CN209085113U - Heat pump system - Google Patents
Heat pump system Download PDFInfo
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- CN209085113U CN209085113U CN201821886809.9U CN201821886809U CN209085113U CN 209085113 U CN209085113 U CN 209085113U CN 201821886809 U CN201821886809 U CN 201821886809U CN 209085113 U CN209085113 U CN 209085113U
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Abstract
The utility model provides a kind of heat pump system.The heat pump system includes compressor, indoor heat exchanger, outdoor heat exchanger, flash evaporation and pressure-regulating device, compressor includes master cylinder and auxiliary cylinders, flash evaporation is arranged between indoor heat exchanger and outdoor heat exchanger, pressure-regulating device is arranged between the liquid refrigerants outlet of flash evaporation and indoor heat exchanger, the gaseous coolant outlet of flash evaporation is connected to the air entry of auxiliary cylinders, refrigerant pressure of the pressure-regulating device for adjusting pressure-regulating device both ends under cooling condition is poor, so that the refrigerant pressure difference at pressure-regulating device both ends is in the first preset range, or make the refrigerant pressure difference at pressure-regulating device both ends in the second preset range, wherein the minimum value of the second preset range is greater than the maximum value of the first preset range.Heat pump system according to the present utility model can conveniently realize the switching of middle the pressure tonifying Qi and low pressure tonifying Qi of compressor, and structure and control system are simple, and cost of implementation is lower.
Description
Technical field
The utility model belongs to air-conditioning technique field, and in particular to a kind of heat pump system.
Background technique
The patent of Publication No. CN106766367A discloses a kind of air-conditioning system, utilizes auxiliary compression cylinder by intermediate pressure
Refrigerant gas in strength liquid/gas separator is sent together with master cylinder exhaust to condenser after directly compressing, and in gas-liquid separator
Refrigerant liquid enters in evaporator after two-step throttle to be evaporated.Relative to conventional system, which be can reduce into steaming
The throttling mass dryness fraction for sending out the refrigerant of device, significantly improves the ability energy valid value of refrigeration system.Two shut-off valves are provided in the system,
By the opening and closing combination of two shut-off valve, realize gas-liquid separator gas outlet be connected with tonifying Qi cylinder air entry or with main compression cylinder
Air entry, which is connected, realizes the conversion of tonifying Qi mode, excessively leads to cylinder body liquid hazards because mending gas carrying liquid to avoid auxiliary compression cylinder.
However the tonifying Qi mode transition structure in the system is complex, causes control system complex, controls cost
Higher, cost of implementation is higher.
Utility model content
Therefore, the technical problem to be solved by the present invention is to provide a kind of heat pump systems, can conveniently realize pressure
The switching of middle the pressure tonifying Qi and low pressure tonifying Qi of contracting machine, structure and control system are simple, and cost of implementation is lower.
To solve the above-mentioned problems, the utility model provides a kind of heat pump system, including compressor, indoor heat exchanger, room
External heat exchanger, flash evaporation and pressure-regulating device, compressor include master cylinder and auxiliary cylinders, flash evaporation setting indoors heat exchanger and
Between outdoor heat exchanger, pressure-regulating device is arranged between the liquid refrigerants outlet of flash evaporation and indoor heat exchanger, flash evaporation
Gaseous coolant outlet be connected to the air entries of auxiliary cylinders, pressure-regulating device, which is used to adjust pressure under cooling condition, adjusts dress
The refrigerant pressure for setting both ends is poor, so that the refrigerant pressure difference at pressure-regulating device both ends is in the first preset range, or makes
The refrigerant pressure difference at pressure-regulating device both ends is in the second preset range, wherein the minimum value of the second preset range is greater than first
The maximum value of preset range.
Preferably, first throttle valve is provided between outdoor heat exchanger and flash evaporation.
Preferably, the first control is provided on the pipeline between the gaseous coolant outlet of flash evaporation and the air entry of auxiliary cylinders
Valve.
Preferably, pressure-regulating device includes the second control valve and second throttle in parallel.
Preferably, pressure-regulating device includes second throttle, when the aperture of second throttle is in the first range, second
The pressure difference at throttle valve both ends is located in the first preset range, and the aperture of second throttle is in the second range, second throttle
The pressure difference at both ends is located in the second preset range.
