CN107421176B - Control method of electronic expansion valve and heat pump system - Google Patents
Control method of electronic expansion valve and heat pump system Download PDFInfo
- Publication number
- CN107421176B CN107421176B CN201710505653.9A CN201710505653A CN107421176B CN 107421176 B CN107421176 B CN 107421176B CN 201710505653 A CN201710505653 A CN 201710505653A CN 107421176 B CN107421176 B CN 107421176B
- Authority
- CN
- China
- Prior art keywords
- expansion valve
- electric expansion
- control method
- heat pump
- pump system
- 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.)
- Active
Links
- 238000000034 method Methods 0.000 title claims abstract description 42
- 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
- 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
- 230000008859 change Effects 0.000 description 2
- 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
- 238000001514 detection method Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 230000006872 improvement Effects 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
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The invention provides a control method of an electronic expansion valve and a heat pump system. The control method of the electronic expansion valve comprises the following steps: and when the current actual suction superheat degree x of the heat pump system is within a preset range, adjusting the opening degree of the electronic expansion valve according to the current actual supercooling degree gamma of the heat pump system and the current load of the compressor. According to the control method of the electronic expansion valve, when the actual suction superheat degree is within the preset range, the opening degree of the electronic expansion valve is adjusted according to the actual supercooling degree and the current load of the compressor, so that the heat pump system has the supercooling degree matched with the actual load of the compressor, the heat exchange capacity and the energy efficiency of the heat pump system are improved while liquid carrying in suction is avoided, the structure of the heat pump system is not changed, and the production cost of the heat pump system is not increased.
Description
Technical field
The present invention relates to heat pump system automation fields, and in particular to a kind of control method and heat pump of electric expansion valve
System.
Background technique
Existing heat pump system is usually the aperture that electric expansion valve is adjusted according to suction superheat, to meet different works
System reliability under condition, but existing heat pump system remains the problem of exchange capability of heat deficiency.
Summary of the invention
In view of this, one of the objects of the present invention is to provide a kind of heat pump system exchange capability of heat and efficiencies of can be improved
The control method and heat pump system of electric expansion valve.
In order to achieve the above objectives, on the one hand, the invention adopts the following technical scheme:
The refrigerant circulation circuit of heat pump system is arranged in a kind of control method of electric expansion valve, the electric expansion valve
In, compressor is additionally provided in the refrigerant circulation circuit, the control method includes: the reality current when the heat pump system
Suction superheat x within a preset range when, it is current according to the current practical degree of supercooling γ of the heat pump system and the compressor
Load Regulation described in electric expansion valve aperture；
When current degree of supercooling target value of the practical degree of supercooling γ≤heat pump system under current compressor load
When C ', the stride that the aperture of the electric expansion valve is turned down, and is turned down is the first stride EXV1, when the practical suction superheat
When spending 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 < the
Two stride EXV2, A are suction superheat lower limit value.
Preferably, the control method further comprises: by the practical degree of supercooling γ with the heat pump system current
Current degree of supercooling target value C ' under compressor load is compared, and adjusts opening for the electric expansion valve according to comparing result
Degree.
Preferably, current degree of supercooling target value the C '=C*Q,
Wherein, C is degree of supercooling target value of the heat pump system 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 practical degree of supercooling γ≤current degree of supercooling target value C ', by the aperture tune of the electric expansion valve
It is small；
And/or
As the practical degree of supercooling γ > current degree of supercooling target value C ', the aperture of the electric expansion valve is kept
It is constant.
Preferably, the control method further comprises:
When the practical degree of supercooling γ persistently meets γ≤C ' within the first predetermined time, by the electric expansion valve
Aperture is turned down, otherwise keeps the aperture of the electric expansion valve constant.
Preferably, the control method further include:
When the practical suction superheat x meets condition A < x < B, according to the practical degree of supercooling γ tune of the heat pump system
Save the aperture of the electric expansion valve, wherein B is suction superheat upper limit value；
And/or
As the practical suction superheat x >=B, the aperture of the electric expansion valve is not allowed to turn down；
And/or
As the practical suction superheat x≤A, the aperture of the electric expansion valve is turned down.
It preferably, will be described when the practical suction superheat persistently meets condition x≤A within second scheduled time
The aperture of electric expansion valve is turned down, otherwise keeps the aperture of the electric expansion valve constant.
