WO2025123797A1 - 串联热泵机组控制方法、系统以及可读存储介质 - Google Patents

串联热泵机组控制方法、系统以及可读存储介质 Download PDF

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Publication number
WO2025123797A1
WO2025123797A1 PCT/CN2024/116193 CN2024116193W WO2025123797A1 WO 2025123797 A1 WO2025123797 A1 WO 2025123797A1 CN 2024116193 W CN2024116193 W CN 2024116193W WO 2025123797 A1 WO2025123797 A1 WO 2025123797A1
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WIPO (PCT)
Prior art keywords
stage compressor
pressure
heat pump
pressure stage
pump unit
Prior art date
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Pending
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PCT/CN2024/116193
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English (en)
French (fr)
Inventor
黄成武
任帅峰
周宇
梁湖
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Gree Electric Appliances Inc of Zhuhai
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Gree Electric Appliances Inc of Zhuhai
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Publication of WO2025123797A1 publication Critical patent/WO2025123797A1/zh
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Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems

Definitions

  • the present disclosure is based on an application with CN application number 202311727335.9 and filing date December 15, 2023, and claims priority.
  • the disclosure content of the CN application is hereby introduced into the present disclosure as a whole.
  • the present disclosure provides a control method, system and readable storage medium for a series heat pump unit, which are used to reasonably distribute the load of each compressor in the series compressor.
  • Some embodiments of the present disclosure provide a control method for a series heat pump unit, comprising the following steps:
  • the frequency of at least one of the first pressure-stage compressor and the second pressure-stage compressor is increased; if it is necessary to perform a unit unloading operation, the frequency of at least one of the first pressure-stage compressor and the second pressure-stage compressor is reduced; if it is necessary to perform a unit holding operation, the frequencies of the first pressure-stage compressor and the second pressure-stage compressor remain unchanged.
  • the frequency of the compressor corresponding to the larger of the setting parameters of the second pressure stage compressor and the setting parameters of the first pressure stage compressor is maintained, and the compressor corresponding to the other setting parameter is loaded; if the first difference is less than the set upper limit threshold value X max , the step of simultaneously increasing the frequencies of the first pressure stage compressor and the second pressure stage compressor is returned to be executed.
  • the series heat pump unit control method further includes the following steps:
  • the process returns to the step of simultaneously increasing the frequencies of the first pressure-stage compressor and the second pressure-stage compressor; if the first difference is greater than or equal to the set lower limit threshold value Xmin , the process returns to the step of maintaining the frequency of the compressor corresponding to the larger one of the set parameters of the second pressure-stage compressor and the set parameters of the first pressure-stage compressor, and loading the compressor corresponding to the other set parameter.
  • control method of the series heat pump unit performs the following steps:
  • the first pressure level compressor is maintained and the frequency of the compressor corresponding to the smaller setting parameter of the second pressure stage compressor, unload the compressor corresponding to the other setting parameter; if the first difference is less than the set upper limit threshold Xmax , return to the step of simultaneously unloading the frequencies of the first pressure stage compressor and the second pressure stage compressor.
  • control method of the series heat pump unit when the first difference is greater than or equal to the set upper limit threshold value X max , the frequency of the compressor corresponding to the first pressure stage compressor and the second pressure stage compressor with the smaller set parameter is maintained, and after the step of unloading the compressor corresponding to the other set parameter, the control method of the series heat pump unit further includes the following steps:
  • the series heat pump unit adopts equal pressure ratio control
  • the first difference is the absolute value of the difference between the square of the pressure ratio of the second pressure stage compressor and the pressure ratio of the first pressure stage compressor.
  • the series heat pump unit adopts equal pressure ratio control
  • the set upper limit threshold X max is the pressure ratio set upper limit threshold P max .
  • the series heat pump unit adopts equal pressure ratio control
  • the set lower limit threshold Xmin is the pressure ratio set lower limit threshold Pmin .
  • the series heat pump units adopt equal current percentage control
  • the first difference is the absolute value of the difference between the current percentage of the second pressure stage compressor and the current percentage of the first pressure stage compressor.
  • the series heat pump units adopt equal current percentage control
  • the set upper limit threshold X max is the current percentage set upper limit threshold I max .
  • the series heat pump units adopt equal current percentage control
  • the set lower limit threshold X min is the current percentage set lower limit threshold I min .
  • the temperature difference is 0.2°C to 0.4°C.
  • the operating parameters of the second pressure stage compressor meet the requirements of the anti-surge line.
  • the present disclosure also provides a series heat pump unit control system, including:
  • a processor coupled to the memory, the processor being configured to execute a control method for a series heat pump unit as provided by any technical solution of the present disclosure based on instructions stored in the memory.
  • An embodiment of the present disclosure further provides a computer-readable storage medium on which a computer program is stored.
  • a control method for a series heat pump unit as provided in any technical solution of the present disclosure is implemented.
  • the control method of a series heat pump unit includes a second-stage compressor and a first-stage compressor. Multi-stage compression is achieved by connecting the second-stage compressor and the first-stage compressor in series.
  • Multi-stage compression is achieved by connecting the second-stage compressor and the first-stage compressor in series.
  • FIG1 is a schematic diagram of the structure of a three-stage compression series heat pump unit provided in some embodiments of the present disclosure.
  • FIG2 is a schematic diagram of the structure of a four-stage compression series heat pump unit provided in some embodiments of the present disclosure.
  • FIG3 is a schematic flow chart of a control method for a series heat pump unit provided in some embodiments of the present disclosure.
  • FIG4 is a logic diagram of a series heat pump unit control method using an equal pressure ratio control method provided in some embodiments of the present disclosure.
  • FIG5 is a logic diagram of a control method for a series heat pump unit using an equal current control method provided in some embodiments of the present disclosure.
  • First pressure stage compressor 2. Second pressure stage compressor; 3. First heat exchanger; 4. Flasher assembly; 5. Second heat exchanger; 6. First air supply branch; 7. Second air supply branch; 8. Third air supply branch;
  • a specific device when a specific device is described as being located between a first device and a second device, there may or may not be an intermediate device between the specific device and the first device or the second device.
  • the specific device When a specific device is described as being connected to other devices, the specific device may be directly connected to the other devices without an intermediate device, or may not be directly connected to the other devices but have an intermediate device.
  • Some embodiments of the present disclosure provide a control method for a series heat pump unit. Before introducing the control method for a series heat pump unit, a specific implementation method of the series heat pump unit is first introduced.
  • the series heat pump unit can utilize low-grade heat sources to meet the heat supply requirements of production processes such as building heating and domestic hot water.
  • the series heat pump unit includes a first-stage compressor 1, a second-stage compressor 2, a first heat exchanger 3, a flasher assembly 4, and a second heat exchanger 5.
  • the second-stage compressor 2, the first heat exchanger 3, the second heat exchanger 5, and the first-stage compressor 1 form a refrigerant circulation loop.
  • the flasher assembly 4 is used to replenish air to at least one of the first-stage compressor 1 and the second-stage compressor 2.
  • the pressure level of the second pressure stage compressor 2 is higher than that of the first pressure stage compressor 1, and the pressure ratio of the second pressure stage compressor 2 is selected as needed.
  • the pressure ratio of the first pressure stage compressor 1 is also selected as needed.
  • the first pressure stage compressor 1 includes at least two coaxially mounted first impellers 101.
  • the two first impellers 101 are mounted on the same drive shaft, and the rotation center lines of the two first impellers 101 coincide.
  • the connection position (i.e., the air supply position A) between the flash assembly 4 and the first pressure stage compressor 1 is located between the two first impellers 101.
  • the first pressure stage compressor 1 may also include three or more first impellers 101, all of which may be driven by the same drive shaft, and the rotation center lines of all of the first impellers 101 coincide.
  • the first pressure stage compressor 1 is a centrifugal compressor, which has a compact structure, a small volume, a large flow rate, a large power, is conducive to energy saving, and can achieve efficient use of energy.
  • the first impellers 101 are arranged side by side, and air can be supplied between every two adjacent first impellers 101 through the flasher assembly 4.
  • the number of branches through which the flasher assembly 4 supplies air to the first pressure stage compressor 1 is related to the number of first impellers 101, and the more the number of first impellers 101, the more the number of branches through which the flasher assembly 4 supplies air to the first pressure stage compressor 1.
  • the number of branches through which the flasher assembly 4 supplies air to the first pressure stage compressor 1 can be one less than the number of first impellers 101, so as to achieve an air supply position between every two adjacent first impellers 101.
  • a first air supply branch 6 is provided between the flash generator assembly 4 and the first pressure stage compressor 1.
  • the first air supply branch 6 is connected to the first pressure stage compressor 1 at a position between two first impellers 101 .
  • the first-stage compressor 1 is located upstream of the second-stage compressor 2 and downstream of the second heat exchanger 5.
  • the refrigerant output by the second heat exchanger 5 flows into the first-stage compressor 1 for compression, and then flows out of the first-stage compressor 1; and then flows into the second-stage compressor 2 for further compression.
  • the refrigerant compressed by the second-stage compressor 2 enters the first heat exchanger 3 for heat exchange.
  • at least part of the fluid enters the second heat exchanger 5 for heat exchange. If the flasher assembly 4 needs to replenish air to at least one of the second-stage compressor 2 and the first-stage compressor 1, part of the refrigerant will be replenished to the corresponding compressor, and the remaining refrigerant will flow into the second heat exchanger 5. If the flasher assembly 4 does not need to replenish air to at least one of the second-stage compressor 2 and the first-stage compressor 1, all the refrigerant will flow directly into the second heat exchanger 5.
  • the series heat pump unit provided by the above technical solution adopts three-stage compression and double air supply in the middle, and the air supply method is to supply air from the flash generator component 4. It has a compact and reasonable structure and high space utilization.
