, the second circulating water is heated to medium temperature water, while the temperature of the CO2 working medium is effectively reduced, thereby completing the secondary heat exchange process.

[0067] Through the structural design of the above-mentioned device, reasonable energy distribution and pressure ratio optimization can be achieved in the transcritical CO2 heat pump system, which can effectively improve the high-temperature heat tracing performance and overall energy efficiency while ensuring the stable operation of the system.

[0068] In one embodiment, such as Figure 1 As shown, the transcritical CO2 heat pump ejector performance enhancement device provided in this application also includes: a throttling valve 6 and an air source evaporator 7;

[0069] The throttle valve 6 is used to throttle and reduce the pressure of another portion of CO2 after heat exchange in the second gas cooler 3.

[0070] The air source evaporator 7 is used to exchange heat between the CO2 from the throttle valve 6 and the external environment, and to transfer the resulting evaporated CO2 to the compressor 1.

[0071] Specifically, the throttling valve 6 is arranged between the outlet of the second gas cooler 3 and the inlet of the air source evaporator 7, and is used to throttle and reduce the pressure of another part of the CO2 fluid after heat exchange in the second gas cooler 3. Through the throttling process, the pressure and temperature of the CO2 working fluid are further reduced, bringing it into a low-temperature and low-pressure state, providing suitable operating conditions for subsequent heat absorption.

[0072] The air source evaporator 7 is connected between the outlet of the throttling valve 6 and the inlet of the compressor 1. The main function of the air source evaporator 7 is to utilize outside air as a heat source, allowing the throttled, low-temperature, low-pressure CO2 working fluid to absorb ambient heat and vaporize in the evaporator, forming low-temperature gaseous CO2, which is then delivered to the inlet of the compressor 1. This forms a complete single-stage cycle, ensuring the continuous flow of the CO2 working fluid in the cycle and providing stable heating operating conditions for the transcritical CO2 heat pump ejector 4 system.

[0073] By setting up the throttle valve 6 and the air source evaporator 7, not only is the pressure regulation and evaporation process of the CO2 fluid at the outlet of the second gas cooler 3 realized, but the compressor 1 is also able to continuously draw in the working fluid in a suitable state, which further improves the stability and overall operating efficiency of the system in low temperature environment.

[0074] In one embodiment, for the primary cycle, CO2 working fluid is introduced into the transcritical CO2 compressor 1 for compression, temperature increase, and pressure increase, and then enters the first gas cooler 2 to exchange heat with the first circulating water. After releasing heat, the CO2 acts as an ejector flow and mixes with the mainstream. For the secondary cycle, the CO2 pump acts as the power source for the secondary cycle, allowing the CO2 in the secondary cycle to be heated and pressurized, and then enters the ejector 4 to become the mainstream. At the same time, it is throttled and depressurized. The medium-pressure ejector flow mixes with the mainstream and acts as a confluence flow. It is pressurized and flows out in the ejector 4 and enters the second gas cooler 3 to release heat, providing heat for the second circulating water. After the CO2 has released heat in the second gas cooler 3, it is split. Part of the CO2 enters the primary cycle, exchanges heat with the air source evaporator 7 to cool down, and returns to the transcritical CO2 compressor 1 as the primary circulating fluid. Part of the CO2 enters the secondary cycle and returns to the CO2 pump to complete the cycle.

[0075] Figure 2 This is a schematic diagram of the structure of a transcritical CO2 heat pump ejector performance enhancement device provided in an embodiment of this application, as shown below. Figure 2 As shown, the transcritical CO2 heat pump ejector performance enhancement device provided in this application also includes: a control module 8, a first control valve 9, and a second control valve 10;

[0076] The control module 8 is electrically connected to the first control valve 9 and the second control valve 10; the first control valve 9 is connected to the inlet of the throttle valve 6, and the second control valve 10 is connected to the inlet of the CO2 pump 5.

[0077] The control module 8 is used to control the first control valve 9 and the second control valve 10 according to the preset heat demand to perform flow distribution.

[0078] Specifically, based on different heat exchange requirements and considering the water temperature requirements for primary and secondary heat exchange, different CO2 flow rates are allocated to the primary and secondary circulations respectively. When the heat demand for primary heat exchange is large, more CO2 flow rate is allocated to the primary circulation, and when the heat demand for primary heat exchange is small, less CO2 flow rate is allocated to the primary circulation, so as to reduce the transcritical CO2 circulation pressure ratio and increase energy consumption.

