CN106500391A - A kind of recuperated cycle system and its control method and air-conditioning - Google Patents
A kind of recuperated cycle system and its control method and air-conditioning Download PDFInfo
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- CN106500391A CN106500391A CN201610909006.XA CN201610909006A CN106500391A CN 106500391 A CN106500391 A CN 106500391A CN 201610909006 A CN201610909006 A CN 201610909006A CN 106500391 A CN106500391 A CN 106500391A
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- 238000000034 method Methods 0.000 title claims abstract description 40
- 238000004378 air conditioning Methods 0.000 title claims abstract description 19
- 239000007788 liquid Substances 0.000 claims abstract description 47
- 238000010438 heat treatment Methods 0.000 claims abstract description 24
- 239000002826 coolant Substances 0.000 claims description 86
- 238000005259 measurement Methods 0.000 claims description 37
- 230000001502 supplementing effect Effects 0.000 claims description 25
- 230000005611 electricity Effects 0.000 claims description 15
- 239000003507 refrigerant Substances 0.000 claims description 13
- 230000006835 compression Effects 0.000 claims description 12
- 238000007906 compression Methods 0.000 claims description 12
- 238000005057 refrigeration Methods 0.000 claims description 10
- 238000012546 transfer Methods 0.000 claims description 9
- 230000017531 blood circulation Effects 0.000 claims description 3
- 238000004519 manufacturing process Methods 0.000 abstract description 3
- 239000003921 oil Substances 0.000 description 33
- 230000004087 circulation Effects 0.000 description 8
- 238000010586 diagram Methods 0.000 description 6
- 239000010687 lubricating oil Substances 0.000 description 6
- 230000008901 benefit Effects 0.000 description 4
- 238000005516 engineering process Methods 0.000 description 3
- 125000004122 cyclic group Chemical group 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 230000004069 differentiation Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000002360 preparation method Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 230000026676 system 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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- 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
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and compressor
-
- 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
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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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/022—Compressor control arrangements
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
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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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0417—Refrigeration circuit bypassing means for the subcooler
-
- 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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/07—Details of compressors or related parts
- F25B2400/075—Details of compressors or related parts with parallel compressors
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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
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
-
- 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
-
- 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
- F25B2600/2501—Bypass valves
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- 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)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Air Conditioning Control Device (AREA)
Abstract
Embodiments of the invention provide a kind of recuperated cycle system and its control method and air-conditioning, are related to air-conditioning technical field, for solving the problems, such as that multi-connected machine heat pump heating capacity is not enough in prior art.The recuperated cycle system includes：First compressor, the second compressor, four-way change-over valve, gas-liquid separator, subcooler, bypass electric expansion valve, outdoor heat exchange loop, indoor heat-exchanging loop, the first electromagnetic valve, the second electromagnetic valve and the 3rd electromagnetic valve.Embodiments of the invention are used for the manufacture of air-conditioning.
Description
Technical field
The present invention relates to air-conditioning technical field, more particularly to a kind of recuperated cycle system and its control method and air-conditioning.
Background technology
Multi-connected machine heat pump is as control is flexible, accurate, the unit suitability is good, occupancy construction area is little, installation and maintenance
The advantages of facilitating is favored by more and more consumers.
Identical with traditional air-conditioning system, the principle that heats of multi-connected machine heat pump is：Compressor first is by High Temperature High Pressure
Gas refrigerant is delivered to indoor heat converter and carries out condensing the liquid refrigerant for becoming High Temperature High Pressure, and indoor set is by High Temperature High Pressure
After gas refrigerant condensation, institute's liberated heat is sent；Then the liquid refrigerant of High Temperature High Pressure flows into room through throttle part again
Outer heat-exchanger is evaporated the gas refrigerant for becoming, and last gas refrigerant returns to compressor from outdoor heat converter, complete
Circulation is heated into one.When multi-connected machine heat pump is used for the heating of cold district, relatively low ambient temperature can limit multi-joint
The exchange capability of heat of machine heat pump outdoor heat exchanger, the heat energy of multi-connected machine heat pump are mainly derived from the power consumption of compressor, because
The problems such as this can cause the compression ratio of compressor to increase, delivery temperature rises, volumetric efficiency declines.In order to solve the above problems,
One stage of compression is carried out to refrigerant suction pressure to middle cavity pressure first by Gas-supplying enthalpy-increasing compressor in prior art, then
Two-stage compression is carried out again after the cold-producing medium after one stage of compression is mixed with intermediate cavity QI invigorating cold-producing medium.Gas-supplying enthalpy-increasing compressor passes through
The mode of two-stage compression reduces the compression ratio of compressor, delivery temperature and improves the volumetric efficiency of compressor.However, by
In prior art cannot precise control there is the multi-connected machine heat pump increasing enthalpy air compensation of multiple compressors, therefore current many
Online heat pump is single compressor Gas-supplying enthalpy-increasing system, is limited by number of compressors, is running compared with low ambient temperature
When, multi-connected machine heat pump yet suffers from the not enough problem of heating capacity.
Content of the invention
Embodiments of the invention provide a kind of recuperated cycle system and its control method and air-conditioning, for solving prior art
The not enough problem of middle multi-connected machine heat pump heating capacity.
For reaching above-mentioned purpose, embodiments of the invention are adopted the following technical scheme that：
A kind of first aspect, there is provided recuperated cycle system, including：First compressor, the second compressor, four-way change-over valve,
Gas-liquid separator, subcooler, bypass electric expansion valve, outdoor heat exchange loop and indoor heat-exchanging loop；
The air vent of the air vent of first compressor and second compressor with the four-way change-over valve
Single port is connected；The air entry of the air entry of first compressor and second compressor with the gas-liquid separator
Coolant outfan is connected, the gas supplementing opening of the gas supplementing opening of first compressor and second compressor with the subcooler
First end is connected；
The second port of the four-way change-over valve is connected with the first end of the indoor heat-exchanging loop, the four-way change-over valve
The 3rd port connect with the coolant input of the gas-liquid separator, the 4th port and the outdoor of the four-way change-over valve
The first end connection of heat-exchanging loop；Second end of the subcooler is connected with the coolant outfan of the bypass electric expansion valve,
3rd end of the subcooler is input into the coolant of second end in the outdoor heat exchange loop and the bypass electric expansion valve
End connection, the 4th end of the subcooler is connected with the second end of the indoor heat-exchanging loop；
Wherein, the first electromagnetism is provided between the coolant input of the first end of the subcooler and the gas-liquid separator
Valve；The second electromagnetic valve is provided between the gas supplementing opening of the first end of the subcooler and first compressor；The subcooler
First end and the gas supplementing opening of second compressor between be provided with the 3rd electromagnetic valve.
A kind of second aspect, there is provided control method of recuperated cycle system, for controlling recuperated cycle described in first aspect
System, methods described include：
Determine mode of operation；
When the mode of operation is refrigeration mode, the first port of four-way change-over valve is connected with the 4th port, the second end
Mouthful connect with the 3rd port, the first electromagnetic valve opening, the second electromagnetic valve and the 3rd closed electromagnetic valve；
When the mode of operation is heating mode, obtains ambient temperature and judge the ambient temperature whether more than first
Preset temperature；
When ambient temperature is more than the first preset temperature, the first port of four-way change-over valve is connected with second port, the 3rd
Port is connected with the 4th port, and the first electromagnetic valve is opened, the second electromagnetic valve and the 3rd closed electromagnetic valve；
When ambient temperature is less than or equal to the first preset temperature, the first port of four-way change-over valve and second port connect
Logical, the 3rd port is connected with the 4th port, the first closed electromagnetic valve, and the second electromagnetic valve is opened when the first compressor operating,
When the second compressor operating, the 3rd electromagnetic valve is opened, when the first compressor and the second compressor run, the second electromagnetic valve
Open with the 3rd electromagnetic valve.
A kind of third aspect, there is provided air-conditioning, including the recuperated cycle system described in first aspect.
