CN107421176A - The control method and heat pump of electric expansion valve - Google Patents
The control method and heat pump of electric expansion valve Download PDFInfo
- Publication number
- CN107421176A CN107421176A CN201710505653.9A CN201710505653A CN107421176A CN 107421176 A CN107421176 A CN 107421176A CN 201710505653 A CN201710505653 A CN 201710505653A CN 107421176 A CN107421176 A CN 107421176A
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- China
- Prior art keywords
- expansion valve
- electric expansion
- control method
- aperture
- supercooling
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Links
- 238000000034 method Methods 0.000 title claims abstract description 41
- 238000004781 supercooling Methods 0.000 claims abstract description 54
- 239000003507 refrigerant Substances 0.000 claims description 16
- 239000007788 liquid Substances 0.000 abstract description 5
- 230000008859 change Effects 0.000 abstract description 4
- 238000004519 manufacturing process Methods 0.000 abstract description 4
- 238000001704 evaporation Methods 0.000 description 6
- 230000008020 evaporation Effects 0.000 description 5
- 238000009833 condensation Methods 0.000 description 4
- 230000005494 condensation Effects 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 230000007812 deficiency Effects 0.000 description 2
- 238000001035 drying Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000001914 filtration Methods 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000007791 liquid phase Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000008439 repair process Effects 0.000 description 1
Classifications
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
-
- 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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Abstract
The present invention provides a kind of control method and heat pump of electric expansion valve.The control method of the electric expansion valve includes：When the current actual suction superheat x of the heat pump within a preset range when, according to the aperture of electric expansion valve described in the current actual degree of supercooling γ of the heat pump and the compressor current Load Regulation.In the control method of electric expansion valve provided by the invention, when actual suction superheat within a preset range when, the aperture of electric expansion valve is adjusted according to the current load of actual degree of supercooling and compressor, so that heat pump has the degree of supercooling to match with compressor actual load, so as to improve the exchange capability of heat and efficiency of heat pump while absorbing gas belt liquid is avoided, and do not change the structure of heat pump in itself, the production cost of heat pump will not be increased.
Description
Technical field
The present invention relates to heat pump automation field, and in particular to the control method and heat pump of a kind of electric expansion valve
System.
Background technology
Existing heat pump is usually the aperture that electric expansion valve is adjusted according to suction superheat, to meet different works
System reliability under condition, but the problem of existing heat pump remains exchange capability of heat deficiency.
The content of the invention
In view of this, an object of the present invention is to provide a kind of heat pump exchange capability of heat and efficiency of can improving
The control method and heat pump of electric expansion valve.
To reach above-mentioned purpose, on the one hand, the present invention uses following technical scheme：
A kind of control method of electric expansion valve, the electric expansion valve are arranged on the refrigerant circulation circuit of heat pump
In, compressor is additionally provided with the refrigerant circulation circuit, the control method includes：When the current reality of the heat pump
Suction superheat x within a preset range when, it is current according to the current actual degree of supercooling γ of the heat pump and the compressor
Load Regulation described in electric expansion valve aperture.
Preferably, the control method further comprises：By the actual degree of supercooling γ with the heat pump current
Current degree of supercooling desired value C ' under compressor load is contrasted, and adjusts opening for the electric expansion valve according to comparing result
Degree.
Preferably, current degree of supercooling desired value the C '=C*Q,
Wherein, C is degree of supercooling desired value of the heat pump under compressor oepration at full load state；
Q is the percentage that current compressor load accounts for compressor total load.
Preferably, the control method further comprises：
As the actual degree of supercooling γ≤current degree of supercooling desired value C ', the aperture of the electric expansion valve is adjusted
It is small；
And/or
As the actual degree of supercooling γ>During the current degree of supercooling desired value C ', the aperture of the electric expansion valve is kept
It is constant.
Preferably, the control method further comprises：
When the actual degree of supercooling γ persistently meets γ≤C ' within first scheduled time, by the electric expansion valve
Aperture is turned down, otherwise keeps the aperture of the electric expansion valve constant.
Preferably, the control method also includes：
When the actual suction superheat x meets condition A<x<During B, adjusted according to the actual degree of supercooling γ of the heat pump
The aperture of the electric expansion valve is saved, wherein, A is suction superheat lower limit, and B is suction superheat higher limit；
And/or
As the actual suction superheat x >=B, the aperture of the electric expansion valve is not allowed to turn down；
And/or
As the actual suction superheat x≤A, the aperture of the electric expansion valve is turned down.
