Ejector with flash vessel

Abstract

The application belongs to the technical field of heat pump systems, and particularly relates to an ejector type air supplementing and enthalpy increasing system with a flash tank. Only the medium-pressure refrigerant vapor separated by the flash tank is used to supplement the air of the compressor, the expansion work loss generated in the throttling and pressure reducing process is not completely recycled, the effect of improving the suction pressure of the compressor is not obvious, and the energy utilization efficiency of the system still has a large space for improvement. In view of the above problems, the application provides an ejector type air supplementing and enthalpy increasing system with a flash tank. The structure comprises a heating system and a refrigerating system, and the heating system and the refrigerating system are respectively connected with the compressor through a reversing valve to realize switching connection. The most core improvement of the application is that an ejector is introduced. By integrating the ejector, the flash tank and the multi-way control valve group in the refrigerant circuit, the flow path and energy distribution of the refrigerant under different modes are optimized, the throttling loss is effectively recycled, the suction pressure of the compressor is improved, and the energy consumption of the heat pump system in operation is significantly reduced.

Description

Technical Field

[0001] This invention belongs to the field of heat pump system technology, specifically relating to an ejector-type gas replenishment and enthalpy enhancement system with a flash evaporator. Background Technology

[0002] With increasing societal demands for energy conservation and emission reduction, heat pump air conditioning systems are widely used in various fields due to their high energy conversion efficiency. Especially in the field of new energy vehicles, heat pump air conditioning systems are crucial for extending driving range in winter. However, traditional heat pump systems face problems such as low evaporation pressure, large suction volume, high compression ratio, and excessively high exhaust temperature when heating in low-temperature environments, leading to a sharp decline in system heating capacity and an unsatisfactory coefficient of performance (COP).

[0003] To improve the operating efficiency of heat pumps under extreme conditions, quasi-two-stage compression (i.e., enthalpy-increasing gas injection) technology has been proposed and applied. This technology increases the compressor's discharge volume by injecting medium-pressure refrigerant vapor into the compressor's intermediate cavity, thereby improving heating capacity and energy efficiency ratio. Existing enthalpy-increasing gas injection systems mostly use flash evaporators for gas-liquid separation and directly feed the separated gas into the compressor. While this method can improve system performance to some extent, the energy loss during the throttling process is not effectively recovered, and the pressure of the injected gas is limited, resulting in a minimal increase in the compressor's suction pressure. Therefore, there is still considerable room for improvement in the system's energy utilization efficiency.

[0004] To address the aforementioned issues, Chinese invention patent CN106918161A discloses a gas injection device and a heat pump system incorporating it. This solution, by setting up a gas-liquid separation chamber, directly introduces the separated gaseous refrigerant into the compressor's gas injection port, aiming to adjust the gas injection volume to reduce exhaust temperature and improve the system's heating performance in low-temperature environments. However, this technical solution still suffers from low energy utilization efficiency in practical applications. Specifically, this patent does not include an ejector; its gas injection enthalpy-increasing process relies solely on the natural flow of medium-pressure refrigerant vapor separated by the flash evaporator into the compressor's gas injection port. While this passive gas injection method can increase the compressor's exhaust volume to some extent, the expansion work loss generated during the throttling and pressure reduction process is completely unrecovered, and the medium-pressure vapor in the flash evaporator has a low energy grade, limiting its effect on increasing the compressor's suction pressure. More critically, in this design, a large amount of high-pressure liquid refrigerant flowing from the condenser is directly depressurized and enters the flash evaporator through a throttling element. A significant amount of usable energy generated during the throttling process is wasted, making it difficult to substantially improve the overall energy efficiency of the system. Furthermore, during variable operating conditions, the refrigerant supply pressure cannot be actively adjusted, making it difficult to maintain the optimal intermediate pressure, further restricting the full realization of system performance.

