CN115523677A - Heat pump system control method, temperature adjusting device and readable storage medium - Google Patents

Heat pump system control method, temperature adjusting device and readable storage medium Download PDF

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CN115523677A
CN115523677A CN202110711527.5A CN202110711527A CN115523677A CN 115523677 A CN115523677 A CN 115523677A CN 202110711527 A CN202110711527 A CN 202110711527A CN 115523677 A CN115523677 A CN 115523677A
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target
outlet
temperature
inlet
heat exchanger
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不公告发明人
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Chongqing Cvs Environmental Protection Technology Co ltd
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Chengdu Huanentropy Technology Co ltd
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    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/64—Electronic processing using pre-stored data
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/65—Electronic processing for selecting an operating mode
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/88—Electrical aspects, e.g. circuits
    • 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
    • F25B39/00—Evaporators; Condensers
    • 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

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
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  • Fuzzy Systems (AREA)
  • Mathematical Physics (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

The application provides a heat pump system control method, a temperature adjusting device and a readable storage medium. The method comprises the following steps: acquiring a working parameter set of a heat pump system and a target working mode of the heat pump system; determining a target flow rate of a target throttling device corresponding to a target working mode in the heat pump system for conveying the refrigerant according to a preset algorithm and the indoor comprehensive temperature in the working parameter set, and the current temperature and the current pressure of the outlet end of an indoor heat exchanger in the heat pump system; the target throttling device is controlled to deliver the refrigerant at the target flow rate. In this scheme, through the current temperature and the current pressure that detect indoor comprehensive temperature, indoor heat exchanger's exit end, so, can confirm the target velocity of flow that target throttling arrangement carried the refrigerant, then, control target throttling arrangement carries the refrigerant with the target velocity of flow, so, can realize heat pump system's accurate control under target mode of operation, be favorable to promoting heat exchange efficiency and user experience.

Description

Heat pump system control method, temperature adjusting device and readable storage medium
Technical Field
The application relates to the field of heat pump control, in particular to a heat pump system control method, temperature adjusting equipment and a readable storage medium.
Background
In the field of thermal management, heat pump systems may provide a more energy efficient option than boilers and air conditioners under conditions requiring moderate cooling or heating to achieve temperature regulation. The heat pump system is limited by a system framework of the heat pump system, temperature regulation of the heat pump system is generally achieved roughly according to a difference value between a set temperature and a current room temperature in a temperature regulation process, regulation precision is insufficient, and heat exchange efficiency is low.
Disclosure of Invention
An object of the embodiments of the present application is to provide a heat pump system control method, a temperature adjustment device, and a readable storage medium, which can accurately control a heat pump system and is beneficial to improving heat exchange efficiency.
In order to achieve the above object, the embodiments of the present application are implemented as follows:
in a first aspect, an embodiment of the present application provides a heat pump system control method, where the method includes:
acquiring a working parameter set of a heat pump system and a target working mode of the heat pump system;
determining a target flow rate of a target throttling device in the heat pump system corresponding to the target working mode for conveying the refrigerant according to a preset algorithm, the indoor comprehensive temperature in the working parameter set, and the current temperature and the current pressure at the outlet end of an indoor heat exchanger in the heat pump system;
and controlling the target throttling device to convey the refrigerant at the target flow rate.
In the above embodiment, by detecting the indoor integrated temperature, the current temperature and the current pressure at the outlet end of the indoor heat exchanger, the target flow rate at which the target throttling device conveys the refrigerant can be determined, and then the target throttling device is controlled to convey the refrigerant at the target flow rate, so that the accurate control of the heat pump system can be realized in the target working mode, and the improvement of the heat exchange efficiency and the user experience are facilitated.
With reference to the first aspect, in some alternative embodiments, the heat pump system includes a compressor, an indoor heat exchanger, an outdoor heat exchanger, and a first common rail line, an inlet of each heat exchanger selectively communicating with an outlet of the compressor or in throttled communication with an outlet of the first common rail line, and an outlet of each heat exchanger selectively communicating with an inlet of the compressor or with an inlet of the first common rail line;
in a cooling mode, an outlet of the compressor is communicated with an inlet of the outdoor heat exchanger, an outlet of the outdoor heat exchanger is communicated with an inlet of the first common rail pipeline, an outlet of the first common rail pipeline is in throttling communication with an inlet of the indoor heat exchanger through the target throttling device, an outlet of the indoor heat exchanger is communicated with an inlet of the compressor, and the target throttling device is a throttling device arranged between the outlet of the first common rail pipeline and the inlet of the indoor heat exchanger in the heat pump system;
determining a target flow rate of a target throttling device in the heat pump system corresponding to the target working mode for conveying the refrigerant according to a preset algorithm, the indoor comprehensive temperature in the working parameter set, and the current temperature and the current pressure at the outlet end of an indoor heat exchanger in the heat pump system, wherein the target flow rate comprises:
when the target working mode is the refrigeration mode, determining a target overheating temperature corresponding to the current temperature and the current pressure based on the corresponding relation between the temperature and the pressure and the overheating temperature of the indoor heat exchanger;
determining the target flow rate of the refrigerant sent by the target throttling device according to a first preset formula, wherein the first preset formula is as follows:
Figure BDA0003133957790000021
in the first predetermined formula, PWM ij Refers to the target flow rate;
PWM cal the flow rate to be corrected;
d denotes a first predetermined coefficient;
e denotes a second predetermined coefficient;
T B refers to the target superheat temperature;
T Bset setting the overheat temperature;
T D refers to the indoor integrated temperature;
T set refers to the set temperature.
In the above embodiment, in the refrigeration mode, the target flow rate of the refrigerant sent by the target throttling device can be accurately calculated through the first preset formula, and then the target throttling device is controlled to send the refrigerant at the target flow rate, so that the heat pump system can be accurately controlled in the refrigeration mode, and the accurate adjustment of the temperature is facilitated.
With reference to the first aspect, in some alternative embodiments, the heat pump system includes a compressor, an indoor heat exchanger, an outdoor heat exchanger, and a first common rail line, an inlet of each heat exchanger selectively communicating with an outlet of the compressor or in throttled communication with an outlet of the first common rail line, and an outlet of each heat exchanger selectively communicating with an inlet of the compressor or with an inlet of the first common rail line;
in the heating mode, an outlet of the compressor is communicated with an inlet of the indoor heat exchanger, an outlet of the indoor heat exchanger is communicated with an inlet of the first common rail pipeline, an outlet of the first common rail pipeline is in throttling communication with an inlet of the outdoor heat exchanger through the target throttling device, an outlet of the outdoor heat exchanger is communicated with an inlet of the compressor, and the target throttling device is a throttling device arranged between the outlet of the first common rail pipeline and the inlet of the outdoor heat exchanger in the heat pump system;
determining a target flow rate of a target throttling device in the heat pump system corresponding to the target working mode for conveying the refrigerant according to a preset algorithm, the indoor comprehensive temperature in the working parameter set, and the current temperature and the current pressure at the outlet end of an indoor heat exchanger in the heat pump system, wherein the target flow rate comprises:
when the target working mode is the heating mode, determining a target supercooling temperature corresponding to the current temperature and the current pressure based on the corresponding relation between the temperature and the pressure and the supercooling temperature of the indoor heat exchanger;
determining the target flow rate of the refrigerant sent by the target throttling device according to a second preset formula, wherein the second preset formula is as follows:
Figure BDA0003133957790000031
wherein, in the second preset formula, PWM ij Refers to the target flow rate;
PWM cal the flow rate to be corrected;
d denotes a first predetermined coefficient;
e denotes a second predetermined coefficient;
T L refers to the target subcooling temperature;
T Lset the set supercooling temperature is indicated;
T D refers to the indoor integrated temperature;
T set refers to the set temperature.
In the above embodiment, in the heating mode, the target flow rate of the refrigerant sent by the target throttling device can be accurately calculated through the second preset formula, so that the heat pump system can be accurately controlled in the heating mode, and accurate adjustment of temperature is facilitated.
With reference to the first aspect, in some alternative embodiments, the number of the indoor heat exchangers is one, and the number of the outdoor heat exchangers is multiple;
acquiring a target working mode of the heat pump system, wherein the target working mode comprises the following steps:
acquiring the temperatures of the plurality of outdoor heat exchangers in the working parameter set;
when the temperatures of the outdoor heat exchangers meet preset defrosting conditions, determining that the target working mode is a heating defrosting mode;
in the heating and defrosting mode, an outlet of the compressor is respectively communicated with an inlet of the indoor heat exchanger and an inlet of a part of outdoor heat exchangers, an outlet of the part of outdoor heat exchangers and an outlet of the indoor heat exchangers are communicated with an inlet of the first common rail pipeline, an outlet of the first common rail pipeline is in throttling communication with an inlet of another part of outdoor heat exchangers through the target throttling device, an outlet of the another part of outdoor heat exchangers is communicated with an inlet of the compressor, and the target throttling device is a throttling device arranged between the outlet of the first common rail pipeline and the another part of outdoor heat exchangers in the heat pump system.
In the above embodiment, whether the outdoor heat exchanger meets the defrosting condition is detected, and when the defrosting condition is met, the heating defrosting mode is used, so that the existing frosting on the outdoor heat exchanger can be removed, or the heating is performed in advance before the outdoor heat exchanger frosts to avoid the frosting of the outdoor heat exchanger.
With reference to the first aspect, in some optional embodiments, the method further comprises:
and when the temperature of any outdoor heat exchanger in the plurality of outdoor heat exchangers is less than or equal to a first preset temperature, determining that the preset defrosting condition is met.
With reference to the first aspect, in some alternative embodiments, the heat pump system includes a compressor, an indoor heat exchanger, an outdoor heat exchanger, and a first common rail line, an inlet of each heat exchanger selectively communicates with an outlet of the compressor or with an outlet of the first common rail line in a throttling communication, an outlet of each heat exchanger selectively communicates with an inlet of the compressor or with an inlet of the first common rail line, the number of the indoor heat exchangers is plural, and the number of the outdoor heat exchangers is one;
in a heating and dehumidifying mode, an outlet of the compressor is communicated with an inlet of a part of indoor heat exchangers, an outlet of the part of indoor heat exchangers is communicated with an inlet of the first common rail pipeline, an outlet of the first common rail pipeline is in throttling communication with an inlet of another part of indoor heat exchangers through the first target throttling device, an outlet of the another part of indoor heat exchangers is communicated with an inlet of the compressor, an outlet of the first common rail pipeline is in throttling communication with an inlet of the outdoor heat exchanger through the second target throttling device, and an outlet of the outdoor heat exchanger is communicated with an inlet of the compressor;
the first target throttling device is a throttling device arranged between an outlet of the first common rail pipeline and an inlet of the other part of indoor heat exchangers in the heat pump system;
the second target throttling device is a throttling device arranged between an outlet of the first common rail pipeline and an inlet of the outdoor heat exchanger in the heat pump system;
the target flow rates include a first target flow rate corresponding to the first target throttling device and a second target flow rate corresponding to the second target throttling device;
determining a target flow rate of a target throttling device in the heat pump system corresponding to the target working mode for conveying the refrigerant according to a preset algorithm, the indoor comprehensive temperature in the working parameter set, and the current temperature and the current pressure at the outlet end of an indoor heat exchanger in the heat pump system, wherein the target flow rate comprises:
when the target working mode is the heating and dehumidifying mode, determining a target supercooling temperature corresponding to the current temperature and the current pressure at the outlet end of a target indoor heat exchanger based on the corresponding relation between the temperature, the pressure and the supercooling temperature of the indoor heat exchanger, wherein the target indoor heat exchanger is one of the indoor heat exchangers which is communicated with the outlet of the compressor;
determining a target dew point temperature corresponding to the current indoor temperature and the current indoor humidity based on the corresponding relationship among the temperature, the humidity and the dew point temperature;
determining the first target flow rate of the refrigerant sent by the first target throttling device and the second target flow rate of the refrigerant sent by the second target throttling device according to a third preset formula, wherein the third preset formula is as follows:
Figure BDA0003133957790000041
wherein the content of the first and second substances,in the third predetermined formula, PWM dew Refers to the first target flow rate;
PWM ij refers to the second target flow rate;
PWM cal the flow rate to be corrected;
d denotes a first predetermined coefficient;
e denotes a second predetermined coefficient;
f denotes a third preset coefficient;
g denotes a fourth predetermined coefficient;
T L refers to the target subcooling temperature;
T Lset the set supercooling temperature is indicated;
T D refers to the indoor integrated temperature;
T set the set temperature is indicated;
T dew refers to the target dew point temperature;
T in refers to the current indoor temperature;
TH in current indoor humidity;
TH max refers to a preset maximum humidity.
In the above embodiment, in the heating and dehumidifying mode, the corresponding target flow rates of the refrigerant sent by the first target throttling device and the refrigerant sent by the second target throttling device can be accurately calculated through the third preset formula, and then the first target throttling device and the second target throttling device are controlled to convey the refrigerant at the corresponding target flow rates, so that the heat pump system can be accurately controlled in the heating and dehumidifying mode, and accurate adjustment of temperature and humidity is facilitated.
With reference to the first aspect, in some alternative embodiments, the heat pump system includes a compressor, an indoor heat exchanger, an outdoor heat exchanger, and a first common rail line, an inlet of each heat exchanger selectively communicating with an outlet of the compressor or in throttled communication with an outlet of the first common rail line, and an outlet of each heat exchanger selectively communicating with an inlet of the compressor or with an inlet of the first common rail line; the number of the indoor heat exchangers is multiple, and the number of the outdoor heat exchangers is multiple;
in a dehumidification and defrosting mode, an outlet of the compressor is respectively communicated with an inlet of a part of indoor heat exchangers and an inlet of a part of outdoor heat exchangers, outlets of the part of indoor heat exchangers and the part of outdoor heat exchangers are communicated with an inlet of the first common rail pipeline, an outlet of the first common rail pipeline is in throttling communication with the other part of indoor heat exchangers through the first target throttling device, an outlet of the first common rail pipeline is also in throttling communication with inlets of the other part of outdoor heat exchangers through the second target throttling device, and outlets of the other part of indoor heat exchangers and the other part of outdoor heat exchangers are communicated with the inlet of the compressor;
the first target throttling device is a throttling device arranged between an outlet of the first common rail pipeline and an inlet of the other part of indoor heat exchangers in the heat pump system;
the second target throttling device is a throttling device arranged between an outlet of the first common rail pipeline and an inlet of the other part of outdoor heat exchanger in the heat pump system;
the target flow rates include a first target flow rate corresponding to the first target throttling device and a second target flow rate corresponding to the second target throttling device;
determining a target flow rate of a target throttling device in the heat pump system corresponding to the target working mode for conveying the refrigerant according to a preset algorithm, the indoor comprehensive temperature in the working parameter set, and the current temperature and the current pressure at the outlet end of an indoor heat exchanger in the heat pump system, wherein the target flow rate comprises:
when the target working mode is the dehumidification and defrosting mode, determining a target supercooling temperature corresponding to the current temperature and the current pressure at the outlet end of a target indoor heat exchanger based on the corresponding relation between the temperature, the pressure and the supercooling temperature of the indoor heat exchanger, wherein the target indoor heat exchanger is one of the indoor heat exchangers which is communicated with the outlet of the compressor;
determining a target dew point temperature corresponding to the current indoor temperature and the current indoor humidity based on the corresponding relationship among the temperature, the humidity and the dew point temperature;
determining the first target flow rate of the refrigerant sent by the first target throttling device and the second target flow rate of the refrigerant sent by the second target throttling device according to a fourth preset formula, wherein the fourth preset formula is as follows:
Figure BDA0003133957790000061
wherein, in the fourth preset formula, PWM dew Refers to the first target flow rate;
PWM ij refers to the second target flow rate;
PWM cal the flow rate to be corrected;
d denotes a first predetermined coefficient;
e denotes a second predetermined coefficient;
f denotes a third preset coefficient;
g denotes a fourth predetermined coefficient;
T L refers to the target subcooling temperature;
T Lset setting the supercooling temperature;
T D refers to the indoor integrated temperature;
T set the set temperature is indicated;
T dew refers to the target dew point temperature;
T in refers to the current indoor temperature;
TH in current indoor humidity;
TH max refers to a preset maximum humidity.
