Multi-condenser, multi-evaporator heat pump system and control method
By introducing a multi-condenser, multi-evaporator heat pump system and compressor frequency regulation, the problems of complex and easily damaged valves and low heat recovery efficiency in the thermal management system of new energy vehicles have been solved, achieving system simplification and efficient heat and cold distribution.
Patent Information
- Application Number
- CN202511802335.X
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2025-12-03
- Publication Date
- 2026-02-10
AI Technical Summary
In existing thermal management systems for new energy vehicles, valves are complex and prone to failure, making it difficult to avoid leakage between circuits, hindering system expansion, and making it difficult to efficiently recover heat under various operating conditions.
The heat pump system employs multiple condensers and multiple evaporators. By introducing evaporators and condensers on the heat source side, the valve structure is simplified, enabling flexible distribution of refrigerant between the condenser and evaporator. Combined with compressor frequency regulation, it achieves on-demand distribution of heat and cooling capacity.
It simplifies the system structure, avoids the need for switching between cooling and heating cycles, improves the utilization efficiency of heat and cold, supports system expansion, and reduces the impact of defrosting on the system.
Smart Images
Figure CN121498263A_ABST
Abstract
Description
Technical Field
[0001] This invention belongs to the field of heat pump technology, and specifically relates to a multi-condenser, multi-evaporator heat pump system and control method. Background Technology
[0002] Existing thermal management systems for new energy vehicles employ various valves to control the circulation of refrigerant and coolant, achieving cooling and heating of components and spaces such as the battery and passenger compartment. This introduces several problems, such as the complexity and susceptibility to failure of octopus-style multi-way valves, the difficulty in preventing leaks between circuits, the challenge in maximizing heat recovery under various operating conditions, and the difficulty in system expansion due to the specialized nature of the valves. These issues indicate that existing heat pump systems still haven't moved beyond the mindset of switching between cooling and heating cycles. In reality, during heat pump operation, the condenser continuously heats and the evaporator continuously cools; it only needs to deliver heat and cold to the components requiring heating or cooling. Excess heat can be released to the heat source through the condenser on the heat source side, and the required heat can be obtained from the heat source through the evaporator on the heat source side. Summary of the Invention
[0003] Based on the above ideas, this invention discloses a multi-condenser, multi-evaporator heat pump system and control method. On the basis of traditional heat pump, a set of heat source side evaporators and condensers are introduced to absorb and release heat in the heat source, so as to solve the cold and heat source problem of the thermal management system of new energy vehicles in a simple and clear way.
[0004] The technical solution disclosed in this invention is: A multi-condenser, multi-evaporator heat pump system includes a compressor interconnected to form the heat pump system, a utilization-side condenser, a utilization-side condenser regulating valve, a heat source-side condenser, a heat source-side condenser regulating valve, a utilization-side throttling device valve, a utilization-side throttling device, a heat source-side throttling device valve, a heat source-side throttling device, a heat source-side throttling device bypass valve, a utilization-side evaporator, and a heat source-side evaporator. The outlet of the compressor is connected to the inlet of the utilization-side condenser regulating valve and the heat source-side condenser regulating valve. The outlet of the utilization-side condenser regulating valve is connected to the inlet of the utilization-side condenser, and the outlet of the heat source-side condenser regulating valve is connected to the inlet of the heat source-side condenser. The outlet of the condenser on the heat source side is connected to the inlet of the throttling device valve on the utilization side and the throttling device valve on the heat source side. The throttling device valve on the utilization side is connected to the throttling device on the utilization side, and then sequentially connected to the evaporator on the utilization side. The throttling device valve on the heat source side is connected to the throttling device on the heat source side. The inlet and outlet of the bypass valve on the heat source side are connected to the inlet and outlet of the throttling device on the heat source side, respectively, forming a parallel path, and then connected to the evaporator on the heat source side. The outlet of the evaporator on the heat source side is connected to the suction port of the compressor. The outlet of the evaporator on the utilization side is connected to the suction port of the compressor through the suction valve. The inlet of the make-up air valve is connected to the outlet of the evaporator on the utilization side, and the outlet is connected to the make-up air port of the compressor.
[0005] Optionally, the outlet of the side evaporator is directly connected to the compressor suction port.