[0005] As a pressure boosting device that requires no additional energy consumption, the ejector can entrain low-pressure fluid using the jetting action of high-pressure fluid, achieving energy exchange and pressure boosting during the mixing process. This provides an effective technical approach for recovering throttling losses and optimizing the gas injection enthalpy enhancement process. How to rationally introduce an ejector and optimize the system configuration based on existing gas injection enthalpy enhancement systems to achieve effective recovery of throttling energy and active boosting of gas injection pressure, thereby significantly improving the energy utilization efficiency of heat pump systems, has become a technical problem urgently needing to be solved by those skilled in the art. Summary of the Invention

[0006] The existing technology has the following problems: relying solely on the medium-pressure refrigerant vapor separated by the flash evaporator to replenish the compressor, the expansion work loss generated during the throttling and pressure reduction process is not fully recovered and utilized, resulting in an insignificant effect on increasing the compressor's suction pressure, and the system's energy utilization efficiency still has considerable room for improvement. To address these problems, this invention provides an ejector-type gas replenishment and enthalpy enhancement system with a flash evaporator. Its structure includes a heating system and a refrigeration system, which can be freely switched between modes via a reversing valve. The condenser, evaporator, reversing valve, compressor, and gas-liquid separator in the ejector-type gas replenishment and enthalpy enhancement system are functional components shared by both the heating and refrigeration systems (the fluid inlet and outlet of each functional component are determined according to the refrigerant flow direction in the pipeline; the outlet in the same direction as the refrigerant flow is the fluid inlet, and the outlet in the opposite direction is the fluid outlet).

[0007] The heating system is formed by connecting the compressor, reversing valve, condenser, flash evaporator, ejector, gas-liquid separator, reversing valve, and compressor in sequence through pipelines to form a closed loop main circuit.

[0008] An electronic expansion valve is installed on the connecting pipe between the condenser and the flash evaporator. A branch pipe is installed between the electronic expansion valve and the condenser. One end of the branch pipe is connected to the closed loop main circuit, and the other end of the branch pipe is connected to the primary inlet of the ejector. The exhaust port of the flash evaporator is connected to the secondary inlet of the ejector. The nozzle of the ejector is connected to the inlet of the gas-liquid separator. The exhaust port of the gas-liquid separator is connected to the gas supply port of the compressor.

[0009] Solenoid valve three and solenoid valve four are respectively installed on the pipelines connecting the condenser and flash evaporator to the ejector. The drain ports at the bottom of gas-liquid separator one and flash evaporator are respectively connected to the liquid inlet of evaporator through pipelines. Electronic expansion valve two and electronic expansion valve four are respectively installed on the connecting pipelines between gas-liquid separator one, flash evaporator and evaporator.

[0010] The exhaust port of the evaporator is connected to branch line one and branch line two through a pipeline. The end of branch line one is connected to the air inlet of gas-liquid separator two. The connecting pipeline between the flash evaporator and the ejector is connected to the end of branch line two. The connection point is located on the connecting pipeline between solenoid valve four and the ejector. Solenoid valve five is installed on branch line two.

[0011] Preferably, the refrigeration system is a closed-loop main circuit II formed by connecting the compressor, reversing valve, evaporator, electronic expansion valve III, condenser, reversing valve, and compressor in that order.

[0012] A solenoid valve is installed on the connecting pipe between the evaporator and the electronic expansion valve three, and a solenoid valve is installed on the connecting pipe between the electronic expansion valve three and the condenser.

[0013] The exhaust port of the condenser is connected to the inlet of the second gas-liquid separator, and the exhaust port of the second gas-liquid separator is connected to the inlet of the compressor.

[0014] Preferably, the exhaust port of the gas-liquid separator is located above the maximum liquid level line defined within the gas-liquid separator.

[0015] Preferably, the air inlet of the second gas-liquid separator is located above the maximum liquid level line defined within the second gas-liquid separator.

[0016] Preferably, the reversing valve is a four-way reversing valve.

[0017] Preferably, the vent of the flash evaporator is located above the maximum liquid level line defined inside the flash evaporator.

[0018] Preferably, the air inlet of the gas-liquid separator is located above the maximum liquid level line defined within the gas-liquid separator.

[0019] Preferably, the exhaust port of the gas-liquid separator is located above the maximum liquid level line defined within the gas-liquid separator.

[0020] Preferably, electronic expansion valve one, electronic expansion valve two, electronic expansion valve three and electronic expansion valve four are all throttling and pressure-reducing expansion valves.

[0021] Preferably, the solenoid valve 1, solenoid valve 2, solenoid valve 3, solenoid valve 4, solenoid valve 5, electronic expansion valve 1, electronic expansion valve 2, electronic expansion valve 3, electronic expansion valve 4, and the directional valve are all controlled by the controller to open or close the valves.