  • the heating capacity can reach more than 10MW. If this heating capacity is to be met, the motor drive power needs to be greatly increased. If the technical solution of the present invention is not adopted, and a single compressor drive method is adopted, the motor volume will be increased and the motor speed will be reduced, which is not conducive to improving the efficiency of the series heat pump unit.
  • the motor power can be shared among the two compressors, which can reduce the power loss of a single electrode, increase the motor speed, and help to improve the energy efficiency of the series heat pump unit.
  • the second-stage compressor 2 is located downstream of the first-stage compressor 1 and the two are connected.
  • the second-stage compressor 2 receives the refrigerant transmitted by the first-stage compressor 1 and compresses it.
  • the compressor 2 includes at least one second impeller 201, and the connection position (i.e., the air supply position B) between the second air supply branch 7 and the first pressure stage compressor 1 is located upstream of the most upstream second impeller 201.
  • the second pressure stage compressor 2 adopts a centrifugal compressor, which has a compact structure, a small volume, a large flow rate, a large power, is conducive to energy saving, and can achieve efficient use of energy.
  • the first heat exchanger 3 is installed downstream of the second pressure stage compressor 2 and the two are connected.
  • the first heat exchanger 3 is specifically a condenser.
  • the condenser is located downstream of the second pressure stage compressor 2 to perform heat exchange using the high-temperature refrigerant output by the second pressure stage compressor 2.
  • the first heat exchanger 3 can specifically adopt a heat exchanger with a compact structure and high heat exchange efficiency, such as a shell and tube heat exchanger.
  • the flasher assembly 4 includes a first throttling element 41 and at least two flashers 42 connected in series, a first throttling element 41 is installed between the two flashers 42 connected in series, and a first throttling element 41 is used in the middle of the flasher assembly 4 to form two independent flash pressure spaces.
  • the flasher 42 is located downstream of the first heat exchanger 3 and the two are connected.
  • the flasher assembly 4 includes two independent flashers 42 as an example.
  • One of the flashers 42 is connected to the second pressure stage compressor 2 through the second air supply branch 7, and the other flasher 42 is connected to the first pressure stage compressor 1 through the first air supply branch 6.
  • At least one of the first air supply branch 6 and the second air supply branch 7 is constructed to switch between an on state and an off state.
  • the first air supply branch 6 and the second air supply branch 7 are relatively independent, that is, the on or off state of one of the air supply branches does not affect the on-off state of the other air supply branch.
  • the second heat exchanger 5 is located downstream of the flasher assembly 4 and is connected to the first pressure stage compressor 1.
  • the second heat exchanger 5 can be a shell and tube heat exchanger or other heat exchanger with compact structure and high heat exchange efficiency.
  • the series heat pump unit further includes a second throttling element 10, which is installed between the first heat exchanger 3 and the flash generator assembly 4.
  • the second throttling element 10 throttles the refrigerant output from the first heat exchanger 3, and the throttled refrigerant enters the flash generator assembly 4.
  • the opening of the second throttling element 10 is adjusted to the maximum, the second throttling element 10 no longer throttles, but serves to conduct the refrigerant branch.
  • the series heat pump unit further includes a third throttling element 11, which is installed between the flasher assembly 4 and the second heat exchanger 5.
  • the third throttling element 11 throttles the refrigerant output by the flasher assembly 4, and the throttled refrigerant enters the second heat exchanger 5.
  • the opening of the third throttling element 11 is adjusted to the maximum, the third throttling element 11 no longer throttles, but serves to conduct the refrigerant branch.
  • the refrigerant flows along the following path: the second heat exchanger 5, the first compressor 1, the second compressor 2, the first heat exchanger 3, the second throttling element 10, the flash unit 4, the first throttling element 41, and the third throttling element 11.
  • the flash gas throttled by the second throttling element 10 is supplied to the suction of the second pressure stage compressor 2.
  • Port (B port) the flash gas throttled by the first throttling element 41 is replenished to the exhaust port (A port) of the first stage compression of the first pressure stage compressor 1.
  • the second pressure stage compressor 2 uses two second impellers 201.
  • the air supply position can be located before the most upstream second impeller 201, or between the two second impellers 201.
  • the flash generator assembly 4 includes a first throttling element 41 and three flash generators 42 connected in series.
  • the entire series heat pump unit is a four-stage compression, using three intermediate air supplies.
  • the series heat pump unit is also provided with a third air supply branch 8, all of which are supplied with air from the flash generator assembly 4.
  • the refrigeration cycle process is: the second heat exchanger 5, the first pressure stage compressor 1, the second pressure stage compressor 2, the first heat exchanger 3, the second throttling element 10, the flasher assembly 4, the first throttling element 41, the fourth throttling element 43, and the third throttling element 11.
  • Each throttling element can be a fixed orifice plate, an electric butterfly valve, etc.
  • a single flasher assembly can be used to achieve multi-stage air replenishment, which saves space and is cost-effective.
  • the flash gas after the second throttling element 10 is supplied to the exhaust port of the third-stage compression, that is, to the exhaust port (port C) of the first-stage impeller of the second-stage compressor 2, and the flash gas after throttling by the fourth throttling element 43 is supplied to the exhaust port (port A) of the first-stage compression of the first-stage compressor 1.
  • the flash gas after the first throttling element 41 is supplied to the suction port (port B) of the second-stage compressor 2.
  • the series heat pump unit after the series heat pump unit is designed and manufactured, the pressure ratio of the second pressure stage compressor 2 and the first pressure stage compressor 1 is determined. If the design parameters are that the pressure ratios of the second pressure stage compressor 2 and the first pressure stage compressor 1 are the same, the series heat pump unit adopts an equal pressure ratio control method to control the load of the dual compressors. If the design parameters are that the pressure ratios of the second pressure stage compressor 2 and the first pressure stage compressor 1 are different, the series heat pump unit adopts an equal current percentage control method to control the load of the dual compressors.
  • the first-stage compressor 1 adopts two-stage compression
  • the second-stage compressor 2 adopts single-stage compression.
  • the series heat pump unit is described by taking the equal pressure ratio control method as an example.
  • the pressure ratio of the first-stage compressor 1 is P d
  • the pressure ratio of the high-compression compressor is P g
  • the upper limit threshold X max is set to the pressure ratio
  • the upper limit threshold is set to P max
  • the lower limit threshold X min is set to the pressure ratio
  • the lower limit threshold is set to P min
  • the first difference is the absolute value of the difference between the square of the pressure ratio of the second-stage compressor 2 and the pressure ratio of the first-stage compressor 1.
  • the control method of the series heat pump unit includes the following steps:
  • Step S100 judging the series heat pump unit according to the temperature difference between the outlet water temperature of the series heat pump unit and the set water temperature
  • the group performs one of the following operations: group maintenance, group loading, and group unloading.
  • the series heat pump group includes a first pressure stage compressor 1 and a second pressure stage compressor 2 connected in series, and the pressure level of the second pressure stage compressor 2 is higher than the pressure level of the first pressure stage compressor 1.
  • the temperature difference is 0.2°C to 0.4°C.
  • 0.2°C is taken as an example.
  • the control target of the series heat pump unit is the heat pump outlet water temperature.
  • ⁇ T>+0.2°C it means that the set temperature is higher than the actual water outlet temperature and the difference between the actual water outlet temperature and the set water temperature is relatively large.
  • the execution capacity of the series heat pump unit needs to be increased and the frequency of the compressor needs to be increased, that is, loading operation needs to be performed.
  • ⁇ T ⁇ -0.2°C it means that the actual outlet water temperature is higher than the set temperature and the difference between the actual outlet water temperature and the set water temperature is relatively large, the unit is unloaded, and the compressor frequency is unloaded.
  • the execution capacity refers to the operating frequency of the compressor. If the compressor maintains the current execution capacity, it means that the compressor maintains the current operating frequency. If loaded, the operating frequency of the compressor is increased. If unloaded, the operating frequency of the compressor is reduced.
  • Step S200 If the unit needs to be loaded, the frequencies of the first pressure stage compressor 1 and the second pressure stage compressor 2 are increased. If the unit needs to be unloaded, the frequencies of the first pressure stage compressor 1 and the second pressure stage compressor 2 are reduced. If the frequencies need to be maintained, the frequencies of the first pressure stage compressor 1 and the second pressure stage compressor 2 remain unchanged.
  • step S200 when the capacity loading is performed according to the water temperature requirement, the two compressor frequencies are loaded at the same time, and the square of the pressure ratio of the second pressure stage compressor 2 is determined.
  • the absolute value of the difference is the first difference in the equal pressure ratio mode. hour, The compressor corresponding to the larger value in P d is kept at execution capacity, and the compressor corresponding to the smaller value is loaded.
  • the control method of the series heat pump unit specifically includes the following steps: simultaneously increasing the setting parameters of the second pressure stage compressor 2 and the frequency of the first pressure stage compressor 1. Then, determining whether the first difference between the setting parameters of the second pressure stage compressor 2 and the setting parameters of the first pressure stage compressor 1 is greater than or equal to the set upper limit threshold value P max .
  • the frequency of the compressor corresponding to the larger one of the set parameters of the second pressure stage compressor 2 and the set parameters of the first pressure stage compressor 1 is maintained, and If the first difference is less than the upper limit threshold value P max , the operation of loading the first stage compressor 1 and the second stage compressor 2 is returned to increase the frequency of the first stage compressor 1 and the second stage compressor 2 .
  • the process returns to the step of loading the first pressure stage compressor 1 and the second pressure stage compressor 2 simultaneously.
  • the first difference It changes in real time.
  • the unit loading process when entering the special control where one compressor is loaded and the other compressor is kept, when the compressor that needs to be loaded is loaded to When the normal control mode of synchronous loading is restored, that is, when Then the mode is restored to that in which both the first pressure stage compressor 1 and the second pressure stage compressor 2 are loaded.