[0006] Optionally, the utilization-side condenser and the utilization-side condenser regulating valve can be composed of multiple sets connected in parallel, and the outlet of each utilization-side condenser is connected to the outlet of the heat source-side condenser; the utilization-side evaporator, the utilization-side throttling device valve, and the utilization-side throttling device can be composed of multiple sets connected in parallel, and the outlet of each utilization-side evaporator is connected to the inlet of the compressor suction valve, or connected to the compressor suction port if there is no compressor suction valve.
[0007] Optionally, the heat source-side condenser and the heat source-side evaporator are placed in contact, or they can be made into an integrated heat exchanger.
[0008] A control method for controlling the multi-condenser, multi-evaporator heat pump system, wherein the gaseous refrigerant discharged from the compressor is regulated by the regulating valves of the utilizing-side condenser and the heat source-side condenser to allow it to enter the utilizing-side condenser and the heat source-side condenser as needed. As the heat load increases, more refrigerant enters the utilizing-side condenser until the regulating valve of the heat source-side condenser is completely closed, and all the refrigerant enters the utilizing-side condenser. As the heat load decreases, the regulating valve of the utilizing-side condenser is closed slightly, and the regulating valve of the heat source-side condenser is opened wider, allowing more and more refrigerant to flow into the heat source-side condenser until the regulating valve of the utilizing-side condenser is closed, and all the refrigerant enters the heat source-side condenser. The condensed refrigerant is controlled by the throttling valves on the utilization side and the heat source side, flowing through them as needed. It then flows into the utilization-side evaporator and the heat source-side evaporator respectively. When there is a cooling load, the utilization-side throttling valve is opened, allowing the refrigerant to flow through it. When the cooling load is zero, the utilization-side throttling valve is closed, and all the refrigerant flows through the heat source-side throttling valve. When the evaporation temperature of the utilization-side evaporator exceeds the evaporation temperature of the heat source-side evaporator by 10°C, the suction valve is closed and the make-up air valve is opened; otherwise, the suction valve is open and the make-up air valve is closed.
[0009] Optionally, if the compressor can operate at a variable frequency, when all regulating valves on the heat source side condenser are closed and the heat provided by the utilization side condenser cannot meet the heat load requirements, the compressor operating frequency is increased; when the throttling device valve on the heat source side is closed and the cooling capacity provided by the utilization side evaporator cannot meet the cooling load requirements, the compressor operating frequency is increased; when the heat provided by the utilization side condenser exceeds the heat load and the evaporator does not require an increase in the compressor operating frequency, the compressor operating frequency is decreased; when the cooling capacity provided by the utilization side evaporator exceeds the cooling load and the condenser does not require an increase in the compressor operating frequency, the compressor operating frequency is decreased.
[0010] An evaporator defrosting control method for controlling the multi-condenser, multi-evaporator heat pump system, wherein the compressor is running, the side condenser regulating valve and the heat source side condenser regulating valve are fully open, the side throttling device valve, the suction valve and the make-up air valve are closed, and the heat source side throttling device valve, the heat source side throttling device and the heat source side throttling device bypass valve are fully open.
[0011] The multi-condenser, multi-evaporator heat pump system and control method disclosed in this invention can achieve the following effects: The system operates in a single cycle without the need for a reversing device to switch between cooling and heating cycles, simplifying the system. Users can extract heat from the condenser or cooling from the evaporator as needed, eliminating the need for multi-way valves, simplifying user design, and facilitating system expansion. The system can perform heat recovery when it needs to provide both heat and cooling simultaneously. By utilizing side-evaporators and heat source-side evaporators, it can operate at different evaporation temperatures, leveraging the energy-saving advantages of the gas injection cycle. The defrosting cycle does not require switching between heating and cooling cycles, reducing the impact on the system. Attached Figure Description
[0012] Figure 1 This is a schematic diagram of the basic structure of the multi-condenser, multi-evaporator heat pump system of the present invention; Figure 2 This is a schematic diagram of the structure of the multi-condenser, multi-evaporator heat pump system of the present invention without gas replenishment function; Figure 3 This is a schematic diagram of the structure of the multi-condenser, multi-evaporator heat pump system of the present invention when it has more sets of utilization side condensers and utilization side evaporators; Figure 4 This is a schematic diagram of the structure of the heat source side condenser and heat source side evaporator of the multi-condenser and multi-evaporator heat pump system of the present invention, which are integrated into one unit.