[0022] The ejector-type enthalpy-increasing system with flash evaporator provided by this invention is a dual-mode heat pump air conditioning system capable of efficient operation in both cooling and heating modes. By integrating an ejector, flash evaporator, and multi-channel control valve assembly into the refrigerant circuit, this system optimizes the refrigerant flow path and energy distribution in different modes, effectively recovers throttling losses, and increases the compressor's suction pressure, thereby significantly improving the system's COP (coefficient of performance) and significantly reducing the energy consumption of the heat pump system.

[0023] This system mainly consists of the following core components and piping connections (as shown in the instruction manual). Figure 1 (as shown)

[0024] Compressor: The core of the system, responsible for compressing the refrigerant and switching between cooling and heating modes through a reversing valve (four-way).

[0025] Reversing valve (four-way): controls the direction of refrigerant flow and enables the switching of functions between the condenser and evaporator.

[0026] Condenser: In heating mode, it acts as a condenser, releasing heat into the vehicle; in cooling mode, it acts as an auxiliary circuit component.

[0027] Evaporator: In cooling mode, it acts as a condenser, releasing heat to the outside; in heating mode, it acts as an evaporator, extracting heat from the external environment.

[0028] Flash evaporator: Used to separate gas and liquid refrigerant, providing high-pressure liquid refrigerant to the ejector and low-temperature, low-pressure refrigerant to the evaporator.

[0029] The ejector (which may be the ejector structure disclosed in Chinese invention patents CN121539513A and CN120062165A, or a conventional commercially available ejector, such as the Carrier centrifuge ejector, model: 02XR54018001 or 02XR54018101): utilizes the jetting action of high-pressure liquid refrigerant to entrain low-pressure gaseous refrigerant from the evaporator, thereby increasing the compressor suction pressure and reducing the compression ratio.

[0030] Gas-liquid separator 1 and gas-liquid separator 2: Separate liquid from the refrigerant to prevent liquid slugging from damaging the compressor.

[0031] Electronic expansion valves one through four: precisely control refrigerant flow and adjust the system's cooling / heating capacity.

[0032] Solenoid valves one through five: control the opening and closing of the refrigerant passage to achieve flow path switching in different modes.

[0033] The various functional components are connected by pipelines to form a complete closed loop of the refrigeration or heating system, and the refrigeration or heating system can be switched freely by valve switching.

[0034] The working principle and process of this system in cooling mode (as shown in the instruction manual) Figure 2 (as shown)

[0035] (1) Compressor exhaust: The high-temperature and high-pressure gaseous refrigerant generated by the compressor flows to the evaporator through the four-way reversing valve.

[0036] (2) Condensation and heat release: In the evaporator, the refrigerant releases heat to the outside environment of the vehicle and condenses into high-pressure liquid refrigerant.

[0037] (3) Throttling: After the high-pressure liquid refrigerant is throttled and depressurized by solenoid valve two and electronic expansion valve three, it becomes a low-temperature, low-pressure gas-liquid mixture.

[0038] (4) Evaporation inside the vehicle: The gas-liquid mixture after throttling enters the condenser through the solenoid valve and exchanges heat with the air inside the vehicle through convection. It absorbs the heat of the air inside the vehicle, and the liquid part vaporizes into gas, eventually forming low-temperature and low-pressure steam.

[0039] (5) Gas-liquid separation: The low-temperature and low-pressure refrigerant vapor flowing out of the condenser enters the second gas-liquid separator. The separated pure gaseous refrigerant flows into the compressor inlet through the four-way reversing valve.

[0040] (6) Compressor intake: The gaseous refrigerant separated by the gas-liquid separator is drawn into the compressor, compressed and discharged as high-temperature and high-pressure gas, thus completing the refrigeration cycle.

[0041] The working principle and process of this system in heating mode (as per the instruction manual) Figure 3 (as shown)

[0042] Compressor exhaust: The compressor adiabatically compresses low-pressure steam to form high-temperature, high-pressure steam, which is then discharged from its exhaust port.

[0043] Four-way reversing valve flow path: High-temperature and high-pressure steam enters the four-way reversing valve. In heating mode, the valve core is in the "heating position" to guide the refrigerant to the condenser.

[0044] In-vehicle condensation and heat release: High-temperature and high-pressure steam enters the condenser and exchanges heat with the air inside the vehicle through forced convection, and the high-temperature and high-pressure steam is condensed into medium-temperature and high-pressure liquid refrigerant.