[0079] The control module 8 is used to intelligently regulate the flow rate within the system. It is electrically connected to the first control valve 9 and the second control valve 10 to form a control relationship. The first control valve 9 is located between the outlet of the second gas cooler 3 and the inlet of the throttle valve 6, and is used to regulate the flow rate of CO2 fluid entering the throttle valve 6. The second control valve 10 is located between the outlet of the second gas cooler 3 and the inlet of the CO2 pump, and is used to regulate the flow rate of CO2 fluid entering the CO2 pump.

[0080] During system operation, the control module 8 can control the opening and closing states or opening degree of the first control valve 9 and the second control valve 10 according to the preset heat requirements of the petroleum process and the heat load required by different heat exchange links. This achieves a reasonable distribution of the CO2 fluid after heat exchange in the second gas cooler 3 between the throttle valve 6 and the CO2 pump. Through this flow distribution mechanism, the heat supply in the primary and secondary heat exchange processes can better meet the actual needs while ensuring stable system operation, thereby improving the overall energy efficiency and adaptability of the transcritical CO2 heat pump ejector 4 system.

[0081] In one embodiment, the control module 8 is specifically used for:

[0082] If the heat demand satisfies the first constraint model, calculate the primary heat exchange flow rate and the secondary heat exchange flow rate according to the first flow rate calculation model.

[0083] If the heat demand satisfies the second constraint model, calculate the primary heat exchange flow rate and the secondary heat exchange flow rate according to the second flow rate calculation model.

[0084] The first control valve 9 and the second control valve 10 are controlled according to the primary heat exchange flow rate and the secondary heat exchange flow rate.

[0085] Specifically, after receiving the preset heat demand information, the control module 8 will make a judgment using the system operating parameters:

[0086] When the heat demand meets the first constraint model, the high flow rate heating mode is entered. The control module 8 determines the primary heat exchange flow rate and the secondary heat exchange flow rate based on the first flow rate calculation model, and outputs the corresponding control signal to drive the first control valve 9 and the second control valve 10 to adjust to the corresponding opening degree, so that more CO2 fluid enters the primary heat exchange loop to meet the larger high temperature heat demand.

[0087] When the heat demand meets the second constraint model, the system enters a low-flow heating mode. The control module 8 determines the primary heat exchange flow rate and the secondary heat exchange flow rate based on the second flow calculation model, and outputs a control signal to adjust the opening and closing states of the first control valve 9 and the second control valve 10, so that more CO2 fluid enters the secondary heat exchange loop and effectively reduces the output heat.

[0088] Through the above design, the control module 8 can automatically select the appropriate constraint model and calculate the optimal flow distribution scheme under different operating conditions, realizing the dynamic adjustment between primary heat exchange and secondary heat exchange, so that the heat output matches the actual demand, effectively improving the overall energy efficiency and adaptability of the system.

[0089] In one embodiment, high-temperature heating is required during oil processing. However, oil fields are typically located in remote northern regions where winter temperatures are low, leading to problems such as excessively high pressure ratios, high exhaust temperatures, and poor performance of transcritical CO2 systems. Therefore, it is recommended to reduce the exhaust pressure of compressor 1 (to approximately 8 MPa) to lower the exhaust temperature (below 120°C, thus ensuring the heating temperature is around 100°C). To ensure that heating energy is introduced into the liquid injector 4, a second-stage heating temperature (approximately 60°C) is provided.

[0090] The heat flow is allocated between the primary and secondary cycles according to different heat demands to achieve the optimal system effect. At the same time, the optimal exhaust pressure of the system is adjusted in combination with the internal performance of the system and the external environmental parameters.

[0091] In one embodiment, when there is a large-scale demand for high-temperature heat tracing in the petroleum process system, especially when the output temperature of high-temperature hot water needs to be increased in cold climates, the system needs to maintain a large heat output. In this case, the control module 8 first calculates based on the actual detected water temperature demand signal and system operating parameters to determine whether the current state satisfies the first constraint model:

[0092]

[0093] In the formula, Q1 is the heat exchange required for primary heat exchange; Q2 is the heat exchange required for secondary heat exchange; A is an empirical coefficient; T water1 The temperature of the first circulating water; T water2 T0 represents the temperature of the second circulating water; T0 represents the ambient temperature.

[0094] If the above conditions are met, it indicates that the system should prioritize heating the primary circulation to obtain high-temperature water. The control module 8 determines that it should switch to the high-flow heating mode. At this time, the control module 8 will call the first flow calculation model to calculate the allocation of the primary heat exchange flow and the secondary heat exchange flow, and output control commands to the first control valve 9 and the second control valve 10, so that the CO2 fluid flow to the secondary circulation decreases and the CO2 fluid flow to the primary circulation increases.

