A one-core dual-purpose heat pump system and a method for controlling the operation mode state machine thereof

Abstract

The present application relates to the technical field of new energy vehicle thermal management system, and belongs to a one-core dual-purpose heat pump system and a running mode state machine control method. The present application designs an indoor heat exchanger architecture with one core and two purposes, completely cancels the indoor condenser core in the traditional scheme, and replaces the high-priced four-way reversing valve with a low-cost electromagnetic valve group, thereby achieving significant optimization of system material cost from the hardware level. The combination of normally open / closed electromagnetic valves is used to replace the easily leaking four-way valve, and a protection mechanism for automatic pressure relief during power failure is designed, thereby fundamentally avoiding the risk of four-way valve leakage and sticking, and improving the system operation reliability. By defining three state machine families, i.e. a refrigeration family, a heating family and a special family, various running modes are organically managed, so that the system can smoothly switch in various complex scenes such as high-temperature refrigeration, low-temperature heating, battery cooling, waste heat recovery, defrosting and dehumidifying, and precise coverage and intelligent switching of all working conditions are achieved.

Description

Technical Field

[0001] This invention relates to the field of thermal management system technology for new energy vehicles, specifically to a dual-purpose heat pump system with a single core and its operating mode state machine control method. Background Technology

[0002] With the rapid popularization of new energy vehicles, consumers have placed higher demands on vehicle range, winter heating energy consumption, and battery safety. As a core component of thermal management, the automotive heat pump system bears the dual responsibility of ensuring passenger cabin comfort and battery thermal safety. However, the current mainstream automotive heat pump system architecture is gradually revealing the following shortcomings when facing increasingly complex demands for vehicle cost control and all-condition thermal management: First, the system has a large number of components and low integration. To balance cooling and heating functions, existing heat pump systems generally require multiple heat exchange cores within the air conditioning unit: either a dual-core architecture of "indoor evaporator + indoor condenser" or a combination of "indoor evaporator + heating core (water-cooled condenser or high-pressure PTC)". Regardless of the approach, at least two independent heat exchange units are needed within the air conditioning unit, resulting in a bulky and heavier HVAC assembly that not only encroaches on passenger compartment space but also increases airflow resistance. Furthermore, multiple cores mean more connecting pipes and seals, directly increasing system material costs and assembly time.

[0003] Secondly, there are potential reliability issues with the reversing mechanism. The four-way valve operates under alternating high and low temperatures and high pressure differentials for extended periods, making its internal slider prone to internal leakage or jamming. This leads to a decrease in the system's cooling or heating capacity, a high after-sales failure rate, and negatively impacts the user experience.

[0004] Third, it lacks adaptability to complex operating conditions. When the vehicle is in a complex operating condition of high-speed driving in winter (the passenger compartment needs strong heating) and the battery overheats due to high-power discharge (the battery needs cooling), the traditional architecture can often only cope by interrupting the heating or adding additional valves. The control logic is highly coupled, making it difficult to balance comfort and safety. Fourth, heat radiation loss exists in cooling mode, affecting cooling performance. In some heat pump systems where the indoor condenser is directly connected in series with the refrigerant circuit, the high-temperature, high-pressure refrigerant still needs to flow through the indoor condenser located inside the air conditioning unit in cooling mode. Even if the damper is closed to prevent heat from being directly blown into the passenger compartment, the high temperature on the surface of the indoor condenser will still heat the surrounding air through heat radiation and natural convection, causing the temperature of the air flowing through the indoor evaporator to passively rise. As a result, the air conditioner's outlet temperature is difficult to reach the ideal low temperature, the cooling efficiency ratio decreases, and the compressor power consumption increases. Summary of the Invention

[0005] To address the aforementioned technical issues, this invention provides a dual-purpose heat pump system and its operating mode state machine control method. The aim is to significantly reduce system hardware costs, improve operational reliability, and achieve intelligent coverage of thermal management for the entire passenger compartment and battery under all operating conditions by reusing the functions of a single indoor heat exchanger and replacing the four-way valve with a solenoid valve group.

[0006] To achieve the above objectives, the present invention provides the following technical solution: On the one hand, the present invention provides a dual-purpose heat pump system and its operating mode state machine control method, including a refrigerant side circuit and a coolant side circuit coupled and heat exchanged; The refrigerant side circuit includes a compressor, and the compressor output is connected to two flow paths: one path goes through the electromagnetic shut-off valve SOV3 to the first end of the indoor heat exchanger IHX, and the other path goes through the electromagnetic shut-off valve SOV5 to the first end of the outdoor heat exchanger OHX. The first end of the indoor heat exchanger IHX is connected to the gas-liquid separator via the electromagnetic shut-off valve SOV1 and the one-way valve A. The second end of the indoor heat exchanger IHX is connected to the Chiller side input end of the battery cooler via the electromagnetic shut-off valve SOV2 and the electronic expansion valve BATEXV of the battery branch in sequence. The Chiller side output end of the battery cooler is connected to return to the compressor via the gas-liquid separator. A main circuit electronic expansion valve HPEXV is connected in series between the second end of the outdoor heat exchanger OHX and the second end of the indoor heat exchanger IHX. The electromagnetic shut-off valve SOV5 is connected to the one-way valve A by an electromagnetic shut-off valve SOV4.

[0007] Preferably, the system further includes a one-way valve B, the input end of which is connected to the second end of the outdoor heat exchanger OHX, and the output end of which is connected between the electromagnetic shut-off valve SOV2 and the battery branch electronic expansion valve BATEXV.

[0008] Preferably, the indoor heat exchanger IHX is further provided with an electric air heater APTC and a blower in sequence on its side; the outdoor heat exchanger OHX is provided with an electric fan on its side.

[0009] Preferably, the coolant-side circuit includes a battery water pump, a water heater WPTC, a battery cooler (Chiller side), a first and third valve port of a three-way proportional valve, and a battery connected in sequence, with the second valve port of the three-way proportional valve connected between the battery water pump and the battery.