  • the system when entering the special control of loading one compressor and maintaining the other compressor, it is necessary to determine whether the first difference between the setting parameters of the second pressure stage compressor 2 and the loaded first pressure stage compressor 1 is less than the set lower limit threshold value Xmin . Specifically, if the first difference is less than the set lower limit threshold value Pmin , the operation of loading both the first pressure stage compressor 1 and the second pressure stage compressor 2 is returned. If the first difference is If the value is greater than or equal to the lower threshold value Pmin , the system returns to the operation of maintaining the frequency of the compressor corresponding to the larger of the set parameters of the first-stage compressor 1 and the second-stage compressor 2, and loading the compressor corresponding to the other set parameter.
  • the corresponding second pressure stage compressor 2 maintains the execution capacity and loads the first pressure stage compressor 1 corresponding to P d until Restore to load both the first pressure stage compressor 1 and the second pressure stage compressor 2. If and then The corresponding second pressure stage compressor 2 is loaded, and the corresponding first pressure stage compressor 1 of P d is maintained until Restore until both the first pressure stage compressor 1 and the second pressure stage compressor 2 are loaded.
  • the first pressure stage compressor 1 and the second pressure stage compressor 2 both maintain the current frequency without adjustment.
  • the control method of the series heat pump unit specifically includes the following steps: simultaneously unloading the frequencies of the first pressure stage compressor 1 and the second pressure stage compressor 2; then determining whether the first difference between the setting parameters of the first pressure stage compressor 1 and the second pressure stage compressor 2 is Is it greater than or equal to the set upper limit threshold P max .
  • the process returns to the step of simultaneously unloading the first pressure stage compressor 1 and the second pressure stage compressor 2 .
  • the first difference It changes in real time. Then the process returns to the step of unloading both the first pressure stage compressor 1 and the second pressure stage compressor 2; otherwise, the process returns to the step of maintaining the smaller of the first pressure stage compressor 1 and the second pressure stage compressor 2 and unloading the larger one alone.
  • the control method for the series heat pump unit adopts an equal pressure ratio control method, which makes the speed distribution reasonable, reduces the compressor shaft grinding phenomenon, avoids the compressor power being too high or too low, and makes the series heat pump unit operate reliably; it avoids the first pressure stage compressor 1 speed being too high and the second pressure stage compressor 2 speed being too low to consume the refrigerant discharged by the first pressure stage compressor 1, resulting in the phenomenon that the power of the whole machine is too large, but the capacity and energy efficiency are low.
  • the series heat pump unit adopts equal current percentage control.
  • the first difference is the absolute value of the difference between the current percentage of the second pressure stage compressor 2 and the current percentage of the first pressure stage compressor 1.
  • the upper limit threshold X max is set as the upper limit threshold I max for the current percentage setting.
  • the lower limit threshold X min is set as the lower limit threshold I min for the current percentage setting.
  • the current percentage is the difference between the actual current of the compressor and the full load rating.
  • the current percentage of the first compression stage compressor 1 is I d
  • the current percentage of the high compression stage compressor is I g .
  • the actual current corresponding to the full load operation of the unit is set to the rated current of the compressor, the maximum current percentage difference is I max , and the minimum current percentage difference is I min .
  • the control method of the series heat pump unit includes the following steps:
  • the series heat pump unit includes a first pressure stage compressor 1 and a second pressure stage compressor 2 in series, and the pressure level of the second pressure stage compressor 2 is higher than the pressure level of the first pressure stage compressor 1.
  • the control target of the series heat pump unit is the heat pump outlet water temperature.
  • ⁇ T set temperature - actual outlet water temperature.
  • the following text still takes 0.2°C as an example.
  • the control logic is the same as the temperature content described above: when -0.2°C ⁇ T ⁇ 0.2°C, the first pressure stage compressor 1 and the second pressure stage compressor 2 both maintain the current frequency. If ⁇ T>+0.2°C, the unit is loaded. If ⁇ T ⁇ -0.2°C, the unit is unloaded.
  • the frequency of at least one of the first pressure stage compressor 1 and the second pressure stage compressor 2 is increased. If the unit needs to be unloaded, the frequency of at least one of the first pressure stage compressor 1 and the second pressure stage compressor 2 is reduced. If it needs to be maintained, the frequencies of the first pressure stage compressor 1 and the second pressure stage compressor 2 remain unchanged.
  • the series heat pump unit control method further includes the following steps: determining whether a first difference between a set parameter of the second pressure stage compressor 2 and a set parameter of the first pressure stage compressor 1 is greater than or equal to a set upper limit threshold value I max .
  • the frequency of the compressor corresponding to the larger one of the set parameters of the second pressure stage compressor 2 and the set parameters of the first pressure stage compressor 1 is maintained, and the compressor corresponding to the other set parameter is loaded. If the first difference is less than the set upper limit threshold value I max , the step of returning to the step of loading both the first pressure stage compressor 1 and the second pressure stage compressor 2 is performed.
  • the execution capacity of the second pressure stage compressor 2 is maintained.
  • the first pressure stage compressor 1 is loaded separately. If I d is greater than I g , the execution capacity of the first pressure stage compressor 1 is maintained, and the second pressure stage compressor 2 is loaded separately. If the first difference
  • the series heat pump unit control method also includes the following steps: determining whether the first difference between the setting parameters of the second pressure stage compressor 2 and the first pressure stage compressor 1 is less than the set lower limit threshold value Imin .
  • the second pressure-stage compressor 2 corresponding to I g is loaded separately, and the first pressure-stage compressor 1 corresponding to I d is kept capable of execution at the current level, until ⁇ I g -I d ⁇ I min , and the process returns to the step of loading both the first pressure-stage compressor 1 and the second pressure-stage compressor 2.
  • the series heat pump unit maintains the current operating parameters, ie, the content corresponding to the middle branch of FIG. 5 , the first pressure stage compressor 1 and the second pressure stage compressor 2 both maintain the current frequency without adjustment.
  • control method of the series heat pump unit specifically includes the following steps: simultaneously unloading the frequencies of the first pressure stage compressor 1 and the second pressure stage compressor 2; determining whether the first difference between the set parameters of the first pressure stage compressor 1 and the second pressure stage compressor 2 is greater than or equal to the set upper limit threshold value I max .
  • the frequency of the compressor corresponding to the smaller set parameter of the first pressure stage compressor 1 and the second pressure stage compressor 2 is maintained, and the other compressor is unloaded separately; if the first difference ⁇ I g -I d ⁇ is less than the set upper limit threshold value I max , then return to the step of unloading both the first pressure stage compressor 1 and the second pressure stage compressor 2.
  • the second pressure stage compressor 2 corresponding to I g is unloaded separately, and the execution capacity of the first pressure stage compressor 1 corresponding to I d is maintained. If I d is greater than I g , then the first pressure stage compressor 1 is unloaded separately, and the execution capacity of the second pressure stage compressor 2 is maintained unchanged. If the first difference ⁇ I g -I d ⁇ is less than the set upper limit threshold value I max , then return to the step of unloading both the first pressure stage compressor 1 and the second pressure stage compressor 2. If I d ⁇ is less than the set upper limit threshold I max , the process returns to the step of simultaneously unloading the first pressure stage compressor 1 and the second pressure stage compressor 2 .
  • the control method of the series heat pump unit also includes the following steps: determining whether the first difference ⁇ I g -I d ⁇ between the setting parameters of the unloaded second-stage compressor 2 and the maintained first-stage compressor 1 is less than the set lower limit threshold I min ; if the first difference ⁇ I g -I d ⁇ is less than the set lower limit threshold I min , returning to the step of unloading both the first-stage compressor 1 and the second-stage compressor 2; if the first difference ⁇ I g -I d ⁇ is greater than or equal to the set lower limit threshold I min , returning to the step of maintaining the frequency of the compressor corresponding to the smaller of the setting parameters of the first-stage compressor 1 and the second-stage compressor 2, and unloading the other compressor
  • the second pressure-stage compressor 2 corresponding to I g is unloaded, and the first pressure-stage compressor 1 corresponding to I d is maintained at the current execution capacity, until ⁇ I g -I d ⁇ I min , and the first pressure-stage compressor 1 and the second pressure-stage compressor 2 are both unloaded.
  • the second pressure-stage compressor 2 corresponding to I g is maintained at the current execution capacity, and the first pressure-stage compressor 1 corresponding to I d is unloaded, until ⁇ I g -I d ⁇ I min , and the first pressure-stage compressor 1 and the second pressure-stage compressor 2 are both unloaded.
  • the control method of the series heat pump unit provided by the above technical solution adopts an equal current percentage control method to reasonably distribute the speed, avoid excessive or low compressor power, and make the series heat pump unit operate reliably.
  • the series heat pump unit provided by the above technical solution adopts the control method of equal pressure ratio and equal current percentage of dual compressors.
  • the dual compressors are loaded and unloaded at the same time. It is only necessary to set an anti-surge line for the second pressure stage compressor 2 to ensure that the second pressure stage compressor 2 does not surge. When the second pressure stage compressor 2 does not surge, the entire unit does not surge. At this time, it returns to the load control mode. Under the equal pressure ratio or equal current percentage control mode, when the unit's execution capacity reduces the unloading frequency, the two compressors perform synchronous unloading or separate unloading. When the high-pressure stage is unloaded to below the minimum frequency + 2Hz, the frequencies of the two compressors are maintained.
  • the unit has been unloaded to the limit minimum load and cannot be unloaded again. If the actual load is smaller and the minimum load of the unit is higher than the actual load, the water temperature of the unit will be higher than the set temperature until the unit runs to the standby temperature and stands by normally. At this point, the entire load and anti-surge control is completed.
  • the anti-surge control method is simple and reliable.
  • Some embodiments of the present disclosure also provide a series heat pump unit control system, including a memory and a processor coupled to the memory.