Recuperated cycle system provided in an embodiment of the present invention includes：First compressor, the second compressor, four-way change-over valve,
Gas-liquid separator, subcooler, bypass electric expansion valve, outdoor heat exchange loop and indoor heat-exchanging loop, wherein, the first compressor
Air vent and the air vent of the second compressor connect with the first port of four-way change-over valve；The air entry of the first compressor and
The air entry of the second compressor is connected with the coolant outfan of gas-liquid separator, and the gas supplementing opening of the first compressor and second compresses
The gas supplementing opening of machine is connected with the first end of subcooler；The second port of four-way change-over valve is connected with the first end of indoor heat-exchanging loop
Logical, the 3rd port of four-way change-over valve is connected with the coolant input of gas-liquid separator, the 4th port of four-way change-over valve and room
The first end connection of outer heat-exchanging loop；Second end of subcooler is connected with the coolant outfan of bypass electric expansion valve, subcooler
Second end in the 3rd end and outdoor heat exchange loop and the coolant input of bypass electric expansion valve connect, the 4th of subcooler the
Hold and connect with the second end of indoor heat-exchanging loop；Wherein, between the coolant input of the first end of subcooler and gas-liquid separator
It is provided with the first electromagnetic valve；The second electromagnetism is provided between the gas supplementing opening of the first end of the subcooler of subcooler and the first compressor
Valve；The 3rd electromagnetic valve is provided between the gas supplementing opening of the first end of the subcooler of subcooler and the second compressor, because of the invention
Can be controlled by the aperture of the first electromagnetic valve, the second electromagnetic valve, the 3rd electromagnetic valve and bypass electric expansion valve in embodiment
Make the increasing enthalpy air compensation of multiple compressors, therefore recuperated cycle system provided in an embodiment of the present invention can make the first compressor and
Second compressor is worked simultaneously, therefore solves the problems, such as that multi-connected machine heat pump heating capacity is not enough.
Description of the drawings
In order to be illustrated more clearly that the embodiment of the present invention or technical scheme of the prior art, below will be to embodiment or existing
Accompanying drawing to be used needed for having technology description is briefly described, it should be apparent that, drawings in the following description are only this
Some embodiments of invention, for those of ordinary skill in the art, on the premise of not paying creative work, can be with
Other accompanying drawings are obtained according to these accompanying drawings.
One of schematic diagram of recuperated cycle system that Fig. 1 is provided for embodiments of the invention；
The schematic diagram of the Gas-supplying enthalpy-increasing compressor that Fig. 2 is provided for embodiments of the invention；
The two of the schematic diagram of the recuperated cycle system that Fig. 3 is provided for embodiments of the invention；
The three of the schematic diagram of the recuperated cycle system that Fig. 4 is provided for embodiments of the invention；
The four of the schematic diagram of the recuperated cycle system that Fig. 5 is provided for embodiments of the invention；
The schematic diagram of the Y shape threeway that Fig. 6 is provided for embodiments of the invention；
The step of control method of the recuperated cycle system that Fig. 7 is provided for embodiments of the invention flow chart；
Circulation of the recuperated cycle system that Fig. 8 is provided for embodiments of the invention in refrigeration is schematically schemed；
Circulation of the recuperated cycle system that Fig. 9 is provided for embodiments of the invention when commonly heating schematically is schemed；
Circulation of the recuperated cycle system that Figure 10 is provided for embodiments of the invention in low-temperature heating is schematically schemed；
The step of control method of another recuperated cycle system that Figure 11 is provided for embodiments of the invention flow chart.
Specific embodiment
Accompanying drawing in below in conjunction with the embodiment of the present invention, to the embodiment of the present invention in technical scheme carry out clear, complete
Site preparation is described, it is clear that described embodiment is only a part of embodiment of the invention, rather than whole embodiment.It is based on
Embodiment in the present invention, it is every other that those of ordinary skill in the art are obtained under the premise of creative work is not made
Embodiment, belongs to the scope of protection of the invention.
" A and/or B " in the application represents three kinds of selections：A, or, B, or, A and B.Namely "and/or" i.e. can be with
Represent " and " relation, it is also possible to represent the relation of "or".
Also, it should be noted the printed words such as " first ", " second " in the application are used for the purpose of to function and effect base
This identical identical entry or similar item make a distinction, and the printed words such as " first ", " second " are not that quantity and execution order are being entered
Row is limited.
Embodiments of the invention provide a kind of recuperated cycle system, specifically, with reference to shown in Fig. 1, the recuperated cycle system
Including：First compressor 1, the second compressor 2, four-way change-over valve 3, gas-liquid separator 4, subcooler 5, bypass electric expansion valve 6,
Outdoor heat exchange loop 7 and indoor heat-exchanging loop 8.
The first compressor 1 and the second compressor equal 2 in the embodiment of the present invention is Gas-supplying enthalpy-increasing compressor.Specifically, join
According to shown in Fig. 2, Gas-supplying enthalpy-increasing compressor includes：Air entry 21, air vent 22, gas supplementing opening 23, oil equalizing pipe 24 and intermediate cavity 25,
In addition do not exclude from gas supplementing opening to ensure the coolant in intermediate cavity 25, gas supplementing opening domestic demand carries check valve (not shown in Fig. 2).
Its operation principle is similar with existing Gas-supplying enthalpy-increasing compressor operating principle, for avoiding repeating, no longer describes in detail in the application.This
Outward, it is preferred that the first compressor 1 and the second compressor in the embodiment of the present invention is model identical frequency-changeable compressor.
Further, subcooler 5 is specifically as follows plate type heat exchanger or double pipe.Outdoor heat exchange loop 7 and interior
Heat-exchanging loop 8 can be to be concatenated the transfer path for being formed by least one heat exchanger and at least one electric expansion valve.
Also, it should be noted the four-way change-over valve 3, gas-liquid separator 4, bypass electric expansion valve in the embodiment of the present invention
6 grade devices can be with the structure of the devices such as four-way change-over valve of the prior art, gas-liquid separator, electric expansion valve and work
Principle is identical.The embodiment of the present invention is done and is not limited to the structure of four-way change-over valve 3, gas-liquid separator 4, bypass electric expansion valve 6,
Can correspondingly realize which is defined in the function of recuperated cycle system.
Hereinafter the annexation of each device in above-mentioned recuperated cycle system is described in detail.
The air vent of the air vent of the first compressor 1 and the second compressor 2 is connected with first port A of four-way change-over valve 3
Logical；The air entry of the air entry of the first compressor 1 and the second compressor 2 is connected with the coolant outfan of gas-liquid separator 4, the
The gas supplementing opening of the gas supplementing opening of one compressor 1 and the second compressor 2 is connected with first end E of subcooler 5；
Second port B of four-way change-over valve 3 is connected with the first end of indoor heat-exchanging loop, the 3rd end of four-way change-over valve 3
Mouthful C is connected with the coolant input of gas-liquid separator 4, the 4th port D of four-way change-over valve and the first end in outdoor heat exchange loop 7
Connection；Second end F of subcooler 5 is connected with the coolant outfan of the bypass electric expansion valve 6, and the 3rd of the subcooler 5 the
End G is connected with second end in the outdoor heat exchange loop 7 and the coolant input of the bypass electric expansion valve 6, the mistake
4th end H of cooler 5 is connected with the second end of the indoor heat-exchanging loop 8；
Wherein, the first electromagnetic valve 9 is provided between the coolant input of first end E of subcooler 5 and gas-liquid separator 4；
The second electromagnetic valve 10 is provided between the gas supplementing opening of first end E of subcooler 5 and the first compressor 1；First end E of subcooler 5
The 3rd electromagnetic valve 11 is provided with and the gas supplementing opening of the second compressor 2 between.
Recuperated cycle system provided in an embodiment of the present invention includes：First compressor, the second compressor, four-way change-over valve,
Gas-liquid separator, subcooler, bypass electric expansion valve, outdoor heat exchange loop and indoor heat-exchanging loop, wherein, the first compressor
Air vent and the air vent of the second compressor connect with the first port of four-way change-over valve；The air entry of the first compressor and
The air entry of the second compressor is connected with the coolant outfan of gas-liquid separator, and the gas supplementing opening of the first compressor and second compresses
The gas supplementing opening of machine is connected with the first end of subcooler；The second port of four-way change-over valve is connected with the first end of indoor heat-exchanging loop
Logical, the 3rd port of four-way change-over valve is connected with the coolant input of gas-liquid separator, the 4th port of four-way change-over valve and room
The first end connection of outer heat-exchanging loop；Second end of subcooler is connected with the coolant outfan of bypass electric expansion valve, subcooler
Second end in the 3rd end and outdoor heat exchange loop and the coolant input of bypass electric expansion valve connect, the 4th of subcooler the
Hold and connect with the second end of indoor heat-exchanging loop；Wherein, the first end of the subcooler of subcooler and the coolant of gas-liquid separator are defeated
Enter the first electromagnetic valve is provided between end；It is provided between the gas supplementing opening of the first end of the subcooler of subcooler and the first compressor
Second electromagnetic valve；The 3rd electromagnetic valve is provided between the gas supplementing opening of the first end of the subcooler of subcooler and the second compressor, because
For the first electromagnetic valve, the second electromagnetic valve, the 3rd electromagnetic valve and bypass electric expansion valve can be passed through in the embodiment of the present invention
Controlling the increasing enthalpy air compensation of multiple compressors, therefore recuperated cycle system provided in an embodiment of the present invention can make first to aperture
Compressor and the second compressor are worked simultaneously, therefore solve the problems, such as that multi-connected machine heat pump heating capacity is not enough.