[0010] On the other hand, the present invention also provides a state machine control method for the operation mode of the above-mentioned dual-purpose heat pump system, comprising the following steps: The operating modes of the single-core dual-purpose heat pump system are divided into three mode families: cooling family, heating family, and special family. Configure a corresponding valve state combination table for each of the aforementioned mode families, with each operating mode corresponding to a set of determined solenoid valve on / off combinations; Obtain the current operating parameters and thermal management request signal of the dual-purpose heat pump system; Based on the current operating parameters and thermal management request signal, determine the target operating mode and its mode family; When the target operating mode and the current operating mode belong to different mode families, the system first enters a transition state to equalize the system pressure, and then controls the solenoid valve group to execute the on / off combination action corresponding to the target operating mode. The solenoid valve assembly consists of a normally open solenoid valve and a normally closed solenoid valve, and is used to replace the four-way reversing valve to switch the refrigerant flow direction.

[0011] Preferably, the refrigeration system includes at least one of the following operating modes: single air conditioner refrigeration mode, single battery refrigeration mode, dual evaporation refrigeration mode, dehumidification dual evaporation mode, and heating dehumidification mode. The heating system includes at least one of the following operating modes: air source heat pump mode, dual condenser mode, and water source heat pump mode. The special family includes at least one of the following operating modes: defrost mode, single battery heating / single APTC mode.

[0012] Preferably, under the refrigeration family, the common features of different modes are: electromagnetic shut-off valve SOV2 is closed, electromagnetic shut-off valve SOV3 is closed, electromagnetic shut-off valve SOV4 is closed, electromagnetic shut-off valve SOV5 is open, and the outlet of indoor heat exchanger IHX is connected to the low-pressure side. Meanwhile, the different features that each mode possesses are: Single air conditioner cooling mode: Solenoid shut-off valve SOV1 is open, check valve A is open, main circuit electronic expansion valve HPEXV is open and throttled, and battery branch electronic expansion valve BATEXV is closed. In this mode, the refrigerant flow path is as follows: compressor discharge → solenoid shut-off valve SOV5 → outdoor heat exchanger OHX condensation heat release → main circuit electronic expansion valve HPEXV throttling and pressure reduction → indoor heat exchanger IHX evaporation heat absorption → solenoid shut-off valve SOV1 → one-way valve A → gas-liquid separator → compressor suction; the battery branch electronic expansion valve BATEXV is fully closed, and the battery side does not participate in heat exchange; the compressor speed is adjusted according to the indoor heat exchanger IHX internal cold surface temperature sensor to prevent frost formation on the evaporator surface; Single-battery cooling mode: Solenoid shut-off valve SOV1 is closed, check valve B is open, main circuit electronic expansion valve HPEXV is closed, and battery branch electronic expansion valve BATEXV is open and throttled. In this mode, the refrigerant flow path is as follows: compressor discharge → solenoid shut-off valve SOV5 → outdoor heat exchanger OHX condensation and heat release → one-way valve B → battery branch electronic expansion valve BATEXV throttling and pressure reduction → battery cooler Chiller evaporation and heat absorption → gas-liquid separator → compressor suction; solenoid shut-off valve SOV1 is closed, and indoor heat exchanger IHX does not participate; the compressor speed is adjusted according to the battery inlet water temperature sensor; the battery water pump on the water circuit side is running, and the three-way proportional valve connects the battery pack and the battery cooler Chiller. The coolant flows through the battery cooler Chiller, is cooled, and then enters the battery pack to absorb heat. Dual-evaporation refrigeration mode: Solenoid shut-off valve SOV1 is open, check valve A is open, check valve B is open, main circuit electronic expansion valve HPEXV is open and throttled, battery branch electronic expansion valve BATEXV is open and throttled. In this mode, the refrigerant flow path is: compressor → solenoid shut-off valve SOV5 → outdoor heat exchanger OHX. After passing through the main outdoor heat exchanger OHX, it splits into two paths. One path goes from the main electronic expansion valve HPEXV → indoor heat exchanger IHX → solenoid shut-off valve SOV1 → check valve A → gas-liquid separator → compressor; the other path goes from check valve B → battery branch electronic expansion valve BATEXV → battery cooler Chiller → gas-liquid separator → compressor. Dehumidification dual-evaporation mode: Solenoid shut-off valve SOV1 is open, check valve A is open, check valve B is open, main circuit electronic expansion valve HPEXV is open and throttles, battery branch electronic expansion valve BATEXV is open and throttles. In this mode, the refrigerant flow path is: compressor → solenoid shut-off valve SOV5 → outdoor heat exchanger OHX. After passing through the outdoor heat exchanger OHX, it splits into two paths. One path goes through the main electronic expansion valve HPEXV → indoor heat exchanger IHX → solenoid shut-off valve SOV1 → check valve A → gas-liquid separator → compressor; the other path goes through the auxiliary check valve B → battery branch electronic expansion valve BATEXV → battery cooler Chiller → gas-liquid separator → compressor. Based on the single air conditioning cooling mode and the single battery cooling mode, the APTC fan heater is turned on to reheat the dehumidified cold air. Heating and dehumidification mode: Solenoid shut-off valve SOV1 is open, solenoid shut-off valve SOV2 is closed, check valve A is open, main circuit electronic expansion valve HPEXV is open and throttled, and battery branch circuit electronic expansion valve BATEXV is closed. In this mode, the refrigerant flow path is: compressor → solenoid shut-off valve SOV5 → outdoor heat exchanger OHX → main electronic expansion valve HPEXV → indoor heat exchanger IHX → solenoid shut-off valve SOV1 → check valve A → gas-liquid separator → compressor.