[0045] Branch flow splitting: The condensed medium-temperature, high-pressure liquid refrigerant is split into two paths. One path of refrigerant flows through the branch pipe and solenoid valve 3, entering the ejector from the primary inlet of the ejector; the other path of refrigerant flows through the closed-loop main circuit (also known as the enthalpy-increasing circuit) and then through the electronic expansion valve 1 before entering the flash evaporator.

[0046] Throttling and flashing in the enthalpy-increasing circuit: The medium-temperature, high-pressure liquid refrigerant expands and depressurizes through the electronic expansion valve to form a gas-liquid mixture; the gas-liquid mixture enters the flash evaporator for gas-liquid separation, forming medium-pressure saturated vapor inside the flash evaporator. The medium-pressure saturated vapor enters the ejector through the secondary inlet of the ejector via the solenoid valve; the remaining liquid refrigerant expands and depressurizes through the electronic expansion valve and enters the evaporator.

[0047] Ejector enthalpy and pressure boosting: The medium-temperature, high-pressure liquid refrigerant flowing into the ejector from the primary inlet is ejected at high speed through the ejector nozzle, forming a low-pressure zone at the nozzle outlet. The medium-pressure saturated vapor separated from the flash evaporator is "drawn" into the ejector's mixing chamber from the secondary inlet. After the medium-temperature, high-pressure liquid refrigerant and medium-pressure saturated vapor are fully mixed in the ejector's mixing chamber, they are decelerated and pressurized in the diffuser section of the ejector to form medium-pressure gas. This gas then enters the first gas-liquid separator. After gas-liquid separation in the first gas-liquid separator, the gas in the first gas-liquid separator is used as makeup gas and directly enters the compressor's intermediate chamber through the compressor's makeup gas port, which can significantly increase the compressor's discharge capacity. This process recovers the energy lost during the throttling and pressure-reducing expansion process and provides the compressor with additional medium-pressure makeup gas, significantly improving its heating capacity.

[0048] External evaporation heat absorption: The liquid refrigerant at the bottom of the flash evaporator forms a low-temperature, low-pressure gas-liquid mixture after passing through the electronic expansion valve. The gas-liquid mixture enters the evaporator through the pipeline, exchanges heat with the ambient air outside the vehicle, and vaporizes into a low-temperature, low-pressure gas.

[0049] Main airflow convergence: The liquid at the bottom of the gas-liquid separator expands and depressurizes through the electronic expansion valve to form a low-temperature, low-pressure gas-liquid mixture, which then enters the evaporator through the liquid inlet.

[0050] The low-pressure steam generated by the evaporator is partially diverted through solenoid valve 5 into the ejector via the secondary inlet, while the remaining portion directly enters the gas-liquid separator 2 via the four-way reversing valve. The gas-liquid separator 2 separates incompletely vaporized droplets, ensuring that the gas entering the compressor is pure gaseous refrigerant. This pure gaseous refrigerant is then compressed by the compressor to form high-temperature, high-pressure gas, which flows back into the condenser via the four-way reversing valve, thus forming a heating cycle.

[0051] Compared with the prior art, the beneficial effects of the present invention are as follows:

[0052] (1) Significantly improve energy utilization efficiency and achieve effective recovery of throttling losses.

[0053] The core improvement of this invention lies in the introduction of an ejector and its organic integration with the flash evaporator circuit. In heating mode, the high-pressure liquid refrigerant flowing from the condenser is not entirely throttled directly, but is divided into two paths: one serves as the primary flow (power fluid) of the ejector, and the other, after being throttled by an electronic expansion valve, enters the flash evaporator. This invention cleverly uses the medium-pressure saturated vapor separated from the flash evaporator and the gas from the evaporator as the secondary flow of the ejector. The primary flow expands and accelerates in the ejector nozzle, converting pressure energy into kinetic energy, forming a local low pressure, thereby entraining (ejecting) the secondary flow (i.e., the medium-pressure refrigerant vapor separated from the flash evaporator and the gas from the evaporator). The two fluids are fully mixed in the ejector mixing chamber and decelerated and pressurized in the diffuser section, ultimately forming a medium-pressure gas that is fed into the compressor. This process effectively recovers the energy (i.e., expansion work) that was originally lost during the throttling process of the electronic expansion valve, and feeds the low-grade flash steam pressure into the compressor, which greatly improves the system efficiency and thus significantly improves the coefficient of performance (COP) of the heat pump system in low-temperature environments.