[0095] The first flow calculation model is shown below:

[0096]

[0097] In the formula, m1 is the primary heat exchange flow rate; m2 is the secondary heat exchange flow rate; E is an empirical coefficient; T water1 The temperature of the first circulating water; T water2 This refers to the temperature of the second circulating water.

[0098] The execution of the above process can significantly improve the volume distribution of high-temperature CO2 fluid in the primary circulation loop, thereby increasing the high-temperature heat exchange capacity in the first gas cooler 2, improving the stability and energy level of high-temperature hot water output, and ultimately meeting the demand for high-flow-rate and high-temperature heat energy supply in petroleum processes.

[0099] In one embodiment, when the petroleum process system is in a low-load operation phase, or when the ambient temperature is high and the demand for high-temperature hot water is reduced, the system does not need to maintain a large flow of high-temperature heating. The control module 8 will determine whether the second heating condition is met based on the current operating status.

[0100] When the system parameters satisfy the second constraint model:

[0101]

[0102] In the formula, C is an empirical coefficient; T water1The temperature of the first circulating water; T water2 The temperature of the second circulating water; T gs1 T is the temperature at the outlet of the first gas cooler 2; gs2 The temperature at the outlet of the second gas cooler 3.

[0103] The control module 8 determines that it should switch to a low-flow heating mode. At this time, it will recalculate the target flow rates of primary and secondary heat exchange by calling the second flow calculation model, and control the opening of the first control valve 9 and the second control valve 10 to reduce the flow rate of CO2 fluid to the primary circulation and increase the flow rate of CO2 fluid to the secondary circulation.

[0104] The second flow calculation model is shown below:

[0105]

[0106] In the formula, F is the empirical coefficient; T water1 The temperature of the first circulating water; T water2 T0 represents the temperature of the second circulating water; T0 represents the ambient temperature.

[0107] In this mode, although the total amount of refrigerant (CO2 working fluid) in the overall system circulation remains unchanged, more CO2 working fluid is introduced into the secondary heat exchange loop, where it is heat exchanged by the second gas cooler 3 to output medium-temperature hot water. Since the outlet temperature of the gas cooler in the secondary cycle is usually lower than that in the primary cycle, the overall heat output is effectively suppressed, which helps to prevent system overheating or energy waste, and improves operating economy and adjustment flexibility.

[0108] In one embodiment, the control module 8 is also used to control the optimal exhaust pressure for a single heat exchange.

[0109] Specifically, the control module 8 is electrically connected to the compressor 1. Based on the preset heat demand information and the operating parameters inside and outside the system, it dynamically calculates and adjusts the exhaust pressure in the first-stage cycle and sends control commands to the compressor 1 to achieve precise control of the exhaust pressure of the compressor 1.

[0110] Through the above settings, the control module 8 can adaptively adjust the exhaust pressure of the primary heat exchange circuit under different ambient temperatures and operating conditions, thereby optimizing the pressure ratio during system operation and avoiding excessively high exhaust temperature and performance degradation caused by excessively high pressure ratio. This ensures that the transcritical CO2 heat pump ejector 4 can still maintain a highly efficient and stable operating state under low ambient temperature conditions.

[0111] In one embodiment, the control module 8 regulates the optimal exhaust pressure for one cycle of the system based on internal and external parameters of the system, combined with the water supply demand temperature, to improve system performance and achieve optimal control. The optimal exhaust pressure regulation satisfies the following formula:

[0112]

[0113] In the formula, m, n, and q are empirical coefficients; T water1 The temperature of the first circulating water; T water2 T is the temperature of the second circulating water; T0 is the ambient temperature; T gs1 T is the temperature at the outlet of the first gas cooler 2; gs2 The temperature at the outlet of the second gas cooler 3.

[0114] In one embodiment, the high-temperature water is 120°C; the medium-temperature water is 60°C.

[0115] This application provides a transcritical CO2 heat pump ejector performance enhancement device, comprising: a compressor, a first gas cooler, a second gas cooler, an ejector, and a CO2 pump; the compressor is used to compress received CO2 to a supercritical state at high temperature and high pressure and transfer the supercritical CO2 to the first gas cooler; the first gas cooler is used to perform a primary heat exchange between the supercritical CO2 and a first circulating water to obtain high-temperature water, and transfer the heat-exchanged CO2 fluid to the ejector's inlet; the CO2 pump is used to pressurize a portion of the CO2 after heat exchange in the second gas cooler to obtain a mainstream fluid and transfer the mainstream fluid to the ejector's mainstream inlet; the ejector's outlet is connected to the second gas cooler, and the ejector is used to eject CO2 fluid from the first gas cooler under the expansion and pressure reduction effect of the mainstream fluid, and after jet mixing, form a confluence flow into the second gas cooler; the second gas cooler is used to perform a secondary heat exchange between the confluence flow and a second circulating water to obtain medium-temperature water. The transcritical CO2 heat pump ejector performance enhancement device provided in this application enables the efficient and stable operation of the transcritical CO2 heat pump system and improves waste heat utilization efficiency and heating energy efficiency.