[0013] As a preferred embodiment, the common features of the different modes under the heating family are: the electromagnetic shut-off valve SOV3 is open and the compressor exhaust is directly introduced into the high-pressure side of the indoor heat exchanger IHX; Meanwhile, the different features that each mode possesses are: Air source heat pump mode: Solenoid shut-off valve SOV1 is closed, solenoid shut-off valve SOV2 is closed, solenoid shut-off valve SOV4 is open, solenoid shut-off valve SOV5 is closed, main circuit electronic expansion valve HPEXV is open and throttled, battery branch electronic expansion valve BATEXV is closed, and one-way valve A is open. In this mode, the refrigerant flow path is: compressor → solenoid shut-off valve SOV3 → indoor heat exchanger IHX → main electronic expansion valve HPEXV → outdoor heat exchanger OHX → solenoid shut-off valve SOV4 → check valve A → gas-liquid separator → compressor.

[0014] Dual condenser mode: Solenoid shut-off valve SOV1 is closed, solenoid shut-off valve SOV2 is open, solenoid shut-off valve SOV4 is closed, solenoid shut-off valve SOV5 is open, main circuit electronic expansion valve HPEXV is closed, battery branch electronic expansion valve BATEXV is open and throttled, and check valve B is open. In this mode, the refrigerant flow path is as follows: after exiting the compressor, it splits into two paths. One path goes through the solenoid shut-off valve SOV3 → indoor heat exchanger IHX → solenoid shut-off valve SOV2 → battery branch electronic expansion valve BATEXV → battery cooler Chiller → gas-liquid separator → compressor; the other path goes through the solenoid shut-off valve SOV5 → indoor / outdoor heat exchanger OHX → check valve B → battery branch electronic expansion valve BATEXV → battery cooler Chiller → gas-liquid separator → compressor.

[0015] Water source heat pump mode: Solenoid shut-off valve SOV1 is closed, solenoid shut-off valve SOV2 is open, solenoid shut-off valve SOV4 is closed, solenoid shut-off valve SOV5 is closed, main circuit electronic expansion valve HPEXV is closed, and battery branch circuit electronic expansion valve BATEXV is open and throttled. In this mode, the refrigerant side flow path is: compressor → solenoid shut-off valve SOV3 → indoor heat exchanger IHX → solenoid shut-off valve SOV2 → battery branch electronic expansion valve BATEXV → battery cooler Chiller → gas-liquid separator → compressor.

[0016] Preferably, under the aforementioned special family, the common features of different modes are: the electromagnetic shut-off valve SOV4 is closed, the electromagnetic shut-off valve SOV5 is open, and the main electronic expansion valve HPEXV is closed. Meanwhile, the different features that each mode possesses are: Defrosting mode: Solenoid shut-off valve SOV1 is closed, solenoid shut-off valve SOV2 is open, solenoid shut-off valve SOV3 is open, battery branch electronic expansion valve BATEXV is open and throttled, and check valve B is open. In this mode, the refrigerant flow path is as follows: after exiting the compressor, it splits into two paths. One path goes through the solenoid shut-off valve SOV5 → outdoor heat exchanger OHX → check valve B → battery branch electronic expansion valve BATEXV → battery cooler Chiller → gas-liquid separator → compressor; the other path goes through the solenoid shut-off valve SOV3 → indoor heat exchanger IHX → solenoid shut-off valve SOV2 → battery branch electronic expansion valve BATEXV → battery cooler Chiller → gas-liquid separator → compressor.

[0017] Single battery heating / single APTC heating mode: Solenoid shut-off valve SOV1 is open, solenoid shut-off valve SOV2 is closed, solenoid shut-off valve SOV3 is closed, battery branch electronic expansion valve BATEXV is closed, and one-way valve A is open.

[0018] Preferably, in the dual-evaporation refrigeration mode, the single air conditioning refrigeration mode circuit and the single battery refrigeration mode circuit operate in parallel. The compressor uses the indoor heat exchanger IHX temperature as the main regulating factor and introduces the battery cooler Chiller water temperature correction compensation.

[0019] Preferably, in the dehumidification dual-evaporation mode, the APTC electric heater is activated to reheat the dehumidified cold air, based on the single air conditioning cooling mode and the single battery cooling mode.

[0020] Preferably, in the heating and dehumidification mode, the refrigerant circuit is the same as in the single air conditioning cooling mode, and the indoor heat exchanger IHX cools and dehumidifies the air; at the same time, the air heater APTC is turned on to reheat the dehumidified cold air and blow it into the passenger compartment to achieve warm air dehumidification; this mode does not require the addition of additional refrigerant pipelines or valves, and only uses the existing air heater APTC as a reheat source.

[0021] Preferably, in the air source heat pump mode, the electromagnetic shut-off valves SOV1 and SOV5 are closed to cut off the passage between the indoor heat exchanger outlet and the low-pressure side, as well as the passage between the compressor exhaust and the outdoor heat exchanger OHX. When the electromagnetic shut-off valves SOV3 and SOV4 are opened, the high-temperature exhaust gas from the compressor enters the indoor heat exchanger directly through SOV3. The indoor heat exchanger acts as a high-pressure condenser to release heat to the crew compartment for heating. The refrigerant from the outlet of the indoor heat exchanger IHX is throttled by the main electronic expansion valve HPEXV and then enters the outdoor heat exchanger OHX for evaporation and heat absorption. It then returns to the gas-liquid separator via the electromagnetic shut-off valve SOV4 and the one-way valve A.

[0022] The indoor heat exchanger IHX achieves a role reversal from evaporator to condenser by using four solenoid valves: SOV1, SOV2, SOV4, and SOV5, completely replacing the indoor condenser and four-way valve in the traditional solution.

[0023] Preferably, in the dual-condenser mode, the compressor exhaust simultaneously enters the indoor heat exchanger IHX to release heat to the passenger compartment and the outdoor heat exchanger OHX to dissipate heat to the environment. After condensation, the two paths converge and are throttled by the electronic expansion valve BATEXV in the battery branch, where they evaporate and cool the battery in the battery cooler Chiller.