[0013] Reference numerals: 1. Compressor; 11. Suction valve; 12. Make-up valve; 21. Utilization side condenser; 22. Utilization side condenser regulating valve; 23. Heat source side condenser; 24. Heat source side condenser regulating valve; 31. Utilization side throttling device valve; 32. Utilization side throttling device; 33. Heat source side throttling device valve; 34. Heat source side throttling device; 35. Heat source side throttling device bypass valve; 41. Utilization side evaporator; 42. Heat source side evaporator. Detailed Implementation Example 1
[0014] This invention can be used as a heat source and cold source in the thermal management system of new energy vehicles, such as... Figure 4As shown, the system includes a compressor 1 that is interconnected to form a heat pump system, a utilization-side condenser 21, a utilization-side condenser regulating valve 22, a heat source-side condenser 23, a heat source-side condenser regulating valve 24, a utilization-side throttling device valve 31, a utilization-side throttling device 32, a heat source-side throttling device valve 33, a heat source-side throttling device 34, a heat source-side throttling device bypass valve 35, a utilization-side evaporator 41, and a heat source-side evaporator 42. The outlet of compressor 1 is connected to the inlet of the utilizing side condenser regulating valve 22 and the heat source side condenser regulating valve 24. The outlet of the utilizing side condenser regulating valve 22 is connected to the inlet of the utilizing side condenser 21. The outlet of the heat source side condenser regulating valve 24 is connected to the inlet of the heat source side condenser 23. The outlets of the utilizing side condenser 21 and the heat source side condenser 23 are connected to the inlet of the utilizing side throttling device valve 31 and the heat source side throttling device valve 33. The utilizing side throttling device valve 31 is connected to the utilizing side throttling device 32, and then sequentially connected to the utilizing side condenser 23. The evaporator 41 is connected, the heat source side throttling device valve 33 is connected to the heat source side throttling device 34, the inlet and outlet of the heat source side throttling device bypass valve 35 are connected to the inlet and outlet of the heat source side throttling device 34 respectively, forming a parallel path, and then connected to the heat source side evaporator 42. The outlet of the heat source side evaporator 42 is connected to the suction port of the compressor 1. The outlet of the utilization side evaporator 41 is connected to the suction port of the compressor 1 through the suction valve 11. The inlet of the make-up air valve 12 is connected to the outlet of the utilization side evaporator 41, and the outlet is connected to the make-up air port of the compressor 1.
[0015] In this embodiment, compressor 1 is a gas-injection enthalpy-increasing compressor. The utilization side condenser 21 and the utilization side evaporator 41 can be plate or shell-and-tube heat exchangers with refrigerant-coolant heat exchange. The heat source side condenser 23 and the heat source side evaporator 42 are air-coolant finned heat exchangers. The two are integrated, but each has an independent flow channel.
[0016] In this embodiment, if the throttling device 32 and the heat source side throttling device 34 are selected with a complete shut-off function, the valve 31 of the throttling device and the valve 33 of the heat source side throttling device can be eliminated, and their shut-off function is incorporated into the throttling device 32 and the heat source side throttling device 34. These valves and throttling devices are all mature products in the field.
[0017] In summer, the batteries, motors, electronic controls, and passenger compartments of new energy vehicles all need cooling. The heat they emit is transferred to the refrigerant through their respective heat exchange devices, and then the refrigerant is transported to the utilization side evaporator 41. The high-temperature and high-pressure refrigerant discharged from the compressor 1 enters the heat source side condenser 23 and is condensed into high-pressure liquid refrigerant. After being throttled by the utilization side throttling device 32, it becomes a low-temperature and low-pressure vapor-liquid two-phase refrigerant, which flows into the utilization side evaporator 41. After absorbing the heat brought by the refrigerant, all the refrigerant returns to the suction port of the compressor 1 through the suction valve 11.