Optionally, with reference to shown in Fig. 3, outdoor heat exchange loop 7 includes First Heat Exchanger 71, second the 72, first electricity of heat exchanger
Sub- expansion valve 73 and the second electric expansion valve 74；
Wherein, First Heat Exchanger 71 and the concatenation of the first electric expansion valve 73 form the first transfer path 31；Second heat exchanger
72 and the second electric expansion valve 74 concatenation formed the second transfer path 32；First transfer path 31 and the second transfer path 32 simultaneously connect
Between the first end in outdoor heat exchange loop 7 and second end in outdoor heat exchange loop 7.
It should be noted that in Fig. 3 so that outdoor heat exchange loop 7 includes two heat exchangers and two electric expansion valves as an example
Illustrate, but the embodiment of the present invention is not limited to this, those skilled in the art can be with the basis of above-described embodiment
Heat exchanger and electric expansion valve in outdoor heat exchange loop 7 is set to other quantity, for example：Be set to a heat exchanger and
One electric expansion valve.Again for example：It is set to three heat exchangers and three electric expansion valves.It is clear that outdoor heat exchange loop 7
The heat exchanger quantity for including is more, then outdoor heat exchange loop exchange capability of heat is stronger, but the manufacture of corresponding recuperated cycle system
Cost is also higher, and therefore in actual design, those skilled in the art can take into full account outdoor heat exchange ability and manufacturing cost two
Aspect factor is arranging the quantity of heat exchanger and electric expansion valve in outdoor heat exchange loop 7.Additionally, working as outdoor heat exchange loop 7
When including multiple heat exchangers, preferably make that the shunt volume of multiple heat exchanger coolant is identical and heat exchange area is equal, make multiple changing
The shunt volume of hot device coolant is identical and heat exchange area is equal which part heat exchanger exchange capability of heat can be avoided to reach capacity, and portion
Divide heat exchanger to underuse, therefore farthest the exchange capability of heat in outdoor heat exchange loop can be utilized.
Optionally, with reference to shown in Fig. 4, above-mentioned recuperated cycle system also includes：First separating of oil 41 device, the second oil eliminator
42nd, the first oil return capillary tube 43 and the second oil return capillary tube 44；
The input of the first oil eliminator 41 is connected with the air vent of the first compressor 1, and the first of the first oil eliminator 41
Outfan is connected with the first port of four-way change-over valve 3, the second outfan of the first oil eliminator 41 and the first oil return capillary tube
43 first end connection, the second end of the first oil return capillary tube 43 is connected with the input of gas-liquid separator 4；
The input of the second oil eliminator 42 is connected with the air vent of the second compressor 2, and the first of the second oil eliminator 42
Outfan is connected with the first port of four-way change-over valve 4, the second outfan of the second oil eliminator 42 and the second oil return capillary tube
44 first end connection, the second end of the second oil return capillary tube 44 is connected with the input of gas-liquid separator 4.
Below to oil eliminator and oil return capillary tube by taking the first oil eliminator 41 and the first oil return capillary tube 43 as an example
Operation principle illustrate.
Lubricating oil in first compressor 1 can be together exported while first compressor, 1 air vent output coolant, first
After the mixture of 41 input of oil eliminator input coolant and lubricating oil, the first oil eliminator 41 by coolant and lubricates oil
From, and coolant is input into first port A of four-way change-over valve 3 by the first outfan of the first oil eliminator 41, by lubricating oil
The first end that the first oil return capillary tube 43 is input into by the second outfan of the first oil eliminator 41, the first oil return capillary tube 43 is again
The input that lubricating oil is input into gas-liquid separator 4 by outfan, last lubricating oil are returned by the outfan of gas-liquid separator 4
To inside the first compressor 1.Because can quickly by lubricating oil by the first oil eliminator 41 and the first oil return capillary tube 43
Inside defeated time the first compressor 1, therefore the first oil eliminator 41 and the first oil return capillary tube 43 can ensure that the first compressor 1
Fuel delivery.In the same manner, the fuel delivery of the second compressor 2 is can ensure that by the second oil eliminator 42 and the second capillary tube 44.
Further, since the first compressor 1 and the second compressor 2 preferably use model identical compressor, therefore first time
Oily capillary tube 42 is with the second oil return capillary tube 44 it is also preferred that using the identical oil return capillary tube of model.
Optionally, with reference to shown in Fig. 5, recuperated cycle system also includes：First stop valve 51 and the second stop valve 52；
First stop valve 51 is arranged between the first end of second port B of four-way change-over valve 3 and indoor heat-exchanging loop 8；
Second stop valve 52 is arranged between the second end of indoor heat-exchanging loop 8 and the 4th end H of subcooler 5.
Optionally, with reference to shown in Fig. 6, between first end E of subcooler 5, the second electromagnetic valve 10 and the 3rd electromagnetic valve 11
Connected by Y-shaped three-way pipe 60；
The central shaft 61 apart from a and Y-shaped three-way pipe 60 of 61 to the second electromagnetic valve of central shaft 10 of Y-shaped three-way pipe 60 is to the
Three electromagnetic valves 11 equal apart from b.That is, a=b.
By making the central shaft apart from a and Y-shaped three-way pipe 60 of 61 to the second electromagnetic valve of central shaft 10 of Y-shaped three-way pipe 60
61 to the 3rd electromagnetic valves 11 can be avoided because of the inconsistent caused QI invigorating non-uniform phenomenon of the pressure loss apart from b is equal.
Yet another embodiment of the invention provides a kind of control method of above-mentioned blood circulation.Specifically, with reference to shown in Fig. 7, should
Method comprises the steps：
S71, the mode of operation for determining recuperated cycle system.
Specifically, the mode of operation of recuperated cycle system is chosen as refrigeration mode or heating mode.When recuperated cycle system
Mode of operation be refrigeration mode when execution step S72, when recuperated cycle system mode of operation be heating mode when execute step
Rapid S73.
S72, the first port of four-way change-over valve are connected with the 4th port, second port is connected with the 3rd port, the first electricity
Magnet valve opening, the second electromagnetic valve and the 3rd closed electromagnetic valve.
That is, when above-mentioned recuperated cycle system is operated in a chiller mode.Four-way change-over valve 3 does not go up electricity, and four-way commutates
First port A of valve 3 and the 4th port D connections, second port B and the 3rd port C connections, the first electromagnetic valve 9 are opened, the second electricity
Magnet valve 10 and the 3rd electromagnetic valve 11 are closed.Now, with reference to shown in Fig. 8, the cyclic process of coolant in recuperated cycle system is：From
The High Temperature High Pressure coolant of the air vent output of the air vent of one compressor 1 and the second compressor 2 initially enters four-way and changes
To first port A of valve 3, the 4th port D of reversal valve 3, the first end in outdoor heat exchange loop 7 are changed by four-way then and enters to enter the room
Outer heat-exchanging loop 7, then outdoor heat-exchanging loop is flowed out by second end in outdoor heat exchange loop 7；Coolant in outdoor heat exchange loop 7
It is divided into two parts between two ends and the 3rd end G of subcooler 5, Part I coolant is flowed into by the 3rd end G of subcooler 5, the 4th
End F flows out；Part II coolant through bypassing electric expansion valve 6, flow out by the second end F inflows, first end E from subcooler 5；And two
Part coolant exchanges heat in subcooler 5.Wherein, Part I coolant is got in by the second end of indoor heat-exchanging loop 8
Heat-exchanging loop 8, then pass sequentially through the first end of indoor heat-exchanging loop 8, second port B of four-way change-over valve 3, four-way change-over valve 3
The 3rd port C, gas-liquid separator 4 coolant input gas-liquid separator 4；First electromagnetic valve 9 is opened, the second electromagnetic valve 10 is closed
Close, the 3rd electromagnetic valve 11 cuts out, Part II coolant is flowed into from the second end F of subcooler 5 through bypassing electric expansion valve 6, first
End E is entered the coolant input of gas-liquid separator 4 and is mixed in gas-liquid separator 4 with Part I coolant after flowing out, finally led to
The air entry for crossing the coolant outfan, the air entry of the first compressor 1 and the second compressor 2 of gas-liquid separator 4 returns to first
Compressor 1 and the second compressor 2, so far complete a circulation under refrigeration work pattern.Wherein, Part I coolant is used for room
Interior refrigeration evaporator, therefore Part I coolant flow through loop and be referred to as main refrigerating circuit, Part II coolant is straight after subcooler 5
Take back gas-liquid separator 4 and return to inside compressor, therefore Part II coolant flows through loop and was referred to as cold loop.