Preferably, the range of suction superheat lower limit value A is 0 DEG C≤A < 5 DEG C；And/or
The range of first stride EXV1 is 0 < EXV1≤0.5%；And/or
The range of second stride EXV2 is 1%≤EXV2≤5%.
Preferably, the range of suction superheat lower limit value A is 0 DEG C≤A < 5 DEG C；And/or
The range of suction superheat upper limit value B is 5 DEG C≤B < 8 DEG C.
Preferably, the aperture regulation range of the electric expansion valve is 10% to 100%.
On the other hand, the invention adopts the following technical scheme:
A kind of heat pump system, including electric expansion valve, using control method as described above to the electric expansion valve into
Row control.
In the control method of electric expansion valve provided by the invention, when practical 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 system has and compressor
The degree of supercooling that actual load matches, to improve the exchange capability of heat and energy of heat pump system while avoiding absorbing gas belt liquid
Effect, and do not change the structure of heat pump system itself, it not will increase the production cost of heat pump system.
Detailed description of the invention
By referring to the drawings to the description of the embodiment of the present invention, the above and other purposes of the present invention, feature and
Advantage will be apparent from, in the accompanying drawings:
Fig. 1 shows heat pump system pressure-enthalpy chart；
Fig. 2 shows the structural schematic diagrams for the heat pump system that the specific embodiment of the invention provides；
Fig. 3 shows the control method flow chart of the electric expansion valve of specific embodiment of the invention offer.
In figure, 1, compressor；2, oil eliminator；3, condenser；4, device for drying and filtering；5, electric expansion valve；6, evaporator；
7, the first temperature sensor；8, first pressure sensor；9, second temperature sensor；10, second pressure sensor.
Specific embodiment
Below based on embodiment, present invention is described, it should be understood by one skilled in the art that provided herein
Attached drawing is provided to the purpose of explanation, and attached drawing is not necessarily drawn to scale.
Unless the context clearly requires otherwise, "include", "comprise" otherwise throughout the specification and claims etc. are similar
Word should be construed as the meaning for including rather than exclusive or exhaustive meaning；That is, be " including but not limited to " contains
Justice.
For the problem of the deficiency of exchange capability of heat existing for existing heat pump system, the application discovery, pressure-enthalpy chart shown in Fig. 1
In, from above-mentioned pressure-enthalpy chart, 1 → 2 (2 ') be evaporation process, 2 (2 ') → 3 be compression process, 3 → 4 (4 ') be condensation process, 4
(4 ') → 1 is throttling process.Ts.c is again cold temperature, then the difference of cold temperature Ts.c and condensation temperature Tk is degree of supercooling △
The difference of Ts.c, the enthalpy h2 (2 ') and 1 point of enthalpy h1 of 2 (2 ') point 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, the liquid phase refrigerant accounting the big, the evaporation latent heat having
Refrigerant is more, and exchange capability of heat is more sufficient, otherwise fewer.When in particular by R134a as circulating refrigerant medium, R134a
The evaporation latent heat of refrigerant 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, need 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 sufficient degree of supercooling △ Ts.c.It, can be by changing in order to obtain sufficient degree of supercooling
Turn cold condenser arrangement, increase refrigerant return branch in heat pump system and realized by the setting modes such as subcooler,
But these modes increase the manufacturing cost of heat pump system, and can not make real-time adjusting for different operating conditions.For this purpose, this
Application proposes a kind of control method of electric expansion valve, which is arranged in the refrigerant circulation circuit of heat pump system
In, as shown in Fig. 2, typical heat pump system 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 system.It is set on the air intake duct of compressor 1
It is equipped with the first temperature sensor 7 and first pressure sensor 8, is respectively used to the suction temperature and pressure of inspiration(Pi) of detection compressor 1,
Second pressure sensor 10 is provided on the exhaust 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 system
Border suction superheat x within a preset range when, according in heat pump system current practical degree of supercooling γ and refrigerant circulation circuit
The aperture of the current Load Regulation electric expansion valve 5 of compressor 1.1 absorbing gas belt of compressor is easily caused since suction superheat x is too low
Liquid damages compressor 1, and the excessively high Mass lost that will lead to unit time compressed gas of suction superheat x, therefore,
It needs first to maintain practical suction superheat x in a certain range, on this basis, by adjusting electric expansion valve 5
Aperture enables practical degree of supercooling γ to match with 1 load of compressor, to improve the exchange capability of heat and energy of heat pump system
Effect, and do not change the structure of heat pump system itself, it not will increase the production cost of heat pump system.