[0018] In winter, the batteries and passenger compartments of new energy vehicles require heating. The required heat is extracted from the refrigerant through their respective heat exchange devices, while the refrigerant extracts its heat from the utilization-side condenser 21. The high-temperature, high-pressure refrigerant discharged from the compressor 1 all enters the utilization-side condenser 21, where it transfers heat to the refrigerant, condensing it into a high-pressure liquid refrigerant. After passing through the heat source-side throttling device 34, it becomes a low-temperature, low-pressure vapor-liquid two-phase refrigerant, flowing into the heat source-side evaporator 42. There, it absorbs heat from the air, becoming a low-pressure gaseous refrigerant, which then returns to the evaporator. The refrigerant flows to the suction port of compressor 1. If necessary, such as when the temperature reaches below -10℃, 20-40% of the refrigerant can enter the air supply port of compressor 1 through the utilization side throttling device 32 and the utilization side evaporator 41. During winter operation, the heat source side evaporator 42 may need to defrost. At this time, compressor 1 runs, and the discharged high-temperature and high-pressure refrigerant flows through the utilization side condenser 21 and the heat source side condenser 23, and then all of it enters the heat source side evaporator 42 through the bypass valve 35 of the heat source side throttling device, and then returns to the suction port of compressor 1.
[0019] In spring and autumn, the batteries, motors, electronic controls, and passenger compartments of new energy vehicles may require cooling or heating. In special cases, simultaneous heating and cooling may be necessary, such as for windshield defogging. In this case, the refrigerant can obtain heat from the utilization-side condenser 21 or cooling from the utilization-side evaporator 41, depending on the needs of each component. Excess heat during operation can be discharged to the atmosphere through the heat source-side condenser 23, and insufficient heat can be absorbed from the air through the heat source-side evaporator 42. The specific adjustment methods are as follows: The gaseous refrigerant discharged from compressor 1 is regulated by the regulating valve 22 on the utilization side condenser and the regulating valve 24 on the heat source side condenser, and enters the utilization side condenser 21 and the heat source side condenser 23 as needed. As the heat load increases, more refrigerant enters the utilization side condenser 21 until the regulating valve 24 on the heat source side condenser is completely closed, and all the refrigerant enters the utilization side condenser 21. As the heat load decreases, the regulating valve 22 on the utilization side condenser is closed, and the regulating valve 24 on the heat source side condenser is opened, and more and more refrigerant flows into the heat source side condenser 23 until the regulating valve 22 on the utilization side condenser is closed, and all the refrigerant enters the heat source side condenser 23. The condensed refrigerant is controlled by the utilization-side throttling device valve 31 and the heat source-side throttling device valve 33 to flow through the utilization-side throttling device 32 and the heat source-side throttling device 34 as needed, and then flows into the utilization-side evaporator 41 and the heat source-side evaporator 42 respectively. When there is a cooling load, the utilization-side throttling device valve 31 is opened to allow the refrigerant to flow through the utilization-side throttling device 32. When the cooling load is zero, the utilization-side throttling device valve 31 is closed and all the refrigerant flows through the heat source-side throttling device valve 33. When the evaporation temperature of the utilization-side evaporator 41 exceeds the evaporation temperature of the heat source-side evaporator 42 by 10°C, the suction valve 11 is closed and the make-up air valve 12 is opened; otherwise, the suction valve 11 is open and the make-up air valve 12 is closed.
[0020] The compressor frequency adjustment method is as follows: when the heat source side condenser regulating valve 24 is completely closed, and the heat provided by the utilization side condenser 21 is insufficient to meet the heat load requirements, the operating frequency of compressor 1 is increased; when the heat source side throttling device valve 33 is closed, and the cooling capacity provided by the utilization side evaporator 41 is insufficient to meet the cooling load requirements, the operating frequency of compressor 1 is increased; when the heat provided by the utilization side condenser 21 exceeds the heat load and the evaporator does not require an increase in the operating frequency of compressor 1, the operating frequency of compressor 1 is decreased; when the cooling capacity provided by the utilization side evaporator 41 exceeds the cooling load and the condenser does not require an increase in the operating frequency of compressor 1, the operating frequency of compressor 1 is decreased.