Preferably, heat pump system further includes four-way valve, and the exhaust end of compressor is arranged in four-way valve.
Heat pump system provided by the utility model, including compressor, indoor heat exchanger, outdoor heat exchanger, flash evaporation and pressure
Apparatus for adjusting force, compressor include master cylinder and auxiliary cylinders, and flash evaporation is arranged between indoor heat exchanger and outdoor heat exchanger, pressure
Regulating device is arranged between the liquid refrigerants outlet of flash evaporation and indoor heat exchanger, and the gaseous coolant outlet of flash evaporation is connected to
The air entry of auxiliary cylinders, refrigerant pressure of the pressure-regulating device for adjusting pressure-regulating device both ends under cooling condition is poor,
So that the refrigerant pressure difference at pressure-regulating device both ends is in the first preset range, or make the cold of pressure-regulating device both ends
Matchmaker's pressure difference is in the second preset range, wherein the minimum value of the second preset range is greater than the maximum value of the first preset range.?
When heat pump system is in cooling condition, the pressure difference at pressure-regulating device both ends can be adjusted by pressure-regulating device, from
And the refrigerant pressure in flash evaporation is adjusted, refrigerant pressure when so that heat pump system being run under low-pressure ratio operating condition, in flash evaporation
In low-pressure state identical with the refrigerant pressure in indoor heat exchanger, low pressure tonifying Qi is realized；Heat pump system is in high pressure ratio operating condition
When lower operation, the refrigerant pressure in flash evaporation is in the centre between the low pressure refrigerant pressure in high-pressure and indoor heat exchanger
Pressure state presses tonifying Qi in realization, realizes the system tonifying Qi mould under different working conditions so as to pass through pressure-regulating device
The conversion of formula can conveniently realize compressor so that heat pump system can realize efficient operation under different working conditions
Middle pressure tonifying Qi and low pressure tonifying Qi switching, structure and control system are simple, and cost of implementation is lower.
Detailed description of the invention
Fig. 1 is the structural schematic diagram of the heat pump system of the utility model embodiment；
Fig. 2 is the refrigerant flow graph of heat pump system low pressure tonifying Qi mode under cooling condition of the utility model embodiment；
Fig. 3 is the refrigerant flow graph of heat pump system startup stage under cooling condition of the utility model embodiment；
Fig. 4 is the refrigerant flow graph of heat pump system middle pressure tonifying Qi mode under cooling condition of the utility model embodiment；
Fig. 5 is refrigerant flow graph of the heat pump system of the utility model embodiment under heating condition；
Fig. 6 is the whole refrigerant flow schematic diagram of the heat pump system of the utility model embodiment；
Fig. 7 is the control principle drawing of the heat pump system of the utility model embodiment；
Fig. 8 is the control flow chart of the heat pump system of the utility model embodiment.
Appended drawing reference indicates are as follows:
1, master cylinder；2, auxiliary cylinders；3, indoor heat exchanger；4, outdoor heat exchanger；5, flash evaporation；6, first throttle valve；7,
One control valve；8, second throttle；9, the second control valve；10, four-way valve.
Specific embodiment
In conjunction with referring to shown in Fig. 1 to Fig. 6, embodiment according to the present utility model, heat pump system includes that compressor, interior are changed
Hot device 3, outdoor heat exchanger 4, flash evaporation 5 and pressure-regulating device, compressor include master cylinder 1 and auxiliary cylinders 2, and flash evaporation 5 is arranged
Between indoor heat exchanger 3 and outdoor heat exchanger 4, the liquid refrigerants outlet and interior of flash evaporation 5 is arranged in pressure-regulating device
Between heat exchanger 3, the gaseous coolant outlet of flash evaporation 5 is connected to the air entry of auxiliary cylinders 2, and pressure-regulating device is for freezing
The refrigerant pressure that pressure-regulating device both ends are adjusted under operating condition is poor, so that the refrigerant pressure difference at pressure-regulating device both ends is first
In preset range, or make the refrigerant pressure difference at pressure-regulating device both ends in the second preset range, wherein second is default
The minimum value of range is greater than the maximum value of the first preset range.