In refrigeration mode, recuperated cycle system is not in the hypodynamic phenomenon of outdoor heat exchange loop heat-energy transducer, therefore
QI invigorating need not be carried out to compressor, the second electromagnetic valve 10 and the 3rd electromagnetic valve 11 are closed.
S73, obtain ambient temperature and judge ambient temperature whether more than the first preset temperature.
Specifically, acquisition ambient temperature specifically can be obtained by the temperature sensor being arranged in outdoor environment.Certainly,
In the technology of above-described embodiment, those skilled in the art can also adopt other modes to obtain ambient temperature, for example：By with
Family input etc..However, it is simple and can improve to obtain ambient temperature by the temperature sensor that is arranged in outdoor environment
The automaticity of the control method of recuperated cycle system, it is therefore preferred that the recuperated cycle system that above-described embodiment is provided is also
Including the temperature sensor being arranged in outdoor environment.
First preset temperature can be set according to the heating capacity of recuperated cycle system by those skilled in the art.Optional
, the first preset temperature more than or equal to 5 DEG C and is less than or equal to 10 DEG C.That is, if the first preset temperature is expressed as Ta, have
5℃≤Ta≤10℃.
In step S73, if ambient temperature is commonly heated control, i.e. execution step more than the first preset temperature
S74；And if ambient temperature carries out low-temperature heating control, i.e. execution step S75 less than or equal to the first preset temperature.
S74, the first port of four-way change-over valve are connected with second port, the 3rd port is connected with the 4th port, the first electricity
Magnet valve opening, the second electromagnetic valve and the 3rd closed electromagnetic valve.
That is, when above-mentioned recuperated cycle system is operated with common heating mode, electricity on four-way change-over valve 3, four-way are changed
Connect to first port A of valve 3 with second port B, the 3rd port C and the 4th port D is connected, the first electromagnetic valve 9 is opened, second
Electromagnetic valve 10 and the 3rd electromagnetic valve 11 are closed.Now, with reference to shown in Fig. 9, the cyclic process of coolant in recuperated cycle system is：From
The High Temperature High Pressure coolant of the air vent output of the air vent of the first compressor 1 and the second compressor 2 enters four-way first and changes
First port A of reversal valve 3, then changes second port B of reversal valve 3, the first end of indoor heat-exchanging loop 8 by four-way and enters
Outdoor heat exchange loop 8, flows out indoor heat exchange by the second end of indoor heat-exchanging loop 8 again after exchanging heat through indoor heat-exchanging loop 8 and returns
Road 8, after coolant is by the outflow of 8 second end of indoor heat-exchanging loop, flows into subcooler 5 and by subcooler 5 by the 4th end H of subcooler 5
The 3rd end G flow out subcooler 5, after coolant is flowed out from the 3rd end G of subcooler 5, change with outdoor in the 3rd end G of subcooler 5
It is divided into two parts between second end of hot loop 7, Part I coolant enters outdoor by second end in outdoor heat exchange loop 7 and changes
Hot loop 7, then pass sequentially through the first end in outdoor heat exchange loop 7, the 4th port D of four-way change-over valve 3, four-way change-over valve 3
3rd port C, the coolant input gas-liquid separator 4 of gas-liquid separator 4；First electromagnetic valve 9 is opened, the second electromagnetic valve 10 cuts out,
3rd electromagnetic valve 11 cuts out, and Part II coolant is flowed into from the second end F of subcooler 5 through bypassing electric expansion valve 6, first end E
The coolant input for entering gas-liquid separator 4 after outflow is mixed in gas-liquid separator 4 with Part I coolant, finally by gas
The air entry of the coolant outfan of liquid/gas separator 4, the air entry of the first compressor 1 and the second compressor 2 returns to the first compression
Machine 1 and the second compressor 2, so far complete commonly to heat a circulation under mode of operation.Wherein, Part I coolant is used for room
Evaporation is heated outward, and therefore Part I coolant flows through loop referred to as master and heats loop, and Part II coolant exchanges heat through subcooler 5
It is returned directly to gas-liquid separator 4 afterwards and returns inside compressor, therefore Part II coolant flows through loop and was referred to as cold loop.
As in common heating mode, recuperated cycle system is also not in that outdoor heat exchange loop heat-energy transducer is hypodynamic
Phenomenon, therefore need not carry out QI invigorating to compressor, and the first electromagnetic valve 10 and the second electromagnetic valve 11 are closed.
S75, the first port of four-way change-over valve are connected with second port, the 3rd port is connected with the 4th port, the first electricity
Magnet valve is closed.When the first compressor operating, the second electromagnetic valve is opened, and when the second compressor operating, the 3rd electromagnetic valve is opened, when
When first compressor and the second compressor run, the second electromagnetic valve and the 3rd electromagnetic valve are opened.
Specifically, with reference to shown in Fig. 7, step S75 may include steps of：
S751, judge compressor operating situation.
The compressor behavior that determines in step S751 potentially includes three kinds of situations, and which is respectively：1st, the first pressure
Contracting machine runs, and the second compressor is closed.2nd, the second compressor operating, the first compressor are closed.3rd, the first compressor, the second compression
Machine runs.Wherein, execution step S752 when the first compressor operating, the second compressor are closed；When the second compressor operating,
Execution step S753 when first compressor is closed；Execution step S754 when the first compressor, the second compressor run.
S752, the first port of four-way change-over valve are connected with second port, the 3rd port is connected with the 4th port, the first electricity
Magnet valve is closed, and the second electromagnetic valve is opened, the 3rd closed electromagnetic valve.
S753, the first port of four-way change-over valve are connected with second port, the 3rd port is connected with the 4th port, the first electricity
Magnet valve is closed, the second closed electromagnetic valve, and the 3rd electromagnetic valve is opened.
S754, the first port of four-way change-over valve are connected with second port, the 3rd port is connected with the 4th port, the first electricity
Magnet valve is closed, and the second electromagnetic valve is opened, and the 3rd electromagnetic valve is opened.
That is, when above-mentioned recuperated cycle system is operated with low-temperature heating pattern, electricity on four-way change-over valve 3, four-way are changed
Connect to first port A of valve 3 with second port B, the 3rd port C and the 4th port D connect the first electromagnetic valve 9 and close, when the
When one compressor 1 runs, the second electromagnetic valve 10 is opened, and when the second compressor 2 runs, the 3rd electromagnetic valve 11 is opened, when the first pressure
When contracting machine 1 and the second compressor 2 run, the second electromagnetic valve 10 and the 3rd electromagnetic valve 11 are opened.Now, with reference to Figure 10 institutes
Show, illustrate so that the first compressor and the second compressor run as an example in Figure 10.The circulation of coolant in recuperated cycle system
Process is：Enter from the High Temperature High Pressure coolant of the air vent output of the air vent and the second compressor 2 of the first compressor 1 first
Enter first port A that four-way changes reversal valve 3, then by four-way change second port B of reversal valve 3, indoor heat-exchanging loop 8 the
One end gets in heat-exchanging loop, is flowed out by the second end of indoor heat-exchanging loop 8 again indoor after exchanging heat through indoor heat-exchanging loop 8
Heat-exchanging loop 8, after coolant is by the outflow of 8 second end of indoor heat-exchanging loop, flows into subcooler 5 and by mistake by the 4th end H of subcooler 5
3rd end G of cooler 5 flows out subcooler 5, after coolant is flowed out from the 3rd end G of subcooler 5, in the 3rd end G and the room of subcooler 5
It is divided into two parts between second end of outer heat-exchanging loop 7, Part I coolant enters to enter the room by second end in outdoor heat exchange loop 7
Outer heat-exchanging loop 7, then pass sequentially through the first end in outdoor heat exchange loop 7, the 4th port D of four-way change-over valve 3, four-way change-over valve
3 the 3rd port C, the coolant input gas-liquid separator 4 of gas-liquid separator 4；Coolant finally by gas-liquid separator 4 is exported
The air entry of end, the air entry of the first compressor 1 and the second compressor 2 returns to the first compressor 1 and the second compressor 2；The
One electromagnetic valve 9 cuts out, the second electromagnetic valve 10 is opened, the 3rd electromagnetic valve 11 is opened, and Part II coolant is through bypassing electric expansion valve 6
The QI invigorating for entering the first compressor 1 after first end E flows out respectively by the second electromagnetic valve 10 is flowed into from the second end F of subcooler 5
Mouth is carried out QI invigorating, is entered the gas supplementing opening of the second compressor 2 by the 3rd electromagnetic valve 11 to the second compressor 2 to the first compressor 1
Carry out QI invigorating.Part I coolant mixes discharge pressure with Part II coolant in 1 intermediate cavity of compressor and 2 intermediate cavity of compressor
Contracting machine, so far completes a circulation under low-temperature heating mode of operation.Part I coolant is used for outdoor evaporation, therefore first
Divide coolant to flow through loop referred to as master and heat loop, Part II coolant is after the heat exchange of subcooler 5 to the benefit by the first compressor
The gas supplementing opening of QI KOU and the second compressor enters the first compressor and the second compressor and carries out QI invigorating, therefore Part II coolant stream
It is referred to as QI invigorating loop through loop.