  • the processor is configured to execute a series heat pump unit control method provided by any technical solution of the present disclosure based on instructions stored in the memory.
  • Some other embodiments of the present disclosure further provide a computer-readable storage medium having a computer program stored thereon.
  • the program is executed by a processor, the control method of the series heat pump unit provided by any technical solution of the present disclosure is implemented.
  • the processor described herein may include a general-purpose processor, a digital signal processor (DSP), an application-specific integrated circuit (ASIC), a field programmable gate array (FPGA) or other programmable logic device, discrete gate or transistor logic, discrete hardware components, or any combination thereof designed to perform the functions described herein.
  • a general-purpose processor may be a microprocessor, but in an alternative, the processor may be any conventional processor, controller, microcontroller, or state machine.
  • the processor may also be implemented as a combination of computing devices, such as a combination of a DSP and a microprocessor, a plurality of microprocessors, one or more microprocessors cooperating with a DSP core, or any other such configuration.
  • Storage media can be any available media that can be accessed by a computer.
  • such computer-readable media may include RAM, ROM, EEPROM, CD-ROM or other optical disk storage, disk storage or other magnetic storage devices, or any other medium that can be used to carry or store the desired program code in the form of instructions or data structures and can be accessed by a computer. Any connection is also properly referred to as a computer-readable medium.
  • disks and discs include compact discs (CDs), laser discs, optical discs, digital versatile discs (DVDs), floppy disks, and blue-ray discs, wherein disks often reproduce data magnetically, and discs reproduce data optically with lasers.
  • CDs compact discs
  • DVDs digital versatile discs
  • floppy disks and blue-ray discs
  • the method embodiments of the present disclosure may be provided as methods, systems, or computer program products. Therefore, the present disclosure may take the form of a complete hardware embodiment, a complete software embodiment, or an embodiment combining software and hardware. Moreover, the present disclosure may take the form of a computer program product implemented on one or more computer-usable non-transient storage media (including but not limited to disk storage, CD-ROM, optical storage, etc.) containing computer-usable program code.
  • computer-usable non-transient storage media including but not limited to disk storage, CD-ROM, optical storage, etc.
  • These computer program instructions may also be stored in a computer-readable memory that can direct a computer or other programmable data processing device to work in a specific manner, so that the instructions stored in the computer-readable memory produce a manufactured product including an instruction device that implements the functions specified in one or more processes in the flowchart and/or one or more boxes in the block diagram.
  • These computer program instructions may also be loaded onto a computer or other programmable data processing device so that a series of operational steps are executed on the computer or other programmable device to produce a computer-implemented process, whereby the instructions executed on the computer or other programmable device provide steps for implementing the functions specified in one or more processes in the flowchart and/or one or more boxes in the block diagram.

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Abstract

一种串联热泵机组控制方法、系统以及可读存储介质，涉及热泵领域，用以合理分配串联压缩机的负荷。串联热泵机组控制方法，包括以下步骤：根据串联热泵机组的出水温度与设定水温的温度差值判断所述串联热泵机组执行以下一种：机组保持、机组加载、机组卸载；串联热泵机组包括串联的第一压级压缩机（1）和第二压级压缩机（2），第二压级压缩机（2）的压级高于第一压级压缩机（1）的压级；如机组加载，则增加第一压级压缩机（1）和第二压级压缩机（2）中至少其中之一的频率；如机组卸载，则减少第一压级压缩机（1）和第二压级压缩机（2）中至少其中之一的频率；如保持，则第一压级压缩机（1）和第二压级压缩机（2）的频率均保持不变。

Description

串联热泵机组控制方法、系统以及可读存储介质
相关申请的交叉引用
本公开是以CN申请号为202311727335.9，申请日为2023年12月15日的申请为基础，并主张其优先权，该CN申请的公开内容在此作为整体引入本公开中。
技术领域
本公开涉及热泵领域，具体涉及一种串联热泵机组控制方法、系统以及可读存储介质。
背景技术
热泵是一种在电能或热能等驱动下，将低品位热源的热能转移到高品位热源的节能装置。其中，工业热泵作为一种主动热回收装置，可将工业工程中的废热温度提升为更高的温度，以用于同一过程或其他相邻过程的热需求。针对热源温度与需求温度相差较大的场合，业内采用多级压缩式热泵，可以大大提高温升。多级压缩式热泵是指采用压缩机串联的形式，以输出更高的温度。