[0024] Preferably, in the water source heat pump mode, the electromagnetic shut-off valve SOV5 is closed to isolate the outdoor heat exchanger OHX, and the refrigerant enters the battery cooler Chiller through the electromagnetic shut-off valve SOV2 to absorb the waste heat from the battery.

[0025] Preferably, in the defrosting mode, the compressor is controlled by high pressure, the electric fan stops, the water heater WPTC provides heat, and the indoor heat exchanger IHX continues to provide heat during defrosting.

[0026] Preferably, in the single-battery heating / single APTC heating mode, the refrigerant side circuit is in a dormant state, and the water-cooled electric heater WPTC or the air-cooled electric heater APTC works independently for heating, in case of extremely low temperatures or failure.

[0027] Compared with the prior art, the present invention provides a dual-purpose heat pump system with a single core and its operating mode state machine control method, which has the following beneficial effects: 1. This invention, by designing a "one core, two uses" indoor heat exchanger architecture, completely eliminates the indoor condenser core in the traditional solution and replaces the expensive four-way reversing valve with a low-cost solenoid valve assembly, thereby achieving significant optimization of system material costs from the hardware level.

[0028] 2. This invention uses a combination of normally open / normally closed solenoid valves to replace the easily leaking four-way valve, and designs an automatic pressure relief protection mechanism when power is lost, which fundamentally avoids the risks of internal leakage and jamming of the four-way valve and improves the reliability of system operation.

[0029] 3. This invention defines three major state machine families: refrigeration family, heating family, and special family (based on the common characteristics of valve combinations, all operating modes of the system are summarized into three mode families). It organically manages 11 operating modes, ensuring that the system can smoothly switch between various complex scenarios such as high-temperature refrigeration, low-temperature heating, battery cooling, waste heat recovery, defrosting and dehumidification. It also specifically solves the industry pain point of "parallel operation of heating and battery cooling" in winter, achieving precise coverage and intelligent switching of all operating conditions.

[0030] 4. This invention completely eliminates the indoor condenser. In cooling mode, the refrigerant only evaporates and absorbs heat in the indoor heat exchanger IHX. There are no high-temperature components in the air conditioning unit, which fundamentally eliminates the problem of increased cooling outlet temperature caused by heat radiation from the indoor condenser in traditional solutions, significantly improving cooling efficiency and reducing compressor power consumption.

[0031] The features and advantages of the present invention will be described in detail through embodiments and in conjunction with the accompanying drawings. Attached Figure Description

[0032] Figure 1 This is a schematic diagram of the system architecture of the present invention; Figure 2 This is a schematic diagram of the state transition rules of the present invention. Detailed Implementation

[0033] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to the accompanying drawings and embodiments. However, it should be understood that the specific embodiments described herein are merely illustrative and not intended to limit the scope of the invention. Furthermore, descriptions of well-known structures and technologies are omitted in the following description to avoid unnecessarily obscuring the concept of the invention.

[0034] See Figures 1-2 This embodiment provides a dual-purpose heat pump system and its operating mode state machine control method, including a refrigerant side loop and a coolant side loop coupled and connected for heat exchange. The refrigerant side circuit includes compressor 1. The output end of compressor 1 is connected to two flow paths: one path goes through electromagnetic shut-off valve SOV3 to the first end of indoor heat exchanger IHX2, and the other path goes through electromagnetic shut-off valve SOV5 to the first end of outdoor heat exchanger OHX3. The first end of the indoor heat exchanger IHX2 is connected to the gas-liquid separator 5 via the electromagnetic shut-off valve SOV1 and the one-way valve A. The second end of the indoor heat exchanger IHX2 is connected to the agent side input end of the battery cooler Chiller4 via the electromagnetic shut-off valve SOV2 and the battery branch electronic expansion valve BATEXV in sequence. The agent side output end of the battery cooler Chiller4 is connected to return to the compressor 1 via the gas-liquid separator 5. A main circuit electronic expansion valve HPEXV is connected in series between the second end of the outdoor heat exchanger OHX3 and the second end of the indoor heat exchanger IHX2. The electromagnetic shut-off valve SOV5 is connected to the one-way valve A by an electromagnetic shut-off valve SOV4.

[0035] It should be further explained that the default states of the valves are as follows: SOV1 and SOV5 are normally open valves that automatically depressurize upon power failure, while SOV2, SOV3, and SOV4 are normally closed valves. This design ensures safety while reducing operating energy consumption.

[0036] In one feasible embodiment, the system further includes a one-way valve B, the input end of which is connected to the second end of the outdoor heat exchanger OHX3, and the output end of which is connected between the electromagnetic shut-off valve SOV2 and the battery branch electronic expansion valve BATEXV.

[0037] In one feasible embodiment, the indoor heat exchanger IHX2 is further provided with an electric air heater APTC21 and a blower 22 in sequence on its side; the outdoor heat exchanger OHX3 is provided with an electric fan on its side.

[0038] In one feasible embodiment, the coolant-side circuit includes a battery water pump 6, a water heater WPTC8, a battery cooler Chiller 4 liquid side, a three-way proportional valve 9 first and third valve ports, and a battery 10 connected in sequence, with the second valve port of the three-way proportional valve 9 connected between the battery water pump 6 and the battery 10.

[0039] The cost comparison between the heat pump system of this invention and the traditional heat pump system is as follows: Obviously, the heat pump system of this invention completely eliminates the indoor condenser core in the traditional solution by designing a "one core, two uses" indoor heat exchanger architecture, and replaces the expensive four-way reversing valve with a low-cost solenoid valve group, thus achieving significant optimization of system material costs from the hardware level.