In the foregoing embodiment, in the dehumidification and defrost mode, the corresponding target flow rates at which the first target throttling device and the second target throttling device respectively deliver the refrigerant may be accurately calculated through a fourth preset formula, and then the first target throttling device and the second target throttling device are controlled to deliver the refrigerant at the corresponding target flow rates, so that the heat pump system may be accurately controlled in the dehumidification and defrost mode, and accurate control of humidity and defrost is facilitated.
With reference to the first aspect, in some optional embodiments, when the target operation mode is an operation mode to be switched determined from a received mode switching command, before controlling the target throttling device to deliver the refrigerant at the target flow rate, the method further includes:
and controlling the heat pump system to enter a standby state, and then switching to the target working mode from the standby state.
In the above embodiment, when the mode switching is required, the heat pump system is controlled to enter the standby state first and then switched to the target working state, so that the phenomenon that the impact of the refrigerant on the pipeline is too large to affect the service life of the heat pump or damage the heat pump system due to the direct mode switching can be avoided.
In a second aspect, the present application further provides a temperature adjustment device, including a control module and a heat pump system;
the control module is used for acquiring a working parameter set of the heat pump system and a target working mode of the heat pump system;
the control module is further used for determining a target flow rate of a target throttling device in the heat pump system corresponding to the target working mode for conveying the refrigerant according to a preset algorithm and the indoor comprehensive temperature in the working parameter set, and the current temperature and the current pressure of the outlet end of the indoor heat exchanger in the heat pump system;
the control module is further configured to control the target throttling device to deliver refrigerant at the target flow rate.
With reference to the second aspect, in some alternative embodiments, the heat pump system includes a compressor, an indoor heat exchanger, an outdoor heat exchanger, and a first common rail line, an inlet of each heat exchanger selectively communicating with an outlet of the compressor or in throttling communication with an outlet of the first common rail line, and an outlet of each heat exchanger selectively communicating with an inlet of the compressor or with an inlet of the first common rail line;
in a cooling mode, an outlet of the compressor is communicated with an inlet of the outdoor heat exchanger, an outlet of the outdoor heat exchanger is communicated with an inlet of the first common rail pipeline, an outlet of the first common rail pipeline is communicated with an inlet of the indoor heat exchanger in a throttling mode through the target throttling device, an outlet of the indoor heat exchanger is communicated with an inlet of the compressor, and the target throttling device is a throttling device arranged between the outlet of the first common rail pipeline and the inlet of the indoor heat exchanger in the heat pump system;
the control module is further configured to:
when the target working mode is the refrigeration mode, determining a target overheating temperature corresponding to the current temperature and the current pressure based on the corresponding relation between the temperature and the pressure and the overheating temperature of the indoor heat exchanger;
determining the target flow rate of the refrigerant sent by the target throttling device according to a first preset formula, wherein the first preset formula is as follows:
Figure BDA0003133957790000071
in the first predetermined formula, PWM ij Refers to the target flow rate;
PWM cal the flow rate to be corrected;
d denotes a first predetermined coefficient;
e denotes a second predetermined coefficient;
T B refers to the target superheat temperature;
T Bset the set overheat temperature is indicated;
T D refers to the indoor integrated temperature;
T set refers to the set temperature.
In combination with the second aspect, in some alternative embodiments, the heat pump system includes a compressor, an indoor heat exchanger, an outdoor heat exchanger, and a first common rail line, an inlet of each heat exchanger selectively communicating with an outlet of the compressor or in throttling communication with an outlet of the first common rail line, and an outlet of each heat exchanger selectively communicating with an inlet of the compressor or with an inlet of the first common rail line;
in the heating mode, an outlet of the compressor is communicated with an inlet of the indoor heat exchanger, an outlet of the indoor heat exchanger is communicated with an inlet of the first common rail pipeline, an outlet of the first common rail pipeline is in throttling communication with an inlet of the outdoor heat exchanger through the target throttling device, an outlet of the outdoor heat exchanger is communicated with an inlet of the compressor, and the target throttling device is a throttling device arranged between the outlet of the first common rail pipeline and the inlet of the outdoor heat exchanger in the heat pump system;
the control module is further configured to:
when the target working mode is the heating mode, determining a target supercooling temperature corresponding to the current temperature and the current pressure based on the corresponding relation between the temperature, the pressure and the supercooling temperature of the indoor heat exchanger;
determining the target flow rate of the refrigerant sent by the target throttling device according to a second preset formula, wherein the second preset formula is as follows:
Figure BDA0003133957790000081
wherein, in the second preset formula, PWM ij Refers to the target flow rate;
PWM cal the flow rate to be corrected;
d denotes a first predetermined coefficient;
e denotes a second predetermined coefficient;
T L refers to the target subcooling temperature;
T Lset the set supercooling temperature is indicated;
T D refers to the indoor integrated temperature;
T set refers to the set temperature.
With reference to the second aspect, in some alternative embodiments, the number of the indoor heat exchangers is one, and the number of the outdoor heat exchangers is multiple; the control module is further configured to:
acquiring the temperatures of the plurality of outdoor heat exchangers in the working parameter set;
when the temperatures of the outdoor heat exchangers meet preset defrosting conditions, determining that the target working mode is a heating defrosting mode;
in the heating and defrosting mode, an outlet of the compressor is respectively communicated with an inlet of the indoor heat exchanger and an inlet of a part of outdoor heat exchangers, an outlet of the part of outdoor heat exchangers and an outlet of the indoor heat exchangers are communicated with an inlet of the first common rail pipeline, an outlet of the first common rail pipeline is in throttling communication with an inlet of another part of outdoor heat exchangers through the target throttling device, an outlet of the another part of outdoor heat exchangers is communicated with an inlet of the compressor, and the target throttling device is a throttling device arranged between the outlet of the first common rail pipeline and the another part of outdoor heat exchangers in the heat pump system.
With reference to the second aspect, in some optional embodiments, the control module is further configured to:
determining that the preset defrosting condition is satisfied when the temperature of any one of the plurality of outdoor heat exchangers is less than or equal to a first preset temperature.
With reference to the second aspect, in some alternative embodiments, the heat pump system includes a compressor, an indoor heat exchanger, an outdoor heat exchanger, and a first common rail line, an inlet of each heat exchanger selectively communicates with an outlet of the compressor or with an outlet of the first common rail line in a throttling communication, an outlet of each heat exchanger selectively communicates with an inlet of the compressor or with an inlet of the first common rail line, the number of the indoor heat exchangers is plural, and the number of the outdoor heat exchangers is one;
in a heating and dehumidifying mode, an outlet of the compressor is communicated with an inlet of a part of indoor heat exchangers, outlets of the part of indoor heat exchangers are communicated with an inlet of the first common rail pipeline, an outlet of the first common rail pipeline is in throttling communication with an inlet of another part of indoor heat exchangers through a first target throttling device, outlets of the another part of indoor heat exchangers are communicated with an inlet of the compressor, an outlet of the first common rail pipeline is in throttling communication with an inlet of the outdoor heat exchanger through a second target throttling device, and an outlet of the outdoor heat exchanger is communicated with an inlet of the compressor;
the target flow rates include a first target flow rate corresponding to the first target throttling device and a second target flow rate corresponding to the second target throttling device;
the first target throttling device is a throttling device arranged between an outlet of the first common rail pipeline and an inlet of the other part of indoor heat exchangers in the heat pump system;
the second target throttling device is a throttling device arranged between an outlet of the first common rail pipeline and an inlet of the outdoor heat exchanger in the heat pump system;
the control module is further configured to:
when the target working mode is the heating and dehumidifying mode, determining a target supercooling temperature corresponding to the current temperature and the current pressure at the outlet end of a target indoor heat exchanger based on the corresponding relation between the temperature, the pressure and the supercooling temperature of the indoor heat exchanger, wherein the target indoor heat exchanger is one of the indoor heat exchangers which is communicated with the outlet of the compressor;
determining a target dew point temperature corresponding to the current indoor temperature and the current indoor humidity based on the corresponding relationship among the temperature, the humidity and the dew point temperature;
determining the first target flow rate of the refrigerant sent by the first target throttling device and the second target flow rate of the refrigerant sent by the second target throttling device according to a third preset formula, wherein the third preset formula is as follows:
Figure BDA0003133957790000091
wherein, in the third preset formula, PWM dew Is referred to asA target flow rate;
PWM ij refers to the second target flow rate;
PWM cal the flow rate to be corrected;
d denotes a first predetermined coefficient;
e denotes a second predetermined coefficient;
f denotes a third preset coefficient;
g denotes a fourth predetermined coefficient;
T L refers to the target subcooling temperature;
T Lset the set supercooling temperature is indicated;
T D refers to the indoor integrated temperature;
T set the set temperature is indicated;
T dew refers to the target dew point temperature;
T in refers to the current indoor temperature;
TH in current indoor humidity;
TH max refers to a preset maximum humidity.
With reference to the second aspect, in some alternative embodiments, the heat pump system includes a compressor, an indoor heat exchanger, an outdoor heat exchanger, and a first common rail line, an inlet of each heat exchanger selectively communicating with an outlet of the compressor or in throttling communication with an outlet of the first common rail line, and an outlet of each heat exchanger selectively communicating with an inlet of the compressor or with an inlet of the first common rail line; the number of the indoor heat exchangers is multiple, and the number of the outdoor heat exchangers is multiple;
in a dehumidification and defrosting mode, an outlet of the compressor is respectively communicated with an inlet of a part of indoor heat exchangers and an inlet of a part of outdoor heat exchangers, outlets of the part of indoor heat exchangers and the part of outdoor heat exchangers are communicated with an inlet of the first common rail pipeline, an outlet of the first common rail pipeline is in throttling communication with the other part of indoor heat exchangers through a first target throttling device, an outlet of the first common rail pipeline is also in throttling communication with an inlet of the other part of outdoor heat exchangers through a second target throttling device, and outlets of the other part of indoor heat exchangers and the other part of outdoor heat exchangers are communicated with the inlet of the compressor;
the target flow rates include a first target flow rate corresponding to the first target throttling device and a second target flow rate corresponding to the second target throttling device;
the first target throttling device is a throttling device arranged between an outlet of the first common rail pipeline and an inlet of the other part of indoor heat exchangers in the heat pump system;
the second target throttling device is a throttling device arranged between an outlet of the first common rail pipeline and an inlet of the other part of outdoor heat exchanger in the heat pump system;
the control module is further configured to:
when the target working mode is a dehumidification and defrosting mode, determining a target supercooling temperature corresponding to the current temperature and the current pressure at the outlet end of a target indoor heat exchanger based on the corresponding relation between the temperature, the pressure and the supercooling temperature of the indoor heat exchanger, wherein the target indoor heat exchanger is one of a plurality of indoor heat exchangers which is communicated with the outlet of the compressor;
determining a target dew point temperature corresponding to the current indoor temperature and the current indoor humidity based on the corresponding relationship among the temperature, the humidity and the dew point temperature;
determining the first target flow rate of the refrigerant sent by the first target throttling device and the second target flow rate of the refrigerant sent by the second target throttling device according to a fourth preset formula, wherein the fourth preset formula is as follows:
Figure BDA0003133957790000111
wherein, in the fourth preset formula, PWM dew Refers to the first target flow rate;
PWM ij refers to the second target flow rate;
PWM cal flow to be correctedSpeed;
d denotes a first predetermined coefficient;
e denotes a second predetermined coefficient;
f denotes a third preset coefficient;
g denotes a fourth predetermined coefficient;
T L refers to the target subcooling temperature;
T Lset the set supercooling temperature is indicated;
T D refers to the indoor integrated temperature;
T set the set temperature is indicated;
T dew refers to the target dew point temperature;
T in refers to the current indoor temperature;
TH in current indoor humidity;
TH max refers to a preset maximum humidity.
With reference to the second aspect, in some optional embodiments, when the target operation mode is the operation mode to be switched determined from the received mode switching command, before the control module controls the target throttling device to deliver the refrigerant at the target flow rate, the control module is further configured to:
and controlling the heat pump system to enter a standby state, and then switching to the target working mode from the standby state.
In a third aspect, the present application also provides a computer-readable storage medium having stored thereon a computer program which, when run on a computer, causes the computer to perform the above-mentioned method.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings that are required to be used in the embodiments of the present application will be briefly described below, it should be understood that the following drawings only illustrate some embodiments of the present application and therefore should not be considered as limiting the scope, and that those skilled in the art can also obtain other related drawings based on the drawings without inventive efforts.
Fig. 1 is a schematic flowchart of a heat pump system control method according to an embodiment of the present disclosure.
Fig. 2 is a schematic flow diagram of a refrigerant of a heat pump system in a cooling mode according to an embodiment of the present application.
Fig. 3 is a schematic flow direction diagram of refrigerant in a heating mode of a heat pump system according to an embodiment of the present application.
Fig. 4 is a schematic flow direction diagram of refrigerant of a heat pump system in a dehumidification mode according to an embodiment of the present disclosure.
Fig. 5 is a schematic flow diagram of refrigerant of a heat pump system in a defrosting mode according to an embodiment of the present application.
Fig. 6 is a schematic flow direction diagram of refrigerant of a heat pump system in a dehumidification-defrost mode according to an embodiment of the present application.
Fig. 7 is a second schematic flow direction diagram of the refrigerant of the heat pump system in the cooling mode according to the embodiment of the present application.
Fig. 8 is a second schematic flow direction diagram of the refrigerant of the heat pump system in the heating mode according to the embodiment of the present application.
Fig. 9 is a second schematic flow direction diagram of the refrigerant of the heat pump system in the dehumidification mode according to the embodiment of the present application.
Fig. 10 is a second schematic flow direction diagram of the refrigerant of the heat pump system in the defrosting mode according to the embodiment of the present application.