Preferably, when the actual suction superheat persistently meets condition x≤A within second scheduled time, by described in
The aperture of electric expansion valve is turned down, otherwise keeps the aperture of the electric expansion valve constant.
Preferably, the current degree of supercooling when the actual degree of supercooling γ≤heat pump under current compressor load
During desired value C ', the aperture of the electric expansion valve is turned down, and the stride turned down is the first stride EXV1, when the actual suction
During gas degree of superheat x≤A, the stride that the aperture of the electric expansion valve is turned down is the second stride EXV2, wherein, the first stride
EXV1<Second stride EXV2.
Preferably, suction superheat lower limit A scope is 0 DEG C≤A<5℃；And/or
Suction superheat higher limit B scope is 5 DEG C≤B<8℃；And/or
First stride EXV1 scope is 0 ＜ EXV1≤0.5%；And/or
Second stride EXV2 scope is 1%≤EXV2≤5%.
Preferably, the aperture regulation scope of the electric expansion valve is 10% to 100%.
On the other hand, the present invention uses following technical scheme：
A kind of heat pump, including electric expansion valve, the electric expansion valve is entered using control method as described above
Row control.
In the control method of electric expansion valve provided by the invention, when actual suction superheat within a preset range when, root
Factually border degree of supercooling and the current load of compressor adjust the aperture of electric expansion valve so that heat pump has and compressor
The degree of supercooling that actual load matches, so as to improve the exchange capability of heat and energy of heat pump while absorbing gas belt liquid is avoided
Effect, and do not change the structure of heat pump in itself, the production cost of heat pump will not be increased.
Brief description of the drawings
By the description to the embodiment of the present invention referring to the drawings, above-mentioned and other purpose of the invention, feature and
Advantage will be apparent from, in the accompanying drawings：
Fig. 1 shows heat pump pressure-enthalpy chart；
Fig. 2 shows the structural representation for the heat pump that the specific embodiment of the invention provides；
Fig. 3 shows the control method flow chart for the electric expansion valve that the specific embodiment of the invention provides.
In figure, 1, compressor；2nd, oil eliminator；3rd, condenser；4th, device for drying and filtering；5th, electric expansion valve；6th, evaporator；
7th, the first temperature sensor；8th, first pressure sensor；9th, second temperature sensor；10th, second pressure sensor.
Embodiment
Below based on embodiment, present invention is described, it should be understood by one skilled in the art that provided herein
Accompanying drawing is provided to the purpose of explanation, and accompanying drawing is not necessarily drawn to scale.
Unless the context clearly requires otherwise, otherwise entire disclosure is similar with the " comprising " in claims, "comprising" etc.
Word should be construed to the implication included rather than exclusive or exhaustive implication；That is, it is containing for " including but is not limited to "
Justice.
For the problem of exchange capability of heat deficiency, the application has found, in the pressure-enthalpy chart shown in Fig. 1 existing for existing heat pump
In, from above-mentioned pressure-enthalpy chart, 1 → 2 (2 ') are evaporation process, and 2 (2 ') → 3 are compression process, and 3 → 4 (4 ') are condensation process, 4
(4 ') → 1 is throttling process.Ts.c is cold temperature again, then cold temperature Ts.c and condensation temperature Tk difference is degree of supercooling △
Ts.c, the enthalpy h2 (2 ') and 1 point of enthalpy h1 of 2 (2 ') point difference are evaporation and heat-exchange amount.Ts.h is overtemperature, overheat temperature
The difference for spending Ts.h and evaporating temperature Te is degree of superheat △ Ts.h.
It will be noted from fig. 1 that 1 point is in vehicle repair major area, its liquid phase refrigerant accounting is more big, the evaporation latent heat having
Refrigerant is more, and exchange capability of heat is more sufficient, otherwise fewer.During in particular by R134a as circulating refrigerant medium, R134a
The evaporation latent heat of refrigerant in itself is smaller compared to traditional refrigerant (R22), if liquid coolant accounting is small after throttling, can lead
Cause exchange capability of heat weaker.