Wherein indoor heat exchanger 3 and outdoor heat exchanger 4 are connected to the master cylinder 1 of compressor, and the connection of flash evaporation 5 is changed indoors
Between hot device 3 and outdoor heat exchanger 4, the gaseous coolant outlet of flash evaporation 5 is connected to the auxiliary cylinders 2 of compressor.
When heat pump system is in cooling condition, pressure-regulating device both ends can be adjusted by pressure-regulating device
Pressure difference, so that the refrigerant pressure in flash evaporation 5 is adjusted, when so that heat pump system being run under low-pressure ratio operating condition, in flash evaporation 5
Refrigerant pressure be in low-pressure state identical with the refrigerant pressure in indoor heat exchanger 3, realize low pressure tonifying Qi；Heat pump system exists
When running under high pressure ratio operating condition, the refrigerant pressure in flash evaporation 5 is in the low pressure refrigerant pressure in high-pressure and indoor heat exchanger 3
Intermediate pressure state between power presses tonifying Qi in realization, so as to be realized by pressure-regulating device in different working conditions
The conversion of lower system tonifying Qi mode can facilitate so that heat pump system can realize efficient operation under different working conditions
The switching of middle the pressure tonifying Qi and low pressure tonifying Qi of compressor is realized on ground, and structure and control system are simple, and cost of implementation is lower.
In the present embodiment, when the refrigerant pressure difference at pressure-regulating device both ends is in the first preset range, flash evaporation 5
The refrigerant pressure of gaseous coolant outlet is low pressure, when the refrigerant pressure difference at pressure-regulating device both ends is in the second preset range,
The refrigerant pressure of the gaseous coolant outlet of flash evaporation 5 is middle pressure, and when refrigerant pressure is low pressure, the gaseous coolant of flash evaporation 5 goes out
The refrigerant pressure of mouth is equal with the refrigerant pressure in indoor heat exchanger 3 or pressure difference is in a smaller range；When refrigerant pressure
The pressure between refrigerant pressure when power is middle pressure, in the refrigerant pressure and indoor heat exchanger 3 of the gaseous coolant outlet of flash evaporation 5
Difference is in a larger range, so that low pressure of the refrigerant pressure of the gaseous coolant outlet of flash evaporation 5 in indoor heat exchanger 3
Between the pressure of the high pressure refrigerant of refrigerant and exhaust outlet of compressor.
First throttle valve 6 is provided between outdoor heat exchanger 4 and flash evaporation 5.The first throttle valve 6 is for changing through outdoor
Refrigerant after hot 4 exothermic condensation of device carries out first time reducing pressure by regulating flow, reduces refrigerant pressure, enables liquid refrigerants part gas
Change, to generate enough gaseous coolants in flash evaporation 5, meets the tonifying Qi requirement of heat pump system.
Preferably, the first control is provided on the pipeline between the air entry of the gaseous coolant outlet and auxiliary cylinders 2 of flash evaporation 5
Valve 7 processed.First control valve 7 is arranged on blowdown pipe road, the on-off of tonifying Qi pipeline can be controlled, so that controlling heat pump system is
No carry out tonifying Qi.Blowdown pipe road can also be not provided with the first control valve 7, so that tonifying Qi pipeline is connected to flash evaporation 5 always
Gaseous coolant outlet and auxiliary cylinders 2 air entry, realize compression cylinder tonifying Qi operation.First control valve 7 is, for example, shut-off valve,
Or the other types of solenoid valve etc. with opening and closing function.
In the present embodiment, pressure-regulating device includes the second control valve 9 and second throttle 8 in parallel.
It is adjusted by the second control valve 9 and the opening and closing combination of the valve of second throttle 8, it can be by the air entry of auxiliary cylinders 2 point
It is not connected with middle pressure gas supplementing opening or low pressure gas supplementing opening, the conversion of the system model under different working conditions is realized, so that heat pump
System system under different working conditions can realize efficient operation.Under high pressure ratio working condition, combination is opened and closed by valve and is adjusted
Section, makes the air entry of auxiliary cylinders 2 be connected with middle pressure tonifying Qi, at this point, indoor heat exchanger 3 and flash evaporation 5 pass through second throttle 8
It connects, presses tonifying Qi in realization；When being run under low-pressure ratio operating condition, combination is opened and closed by valve and is adjusted, make the air entries of auxiliary cylinders 2 with
Low pressure gas supplementing opening connection, indoor heat exchanger 3 is directly connected to flash evaporation 5 by connecting line at this time, the pressure in flash evaporation 5 and
3 inner refrigerant pressure of indoor heat exchanger is identical, realizes low pressure tonifying Qi.