[0116] This application solves the problem of performance degradation caused by excessive system pressure ratio and excessive exhaust temperature at low ambient temperatures by introducing an ejector into the transcritical CO2 cycle process, thus achieving efficient and stable operation of the system in winter conditions. By coupling the ejector circuit with the conventional throttling circuit, hot water of different temperature levels can be output simultaneously, realizing precise distribution and flexible supply of heat energy. Under the premise of ensuring stable operation, the waste heat of different temperature levels is fully utilized, significantly improving the overall energy efficiency of the transcritical CO2 heat pump system.

[0117] In addition, this application also provides a method for improving the performance of a transcritical CO2 heat pump ejector, which improves the performance of the transcritical CO2 heat pump ejector by using the transcritical CO2 heat pump ejector performance improvement device described in the above embodiments.

[0118] Figure 3 This is a schematic flowchart of a method for improving the performance of a transcritical CO2 heat pump ejector according to an embodiment of this application, as shown below. Figure 3 As shown, the method for improving the performance of a transcritical CO2 heat pump ejector provided in this application includes:

[0119] S301: The compressor compresses the received CO2 to a supercritical state with high temperature and high pressure and transfers the supercritical CO2 to the first gas cooler;

[0120] S302: The first gas cooler performs a heat exchange between the supercritical CO2 and the first circulating water to obtain high-temperature water, and then transmits the heat-exchanged CO2 fluid to the ejector inlet of the ejector.

[0121] S303: The CO2 pump pressurizes a portion of the CO2 after heat exchange in the second gas cooler to obtain the mainstream fluid and transmits the mainstream fluid to the mainstream inlet of the ejector;

[0122] S304: The ejector, under the expansion and pressure reduction of the mainstream fluid, draws CO2 fluid from the first gas cooler and forms a confluence flow into the second gas cooler after injection and mixing;

[0123] S305: The second gas cooler allows the confluence stream to exchange heat with the second circulating water a second time to obtain medium-temperature water.

[0124] Figure 4 This is a schematic flowchart of a method for improving the performance of a transcritical CO2 heat pump ejector according to an embodiment of this application. The transcritical CO2 heat pump ejector performance improvement device further includes a throttling valve and an air source evaporator; as... Figure 4 As shown, the method for improving the performance of a transcritical CO2 heat pump ejector provided in this application also includes:

[0125] S401: The throttling valve reduces the pressure of another portion of CO2 after heat exchange in the second gas cooler;

[0126] S402: The air source evaporator allows CO2 from the throttle valve to exchange heat with the external environment, and transfers the resulting evaporated CO2 to the compressor.

[0127] In one embodiment, the transcritical CO2 heat pump ejector performance enhancement device further includes a control module, a first control valve, and a second control valve; the transcritical CO2 heat pump ejector performance enhancement method provided in this application further includes:

[0128] The control module controls the first control valve and the second control valve according to the preset heat demand to distribute the flow.

[0129] Figure 5 This is a schematic flowchart of a method for improving the performance of a transcritical CO2 heat pump ejector according to an embodiment of this application, as shown below. Figure 5 As shown, the control module controls the first control valve and the second control valve according to a preset heat demand, including:

[0130] S501: If the heat demand satisfies the first constraint model, calculate the primary heat exchange flow rate and the secondary heat exchange flow rate according to the first flow rate calculation model;

[0131] S502: If the heat demand satisfies the second constraint model, calculate the primary heat exchange flow rate and the secondary heat exchange flow rate according to the second flow rate calculation model;

[0132] S503: Control the first control valve and the second control valve according to the primary heat exchange flow rate and the secondary heat exchange flow rate.

[0133] Specifically, after receiving the preset heat demand information, the control module will make a judgment using the system operating parameters:

[0134] When the heat demand meets the first constraint model, the high flow rate heating mode is entered. The control module determines the primary heat exchange flow rate and the secondary heat exchange flow rate based on the first flow rate calculation model, and outputs the corresponding control signals to drive the first control valve and the second control valve to adjust to the corresponding opening degree, so that more CO2 fluid enters the primary heat exchange loop to meet the larger high temperature heat demand.