Further, when mode of operation is refrigeration mode or common heating mode (heating mode and ambient temperature is more than
First preset temperature) when, the control method of the recuperated cycle system that above-described embodiment is provided also includes：
The pressure at expulsion of a, the delivery temperature for obtaining compressor and compressor.
Wherein, when the first compressor operating, the delivery temperature of compressor is the delivery temperature of the first compressor, compressor
Pressure at expulsion be the first compressor pressure at expulsion；When the second compressor operating, the delivery temperature of compressor is the second pressure
The delivery temperature of contracting machine, the pressure at expulsion of compressor are the pressure at expulsion of the second compressor；When the first compressor and the second compression
When machine runs, the delivery temperature of compressor is that the delivery temperature of the first compressor is average with the delivery temperature of the second compressor
Value, the mixed pressure of the coolant that the pressure at expulsion of compressor is the coolant discharged of the first compressor with second compressor is discharged
Power；
Exemplary, the delivery temperature for obtaining compressor can be passed by being arranged at the temperature of the air vent of the first compressor
The temperature sensor of the air vent of sensor and the second compressor is obtained；The pressure at expulsion for obtaining compressor can be by being arranged at
The pressure transducer of the air vent of the pressure transducer of the air vent of the first compressor and the second compressor is obtained.Equally, originally
Art personnel can also adopt other modes to obtain the delivery temperature and pressure at expulsion of compressor, and the embodiment of the present invention is to this
Do not limit.However, by the temperature sensor of the air vent for being arranged at the first compressor, pressure transducer and being arranged at
The delivery temperature and pressure at expulsion that the temperature sensor of the air vent of two compressors, pressure transducer obtain compressor is simple
And the automaticity of the control method of recuperated cycle system can be improved, it is therefore preferred that the heat exchange that above-described embodiment is provided
Blood circulation also includes：It is arranged at the temperature sensor of the air vent of the first compressor and pressure transducer and is arranged at second
The temperature sensor of the air vent of compressor and pressure transducer.
B, the corresponding saturation temperature of pressure at expulsion for obtaining compressor according to the pressure at expulsion of compressor.
The corresponding saturation temperature of the pressure at expulsion of c, the delivery temperature according to compressor and compressor is to bypassing electronic expansion
The aperture of valve is adjusted.
Further, according to the delivery temperature of compressor and the corresponding saturation of the pressure at expulsion of compressor in above-mentioned steps c
Temperature is adjusted to the aperture for bypassing electric expansion valve, can be specifically achieved by the steps of：
The corresponding saturation temperature of the pressure at expulsion of d, the delivery temperature according to compressor and compressor obtains working as compressor
The front exhaust degree of superheat.
Difference of the discharge superheat for delivery temperature saturation temperature corresponding with pressure at expulsion, therefore according to the row of compressor
The corresponding saturation temperature of the pressure at expulsion of temperature degree and compressor obtains the current exhaust degree of superheat of compressor and is specially：Obtain pressure
The difference of the delivery temperature of contracting machine saturation temperature corresponding with the pressure at expulsion of compressor.
The magnitude relationship of e, the discharge superheat for judging compressor and the default degree of superheat.
Wherein, the default degree of superheat can be required to be set according to the use environment of recuperated cycle system and user.Show
Example property, the default degree of superheat can be 0 DEG C.
F, when the discharge superheat of compressor is more than the default degree of superheat, the aperture of increase bypass electric expansion valve.
G, when the discharge superheat of compressor is less than the default degree of superheat, reduce the aperture of bypass electric expansion valve.
If the discharge superheat of compressor is defined as Δ Td (n), the default degree of superheat is defined as b；As Δ Td (n) ＜ b,
Reduce the aperture of bypass electric expansion valve, the coolant for flowing through subcooler can be reduced by the aperture for reducing bypass electric expansion valve
Amount, increases the delivery temperature of compressor, and then lifts the discharge superheat of compressor；As Δ Td (n) ＞ b, increase bypass electricity
The aperture of sub- expansion valve, can increase the coolant quantity for flowing through subcooler by the aperture for increasing bypass electric expansion valve, reduce pressure
The delivery temperature of contracting machine, and then reduce the discharge superheat of compressor.In addition it is also necessary to illustrate, when the aerofluxuss of compressor
When the degree of superheat is equal to the default degree of superheat, the aperture for bypassing electric expansion valve is constant.I.e. as Δ Td (n)=b, bypass electronics is kept
The aperture of expansion valve is constant.
Further, the embodiment of the present invention is additionally provided and a kind of specifically the aperture for bypassing electric expansion valve is adjusted
Method.According to the delivery temperature of compressor and the corresponding saturation temperature of the pressure at expulsion of compressor to bypass electricity in above-described embodiment
The aperture of sub- expansion valve is adjusted, and specifically includes：
H, according to formula：Δ EVB=Kp × { Δ Td (n)-Δ Td (n-1) }+Ki × Δ Td (n) obtains regulation parameter
Wherein, Δ EVB is regulation parameter；Kp, Ki are PID (English full name：Proportion Integration
Differentiation, Chinese full name：Proportional-integral-differential) control constant；Δ Td (n) is the compressor that n-th is obtained
Discharge superheat, Δ Td (n)=Td (n)-Tdo (n), Td (n) are the delivery temperature of the compressor that n-th is obtained；Tdo (n) is
The target exhaust temperature of compressor, Tdo (n)=Td_slv (n)+B, B are preset constant, and Td_slv (n) is the pressure that n-th is obtained
The corresponding saturation temperature of the pressure at expulsion of contracting machine；Δ Td (n-1) is the discharge superheat of the compressor of (n-1)th acquisition, and n is for just
Integer.
That is, obtaining regulation parameter Δ EVB processes in above-described embodiment is：
First, the corresponding saturation temperature of pressure at expulsion of the compressor for being obtained according to n-th obtains the target row of compressor
Temperature degree.That is, Td_slv (n) is substituted into formula：Tdo (n)=Td_slv (n)+B obtains Tdo (n).Exemplary, B more than or
It is equal to 30 DEG C and is less than or equal to 35 DEG C.
Secondly, the delivery temperature n-th of the compressor for being obtained according to the target exhaust temperature and n-th of compressor is obtained
The discharge superheat of compressor.That is, Tdo (n), Td (n) are substituted in formula Δ Td (n)=Td (n)-Tdo (n) and is calculated Δ
Td(n).
Finally, the aerofluxuss of the compressor of the discharge superheat of the compressor for being obtained according to n-th and (n-1)th acquisition
Temperature obtains regulation parameter, i.e. Δ Td (n), Δ Td (n-1) are substituted into formula Δ EVB=Kp × { Δ Td (n)-Δ Td (n-1) }
+ Ki × Δ Td (n) is calculated Δ EVB.
Wherein, n-th and the interval time lengths of (n-1)th time are TS, and the setting of TS should be met to bypassing electric expansion valve
Aperture be adjusted rear recuperated cycle system and can reach steady statue in TS time spans, to TS in the embodiment of the present invention
Concrete length do not limit, can allow the aperture for bypassing electric expansion valve is adjusted rear recuperated cycle system and reaches
Steady statue is defined.
I, according to regulation parameter and formula：EVB (n)=EVB (n-1)+Δ EVB is adjusted to the aperture of electric expansion valve
Section；
Wherein, EVB (n) is the aperture of electric expansion valve after n-th regulation, and EVB (n-1) is electronics after (n-1)th regulation
The aperture of expansion valve.
That is, bypass electric expansion valve aperture regulation amplitude be Δ EVB, so as to by bypass electric expansion valve aperture by
EVB (n-1) is adjusted to EVB (n).