[0054] (2) Actively increase the gas supply pressure and compressor suction pressure to reduce compressor energy consumption.

[0055] Compared to the passive refrigerant replenishment method in prior art CN106918161A, which relies solely on the medium-pressure vapor naturally separated by the flash evaporator, this invention utilizes the pressurization effect of the ejector to achieve a higher refrigerant pressure entering the compressor's replenishment port, thus realizing active refrigerant replenishment and enthalpy enhancement. The higher replenishment pressure more effectively increases the compressor's discharge volume and directly affects the compressor's compression chamber, reducing the compressor's pressure ratio and decreasing the input power required by the compressor motor. Simultaneously, the pressurized gas mixture formed after the ejector operates is not only used for replenishment but also contributes some of its energy to increasing the pressure on the low-pressure side of the system. This design effectively increases the compressor's suction pressure, further reducing compressor power consumption and achieving a significant leap in overall system energy efficiency.

[0056] (3) Optimize system circulation to improve low-temperature heating capacity and operational reliability.

[0057] In heating mode, this invention optimizes refrigerant distribution into the evaporator through the coordinated control of electronic expansion valves two and four, and solenoid valve five. The liquid at the bottom of the gas-liquid separator enters the evaporator after being throttled by electronic expansion valve four, merging with the refrigerant flowing out from the bottom of the flash evaporator, fully utilizing every part of the system's cooling capacity. More importantly, this invention incorporates solenoid valve five and a bypass branch, allowing a portion of the low-pressure vapor generated in the evaporator to be directly entrained by the ejector and participate in the energy recovery cycle, while the other portion passes through gas-liquid separator two to ensure that only pure gaseous refrigerant enters the compressor. This dual-path return gas design not only ensures the reliability of compressor operation (preventing liquid slugging) but also maximizes the recovery of energy from the evaporator outlet vapor, further expanding the system's stable operating range under extreme low-temperature conditions.

[0058] (4) Achieve efficient operation in both cooling and heating modes with high system integration.

[0059] This invention constructs a complete dual-mode heat pump air conditioning system through the rational configuration of a reversing valve (four-way valve) and multiple solenoid valves. In cooling mode, the system can switch to a conventional cooling cycle to ensure efficient satisfaction of the vehicle's cooling needs under high-temperature conditions; in heating mode, it switches to the aforementioned unique ejector-type enthalpy-increasing cycle. This design allows a single system to operate efficiently under various conditions throughout the year without the need for additional complex components. It boasts advantages such as high integration, flexible control, and strong adaptability, making it particularly suitable for the new energy vehicle sector, where energy efficiency and space requirements are extremely high. Attached Figure Description

[0060] Figure 1 This is a schematic diagram of an ejector-type gas replenishment and enthalpy enhancement system with a flash generator provided by the present invention.

[0061] Figure 2 This is a schematic diagram of the refrigeration system in an ejector-type gas replenishment and enthalpy enhancement system with a flash generator provided by the present invention.

[0062] Figure 3 This is a schematic diagram of the heating system in an ejector-type gas replenishment and enthalpy enhancement system with a flash igniter provided by the present invention. Detailed Implementation

[0063] The present invention will be described in detail below with reference to embodiments. However, it should be understood that the following embodiments are merely illustrative examples of implementation of the present invention and are not intended to limit the scope of the present invention.

[0064] As per the instruction manual Figures 1-3As shown, this invention provides an ejector-type gas replenishment enthalpy enhancement system with a flash evaporator. Its structure includes a heating system and a cooling system, which can be freely switched between modes through a reversing valve. The condenser, evaporator, reversing valve, compressor, and gas-liquid separator in the ejector-type gas replenishment enthalpy enhancement system are functional components shared by the heating system and the cooling system.

[0065] The heating system is formed by connecting the compressor, reversing valve, condenser, flash evaporator, ejector (which can be a Carrier centrifugal ejector, model: 02XR54018001), gas-liquid separator, reversing valve, and compressor in sequence through pipelines to form a closed loop main circuit.

[0066] An electronic expansion valve is installed on the connecting pipe between the condenser and the flash evaporator. A branch pipe is installed between the electronic expansion valve and the condenser. One end of the branch pipe is connected to the closed loop main circuit, and the other end of the branch pipe is connected to the primary inlet of the ejector. The exhaust port of the flash evaporator is connected to the secondary inlet of the ejector. The nozzle of the ejector is connected to the inlet of the gas-liquid separator. The exhaust port of the gas-liquid separator is connected to the gas supply port of the compressor.