Icon: 10-a heat pump system; 20-a compressor; 31-a second common rail line; 33-a first common rail line; 34-third common rail line; 46-a one-way valve; 50-indoor heat exchange assembly; 51-a first indoor heat exchanger; 52-a second indoor heat exchanger; 60-an outdoor heat exchange assembly; 61-a first outdoor heat exchanger; 62-a second outdoor heat exchanger; 71-an indoor fan; 72-outdoor fan; 110-a first inlet valve assembly; 111-a first inlet; 112-a second inlet; 113-an outlet; 120-a second inlet valve assembly; 121 — a first inlet; 122-a second inlet; 123-an outlet; 130-a third inlet valve assembly; 131-a first inlet; 132-a second inlet; 133-an outlet; 140-a fourth inlet valve assembly; 141-a first inlet; 142-a second inlet; 143-an outlet; 210 — a first outlet valve assembly; 211-an inlet; 212-first outlet; 213-a second outlet; 220-a second outlet valve assembly; 221-an inlet; 222 — a first outlet; 223-a second outlet; 230-a third outlet valve assembly; 231-an inlet; 232-a first outlet; 233-a second outlet; 240-a fourth outlet valve assembly; 241-an inlet; 242 — a first outlet; 243-second outlet.
Detailed Description
The technical solutions in the embodiments of the present application will be described below with reference to the drawings in the embodiments of the present application. It should be noted that the terms "first," "second," and the like are used solely to distinguish one from another and are not to be construed as indicating or implying any relative importance. The embodiments and features of the embodiments described below can be combined with each other without conflict.
First embodiment
The application provides a temperature regulation device, which comprises a control module and a heat pump system, wherein the control module is used for accurately controlling the heat pump system so as to execute each step in the following heat pump system control method, thereby being beneficial to improving the heat exchange efficiency.
The control module is used for acquiring the working parameter set of the heat pump system and the target of the heat pump system. The temperature adjusting device and the heat pump system can be applied to the fields of vehicles, rooms, ships and the like and are used for adjusting the temperature. The frame structure of the heat pump system can be flexibly determined according to actual conditions, and reference can be made to the frame structure of the heat pump system described in the implementation process of the following method.
Referring to fig. 1 and fig. 2 in combination, the present application further provides a heat pump system control method, which can be applied to the control module, and the control module executes or implements the steps of the method. Wherein, the arrows shown in fig. 2 to 10 are the flow directions of the refrigerants in the corresponding target operation modes, and the refrigerants can be selected according to actual conditions. The method may comprise the steps of:
step S310, acquiring a working parameter set of the heat pump system 10 and a target working mode of the heat pump system 10;
step S320, determining a target flow rate of the refrigerant delivered by the target throttling device corresponding to the target working mode in the heat pump system 10 according to a preset algorithm and the indoor integrated temperature in the working parameter set, the current temperature and the current pressure at the outlet end of the indoor heat exchanger in the heat pump system 10;
and step S330, controlling the target throttling device to convey the refrigerant at the target flow rate.
In the above embodiment, by detecting the indoor integrated temperature, the current temperature at the outlet end of the indoor heat exchanger, and the current pressure, the target flow rate at which the target throttling device delivers the refrigerant can be determined, and then the target throttling device is controlled to deliver the refrigerant at the target flow rate, so that the heat pump system 10 can be accurately controlled in the target working mode, and the heat exchange efficiency and the user experience can be improved.
The individual steps of the method are explained in detail below:
in step S310, the corresponding portion of the heat pump system 10 may be collected by the sensing assembly to obtain the set of operation parameters of the heat pump system 10. The operating parameter set includes, but is not limited to, indoor temperature, indoor humidity, temperature and pressure at the outlet end of the indoor heat exchanger, and the like. In addition, the set of operating parameters may also include data set by a user, for example, the set of operating parameters may also include a set temperature, a preset maximum humidity, a set supercooling temperature, a set superheating temperature, and the like of the room.
Understandably, the sensing components may include, but are not limited to, indoor temperature sensors, outdoor temperature sensors, heat exchanger temperature sensors, temperature and humidity sensors, illumination sensors, pressure sensors, and loop temperature sensors.
The number of each sensor in the sensing assembly can be determined according to actual conditions, and the setting position of the sensor can be flexibly determined. For example, when the heat pump system 10 is applied to a vehicle, an indoor temperature sensor may be disposed in a cab of the vehicle for detecting an environment (e.g., air) temperature inside the vehicle, so as to regulate the temperature inside the vehicle; the outdoor temperature sensor may be disposed outside a cab of the vehicle for detecting an outdoor temperature. Temperature and humidity sensor can set up in the indoor of driver's cabin for detect indoor temperature and humidity, so that regulate and control the temperature and humidity in the driver's cabin. For example, the temperature and humidity sensor can be used for detecting the humidity of the window glass on the indoor side of the vehicle so as to judge whether the glass on the indoor side is fogged or not. The illumination sensor may be disposed within the cab for detecting an illumination intensity within the cab. The heat exchanger temperature sensor and the pressure sensor may be disposed at an outlet end of an indoor heat exchanger of the heat pump system 10, and are configured to detect a temperature at the outlet end and a pressure of the refrigerant.
The target operation mode may be a current operation mode of the heat pump system 10, such as a heating mode or a cooling mode. Alternatively, the target operation mode is an operation mode to be switched by the heat pump system 10 during the mode switching process, for example, when the cooling mode needs to be switched to the heating mode, the target operation mode is the heating mode.
In step S320, the preset algorithm may be flexibly determined according to the target operation mode, and is used for determining the target flow rate of the refrigerant delivered by the corresponding target throttling device according to various parameters in the operation parameter set. The target throttling device is used for throttling and expanding the refrigerant, so that the heat pump system 10 can achieve the purposes of cooling or heating and the like. The target throttling device may be determined according to the frame structure and the target operation mode of the heat pump system 10, and is a throttling device that needs to deliver the refrigerant when the heat pump system 10 is in operation. The throttling device is an electric valve capable of realizing throttling injection and can convey the refrigerant in a pulse injection mode. For example, the throttling device may be a throttling injection valve.
Wherein the throttle injection valve can deliver the refrigerant in a pulsed injection. Understandably, the control module can adjust the cumulative injection duration of the refrigerant injected by the throttling injection valve within a preset duration based on Pulse Width Modulation (PWM) to achieve the adjustment of the refrigerant flow rate/quantity. The flow rate of the refrigerant refers to an average flow rate over a preset time period, and the flow rate of the refrigerant refers to a total flow rate over the preset time period. Therefore, the throttling injection valve is utilized to convey the refrigerant, and the precise adjustment of the flow speed/flow of the refrigerant is facilitated. The cumulative injection time period can be understood as: and within the preset time length, the accumulated total time length of the channel of the throttling injection valve in the opening state. Within the preset duration, the throttling injection valve can be opened and closed for multiple times, and the switching frequency can be flexibly determined according to the actual condition. In addition, the preset time period may be used as a flow rate adjustment period, and may be flexibly determined according to actual conditions, which is not specifically limited herein.
In this embodiment, the flow rate at which the throttle delivers refrigerant is positively correlated to the cumulative injection period over the preset period. The larger the cumulative injection period within the preset period, the higher the flow rate. The control module can adjust the flow speed and flow of the delivered refrigerant by adjusting the accumulated injection time of the refrigerant delivered by the target throttling device, and further can adjust the temperature of modes such as refrigeration or heating.
In step S330, the target throttling device delivers the refrigerant at the target flow rate, the corresponding requirements of the current target operating mode can be met. For example, in a cooling or heating mode, the indoor temperature can be ensured to be in a corresponding set range, and the set range can be flexibly set according to actual conditions.
In the present embodiment, the heat pump system 10 may include a compressor 20, an indoor heat exchange assembly 50, an outdoor heat exchange assembly 60, a first common rail line 33, a second common rail line 31, a third common rail line 34, an inlet valve assembly, and an outlet valve assembly, and may form a circuit through which a refrigerant circulates. The indoor heat exchange assembly 50 may include one or more indoor heat exchangers and the outdoor heat exchange assembly 60 may include one or more outdoor heat exchangers, one inlet valve assembly and one outlet valve assembly for each heat exchanger. The number of the heat exchangers and the inlet valve assemblies and the number of the outlet valve assemblies can be flexibly determined, and are not particularly limited.
Each inlet valve assembly includes a first through-flow device and a throttling device, and each outlet valve assembly includes a first through-flow device and a second through-flow device. The first through-flow device, the second through-flow device and the throttling device can open or close corresponding valve channels under the control of the control module. The first and second flow-through devices may be the same or different. For example, the first through-flow device may be, but is not limited to, a shut-off valve. The second flow means may be, but is not limited to, a one-way valve. The throttling device may be, but is not limited to, a throttling injection valve.
As an alternative embodiment, referring to fig. 2, in the heat pump system 10, the indoor heat exchange assembly 50 is a first indoor heat exchanger 51, and the outdoor heat exchange assembly 60 is a first outdoor heat exchanger 61. The inlet of each heat exchanger is in selective communication with the outlet of the compressor 20 or in throttled communication with the outlet of the first common rail line 33, and the outlet of each heat exchanger is in selective communication with the inlet of the compressor 20 or with the inlet of the first common rail line 33.
Understandably, the outlet of the compressor 20 is communicated with the inlet of the second common rail line 31, the first inlet 111 of the first inlet valve assembly 110 and the first inlet 131 of the third inlet valve assembly 130 are communicated with the second common rail line 31, and the second inlet 112 of the first inlet valve assembly 110 and the second inlet 132 of the third inlet valve assembly 130 are communicated with the first common rail line 33.
The outlet 113 of the first inlet valve assembly 110 communicates with an inlet of the first indoor heat exchanger 51, an outlet of the first indoor heat exchanger 51 communicates with an inlet 211 of the first outlet valve assembly 210, a first outlet 212 of the first outlet valve assembly 210 communicates with the first common rail line 33, and a second outlet 213 of the first outlet valve assembly 210 communicates with the third common rail line 34. The outlet of the third common rail line 34 communicates with the inlet of the compressor 20.
The outlet 133 of the third inlet valve assembly 130 communicates with the inlet of the first outdoor heat exchanger 61, the outlet of the first outdoor heat exchanger 61 communicates with the inlet 231 of the third outlet valve assembly 230, the first outlet 232 of the third outlet valve assembly 230 communicates with the first common rail line 33, and the second outlet 233 of the third outlet valve assembly 230 communicates with the third common rail line 34.
Between the first inlet 111 and the outlet 113 of the first inlet valve assembly 110, the above-mentioned first through-flow device is arranged for controlling the opening or closing of the passage between the first inlet 111 and the outlet 113. Between the second inlet 112 and the outlet 113 of the first inlet valve assembly 110, the above mentioned throttling arrangement is arranged.
Between the inlet 211 and the first outlet 212 of the first outlet valve assembly 210, the second flow passage device is provided for controlling the opening or closing of the passage between the inlet 211 and the first outlet 212. Between the inlet 211 and the second outlet 213 of the first outlet valve assembly 210, the above-mentioned first through-flow means is arranged.
Between the first inlet 131 and the outlet 133 of the third inlet valve assembly 130, the above-mentioned first through-flow device is arranged for controlling the opening or closing of the passage between the first inlet 131 and the outlet 133. Between the second inlet 132 and the outlet 133 of the third inlet valve assembly 130, the above-mentioned throttling device is arranged.
Between the inlet 231 and the first outlet 232 of the third outlet valve assembly 230, the second flow passage device is provided for controlling the opening or closing of the passage between the inlet 231 and the first outlet 232. Between the inlet 231 and the second outlet 233 of the third outlet valve assembly 230, the above-mentioned first through-flow device is arranged.
In the cooling mode, the outlet of the compressor 20 is communicated with the inlet of the outdoor heat exchanger, the outlet of the outdoor heat exchanger is communicated with the inlet of the first common rail pipeline 33, the outlet of the first common rail pipeline 33 is in throttling communication with the inlet of the indoor heat exchanger through the target throttling device, the outlet of the indoor heat exchanger is communicated with the inlet of the compressor 20, and the target throttling device is a throttling device arranged between the outlet of the first common rail pipeline 33 and the inlet of the indoor heat exchanger in the first inlet valve assembly 110 of the heat pump system 10.
Understandably, in the refrigeration mode, the control module can control various valve assemblies to be in a state corresponding to the refrigeration mode.
For example, in the first inlet valve assembly 110, the first through-flow device between the first inlet 111 and the outlet 113 closes the passage, and the throttling device between the second inlet 112 and the outlet 113 is in an open state.
In the first outlet valve assembly 210, the second flow passage between the inlet 211 and the first outlet 212 is in a closed state to close the inlet 211 and the first outlet 212 passages. The first through-flow means between the inlet 211 and the second outlet 213 is in an open state to open a passage between the inlet 211 and the second outlet 213.
In the third inlet valve assembly 130, the first through-flow means between the first inlet 131 and the outlet 133 opens the passage and the throttling means between the second inlet 132 and the outlet 133 is in a closed state.
In the third outlet valve assembly 230, the second flow passage between the inlet 231 and the first outlet 232 is in an open state to open the inlet 231 and the first outlet 232. The first through-flow means between the inlet 231 and the second outlet 233 is in a closed state to close the passage between the inlet 231 and the second outlet 233.
Referring to fig. 2 again, in the refrigeration process of the heat pump system 10, the process of implementing the refrigeration cycle is as follows:
a low-temperature low-pressure refrigerant enters the inlet of the compressor 20, is compressed by the compressor 20, and then becomes a high-temperature high-pressure refrigerant, and the high-temperature high-pressure refrigerant flows into the second common rail line 31 from the outlet of the compressor 20; then, is delivered to the inlet of the first outdoor heat exchanger 61 through the third inlet valve assembly 130, a part of the heat of the refrigerant is released by the first outdoor heat exchanger 61, and is output from the outlet of the first outdoor heat exchanger 61 to the first common rail line 33 via the third outlet valve assembly 230; then, the refrigerant is delivered to the first indoor heat exchanger 51 by means of pulse injection through the throttling device of the first inlet valve assembly 110, and during the process of delivering the refrigerant to the first indoor heat exchanger 51, the refrigerant with high temperature and high pressure is throttled and expanded (for example, the refrigerant in a high-temperature liquid state is atomized and/or vaporized after being throttled and expanded, so that the temperature of the refrigerant is far lower than the ambient temperature), so that the heat of the external environment (such as air) is absorbed by the first indoor heat exchanger 51, and at this time, the air cooled by the absorbed heat is blown into the room by the indoor fan 71, so as to achieve the purpose of indoor refrigeration. In addition, the throttled and expanded refrigerant in the first indoor heat exchanger 51 is output to the third common rail line 34 through the first outlet valve assembly 210, and at this time, the refrigerant in the third common rail line 34 is in a low-temperature and low-pressure state; finally, the refrigerant is delivered to the inlet of the compressor 20 through the third common rail line 34, completing the primary refrigeration cycle. When the subsequent refrigeration is performed, the next refrigeration cycle is performed, which is not described herein again.
During the cooling process, the target flow rate of the refrigerant delivered by the target throttling device needs to be calculated. For example, in the heat pump system 10 shown in fig. 2, step S320 may include:
when the target working mode is the refrigeration mode, determining a target overheat temperature corresponding to the current temperature and the current pressure based on the corresponding relation between the temperature, the pressure and the overheat temperature of the indoor heat exchanger;
determining the target flow rate of the refrigerant sent by the target throttling device according to a first preset formula, wherein the first preset formula is as follows:
Figure BDA0003133957790000171
in the first predetermined formula, PWM ij Refers to the target flow rate;
PWM cal the flow rate to be corrected;
d refers to a first preset coefficient which can be flexibly determined according to actual conditions;
e refers to a second preset coefficient which can be flexibly determined according to actual conditions;
T B target superheat temperature;
T Bset the set overheating temperature can be the overheating temperature of the indoor heat exchanger before the current moment;
T D the indoor comprehensive temperature;
T set the temperature setting is referred to, temperature data can be set or input for a user, and flexible setting can be performed according to actual conditions.