[0021] This embodiment eliminates the refrigerant reversing mechanism and various multi-way valves used in conventional new energy vehicle heat pumps, simplifying the system; it can add heating or cooling circuits according to user needs, making it convenient for users to expand or change the system; during system operation, the refrigerant can be delivered to the condenser or evaporator at any time as needed to achieve heat recovery, without relying on the pre-setting of various multi-way valves. Example 2
[0022] If the passenger cabin has higher requirements for comfort, this invention can directly introduce refrigerant into the condenser and evaporator in the passenger cabin air conditioning unit, forming multiple sets of new energy vehicle heat pump systems utilizing side condensers and side evaporators, such as... Figure 3 As shown, based on Example 1, the side condenser 21 and the side condenser regulating valve 22 can be composed of multiple sets connected in parallel. The outlet of each side condenser 21 is connected to the outlet of the heat source side condenser 23. Similarly, the side evaporator 41, the side throttling device valve 31, and the side throttling device 32 can be composed of multiple sets connected in parallel. The outlet of each side evaporator 41 is connected to the inlet of the compressor suction valve 11. If there is no compressor suction valve 11, it is connected to the suction port of the compressor 1.
[0023] In this embodiment, in order to enable the passenger compartment to reach a comfortable temperature more quickly, in addition to the existing heat exchanger that uses refrigerant for cooling and heating, a finned tube condenser and a finned tube evaporator are added to the air conditioning unit.
[0024] The control method in this embodiment is the same as that in Embodiment 1, and will not be described again.
[0025] In addition to the advantages of Embodiment 1, this embodiment adds an evaporator and condenser to the air conditioning unit, allowing the passenger compartment to cool or heat to a suitable temperature more quickly, which is especially suitable for high-end vehicles. Example 3
[0026] This invention can be applied to direct expansion air handling units, such as... Figure 2As shown, the system includes a compressor 1 that is interconnected to form a heat pump system, a utilization-side condenser 21, a utilization-side condenser regulating valve 22, a heat source-side condenser 23, a heat source-side condenser regulating valve 24, a utilization-side throttling device valve 31, a utilization-side throttling device 32, a heat source-side throttling device valve 33, a heat source-side throttling device 34, a heat source-side throttling device bypass valve 35, a utilization-side evaporator 41, and a heat source-side evaporator 42. The outlet of compressor 1 is connected to the inlet of the utilizing side condenser regulating valve 22 and the heat source side condenser regulating valve 24. The outlet of the utilizing side condenser regulating valve 22 is connected to the inlet of the utilizing side condenser 21. The outlet of the heat source side condenser regulating valve 24 is connected to the inlet of the heat source side condenser 23. The outlets of the utilizing side condenser 21 and the heat source side condenser 23 are connected to the inlet of the utilizing side throttling device valve 31 and the heat source side throttling device valve 33. The utilizing side throttling device valve 31 is connected to the utilizing side throttling device 32, and then sequentially connected to the utilizing side evaporator 41. The heat source side throttling device valve 33 is connected to the heat source side throttling device 34. The inlet and outlet of the heat source side throttling device bypass valve 35 are connected to the inlet and outlet of the heat source side throttling device 34, respectively, forming a parallel path, and then connected to the heat source side evaporator 42. The outlets of the heat source side evaporator 42 and the utilizing side evaporator 41 are connected to the suction port of compressor 1.
[0027] In this embodiment, the side evaporator 41 and the side condenser 21 are air-to-refrigerant finned heat exchangers, which are installed sequentially in the air conditioning unit in the direction of airflow; the heat source side condenser 23 and the heat source side evaporator 42 are also air-to-refrigerant finned heat exchangers, which are installed in the outdoor unit along with the compressor 1.
[0028] In this embodiment, if the throttling device 32 and the heat source side throttling device 34 are selected with a complete shut-off function, the valve 31 of the throttling device and the valve 33 of the heat source side throttling device can be eliminated, and their shut-off function is incorporated into the throttling device 32 and the heat source side throttling device 34. These valves and throttling devices are all mature products in the field.
[0029] In cooling mode, all the high-temperature and high-pressure refrigerant discharged by compressor 1 enters the heat source side condenser 23 and is condensed into high-pressure liquid refrigerant. After being throttled by the utilization side throttling device 32, it becomes low-temperature and low-pressure vapor-liquid two-phase refrigerant, which flows into the utilization side evaporator 41 to cool and dehumidify the fresh air. Finally, all the refrigerant returns to the suction port of compressor 1.