[0067] Solenoid valve three and solenoid valve four are respectively installed on the pipelines connecting the condenser and flash evaporator to the ejector. The drain ports at the bottom of gas-liquid separator one and flash evaporator are respectively connected to the liquid inlet of evaporator through pipelines. Electronic expansion valve two and electronic expansion valve four are respectively installed on the connecting pipelines between gas-liquid separator one, flash evaporator and evaporator.

[0068] The exhaust port of the evaporator is connected to branch line one and branch line two through a pipeline. The end of branch line one is connected to the air inlet of gas-liquid separator two. The connecting pipeline between the flash evaporator and the ejector is connected to the end of branch line two. The connection point is located on the connecting pipeline between solenoid valve four and the ejector. Solenoid valve five is installed on branch line two.

[0069] In one specific implementation, the refrigeration system is a closed-loop main circuit II formed by sequentially connecting the compressor, reversing valve, evaporator, electronic expansion valve, condenser, reversing valve, and compressor.

[0070] A solenoid valve is installed on the connecting pipe between the evaporator and the electronic expansion valve three, and a solenoid valve is installed on the connecting pipe between the electronic expansion valve three and the condenser.

[0071] The exhaust port of the condenser is connected to the inlet of the second gas-liquid separator, and the exhaust port of the second gas-liquid separator is connected to the inlet of the compressor.

[0072] In one specific implementation, the exhaust port of the gas-liquid separator two is located above the maximum liquid level line defined within the gas-liquid separator two.

[0073] In one specific implementation, the air inlet of the second gas-liquid separator is located above the maximum liquid level line defined within the second gas-liquid separator.

[0074] In one specific implementation, the reversing valve is a four-way reversing valve.

[0075] In one specific implementation, the vent of the flash generator is located above the maximum liquid level line defined within the flash generator.

[0076] In one specific embodiment, the air inlet of the gas-liquid separator is located above the maximum liquid level line defined within the gas-liquid separator.

[0077] In one specific embodiment, the exhaust port of the gas-liquid separator is located above the maximum liquid level line defined within the gas-liquid separator.

[0078] In one specific implementation, electronic expansion valve one, electronic expansion valve two, electronic expansion valve three and electronic expansion valve four are all throttling and pressure-reducing expansion valves.

[0079] In one specific implementation, solenoid valve 1, solenoid valve 2, solenoid valve 3, solenoid valve 4, solenoid valve 5, electronic expansion valve 1, electronic expansion valve 2, electronic expansion valve 3, electronic expansion valve 4, and the directional valve are all controlled by a controller to open and close the valves.

[0080] The working principle and process of the above-mentioned ejector-type gas injection and enthalpy enhancement system with flash emitter in refrigeration mode (as shown in the instruction manual). Figure 2 (as shown)

[0081] (1) Compressor exhaust: The high-temperature and high-pressure (2.0-2.8MPa, 80-120℃) gaseous refrigerant generated by the compressor flows to the evaporator through the four-way reversing valve.

[0082] (2) Condensation and heat release: In the evaporator, the refrigerant releases heat to the outside environment of the vehicle and condenses into high-pressure liquid refrigerant.

[0083] (3) Throttling: After the high-pressure liquid refrigerant is throttled and depressurized by the second solenoid valve and the third electronic expansion valve, it becomes a low-temperature and low-pressure (0.15-0.35MPa, temperature 5-10℃ lower than ambient temperature) gas-liquid mixture.

[0084] (4) Evaporation inside the vehicle: The gas-liquid mixture after throttling enters the condenser through the solenoid valve and exchanges heat with the air inside the vehicle through convection. It absorbs the heat of the air inside the vehicle, and the liquid part vaporizes into gas, eventually forming low-temperature and low-pressure steam.

[0085] (5) Gas-liquid separation: The low-temperature and low-pressure refrigerant vapor flowing out of the condenser enters the second gas-liquid separator. The separated pure gaseous refrigerant flows into the compressor inlet through the four-way reversing valve.

[0086] (6) Compressor intake: The gaseous refrigerant separated by the gas-liquid separator is drawn into the compressor, compressed and discharged as high-temperature and high-pressure gas, thus completing the refrigeration cycle.