Indoor comprehensive temperature T D Can be obtained by calculating a comprehensive temperature calculation formula, wherein the formula is as follows:
T D ＝a*T in +b*T out +c*P solar (2)
in the formula (2), a refers to a fifth preset coefficient, b refers to a sixth preset coefficient, and c refers to a seventh preset coefficient, which can be flexibly determined according to actual conditions;
T in the current indoor temperature can be acquired by an indoor temperature sensor;
T out the current outdoor temperature can be acquired by an outdoor temperature sensor;
P solar the current illumination intensity can be acquired by an illumination sensor.
After the indoor comprehensive temperature is obtained through calculation, the control module can calculate the flow speed corresponding to the temperature difference through the formula based on the difference between the indoor comprehensive temperature and the set temperature expected by the user, namely the PWM cal ＝d*(T set -T D ). Then, the flow rate is corrected by combining the target overheat temperature and the set overheat temperature of the indoor heat exchanger, so that the target flow rate of the throttling device (i.e., the target throttling device) in the first inlet valve assembly 110 can be obtained, i.e., PWM ij 。
After the target flow rate is obtained, the control module can control the throttling device in the first inlet valve assembly 110 to deliver the refrigerant at the target flow rate to adjust the indoor integrated temperature to ensure that the difference between the adjusted indoor integrated temperature and the set temperature is within a first preset range. The first preset range may be determined according to actual conditions, and for example, the first preset range may be 0-1 ℃.
Control module can save in advance the length of time and the corresponding relation of the velocity of flow of the accumulative injection of throttling arrangement in predetermineeing long time, when adjusting the velocity of flow of carrying the refrigerant, can be based on this corresponding relation, length of time through the accumulative injection of accurate regulation throttling arrangement in predetermineeing long time, realize the accurate adjustment of the velocity of flow, and then realize the accurate adjustment of temperature, so, be favorable to improving heat pump system 10's heat exchange efficiency, realize the accurate control of heat pump, promote user's experience and feel.
When the target overheating temperature of the indoor heat exchanger is obtained, the control module can store a corresponding data table or array in advance. In the data table, the corresponding relations of different temperatures, different pressures and the overheating temperature of the indoor heat exchanger are recorded in advance. When the current temperature at the outlet end of the first indoor heat exchanger 51 and the current pressure of the refrigerant are obtained, the superheat temperature corresponding to the current temperature and the current pressure may be obtained by looking up a table, and the superheat temperature is the current target superheat temperature of the first indoor heat exchanger 51.
Referring to fig. 3, the frame structure of the heat pump system 10 in the heating mode is the same as that shown in fig. 2, except that there is a difference in the flow direction of the refrigerant.
In the heating mode, the outlet of the compressor 20 is communicated with the inlet of the indoor heat exchanger, the outlet of the indoor heat exchanger is communicated with the inlet of the first common rail pipeline 33, the outlet of the first common rail pipeline 33 is in throttling communication with the inlet of the outdoor heat exchanger through the target throttling device, the outlet of the outdoor heat exchanger is communicated with the inlet of the compressor 20, and the target throttling device is a throttling device arranged between the outlet of the first common rail pipeline 33 and the inlet of the outdoor heat exchanger in the heat pump system 10.
Understandably, in the heating mode of the heat pump system 10 shown in fig. 3, the control module can control various valve components to be in the switch states corresponding to the heating mode.
For example, in the first inlet valve assembly 110, the first through-flow device between the first inlet 111 and the outlet 113 opens the passage, and the throttling device between the second inlet 112 and the outlet 113 is in a closed state;
in the first outlet valve assembly 210, the second flow passage between the inlet 211 and the first outlet 212 is in an open state to open the inlet 211 and the first outlet 212 passages. The first through-flow means between the inlet 211 and the second outlet 213 is in a closed state to close the passage between the inlet 211 and the second outlet 213;
in the third inlet valve assembly 130, the first through-flow device between the first inlet 131 and the outlet 133 closes the passage, and the throttling device between the second inlet 132 and the outlet 133 is in an open state;
in the third outlet valve assembly 230, the second flow passage between the inlet 231 and the first outlet 232 is in a closed state to close the inlet 231 and the first outlet 232 passages. The first through-flow means between the inlet 231 and the second outlet 233 is in an open state to open a passage between the inlet 231 and the second outlet 233.
Referring to fig. 3 again, in the heating process of the heat pump system 10, the process of implementing the heating cycle is:
a low-temperature low-pressure refrigerant enters the inlet of the compressor 20, is compressed by the compressor 20, and then becomes a high-temperature high-pressure refrigerant, and the high-temperature high-pressure refrigerant flows into the second common rail line 31 from the outlet of the compressor 20; then, the heat of the refrigerant is released from the first indoor heat exchanger 51 to heat the air of the external environment by being transferred to the inlet of the first indoor heat exchanger 51 through the first inlet valve assembly 110, and then the heated air is blown into the room by the indoor fan 71, thereby achieving the purpose of heating the room. Then, the refrigerant is output from the outlet of the first indoor heat exchanger 51 to the first common rail line 33 via the first outlet valve assembly 210; then, the refrigerant is sent to the first outdoor heat exchanger 61 by a pulse jet method through the throttling device of the third inlet valve assembly 130, and the high-temperature and high-pressure refrigerant is throttled and expanded in the process of being sent to the first outdoor heat exchanger 61, so that the heat of the external environment is absorbed by the outdoor fan 72. The throttled and expanded refrigerant in the first outdoor heat exchanger 61 is output to the third common rail line 34 through the third outlet valve assembly 230, and at this time, the refrigerant in the third common rail line 34 is in a low-temperature and low-pressure state; finally, the refrigerant is delivered to the inlet of the compressor 20 through the third common rail line 34, completing one heating cycle. When heating is performed subsequently, the next heating cycle is performed, which is not described herein again.
During heating, the control module may calculate a target flow rate of the refrigerant delivered by the target throttling device, that is, step S320 may include:
when the target working mode is the heating mode, determining a target supercooling temperature corresponding to the current temperature and the current pressure based on the corresponding relation between the temperature, the pressure and the supercooling temperature of the indoor heat exchanger;
determining the target flow rate of the refrigerant sent by the target throttling device according to a second preset formula, wherein the second preset formula is as follows:
Figure BDA0003133957790000191
wherein, in the second preset formula, PWM ij Refers to the target flow rate;
PWM cal the flow rate to be corrected;
d denotes a first predetermined coefficient;
e denotes a second predetermined coefficient;
T L refers to the target subcooling temperature;
T Lset setting the supercooling temperature;
T D refers to the indoor integrated temperature;
T set refers to the set temperature.
In the second predetermined formula, the indoor integrated temperature can be calculated by the above formula (2). After the indoor comprehensive temperature is obtained through calculation, the control module can calculate the flow speed corresponding to the temperature difference through the formula based on the difference between the indoor comprehensive temperature and the set temperature expected by the user, namely PWM cal ＝d*(T set -T D ). Then, the flow rate is corrected by combining the target supercooling temperature and the set supercooling temperature of the indoor heat exchanger, so that the target flow rate of the throttling device (i.e., the target throttling device) in the third inlet valve assembly 130, that is, the PWM, can be obtained ij 。
After the target flow rate is obtained, the control module may control the throttling device in the third inlet valve assembly 130 to deliver the refrigerant at the target flow rate to adjust the indoor integrated temperature to ensure that the difference between the adjusted indoor integrated temperature and the set temperature is within the first preset range.
When the target supercooling temperature of the indoor heat exchanger is obtained, the obtaining mode is similar to the obtaining of the target supercooling temperature. For example, the control module may pre-store a corresponding data table or array. In the data table, correspondence between different temperatures, different pressures, and supercooling temperatures of the indoor heat exchangers is recorded in advance. When the current temperature at the outlet end of the first indoor heat exchanger 51 and the current pressure of the refrigerant at the outlet end are obtained, the supercooling temperature corresponding to the current temperature and the current pressure may be obtained by looking up a table, and the supercooling temperature is the current target supercooling temperature of the first indoor heat exchanger 51.
In the above embodiment, in the heating mode, the target flow rate of the refrigerant sent by the target throttling device can be accurately calculated through the second preset formula, so that the heat pump system 10 can be accurately controlled in the heating mode, and accurate adjustment of the temperature is facilitated.
It should be noted that when the frame structure of the heat pump system 10 is different from that of fig. 2, the target throttle and the target flow rate in step S320 may be determined based on the frame structure and the operation mode of the actual heat pump system 10 when controlling the heat pump system 10.
Second embodiment
Referring to fig. 4, the heat pump system 10 in the second embodiment has a similar frame structure to the heat pump system 10 in the first embodiment, except that in the second embodiment, the indoor heat exchange assembly 50 further includes a second indoor heat exchanger 52, and the heat pump system 10 further includes a second inlet valve assembly 120 and a second outlet valve assembly 220. The structure of the second inlet valve assembly 120 and the first inlet valve assembly 110 may be the same, and the structure of the second outlet valve assembly 220 and the first outlet valve assembly 210 may be the same.
In the second inlet valve assembly 120, the first inlet port 121 communicates with the second common rail line 31, the second inlet port 122 communicates with the first common rail line 33, and the outlet port 123 communicates with the inlet port of the second indoor heat exchanger 52. A first through-flow device is arranged between the first inlet 121 and the outlet 123, and a throttle device is arranged between the second inlet 122 and the outlet 123.
In the second outlet valve assembly 220, the inlet 221 communicates with the outlet of the second indoor heat exchanger 52, the first outlet 222 communicates with the first common rail line 33, and the second outlet 223 communicates with the third common rail line 34. A second flow-through device (e.g., a one-way valve) is disposed between the inlet 221 and the first outlet 222, and a first flow-through device (e.g., a shut-off valve) is disposed between the inlet 221 and the second outlet 223.
In the heating and dehumidifying mode, an outlet of the compressor 20 is communicated with an inlet of a part of indoor heat exchangers, outlets of the part of indoor heat exchangers are communicated with an inlet of the first common rail pipeline 33, an outlet of the first common rail pipeline 33 is in throttling communication with an inlet of another part of indoor heat exchangers through the first target throttling device, outlets of the another part of indoor heat exchangers are communicated with an inlet of the compressor 20, an outlet of the first common rail pipeline 33 is in throttling communication with an inlet of the outdoor heat exchanger through the second target throttling device, and an outlet of the outdoor heat exchanger is communicated with an inlet of the compressor 20.
The first target throttling device is a throttling device arranged between the outlet of the first common rail pipeline 33 and the inlet of the other part of indoor heat exchangers in the heat pump system 10;
the second target throttling device is a throttling device arranged between the outlet of the first common rail pipeline 33 and the inlet of the outdoor heat exchanger in the heat pump system 10;
the target flow rates include a first target flow rate corresponding to the first target throttling device and a second target flow rate corresponding to the second target throttling device.
Referring to fig. 4 again, in the heating and dehumidifying process of the heat pump system 10, of the two indoor heat exchangers, the heat exchanger near the inlet of the air duct is used for cooling, the heat exchanger near the outlet of the air duct is used for heating, and the air duct is used for supplying air to the indoor space through the indoor fan 71. Understandably, when the first indoor heat exchanger 51 is closer to the air duct inlet than the second indoor heat exchanger 52 and when indoor dehumidification is required at a low ambient temperature (for example, the ambient temperature is 0 to 15 ℃), the first indoor heat exchanger 51 cools to condense water vapor in air in the air duct to remove part of water vapor in the air, then the air cooled and dehumidified by the indoor fan 71 is conveyed to the second indoor heat exchanger 52 side, the air in the air duct is heated by the second indoor heat exchanger 52, and the heated and dehumidified air is blown into the room by the indoor fan 71, so that the indoor heating and dehumidifying purposes are achieved. At this time, the first target throttling means is a throttling means provided between the second inlet 112 and the outlet 113 in the first inlet valve assembly 110, and the second target throttling means is a throttling means provided between the second inlet 132 and the outlet 133 in the third inlet valve assembly 130
The process of realizing heating and dehumidifying circulation comprises the following steps:
a low-temperature low-pressure refrigerant enters the inlet of the compressor 20, is compressed by the compressor 20, and then becomes a high-temperature high-pressure refrigerant, and the high-temperature high-pressure refrigerant flows into the second common rail line 31 from the outlet of the compressor 20; then, the heat of the refrigerant is released by the second indoor heat exchanger 52 to heat the air of the external environment through being transferred to the inlet of the second indoor heat exchanger 52 through the second inlet valve assembly 120, and then the heated air is blown into the room by the indoor fan 71, thereby achieving the purpose of heating the room. Then, the refrigerant is output from the outlet of the second indoor heat exchanger 52 to the first common rail line 33 via the second outlet valve assembly 220. Then, the refrigerant is delivered to the first outdoor heat exchanger 61 by means of a pulse injection through the throttling device of the third inlet valve assembly 130, and the high-temperature and high-pressure refrigerant is throttled and expanded in the process of delivering the refrigerant to the first outdoor heat exchanger 61, thereby absorbing heat of the external environment; in addition, the refrigerant in the first common rail line 33 is also injected to the first indoor heat exchanger 51 through the throttling device in the first inlet valve assembly 110, and the refrigerant is throttled and expanded in the first indoor heat exchanger 51 so as to absorb the temperature of the outside air, so that the water vapor in the air is condensed, and the dehumidification purpose is achieved. The throttled and expanded refrigerant in the first indoor heat exchanger 51 and the first outdoor heat exchanger 61 is output to the third common rail pipeline 34 through the first outlet valve assembly 210 and the third outlet valve assembly 230, respectively, and at this time, the refrigerant in the third common rail pipeline 34 is in a low-temperature and low-pressure state; finally, the refrigerant is delivered to the inlet of the compressor 20 through the third common rail line 34, completing one heating and dehumidifying cycle.
In the heating and dehumidifying process, the control module can calculate the flow rate of the first target throttling device and the second target throttling device for conveying the refrigerant, so that the purpose of accurately controlling heating and dehumidifying is achieved. As an alternative implementation, step S320 may include:
when the target working mode is the heating and dehumidifying mode, determining a target supercooling temperature corresponding to the current temperature and the current pressure at the outlet end of a target indoor heat exchanger based on the corresponding relationship between the temperature, the pressure and the supercooling temperature of the indoor heat exchanger, wherein the target indoor heat exchanger is one of the plurality of indoor heat exchangers which is communicated with the outlet of the compressor 20;
determining a target dew point temperature corresponding to the current indoor temperature and the current indoor humidity based on the corresponding relationship among the temperature, the humidity and the dew point temperature;
determining the first target flow rate of the refrigerant sent by the first target throttling device and the second target flow rate of the refrigerant sent by the second target throttling device according to a third preset formula, wherein the third preset formula is as follows:
Figure BDA0003133957790000221
wherein, in the third preset formula, PWM dew Refers to the first target flow rate;
PWM ij refers to the second target flow rate;
PWM cal the flow rate to be corrected;
d denotes a first predetermined coefficient;
e denotes a second predetermined coefficient;
f denotes a third preset coefficient;
g denotes a fourth predetermined coefficient;
T L refers to the target subcooling temperature;
T Lset setting the supercooling temperature;
T D refers to the indoor integrated temperature;
T set finger set temperature；
T dew Refers to the target dew point temperature;
T in refers to the current indoor temperature;
TH in current indoor humidity;
TH max refers to a preset maximum humidity.