[0030] In heating mode, all the high-temperature and high-pressure refrigerant discharged from compressor 1 enters the utilization-side condenser 21 to heat the fresh air and condense it into high-pressure liquid refrigerant. After passing through the heat source-side throttling device 34, it becomes low-temperature and low-pressure vapor-liquid two-phase refrigerant, flows into the heat source-side evaporator 42, absorbs heat from the air, becomes low-pressure gaseous refrigerant, and returns to the suction port of compressor 1. During winter heating operation, the heat source-side evaporator 42 may need to defrost. At this time, compressor 1 runs, and the discharged high-temperature and high-pressure refrigerant passes through the utilization-side condenser 21, then passes through the heat source-side throttling device bypass valve 35 to enter the heat source-side evaporator 42, and then returns to the suction port of compressor 1.
[0031] When the outdoor air is humid, the fresh air unit can operate in dehumidification mode. In this mode, the outdoor air is dehumidified and cooled by the side evaporator 41, and then heated by the side condenser 21 before being sent indoors. The specific adjustment method is as follows: The gaseous refrigerant discharged from compressor 1 is regulated by the regulating valve 22 on the utilization side condenser and the regulating valve 24 on the heat source side condenser, and enters the utilization side condenser 21 and the heat source side condenser 23 as needed. As the heat load increases, more refrigerant enters the utilization side condenser 21 until the regulating valve 24 on the heat source side condenser is completely closed, and all the refrigerant enters the utilization side condenser 21. As the heat load decreases, the regulating valve 22 on the utilization side condenser is closed, and the regulating valve 24 on the heat source side condenser is opened, and more and more refrigerant flows into the heat source side condenser 23 until the regulating valve 22 on the utilization side condenser is closed, and all the refrigerant enters the heat source side condenser 23. After condensation, the refrigerant is controlled by the throttling device valve 31 on the utilization side and the throttling device valve 33 on the heat source side, flowing as needed through the throttling device 32 on the utilization side and the throttling device 34 on the heat source side, and then flowing into the evaporator 41 on the utilization side and the evaporator 42 on the heat source side, respectively. When there is a cooling load, the throttling device valve 31 on the utilization side is opened, allowing the refrigerant to flow into the throttling device 32 on the utilization side. When the cooling load is zero, the throttling device valve 31 on the utilization side is closed, and all the refrigerant flows through the throttling device valve 33 on the heat source side, and finally the refrigerant returns to the compressor 1.
[0032] Compared to traditional direct expansion air handling units, the biggest advantage of this embodiment is that it achieves simultaneous cooling and heating of outdoor air with a simplified system, thus possessing the functions of a constant temperature and humidity machine.
Claims
1. A multi-condenser, multi-evaporator heat pump system, comprising a compressor (1) interconnected to form the heat pump system, a utilization-side condenser (21), a utilization-side condenser regulating valve (22), a heat source-side condenser (23), a heat source-side condenser regulating valve (24), a utilization-side throttling device valve (31), a utilization-side throttling device (32), a heat source-side throttling device valve (33), a heat source-side throttling device (34), a heat source-side throttling device bypass valve (35), a utilization-side evaporator (41), and a heat source-side evaporator (42), characterized in that, The outlet of the compressor (1) is connected to the inlet of the utilizing side condenser regulating valve (22) and the heat source side condenser regulating valve (24). The outlet of the utilizing side condenser regulating valve (22) is connected to the inlet of the utilizing side condenser (21). The outlet of the heat source side condenser regulating valve (24) is connected to the inlet of the heat source side condenser (23). The outlets of the utilizing side condenser (21) and the heat source side condenser (23) are connected to the inlet of the utilizing side throttling device valve (31) and the heat source side throttling device valve (33). The utilizing side throttling device valve (31) is connected to the utilizing side throttling device (32), and then sequentially connected to the utilizing side condenser. The evaporator (41) is connected, the valve (33) of the heat source side throttling device is connected to the heat source side throttling device (34), the inlet and outlet of the bypass valve (35) of the heat source side throttling device are connected to the inlet and outlet of the heat source side throttling device (34) respectively, forming a parallel path, and then connected to the heat source side evaporator (42). The outlet of the heat source side evaporator (42) is connected to the suction port of the compressor (1). The outlet of the utilization side evaporator (41) is connected to the suction port of the compressor (1) through the suction valve (11). The inlet of the make-up valve (12) is connected to the outlet of the utilization side evaporator (41), and the outlet is connected to the make-up port of the compressor (1).