Further, heat pump system further includes controller (not shown), controller and the 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, practical suction superheat x and practical degree of superheat γ can be obtained in the following way
, the practical suction superheat x=suction temperature-corresponding saturation temperature of pressure of inspiration(Pi), wherein suction temperature is the first temperature
The temperature that sensor 7 detects, the corresponding saturation temperature of pressure of inspiration(Pi) can be obtained according to the pressure of inspiration(Pi) that first pressure sensor 8 detects
?.Practical degree of supercooling γ=| refrigerant temperature-condensation temperature of condensator outlet |, wherein the refrigerant temperature of condensator outlet is
The temperature that second temperature sensor 9 detects, the pressure at expulsion that condensation temperature can be detected according to second pressure sensor 10 obtain.
Preferably, it is specifically wrapped according to the aperture of practical degree of supercooling γ and compressor 1 current Load Regulation electric expansion valve 5
It includes: the current degree of supercooling target value C ' of practical degree of supercooling γ and heat pump system under current compressor load is compared, and
The aperture of electric expansion valve 5 is adjusted according to comparing result.Wherein, current degree of supercooling target value C ' can be obtained by following formula:
C '=C*Q,
Wherein, C is degree of supercooling target value of the heat pump system 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 practical degree of supercooling γ≤current degree of supercooling target value C ', to illustrate current
Degree of supercooling be not able to satisfy heat exchange demand, controller turns the aperture of electric expansion valve 5 down；
As practical degree of supercooling γ > current degree of supercooling target value C ', illustrate that current degree of supercooling can satisfy heat exchange demand,
Controller control keeps the aperture of electric expansion valve 5 constant.
It is further preferred that system stability is further ensured that avoid causing controller maloperation due to disturbing factor,
When practical degree of supercooling γ persistently meets γ≤C ' within the first predetermined time, controller is again by the aperture tune of electric expansion valve 5
It is small, otherwise maintain the aperture of electric expansion valve 5 constant.First predetermined time can be configured according to specific requirements, for example, first
The range of predetermined time T1 is 0 < T1≤20s.
Further, when practical suction superheat x meets condition A < x < B, controller is according to the practical mistake of heat pump system
Cold degree γ adjusts the aperture of electric expansion valve 5, wherein A is suction superheat lower limit value, and B is suction superheat upper limit value, can be pre-
It deposits in the controller, in a specific embodiment, the range of suction superheat lower limit value A is 0 DEG C≤A < 5 DEG C, air-breathing mistake
The range of temperature upper limit value B is 5 DEG C≤B < 8 DEG C；
As practical suction superheat x >=B, controller does not allow the aperture of electric expansion valve 5 to turn down；
As practical suction superheat x≤A, controller turns the aperture of electric expansion valve 5 down.
1 absorbing gas belt liquid of compressor can either be avoided by above-mentioned control method, and can guarantee the efficiency of compressor 1.
It is further preferred that system stability is further ensured that avoid causing controller maloperation due to disturbing factor,
When practical 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 predetermined time can be configured according to specific requirements, for example,
The range of second predetermined time T2 is 30s≤T2≤90s.
A specific embodiment of the application control method is given below, as shown in figure 3, control method provided by the present application
Include the following steps:
Step S001, start electric expansion valve 5 and initialized, the aperture of electric expansion valve 5 is arranged scheduled
Initial value, and step S002 is carried out after electric expansion valve 5 starts the scheduled time；
S002, the current practical suction superheat x of heat pump system is obtained by calculation, and judges practical suction superheat x
Whether meet condition A < x < B, if so, carrying out step S005, otherwise carries out step S003 step S003, the practical air-breathing mistake of judgement
Whether temperature x meets condition x >=B, if so, not allowing the aperture of electric expansion valve 5 to turn down, and return step S002, otherwise
Carry out step S004；
Step S004, controller turns the aperture of electric expansion valve 5 down, and return step S002；
Step S005, heat pump system current practical degree of supercooling γ and current degree of supercooling target value C ' is obtained by calculation,
And judge whether practical degree of supercooling γ meets condition γ≤C ', if so, carrying out step S006, otherwise return step S002；
Step S006, the aperture of electric expansion valve 5 is turned down, return 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 of stride EXV1 < second EXV2.