Specifically, when the second control valve 9 is closed, when the first control valve 7 is opened, outdoor heat exchanger 4 and indoor heat exchanger 3
Between be connected by first throttle valve 6, flash evaporation 5 with second throttle 8, at this time the refrigerant pressure in flash evaporation 5 between
Intermediate pressure between high-low pressure, the pressure of inspiration(Pi) of auxiliary cylinders 2 is intermediate pressure at this time, i.e., middle pressure tonifying Qi, under the operational mode,
Auxiliary cylinders 2 are lowered into the refrigerant mass dryness fraction of indoor heat exchanger 3 by sucking medium pressure gas, to improve the unit matter of master cylinder 1
Refrigerating capacity and system operational energy efficiency are measured, which is suitable for the throttling biggish occasion of mass dryness fraction of indoor heat exchanger 3, i.e. compressor suction
The bigger occasion of air pressure improves the tonifying Qi quality stream of auxiliary cylinders 2 by providing superfeed pressure when suction and discharge pressure ratio is larger
Amount, is more advantageous to the promotion of heat pump system ability efficiency.
When the first control valve 7 is opened, the second control valve 9 is also opened, the pressure of 5 inner refrigerant of flash evaporation and indoor heat exchange
Refrigerant pressure at device 3 is identical, at this point, the pressure of inspiration(Pi) of auxiliary cylinders 2 is low pressure air suction, realizes low pressure tonifying Qi, passes through compression
The refrigerant gas isolated in flash evaporation 5 realizes the reduction of 3 entrance mass dryness fraction of indoor heat exchanger, improves making for indoor heat exchanger 3
With efficiency, increase the unit mass refrigerating capacity and system energy efficiency of master cylinder 1, is suitable for the lower occasion of load and suction and discharge pressure ratio
Low occasion avoids under the conditions of underrun due to the unfavorable shadow of the small caused excessive bring of tonifying Qi liquid carrying rate of air compensation
It rings, guarantees heat pump system reliability of operation.
In the present embodiment, only by the simple combination and control of 9 two valves of second throttle 8 and the second control valve,
The switching that low pressure tonifying Qi and the middle pressure tonifying Qi of auxiliary cylinders can be conveniently realized, allows heat pump system in different load item
The conversion that mode is carried out under part guarantees that heat pump system runs high efficiency under different operating conditions, and structure is simple, and control cost substantially drops
It is low.
In another unshowned embodiment, pressure-regulating device includes second throttle 8, and second throttle 8 is opened
When degree is in the first range, the pressure difference at 8 both ends of second throttle is located in the first preset range, the aperture of second throttle 8
In the second range, the pressure difference at 8 both ends of second throttle is located in the second preset range.Second throttle 8 can have compared with
Big aperture regulation range, so that second throttle 8 during being adjusted, enables to the cold of 8 both ends of second throttle
Matchmaker's pressure difference is maintained in the first preset range, realizes the low pressure tonifying Qi of heat pump system；It is also possible that 8 both ends of second throttle
Refrigerant pressure difference be maintained in the second preset range, realize the middle pressure tonifying Qi of heat pump system.Due to the adjusting of second throttle 8
Range can satisfy the low pressure tonifying Qi requirement and high pressure tonifying Qi requirement of heat pump system, and there is no need to the second control valve 9 is arranged.
Heat pump system further includes four-way valve 10, and the exhaust end of compressor is arranged in four-way valve 10.By the way that four-way valve 10 is arranged,
Realize the refrigeration of heat pump system and the switching of heating condition with can be convenient.