Optionally, the embodiment of the present invention additionally provides a kind of low-temperature heating (mode of operation is heating mode and ambient temperature
Be less than or equal to the first preset temperature) when to bypassing the method that is adjusted of electronic expansion valve opening.Specifically, with reference to Figure 11 institutes
Show, the method comprises the steps：
S101, the calculating actual measurement degree of superheat.
Wherein, the QI invigorating degree of superheat of the intermediate cavity that the degree of superheat is the first compressor, when the first compressor operating, is surveyed, when
During the second compressor operating, the QI invigorating degree of superheat of the intermediate cavity that the degree of superheat is the second compressor is surveyed, when the first compressor and the
When two compressors run, the QI invigorating degree of superheat of the intermediate cavity that the degree of superheat is the first compressor and the centre of the second compressor is surveyed
Smaller value in the QI invigorating degree of superheat in chamber.That is, needed to first determine whether that recuperated cycle system is list before the actual measurement degree of superheat is calculated
Compressor operating (the first compressor operating or the second compressor operating) or double-compressor (the first compressor operating and the second pressure
Contracting machine runs).
With reference to shown in Figure 11, step S101 can specifically be achieved by the steps of：
The QI invigorating degree of superheat of the first compressor intermediate cavity is calculated when the first compressor operating as the actual measurement degree of superheat；When
The QI invigorating degree of superheat of the second compressor intermediate cavity is calculated during two compressor operatings as the actual measurement degree of superheat；When the first compressor,
Two compressors judge when running whether the QI invigorating degree of superheat of the first compressor intermediate cavity is more than the intermediate cavity of the second compressor
The QI invigorating degree of superheat, if so, calculates the second compressor intermediate cavity QI invigorating degree of superheat as the actual measurement degree of superheat, if it is not, calculate first pressing
The contracting machine intermediate cavity QI invigorating degree of superheat is used as the actual measurement degree of superheat.In addition it is also necessary to illustrate, when the benefit of the first compressor intermediate cavity
When the gas degree of superheat is equal to the QI invigorating degree of superheat of the intermediate cavity of the second compressor, the benefit of the intermediate cavity of arbitrary compressor can be calculated
The gas degree of superheat is used as the actual measurement degree of superheat.
Additionally, difference of the QI invigorating degree of superheat of intermediate cavity for corresponding with the pressure of the intermediate cavity saturation temperature of temperature of intermediate cavity
Value.Therefore, before the actual measurement degree of superheat is calculated, the temperature and pressure of the intermediate cavity of compressor also first should be obtained.Specifically, can be with
By be arranged at middle intracavity temperature sensor and pressure transducer obtaining the temperature and pressure of the intermediate cavity of compressor.Cause
This is preferred, and the recuperated cycle system that above-described embodiment is provided also includes the intermediate cavity for being arranged at the first compressor and the second pressure
The QI invigorating temperature sensor of the intermediate cavity of contracting machine and superfeed pressure sensor.
S102, the magnitude relationship for judging the actual measurement degree of superheat and target superheat degree.
Wherein, target superheat degree can be set as arbitrary value according to the actual requirements.Exemplary, the default degree of superheat can be
0℃.
In step S102, if the actual measurement degree of superheat is equal to target superheat degree, execution step S103.
S103, judge throttle temperature difference whether more than or equal to the second preset temperature.
Wherein, throttle temperature difference is the first refrigerant temperature before bypass electric expansion valve throttling and bypass electric expansion valve section
The temperature difference of the second refrigerant temperature after stream.
Specifically, obtain the first refrigerant temperature to pass by being arranged at the temperature of bypass electric expansion valve coolant input
Sensor is obtained, and obtaining the second refrigerant temperature can be obtained by being arranged at the temperature sensor of bypass electric expansion valve coolant outfan
Take.It is therefore preferred that the recuperated cycle system that above-described embodiment is provided also includes being arranged at the coolant output of bypass electric expansion valve
The temperature sensor at end and be arranged at bypass electric expansion valve coolant outfan temperature sensor.
Wherein, the second preset temperature can be set as arbitrary value according to the actual requirements.Exemplary, the second preset temperature is big
In or be equal to 0 DEG C and be less than or equal to 5 DEG C.
In step s 103, if throttle temperature difference keeps Current electronic expansion valve more than or equal to the second preset temperature
Aperture is constant, intermediate cavity target temperature is constant, this time adjusts and terminates；If throttle temperature difference is executed less than the second preset temperature
Step S104.
S104, intermediate cavity target temperature lift preset value.
Lifted in intermediate cavity target temperature and rejudge in return to step S102 after preset value the actual measurement degree of superheat and target
The magnitude relationship of the degree of superheat.
Preset value is the range value that intermediate cavity target temperature is lifted each time.Exemplary, preset value more than 0 DEG C and is less than
Or it is equal to 4 DEG C.
That is, in step S104 after intermediate cavity target temperature lifting preset value in return to step S102.
Further, in step s 102, if the actual measurement degree of superheat is less than target superheat degree, execution step S105.
S105, the aperture for reducing bypass electric expansion valve.
After the aperture for reducing bypass electric expansion valve, judge throttle temperature difference whether more than or equal to the second preset temperature.
That is, step S103 is returned to after step S105.
In step s 103, if throttle temperature difference is less than the second preset temperature, intermediate cavity target temperature lifts preset value
And rejudge the magnitude relationship of the actual measurement degree of superheat and target superheat degree.That is, if throttle temperature difference is less than the second preset temperature,
In return to step S104, the process of S104 is repeated, when meeting throttle temperature difference more than or equal to the second preset temperature,
Intermediate cavity target temperature keeps constant, and return to step S102.
In step s 103, if throttle temperature difference is more than or equal to the second preset temperature, intermediate cavity target temperature is constant
And rejudge the magnitude relationship of the actual measurement degree of superheat and target superheat degree.That is, if throttle temperature difference is preset more than or equal to second
Temperature, then rejudge the magnitude relationship of the actual measurement degree of superheat and target superheat degree in return to step S102.
Further, in step s 102, if the actual measurement degree of superheat is more than target superheat degree, execution step S106.
S106, the aperture of increase bypass electric expansion valve.
Judge whether throttle temperature difference is preset more than or equal to second after the aperture of increase bypass electric expansion valve again
Temperature.That is, step S103 is returned to after step s 106.
In step s 103, if throttle temperature difference is less than the second preset temperature, intermediate cavity target temperature lifts preset value
And rejudge the magnitude relationship of the actual measurement degree of superheat and target superheat degree.That is, if throttle temperature difference is less than the second preset temperature,
In return to step S104, the process of S104 is repeated, when meeting throttle temperature difference more than or equal to the second preset temperature,
Intermediate cavity target temperature keeps constant and return to step S102.
In step s 103, if throttle temperature difference is more than or equal to the second preset temperature, intermediate cavity target temperature is constant
And rejudge the magnitude relationship of the actual measurement degree of superheat and target superheat degree.That is, if throttle temperature difference is preset more than or equal to second
Temperature, then in return to step S102.
Further, the embodiment of the present invention additionally provides a kind of aperture for reducing bypass electric expansion valve or increase bypass
The method of the aperture of electric expansion valve, specifically, reduces aperture or the increase bypass electric expansion valve of bypass electric expansion valve
Aperture comprise the steps：
According to formula：Δ EVB=Kp × { Δ Tdm (n)-Δ Tdm (n-1) }+Ki × Δ Tdm (n) obtains regulation parameter；
Wherein, Δ EVB is regulation parameter；Kp, Ki be PID control constant；Δ Tdm (n) is the compressor that n-th is obtained
The actual measurement degree of superheat, Δ Tdm (n)=Tdm (n)-Tdmo (n), the compressor intermediate cavity temperature that Tdm (n) is obtained for n-th, Tdmo
(n) target intermediate cavity temperature；Tdmo (n)=Tdm_slv (n)+D, Tdm_slv (n) are the compressor intermediate cavity pressure that n-th is obtained
The corresponding saturation temperature of power, D is preset constant；Δ Tdm (n-1) is the actual measurement degree of superheat of the compressor of (n-1)th acquisition, and n is
Positive integer.
That is, obtaining regulation parameter Δ EVB processes in above-described embodiment is：
First, middle the cavity pressure corresponding saturation temperature acquisition target intermediate cavity temperature of the compressor for being obtained according to n-th
Degree.That is, Tdm_slv (n) is substituted into formula：Tdmo (n)=Tdm_slv (n)+D obtains Tdmo (n).Exemplary, D more than or
It is equal to 0 DEG C and is less than or equal to 2 DEG C.