First stride EXV1 and the second stride EXV2 can be fixed value, and prestore in the controller, for example, the first stride
The range that the range of EXV1 is 0 < EXV1≤0.5%, the second stride EXV2 is 1%≤EXV2≤5%, it is preferable that is further
The accuracy of control is improved, controller is determined according to the ratio or difference of practical degree of supercooling γ and current degree of supercooling target value C '
First stride EXV1, the two difference is bigger, and the first stride EXV1 is bigger, and the two difference is smaller, then the first stride EXV1 is smaller.Class
As, controller determines the second stride according to the ratio or difference of practical suction superheat x and suction superheat upper limit value B
EXV2, the two difference is bigger, and the second stride EXV2 is bigger, and the two difference is smaller, then the second stride EXV2 is smaller.
It is further preferred that the aperture regulation range setting of electric expansion valve 5 is passed through setting electricity 10% to 100%
The aperture lower limit value of sub- expansion valve 5 carries out influence caused by maloperation to electric expansion valve 5 reducing due to system exception,
Further increase system stability.
Control method provided by the present application can be widely applied in the large-size air conditionings equipment such as domestic air conditioner and screw machine.
Further, present invention also provides a kind of heat pump system, electric expansion valve therein is carried out using the above method
Control, to improve the exchange capability of heat and efficiency of heat pump system.
Those skilled in the art will readily recognize that above-mentioned each preferred embodiment can be free under the premise of not conflicting
Ground combination, superposition.
The above description is only a preferred embodiment of the present invention, is not intended to restrict the invention, for those skilled in the art
For, the invention can have various changes and changes.All any modifications made within the spirit and principles of the present invention are equal
Replacement, improvement etc., should all be included in the protection scope of the present invention.
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 system,
Compressor is additionally provided in the refrigerant circulation circuit, which is characterized in that the control method includes: when the heat pump system is worked as
Preceding practical suction superheat x within a preset range when, according to the current practical degree of supercooling γ of the heat pump system and the pressure
The aperture of electric expansion valve described in the current Load Regulation of contracting machine；
As current degree of supercooling target value C ' of the practical degree of supercooling γ≤heat pump system under current compressor load,
The stride that the aperture of the electric expansion valve is turned down, and is turned down be the first stride EXV1, when the practical suction superheat x≤
When A, the stride that the aperture of the electric expansion valve is turned down is the second stride EXV2, wherein the first stride of stride EXV1 < second
EXV2, A are suction superheat lower limit value.
2. control method according to claim 1, which is characterized in that the control method further comprises: by the reality
Border degree of supercooling γ is compared with current degree of supercooling target value C ' of the heat pump system under current compressor load, and according to
Comparing result adjusts the aperture of the electric expansion valve.
3. control method according to claim 2, which is characterized in that current degree of supercooling target value the C '=C*Q,
Wherein, C is degree of supercooling target value of the heat pump system 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, which is characterized in that the control method further comprises:
As the practical degree of supercooling γ≤current degree of supercooling target value C ', the aperture of the electric expansion valve is turned down；
And/or
As the practical degree of supercooling γ > current degree of supercooling target value C ', keep the aperture of the electric expansion valve constant.
5. control method according to claim 4, which is characterized in that the control method further comprises:
When the practical degree of supercooling γ persistently meets γ≤C ' within the first predetermined time, by the aperture of the electric expansion valve
It turns down, otherwise keeps the aperture of the electric expansion valve constant.
6. control method described in one of -5 according to claim 1, which is characterized in that the control method further include:
When the practical suction superheat x meets condition A < x < B, institute is adjusted according to the practical degree of supercooling γ of the heat pump system
State the aperture of electric expansion valve, wherein B is suction superheat upper limit value；
And/or
As the practical suction superheat x >=B, the aperture of the electric expansion valve is not allowed to turn down；
And/or
As the practical suction superheat x≤A, the aperture of the electric expansion valve is turned down.
7. control method according to claim 6, which is characterized in that when the practical 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, opening for the electric expansion valve is otherwise kept
It spends constant.