[0135] When the heat demand meets the second constraint model, the system enters a low-flow heating mode. The control module determines the primary heat exchange flow rate and the secondary heat exchange flow rate based on the second flow calculation model, and outputs control signals to adjust the opening and closing states of the first control valve and the second control valve, so that more CO2 fluid enters the secondary heat exchange loop and effectively reduces the output heat.

[0136] Through the above design, the control module can automatically select the appropriate constraint model and calculate the optimal flow distribution scheme under different operating conditions, realizing dynamic adjustment between primary and secondary heat exchange, thereby matching the heat output with actual demand and effectively improving the overall energy efficiency and adaptability of the system.

[0137] In one embodiment, high-temperature heating is required during oil processing. However, oil fields are typically located in remote northern regions where winter temperatures are low, leading to problems such as excessively high pressure ratios, high exhaust temperatures, and poor performance of transcritical CO2 systems. Therefore, it is recommended to reduce the compressor exhaust pressure (only about 8 MPa is needed) to lower the exhaust temperature (below 120°C, thus ensuring the heating temperature is around 100°C). To ensure that heating energy is introduced into the liquid injector, a second-stage heating temperature (approximately 60°C) is provided.

[0138] The heat flow is allocated between the primary and secondary cycles according to different heat demands to achieve the optimal system effect. At the same time, the optimal exhaust pressure of the system is adjusted in combination with the internal performance of the system and the external environmental parameters.

[0139] In one embodiment, when there is a large-scale demand for high-temperature heat tracing in the petroleum process system, especially when the output temperature of high-temperature hot water needs to be increased in cold climates, the system needs to maintain a large heat output. In this case, the control module first calculates based on the actual detected water temperature demand signal and system operating parameters to determine whether the current state satisfies the first constraint model:

[0140]

[0141] In the formula, Q1 is the heat exchange required for primary heat exchange; Q2 is the heat exchange required for secondary heat exchange; A is an empirical coefficient; T water1 The temperature of the first circulating water; T water2 T0 represents the temperature of the second circulating water; T0 represents the ambient temperature.

[0142] If the above conditions are met, it indicates that the system should prioritize heating the primary circulation to obtain high-temperature water. The control module determines that it should switch to a high-flow-rate heating mode. At this time, the control module will call the first flow calculation model to calculate the allocation of primary and secondary heat exchange flow rates, and output control commands to the first and second control valves, thereby reducing the CO2 fluid flow rate to the secondary circulation and increasing the CO2 fluid flow rate to the primary circulation.

[0143] The first flow calculation model is shown below:

[0144]

[0145] In the formula, m1 is the primary heat exchange flow rate; m2 is the secondary heat exchange flow rate; E is an empirical coefficient; T water1 The temperature of the first circulating water; T water2 This refers to the temperature of the second circulating water.

[0146] The execution of the above process can significantly improve the volume distribution of high-temperature CO2 fluid in the primary circulation loop, thereby increasing the high-temperature heat exchange capacity in the first gas cooler, improving the stability and energy level of high-temperature hot water output, and ultimately meeting the demand for high-flow-rate and high-temperature heat energy supply in petroleum processes.

[0147] In one embodiment, when the petroleum process system is in a low-load operation phase, or when the ambient temperature is high and the demand for high-temperature hot water is reduced, the system does not need to maintain a large flow of high-temperature heating. The control module will determine whether the second heating condition is met based on the current operating status.

[0148] When the system parameters satisfy the second constraint model:

[0149]

[0150] In the formula, C is an empirical coefficient; T water1 The temperature of the first circulating water; T water2 The temperature of the second circulating water; T gs1 T represents the temperature at the outlet of the first gas cooler. gs2 This refers to the temperature at the outlet of the second gas cooler.

[0151] The control module determines that it should switch to a low-flow heating mode. At this time, it will recalculate the target flow rates of primary and secondary heat exchange by calling the second flow calculation model, and control the opening of the first and second control valves to reduce the flow rate of CO2 fluid to the primary circulation and increase the flow rate of CO2 fluid to the secondary circulation.

[0152] The second flow calculation model is shown below:

[0153]

[0154] In the formula, F is the empirical coefficient; T water1 The temperature of the first circulating water; T water2 T0 represents the temperature of the second circulating water; T0 represents the ambient temperature.