In the third preset formula, the first preset coefficient, the second preset coefficient, the third preset coefficient, and the fourth preset coefficient may all be determined according to actual conditions (for example, obtained through multiple test measurements). The current indoor humidity can be acquired by a humidity sensor (or a temperature and humidity sensor). In the dehumidification calculation process, based on the difference between the target dew point temperature and the indoor temperature, and the difference between the indoor humidity and the preset maximum humidity, the target flow rate PWM of the throttling device (i.e. the first target throttling device) in the first inlet valve assembly 110 for delivering the refrigerant can be calculated by the above formula (4) dew (i.e., the first target flow rate). The preset maximum humidity can be understood as the maximum value of the suitable humidity, and can be flexibly set according to actual conditions.
It should be noted that, the control module can adjust the first target flow rate of the first target throttling device based on the humidity data collected by the indoor humidity sensor and the expected humidity data set by the user, so that the difference between the adjusted indoor humidity and the set expected humidity is within a second preset range, the second preset range can be flexibly set according to actual conditions, and no specific limitation is made here, so that the indoor humidity can be accurately controlled, the user requirements can be met, and the user experience can be improved.
The dew point temperature refers to the temperature at which the air is cooled to saturation, that is, the temperature at which the water vapor and the water reach an equilibrium state, under the condition that the water vapor content in the air is unchanged and the air pressure is kept constant. Differences in dew point temperature at different temperatures, humidity, are well known to those skilled in the art.
In acquiring the target dew point temperature in the room, the acquisition manner is similar to the above-described acquisition of the target supercooling temperature. For example, the control module may pre-store a table or array of corresponding dew point temperature data. In the dew point temperature data table, correspondence between different temperatures, different humidities, and dew point temperatures is recorded in advance. When the current indoor temperature and the current indoor humidity are obtained, the dew point temperature corresponding to the current indoor temperature and the current indoor humidity can be obtained through table lookup, and the dew point temperature is the current target dew point temperature.
In addition, the indoor integrated temperature can be calculated by the above formula (2). After the indoor comprehensive temperature is obtained through calculation, the control module can calculate the flow speed corresponding to the temperature difference through the formula based on the difference between the indoor comprehensive temperature and the set temperature expected by the user, namely the PWM cal ＝d*(T set -T D ). Then, the flow rate is corrected by combining the target supercooling temperature and the set supercooling temperature of the indoor heat exchanger, so that the target flow rate (i.e., the second target flow rate) of the throttling device (i.e., the second target throttling device) in the third inlet valve assembly 130 can be obtained, i.e., the PWM target flow rate ij 。
After the target flow rate is obtained, the control module may control the throttling device in the third inlet valve assembly 130 to deliver the refrigerant at the target flow rate to adjust the indoor integrated temperature to ensure that the difference between the adjusted indoor integrated temperature and the set temperature is within the first preset range.
When the target supercooling temperature of the indoor heat exchanger is obtained, the obtaining mode is similar to the obtaining of the target supercooling temperature. For example, the control module may pre-store a corresponding data table or array. In the data table, correspondence between different temperatures, different pressures, and supercooling temperatures of the indoor heat exchangers is recorded in advance. When the current temperature at the outlet end of the first indoor heat exchanger 51 and the current pressure of the refrigerant at the outlet end are obtained, the supercooling temperature corresponding to the current temperature and the current pressure can be obtained by looking up a table, and the supercooling temperature is the current target supercooling temperature of the first indoor heat exchanger 51.
In the above embodiment, in the heating and dehumidifying mode, the corresponding target flow rates of the refrigerants respectively sent by the first target throttling device and the second target throttling device can be accurately calculated through the third preset formula, and then the first target throttling device and the second target throttling device are controlled to convey the refrigerants at the corresponding target flow rates, so that the heat pump system 10 can be accurately controlled in the heating and dehumidifying mode, and accurate adjustment of temperature and humidity is facilitated.
In other embodiments, the heat pump system 10 may only operate in the natural dehumidification mode, i.e., indoor and outdoor temperatures are maintained to be the same, and the dehumidification mode is referred to as the heating dehumidification mode, and will not be described herein.
Within the framework of the heat pump system 10 shown in fig. 4, the control module may also control the heat pump system 10 to enter a heating mode or a cooling mode.
For example, in the heating mode, the flow rates of the target throttle and the switches of the first inlet valve assembly 110, the second inlet valve assembly 120, the third inlet valve assembly 130, the first outlet valve assembly 210, the second outlet valve assembly 220, and the third outlet valve assembly 230 are controlled by the control module, so that the inlet of one or both of the first indoor heat exchanger 51 and the second indoor heat exchanger 52 can be communicated with the second common rail pipeline 31, and the outlet of the indoor heat exchanger communicated with the second common rail pipeline 31 is communicated with the first common rail pipeline 33; the inlet of the first outdoor heat exchanger 61 is communicated with the outlet of the first common rail 33, and the outlet of the first outdoor heat exchanger 61 is communicated with the third common rail 34, so that the indoor heat exchanger communicated with the second common rail 31 can be used for heating the indoor by circulating high-temperature and high-pressure refrigerant, thereby achieving the purpose of heating.
For another example, in the cooling mode, by controlling the opening and closing and the flow rate of each type of valve assembly, the inlet of the first outdoor heat exchanger 61 can be communicated with the outlet of the second common rail line 31, and the outlet of the first outdoor heat exchanger 61 can be communicated with the inlet of the first common rail line 33; the inlet of one or both of the first indoor heat exchanger 51 and the second indoor heat exchanger 52 is communicated with the outlet of the first common rail pipeline 33, and the outlet of the indoor heat exchanger communicated with the first common rail pipeline 33 is communicated with the third common rail pipeline 34, so that the indoor heat exchanger communicated with the first common rail pipeline 33 can be used for circulating low-temperature and low-pressure refrigerant to refrigerate the indoor space, and the aim of refrigerating is fulfilled.
It should be noted that, in the second embodiment, the target flow rate of the target throttling device is determined in the heating mode, and reference may be made to the manner of determining the target flow rate in the heating mode described in the first embodiment. The target flow rate of the target throttle valve in the cooling mode may be determined in the manner described in the first embodiment in the cooling mode. Here, the manner of controlling the target throttle device may be the same as or similar to that of the first embodiment, except that in the second embodiment, either one or both of the first indoor heat exchanger 51 and the second indoor heat exchanger 52 may be selected to flow refrigerant therethrough.
In addition, in the heat pump system 10 shown in fig. 4, the indoor heat exchange assembly 50 may further include a greater number of indoor heat exchangers, for example, a third indoor heat exchanger, and at this time, the heat pump system 10 may further include an inlet valve assembly and an outlet valve assembly corresponding to the third indoor heat exchanger, and a connection relationship between the inlet valve assembly and the outlet valve assembly and the third indoor heat exchanger and a common rail pipeline is the same as a connection relationship between a group of the first inlet valve assembly 110, the first indoor heat exchanger 51, and the first outlet valve assembly 210 and the common rail pipeline, and is not described herein again. In the heating or refrigerating mode, the two or more indoor heat exchangers can increase the heat exchange area, and are beneficial to improving the heat exchange efficiency of indoor heating or refrigerating.
Third embodiment
In the heat pump system 10 of the third embodiment, the number of indoor heat exchangers is one, and the number of outdoor heat exchangers is plural. That is, the outdoor heat exchange assembly 60 may include two or more heat exchangers, one inlet valve assembly and one outlet valve assembly for each heat exchanger. The number of the heat exchangers can be flexibly set, and is not particularly limited.
For example, referring to fig. 5, the outdoor heat exchange assembly 60 includes a first outdoor heat exchanger 61 and a second outdoor heat exchanger 62. The heat pump system 10 of fig. 5 is similar in frame construction to the heat pump system 10 of fig. 3, except that the outdoor heat exchange assembly 60 further includes a second outdoor heat exchanger 62, and the heat pump system 10 further includes a fourth inlet valve assembly 140 and a fourth outlet valve assembly 240. The structure of the fourth inlet valve assembly 140 and the first inlet valve assembly 110 may be the same, and the structure of the fourth outlet valve assembly 240 and the first outlet valve assembly 210 may be the same.
In the fourth inlet valve assembly 140, the first inlet port 141 communicates with the second common rail line 31, the second inlet port 142 communicates with the first common rail line 33, and the outlet port 143 communicates with the inlet port of the second outdoor heat exchanger 62. A first through-flow device is arranged between the first inlet 141 and the outlet 143, and a throttling device is arranged between the second inlet 142 and the outlet 143.
In the fourth outlet valve assembly 240, the inlet 241 communicates with the outlet of the second outdoor heat exchanger 62, the first outlet 242 communicates with the first common rail line 33, and the second outlet 243 communicates with the third common rail line 34. A second flow-through device (e.g., a one-way valve) is disposed between the inlet 241 and the first outlet 242, and a first flow-through device (e.g., a shut-off valve) is disposed between the inlet 241 and the second outlet 243.
When the outdoor heat exchange assembly 60 includes two or more heat exchangers, the heat pump system 10 may perform defrosting without stopping if there is frost in the outdoor heat exchanger in the indoor heating mode.
As an alternative embodiment, the control module may determine whether a defrost mode needs to be entered. For example, obtaining the target operating mode of the heat pump system 10 may include:
acquiring the temperatures of the plurality of outdoor heat exchangers in the working parameter set;
when the temperatures of the outdoor heat exchangers meet preset defrosting conditions, determining that the target working mode is a heating defrosting mode;
in the heating and defrosting mode, the outlet of the compressor 20 is respectively communicated with the inlet of the indoor heat exchanger and the inlet of a part of outdoor heat exchangers, the outlet of the part of outdoor heat exchangers and the outlet of the indoor heat exchangers are communicated with the inlet of the first common rail pipeline 33, the outlet of the first common rail pipeline 33 is in throttling communication with the inlet of another part of outdoor heat exchangers through the target throttling device, the outlet of the another part of outdoor heat exchangers is communicated with the inlet of the compressor 20, and the target throttling device is a throttling device arranged between the outlet of the first common rail pipeline 33 and the another part of outdoor heat exchangers in the heat pump system 10.
The preset defrosting condition can be flexibly determined according to the actual condition. Understandably, each outdoor heat exchanger may be provided with a respective sensor for detecting the temperature of the outdoor heat exchanger and/or the pressure of the refrigerant of the outdoor heat exchanger. The temperature and/or pressure collected by the sensor may be communicated to the control module. The control module can judge whether the plurality of outdoor heat exchangers meet the preset defrosting condition according to the temperature or the pressure intensity or simultaneously based on the temperature and the pressure intensity. As an optional implementation manner, the manner of determining whether the preset defrosting condition is met may be: and when the temperature of any outdoor heat exchanger in the plurality of outdoor heat exchangers is less than or equal to a first preset temperature, determining that the preset defrosting condition is met. The first preset temperature can be flexibly determined according to actual conditions, and can be a frosting critical temperature or a temperature slightly higher than the frosting critical temperature (for example, the first preset temperature is higher than the frosting critical temperature by 1 ℃). When the pressure is used for judging whether the outdoor heat exchanger meets the preset defrosting condition, the judging mode is similar to that of judging whether the outdoor heat exchanger meets the preset defrosting condition by using the temperature, and the description is omitted here.
Understandably, when the temperature of one or more of the plurality of outdoor heat exchangers is less than or equal to the frost formation critical temperature, it means that the outdoor heat exchanger is frosted or about to be frosted, and the frosted outdoor heat exchanger may cause the heat pump system 10 to fail to operate normally, so that the defrosting operation is required. If the first preset temperature is slightly higher than the frosting critical temperature, when the temperature of one or more heat exchangers in the plurality of outdoor heat exchangers is lower than the first preset temperature, the outdoor heat exchanger is indicated to be frosted, and at the moment, the outdoor heat exchanger can be heated to avoid frosting of the outdoor heat exchanger. The control module can defrost the frosted outdoor heat exchanger or make the frosted outdoor heat exchanger not frosted based on the first preset temperature.
When the outdoor heat exchanger needs defrosting, the indoor heat exchanger is used for heating, and therefore, the heat pump system 10 needs to work in a heating defrosting mode.
Referring to fig. 5 again, it is assumed that, when it is determined that the first outdoor heat exchanger 61 satisfies the defrosting condition and frosting is present when it is determined whether the defrosting condition is satisfied, the defrosting operation is performed on the first outdoor heat exchanger 61. In the heating defrosting mode, the process of defrosting can be as follows:
a low-temperature low-pressure refrigerant enters the inlet of the compressor 20, is compressed by the compressor 20, and then becomes a high-temperature high-pressure refrigerant, and the high-temperature high-pressure refrigerant flows into the second common rail line 31 from the outlet of the compressor 20; then, the heat of the refrigerant is released from the first indoor heat exchanger 51 to heat the air of the external environment by being transferred to the inlet of the first indoor heat exchanger 51 through the first inlet valve assembly 110, and then the heated air is blown into the room by the indoor fan 71, thereby achieving the purpose of heating the room. In addition, the high-temperature and high-pressure refrigerant in the second common rail line 31 is also sent to the inlet of the first outdoor heat exchanger 61 through the third inlet valve assembly 130, and the heat of the refrigerant is released by the first outdoor heat exchanger 61 to raise the temperature of the first outdoor heat exchanger 61, thereby removing the frost formed on the first outdoor heat exchanger 61.
Then, the refrigerant is output from the outlet of the first indoor heat exchanger 51 to the first common rail line 33 via the first outlet valve assembly 210, and is output from the outlet of the first outdoor heat exchanger 61 to the first common rail line 33 via the third outlet valve assembly 230; then, the refrigerant in the first common rail line 33 is sent to the second outdoor heat exchanger 62 by pulse injection through the throttling device of the fourth inlet valve assembly 140, and the refrigerant of high temperature and high pressure is throttled and expanded in the process of being sent to the second outdoor heat exchanger 62, thereby absorbing heat of the external environment in cooperation with the outdoor fan 72. The throttled and expanded refrigerant in the second outdoor heat exchanger 62 is output to the third common rail line 34 through the fourth outlet valve assembly 240, and at this time, the refrigerant in the third common rail line 34 is in a low-temperature and low-pressure state; finally, the refrigerant is delivered to the inlet of the compressor 20 through the third common rail line 34, and a heating and defrosting cycle is completed, and in the defrosting process, the heat pump system 10 can circulate the refrigerant through the second outdoor heat exchanger 62, so that defrosting without stopping the machine can be realized.