For this problem, it is necessary to by 1 point of side movement of turning left, so that the distance between h2 (2 ') and h1 increase, from
And increase evaporation and heat-exchange amount, it means that need the degree of supercooling △ Ts.c of abundance., can be by changing in order to obtain the degree of supercooling of abundance
Become the arrangement of condenser, increase refrigerant return branch road and by setting the modes such as subcooler to realize in heat pump,
But these modes add the manufacturing cost of heat pump, and can not make real-time regulation for different operating modes.Therefore, this
Application proposes a kind of control method of electric expansion valve, and the electric expansion valve is arranged on the refrigerant circulation circuit of heat pump
In, as shown in Fig. 2 typical heat pump includes compressor 1, oil eliminator 2, condenser 3, device for drying and filtering 4, electronic expansion
Valve 5, evaporator 6, these structures are in turn connected to form the refrigerant circulation circuit of heat pump.Set on the air intake duct of compressor 1
The first temperature sensor 7 and first pressure sensor 8 are equipped with, is respectively used to detect the suction temperature and pressure of inspiration(Pi) of compressor 1,
Second pressure sensor 10 is provided with the blast pipe of compressor 1, for detecting the pressure at expulsion of compressor 1, condenser 3 goes out
Mouth position is provided with second temperature sensor 9, for detecting the refrigerant temperature of the outlet of condenser 3.When the current reality of heat pump
Border suction superheat x within a preset range when, according in heat pump current actual degree of supercooling γ and refrigerant circulation circuit
The aperture of the current Load Regulation electric expansion valve 5 of compressor 1.The absorbing gas belt of compressor 1 is easily caused because suction superheat x is too low
Liquid, compressor 1 is caused damage, and the too high Mass losts that can cause unit interval compressed gas of suction superheat x, therefore,
Need first to maintain actual suction superheat x in certain scope, on this basis, by adjusting electric expansion valve 5
Aperture enables actual degree of supercooling γ to match with the load of compressor 1, so as to improve the exchange capability of heat of heat pump and energy
Effect, and do not change the structure of heat pump in itself, the production cost of heat pump will not be increased.
Further, heat pump also includes controller (not shown), controller and first, second temperature sensor
And first, second pressure sensor be connected, controller can according to each temperature sensor, pressure sensor detect data come
Adjust the aperture of electric expansion valve 5.
In a specific embodiment, actual suction superheat x and actual degree of superheat γ can be obtained in the following way
, actual suction superheat x=suction temperatures-saturation temperature corresponding to pressure of inspiration(Pi), wherein suction temperature are the first temperature
The temperature that sensor 7 detects, saturation temperature corresponding to pressure of inspiration(Pi) can obtain according to the pressure of inspiration(Pi) that first pressure sensor 8 detects
.Actual degree of supercooling γ=| refrigerant temperature-condensation temperature of condensator outlet |, the refrigerant temperature of wherein condensator outlet is
The temperature that second temperature sensor 9 detects, the pressure at expulsion that condensation temperature can detect according to second pressure sensor 10 obtain.
Preferably, specifically wrapped according to the aperture of actual degree of supercooling γ and compressor 1 current Load Regulation electric expansion valve 5
Include：Current degree of supercooling desired value Cs ' of the actual degree of supercooling γ with heat pump under current compressor load is contrasted, and
The aperture of electric expansion valve 5 is adjusted according to comparing result.Wherein, current degree of supercooling desired value C ' can be obtained by equation below：
C '=C*Q,
Wherein, C is degree of supercooling desired value of the heat pump under compressor oepration at full load state；
Q is the percentage that current compressor load accounts for compressor total load.
Preferably, specific regulative mode is, as actual degree of supercooling γ≤current degree of supercooling desired value C ', to illustrate current
Degree of supercooling can not meet heat exchange demand, controller turns the aperture of electric expansion valve 5 down；
As actual degree of supercooling γ>During current degree of supercooling desired value C ', illustrate that current degree of supercooling disclosure satisfy that heat exchange demand,
Controller control keeps the aperture of electric expansion valve 5 constant.
It is further preferred that to avoid, because disturbing factor causes controller maloperation, being further ensured that the stability of a system,
When actual degree of supercooling γ persistently meets γ≤C ' within first scheduled time, controller again adjusts the aperture of electric expansion valve 5
It is small, otherwise maintain the aperture of electric expansion valve 5 constant.First scheduled time can be configured according to real needs, for example, first
Scheduled time T1 scope is 0 ＜ T1≤20s.