[0040] Table 1 Cost Comparison Table The present invention also provides a state machine control method for the operation mode of the above-mentioned dual-purpose heat pump system, comprising the following steps: The operating modes of the single-core dual-purpose heat pump system are divided into three mode families: cooling family, heating family, and special family. Configure a corresponding valve state combination table for each of the aforementioned mode families, with each operating mode corresponding to a set of determined solenoid valve on / off combinations; Obtain the current operating parameters and thermal management request signal of the dual-purpose heat pump system; Based on the current operating parameters and thermal management request signal, determine the target operating mode and its mode family; When the target operating mode and the current operating mode belong to different mode families, the system first enters a transition state to equalize the system pressure, and then controls the solenoid valve group to execute the on / off combination action corresponding to the target operating mode. The solenoid valve assembly consists of a normally open solenoid valve and a normally closed solenoid valve, and is used to replace the four-way reversing valve to switch the refrigerant flow direction.

[0041] The method of this invention categorizes all operating modes into three major families for management, and the valve status of each mode is shown in Table 2 below: Table 2. Valve Status Table Specifically, the following further explanation is provided regarding the three major clans and their corresponding operating modes: In one feasible embodiment, the refrigeration system includes at least one of the following operating modes: single air conditioning refrigeration mode, single battery refrigeration mode, dual evaporation refrigeration mode, dehumidification dual evaporation mode, and heating dehumidification mode. The heating system includes at least one of the following operating modes: air source heat pump mode, dual condenser mode, and water source heat pump mode. The special family includes at least one of the following operating modes: defrost mode, single battery heating / single APTC mode.

[0042] In a feasible embodiment, under the refrigeration family, the common feature of different modes is that: the electromagnetic shut-off valve SOV2 is closed, the electromagnetic shut-off valve SOV3 is closed, the electromagnetic shut-off valve SOV4 is closed, the electromagnetic shut-off valve SOV5 is open, and the outlet of the indoor heat exchanger IHX2 is connected to the low-pressure side. It should be noted that, in this invention, the "low-pressure side" refers to the area between the outlet of the throttling element and the outlet of the compressor 1 after evaporation and heat absorption, where the refrigerant is in a low-temperature and low-pressure state after throttling and pressure reduction.

[0043] Meanwhile, the different features that each mode possesses are: Single air conditioner cooling mode: Solenoid shut-off valve SOV1 is open, check valve A is open, main circuit electronic expansion valve HPEXV is open and throttled, and battery branch electronic expansion valve BATEXV is closed. In this mode, the refrigerant flow path is as follows: Compressor 1 discharges → Solenoid shut-off valve SOV5 → Outdoor heat exchanger OHX3 condenses and releases heat → Main circuit electronic expansion valve HPEXV throttles and reduces pressure → Indoor heat exchanger IHX2 evaporates and absorbs heat → Solenoid shut-off valve SOV1 → Check valve A → Gas-liquid separator 5 → Compressor 1 draws in; Battery branch electronic expansion valve BATEXV is fully closed, and the battery side does not participate in heat exchange; The compressor 1 speed is adjusted according to the internal cold surface temperature sensor of indoor heat exchanger IHX2 to prevent frost formation on the evaporator surface. Single-battery cooling mode: Solenoid shut-off valve SOV1 is closed, check valve B is open, main circuit electronic expansion valve HPEXV is closed, and battery branch electronic expansion valve BATEXV is open and throttled. In this mode, the refrigerant flow path is as follows: compressor 1 discharges → solenoid shut-off valve SOV5 → outdoor heat exchanger OHX3 condenses and releases heat → one-way valve B → battery branch electronic expansion valve BATEXV throttling and pressure reduction → battery cooler Chiller4 evaporates and absorbs heat → gas-liquid separator 5 → compressor 1 draws in; solenoid shut-off valve SOV1 is closed, and indoor heat exchanger IHX2 does not participate; the compressor 1 speed is adjusted according to the battery inlet water temperature sensor; the battery water pump 6 on the water circuit side is running, and the three-way proportional valve 9 connects the battery pack and the battery cooler Chiller4. The coolant flows through the battery cooler Chiller4, is cooled, and then enters the battery pack to absorb heat. Dual-evaporation refrigeration mode: Solenoid shut-off valve SOV1 is open, check valve A is open, check valve B is open, main circuit electronic expansion valve HPEXV is open and throttled, battery branch electronic expansion valve BATEXV is open and throttled. In this mode, the refrigerant flow path is as follows: Compressor 1 → Solenoid shut-off valve SOV5 → Outdoor heat exchanger OHX3 (condensation and heat release). After passing through the outdoor heat exchanger OHX3, it splits into two paths. One path, after being throttled by the main electronic expansion valve HPEXV, enters the indoor heat exchanger IHX2 (evaporation and heat absorption), then passes through the solenoid shut-off valve SOV1 → one-way valve A → gas-liquid separator 5 → compressor 1. The other path, after being throttled by the one-way valve B → battery branch electronic expansion valve BATEXV, enters the battery cooler Chiller4 (evaporation and heat absorption) → gas-liquid separator 5 → compressor 1. The gaseous refrigerant from both paths merges in the gas-liquid separator 5. Dehumidification dual-evaporation mode: Solenoid shut-off valve SOV1 is open, check valve A is open, check valve B is open, main circuit electronic expansion valve HPEXV is open and throttles, battery branch electronic expansion valve BATEXV is open and throttles. In this mode, the refrigerant flow path is exactly the same as in the dual-evaporation refrigeration mode: Compressor 1 → Solenoid shut-off valve SOV5 → Outdoor heat exchanger OHX3. After condensation, it splits into two paths: one path goes through the main electronic expansion valve HPEXV → Indoor heat exchanger IHX2 → Solenoid shut-off valve SOV1 → Check valve A → Gas-liquid separator 5 → Compressor 1; the other path goes through check valve B → Battery branch electronic expansion valve BATEXV → Battery cooler Chiller4 → Gas-liquid separator 5 → Compressor 1. Simultaneously, the fan heater APTC21 is activated to reheat the dehumidified cold air.