Wherein, the control module can judge whether the first outdoor heat exchanger 61 completes the defrosting operation according to the temperature data collected by the temperature sensor on the outdoor heat exchanger. For example, when the temperature of the outdoor heat exchanger is greater than the second preset temperature, it is determined that the outdoor heat exchanger completes the defrosting operation. The second preset temperature is higher than the first preset temperature, namely higher than the frosting critical temperature, and can be flexibly set. When the defrosting operation is completed, the defrosting of the first outdoor heat exchanger 61 is stopped, and it is determined whether or not the other outdoor heat exchangers (e.g., the second outdoor heat exchanger 62) satisfy the defrosting condition. When other outdoor heat exchangers still need defrosting operation, the outdoor heat exchanger meeting defrosting conditions is defrosted. When all outdoor heat exchangers do not meet the defrosting condition, the heat exchangers can directly enter a heating mode without defrosting.
During the heating process, the control module may calculate the target flow rate of the refrigerant delivered by the target throttling device, and the calculation manner is the same as that in the heating mode in the first embodiment, and is not described herein again.
In the structural framework of the heat pump system 10 shown in fig. 5, in addition to the heat pump system 10 being able to perform the above-mentioned non-stop defrosting, the control module may also control the heat pump system 10 to enter a heating mode or a cooling mode.
For example, in the heating mode, the flow rates of the target throttle and the switches of the first inlet valve assembly 110, the third inlet valve assembly 130, the fourth inlet valve assembly 140, the first outlet valve assembly 210, the third outlet valve assembly 230, and the fourth outlet valve assembly 240 are controlled by the control module, such that the inlet of the first indoor heat exchanger 51 is communicated with the outlet of the second common rail line 31, the outlet of the first indoor heat exchanger 51 is communicated with the first common rail line 33, the inlets of one or both of the first outdoor heat exchanger 61 and the second outdoor heat exchanger 62 are communicated with the first common rail line 33, and the outlet of the outdoor heat exchanger communicated with the first common rail line 33 is communicated with the third common rail line 34; in this way, the first indoor heat exchanger 51 communicating with the second common rail line 31 can be used to circulate high-temperature and high-pressure refrigerant, thereby heating the indoor space.
For another example, in the cooling mode, by controlling the on/off and flow rate of each type of valve assembly, the inlets of one or both of the first outdoor heat exchanger 61 and the second outdoor heat exchanger 62 can be communicated with the second common rail line 31, and the outlet of the outdoor heat exchanger communicated with the second common rail line 31 is communicated with the first common rail line 33; the inlet of the first indoor heat exchanger 51 is communicated with the outlet of the first common rail line 33, and the outlet of the first indoor heat exchanger 51 is communicated with the third common rail line 34, so that the first indoor heat exchanger 51 communicated with the first common rail line 33 can be used for circulating low-temperature and low-pressure refrigerant to refrigerate the indoor space, and the aim of refrigerating is fulfilled.
It should be noted that, in the third embodiment, the target flow rate of the target throttling device is determined in the heating mode, and reference may be made to the manner of determining the target flow rate in the heating mode described in the first embodiment. The target flow rate of the target throttle valve in the cooling mode may be determined in the manner described in the first embodiment in the cooling mode. Here, the manner of controlling the target throttle device may be the same as or similar to that of the first embodiment, except that in the third embodiment, either one or both of the first outdoor heat exchanger 61 and the second outdoor heat exchanger 62 may be selected to pass refrigerant.
In addition, in the heat pump system 10 shown in fig. 5, the outdoor heat exchange assembly 60 may further include a greater number of outdoor heat exchangers, for example, a third outdoor heat exchanger may also be included, at this time, the heat pump system 10 may further include an inlet valve assembly and an outlet valve assembly corresponding to the third outdoor heat exchanger, and a connection relationship between the inlet valve assembly and the outlet valve assembly and the third outdoor heat exchanger and a common rail pipeline is the same as a connection relationship between a set of the third inlet valve assembly 130, the first outdoor heat exchanger 61, and the third outlet valve assembly 230 and the common rail pipeline, which is not described herein again. In the heating or refrigerating mode, two or more outdoor heat exchangers can increase the heat exchange area, and the indoor heating or refrigerating effect can be improved.
Fourth embodiment
In the fourth embodiment, the indoor heat exchange assembly 50 may include a plurality of indoor heat exchangers, and the outdoor heat exchange assembly 60 may include a plurality of outdoor heat exchangers. Each heat exchanger corresponds to one inlet valve assembly and one outlet valve assembly.
Referring to fig. 6, the frame structure of the heat pump system 10 in the fourth embodiment is similar to that of the first embodiment, and compared with the heat pump system 10 shown in fig. 2 in the first embodiment, the difference is that in the fourth embodiment, the indoor heat exchange assembly 50 further includes a second indoor heat exchanger 52, and the outdoor heat exchange assembly 60 further includes a second outdoor heat exchange assembly 60. The heat pump system 10 further includes a second inlet valve assembly 120, a second outlet valve assembly 220, a fourth inlet valve assembly 140, and a fourth outlet valve assembly 240.
The connection relationship between the second inlet valve assembly 120 and the second outlet valve assembly 220 in the heat pump system 10 is shown in the second embodiment, and the connection relationship between the fourth inlet valve assembly 140 and the fourth outlet valve assembly 240 in the heat pump system 10 is shown in the third embodiment.
When there are a plurality of indoor heat exchangers and a plurality of outdoor heat exchangers in the heat pump system 10, the operation mode of the heat pump system 10 may include a heating mode, a cooling mode, a heating and dehumidifying mode, and a heating and defrosting mode, and may further include a defrosting and dehumidifying mode.
In the dehumidification and defrost mode, the outlet of the compressor 20 is respectively communicated with the inlet of a part of indoor heat exchangers and the inlet of a part of outdoor heat exchangers, the outlets of the part of indoor heat exchangers and the part of outdoor heat exchangers are communicated with the inlet of the first common rail pipeline 33, the outlet of the first common rail pipeline 33 is in throttling communication with the other part of indoor heat exchangers through the first target throttling device, the outlet of the first common rail pipeline 33 is also in throttling communication with the inlet of the other part of outdoor heat exchangers through the second target throttling device, and the outlets of the other part of indoor heat exchangers and the other part of outdoor heat exchangers are communicated with the inlet of the compressor 20.
The first target throttling device is a throttling device arranged between the outlet of the first common rail pipeline 33 and the inlet of the other part of indoor heat exchangers in the heat pump system 10;
the second target throttling device is a throttling device arranged between the outlet of the first common rail pipeline 33 and the inlet of the other part of outdoor heat exchangers in the heat pump system 10;
the target flow rates include a first target flow rate corresponding to the first target throttling device and a second target flow rate corresponding to the second target throttling device.
Referring to fig. 6, in the dehumidification-defrost mode, the implementation process of the heat pump system 10 is the combination of the heating-dehumidification mode described in the second embodiment and the heating-defrost mode in the third embodiment. It is assumed that the first indoor heat exchanger 51 is closer to the air duct inlet than the second indoor heat exchanger 52, and it is determined that the first outdoor heat exchanger 61 satisfies the frosting condition and frosting exists, at this time, the first target throttling device is a throttling device provided between the second inlet 112 and the outlet 113 in the first inlet valve assembly 110, and the second target throttling device is a throttling device provided between the second inlet 142 and the outlet 143 in the fourth inlet valve assembly 140. The implementation process of the dehumidification and defrosting mode can be as follows:
a low-temperature low-pressure refrigerant enters the inlet of the compressor 20, is compressed by the compressor 20, and then becomes a high-temperature high-pressure refrigerant, and the high-temperature high-pressure refrigerant flows into the second common rail line 31 from the outlet of the compressor 20; and then to the inlet of the second indoor heat exchanger 52 through the second inlet valve assembly 120, and to the inlet of the first outdoor heat exchanger 61 through the third inlet valve assembly 130. The heat of the refrigerant is released by the second indoor heat exchanger 52 to heat the air in the external environment, and then the heated air is blown into the room by the indoor fan 71, thereby achieving the purpose of heating the room. The high-temperature and high-pressure refrigerant in the first outdoor heat exchanger 61 releases heat, so that frost is removed from the first outdoor heat exchanger 61, and defrosting is achieved without stopping.
Then, the refrigerant is output from the outlet of the second indoor heat exchanger 52 and the outlet of the first outdoor heat exchanger 61 to the first common rail line 33 via the second outlet valve assembly 220 and the third outlet valve assembly 230, respectively. Then, the refrigerant in the first common rail line 33 is sent to the second outdoor heat exchanger 62 by means of pulse injection through the throttling device of the fourth inlet valve assembly 140, and the refrigerant with high temperature and high pressure is throttled and expanded in the process of sending the refrigerant to the second outdoor heat exchanger 62, so as to absorb the heat of the external environment; in addition, the refrigerant in the first common rail line 33 is also injected to the first indoor heat exchanger 51 through the throttling device in the first inlet valve assembly 110, and the refrigerant is throttled and expanded in the first indoor heat exchanger 51, so as to absorb the temperature of the outside air, so that the water vapor in the air is condensed, and the dehumidification purpose is achieved. The throttled and expanded refrigerant in the first indoor heat exchanger 51 and the second outdoor heat exchanger 62 is output to the third common rail line 34 through the first outlet valve assembly 210 and the fourth outlet valve assembly 240, respectively, and at this time, the refrigerant in the third common rail line 34 is in a low-temperature and low-pressure state; finally, the refrigerant is delivered to the inlet of the compressor 20 through the third common rail line 34, completing one dehumidification and defrost cycle.
In the dehumidification and defrosting process, the control module can calculate the flow rate of the refrigerant conveyed by the first target throttling device and the second target throttling device so as to achieve the purpose of accurately controlling the dehumidification and defrosting. As an alternative implementation, step S320 may include:
when the target working mode is the dehumidification-defrosting mode, determining a target supercooling temperature corresponding to the current temperature and the current pressure at the outlet end of a target indoor heat exchanger based on the corresponding relationship between the temperature, the pressure and the supercooling temperature of the indoor heat exchanger, wherein the target indoor heat exchanger is one of the plurality of indoor heat exchangers which is communicated with the outlet of the compressor 20;
determining a target dew point temperature corresponding to the current indoor temperature and the current indoor humidity based on the corresponding relationship among the temperature, the humidity and the dew point temperature;
determining the first target flow rate of the refrigerant sent by the first target throttling device and the second target flow rate of the refrigerant sent by the second target throttling device according to a fourth preset formula, wherein the fourth preset formula is as follows:
Figure BDA0003133957790000291
wherein, in the fourth preset formula, PWM dew Refers to the first target flow rate;
PWM ij refers to the second target flow rate;
PWM cal the flow rate to be corrected;
d denotes a first predetermined coefficient;
e denotes a second predetermined coefficient;
f denotes a third predetermined coefficient;
g denotes a fourth predetermined coefficient;
T L refers to the target subcooling temperature;
T Lset the set supercooling temperature is indicated;
T D refers to the indoor integrated temperature;
T set the set temperature is indicated;
T dew refers to the target dew point temperature;
T in refers to the current indoor temperature;
TH in current indoor humidity;
TH max refers to a preset maximum humidity.
The calculation method of formula (5) is the same as that of formula (4), and is not described herein again.
In the dehumidification and defrosting mode, the corresponding target flow rates of the refrigerants respectively sent by the first target throttling device and the second target throttling device can be accurately calculated through a fourth preset formula, and then the first target throttling device and the second target throttling device are controlled to convey the refrigerants at the corresponding target flow rates, so that the heat pump system 10 can be accurately controlled in the dehumidification and defrosting mode, and accurate control of humidity and defrosting is facilitated.
In the structural framework of the heat pump system 10 shown in fig. 6, in addition to the non-stop defrosting of the heat pump system 10, the control module can control the heat pump system 10 to enter a cooling mode as shown in fig. 7, a heating mode as shown in fig. 8, a dehumidifying mode as shown in fig. 9, or a defrosting mode as shown in fig. 10. Wherein, under the condition that has a plurality of indoor heat exchangers, a plurality of outdoor heat exchanger, control module can be according to the demand, and corresponding heat exchanger operation (namely the inlet valve subassembly of heat exchanger, outlet valve subassembly selectivity and corresponding rail way intercommunication to the circulation refrigerant) is selected in a flexible way, and some heat exchangers do not operate (namely the inlet valve subassembly of heat exchanger, outlet valve subassembly all close, do not circulate the refrigerant), so, can realize the nimble control of heat pump.
For example, in a scene where a plurality of rooms exist, the heat pump system 10 having a plurality of indoor heat exchangers and a plurality of outdoor heat exchangers is deployed, wherein each room may have one indoor heat exchanger installed therein, and a user may flexibly select a corresponding indoor heat exchanger to operate according to requirements for cooling or heating, and other indoor heat exchangers stop operating, so that start and stop control of the indoor heat exchangers can be flexibly implemented under the condition of sharing the outdoor heat exchange assembly 60.
In the foregoing embodiments, when the target operation mode is the operation mode to be switched determined from the received mode switching command, before controlling the target throttling device to deliver the refrigerant at the target flow rate, the method further includes:
and controlling the heat pump system 10 to enter a standby state, and then switching to the target working mode from the standby state. In the standby mode, in the heat pump system 10, the channels of the inlet valve assembly and the outlet valve assembly connected to all the indoor heat exchangers are closed, and the channels of the inlet valve assembly and the outlet valve assembly connected to all the outdoor heat exchangers are closed (i.e., the inlet valve assembly and the outlet valve assembly are closed). The duration of the standby mode can be flexibly set according to actual conditions, and is not particularly limited herein.
For example, when the control module obtains a mode switching instruction for switching from the heating mode to the cooling mode, the control module may first control the heat pump system 10 to enter the standby mode from the heating mode, and then switch from the standby mode to the cooling mode. And then, the target working mode is taken as a refrigerating mode, and corresponding channels of corresponding inlet valve assemblies and outlet valve assemblies are opened, so that the switching from the heating mode to the refrigerating mode is realized.
Referring again to fig. 7, within the framework of the heat pump system 10 shown in fig. 7, during the switching of the heat pump system 10 from the heating mode to the cooling mode, the channel switching states of the respective inlet and outlet valve assemblies may be as follows:
first, the control module may first control the heat pump system 10 to enter a standby mode from a heating mode, in which the first inlet valve assembly 110, the second inlet valve assembly 120, the third inlet valve assembly 130, and the fourth inlet valve assembly 140 are all closed, and the first outlet valve assembly 210, the second outlet valve assembly 220, the third outlet valve assembly 230, and the fourth outlet valve assembly 240 are all closed. Then, the standby mode is switched to the cooling mode. In the cooling mode, the opening and closing conditions of the inlet valve assembly and the outlet valve assembly are as follows:
in the first inlet valve assembly 110, the first through-flow device between the first inlet 111 and the outlet 113 closes the passage, and the throttling device (such as an injection valve) between the second inlet 112 and the outlet 113 is in an open state, and injects refrigerant to the first indoor heat exchanger 51 to perform indoor cooling.
In the first outlet valve assembly 210, the second flow passage between the inlet 211 and the first outlet 212 is in a closed state to close the inlet 211 and the first outlet 212 passages. The first through-flow means between the inlet 211 and the second outlet 213 is in an open state to open a passage between the inlet 211 and the second outlet 213.