Further, when actual suction superheat x meets condition A<x<During B, controller is according to the actual mistake of heat pump
The aperture of cold degree γ regulations electric expansion valve 5, wherein, A is suction superheat lower limit, and B is suction superheat higher limit, can be pre-
Deposit in the controller, in a specific embodiment, suction superheat lower limit A scope is 0 DEG C≤A<5 DEG C, air-breathing mistake
Temperature higher limit B scope is 5 DEG C≤B<8℃；
As actual suction superheat x >=B, controller does not allow the aperture of electric expansion valve 5 to turn down；
As actual suction superheat x≤A, controller turns the aperture of electric expansion valve 5 down.
The absorbing gas belt liquid of compressor 1 can either be avoided by above-mentioned control method, and can enough ensures the efficiency of compressor 1.
It is further preferred that to avoid, because disturbing factor causes controller maloperation, being further ensured that the stability of a system,
When actual suction superheat persistently meets condition x≤A within second scheduled time, controller opening electric expansion valve 5 again
Degree is turned down, otherwise maintains the aperture of electric expansion valve 5 constant.Second scheduled time can be configured according to real needs, for example,
Second scheduled time T2 scope is 30s≤T2≤90s.
A specific embodiment of the application control method is given below, as shown in figure 3, the control method that the application provides
Comprise the following steps：
Step S001, start electric expansion valve 5 and initialized, the aperture of electric expansion valve 5 is arranged on predetermined
Initial value, and carry out step S002 after starting the predetermined time in electric expansion valve 5；
S002, the actual suction superheat x current by the way that heat pump is calculated, and judge actual suction superheat x
Whether condition A is met<x<B, if so, then carrying out step S005, otherwise carry out step S003
Step S003, judge whether actual suction superheat x meets condition x >=B, if so, not allowing electric expansion valve 5 then
Aperture turn down, and return to step S002, otherwise carry out step S004；
Step S004, controller turns the aperture of electric expansion valve 5 down, and return to step S002；
Step S005, by the way that heat pump current actual degree of supercooling γ and current degree of supercooling desired value C ' is calculated,
And judge whether actual degree of supercooling γ meets condition γ≤C ', if so, then carrying out step S006, otherwise return to step S002；
Step S006, the aperture of electric expansion valve 5 is turned down, return to step S002.
Wherein, the stride turned the aperture of electric expansion valve 5 down in step S006 is the first stride EXV1, in step S004
The stride that the aperture of electric expansion valve 5 is turned down is the second stride EXV2, wherein, the first stride EXV1<Second stride EXV2.
First stride EXV1 and the second stride EXV2 can be fixed value, and prestore in the controller, for example, the first stride
EXV1 scope is that 0 ＜ EXV1≤0.5%, the second stride EXV2 scope is 1%≤EXV2≤5%, it is preferable that is further
The accuracy of control is improved, controller determines according to actual degree of supercooling γ and current degree of supercooling desired value C ' ratio or difference
First stride EXV1, both differ bigger, and the first stride EXV1 is bigger, and both differ smaller, then the first stride EXV1 is smaller.Class
As, controller determines the second stride according to actual suction superheat x and suction superheat higher limit B ratio or difference
EXV2, both differ bigger, and the second stride EXV2 is bigger, and both differ smaller, then the second stride EXV2 is smaller.
It is further preferred that the aperture regulation scope of electric expansion valve 5 is arranged on 10% to 100%, by setting electricity
The aperture lower limit of sub- expansion valve 5 come reduce due to system exception and to electric expansion valve 5 carry out maloperation caused by influence,
Further improve the stability of a system.
The control method that the application provides can be widely applied in the large-size air conditioning equipment such as domestic air conditioner and screw machine.
Further, present invention also provides a kind of heat pump, electric expansion valve therein to be carried out using the above method
Control, so as to improve the exchange capability of heat of heat pump and efficiency.
For those skilled in the art it is easily understood that on the premise of not conflicting, above-mentioned each preferred scheme can be free
Ground combination, superposition.
The preferred embodiments of the present invention are the foregoing is only, are not intended to limit the invention, for those skilled in the art
For, the present invention can have various changes and change.All any modifications made within spirit and principles of the present invention, it is equal
Replace, improve etc., it should be included in the scope of the protection.