Secondly, the compressor intermediate cavity temperature n-th for being obtained according to target intermediate cavity temperature and n-th obtains compressor
The actual measurement degree of superheat.That is, Tdmo (n), Tdm (n) are substituted in formula Δ Tdm (n)=Tdm (n)-Tdmo (n) and is calculated Δ
Tdm(n).
Finally, the actual measurement of the compressor of the actual measurement degree of superheat of the compressor for being obtained according to n-th and (n-1)th acquisition
Temperature obtains regulation parameter, i.e. Δ Tdm (n), Δ Tdm (n-1) are substituted into formula Δ EVB=Kp × { Δ Tdm (n)-Δ Tdm
(n-1) }+Ki × Δ T dm (n) is calculated Δ EVB.
Wherein, n-th and the interval time lengths of (n-1)th time are TS, and the setting of TS should be met to bypassing electric expansion valve
Aperture be adjusted rear recuperated cycle system and can reach steady statue in TS time spans, to TS in the embodiment of the present invention
Concrete length do not limit, can allow the aperture for bypassing electric expansion valve is adjusted rear recuperated cycle system and reaches
Steady statue is defined.
According to formula：EVB (n)=EVB (n-1)+Δ EVB reduces the aperture of bypass electric expansion valve or increase bypass electricity
The aperture of sub- expansion valve；
Wherein, wherein EVB (n) is the aperture of electric expansion valve after n-th regulation, after EVB (n-1) is (n-1)th regulation
The aperture of electric expansion valve.
That is, bypass electric expansion valve aperture regulation amplitude be Δ EVB, so as to by bypass electric expansion valve aperture by
EVB (n-1) is adjusted to EVB (n).
Yet another embodiment of the invention provides a kind of air-conditioning, and the air-conditioning includes the recuperated cycle system that any of the above-described embodiment is provided
System.
Specifically, the air-conditioning in the embodiment of the present invention can be domestic air conditioning, i.e. one-to-one；Can also be multi-gang air-conditioner
System, i.e., one drag many.One-to-one refers to the air conditioning system that an off-premises station connects an indoor set by pipe arrangement；One drags and refers to more
To be an off-premises station connected by pipe arrangement more than two (i.e. at least two) indoor sets air conditioning system.No matter for small-sized family
The recuperated cycle system that above-described embodiment is provided can be included with air-conditioning or multi-online air-conditioning system.
The above, the only specific embodiment of the present invention, but protection scope of the present invention is not limited thereto, any
Those familiar with the art the invention discloses technical scope in, the change or replacement that can readily occur in all are answered
It is included within the scope of the present invention.Therefore, protection scope of the present invention should be defined by scope of the claims.
Claims (16)
1. a kind of recuperated cycle system, it is characterised in that include：First compressor, the second compressor, four-way change-over valve, gas-liquid
Separator, subcooler, bypass electric expansion valve, outdoor heat exchange loop and indoor heat-exchanging loop；
First end of the air vent of the air vent of first compressor and second compressor with the four-way change-over valve
Mouth connection；Coolant of the air entry of the air entry of first compressor and second compressor with the gas-liquid separator
The gas supplementing opening of outfan connection, the gas supplementing opening of first compressor and second compressor with the subcooler first
End connection；
The second port of the four-way change-over valve is connected with the first end of the indoor heat-exchanging loop, and the of the four-way change-over valve
Three ports are connected with the coolant input of the gas-liquid separator, the 4th port and the outdoor heat exchange of the four-way change-over valve
The first end connection in loop；Second end of the subcooler is connected with the coolant outfan of the bypass electric expansion valve, described
3rd end of subcooler is connected with the coolant input of second end in the outdoor heat exchange loop and the bypass electric expansion valve
Logical, the 4th end of the subcooler is connected with the second end of the indoor heat-exchanging loop；
Wherein, the first electromagnetic valve is provided between the coolant input of the first end of the subcooler and the gas-liquid separator；
The second electromagnetic valve is provided between the gas supplementing opening of the first end of the subcooler and first compressor；The of the subcooler
The 3rd electromagnetic valve is provided between the gas supplementing opening of one end and second compressor.
2. recuperated cycle system according to claim 1, it is characterised in that the outdoor heat exchange loop includes the first heat exchange
Device, the second heat exchanger, the first electric expansion valve and the second electric expansion valve；
Wherein, the First Heat Exchanger and the first electric expansion valve concatenate to form the first transfer path；Second heat exchanger and
Second electric expansion valve concatenates to form the second transfer path；First transfer path and second transfer path simultaneously connect and institute
State between the first end in outdoor heat exchange loop and second end in the outdoor heat exchange loop.
3. recuperated cycle system according to claim 1, it is characterised in that the recuperated cycle system also includes：First
Oil eliminator, the second oil eliminator, the first oil return capillary tube and the second oil return capillary tube；
The input of first oil eliminator is connected with the air vent of first compressor, and the of first oil eliminator
One outfan is connected with the first port of the four-way change-over valve, the second outfan of first oil eliminator and described first
The first end connection of oil return capillary tube, the second end of the first oil return capillary tube is connected with the input of the gas-liquid separator
Logical；
The input of second oil eliminator is connected with the air vent of second compressor, and the of second oil eliminator
One outfan is connected with the first port of the four-way change-over valve, the second outfan of second oil eliminator and described second
The first end connection of oil return capillary tube, the second end of the second oil return capillary tube is connected with the input of the gas-liquid separator
Logical.
4. recuperated cycle system according to claim 1, it is characterised in that the recuperated cycle system also includes：First
Stop valve and the second stop valve；
First stop valve be arranged at the second port of the four-way change-over valve and the indoor heat-exchanging loop first end it
Between；
Second stop valve is arranged between the second end of the indoor heat-exchanging loop and the 4th end of the subcooler.
5. recuperated cycle system according to claim 1, it is characterised in that the first end of the subcooler, described second
Connected by Y-shaped three-way pipe between electromagnetic valve and the 3rd electromagnetic valve；
The central shaft of the Y-shaped three-way pipe to second electromagnetic valve distance and the central shaft of the Y-shaped three-way pipe to described
The distance of the 3rd electromagnetic valve is equal.
6. a kind of control method of recuperated cycle system, it is characterised in that for controlling to exchange heat described in any one of claim 1-5
Blood circulation, methods described include：
Determine the mode of operation of recuperated cycle system；
When the mode of operation be refrigeration mode when, the first port of four-way change-over valve is connected with the 4th port, second port and
The connection of 3rd port, the first electromagnetic valve opening, the second electromagnetic valve and the 3rd closed electromagnetic valve；
When the mode of operation is heating mode, obtains ambient temperature and judge whether the ambient temperature is preset more than first
Temperature；
When ambient temperature is more than the first preset temperature, the first port of four-way change-over valve is connected with second port, the 3rd port
Connect with the 4th port, the first electromagnetic valve is opened, the second electromagnetic valve and the 3rd closed electromagnetic valve；
When ambient temperature is less than or equal to the first preset temperature, the first port of four-way change-over valve connected with second port, the
Three ports are connected with the 4th port, the first closed electromagnetic valve, and the second electromagnetic valve is opened when the first compressor operating, when second
During compressor operating, the 3rd electromagnetic valve is opened, when the first compressor and the second compressor run, the second electromagnetic valve and the 3rd
Electromagnetic valve is opened.
7. method according to claim 6, it is characterised in that when the mode of operation is refrigeration mode or the work
When pattern is that heating mode and ambient temperature are more than the first preset temperature, methods described also includes：
Obtain the delivery temperature of compressor and the pressure at expulsion of compressor；Wherein, when first compressor operating, the pressure
The delivery temperature of contracting machine is the delivery temperature of first compressor, and the pressure at expulsion of the compressor is first compressor
Pressure at expulsion；When second compressor operating, the delivery temperature of the compressor is the aerofluxuss of second compressor
Temperature, the pressure at expulsion of the compressor are the pressure at expulsion of second compressor；When first compressor and described
When two compressors run, the delivery temperature of the compressor is delivery temperature and described second compression of first compressor
The meansigma methodss of the delivery temperature of machine, the pressure at expulsion of the compressor are the coolant and described second that first compressor is discharged
The mixed pressure of coolant that compressor is discharged；
The corresponding saturation temperature of pressure at expulsion that the compressor is obtained according to the pressure at expulsion of the compressor；
According to the corresponding saturation temperature of the pressure at expulsion of delivery temperature and the compressor of the compressor to bypassing electronics
The aperture of expansion valve is adjusted.