In the second inlet valve assembly 120, the first through-flow device between the first inlet 121 and the outlet 123 closes the passage, and the throttling device between the second inlet 122 and the outlet 123 is in an open state, injecting the refrigerant to the second indoor heat exchanger 52 to perform indoor cooling.
In the second outlet valve assembly 220, the second flow passage between the inlet 221 and the first outlet 222 is in a closed state to close the inlet 221 and the first outlet 222 passages. The first through-flow means between the inlet 221 and the second outlet 223 is in an open state to open a passage between the inlet 221 and the second outlet 223.
In the third inlet valve assembly 130, the first through-flow means between the first inlet 131 and the outlet 133 opens the passage and the throttling means between the second inlet 132 and the outlet 133 is in a closed state.
In the third outlet valve assembly 230, the second flow passage between the inlet 231 and the first outlet 232 is in an open state to open the inlet 231 and the first outlet 232. The first through-flow means between the inlet 231 and the second outlet 233 is in a closed state to close the passage between the inlet 231 and the second outlet 233.
In fourth inlet valve assembly 140, the first flow-through device between first inlet 141 and outlet 143 opens a passage, and the throttling device between second inlet 142 and outlet 143 is in a closed state.
In the fourth outlet valve assembly 240, the second flow passage between the inlet 241 and the first outlet 242 is in an open state to open the inlet 241 and the first outlet 242 passages. The first through-flow means between the inlet 241 and the second outlet 243 is in a closed state to close the passage between the inlet 241 and the second outlet 243.
Based on the above-mentioned on-off control of the valve assembly channels, the heat pump system 10 can be controlled to switch from the heating mode to the standby mode, and then from the standby mode to the cooling mode, so as to realize the mode switching. After entering the cooling mode, the heat pump system 10 collects corresponding parameters and adjusts the flow rate of the throttling devices in the first inlet valve assembly 110 and the second inlet valve assembly 120 so as to make the indoor temperature meet the set temperature input by the user through the panel (or the remote controller). The flow rate adjustment process can be referred to as the calculation control process in the cooling mode in the first embodiment. When it is desired to exit the cooling mode, the heat pump system 10 may be shut down or enter a standby mode.
In other embodiments, the heat pump system 10 may also include a constant pressure valve or check valve 46, or both a constant pressure valve and check valve 46.
For example, a constant pressure valve and a check valve 46 may be provided between the outlet of the compressor 20 and the inlet of the second common rail line 31, and the positions of the constant pressure valve and the check valve 46 may be exchanged, which is not particularly limited herein. The constant pressure valve is used to adjust the pressure of the refrigerant discharged from the compressor 20 so that the pressure satisfies a corresponding operation mode. The check valve 46 serves to prevent the refrigerant in the second common rail line 31 from reversely flowing into the inlet of the compressor 20.
It should be noted that the heat pump system 10 can close the passages of all valve components and single valves (e.g., constant pressure valve, check valve 46) during shutdown. For example, when the control module of the heat pump system 10 receives a shutdown instruction, it may control all channels of the inlet valve assemblies and the outlet valve assemblies connected to the inlets and the outlets of all indoor heat exchangers to be closed, control all channels of the inlet valve assemblies and the outlet valve assemblies connected to the inlets and the outlets of all outdoor heat exchangers to be closed, and control channels of the single valves, such as the check valve 46 and the constant pressure valve, to be closed. In addition, the heat pump system 10 may directly enter the target operation mode (for example, directly enter the heating mode) during the startup process; or, in the starting process, the heat pump system may enter the standby mode first, and then switch from the standby mode to the current target working mode, which is beneficial to improving the reliability of the starting operation of the heat pump system 10, and avoids that the normal transportation of the refrigerant is affected by the presence of a valve which is not closed in the heat pump system 10 before the starting operation, so that the heat pump system 10 cannot operate normally.
In the above embodiments, the processing module may be an integrated circuit chip having signal processing capability. The processing module may be a general purpose processor. For example, the Processor may be a Central Processing Unit (CPU), a Graphics Processing Unit (GPU), a Network Processor (NP), or the like; and may also be 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, or discrete hardware components, which may implement or perform the methods, steps, and logic blocks disclosed in the embodiments of the present Application.
The memory module may be, but is not limited to, a random access memory, a read only memory, a programmable read only memory, an erasable programmable read only memory, an electrically erasable programmable read only memory, and the like. In this embodiment, the storage module may be configured to store an operating parameter set, a preset algorithm, and the like. Of course, the storage module may also be used to store a program, and the processing module executes the program after receiving the execution instruction.
It should be noted that, as will be clear to those skilled in the art, for convenience and brevity of description, the specific working process of the control module described above may refer to the corresponding process of each step in the foregoing method, and will not be described in detail herein.
The embodiment of the application also provides a computer readable storage medium. The computer-readable storage medium has stored therein a computer program that, when run on a computer, causes the computer to execute the heat pump system control method as described in the above-described embodiments.
From the above description of the embodiments, it is clear to those skilled in the art that the present application can be implemented by hardware, or by software plus a necessary general hardware platform, and based on such understanding, the technical solution of the present application can be embodied in the form of a software product, which can be stored in a non-volatile storage medium (which can be a CD-ROM, a usb disk, a removable hard disk, etc.), and includes several instructions to enable a computer device (which can be a personal computer, a server, or a network device, etc.) to execute the method described in the embodiments of the present application.
In summary, the present application provides a heat pump system control method, a temperature adjustment device, and a readable storage medium. The method comprises the following steps: acquiring a working parameter set of a heat pump system and a target working mode of the heat pump system; determining a target flow rate of a target throttling device corresponding to a target working mode in the heat pump system for conveying the refrigerant according to a preset algorithm and the indoor comprehensive temperature in the working parameter set, and the current temperature and the current pressure of the outlet end of an indoor heat exchanger in the heat pump system; the target throttling device is controlled to deliver refrigerant at a target flow rate. In this scheme, through current temperature and the current pressure that detects indoor temperature, indoor heat exchanger's exit end of synthesizing, so, can confirm the target velocity of flow that target throttling arrangement carried the refrigerant, then, control target throttling arrangement carries the refrigerant with the target velocity of flow, so, can realize heat pump system's accurate control under target mode, be favorable to promoting heat exchange efficiency and user experience.
In the embodiments provided in the present application, it should be understood that the disclosed apparatus, system, and method may be implemented in other ways. The apparatus, system, and method embodiments described above are illustrative only, as the flowcharts and block diagrams in the figures illustrate the architecture, functionality, and operation of possible implementations of systems, methods and computer program products according to various embodiments of the present application. In this regard, each block in the flowchart or block diagrams may represent a module, segment, or portion of code, which comprises one or more executable instructions for implementing the specified logical function(s). It will also be noted that each block of the block diagrams and/or flowchart illustration, and combinations of blocks in the block diagrams and/or flowchart illustration, can be implemented by special purpose hardware-based systems which perform the specified functions or acts, or combinations of special purpose hardware and computer instructions. In addition, functional modules in the embodiments of the present application may be integrated together to form an independent part, or each module may exist separately, or two or more modules may be integrated to form an independent part.
The above description is only an example of the present application and is not intended to limit the scope of the present application, and various modifications and changes may be made to the present application by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present application shall be included in the protection scope of the present application.

Claims (17)

1. A heat pump system control method, characterized in that the method comprises:
acquiring a working parameter set of a heat pump system and a target working mode of the heat pump system;
determining a target flow rate of a target throttling device in the heat pump system corresponding to the target working mode for conveying the refrigerant according to a preset algorithm, the indoor comprehensive temperature in the working parameter set, and the current temperature and the current pressure of the outlet end of an indoor heat exchanger in the heat pump system;
and controlling the target throttling device to convey the refrigerant at the target flow rate.
2. The method of claim 1, wherein the heat pump system comprises a compressor, indoor heat exchangers, outdoor heat exchangers, and a first common rail line, an inlet of each heat exchanger selectively communicating with an outlet of the compressor or in throttling communication with an outlet of the first common rail line, and an outlet of each heat exchanger selectively communicating with an inlet of the compressor or with an inlet of the first common rail line;
in a cooling mode, an outlet of the compressor is communicated with an inlet of the outdoor heat exchanger, an outlet of the outdoor heat exchanger is communicated with an inlet of the first common rail pipeline, an outlet of the first common rail pipeline is communicated with an inlet of the indoor heat exchanger in a throttling mode through the target throttling device, an outlet of the indoor heat exchanger is communicated with an inlet of the compressor, and the target throttling device is a throttling device arranged between the outlet of the first common rail pipeline and the inlet of the indoor heat exchanger in the heat pump system;
determining a target flow rate of a target throttling device in the heat pump system corresponding to the target working mode for conveying the refrigerant according to a preset algorithm, the indoor comprehensive temperature in the working parameter set, and the current temperature and the current pressure at the outlet end of an indoor heat exchanger in the heat pump system, wherein the target flow rate comprises:
when the target working mode is the refrigeration mode, determining a target overheat temperature corresponding to the current temperature and the current pressure based on the corresponding relation between the temperature, the pressure and the overheat temperature of the indoor heat exchanger;
determining the target flow rate of the refrigerant sent by the target throttling device according to a first preset formula, wherein the first preset formula is as follows:
Figure FDA0003133957780000011
in the first predetermined formula, PWM ij Refers to the target flow rate;
PWM cal the flow rate to be corrected;
d denotes a first predetermined coefficient;
e denotes a second predetermined coefficient;
T B refers to the target superheat temperature;
T Bset the set overheat temperature is indicated;
T D refers to the indoor integrated temperature;
T set refers to the set temperature.
3. The method of claim 1, wherein the heat pump system comprises a compressor, an indoor heat exchanger, an outdoor heat exchanger, and a first common rail line, an inlet of each heat exchanger selectively communicating with an outlet of the compressor or in throttled communication with an outlet of the first common rail line, an outlet of each heat exchanger selectively communicating with an inlet of the compressor or with an inlet of the first common rail line;
in the heating mode, an outlet of the compressor is communicated with an inlet of the indoor heat exchanger, an outlet of the indoor heat exchanger is communicated with an inlet of the first common rail pipeline, an outlet of the first common rail pipeline is in throttling communication with an inlet of the outdoor heat exchanger through the target throttling device, an outlet of the outdoor heat exchanger is communicated with an inlet of the compressor, and the target throttling device is a throttling device arranged between the outlet of the first common rail pipeline and the inlet of the outdoor heat exchanger in the heat pump system;
determining a target flow rate of a target throttling device in the heat pump system corresponding to the target working mode for conveying the refrigerant according to a preset algorithm, the indoor comprehensive temperature in the working parameter set, and the current temperature and the current pressure at the outlet end of an indoor heat exchanger in the heat pump system, wherein the target flow rate comprises:
when the target working mode is the heating mode, determining a target supercooling temperature corresponding to the current temperature and the current pressure based on the corresponding relation between the temperature, the pressure and the supercooling temperature of the indoor heat exchanger;
determining the target flow rate of the refrigerant sent by the target throttling device according to a second preset formula, wherein the second preset formula is as follows:
Figure FDA0003133957780000021
wherein, in the second preset formula, PWM ij Refers to the target flow rate;
PWM cal the flow rate to be corrected;
d denotes a first predetermined coefficient;
e denotes a second predetermined coefficient;
T L refers to the target subcooling temperature;
T Lset setting the supercooling temperature;
T D refers to the indoor integrated temperature;
T set refers to the set temperature.
4. The method of claim 3, wherein the number of indoor heat exchangers is one, and the number of outdoor heat exchangers is plural;
acquiring a target working mode of the heat pump system, wherein the target working mode comprises the following steps:
acquiring the temperatures of the plurality of outdoor heat exchangers in the working parameter set;
when the temperatures of the outdoor heat exchangers meet preset defrosting conditions, determining that the target working mode is a heating defrosting mode;
in the heating and defrosting mode, an outlet of the compressor is respectively communicated with an inlet of the indoor heat exchanger and an inlet of a part of outdoor heat exchangers, an outlet of the part of outdoor heat exchangers and an outlet of the indoor heat exchangers are communicated with an inlet of the first common rail pipeline, an outlet of the first common rail pipeline is in throttling communication with an inlet of another part of outdoor heat exchangers through the target throttling device, an outlet of the another part of outdoor heat exchangers is communicated with an inlet of the compressor, and the target throttling device is a throttling device arranged between the outlet of the first common rail pipeline and the another part of outdoor heat exchangers in the heat pump system.
5. The method of claim 4, further comprising:
and when the temperature of any outdoor heat exchanger in the plurality of outdoor heat exchangers is less than or equal to a first preset temperature, determining that the preset defrosting condition is met.
6. The method of claim 1, wherein the heat pump system comprises a compressor, an indoor heat exchanger, an outdoor heat exchanger, and a first common rail line, an inlet of each heat exchanger selectively communicating with an outlet of the compressor or with an outlet throttle of the first common rail line, an outlet of each heat exchanger selectively communicating with an inlet of the compressor or with an inlet of the first common rail line, the number of indoor heat exchangers being plural, the number of outdoor heat exchangers being one;
in a heating and dehumidifying mode, an outlet of the compressor is communicated with an inlet of a part of indoor heat exchangers, outlets of the part of indoor heat exchangers are communicated with an inlet of the first common rail pipeline, an outlet of the first common rail pipeline is in throttling communication with an inlet of another part of indoor heat exchangers through a first target throttling device, outlets of the another part of indoor heat exchangers are communicated with an inlet of the compressor, an outlet of the first common rail pipeline is in throttling communication with an inlet of the outdoor heat exchanger through a second target throttling device, and an outlet of the outdoor heat exchanger is communicated with an inlet of the compressor;
the target flow rates include a first target flow rate corresponding to the first target throttling device and a second target flow rate corresponding to the second target throttling device;
the first target throttling device is a throttling device arranged between an outlet of the first common rail pipeline and an inlet of the other part of indoor heat exchangers in the heat pump system;
the second target throttling device is a throttling device arranged between an outlet of the first common rail pipeline and an inlet of the outdoor heat exchanger in the heat pump system;
determining a target flow rate of a target throttling device in the heat pump system corresponding to the target working mode for conveying the refrigerant according to a preset algorithm, the indoor comprehensive temperature in the working parameter set, and the current temperature and the current pressure at the outlet end of an indoor heat exchanger in the heat pump system, wherein the target flow rate comprises:
when the target working mode is the heating and dehumidifying mode, determining a target supercooling temperature corresponding to the current temperature and the current pressure at the outlet end of a target indoor heat exchanger based on the corresponding relation between the temperature, the pressure and the supercooling temperature of the indoor heat exchanger, wherein the target indoor heat exchanger is one of the indoor heat exchangers which is communicated with the outlet of the compressor;
determining a target dew point temperature corresponding to the current indoor temperature and the current indoor humidity based on the corresponding relationship among the temperature, the humidity and the dew point temperature;
determining the first target flow rate of the refrigerant sent by the first target throttling device and the second target flow rate of the refrigerant sent by the second target throttling device according to a third preset formula, wherein the third preset formula is as follows:
Figure FDA0003133957780000041
wherein, in the third preset formula, PWM dew Refers to the first target flow rate;
PWM ij refers to the second target flow rate;
PWM cal the flow rate to be corrected;
d denotes a first predetermined coefficient;
e denotes a second predetermined coefficient;
f denotes a third predetermined coefficient;
g denotes a fourth predetermined coefficient;
T L refers to the target subcooling temperature;
T Lset setting the supercooling temperature;
T D refers to the indoor integrated temperature;
T set the set temperature is indicated;
T dew refers to the target dew point temperature;
T in refers to the current indoor temperature;
TH in current indoor humidity;
TH max refers to a preset maximum humidity.