离心压缩机结构简单，运动零件少且制造精度要求低，具有制造成本低与可靠性高的优点。虽然离心压缩机在部分负荷下具有喘振风险，但在工作压力变化范围小、制热量较大的场合(如大温升超高温热泵)，具有良好的系统总效率。
发明内容
发明人发现，相关技术中至少存在下述不足：业内亟需解决双压缩机串联运行时的负荷分配问题。
本公开提出一种串联热泵机组控制方法、系统以及可读存储介质，用以合理分配串联压缩机中各个压缩机的负荷。
本公开一些实施例提供了一种串联热泵机组控制方法，包括以下步骤：
根据串联热泵机组的出水温度与设定水温的温度差值判断所述串联热泵机组执行以下其中一种操作：机组保持、机组加载、机组卸载；所述串联热泵机组包括串联的第一压级压缩机和第二压级压缩机，所述第二压级压缩机的压级高于所述第一压级压缩机的压级；
如果需要执行机组加载操作，则增加所述第一压级压缩机和所述第二压级压缩机中至少其中之一的频率；如果需要执行机组卸载操作，则减少所述第一压级压缩机和所述第二压级压缩机中至少其中之一的频率；如果需要执行机组保持操作，则所述第一压级压缩机和所述第二压级压缩机的频率均保持不变。
在一些实施例中，在执行机组加载操作过程中，所述串联热泵机组控制方法执行以下步骤：
同时增加所述第一压级压缩机和所述第二压级压缩机的频率；
判断所述第二压级压缩机的设定参数和所述第一压级压缩机的设定参数的第一差值是否大于或者等于设定上限阈值Xmax；
如果所述第一差值大于或者等于设定上限阈值Xmax，则保持所述第二压级压缩机的设定参数和所述第一压级压缩机的设定参数中较大者对应的压缩机的频率，并对另一设定参数所对应的压缩机加载；如果所述第一差值小于设定上限阈值Xmax，则返回执行所述同时增加所述第一压级压缩机和所述第二压级压缩机的频率的步骤。
在一些实施例中，在执行机组加载操作过程中，在所述如果所述第一差值大于或者等于设定上限阈值Xmax，则保持所述第二压级压缩机的设定参数和所述第一压级压缩机的设定参数中较大者对应的压缩机的频率，并对另一设定参数所对应的压缩机加载的步骤之后，所述串联热泵机组控制方法还包括以下步骤：
判断所述第一压级压缩机和所述第二压级压缩机的设定参数的第一差值是否小于设定下限阈值Xmin；
如果所述第一差值小于设定下限阈值Xmin，则返回执行所述同时增加所述第一压级压缩机和所述第二压级压缩机的频率的步骤；如果所述第一差值大于或者等于设定下限阈值Xmin，则返回执行所述保持所述第二压级压缩机的设定参数和所述第一压级压缩机的设定参数中较大者对应的压缩机的频率，并对另一设定参数所对应的压缩机加载的步骤。
在一些实施例中，在执行机组卸载操作过程中，所述串联热泵机组控制方法执行以下步骤：
同时卸载所述第一压级压缩机和所述第二压级压缩机的频率；
判断所述第一压级压缩机和所述第二压级压缩机的设定参数的第一差值是否大于或者等于设定上限阈值Xmax；
如果所述第一差值大于或者等于设定上限阈值Xmax，则保持所述第一压级压缩机 和所述第二压级压缩机中设定参数较小者的对应的压缩机的频率，对另一设定参数所对应的压缩机卸载；如果所述第一差值小于设定上限阈值Xmax，则返回执行同时卸载所述第一压级压缩机和所述第二压级压缩机的频率的步骤。
在一些实施例中，在执行机组卸载操作的过程中，在所述第一差值大于或者等于设定上限阈值Xmax，则保持所述第一压级压缩机和所述第二压级压缩机中设定参数较小者的对应的压缩机的频率，对另一设定参数所对应的压缩机卸载的步骤之后，所述串联热泵机组控制方法还包括以下步骤：
判断卸载后的所述第二压级压缩机和保持的所述第一压级压缩机的设定参数的第一差值是否小于设定下限阈值Xmin；
如果第一差值小于设定下限阈值Xmin，则返回执行同时卸载所述第一压级压缩机和所述第二压级压缩机的频率的步骤；如果第一差值大于或者等于设定下限阈值Xmin，则返回执行所述保持所述第一压级压缩机和所述第二压级压缩机中设定参数较小者的对应的压缩机的频率，对另一设定参数所对应的压缩机卸载的步骤。
在一些实施例中，所述串联热泵机组采用等压比控制，则所述第一差值为所述第二压级压缩机的压比的平方与所述第一压级压缩机的压比的差值的绝对值。
在一些实施例中，所述串联热泵机组采用等压比控制，所述设定上限阈值Xmax为压比设定上限阈值Pmax。
在一些实施例中，所述串联热泵机组采用等压比控制，所述设定下限阈值Xmin为压比设定下限阈值Pmin。
在一些实施例中，所述串联热泵机组采用等电流百分比控制，则所述第一差值为所述第二压级压缩机的电流百分比与所述第一压级压缩机的电流百分比的差值的绝对值。
在一些实施例中，所述串联热泵机组采用等电流百分比控制，所述设定上限阈值Xmax为电流百分比设定上限阈值Imax。
在一些实施例中，所述串联热泵机组采用等电流百分比控制，所述设定下限阈值Xmin为电流百分比设定下限阈值Imin。
在一些实施例中，所述温度差值为0.2℃～0.4℃。
在一些实施例中，所述第二压级压缩机的运行参数满足防喘线的要求。
本公开实施例还提供一种串联热泵机组控制系统，包括：
存储器；和
耦接至所述存储器的处理器，所述处理器被配置为基于存储在所述存储器中的指令，执行如本公开任一技术方案所提供的串联热泵机组控制方法。
本公开实施例又提供一种计算机可读存储介质，其上存储有计算机程序，该程序被处理器执行时实现如本公开任一技术方案所提供的串联热泵机组控制方法。
上述技术方案提供的串联热泵机组控制方法，包括第二压级压缩机和第一压级压缩机，通过将第二压级压缩机和第一压级压缩机串联，实现多级压缩；在负荷分配时，按照两个压缩机叶轮的设计压比是否一致，确定进行等压比控制和等电流控制方式，如果两个压缩机叶轮的设计压比一致，则采用等压比控制，否则采用等电流控制方式，保证了双压缩机转速合理分配与防喘可靠运行。
附图说明
图1为本公开一些实施例提供的串联热泵机组三级压缩的结构示意图。
图2为本公开一些实施例提供的串联热泵机组四级压缩的结构示意图。
图3为本公开一些实施例提供的串联热泵机组控制方法流程示意图。
图4为本公开一些实施例提供的串联热泵机组控制方法采用等压比控制方式的逻辑示意图。
图5为本公开一些实施例提供的串联热泵机组控制方法采用等电流控制方式的逻辑示意图。
附图标记：
1、第一压级压缩机；2、第二压级压缩机；3、第一换热器；4、闪发器组件；5、第二换热器；6、第一补气支路；7、第二补气支路；8、第三补气支路；
41、第一节流元件；10、第二节流元件；11、第三节流元件；42、闪发器；43、第四节流元件；
101、第一叶轮；201、第二叶轮。
具体实施方式
下面结合图1～图5对本公开提供的技术方案进行更为详细的阐述。对示例性实施例的描述仅仅是说明性的，决不作为对本公开及其应用或使用的任何限制。本公开可以以许多不同的形式实现，不限于这里介绍的实施例。提供这些实施例是为了使本公开透彻且完整，并且向本领域技术人员充分表达本公开的范围。应注意到：除非另 外具体说明，否则在这些实施例中阐述的部件和步骤的相对布置、材料的组分、数字表达式和数值应被解释为仅仅是示例性的，而不作为限制。
本公开中使用的“第一”、“第二”以及类似的词语并不表示任何顺序、数量或者重要性，而只是用来区分不同的部分。“包括”或者“包含”等类似的词语意指在该词前的要素涵盖在该词后列举的要素，并不排除也涵盖其他要素的可能。
在本公开中，当描述到特定器件位于第一器件和第二器件之间时，在该特定器件与第一器件或第二器件之间可以存在居间器件，也可以不存在居间器件。当描述到特定器件连接其它器件时，该特定器件可以与其它器件直接连接而不具有居间器件，也可以不与其它器件直接连接而具有居间器件。
本公开使用的所有术语(包括技术术语或者科学术语)与本公开所属领域的普通技术人员理解的含义相同，除非另外特别定义。还应当理解，在诸如通用字典中定义的术语应当被解释为具有与它们在相关技术的上下文中的含义相一致的含义，而不应用理想化或极度形式化的意义来解释，除非这里明确地这样定义。
对于相关领域普通技术人员已知的技术、方法和设备可能不作详细讨论，但在适当情况下，技术、方法和设备应当被视为说明书的一部分。
附图中所示出的各个部分的尺寸并不是按照实际的比例关系绘制的。在各附图中对共同的结构要素或者同种类的结构要素附加相同的附图标记，并适当省略对它们的重复说明。
本公开一些实施例提供一种串联热泵机组控制方法，在介绍串联热泵机组控制方法之前，先介绍串联热泵机组的具体实现方式。
串联热泵机组可以利用低品位热源，满足建筑供暖、生活热水等生产过程的热量供应需求。参见图1，串联热泵机组包括第一压级压缩机1、第二压级压缩机2、第一换热器3、闪发器组件4以及第二换热器5。第二压级压缩机2、第一换热器3、第二换热器5、第一压级压缩机1组成冷媒循环回路。闪发器组件4用于给第一压级压缩机1、第二压级压缩机2中的至少一个补气。
第二压级压缩机2的压级高于第一压级压缩机1，第二压级压缩机2的压比根据需要来选定。第一压级压缩机1的压比也根据需要来选定。在一些实施例中，第一压级压缩机1包括至少两个同轴安装的第一叶轮101。两个第一叶轮101安装于同一根驱动轴，并且两个第一叶轮101转动中心线重合。闪发器组件4与第一压级压缩机1的连通位置(即补气位置A)位于两个第一叶轮101之间。
在另一些实施例中，第一压级压缩机1也可以包括三个甚至更多数量的第一叶轮101，所有的第一叶轮101可以由同一根驱动轴驱动，并且所有第一叶轮101的转动中心线都重合。第一压级压缩机1采用离心压缩机，结构紧凑，体积小，流量大，功率大且有利于节能，能实现能源的高效利用。
各个第一叶轮101并排布置，在每两个相邻的第一叶轮101之间都可以通过闪发器组件4进行补气。闪发器组件4给第一压级压缩机1补气的支路数量与第一叶轮101的数量相关，且第一叶轮101的数量越多，闪发器组件4给第一压级压缩机1补气的支路数量也可以越多。具体地，闪发器组件4给第一压级压缩机1补气的支路数量可以比第一叶轮101的数量少1，以实现每两个相邻的第一叶轮101之间都有一个补气位置。上述技术方案，通过合理设置补气位置，提升了串联热泵机组的能效。