Claims (11)
1. a kind of control method of electric expansion valve, the electric expansion valve are arranged in the refrigerant circulation circuit of heat pump,
Compressor is additionally provided with the refrigerant circulation circuit, it is characterised in that the control method includes：When the heat pump is worked as
Preceding actual suction superheat x within a preset range when, according to the current actual degree of supercooling γ of the heat pump and the pressure
The aperture of electric expansion valve described in the current Load Regulation of contracting machine.
2. control method according to claim 1, it is characterised in that the control method further comprises：By the reality
Current degree of supercooling desired value Cs ' of the border degree of supercooling γ with the heat pump under current compressor load is contrasted, and according to
Comparing result adjusts the aperture of the electric expansion valve.
3. control method according to claim 2, it is characterised in that current degree of supercooling desired value the C '=C*Q,
Wherein, C is degree of supercooling desired value of the heat pump under compressor oepration at full load state；
Q is the percentage that current compressor load accounts for compressor total load.
4. control method according to claim 2, it is characterised in that the control method further comprises：
As the actual degree of supercooling γ≤current degree of supercooling desired value C ', the aperture of the electric expansion valve is turned down；
And/or
As the actual degree of supercooling γ>During the current degree of supercooling desired value C ', keep the aperture of the electric expansion valve constant.
5. control method according to claim 4, it is characterised in that the control method further comprises：
When the actual degree of supercooling γ persistently meets γ≤C ' within first scheduled time, by the aperture of the electric expansion valve
Turn down, otherwise keep the aperture of the electric expansion valve constant.
6. according to the control method described in one of claim 1-5, it is characterised in that the control method also includes：
When the actual suction superheat x meets condition A<x<During B, institute is adjusted according to the actual degree of supercooling γ of the heat pump
The aperture of electric expansion valve is stated, wherein, A is suction superheat lower limit, and B is suction superheat higher limit；
And/or
As the actual suction superheat x >=B, the aperture of the electric expansion valve is not allowed to turn down；
And/or
As the actual suction superheat x≤A, the aperture of the electric expansion valve is turned down.
7. control method according to claim 6, it is characterised in that when the actual suction superheat is in the second pre- timing
In when persistently meeting condition x≤A, the aperture of the electric expansion valve is turned down, otherwise keeps opening for the electric expansion valve
Spend constant.
8. control method according to claim 6, it is characterised in that when the actual degree of supercooling γ≤heat pump
During current degree of supercooling desired value C ' under current compressor load, the aperture of the electric expansion valve is turned down, and turn down
Stride is the first stride EXV1, as the actual suction superheat x≤A, step that the aperture of the electric expansion valve is turned down
Width is the second stride EXV2, wherein, the first stride EXV1<Second stride EXV2.
9. control method according to claim 8, it is characterised in that suction superheat lower limit A scope is 0 DEG C≤A<
5℃；And/or
Suction superheat higher limit B scope is 5 DEG C≤B<8℃；And/or
First stride EXV1 scope is 0 ＜ EXV1≤0.5%；And/or
Second stride EXV2 scope is 1%≤EXV2≤5%.
10. according to the control method described in one of claim 1-5, it is characterised in that the aperture regulation of the electric expansion valve
Scope is 10% to 100%.
11. a kind of heat pump, including electric expansion valve, it is characterised in that using the control as described in one of claim 1-10
Method processed is controlled to the electric expansion valve.
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| CN201710505653.9A CN107421176B (en) | 2017-06-28 | 2017-06-28 | The control method and heat pump system of electric expansion valve |
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| CN201710505653.9A CN107421176B (en) | 2017-06-28 | 2017-06-28 | The control method and heat pump system of electric expansion valve |
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| CN108800634A (en) * | 2018-06-29 | 2018-11-13 | 重庆美的通用制冷设备有限公司 | Two stage centrifugal handpiece Water Chilling Units and its control method of level-one throttling, device |
| CN109099612A (en) * | 2018-08-17 | 2018-12-28 | 珠海格力电器股份有限公司 | Heat-pump apparatus and its control method for electronic expansion valve, device and storage medium |
| CN109253524A (en) * | 2018-08-23 | 2019-01-22 | 珠海格力电器股份有限公司 | A kind of control method of heat pump system, heat pump system and air-conditioning |
| CN110553441A (en) * | 2019-09-19 | 2019-12-10 | 重庆美的通用制冷设备有限公司 | Operation control method and system, readable storage medium, compression and air conditioning system |
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