[0087] The working principle and process of the above-mentioned ejector-type gas replenishment and enthalpy enhancement system with flash evaporator in heating mode (as shown in the instruction manual). Figure 3 (as shown)

[0088] Compressor exhaust: The compressor adiabatically compresses low-pressure steam to form high-temperature and high-pressure (2.0-2.8MPa, 80-120℃) steam, which is then discharged from its exhaust port.

[0089] Four-way reversing valve flow path: High-temperature and high-pressure steam enters the four-way reversing valve. In heating mode, the valve core is in the "heating position" to guide the refrigerant to the condenser.

[0090] In-vehicle condensation and heat release: High-temperature and high-pressure steam enters the condenser and exchanges heat with the air inside the vehicle through forced convection, and the high-temperature and high-pressure steam is condensed into medium-temperature and high-pressure liquid refrigerant.

[0091] Branch flow splitting: The condensed medium-temperature, high-pressure liquid refrigerant is split into two paths. One path of refrigerant flows through the branch pipe and solenoid valve 3, entering the ejector from the primary inlet of the ejector; the other path of refrigerant flows through the closed-loop main circuit (also known as the enthalpy-increasing circuit) and then through the electronic expansion valve 1 before entering the flash evaporator.

[0092] Throttling and flashing in the enthalpy-increasing circuit: The medium-temperature, high-pressure liquid refrigerant expands and depressurizes (0.15-0.35MPa) through the electronic expansion valve to form a gas-liquid mixture; the gas-liquid mixture enters the flash evaporator for gas-liquid separation, forming medium-pressure (1-1.6MPa) saturated vapor inside the flash evaporator. The medium-pressure saturated vapor enters the ejector through the secondary inlet of the ejector via the solenoid valve; the remaining liquid refrigerant expands and depressurizes through the electronic expansion valve and then enters the evaporator.

[0093] Ejector enthalpy and pressure boosting: The medium-temperature, high-pressure liquid refrigerant flowing into the ejector from the primary inlet is ejected at high speed through the ejector nozzle, forming a low-pressure zone at the nozzle outlet. The medium-pressure saturated vapor separated from the flash generator is "drawn" into the ejector's mixing chamber from the secondary inlet. After the medium-temperature, high-pressure liquid refrigerant and medium-pressure saturated vapor are fully mixed in the ejector's mixing chamber, they are decelerated and pressurized in the diffuser section of the ejector to form medium-pressure gas (0.9-1.7 MPa). This gas then enters the first gas-liquid separator. After gas-liquid separation in the first gas-liquid separator, the gas in the first gas-liquid separator is used as makeup gas and enters the compressor's intermediate chamber directly through the compressor's makeup gas port (compressor makeup gas port pressure does not exceed 0.9 MPa), which can significantly increase the compressor's discharge capacity. This process recovers the energy lost during the throttling and pressure-reducing expansion process and provides the compressor with additional medium-pressure makeup gas, significantly improving its heating capacity.

[0094] External evaporative heat absorption: The liquid refrigerant at the bottom of the flash evaporator forms a low-temperature, low-pressure (0.15-0.35MPa, temperature 5-10℃ lower than ambient temperature) gas-liquid mixture after passing through the electronic expansion valve 2. The gas-liquid mixture enters the evaporator through the pipeline, exchanges heat with the ambient air outside the vehicle, and vaporizes into a low-temperature, low-pressure (0.3-0.6MPa, temperature close to ambient temperature) gas.

[0095] Main airflow convergence: The liquid at the bottom of the gas-liquid separator expands and depressurizes through the electronic expansion valve to form a low-temperature, low-pressure (0.15-0.35MPa, temperature 5-10℃ lower than ambient temperature) gas-liquid mixture, which then enters the evaporator through the liquid inlet.

[0096] The low-pressure (0.3-0.6MPa) vapor produced by the evaporator is partially diverted through solenoid valve five into the ejector via the secondary inlet, while the remaining portion directly enters the gas-liquid separator two via the four-way reversing valve. The gas-liquid separator two separates incompletely vaporized droplets, ensuring that the gas entering the compressor is pure gaseous refrigerant. This pure gaseous refrigerant gas is then compressed by the compressor, forming a high-temperature, high-pressure gas that flows back into the condenser via the four-way reversing valve, thus completing the heating cycle.

[0097] Based on the above-described preferred embodiments of the present invention, and through the foregoing description, those skilled in the art can make various changes and modifications without departing from the inventive concept. The technical scope of this invention is not limited to the contents of the specification, but must be determined according to the scope of the claims.