继续参见图1，闪发器组件4和第一压级压缩机1之间设置有第一补气支路6。第一补气支路6与第一压级压缩机1的连通位置位于其中两个第一叶轮101之间。
第一压级压缩机1位于第二压级压缩机2的上游，且位于第二换热器5的下游。第二换热器5输出的冷媒流入到第一压级压缩机1内部进行压缩，然后从第一压级压缩机1流出；而后流入到第二压级压缩机2内继续压缩。第二压级压缩机2压缩后的冷媒进入到第一换热器3内进行换热。然后经过闪发器组件4后至少部分流体进入到第二换热器5内部进行换热。如果闪发器组件4需要给第二压级压缩机2、第一压级压缩机1中的至少一个补气，则有部分冷媒会被补充到相应的压缩机中，剩余的冷媒流入第二换热器5内部。如果闪发器组件4不需要给第二压级压缩机2、第一压级压缩机1中的至少一个补气，则冷媒全部直接流入第二换热器5内部。
上述技术方案提供的串联热泵机组，采用三级压缩，中间双补气，补气方式均为从闪发器组件4补气，结构紧凑合理，空间利用率高。
对于大容量的串联热泵机组而言，其制热量可以达到10MW以上。如果要满足该制热量，需要大大增加电机驱动功率。如果不采用本公开的技术方案，而是采用单压缩机驱动的方式，会增大电机体积，并且会降低电机转速，不利于串联热泵机组效率提升。采用本公开实施例提供的双压缩机的结构形式，可以将电机功率分摊到两个压缩机上，这样可以降低单个电极的功率降低，提高电机转速，有利于提供串联热泵机组的能效。
继续参见图1，第二压级压缩机2位于第一压级压缩机1的下游且两者连通。第二压级压缩机2接收第一压级压缩机1传输过来的冷媒，并进行压缩。第二压级压缩 机2包括至少一个第二叶轮201，第二补气支路7与第一压级压缩机1的连通位置(即补气位置B)位于最上游的第二叶轮201的上游。第二压级压缩机2采用离心压缩机，结构紧凑，体积小，流量大，功率大且有利于节能，能实现能源的高效利用。
第一换热器3安装于第二压级压缩机2的下游且两者连通。第一换热器3具体比如为冷凝器。冷凝器位于第二压级压缩机2的下游，以利用第二压级压缩机2输出的高温冷媒进行换热。第一换热器3具体可以采用管壳式换热器等结构紧凑、换热效率高的换热器。
闪发器组件4包括第一节流元件41以及至少两个串联的闪发器42，串联的两个闪发器42之间安装有第一节流元件41，闪发器组件4中间采用一个第一节流元件41形成两个独立的闪发压力空间。闪发器42位于第一换热器3的下游且两者连通。在一些实施例中，以闪发器组件4包括两个独立的闪发器42为例。其中一个闪发器42与第二压级压缩机2通过第二补气支路7连通，另一个闪发器42与第一压级压缩机1通过第一补气支路6连通。第一补气支路6和第二补气支路7至少其中之一被构造为在导通状态、断开状态之间切换。第一补气支路6和第二补气支路7是相对独立的，即其中一个补气支路导通或者断开，并不影响另一个补气支路的通断状态。
继续参见图1，第二换热器5位于闪发器组件4的下游；第二换热器5与第一压级压缩机1连通。第二换热器5具体可以采用管壳式换热器等结构紧凑、换热效率高的换热器。
参见图1，在一些实施例中，串联热泵机组还包括第二节流元件10，第二节流元件10安装于第一换热器3和闪发器组件4之间。第二节流元件10对第一换热器3输出的冷媒起到节流作用，节流后的冷媒进入到闪发器组件4内。当第二节流元件10的开度调节到最大，第二节流元件10不再起到节流作用，而是起到导通冷媒支路的作用。
继续参见图1，串联热泵机组还包括第三节流元件11，第三节流元件11安装于闪发器组件4和第二换热器5之间。第三节流元件11对闪发器组件4输出的冷媒起到节流作用，节流后的冷媒进入到第二换热器5内。当第三节流元件11的开度调节到最大，第三节流元件11不再起到节流作用，而是起到导通冷媒支路的作用。
参见图1，在制冷循环时，冷媒按照以下路径流动：第二换热器5、第一压缩机1、第二压缩机2、第一换热器3、第二节流元件10、闪发器组件4、第一节流元件41、第三节流元件11。第二节流元件10节流后的闪发气体补气至第二压级压缩机2的吸气 口(B口)，第一节流元件41节流后的闪发气体补气至第一压级压缩机1第一级压缩的排气口(A口)。
参见图2，图2示意了四级压缩。与上述一些实施例不同的是，在图2所示意的一些实施例中，第二压级压缩机2采用了两个第二叶轮201。第二压级压缩机2的补气位置有更多的选择，补气位置可位于最上游的第二叶轮201之前，也可位于两个第二叶轮201之间。闪发器组件4包括第一节流元件41以及三个串联的闪发器42。整个串联热泵机组为四级压缩，采用中间三补气，除了上文介绍的第二补气支路7、第一补气支路6，串联热泵机组还设置有第三补气支路8，均从闪发器组件4补气。
四级压缩时，闪发器组件4内部设两个隔板，形成三个独立的闪发压力空间，制冷循环过程为：第二换热器5、第一压级压缩机1、第二压级压缩机2、第一换热器3、第二节流元件10、闪发器组件4、第一节流元件41、第四节流元件43、第三节流元件11。各个节流元件可为固定孔板、电动蝶阀等。上述方案，采用一个闪发器组件即可实现多级补气，节省空间性价比高。
第二节流元件10后的闪发气体补气至三级压缩排气口，即补气至第二压级压缩机2的一级叶轮的排气口(C口)，第四节流元件43节流后的闪发气体补气至第一压级压缩机1的第一级压缩的排气口(A口)。第一节流元件41后的闪发气体补气至第二压级压缩机2的吸气口(B口)。
在上述的各个实施例中，串联热泵机组设计制造完成之后，第二压级压缩机2、第一压级压缩机1的压比就确定了。如果设计参数为第二压级压缩机2、第一压级压缩机1的压比相同，则串联热泵机组采用等压比控制方式来控制双压缩机负荷。如果设计参数为第二压级压缩机2、第一压级压缩机1的压比不相同，则串联热泵机组采用等电流百分比控制方式来控制双压缩机负荷。
此处以三级压缩举例说明，第一压级压缩机1采用双级压缩，第二压级压缩机2采用单级压缩。串联热泵机组以采用等压比控制方式为例进行描述。第一压级压缩机1的压比为Pd,高压缩级压缩机的压比为Pg，设定上限阈值Xmax为压比设定上限阈值为Pmax,设定下限阈值Xmin为压比设定下限阈值为Pmin。第一差值为第二压级压缩机2的压比的平方与第一压级压缩机1的压比的差值的绝对值。
参见图3和图4，下面介绍串联热泵机组控制方法的具体实现方式。
串联热泵机组控制方法包括以下步骤：
步骤S100，根据串联热泵机组的出水温度与设定水温的温度差值判断串联热泵机 组执行以下其中一种操作：机组保持、机组加载、机组卸载。串联热泵机组包括串联的第一压级压缩机1和第二压级压缩机2，第二压级压缩机2的压级高于第一压级压缩机1的压级。
参见图1，在一些实施例中，温度差值为0.2℃～0.4℃。本文以0.2℃为例。
串联热泵机组的控制目标为热泵出水温度。通过计算串联热泵机组实际出水温度与设定温度的差值，可以确定对串联热泵机组采取何种操作。△T＝设定温度-实际出水温度。△T大于0，说明设定温度高于实际出水温度；△T小于0，说明设定温度低于实际出水温度。
当-0.2℃≤△T≤0.2℃时，说明串联热泵机组的工作参数满足设定要求，此时第一压级压缩机1和第二压级压缩机2均保持当前的频率。
如果△T＞+0.2℃，说明设定温度高于实际出水温度且实际出水温度和设定水温的差值比较大，串联热泵机组的执行能力需要增大，压缩机的频率需要增加，即进行加载操作。
如果△T＜-0.2℃，说明实际出水温度高于设定温度且实际出水温度和设定水温的差值比较大，机组卸载，压缩机频率卸载。执行能力是指压缩机的运行频率。如果压缩机保持当前的执行能力，则是指压缩机保持当前的运行频率。如果加载，则增加压缩机的运行频率。如果卸载，则减小压缩机的运行频率。
步骤S200，如果需要机组加载，则增加第一压级压缩机1和第二压级压缩机2的频率。如果需要机组卸载，则减少第一压级压缩机1和第二压级压缩机2的频率。如果需要保持，则第一压级压缩机1和第二压级压缩机2的频率均保持不变。
在上述的步骤S200中，根据水温需求，执行能力加载时，同时加载两个压缩机频率，同时判定第二压级压缩机2压比的平方与第一压级压缩机1的压比Pd差值，该差值的绝对值为等压比模式下的第一差值。当时，和Pd中数值较大的对应的压缩机被保持执行能力，数值较小者对应的压缩机则被加载。
参见图3和图4，具体来说，在机组加载过程中，即图4中左侧支路对应的内容，串联热泵机组控制方法具体包括以下步骤：同时增加第二压级压缩机2的设定参数和第一压级压缩机1的频率。然后，判断第二压级压缩机2的设定参数和第一压级压缩机1的设定参数的第一差值是否大于或者等于设定上限阈值Pmax。
如果第一差值大于或者等于设定上限阈值Pmax，则保持第二压级压缩机2的设定参数和第一压级压缩机1的设定参数中较大者对应的压缩机的频率，并 对另一设定参数所对应的压缩机加载。如果第一差值小于设定上限阈值Pmax，则返回执行对第一压级压缩机1和第二压级压缩机2均被加载的操作，使得第一压级压缩机1和第二压级压缩机2均被增加频率。
具体来说，如果第一差值大于或者等于设定上限阈值Pmax，并且大于Pd，则保持第二压级压缩机2的执行能力，单独对第一压级压缩机1进行加载。如果Pd大于则保持第一压级压缩机1的执行能力，单独对第二压级压缩机2进行加载。如果第一差值小于设定上限阈值Pmax，则返回执行同时对第一压级压缩机1和第二压级压缩机2进行加载的步骤。
在上述机组加载调节过程中，第一差值是实时变化的。在机组加载过程中，当进入一个压缩机加载、另一个压缩机保持的特殊控制时，当需要加载的那个压缩机加载至时，再恢复同步加载的正常控制模式，即当 则恢复至对第一压级压缩机1和第二压级压缩机2都加载的模式。
参见图3和图4，如上文所述的，在机组加载过程中，当进入一个压缩机加载、另一个压缩机保持的特殊控制时，需要判断第二压级压缩机2和加载后的第一压级压缩机1的设定参数的第一差值是否小于设定下限阈值Xmin。具体来说，如果第一差值小于设定下限阈值Pmin，则返回执行对第一压级压缩机1和第二压级压缩机2均加载的操作。如果第一差值大于或者等于设定下限阈值Pmin，则返回执行保持第一压级压缩机1和第二压级压缩机2中设定参数中较大者对应的压缩机的频率，并对另一设定参数所对应的压缩机加载的操作。展开来说，如果且则对所对应的第二压级压缩机2保持执行能力，对Pd所对应的第一压级压缩机1加载，直至恢复至对第一压级压缩机1和第二压级压缩机2均加载。如果且则对所对应的第二压级压缩机2加载，对Pd所对应的第一压级压缩机1保持，直至恢复至对第一压级压缩机1和第二压级压缩机2均加载。