[0044] Heating and dehumidification mode: Solenoid shut-off valve SOV1 is open, solenoid shut-off valve SOV2 is closed, check valve A is open, main circuit electronic expansion valve HPEXV is open and throttled, and battery branch circuit electronic expansion valve BATEXV is closed. In this mode, the refrigerant side flow path is: compressor 1 → solenoid shut-off valve SOV5 → outdoor heat exchanger OHX3 → main circuit electronic expansion valve HPEXV → indoor heat exchanger IHX2 → solenoid shut-off valve SOV1 → check valve A → gas-liquid separator 5 → compressor 1.

[0045] In a feasible embodiment, under the heating family, the common feature of different modes is: the electromagnetic shut-off valve SOV3 is open, and the compressor 1 exhausts directly into the high-pressure side of the indoor heat exchanger IHX2. It should be noted that, in this invention, the "high-pressure side" refers to the region in the refrigerant cycle from the discharge port of compressor 1 to the inlet of the throttling element (main circuit electronic expansion valve HPEXV or battery branch electronic expansion valve BATEXV). The refrigerant in this region is in a high-temperature, high-pressure state after the compressor 1 discharges. Taking the air-source heat pump mode as an example, the indoor heat exchanger IHX2 is connected in series between the discharge port of compressor 1 and the main circuit electronic expansion valve HPEXV, and is located on the high-pressure side; the outdoor heat exchanger OHX3 is connected in series between the main circuit electronic expansion valve HPEXV and the suction port of compressor 1, and is located on the low-pressure side.

[0046] Meanwhile, the different features that each mode possesses are: Air source heat pump mode: Solenoid shut-off valve SOV1 is closed, solenoid shut-off valve SOV2 is closed, solenoid shut-off valve SOV4 is open, solenoid shut-off valve SOV5 is closed, main circuit electronic expansion valve HPEXV is open and throttled, battery branch electronic expansion valve BATEXV is closed, and one-way valve A is open. In this mode, the refrigerant side flow path is: compressor 1 → solenoid shut-off valve SOV3 → indoor heat exchanger IHX2 → main circuit electronic expansion valve HPEXV → outdoor heat exchanger OHX3 → solenoid shut-off valve SOV4 → check valve A → gas-liquid separator 5 → compressor 1.

[0047] Dual condenser mode: Solenoid shut-off valve SOV1 is closed, solenoid shut-off valve SOV2 is open, solenoid shut-off valve SOV4 is closed, solenoid shut-off valve SOV5 is open, main circuit electronic expansion valve HPEXV is closed, battery branch electronic expansion valve BATEXV is open and throttled, and check valve B is open. In this mode, the refrigerant flow path is as follows: after exiting compressor 1, it splits into two paths. One path goes through solenoid shut-off valve SOV3 → indoor heat exchanger IHX2 → solenoid shut-off valve SOV2 → battery branch electronic expansion valve BATEXV → battery cooler Chiller4 → gas-liquid separator 5 → compressor 1; the other path goes through solenoid shut-off valve SOV5 → outdoor heat exchanger OHX3 → one-way valve B → battery branch electronic expansion valve BATEXV → battery cooler Chiller4 → gas-liquid separator 5 → compressor 1.

[0048] Water source heat pump mode: Solenoid shut-off valve SOV1 is closed, solenoid shut-off valve SOV2 is open, solenoid shut-off valve SOV4 is closed, solenoid shut-off valve SOV5 is closed, main circuit electronic expansion valve HPEXV is closed, and battery branch circuit electronic expansion valve BATEXV is open and throttled. In this mode, the refrigerant side flow path is: compressor 1 → solenoid shut-off valve SOV3 → indoor heat exchanger IHX2 → solenoid shut-off valve SOV2 → battery branch electronic expansion valve BATEXV → battery cooler Chiller4 → gas-liquid separator 5 → compressor 1.

[0049] In a feasible embodiment, under the special family, the common feature of different modes is that the electromagnetic shut-off valve SOV4 is closed, the electromagnetic shut-off valve SOV5 is open, and the main electronic expansion valve HPEXV is closed. Meanwhile, the different features that each mode possesses are: Defrosting mode: Solenoid shut-off valve SOV1 is closed, solenoid shut-off valve SOV2 is open, solenoid shut-off valve SOV3 is open, battery branch electronic expansion valve BATEXV is open and throttled, and check valve B is open. In this mode, the refrigerant flow path is as follows: after exiting compressor 1, it splits into two paths. One path goes through solenoid shut-off valve SOV5 → outdoor heat exchanger OHX3 → one-way valve B → battery branch electronic expansion valve BATEXV → battery cooler Chiller4 → gas-liquid separator 5 → compressor 1; the other path goes through solenoid shut-off valve SOV3 → indoor heat exchanger IHX2 → solenoid shut-off valve SOV2 → battery branch electronic expansion valve BATEXV → battery cooler Chiller4 → gas-liquid separator 5 → compressor 1.

[0050] Single battery heating / single APTC heating mode: Solenoid shut-off valve SOV1 is open, solenoid shut-off valve SOV2 is closed, solenoid shut-off valve SOV3 is closed, and battery branch electronic expansion valve BATEXV is closed.

[0051] In one feasible embodiment, in the dual-evaporation refrigeration mode, the single air conditioning refrigeration mode circuit and the single battery refrigeration mode circuit operate in parallel. The compressor 1 uses the temperature of the indoor heat exchanger IHX2 as the main regulating factor and introduces water temperature correction compensation for the battery cooler Chiller4.

[0052] In one feasible embodiment, in the dehumidification dual-evaporation mode, the APTC217 air heater is turned on to reheat the dehumidified cold air based on the single air conditioning cooling mode and the single battery cooling mode.