8. method according to claim 7, it is characterised in that the delivery temperature and the pressure according to the compressor
The corresponding saturation temperature of the pressure at expulsion of contracting machine is adjusted to the aperture for bypassing electric expansion valve, including：
The compression is obtained according to the delivery temperature of the compressor and the corresponding saturation temperature of the pressure at expulsion of the compressor
The discharge superheat of machine；
Judge the discharge superheat of the compressor and the magnitude relationship of the default degree of superheat；
When the discharge superheat of the compressor is more than the default degree of superheat, increase opening for the bypass electric expansion valve
Degree；
When the discharge superheat of the compressor is less than the default degree of superheat, reduce opening for the bypass electric expansion valve
Degree.
9. method according to claim 7, it is characterised in that the delivery temperature and the pressure according to the compressor
The corresponding saturation temperature of the pressure at expulsion of contracting machine is adjusted to the aperture for bypassing electric expansion valve, including：
According to formula：Δ EVB=Kp × { Δ Td (n)-Δ Td (n-1) }+Ki × Δ Td (n) obtains regulation parameter；
Wherein, Δ EVB is regulation parameter；Kp, Ki are PID control constant；Δ Td (n) is the aerofluxuss of the compressor that n-th is obtained
The degree of superheat, Δ Td (n)=Td (n)-Tdo (n), Td (n) are the delivery temperature of the compressor that n-th is obtained；Tdo (n) is compression
The target exhaust temperature of machine, Tdo (n)=Td_slv (n)+B, Td_slv (n) are the pressure at expulsion pair of the compressor that n-th is obtained
The saturation temperature that answers, B are preset constant；Δ Td (n-1) is the discharge superheat of the compressor of (n-1)th acquisition, and n is just whole
Number；
According to the regulation parameter and formula：EVB (n)=EVB (n-1)+Δ EVB is carried out to the aperture of the electric expansion valve
Adjust；
Wherein, EVB (n) is the aperture of the electric expansion valve after n-th regulation, after EVB (n-1) is (n-1)th regulation
The aperture of the electric expansion valve.
10. method according to claim 6, it is characterised in that when the mode of operation is heating mode and ambient temperature
During less than or equal to the first preset temperature, methods described also includes：
Calculate the actual measurement degree of superheat；Wherein, when first compressor operating, the actual measurement degree of superheat is first compressor
Intermediate cavity the QI invigorating degree of superheat, when second compressor operating, the actual measurement degree of superheat is second compressor
The QI invigorating degree of superheat of intermediate cavity, when first compressor and second compressor run, the actual measurement degree of superheat is
In the QI invigorating degree of superheat of the intermediate cavity of first compressor and the QI invigorating degree of superheat of the intermediate cavity of second compressor compared with
Little value；
Judge the magnitude relationship of the actual measurement degree of superheat and target superheat degree；
When the actual measurement degree of superheat is spent equal to the target superheat, judge whether throttle temperature difference is preset more than or equal to second
Temperature；Wherein, the throttle temperature difference is the first refrigerant temperature before the bypass electric expansion valve throttling and the bypass electricity
The temperature difference of the second refrigerant temperature after sub- expansion valve throttling；
If the throttling temperature difference is less than the second preset temperature, intermediate cavity target temperature lifts preset value and rejudges the reality
Survey the magnitude relationship of the degree of superheat and target superheat degree.
11. methods according to claim 10, it is characterised in that methods described also includes：
When the actual measurement degree of superheat is spent less than the target superheat, reduce the aperture of the bypass electric expansion valve；
After the aperture for reducing the bypass electric expansion valve, judge whether throttle temperature difference presets temperature more than or equal to second
Degree；
If it is not, the intermediate cavity target temperature lifts preset value and to rejudge the actual measurement degree of superheat big with target superheat degree
Little relation；
If so, judge the magnitude relationship of the actual measurement degree of superheat and target superheat degree.
12. methods according to claim 10, it is characterised in that methods described also includes：
When the actual measurement degree of superheat is spent more than the target superheat, increase the aperture of the bypass electric expansion valve；
Judge throttle temperature difference whether more than the second preset temperature after the aperture of the increase bypass electric expansion valve；
If it is not, the intermediate cavity target temperature lifts preset value and to rejudge the actual measurement degree of superheat big with target superheat degree
Little relation；
If so, judge the magnitude relationship of the actual measurement degree of superheat and target superheat degree.
13. methods according to claim 11 or 12, it is characterised in that the reduction is described to bypass opening for electric expansion valve
The aperture for spending or increasing the bypass electric expansion valve includes：
According to formula：Δ EVB=Kp × { Δ Tdm (n)-Δ Tdm (n-1) }+Ki × Δ Tdm (n) obtains regulation parameter；
Wherein, Δ EVB is regulation parameter；Kp, Ki are PID control constant；Δ Tdm (n) is the actual measurement of the compressor that n-th is obtained
The degree of superheat, Δ Tdm (n)=Tdm (n)-Tdmo (n), the temperature of the intermediate cavity of the compressor that Tdm (n) is obtained for n-th, Tdmo
N () is intermediate cavity target temperature；Tdmo (n)=Tdm_slv (n)+D, Tdm_slv (n) are the compressor intermediate cavity that n-th is obtained
The corresponding saturation temperature of pressure, D is preset constant；Δ Tdm (n-1) is the actual measurement degree of superheat of the compressor of (n-1)th acquisition,
N is positive integer；
According to formula：EVB (n)=EVB (n-1)+Δ EVB reduces the aperture of the bypass electric expansion valve or increases the side
The aperture of logical electric expansion valve；
Wherein, wherein EVB (n) is the aperture of the electric expansion valve after n-th regulation, and EVB (n-1) is adjusted for (n-1)th time
The aperture of the electric expansion valve after section.
14. methods according to claim 6, it is characterised in that first preset temperature more than or equal to 5 DEG C and is less than
Or it is equal to 10 DEG C.
15. methods according to claim 10, it is characterised in that second preset temperature is more than or equal to 0 DEG C and little
In or be equal to 5 DEG C, the preset value more than 0 DEG C and be less than or equal to 4 DEG C.
16. a kind of air-conditionings, it is characterised in that including the recuperated cycle system described in any one of claim 1-5.
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08200869A (en) * | 1995-01-31 | 1996-08-06 | Daikin Ind Ltd | Refrigerator |
| CN103175344A (en) * | 2013-03-13 | 2013-06-26 | 青岛海信日立空调系统有限公司 | Cold-region used multi-connected heat pump system and control method thereof |
| CN103307817A (en) * | 2013-06-17 | 2013-09-18 | 江苏科立德制冷设备有限公司 | Vortex shunt-wound compression condensing unit |
| CN103471275A (en) * | 2013-08-30 | 2013-12-25 | 青岛海信日立空调系统有限公司 | Enhanced vapor injection air-conditioning circulating system and control method thereof |
| CN104254743A (en) * | 2012-04-27 | 2014-12-31 | 三菱电机株式会社 | Air conditioning device |
| CN104329821A (en) * | 2013-07-22 | 2015-02-04 | 刘雄 | Air conditioning refrigeration equipment and control method thereof |
-
2016
- 2016-10-18 CN CN201610909006.XA patent/CN106500391B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08200869A (en) * | 1995-01-31 | 1996-08-06 | Daikin Ind Ltd | Refrigerator |
| CN104254743A (en) * | 2012-04-27 | 2014-12-31 | 三菱电机株式会社 | Air conditioning device |
| CN103175344A (en) * | 2013-03-13 | 2013-06-26 | 青岛海信日立空调系统有限公司 | Cold-region used multi-connected heat pump system and control method thereof |
| CN103307817A (en) * | 2013-06-17 | 2013-09-18 | 江苏科立德制冷设备有限公司 | Vortex shunt-wound compression condensing unit |
| CN104329821A (en) * | 2013-07-22 | 2015-02-04 | 刘雄 | Air conditioning refrigeration equipment and control method thereof |
| CN103471275A (en) * | 2013-08-30 | 2013-12-25 | 青岛海信日立空调系统有限公司 | Enhanced vapor injection air-conditioning circulating system and control method thereof |
Cited By (22)
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|---|---|---|---|---|
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| CN107975959A (en) * | 2017-11-08 | 2018-05-01 | 宁波奥克斯电气股份有限公司 | A kind of multi-online air-conditioning system and control method |
| CN108151213A (en) * | 2017-12-25 | 2018-06-12 | 广东美的制冷设备有限公司 | Air conditioner, progress control method and computer readable storage medium |
| CN108362051A (en) * | 2018-02-08 | 2018-08-03 | 广东高而美制冷设备有限公司 | A kind of wide area increasing enthalpy method |
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