2. The multi-condenser, multi-evaporator heat pump system as described in claim 1, characterized in that, The outlet of the side evaporator (41) is directly connected to the suction port of the compressor (1).
3. The multi-condenser, multi-evaporator heat pump system as described in claim 1, characterized in that, The utilization side condenser (21) and the utilization side condenser regulating valve (22) can be composed of multiple sets connected in parallel, and the outlet of each utilization side condenser (21) is connected to the outlet of the heat source side condenser (23); the utilization side evaporator (41), the utilization side throttling device valve (31), and the utilization side throttling device (32) can be composed of multiple sets connected in parallel, and the outlet of each utilization side evaporator (41) is connected to the inlet of the compressor suction valve (11). If there is no compressor suction valve (11), it is connected to the suction port of the compressor (1).
4. The multi-condenser, multi-evaporator heat pump system as described in claim 1, characterized in that, The heat source side condenser (23) is placed in contact with the heat source side evaporator (42), or it can be made into an integrated heat exchanger.
5. A control method for controlling the multi-condenser, multi-evaporator heat pump system of claim 1, characterized in that, The gaseous refrigerant discharged by the compressor (1) is regulated by the regulating valve (22) of the condenser on the utilization side and the regulating valve (24) of the condenser on the heat source side, and enters the condenser (21) and the condenser (23) on the utilization side as needed. As the heat load increases, more refrigerant enters the condenser (21) on the utilization side until the regulating valve (24) of the condenser on the heat source side is completely closed, and all the refrigerant enters the condenser (21) on the utilization side. As the heat load decreases, the regulating valve (22) of the condenser on the utilization side is closed, and the regulating valve (24) of the condenser on the heat source side is opened, and more and more refrigerant flows into the condenser (23) on the heat source side until the regulating valve (22) of the condenser on the utilization side is closed, and all the refrigerant enters the condenser on the heat source side. The condenser (23) controls the refrigerant after condensation to flow through the throttling device (32) and the heat source throttling device (34) as needed, controlled by the throttling device valve (31) on the utilization side and the throttling device valve (33) on the heat source side, and then flows into the evaporator (41) on the utilization side and the evaporator (42) on the heat source side respectively. When there is a cooling load, the throttling device valve (31) on the utilization side is opened to allow the refrigerant to flow through the throttling device (32) on the utilization side. When the cooling load is zero, the throttling device valve (31) on the utilization side is closed and all the refrigerant flows through the throttling device valve (33) on the heat source side. When the evaporation temperature of the evaporator (41) on the utilization side exceeds the evaporation temperature of the evaporator (42) on the heat source side by 10°C, the suction valve (11) is closed and the make-up valve (12) is opened. Otherwise, the suction valve (11) is opened and the make-up valve (12) is closed.
6. The control method as described in claim 5, characterized in that, If the compressor (1) can operate at a variable frequency, when the heat source side condenser regulating valve (24) is completely closed and the heat provided by the side condenser (21) cannot meet the heat load requirements, the operating frequency of the compressor (1) is increased; when the heat source side throttling device valve (33) is closed and the cooling capacity provided by the side evaporator (41) cannot meet the cooling load requirements, the operating frequency of the compressor (1) is increased; when the heat provided by the side condenser (21) exceeds the heat load and the evaporator does not increase the operating frequency of the compressor (1), the operating frequency of the compressor (1) is reduced; when the cooling capacity provided by the side evaporator (41) exceeds the cooling load and the condenser does not increase the operating frequency of the compressor (1), the operating frequency of the compressor (1) is reduced.
7. A defrosting control method for an evaporator in a multi-condenser, multi-evaporator heat pump system as described in claim 1, characterized in that, When the compressor (1) is running, the side condenser regulating valve (22) and the heat source side condenser regulating valve (24) are fully open, the side throttling device valve (31), the suction valve (11) are closed, the gas supply valve (12) is closed, and the heat source side throttling device valve (33), the heat source side throttling device (34), and the heat source side throttling device bypass valve (35) are fully open.