[0053] In one feasible embodiment, in the heating and dehumidification mode, the refrigerant circuit is the same as in the single air conditioning cooling mode. The indoor heat exchanger IHX2 cools and dehumidifies the air. At the same time, the air heater APTC21 is turned on to reheat the dehumidified cold air and blow it into the passenger compartment to achieve warm air dehumidification. This mode does not require the addition of additional refrigerant pipelines or valves, and only uses the existing air heater APTC21 as a reheat source.

[0054] In one feasible embodiment, in the air source heat pump mode, the electromagnetic shut-off valves SOV1 and SOV5 are closed to cut off the passage between the outlet of the indoor heat exchanger IHX2 and the low-pressure side, as well as the passage between the exhaust of the compressor 1 and the outdoor heat exchanger OHX3. When the electromagnetic shut-off valves SOV3 and SOV4 are opened, the high-temperature exhaust of compressor 1 enters the indoor heat exchanger IHX2 directly through SOV3. The indoor heat exchanger IHX2 acts as a high-pressure condenser to release heat to the crew compartment for heating. The refrigerant from the outlet of the indoor heat exchanger IHX2 is throttled by the main electronic expansion valve HPEXV and then enters the outdoor heat exchanger OHX3 for evaporation and heat absorption. It then returns to the gas-liquid separator 5 via the electromagnetic shut-off valve SOV4 and the one-way valve A.

[0055] The indoor heat exchanger IHX2 achieves a role reversal from evaporator to condenser by using four solenoid valves: SOV1, SOV2, SOV4, and SOV5, completely replacing the indoor condenser and four-way valve in the traditional solution.

[0056] In one feasible embodiment, in the dual-condenser mode, the exhaust of compressor 1 simultaneously enters indoor heat exchanger IHX2 to release heat to the passenger compartment and outdoor heat exchanger OHX3 to dissipate heat to the environment. After the two condensation paths converge, they are throttled by the electronic expansion valve BATEXV of the battery branch and evaporate to cool the battery 10 in the battery cooler Chiller 4.

[0057] In one feasible embodiment, in the water source heat pump mode, the electromagnetic shut-off valve SOV5 is closed to isolate the outdoor heat exchanger OHX3, and the refrigerant enters the battery cooler Chiller4 through the electromagnetic shut-off valve SOV2 to absorb the waste heat of the battery.

[0058] In one feasible embodiment, in the defrosting mode, the compressor 1 is controlled by high pressure, the electric fan stops, the water heater WPTC8 provides heat, and the indoor heat exchanger IHX2 continues to provide heat during the defrosting period.

[0059] In one feasible embodiment, in the single-battery heating / single APTC heating mode, the refrigerant side circuit is in a dormant state, and the water heating electric heater WPTC8 or the air heating electric heater APTC21 works independently for heating, in case of extremely low temperatures or failure.

[0060] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions or improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A dual-purpose heat pump system with a single core, characterized in that: This includes the refrigerant-side circuit and the coolant-side circuit, which are coupled and connected for heat exchange. The refrigerant side circuit includes a compressor (1), and the output end of the compressor (1) is connected to two flow paths, one of which goes through the electromagnetic shut-off valve SOV3 to the first end of the indoor heat exchanger IHX (2), and the other goes through the electromagnetic shut-off valve SOV5 to the first end of the outdoor heat exchanger OHX (3). The first end of the indoor heat exchanger IHX (2) is connected to the gas-liquid separator (5) via the electromagnetic shut-off valve SOV1 and the one-way valve A. The second end of the indoor heat exchanger IHX (2) is connected to the agent side input end of the battery cooler Chiller (4) via the electromagnetic shut-off valve SOV2 and the battery branch electronic expansion valve BATEXV in sequence. The agent side output end of the battery cooler Chiller (4) is connected to the compressor (1) via the gas-liquid separator (5). A main circuit electronic expansion valve HPEXV is connected in series between the second end of the outdoor heat exchanger OHX (3) and the second end of the indoor heat exchanger IHX (2); The electromagnetic shut-off valve SOV5 is connected to the one-way valve A by an electromagnetic shut-off valve SOV4.

2. The dual-purpose heat pump system according to claim 1, characterized in that: The system also includes a one-way valve B, the input end of which is connected to the second end of the outdoor heat exchanger OHX (3), and the output end of which is connected between the electromagnetic shut-off valve SOV2 and the battery branch electronic expansion valve BATEXV.

3. The dual-purpose heat pump system according to claim 1, characterized in that: The indoor heat exchanger IHX (2) is also provided with an electric heater APTC (21) and a blower (22) in sequence on the side; the outdoor heat exchanger OHX (3) is provided with an electric fan on the side.

4. A dual-purpose heat pump system according to claim 1, characterized in that: The coolant side circuit includes a battery water pump (6), a water heater WPTC (8), a battery cooler (4) liquid side, a three-way proportional valve (9) first and third valve ports, and a battery (10) connected in sequence. The second valve port of the three-way proportional valve (9) is connected between the battery water pump (6) and the battery (10).

5. The operating mode state machine control method for a single-core dual-purpose heat pump system according to any one of claims 1-4, characterized in that: Includes the following steps: The operating modes of the single-core dual-purpose heat pump system are divided into three mode families: cooling family, heating family, and special family. Configure a corresponding valve state combination table for each of the aforementioned mode families, with each operating mode corresponding to a set of determined solenoid valve on / off combinations; Obtain the current operating parameters and thermal management request signal of the dual-purpose heat pump system; Based on the current operating parameters and thermal management request signal, determine the target operating mode and its mode family; When the target operating mode and the current operating mode belong to different mode families, the system first enters a transition state to equalize the system pressure, and then controls the solenoid valve group to execute the on / off combination action corresponding to the target operating mode. The solenoid valve assembly consists of a normally open solenoid valve and a normally closed solenoid valve, and is used to replace the four-way reversing valve to switch the refrigerant flow direction.