In conjunction with shown in referring to figs. 7 and 8, embodiment according to the present utility model, a kind of control of above-mentioned heat pump system
Method, comprising: obtain the operating condition of heat pump system；When heat pump system is in refrigeration mode, the master cylinder 1 of compressor is obtained
Running parameter；The tonifying Qi mode of auxiliary cylinders 2 is determined according to the running parameter of the master cylinder 1 of compressor；Pressure-regulating device is carried out
It adjusts, so that auxiliary cylinders 2 operate in identified tonifying Qi mode.
Before obtaining the running parameter of master cylinder 1 of compressor, control method further include: auxiliary in starting up's stage control
Help cylinder 2 according to low pressure tonifying Qi mode operation；6 aperture of first throttle valve is adjusted, so that the suction superheat Δ Tsuc of master cylinder 1 is pre-
In the range of if.At starting up's stage, due to containing refrigerant in flash evaporation 5, it is easy to happen product in flash evaporation 5
The refrigerant deposited enter auxiliary cylinders 2 and cause auxiliary cylinders 2 occur liquid hammer danger, by control auxiliary cylinders 2 according to low pressure tonifying Qi
Mode operation, enabling to the refrigerant entered in auxiliary cylinders 2 is gaseous coolant, and liquid refrigerants is effectively avoided to enter auxiliary cylinders 2
And liquid hit phenomenon occurs, compressor is run to form effective protection.
By controlling the aperture of first throttle valve 6, it can make the suction superheat of master cylinder 1 in default range, energy
Enough avoid the problem that the suction superheat of compressor master cylinder 1 is excessively high and operational energy efficiency is caused to reduce.
Preferably, the preset range of the suction superheat Δ Tsuc of master cylinder 1 is 3~5 DEG C.
The tonifying Qi mode of auxiliary cylinders 2 is determined according to the running parameter of the operating condition of heat pump system and the master cylinder 1 of compressor
The step of include:
Determine the suction and discharge pressure ratio Pc/Pe of master cylinder 1；
If Pc/Pe < n, heat pump system is controlled with low pressure tonifying Qi mode operation；
If Pc/Pe >=n, heat pump system is controlled with middle pressure tonifying Qi mode operation.
Pressure-regulating device is adjusted, so that auxiliary cylinders 2 include: the step of operating in identified tonifying Qi mode
If Pc/Pe < n, the second control valve 9 of control is opened, so that the refrigerant pressure difference at pressure-regulating device both ends is first
In preset range；
If Pc/Pe >=n, the second control valve 9 of control is closed, and adjusts second throttle 8, so that pressure-regulating device both ends
Refrigerant pressure difference is in the second preset range.Wherein the value of n is 1.5~2.0.
The tonifying Qi mode of auxiliary cylinders 2 is determined according to the running parameter of the operating condition of heat pump system and the master cylinder 1 of compressor
The step of include:
Determine the condensation temperature of indoor heat exchanger 3 and the ratio Tc/Te of evaporating temperature；
The tonifying Qi mode of heat pump system is determined according to Tc/Te.The wherein condensation temperature and evaporating temperature of indoor heat exchanger 3
When by be arranged the temperature sensing package at the middle part of heat exchanger 3 indoors carry out it is detected.The value range of Tc/Te can be according to heat pump
The actual working condition of system is set.
When heat pump system is in heating mode, control the second control valve 9 be in close state, run heat pump system with
Middle pressure tonifying Qi mode operation；According to the refrigerant of 2 air entry of suction superheat and auxiliary cylinders of 1 air entry refrigerant of master cylinder band liquid
Rate combines to adjust the aperture of first throttle valve 6 and second throttle 8.
The operational process of the heat pump system of the present embodiment is illustrated below:
When the starting of heat pump system refrigeration mode, in order to guarantee that the refrigerant liquid in startup stage flash evaporation 5 is excessive
Into auxiliary cylinders 2, starts the initial stage by low pressure tonifying Qi mode operation, pass through the aperture for adjusting first throttle valve 6, control master cylinder
1 suction superheat Δ Tsuc is in reasonable range, and the general value of Δ Tsuc is at 3-5 DEG C.After stable operation for a period of time,
By detecting the size of the suction and discharge pressure ratio Pc/Pe value of master cylinder 1, judge system with middle pressure tonifying Qi mode operation or low pressure tonifying Qi
Mode operation, as Pc/Pe < n, system needs to open at this time the second control valve 9 with low pressure tonifying Qi mode operation；Work as Pc/Pe
When >=n, the second control valve 9 is closed, refrigerant exports from the liquid refrigerants of flash evaporation 5 and enters the room heat exchanger through second throttle 8
3, pressure tonifying Qi operation can make master cylinder air entry by adjusting the aperture of first throttle valve 6 and second throttle 8 in realization
The suction superheat of refrigerant and the refrigerant liquid carrying rate of auxiliary cylinders air entry meet design object.The wherein size value of n value
Range is between 1.5~2.0.