Claims

1. An ejector-type gas replenishment and enthalpy enhancement system with a flash igniter, characterized in that, It includes a heating system and a cooling system, which can be freely switched between modes through a reversing valve; the condenser, evaporator, reversing valve, compressor, and gas-liquid separator in the ejector-type gas injection enthalpy enhancement system are functional components shared by the heating system and the cooling system. The heating system is formed by connecting the compressor, reversing valve, condenser, flash evaporator, ejector, gas-liquid separator, and reversing valve in sequence through pipelines to form a closed loop main circuit. An electronic expansion valve is installed on the connecting pipe between the condenser and the flash evaporator. A branch pipe is installed between the electronic expansion valve and the condenser. One end of the branch pipe is connected to the closed loop main circuit, and the other end of the branch pipe is connected to the primary inlet of the ejector. The exhaust port of the flash evaporator is connected to the secondary inlet of the ejector. The nozzle of the ejector is connected to the inlet of the gas-liquid separator. The exhaust port of the gas-liquid separator is connected to the gas supply port of the compressor. Solenoid valve three and solenoid valve four are respectively installed on the pipelines connecting the condenser and flash evaporator to the ejector. The drain ports at the bottom of gas-liquid separator one and flash evaporator are respectively connected to the liquid inlet of evaporator through pipelines. Electronic expansion valve two and electronic expansion valve four are respectively installed on the connecting pipelines between gas-liquid separator one, flash evaporator and evaporator. The exhaust port of the evaporator is connected to branch line one and branch line two through a pipeline. The end of branch line one is connected to the air inlet of gas-liquid separator two. The connecting pipeline between the flash evaporator and the ejector is connected to the end of branch line two. The connection point is located on the connecting pipeline between solenoid valve four and the ejector. Solenoid valve five is installed on branch line two.

2. The ejector-type gas replenishment and enthalpy enhancement system with flash generator according to claim 1, characterized in that, The refrigeration system is a closed loop main circuit formed by connecting the compressor, reversing valve, evaporator, electronic expansion valve, condenser, and reversing valve in sequence. A solenoid valve is installed on the connecting pipe between the evaporator and the electronic expansion valve three, and a solenoid valve is installed on the connecting pipe between the electronic expansion valve three and the condenser. The exhaust port of the condenser is connected to the inlet of the second gas-liquid separator, and the exhaust port of the second gas-liquid separator is connected to the inlet of the compressor.

3. The ejector-type gas replenishment and enthalpy enhancement system with flash generator according to claim 2, characterized in that, The exhaust port of the gas-liquid separator is located above the maximum liquid level line defined within the gas-liquid separator.

4. The ejector-type gas replenishment and enthalpy enhancement system with flash generator according to claim 2, characterized in that, The air inlet of the second gas-liquid separator is located above the maximum liquid level line defined within the second gas-liquid separator.

5. The ejector-type gas replenishment and enthalpy enhancement system with flash generator according to claim 1, characterized in that, The reversing valve is a four-way reversing valve.

6. The ejector-type gas replenishment and enthalpy enhancement system with flash generator according to claim 1, characterized in that, The vent of the flash generator is located above the maximum liquid level line defined inside the flash generator.

7. The ejector-type gas replenishment and enthalpy enhancement system with flash generator according to claim 1, characterized in that, The air inlet of the gas-liquid separator is located above the maximum liquid level line defined within the gas-liquid separator.

8. The ejector-type gas replenishment and enthalpy enhancement system with flash generator according to claim 1, characterized in that, The exhaust port of the gas-liquid separator is located above the maximum liquid level line defined within the gas-liquid separator.

9. The ejector-type gas replenishment and enthalpy enhancement system with flash generator according to claim 1, characterized in that, Electronic expansion valve 1, electronic expansion valve 2, electronic expansion valve 3, and electronic expansion valve 4 are all throttling and pressure-reducing expansion valves.

10. The ejector-type gas replenishment and enthalpy enhancement system with flash generator according to claim 1, characterized in that, Solenoid valve 1, solenoid valve 2, solenoid valve 3, solenoid valve 4, solenoid valve 5, electronic expansion valve 1, electronic expansion valve 2, electronic expansion valve 3, electronic expansion valve 4, and directional valve are all controlled by a controller to open and close the valves.

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