6. The state machine control method for the operation mode of a dual-purpose heat pump system according to claim 5, characterized in that: The refrigeration system includes at least one of the following operating modes: single air conditioner refrigeration mode, single battery refrigeration mode, dual evaporation refrigeration mode, dehumidification dual evaporation mode, and heating dehumidification mode. The heating system includes at least one of the following operating modes: air source heat pump mode, dual condenser mode, and water source heat pump mode. The special family includes at least one of the following operating modes: defrost mode, single battery heating / single APTC mode.

7. The state machine control method for the operation mode of a dual-purpose heat pump system according to claim 6, characterized in that: Under the refrigeration family, the common features of different modes are: the electromagnetic shut-off valve SOV2 is closed, the electromagnetic shut-off valve SOV3 is closed, the electromagnetic shut-off valve SOV4 is closed, the electromagnetic shut-off valve SOV5 is open, and the outlet of the indoor heat exchanger IHX (2) is connected to the low-pressure side. Meanwhile, the different features that each mode possesses are: Single air conditioner cooling mode: Solenoid shut-off valve SOV1 is open, check valve A is open, main circuit electronic expansion valve HPEXV is open and throttled, and battery branch electronic expansion valve BATEXV is closed. Single-battery cooling mode: Solenoid shut-off valve SOV1 is closed, check valve B is open, main circuit electronic expansion valve HPEXV is closed, and battery branch electronic expansion valve BATEXV is open and throttled. Dual-evaporation refrigeration mode: Solenoid shut-off valve SOV1 is open, check valve A is open, check valve B is open, main circuit electronic expansion valve HPEXV is open and throttled, battery branch electronic expansion valve BATEXV is open and throttled. Dehumidification dual-evaporation mode: Solenoid shut-off valve SOV1 is open, check valve A is open, check valve B is open, main circuit electronic expansion valve HPEXV is open and throttles, battery branch electronic expansion valve BATEXV is open and throttles. Heating and dehumidification mode: Solenoid shut-off valve SOV1 is open, check valve A is open, main circuit electronic expansion valve HPEXV is open and throttled, and battery branch electronic expansion valve BATEXV is closed.

8. The state machine control method for the operation mode of a dual-purpose heat pump system according to claim 6, characterized in that: Under the aforementioned heating family, the common features of different modes are: the electromagnetic shut-off valve SOV3 is open, and the compressor (1) exhausts directly into the indoor heat exchanger IHX (2) high-pressure side; Meanwhile, the different features that each mode possesses are: Air source heat pump mode: Solenoid shut-off valve SOV1 is closed, solenoid shut-off valve SOV2 is closed, solenoid shut-off valve SOV4 is open, solenoid shut-off valve SOV5 is closed, main circuit electronic expansion valve HPEXV is open and throttled, battery branch electronic expansion valve BATEXV is closed, and one-way valve A is open. Dual condenser mode: Solenoid shut-off valve SOV1 is closed, solenoid shut-off valve SOV2 is open, solenoid shut-off valve SOV4 is closed, solenoid shut-off valve SOV5 is open, main circuit electronic expansion valve HPEXV is closed, battery branch electronic expansion valve BATEXV is open and throttled, and check valve B is open. Water source heat pump mode: Solenoid shut-off valve SOV1 is closed, solenoid shut-off valve SOV2 is open, solenoid shut-off valve SOV4 is closed, solenoid shut-off valve SOV5 is closed, main circuit electronic expansion valve HPEXV is closed, and battery branch circuit electronic expansion valve BATEXV is open and throttled.

9. The state machine control method for the operation mode of a dual-purpose heat pump system according to claim 6, characterized in that: Under the aforementioned special family, the common features of different modes are: the electromagnetic shut-off valve SOV4 is closed, the electromagnetic shut-off valve SOV5 is open, and the main electronic expansion valve HPEXV is closed. Meanwhile, the different features that each mode possesses are: Defrosting mode: Solenoid shut-off valve SOV1 is closed, solenoid shut-off valve SOV2 is open, solenoid shut-off valve SOV3 is open, battery branch electronic expansion valve BATEXV is open and throttled, and check valve B is open. Single battery heating / single APTC heating mode: Solenoid shut-off valve SOV1 is open, solenoid shut-off valve SOV2 is closed, solenoid shut-off valve SOV3 is closed, and battery branch electronic expansion valve BATEXV is closed.

10. The state machine control method for the operation mode of a dual-purpose heat pump system according to claim 7, characterized in that: In the dual-evaporation refrigeration mode, the single air conditioning refrigeration mode circuit and the single battery refrigeration mode circuit operate in parallel. The compressor (1) is adjusted mainly by the temperature of the indoor heat exchanger IHX (2), and the water temperature correction compensation of the battery cooler Chiller (4) is introduced.

11. The state machine control method for the operation mode of a dual-purpose heat pump system according to claim 8, characterized in that: In the air source heat pump mode, the electromagnetic shut-off valves SOV1 and SOV5 are closed to cut off the passage between the outlet of the indoor heat exchanger IHX (2) and the low-pressure side, as well as the passage between the compressor exhaust and the outdoor heat exchanger OHX (3). When the electromagnetic shut-off valves SOV3 and SOV4 are opened, the high-temperature exhaust gas from the compressor enters the indoor heat exchanger IHX (2) directly through SOV3. The indoor heat exchanger IHX (2) acts as a high-pressure condenser to release heat to the crew compartment for heating. The refrigerant from the outlet of the indoor heat exchanger IHX (2) is throttled by the main electronic expansion valve HPEXV and then enters the outdoor heat exchanger OHX (3) to evaporate and absorb heat. It then returns to the gas-liquid separator via the electromagnetic shut-off valve SOV4 and the one-way valve A.

12. The state machine control method for the operation mode of a dual-purpose heat pump system according to claim 9, characterized in that: In the defrosting mode, the compressor (1) controls the high pressure, the electric fan stops, the water heater WPTC (8) provides heat, and the indoor heat exchanger IHX (2) continues to provide heat during the defrosting period.

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