[0155] In this mode, although the total amount of refrigerant (CO2 working fluid) in the overall system cycle remains unchanged, more CO2 working fluid is introduced into the secondary heat exchange loop, where it is heat-exchanged by the second gas cooler to output medium-temperature hot water. Since the outlet temperature of the gas cooler in the secondary cycle is usually lower than that in the primary cycle, the overall heat output is effectively suppressed, which helps to prevent system overheating or energy waste, and improves operational economy and adjustment flexibility.

[0156] In one embodiment, the method for improving the performance of a transcritical CO2 heat pump ejector provided in this application further includes:

[0157] The control module regulates the optimal exhaust pressure for a single heat exchange.

[0158] Specifically, the control module is electrically connected to the compressor. Based on the preset heat demand information and the operating parameters inside and outside the system, it dynamically calculates and adjusts the exhaust pressure in the first-stage cycle and sends control commands to the compressor to achieve precise control of the compressor's exhaust pressure.

[0159] With the above settings, the control module can adaptively adjust the exhaust pressure of the primary heat exchange circuit under different ambient temperatures and operating conditions, thereby optimizing the pressure ratio during system operation and avoiding excessively high exhaust temperature and performance degradation caused by excessively high pressure ratio. This ensures that the transcritical CO2 heat pump ejector can still maintain a highly efficient and stable operating state under low ambient temperature conditions.

[0160] In one embodiment, the control module regulates the optimal venting pressure for one cycle of the system based on internal and external parameters, combined with the water supply demand temperature, to improve system performance and achieve optimal control. The optimal venting pressure regulation satisfies the following formula:

[0161]

[0162] In the formula, m, n, and q are empirical coefficients; T water1 The temperature of the first circulating water; T water2 T is the temperature of the second circulating water; T0 is the ambient temperature; T gs1 T represents the temperature at the outlet of the first gas cooler. gs2 This refers to the temperature at the outlet of the second gas cooler.

[0163] This application provides a method for improving the performance of a transcritical CO2 heat pump ejector. The method involves compressing received CO2 to a high-temperature, high-pressure supercritical state using a compressor and then transferring the supercritical CO2 to a first gas cooler. The first gas cooler allows the supercritical CO2 to exchange heat with first circulating water to obtain high-temperature water, and then transfers the heat-exchanged CO2 fluid to the ejector's inlet. A CO2 pump pressurizes a portion of the CO2 after heat exchange in the second gas cooler to obtain a mainstream fluid, which is then transferred to the ejector's mains inlet. Under the expansion and pressure reduction of the mainstream fluid, the ejector ejects the CO2 fluid from the first gas cooler, and after mixing, forms a confluence flow that flows into the second gas cooler. The second gas cooler allows the confluence flow to exchange heat a second time with second circulating water to obtain medium-temperature water. This method achieves efficient and stable operation of the transcritical CO2 heat pump system and improves waste heat utilization efficiency and heating efficiency.

[0164] This application solves the problem of performance degradation caused by excessive system pressure ratio and excessive exhaust temperature at low ambient temperatures by introducing an ejector into the transcritical CO2 cycle process, thus achieving efficient and stable operation of the system in winter conditions. By coupling the ejector circuit with the conventional throttling circuit, hot water of different temperature levels can be output simultaneously, realizing precise distribution and flexible supply of heat energy. Under the premise of ensuring stable operation, the waste heat of different temperature levels is fully utilized, significantly improving the overall energy efficiency of the transcritical CO2 heat pump system.

[0165] Figure 6 This is a schematic diagram of the physical structure of an electronic device provided in an embodiment of this application, as shown below. Figure 6 As shown, the electronic device may include a processor 601, a communication interface 602, a memory 603, and a communication bus 604. The processor 601, communication interface 602, and memory 603 communicate with each other via the communication bus 604. The processor 601 can call logical instructions in the memory 603 to execute the following methods: performing ashing processing on preprocessed cementing data to obtain ashing data; inputting the ashing data into a pre-generated cementing quality prediction model to obtain ashing prediction values; the cementing quality prediction model is trained using the main control factors of cementing quality; the main control factors are determined from acquired historical cementing data; and performing whitening and restoration processing on the ashing prediction values ​​to obtain actual prediction values.

[0166] Furthermore, the logical instructions in the aforementioned memory 603 can be implemented as software functional units and, when sold or used as independent products, can be stored in a computer-readable storage medium. Based on this understanding, the technical solution of this application, in essence, or the part that contributes to the prior art, or a part of the technical solution, can be embodied in the form of a software product. This computer software product is stored in a storage medium and includes several instructions to cause a computer device (which may be a personal computer, a top-drive control center server, or a network device, etc.) to execute all or part of the steps of the methods described in the various embodiments of this application. The aforementioned storage medium includes various media capable of storing program code, such as USB flash drives, portable hard drives, read-only memory (ROM), random access memory (RAM), magnetic disks, or optical disks.