参见图3和图4，在一些实施例中，如果串联热泵机组为机组保持状态，则对应图4中间支路对应的内容，则第一压级压缩机1和第二压级压缩机2均保持当前的频率，无需调整。
参见图3和图4，具体是指图4右侧支路对应的内容，在机组卸载过程中，串联热泵机组控制方法具体包括以下步骤：同时卸载第一压级压缩机1和第二压级压缩机2的频率；随后判断第一压级压缩机1和第二压级压缩机2的设定参数的第一差值是 否大于或者等于设定上限阈值Pmax。
如果第一差值大于或者等于设定上限阈值Pmax，则保持第一压级压缩机1和第二压缩机2中较小者对应的状态，对较大者单独卸载；如果第一差值小于设定上限阈值Pmax，则返回执行对第一压级压缩机1和第二压级压缩机2均卸载的步骤。具体来说，如果第一差值大于或者等于设定上限阈值Pmax，并且大于Pd，则单独对第二压级压缩机2卸载，保持第一压级压缩机1的执行能力。如果Pd大于则单独对第一压级压缩机1进行卸载，保持第二压级压缩机2的执行能力不变。如果第一差值小于设定上限阈值Pmax，则返回执行同时对第一压级压缩机1和第二压级压缩机2卸载的步骤。
在上述机组卸载调节过程中，当进入保持第一压级压缩机1和第二压缩机2中较小者对应的状态，对较大者单独卸载的过程时，第一差值是实时变化的。当则返回执行对第一压级压缩机1和第二压级压缩机2都进行卸载的步骤；否则，返回执行对第一压级压缩机1和第二压缩机2中较小者保持，对较大者单独卸载的步骤。
具体来说，如果且则单独对所对应的第二压级压缩机2进行卸载，对Pd所对应的第一压级压缩机1保持当前的执行能力，直至丨恢复至对第一压级压缩机1和第二压级压缩机2均卸载的操作。如果且则对所对应的第二压级压缩机2保持当前的执行能力，单独对Pd所对应的第一压级压缩机1卸载，直至恢复至对第一压级压缩机1和第二压级压缩机2均卸载的步骤。
上述技术方案提供的串联热泵机组控制方法，采用等压比的控制方式，使得转速合理分配，减少了压缩机磨轴现象，避免了压缩机功率过高或者过低，使得串联热泵机组可靠运行；避免了第一压级压缩机1转速过高，第二压级压缩机2转速过低时不能消耗第一压级压缩机1排出的冷媒，造成整机功率过大，能力、能效却较低的现象。
参见图5，下面介绍采用等电流控制方式的内容。
参见图5，在一些实施例中，如果串联热泵机组设计的参数是第一压级压缩机1和第二压级压缩机2的压比不相同，则串联热泵机组采用等电流百分比控制。此模式下，第一差值为第二压级压缩机2的电流百分比与第一压级压缩机1的电流百分比的差值的绝对值。设定上限阈值Xmax为电流百分比设定上限阈值Imax。设定下限阈值Xmin为电流百分比设定下限阈值Imin。电流百分比为压缩机当前实际运行电流与满负荷额 定电流的比值。第一压级压缩机1电流百分比为Id,高压缩级压缩机电流百分比为Ig。将机组满负荷运行时对应的实际电流设值为压缩机额定电流，电流百分比最大差值为Imax,电流百分比最小差值为Imin。
串联热泵机组控制方法包括以下步骤：
首先，根据串联热泵机组的出水温度与设定水温的温度差值判断串联热泵机组执行哪种操作：机组保持、机组加载还是机组卸载。串联热泵机组包括串联的第一压级压缩机1和第二压级压缩机2，第二压级压缩机2的压级高于第一压级压缩机1的压级。
串联热泵机组的控制目标为热泵出水温度。通过计算串联热泵机组实际出水温度与设定温度的差值，△T＝设定温度-实际出水温度。后文仍以0.2℃为例。控制逻辑与上文描述的温度内容相同：当-0.2℃≤△T≤0.2℃时，此时第一压级压缩机1和第二压级压缩机2均保持当前的频率。如果△T＞+0.2℃，进行机组加载操作。如果△T＜-0.2℃，进行机组卸载操作。
其次，如果需要机组加载，则增加第一压级压缩机1和第二压级压缩机2至少其中之一的频率。如果需要机组卸载，则减少第一压级压缩机1和第二压级压缩机2至少其中之一的频率。如果需要保持，则第一压级压缩机1和第二压级压缩机2的频率均保持不变。
根据水温需求，执行机组加载时，同时加载两个压缩机频率，然后判定第二压级压缩机2电流百分比Ig与第一压级压缩机1的电流百分比Id差值。当丨Ig-Id丨≥Imax时，Ig和Id中数值较大的对应的压缩机被保持执行能力，数值较小的对应的压缩机则被加载。
参见图5，具体来说，在机组加载过程中，即图5中左侧支路对应的内容，串联热泵机组控制方法还包括以下步骤：判断第二压级压缩机2的设定参数和第一压级压缩机1的设定参数的第一差值是否大于或者等于设定上限阈值Imax。
如果第一差值丨Ig-Id丨大于或者等于设定上限阈值Imax，则保持第二压级压缩机2的设定参数和第一压级压缩机1的设定参数中较大者对应的压缩机的频率，并对另一设定参数所对应的压缩机加载。如果第一差值小于设定上限阈值Imax，则返回执行第一压级压缩机1和第二压级压缩机2均加载的步骤。
具体来说，等电流控制模式下，机组加载控制中，如果第一差值丨Ig-Id丨大于或者等于设定上限阈值Imax，并且Ig大于Id，则保持第二压级压缩机2的执行能力， 单独对第一压级压缩机1进行加载。如果Id大于Ig，则保持第一压级压缩机1的执行能力，单独对第二压级压缩机2进行加载。如果第一差值丨Ig-Id丨小于设定上限阈值Imax，则返回执行同时对第一压级压缩机1和第二压级压缩机2加载的步骤。
参见图5，在机组加载过程中，在进入保持第二压级压缩机2的设定参数和第一压级压缩机1的设定参数中较大者对应的压缩机的频率，并对另一设定参数所对应的压缩机加载的步骤之后，串联热泵机组控制方法还包括以下步骤：判断第二压级压缩机2和第一压级压缩机1的设定参数的第一差值是否小于设定下限阈值Imin。
如果第一差值丨Ig-Id丨小于设定下限阈值Imin，则返回对第一压级压缩机1和第二压级压缩机2均加载的步骤。如果第一差值大于或者等于设定下限阈值Imin，则返回执行保持第一压级压缩机1和第二压级压缩机2中设定参数中较大者对应的压缩机的频率，并对另一设定参数所对应的压缩机加载的步骤。
具体来说，如果丨Ig-Id丨≥Imin，且Ig>Id，则对Ig所对应的第二压级压缩机2保持执行能力，单独对Id所对应的第一压级压缩机1加载，直至丨Ig-Id丨<Imin，返回对第一压级压缩机1和第二压级压缩机2均加载的步骤。如果丨Ig-Id丨≥Imin，且Ig<Id，则单独对Ig所对应的第二压级压缩机2加载，对Id所对应的第一压级压缩机1保持当前的执行能力，直至丨Ig-Id丨<Imin，返回至对第一压级压缩机1和第二压级压缩机2均加载的步骤。
参见图5，如果串联热泵机组保持当前的运行参数，即图5中间支路对应的内容，则第一压级压缩机1和第二压级压缩机2均保持当前的频率，无需调整。
参见图5右侧支路对应的内容，在机组卸载过程中，串联热泵机组控制方法具体包括以下步骤：同时卸载第一压级压缩机1和第二压级压缩机2的频率；判断第一压级压缩机1和第二压级压缩机2的设定参数的第一差值是否大于或者等于设定上限阈值Imax。
如果第一差值丨Ig-Id丨大于或者等于设定上限阈值Imax，则保持第一压级压缩机1和第二压级压缩机2的设定参数较小者对应的压缩机的频率，而对另一压缩机单独卸载；如果第一差值丨Ig-Id丨小于设定上限阈值Imax，则返回执行对第一压级压缩机1和第二压级压缩机2均卸载的步骤。具体来说，如果第一差值丨Ig-Id丨大于或者等于设定上限阈值Imax，并且Ig大于Id，则单独对Ig所对应的第二压级压缩机2卸载，保持Id所对应的第一压级压缩机1的执行能力。如果Id大于Ig，则单独对第一压级压缩机1进行卸载，保持第二压级压缩机2的执行能力不变。如果第一差值丨Ig- Id丨小于设定上限阈值Imax，则返回同时对第一压级压缩机1和第二压级压缩机2卸载的步骤。
继续参见图5，等电流模式下，在机组卸载过程中，在保持第一压级压缩机1和第二压级压缩机2的设定参数较小者对应的压缩机的频率，而对另一压缩机单独卸载的步骤之后，串联热泵机组控制方法还包括以下步骤：判断卸载后的第二压级压缩机2和保持的第一压级压缩机1的设定参数的第一差值丨Ig-Id丨是否小于设定下限阈值Imin；如果第一差值小于设定下限阈值Imin，则返回至对第一压级压缩机1和第二压级压缩机2均卸载的步骤；如果第一差值丨Ig-Id丨大于或者等于设定下限阈值Imin，则返回至保持第一压级压缩机1和第二压级压缩机2的设定参数较小者对应的压缩机的频率，而对另一压缩机单独卸载的步骤。具体来说，如果丨Ig-Id丨≥Imin，且Ig>Id，则对Ig所对应的第二压级压缩机2进行卸载，对Id所对应的第一压级压缩机1保持当前的执行能力，直至丨Ig-Id丨<Imin，恢复至对第一压级压缩机1和第二压级压缩机2均卸载。如果丨Ig-Id丨≥Imin，且Ig<Id，则对Ig所对应的第二压级压缩机2保持当前的执行能力，对Id所对应的第一压级压缩机1卸载，直至丨Ig-Id丨<Imin，恢复至对第一压级压缩机1和第二压级压缩机2均卸载。
上述技术方案提供的串联热泵机组控制方法，采用等电流百分比的控制方式，使得转速合理分配，避免了压缩机功率过高或者过低，使得串联热泵机组可靠运行。
上述技术方案提供的串联热泵机组，由于采用双压缩机等压比、等电流百分比的控制方式，双压缩机同时加载、卸载，只需为第二压级压缩机2设置防喘线，即保证第二压级压缩机2不喘振。在第二压级压缩机2不喘振的情况下，整个机组都不发生喘振。此时转回到负荷控制方式处，在等压比或等电流百分比控制模式下，当机组执行能力减小卸载频率时，两压缩机执行同步卸载或单独卸载的过程中，高压级卸载到最小频率+2Hz以下时，两压缩机频率保持，此时机组已经卸载到极限最小负荷，无法再行卸载。如果实际负荷更小，机组最小负荷高于实际负荷，机组的水温便会高于设定温度，直到机组运行到待机温度正常待机即可，至此完成整个负荷与防喘控制，防喘控制方式简易且可靠性高。
本公开一些实施例还提供一种串联热泵机组控制系统，包括存储器以及耦接至存储器的处理器。处理器被配置为基于存储在存储器中的指令，执行如本公开任一技术方案所提供的串联热泵机组控制方法。
本公开另一些实施例还提供一种计算机可读存储介质，其上存储有计算机程序， 该程序被处理器执行时实现本公开任一技术方案所提供的串联热泵机组控制方法。