7. The method of claim 1, wherein the heat pump system comprises a compressor, indoor heat exchangers, outdoor heat exchangers, and a first common rail line, an inlet of each heat exchanger selectively communicating with an outlet of the compressor or in throttling communication with an outlet of the first common rail line, and an outlet of each heat exchanger selectively communicating with an inlet of the compressor or with an inlet of the first common rail line; the number of the indoor heat exchangers is multiple, and the number of the outdoor heat exchangers is multiple;
in a dehumidification-defrosting mode, an outlet of the compressor is respectively communicated with an inlet of a part of indoor heat exchangers and an inlet of a part of outdoor heat exchangers, outlets of the part of indoor heat exchangers and the part of outdoor heat exchangers are communicated with an inlet of the first common rail pipeline, an outlet of the first common rail pipeline is in throttling communication with the other part of indoor heat exchangers through a first target throttling device, an outlet of the first common rail pipeline is also in throttling communication with inlets of the other part of outdoor heat exchangers through a second target throttling device, and outlets of the other part of indoor heat exchangers and the other part of outdoor heat exchangers are communicated with the inlet of the compressor;
the target flow rates include a first target flow rate corresponding to the first target throttling device and a second target flow rate corresponding to the second target throttling device;
the first target throttling device is a throttling device arranged between an outlet of the first common rail pipeline and an inlet of the other part of indoor heat exchangers in the heat pump system;
the second target throttling device is a throttling device arranged between an outlet of the first common rail pipeline and an inlet of the other part of outdoor heat exchanger in the heat pump system;
determining a target flow rate of a target throttling device in the heat pump system corresponding to the target working mode for conveying the refrigerant according to a preset algorithm, the indoor comprehensive temperature in the working parameter set, and the current temperature and the current pressure at the outlet end of an indoor heat exchanger in the heat pump system, wherein the target flow rate comprises:
when the target working mode is a dehumidification-defrosting mode, determining a target supercooling temperature corresponding to the current temperature and the current pressure at the outlet end of a target indoor heat exchanger based on the corresponding relation between the temperature, the pressure and the supercooling temperature of the indoor heat exchanger, wherein the target indoor heat exchanger is one of the indoor heat exchangers which is communicated with the outlet of the compressor;
determining a target dew point temperature corresponding to the current indoor temperature and the current indoor humidity based on the corresponding relationship among the temperature, the humidity and the dew point temperature;
determining the first target flow rate of the refrigerant sent by the first target throttling device and the second target flow rate of the refrigerant sent by the second target throttling device according to a fourth preset formula, wherein the fourth preset formula is as follows:
Figure FDA0003133957780000051
wherein, in the fourth preset formula, PWM dew Refers to the first target flow rate;
PWM ij refers to the second target flow rate;
PWM cal the flow rate to be corrected;
d denotes a first predetermined coefficient;
e denotes a second predetermined coefficient;
f denotes a third preset coefficient;
g denotes a fourth predetermined coefficient;
T L refers to the target subcooling temperature;
T Lset the set supercooling temperature is indicated;
T D refers to the indoor integrated temperature;
T set the set temperature is indicated;
T dew refers to the target dew point temperature;
T in refers to the current indoor temperature;
TH in current indoor humidity;
TH max refers to a preset maximum humidity.
8. The method of claim 1, wherein when the target operating mode is an operating mode to be switched determined from a received mode switch command, prior to controlling the target throttling device to deliver refrigerant at the target flow rate, the method further comprises:
and controlling the heat pump system to enter a standby state, and then switching to the target working mode from the standby state.
9. The temperature adjusting equipment is characterized by comprising a control module and a heat pump system;
the control module is used for acquiring a working parameter set of the heat pump system and a target working mode of the heat pump system;
the control module is further used for determining a target flow rate of a target throttling device in the heat pump system corresponding to the target working mode for conveying the refrigerant according to a preset algorithm, the indoor comprehensive temperature in the working parameter set, and the current temperature and the current pressure at the outlet end of an indoor heat exchanger in the heat pump system;
the control module is further configured to control the target throttling device to deliver refrigerant at the target flow rate.
10. The apparatus of claim 9, wherein the heat pump system comprises a compressor, an indoor heat exchanger, an outdoor heat exchanger, and a first common rail line, an inlet of each heat exchanger selectively communicating with an outlet of the compressor or in throttling communication with an outlet of the first common rail line, an outlet of each heat exchanger selectively communicating with an inlet of the compressor or with an inlet of the first common rail line;
in a cooling mode, an outlet of the compressor is communicated with an inlet of the outdoor heat exchanger, an outlet of the outdoor heat exchanger is communicated with an inlet of the first common rail pipeline, an outlet of the first common rail pipeline is in throttling communication with an inlet of the indoor heat exchanger through the target throttling device, an outlet of the indoor heat exchanger is communicated with an inlet of the compressor, and the target throttling device is a throttling device arranged between the outlet of the first common rail pipeline and the inlet of the indoor heat exchanger in the heat pump system;
the control module is further configured to:
when the target working mode is the refrigeration mode, determining a target overheating temperature corresponding to the current temperature and the current pressure based on the corresponding relation between the temperature and the pressure and the overheating temperature of the indoor heat exchanger;
determining the target flow rate of the refrigerant sent by the target throttling device according to a first preset formula, wherein the first preset formula is as follows:
Figure FDA0003133957780000061
in the first predetermined formula, PWM ij Refers to the target flow rate;
PWM cal the flow rate to be corrected;
d denotes a first predetermined coefficient;
e denotes a second predetermined coefficient;
T B refers to the target superheat temperature;
T Bset the set overheat temperature is indicated;
T D refers to the indoor integrated temperature;
T set refers to the set temperature.
11. The apparatus of claim 9, wherein the heat pump system comprises a compressor, an indoor heat exchanger, an outdoor heat exchanger, and a first common rail line, an inlet of each heat exchanger selectively communicating with an outlet of the compressor or in throttled communication with an outlet of the first common rail line, an outlet of each heat exchanger selectively communicating with an inlet of the compressor or with an inlet of the first common rail line;
in the heating mode, an outlet of the compressor is communicated with an inlet of the indoor heat exchanger, an outlet of the indoor heat exchanger is communicated with an inlet of the first common rail pipeline, an outlet of the first common rail pipeline is in throttling communication with an inlet of the outdoor heat exchanger through the target throttling device, an outlet of the outdoor heat exchanger is communicated with an inlet of the compressor, and the target throttling device is a throttling device arranged between the outlet of the first common rail pipeline and the inlet of the outdoor heat exchanger in the heat pump system;
the control module is further configured to:
when the target working mode is the heating mode, determining a target supercooling temperature corresponding to the current temperature and the current pressure based on the corresponding relation between the temperature and the pressure and the supercooling temperature of the indoor heat exchanger;
determining the target flow rate of the refrigerant sent by the target throttling device according to a second preset formula, wherein the second preset formula is as follows:
Figure FDA0003133957780000071
wherein, in the second preset formula, PWM ij Refers to the target flow rate;
PWM cal the flow rate to be corrected;
d denotes a first predetermined coefficient;
e denotes a second predetermined coefficient;
T L refers to the target subcooling temperature;
T Lset the set supercooling temperature is indicated;
T D refers to the indoor integrated temperature;
T set refers to the set temperature.
12. The apparatus of claim 11, wherein the number of the indoor heat exchangers is one, and the number of the outdoor heat exchangers is plural; the control module is further configured to:
acquiring the temperatures of the plurality of outdoor heat exchangers in the working parameter set;
when the temperatures of the outdoor heat exchangers meet preset defrosting conditions, determining that the target working mode is a heating defrosting mode;
in the heating and defrosting mode, an outlet of the compressor is respectively communicated with an inlet of the indoor heat exchanger and an inlet of a part of outdoor heat exchangers, an outlet of the part of outdoor heat exchangers and an outlet of the indoor heat exchangers are communicated with an inlet of the first common rail pipeline, an outlet of the first common rail pipeline is in throttling communication with an inlet of another part of outdoor heat exchangers through the target throttling device, an outlet of the another part of outdoor heat exchangers is communicated with an inlet of the compressor, and the target throttling device is a throttling device arranged between the outlet of the first common rail pipeline and the another part of outdoor heat exchangers in the heat pump system.
13. The apparatus of claim 12, wherein the control module is further configured to:
and when the temperature of any outdoor heat exchanger in the plurality of outdoor heat exchangers is less than or equal to a first preset temperature, determining that the preset defrosting condition is met.
14. The apparatus of claim 9, wherein the heat pump system comprises a compressor, indoor heat exchangers, an outdoor heat exchanger, and a first common rail line, an inlet of each heat exchanger selectively communicating with an outlet of the compressor or in throttling communication with an outlet of the first common rail line, an outlet of each heat exchanger selectively communicating with an inlet of the compressor or with an inlet of the first common rail line, the number of indoor heat exchangers being plural, the number of outdoor heat exchangers being one;
in a heating and dehumidifying mode, an outlet of the compressor is communicated with an inlet of a part of indoor heat exchangers, an outlet of the part of indoor heat exchangers is communicated with an inlet of the first common rail pipeline, an outlet of the first common rail pipeline is in throttling communication with an inlet of another part of indoor heat exchangers through a first target throttling device, an outlet of the another part of indoor heat exchangers is communicated with an inlet of the compressor, an outlet of the first common rail pipeline is in throttling communication with an inlet of the outdoor heat exchanger through a second target throttling device, and an outlet of the outdoor heat exchanger is communicated with an inlet of the compressor;
the target flow rates include a first target flow rate corresponding to the first target throttling device and a second target flow rate corresponding to the second target throttling device;
the first target throttling device is a throttling device arranged between an outlet of the first common rail pipeline and an inlet of the other part of indoor heat exchangers in the heat pump system;
the second target throttling device is a throttling device arranged between an outlet of the first common rail pipeline and an inlet of the outdoor heat exchanger in the heat pump system;
the control module is further configured to:
when the target working mode is the heating and dehumidifying mode, determining a target supercooling temperature corresponding to the current temperature and the current pressure at the outlet end of a target indoor heat exchanger based on the corresponding relation between the temperature, the pressure and the supercooling temperature of the indoor heat exchanger, wherein the target indoor heat exchanger is one of the indoor heat exchangers which is communicated with the outlet of the compressor;
determining a target dew point temperature corresponding to the current indoor temperature and the current indoor humidity based on the corresponding relationship among the temperature, the humidity and the dew point temperature;
determining the first target flow rate of the refrigerant sent by the first target throttling device and the second target flow rate of the refrigerant sent by the second target throttling device according to a third preset formula, wherein the third preset formula is as follows:
Figure FDA0003133957780000081
wherein, in the third preset formula, PWM dew Refers to the first target flow rate;
PWM ij refers to the second target flow rate;
PWM cal the flow rate to be corrected;
d denotes a first predetermined coefficient;
e denotes a second predetermined coefficient;
f denotes a third predetermined coefficient;
g denotes a fourth predetermined coefficient;
T L refers to the target subcooling temperature;
T Lset the set supercooling temperature is indicated;
T D refers to the indoor integrated temperature;
T set the set temperature is indicated;
T dew indicates the target lotionA point temperature;
T in refers to the current indoor temperature;
TH in current indoor humidity;
TH max refers to a preset maximum humidity.
15. The apparatus of claim 9, wherein the heat pump system comprises a compressor, an indoor heat exchanger, an outdoor heat exchanger, and a first common rail line, an inlet of each heat exchanger selectively communicating with an outlet of the compressor or in throttled communication with an outlet of the first common rail line, an outlet of each heat exchanger selectively communicating with an inlet of the compressor or with an inlet of the first common rail line; the number of the indoor heat exchangers is multiple, and the number of the outdoor heat exchangers is multiple;
in a dehumidification-defrosting mode, an outlet of the compressor is respectively communicated with an inlet of a part of indoor heat exchangers and an inlet of a part of outdoor heat exchangers, outlets of the part of indoor heat exchangers and the part of outdoor heat exchangers are communicated with an inlet of the first common rail pipeline, an outlet of the first common rail pipeline is in throttling communication with the other part of indoor heat exchangers through a first target throttling device, an outlet of the first common rail pipeline is also in throttling communication with inlets of the other part of outdoor heat exchangers through a second target throttling device, and outlets of the other part of indoor heat exchangers and the other part of outdoor heat exchangers are communicated with the inlet of the compressor;
the target flow rates include a first target flow rate corresponding to the first target throttling device and a second target flow rate corresponding to the second target throttling device;
the first target throttling device is a throttling device arranged between an outlet of the first common rail pipeline and an inlet of the other part of indoor heat exchangers in the heat pump system;
the second target throttling device is a throttling device arranged between an outlet of the first common rail pipeline and an inlet of the other part of outdoor heat exchanger in the heat pump system;
the control module is further configured to:
when the target working mode is a dehumidification and defrosting mode, determining a target supercooling temperature corresponding to the current temperature and the current pressure at the outlet end of a target indoor heat exchanger based on the corresponding relation between the temperature, the pressure and the supercooling temperature of the indoor heat exchanger, wherein the target indoor heat exchanger is one of a plurality of indoor heat exchangers which is communicated with the outlet of the compressor;
determining a target dew point temperature corresponding to the current indoor temperature and the current indoor humidity based on the corresponding relationship among the temperature, the humidity and the dew point temperature;
determining the first target flow rate of the refrigerant sent by the first target throttling device and the second target flow rate of the refrigerant sent by the second target throttling device according to a fourth preset formula, wherein the fourth preset formula is as follows:
Figure FDA0003133957780000091
wherein, in the fourth preset formula, PWM dew Refers to the first target flow rate;
PWM ij refers to the second target flow rate;
PWM cal the flow rate to be corrected;
d denotes a first predetermined coefficient;
e denotes a second predetermined coefficient;
f denotes a third preset coefficient;
g denotes a fourth predetermined coefficient;
T L refers to the target subcooling temperature;
T Lset the set supercooling temperature is indicated;
T D refers to the indoor integrated temperature;
T set the set temperature is indicated;
T dew refers to the target dew point temperature;
T in refers to the current indoor temperature;
TH in current indoor humidity;
TH max refers to a preset maximum humidity.
16. The apparatus of claim 9, wherein when the target operating mode is the operating mode to be switched determined from the received mode switch command, the control module is further configured to, prior to the control module controlling the target throttling device to deliver refrigerant at the target flow rate:
and controlling the heat pump system to enter a standby state, and then switching to the target working mode from the standby state.
17. A computer-readable storage medium, in which a computer program is stored which, when run on a computer, causes the computer to carry out the method according to any one of claims 1-8.
CN202110711527.5A 2021-06-25 2021-06-25 Heat pump system control method, temperature adjusting device and readable storage medium Pending CN115523677A (en)

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