Those skilled in the art will readily recognize that above-mentioned each advantageous manner can be free under the premise of not conflicting
Ground combination, superposition.
The above is only the preferred embodiments of the present utility model only, is not intended to limit the utility model, all practical at this
Made any modifications, equivalent replacements, and improvements etc., should be included in the guarantor of the utility model within novel spirit and principle
Within the scope of shield.Above are merely preferred embodiments of the utility model, it is noted that for the ordinary skill of the art
For personnel, without deviating from the technical principle of the utility model, several improvements and modifications can also be made, these improvement
It also should be regarded as the protection scope of the utility model with modification.
Claims (6)
1. a kind of heat pump system, which is characterized in that including compressor, indoor heat exchanger (3), outdoor heat exchanger (4), flash evaporation
(5) and pressure-regulating device, the compressor include master cylinder (1) and auxiliary cylinders (2), and the flash evaporation (5) is arranged in the room
Between interior heat exchanger (3) and the outdoor heat exchanger (4), liquid of the pressure-regulating device setting in the flash evaporation (5)
Between refrigerant exit and the indoor heat exchanger (3), the gaseous coolant outlet of the flash evaporation (5) is connected to the auxiliary cylinders
(2) air entry, the pressure-regulating device are used to adjust the refrigerant pressure at the pressure-regulating device both ends under cooling condition
Power is poor, so that the refrigerant pressure difference at the pressure-regulating device both ends is in the first preset range, or makes the pressure tune
The refrigerant pressure difference at regulating device both ends is in the second preset range, wherein the minimum value of the second preset range is greater than the first default model
The maximum value enclosed.
2. heat pump system according to claim 1, which is characterized in that the outdoor heat exchanger (4) and the flash evaporation (5)
Between be provided with first throttle valve (6).
3. heat pump system according to claim 1, which is characterized in that the gaseous coolant outlet of the flash evaporation (5) and institute
It states and is provided with the first control valve (7) on the pipeline between the air entry of auxiliary cylinders (2).
4. heat pump system according to any one of claim 1 to 3, which is characterized in that the pressure-regulating device includes
Second control valve (9) and second throttle (8) in parallel.
5. heat pump system according to any one of claim 1 to 3, which is characterized in that the pressure-regulating device includes
Second throttle (8), when the aperture of the second throttle (8) is in the first range, the pressure at second throttle (8) both ends
Power difference is located in the first preset range, and the aperture of the second throttle (8) is in the second range, the second throttle (8)
The pressure difference at both ends is located in the second preset range.
6. heat pump system according to any one of claim 1 to 3, which is characterized in that the heat pump system further includes four
The exhaust end of the compressor is arranged in port valve (10), the four-way valve (10).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821886809.9U CN209085113U (en) | 2018-11-15 | 2018-11-15 | Heat pump system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821886809.9U CN209085113U (en) | 2018-11-15 | 2018-11-15 | Heat pump system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN209085113U true CN209085113U (en) | 2019-07-09 |
Family
ID=67124206
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201821886809.9U Active CN209085113U (en) | 2018-11-15 | 2018-11-15 | Heat pump system |
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| Country | Link |
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| CN (1) | CN209085113U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109341132A (en) * | 2018-11-15 | 2019-02-15 | 珠海格力电器股份有限公司 | Heat pump system and its control method |
-
2018
- 2018-11-15 CN CN201821886809.9U patent/CN209085113U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109341132A (en) * | 2018-11-15 | 2019-02-15 | 珠海格力电器股份有限公司 | Heat pump system and its control method |
| CN109341132B (en) * | 2018-11-15 | 2023-06-30 | 珠海格力电器股份有限公司 | Heat pump system and control method thereof |
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