[0167] This embodiment discloses a computer program product, which includes a computer program stored on a computer-readable storage medium. The computer program includes program instructions, and when the program instructions are executed by the computer, the computer can execute the methods provided in the above-described method embodiments, such as: performing ashing processing on preprocessed cementing data to obtain ashing data; inputting the ashing data into a pre-generated cementing quality prediction model to obtain ashing prediction values; the cementing quality prediction model is trained using the main control factors of cementing quality; the main control factors are determined from acquired historical cementing data; and performing whitening and restoration processing on the ashing prediction values ​​to obtain actual prediction values.

[0168] This embodiment provides a computer-readable storage medium storing a computer program that causes the computer to execute the methods provided in the above-described method embodiments. For example, the methods include: performing ashing processing on preprocessed cementing data to obtain ashing data; inputting the ashing data into a pre-generated cementing quality prediction model to obtain ashing prediction values; the cementing quality prediction model is trained using the main control factors of cementing quality; the main control factors are determined from acquired historical cementing data; and performing whitening and restoration processing on the ashing prediction values ​​to obtain actual prediction values.

[0169] Those skilled in the art will understand that embodiments of this application can be provided as methods, systems, or computer program products. Therefore, this application can take the form of a completely hardware embodiment, a completely software embodiment, or an embodiment combining software and hardware aspects. Furthermore, this application can take the form of a computer program product embodied on one or more computer-usable storage media (including but not limited to disk storage, CD-ROM, optical storage, etc.) containing computer-usable program code.

[0170] This application is described with reference to flowchart illustrations and / or block diagrams of methods, apparatus (systems), and computer program products according to embodiments of this application. It will be understood that each block of the flowchart illustrations and / or block diagrams, and combinations of blocks in the flowchart illustrations and / or block diagrams, can be implemented by computer program instructions. These computer program instructions can be provided to a processor of a general-purpose computer, special-purpose computer, embedded processor, or other programmable data processing apparatus to produce a machine, such that the instructions, which execute via the processor of the computer or other programmable data processing apparatus, generate instructions for implementing the flowchart... Figure 1 One or more processes and / or boxes Figure 1 A device that provides the functions specified in one or more boxes.

[0171] These computer program instructions may also be stored in a computer-readable storage medium that can direct a computer or other programmable data processing device to function in a particular manner, such that the instructions stored in the computer-readable storage medium produce an article of manufacture including instruction means, which are implemented in a process Figure 1 One or more processes and / or boxes Figure 1 The function specified in one or more boxes.

[0172] These computer program instructions may also be loaded onto a computer or other programmable data processing equipment to cause a series of operational steps to be performed on the computer or other programmable equipment to produce a computer-implemented process, thereby providing instructions that execute on the computer or other programmable equipment for implementing the process. Figure 1 One or more processes and / or boxes Figure 1 The steps of the function specified in one or more boxes.

[0173] In the description of this specification, the references to terms such as "an embodiment," "a specific embodiment," "some embodiments," "for example," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0174] The specific embodiments described above further illustrate the purpose, technical solution, and beneficial effects of this application. It should be understood that the above descriptions are merely specific embodiments of this application and are not intended to limit the scope of protection of this application. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the scope of protection of this application.

Claims

1. A device for improving the performance of a transcritical CO2 heat pump ejector, characterized in that, include: Compressor, first gas cooler, second gas cooler, ejector and CO2 pump; The compressor is used to compress the received CO2 to a supercritical state with high temperature and high pressure and to transfer the supercritical CO2 to the first gas cooler. The first gas cooler is used to exchange heat between the supercritical CO2 and the first circulating water to obtain high-temperature water, and to transfer the heat-exchanged CO2 fluid to the ejector inlet of the ejector. The CO2 pump is used to pressurize a portion of the CO2 after heat exchange in the second gas cooler to obtain the mainstream fluid and to transmit the mainstream fluid to the mainstream inlet of the ejector; The outlet of the ejector is connected to the second gas cooler. The ejector is used to eject CO2 fluid from the first gas cooler under the expansion and pressure reduction of the mainstream fluid, and form a confluence flow into the second gas cooler after injection and mixing. The second gas cooler is used to perform secondary heat exchange between the confluence stream and the second circulating water to obtain medium-temperature water.

2. The transcritical CO2 heat pump ejector performance enhancement device according to claim 1, characterized in that, Also includes: Throttling valve and air source evaporator; The throttling valve is used to throttle and reduce the pressure of another portion of CO2 after heat exchange in the second gas cooler. The air source evaporator is used to exchange heat between the CO2 from the throttle valve and the external environment, and to transfer the resulting evaporated CO2 to the compressor.