8. control method according to claim 1, which is characterized in that the range of suction superheat lower limit value A be 0 DEG C≤A <
5℃；And/or
The range of first stride EXV1 is 0 < EXV1≤0.5%；And/or
The range of second stride EXV2 is 1%≤EXV2≤5%.
9. control method according to claim 6, which is characterized in that the range of suction superheat lower limit value A be 0 DEG C≤A <
5℃；And/or
The range of suction superheat upper limit value B is 5 DEG C≤B < 8 DEG C.
10. control method described in one of -5 according to claim 1, which is characterized in that the aperture regulation of the electric expansion valve
Range is 10% to 100%.
11. a kind of heat pump system, including electric expansion valve, which is characterized in that using the control as described in one of claim 1-10
Method processed controls the electric expansion valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710505653.9A CN107421176B (en) | 2017-06-28 | 2017-06-28 | Control method of electronic expansion valve and heat pump system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710505653.9A CN107421176B (en) | 2017-06-28 | 2017-06-28 | Control method of electronic expansion valve and heat pump system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107421176A CN107421176A (en) | 2017-12-01 |
| CN107421176B true CN107421176B (en) | 2019-07-23 |
Family
ID=60427414
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710505653.9A Active CN107421176B (en) | 2017-06-28 | 2017-06-28 | Control method of electronic expansion valve and heat pump system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN107421176B (en) |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108800634B (en) * | 2018-06-29 | 2020-11-24 | 重庆美的通用制冷设备有限公司 | Two-stage centrifugal water chilling unit and one-stage throttling control method and device thereof |
| CN109099612A (en) * | 2018-08-17 | 2018-12-28 | 珠海格力电器股份有限公司 | Heat pump equipment, electronic expansion valve control method and device thereof and storage medium |
| CN109253524B (en) * | 2018-08-23 | 2020-11-10 | 珠海格力电器股份有限公司 | Control method of heat pump system, heat pump system and air conditioner |
| KR102223949B1 (en) * | 2018-11-15 | 2021-03-05 | 이동원 | Heat pump with improved efficiency |
| CN111854204B (en) * | 2019-04-28 | 2021-08-24 | 青岛海尔智能技术研发有限公司 | Refrigerator equipment, refrigerating system and control method of refrigerating system |
| CN111854200B (en) * | 2019-04-28 | 2021-09-24 | 青岛海尔智能技术研发有限公司 | Refrigerator equipment, refrigerating system and control method of refrigerating system |
| CN110553441B (en) * | 2019-09-19 | 2021-08-20 | 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 |
| CN113970439B (en) * | 2020-07-24 | 2023-12-22 | 广东美的暖通设备有限公司 | Enthalpy-increasing jet system and auxiliary road valve body detection method and device thereof |
| CN114061018B (en) * | 2020-07-30 | 2024-01-02 | 广东美的暖通设备有限公司 | Air conditioning system, detection method and detection device of electronic expansion valve of air conditioning system and controller |
| CN112344511A (en) * | 2020-10-23 | 2021-02-09 | 烽火通信科技股份有限公司 | Control method, device and system suitable for machine room air conditioner refrigerant flow |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH1089780A (en) * | 1996-09-13 | 1998-04-10 | Mitsubishi Electric Corp | Refrigerating system |
| JP2001248920A (en) * | 2000-03-06 | 2001-09-14 | Mitsubishi Electric Corp | Controller for refrigeration circuit |
| CN1609529A (en) * | 2003-10-16 | 2005-04-27 | Lg电子株式会社 | System and method for controlling temperature of refrigerant in air conditioner |
| CN101995125A (en) * | 2009-08-10 | 2011-03-30 | 海尔集团公司 | Methods for controlling and amending multi-split air conditioner expansion valve |
| CN102032725A (en) * | 2010-12-08 | 2011-04-27 | 海尔集团公司 | Supercooling device, air conditioner with device and method for controlling refrigerant flow of air conditioner |
| CN103673416A (en) * | 2012-08-31 | 2014-03-26 | 杭州三花研究院有限公司 | Control method for refrigerant flow quantity in automobile air conditioning system and automobile air conditioning system |
| CN105864984A (en) * | 2016-04-27 | 2016-08-17 | 广东美的暖通设备有限公司 | Adjusting method and device for indoor unit electronic expansion valve |
| CN106052216A (en) * | 2016-06-29 | 2016-10-26 | 宁波奥克斯电气股份有限公司 | Method for controlling electronic expansion valves during multi-connected air conditioning unit heating |