这里所描述的处理器可以包括通用处理器、数字信号处理器(DSP)、专用集成电路(ASIC)、现场可编程门阵列(FPGA)或其它可编程逻辑器件、分立的门或晶体管逻辑、分立的硬件组件、或其设计成执行本文所描述功能的任何组合来实现或执行。通用处理器可以是微处理器，但在替换方案中，该处理器可以是任何常规的处理器、控制器、微控制器、或状态机。处理器还可以被实现为计算设备的组合，例如DSP与微处理器的组合、多个微处理器、与DSP核心协作的一个或多个微处理器、或任何其他此类配置。
存储介质可以是能被计算机访问的任何可用介质。作为示例而非限定，这样的计算机可读介质可包括RAM、ROM、EEPROM、CD-ROM或其它光盘存储、磁盘存储或其它磁存储设备、或能被用来携带或存储指令或数据结构形式的合意程序代码且能被计算机访问的任何其它介质。任何连接也被正当地称为计算机可读介质。例如，如果软件是使用同轴电缆、光纤电缆、双绞线、数字订户线(DSL)、或诸如红外、无线电、以及微波之类的无线技术从web网站、服务器、或其它远程源传送而来，则该同轴电缆、光纤电缆、双绞线、DSL、或诸如红外、无线电、以及微波之类的无线技术就被包括在介质的定义之中。如本文中所使用的盘(disk)和碟(disc)包括压缩碟(CD)、激光碟、光碟、数字多用碟(DVD)、软盘和蓝光碟，其中盘(disk)往往以磁的方式再现数据，而碟(disc)用激光以光学方式再现数据。上述的组合也应被包括在计算机可读介质的范围内。
本领域内的技术人员应当明白，本公开的方法实施例可提供为方法、系统、或计算机程序产品。因此，本公开可采用完全硬件实施例、完全软件实施例、或结合软件和硬件方面的实施例的形式。而且，本公开可采用在一个或多个其中包含有计算机可用程序代码的计算机可用非瞬时性存储介质(包括但不限于磁盘存储器、CD-ROM、光学存储器等)上实施的计算机程序产品的形式。
本公开是参照根据本公开实施例的方法、设备(系统)、和计算机程序产品的流程图和/或方框图来描述的。应理解为可由计算机程序指令实现流程图和/或方框图中的每一流程和/或方框、以及流程图和/或方框图中的流程和/或方框的结合。可提供这些计算机程序指令到通用计算机、专用计算机、嵌入式处理机或其他可编程数据处理设备的处理器以产生一个机器，使得通过计算机或其他可编程数据处理设备的处理器 执行的指令产生用于实现在流程图一个流程或多个流程和/或方框图一个方框或多个方框中指定的功能的装置。
这些计算机程序指令也可存储在能引导计算机或其他可编程数据处理设备以特定方式工作的计算机可读存储器中，使得存储在该计算机可读存储器中的指令产生包括指令装置的制造品，该指令装置实现在流程图一个流程或多个流程和/或方框图一个方框或多个方框中指定的功能。
这些计算机程序指令也可装载到计算机或其他可编程数据处理设备上，使得在计算机或其他可编程设备上执行一系列操作步骤以产生计算机实现的处理，从而在计算机或其他可编程设备上执行的指令提供用于实现在流程图一个流程或多个流程和/或方框图一个方框或多个方框中指定的功能的步骤。
在本公开的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”、“内”、“外”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本公开和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本公开保护范围的限制。
最后应当说明的是:以上实施例仅用以说明本公开的技术方案而非对其限制；尽管参照较佳实施例对本公开进行了详细的说明，所属领域的普通技术人员应当理解：依然可以对本公开的具体实施方式进行修改或者对部分技术特征进行等同替换；而不脱离本公开技术方案的精神，其均应涵盖在本公开请求保护的技术方案范围当中。

Claims (15)

  1. 一种串联热泵机组控制方法，包括以下步骤：
    根据串联热泵机组的出水温度与设定水温的温度差值判断所述串联热泵机组执行以下其中一种操作：机组保持、机组加载、机组卸载；所述串联热泵机组包括串联的第一压级压缩机(1)和第二压级压缩机(2)，所述第二压级压缩机(2)的压级高于所述第一压级压缩机(1)的压级；
    如果需要执行机组加载的操作，则增加所述第一压级压缩机(1)和所述第二压级压缩机(2)中至少其中之一的频率；如果需要执行机组卸载的操作，则减少所述第一压级压缩机(1)和所述第二压级压缩机(2)中至少其中之一的频率；如果需要执行机组保持的操作，则所述第一压级压缩机(1)和所述第二压级压缩机(2)的频率均保持不变。
  2. 根据权利要求1所述的串联热泵机组控制方法，其中在执行机组加载操作的过程中，所述串联热泵机组控制方法执行以下步骤：
    同时增加所述第一压级压缩机(1)和所述第二压级压缩机(2)的频率；
    判断所述第二压级压缩机(2)的设定参数和所述第一压级压缩机(1)的设定参数的第一差值是否大于或者等于设定上限阈值Xmax；
    如果所述第一差值大于或者等于设定上限阈值Xmax，则保持所述第二压级压缩机(2)的设定参数和所述第一压级压缩机(1)的设定参数中较大者对应的压缩机的频率，并对另一设定参数所对应的压缩机加载；如果所述第一差值小于设定上限阈值Xmax，则返回执行所述同时增加所述第一压级压缩机(1)和所述第二压级压缩机(2)的频率的步骤。
  3. 根据权利要求2所述的串联热泵机组控制方法，其中在执行机组加载操作的过程中，在所述如果所述第一差值大于或者等于设定上限阈值Xmax，则保持所述第二压级压缩机(2)的设定参数和所述第一压级压缩机(1)的设定参数中较大者对应的压缩机的频率，并对另一设定参数所对应的压缩机执行加载操作的步骤之后，所述串联热泵机组控制方法还包括以下步骤：
    判断所述第一压级压缩机(1)和所述第二压级压缩机(2)的设定参数的第一差值是否小于设定下限阈值Xmin；
    如果所述第一差值小于设定下限阈值Xmin，则返回执行所述同时增加所述第一压 级压缩机(1)和所述第二压级压缩机(2)的频率的步骤；如果所述第一差值大于或者等于设定下限阈值Xmin，则返回执行所述保持所述第二压级压缩机(2)的设定参数和所述第一压级压缩机(1)的设定参数中较大者对应的压缩机的频率，并对另一设定参数所对应的压缩机加载的步骤。
  4. 根据权利要求1所述的串联热泵机组控制方法，其中在执行机组卸载操作的过程中，所述串联热泵机组控制方法执行以下步骤：
    同时卸载所述第一压级压缩机(1)和所述第二压级压缩机(2)的频率；
    判断所述第一压级压缩机(1)和所述第二压级压缩机(2)的设定参数的第一差值是否大于或者等于设定上限阈值Xmax；
    如果所述第一差值大于或者等于设定上限阈值Xmax，则保持所述第一压级压缩机(1)和所述第二压级压缩机(2)中设定参数较小者对应的压缩机的频率，对另一设定参数所对应的压缩机卸载；如果所述第一差值小于设定上限阈值Xmax，则返回执行同时卸载所述第一压级压缩机(1)和所述第二压级压缩机(2)的频率的步骤。
  5. 根据权利要求4所述的串联热泵机组控制方法，其中在执行机组卸载操作的过程中，在所述第一差值大于或者等于设定上限阈值Xmax，则保持所述第一压级压缩机(1)和所述第二压级压缩机(2)中设定参数较小者对应的压缩机的频率，对另一设定参数所对应的压缩机卸载的步骤之后，所述串联热泵机组控制方法还包括以下步骤：
    判断卸载后的所述第二压级压缩机(2)和保持的所述第一压级压缩机(1)的设定参数的第一差值是否小于设定下限阈值Xmin；
    如果第一差值小于设定下限阈值Xmin，则返回执行同时卸载所述第一压级压缩机(1)和所述第二压级压缩机(2)的频率的步骤；如果第一差值大于或者等于设定下限阈值Xmin，则返回执行所述保持所述第一压级压缩机(1)和所述第二压级压缩机(2)中设定参数较小者对应的压缩机的频率，对另一设定参数所对应的压缩机卸载的步骤。
  6. 根据权利要求1～5任一所述的串联热泵机组控制方法，其中所述串联热泵机组采用等压比控制，则所述第一差值为所述第二压级压缩机(2)的压比的平方与所述第一压级压缩机(1)的压比的差值的绝对值。
  7. 根据权利要求2所述的串联热泵机组控制方法，其中所述串联热泵机组采用等压比控制，所述设定上限阈值Xmax为压比设定上限阈值Pmax。
  8. 根据权利要求3所述的串联热泵机组控制方法，其中所述串联热泵机组采用等 压比控制，所述设定下限阈值Xmin为压比设定下限阈值Pmin。
  9. 根据权利要求1～5任一所述的串联热泵机组控制方法，其中所述串联热泵机组采用等电流百分比控制，则所述第一差值为所述第二压级压缩机(2)的电流百分比与所述第一压级压缩机(1)的电流百分比的差值的绝对值。
  10. 根据权利要求2或者3所述的串联热泵机组控制方法，其中所述串联热泵机组采用等电流百分比控制，所述设定上限阈值Xmax为电流百分比设定上限阈值Imax。
  11. 根据权利要求3所述的串联热泵机组控制方法，其中所述串联热泵机组采用等电流百分比控制，所述设定下限阈值Xmin为电流百分比设定下限阈值Imin。
  12. 根据权利要求1～11任一所述的串联热泵机组控制方法，其中所述温度差值为0.2℃～0.4℃。
  13. 根据权利要求1～11任一所述的串联热泵机组控制方法，其中所述第二压级压缩机(2)的运行参数满足防喘线的要求。
  14. 一种串联热泵机组控制系统，包括：
    存储器；和
    耦接至所述存储器的处理器，所述处理器被配置为基于存储在所述存储器中的指令，执行如权利要求1～13任一所述的串联热泵机组控制方法。
  15. 一种计算机可读存储介质，其中其上存储有计算机程序，该程序被处理器执行时实现如权利要求1～13任一所述的串联热泵机组控制方法。
PCT/CN2024/116193 2023-12-15 2024-09-02 串联热泵机组控制方法、系统以及可读存储介质 Pending WO2025123797A1 (zh)

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