3. The transcritical CO2 heat pump ejector performance enhancement device according to claim 2, characterized in that, Also includes: Control module, first control valve and second control valve; The control module is electrically connected to the first control valve and the second control valve; the first control valve is connected to the inlet of the throttle valve, and the second control valve is connected to the inlet of the CO2 pump. The control module is used to control the first control valve and the second control valve according to the preset heat demand in order to distribute the flow.

4. The transcritical CO2 heat pump ejector performance enhancement device according to claim 3, characterized in that, The control module is specifically used for: If the heat demand satisfies the first constraint model, calculate the primary heat exchange flow rate and the secondary heat exchange flow rate according to the first flow rate calculation model. If the heat demand satisfies the second constraint model, calculate the primary heat exchange flow rate and the secondary heat exchange flow rate according to the second flow rate calculation model. The first control valve and the second control valve are controlled according to the primary heat exchange flow rate and the secondary heat exchange flow rate.

5. The transcritical CO2 heat pump ejector performance enhancement device according to claim 3, characterized in that, The control module is also used to control the optimal exhaust pressure for a single heat exchange.

6. The transcritical CO2 heat pump ejector performance enhancement device according to claim 1, characterized in that, The high-temperature water is 120°C; the medium-temperature water is 60°C.

7. A method for improving the performance of a transcritical CO2 heat pump ejector, applied to the transcritical CO2 heat pump ejector performance improvement apparatus as described in any one of claims 1-6, characterized in that, include: The compressor compresses the received CO2 to a supercritical state with high temperature and high pressure and then transfers the supercritical CO2 to the first gas cooler. The first gas cooler allows the supercritical CO2 to exchange heat with the first circulating water once to obtain high-temperature water, and then transmits the heat-exchanged CO2 fluid to the ejector inlet. The CO2 pump pressurizes a portion of the CO2 after heat exchange in the second gas cooler to obtain the mainstream fluid and then transmits the mainstream fluid to the mainstream inlet of the ejector. The injector, under the expansion and pressure reduction of the mainstream fluid, draws CO2 fluid from the first gas cooler, and after injection and mixing, forms a confluence flow that flows into the second gas cooler; The second gas cooler allows the confluence stream to exchange heat with the second circulating water a second time to obtain medium-temperature water.

8. The method for improving the performance of a transcritical CO2 heat pump ejector according to claim 7, characterized in that, The aforementioned transcritical CO2 heat pump ejector performance enhancement device also includes a throttling valve and an air source evaporator; The method for improving the performance of transcritical CO2 heat pump ejectors also includes: The throttling valve reduces the pressure of another portion of CO2 after heat exchange in the second gas cooler. The air source evaporator allows CO2 from the throttle valve to exchange heat with the external environment and transfers the resulting evaporated CO2 to the compressor.

9. The method for improving the performance of a transcritical CO2 heat pump ejector according to claim 8, characterized in that, The transcritical CO2 heat pump ejector performance enhancement device further includes a control module, a first control valve, and a second control valve; the transcritical CO2 heat pump ejector performance enhancement method further includes: The control module controls the first control valve and the second control valve according to the preset heat demand to distribute the flow.

10. The method for improving the performance of a transcritical CO2 heat pump ejector according to claim 9, characterized in that, The control module controls the first control valve and the second control valve according to a preset heat demand, including: If the heat demand satisfies the first constraint model, calculate the primary heat exchange flow rate and the secondary heat exchange flow rate according to the first flow rate calculation model. If the heat demand satisfies the second constraint model, calculate the primary heat exchange flow rate and the secondary heat exchange flow rate according to the second flow rate calculation model. The first control valve and the second control valve are controlled according to the primary heat exchange flow rate and the secondary heat exchange flow rate.

11. The method for improving the performance of a transcritical CO2 heat pump ejector according to claim 9, characterized in that, Also includes: The control module regulates the optimal exhaust pressure for a single heat exchange.

12. A computer device, comprising a memory, a processor, and a computer program stored in the memory and executable on the processor, characterized in that, When the processor executes the computer program, it implements the method according to any one of claims 7 to 11.

13. A computer-readable storage medium, characterized in that, The computer-readable storage medium stores a computer program that, when executed by a processor, implements the method according to any one of claims 7 to 11.

14. A computer program product, characterized in that, The computer program product includes a computer program that, when executed by a processor, implements the method according to any one of claims 7 to 11.

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