| CN106152633A (en) * | 2016-06-28 | 2016-11-23 | 广东美的暖通设备有限公司 | multiple on-line system and control method thereof |
-
2017
- 2017-06-28 CN CN201710505653.9A patent/CN107421176B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH1089780A (en) * | 1996-09-13 | 1998-04-10 | Mitsubishi Electric Corp | Refrigerating system |
| JP2001248920A (en) * | 2000-03-06 | 2001-09-14 | Mitsubishi Electric Corp | Controller for refrigeration circuit |
| CN1609529A (en) * | 2003-10-16 | 2005-04-27 | Lg电子株式会社 | System and method for controlling temperature of refrigerant in air conditioner |
| CN101995125A (en) * | 2009-08-10 | 2011-03-30 | 海尔集团公司 | Methods for controlling and amending multi-split air conditioner expansion valve |
| CN102032725A (en) * | 2010-12-08 | 2011-04-27 | 海尔集团公司 | Supercooling device, air conditioner with device and method for controlling refrigerant flow of air conditioner |
| CN103673416A (en) * | 2012-08-31 | 2014-03-26 | 杭州三花研究院有限公司 | Control method for refrigerant flow quantity in automobile air conditioning system and automobile air conditioning system |
| CN105864984A (en) * | 2016-04-27 | 2016-08-17 | 广东美的暖通设备有限公司 | Adjusting method and device for indoor unit electronic expansion valve |
| CN106152633A (en) * | 2016-06-28 | 2016-11-23 | 广东美的暖通设备有限公司 | multiple on-line system and control method thereof |
| CN106052216A (en) * | 2016-06-29 | 2016-10-26 | 宁波奥克斯电气股份有限公司 | Method for controlling electronic expansion valves during multi-connected air conditioning unit heating |
Also Published As
| Publication number | Publication date |
|---|---|
| CN107421176A (en) | 2017-12-01 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN107421176B (en) | Control method of electronic expansion valve and heat pump system | |
| USRE43998E1 (en) | Refrigeration/air conditioning equipment | |
| CN100557348C (en) | The equipment and the method for the degree of superheat in the control heat pump | |
| CN109373497B (en) | Refrigerant quantity adjusting method, device and system of temperature adjusting equipment and air conditioner | |
| CN102368009B (en) | Control method of electronic expansion valve of indoor machine during refrigerating of convertible frequency air conditioner | |
| US20010000050A1 (en) | Method for determining a charging amount of refrigerant for an air conditioner, a method for controlling refrigerant for an air conditioner and an air conditioner | |
| CN107990609B (en) | Control method of electronic expansion valve and refrigerant circulating system | |
| EP2107322A2 (en) | Heat pump type hot water supply outdoor apparatus | |
| JP5046895B2 (en) | Air conditioner and operation control method thereof | |
| CN105004115B (en) | Control method of electronic expansion valve | |
| CN101504177A (en) | Air conditioning apparatus and method for determining the amount of refrigerant of air-conditioning apparatus | |
| CN103673416A (en) | Control method for refrigerant flow quantity in automobile air conditioning system and automobile air conditioning system | |
| CN106642787A (en) | Refrigerating or heating pump system with adjustable refrigerant circulation quantity | |
| US10876777B2 (en) | Air conditioning device using vapor injection cycle and method for controlling the device | |
| CN111473496B (en) | Air conditioning system, control method and device thereof and storage medium | |
| CN102725596B (en) | Heat pump system | |
| CN109579344A (en) | A kind of air-conditioning system and its control method that can prevent compressor liquid hammer | |
| CN110671782A (en) | Control method and control device of air conditioner and air conditioner | |
| JP2004278825A (en) | Air conditioner | |
| CN114322269A (en) | Refrigerant balance control method and device, multi-split air conditioner and computer readable storage medium | |
| KR102165354B1 (en) | An air conditioning system and a method for controlling the same | |
| US10823474B2 (en) | Perturbation of expansion valve in vapor compression system | |
| US20220163241A1 (en) | Hybrid multi-air conditioning system | |
| CN205448298U (en) | Heat pump water heater electronic expansion valve control system | |
| JP2006242506A (en) | Thermal storage type air conditioner |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |