CN106500391B - A kind of heat exchange cycle system and its control method and air-conditioning - Google Patents
A kind of heat exchange cycle system and its control method and air-conditioning Download PDFInfo
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- CN106500391B CN106500391B CN201610909006.XA CN201610909006A CN106500391B CN 106500391 B CN106500391 B CN 106500391B CN 201610909006 A CN201610909006 A CN 201610909006A CN 106500391 B CN106500391 B CN 106500391B
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- 238000004378 air conditioning Methods 0.000 title claims abstract description 18
- 238000000034 method Methods 0.000 title abstract description 24
- 239000007788 liquid Substances 0.000 claims abstract description 47
- 238000010438 heat treatment Methods 0.000 claims abstract description 30
- 239000003507 refrigerant Substances 0.000 claims description 97
- 230000001502 supplementing effect Effects 0.000 claims description 25
- 230000005611 electricity Effects 0.000 claims description 12
- 230000006835 compression Effects 0.000 claims description 11
- 238000007906 compression Methods 0.000 claims description 11
- 238000005057 refrigeration Methods 0.000 claims description 10
- 238000012546 transfer Methods 0.000 claims description 9
- 238000004519 manufacturing process Methods 0.000 abstract description 3
- 239000003921 oil Substances 0.000 description 33
- 238000005259 measurement Methods 0.000 description 25
- 238000010586 diagram Methods 0.000 description 6
- 239000010687 lubricating oil Substances 0.000 description 6
- 230000008901 benefit Effects 0.000 description 4
- 230000007812 deficiency Effects 0.000 description 3
- 230000033228 biological regulation Effects 0.000 description 2
- 238000009833 condensation Methods 0.000 description 2
- 230000005494 condensation Effects 0.000 description 2
- 125000004122 cyclic group Chemical group 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 241000208340 Araliaceae Species 0.000 description 1
- 235000005035 Panax pseudoginseng ssp. pseudoginseng Nutrition 0.000 description 1
- 235000003140 Panax quinquefolius Nutrition 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 230000007423 decrease Effects 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
- 235000008434 ginseng Nutrition 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
- 239000010726 refrigerant oil Substances 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 238000006467 substitution reaction 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
-
- 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
-
- 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
-
- 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
-
- 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
The embodiment of the present invention provides a kind of heat exchange cycle system and its control method and air-conditioning, is related to air-conditioning technical field, for solving the problems, such as that multi-connected machine heat pump system heating capacity is insufficient in the prior art.The heat exchange cycle system includes: the first compressor, the second compressor, four-way reversing valve, gas-liquid separator, subcooler, bypass electric expansion valve, outdoor heat exchange circuit, indoor heat-exchanging loop, the first solenoid valve, second solenoid valve and third solenoid valve.The embodiment of the present invention is 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 heat exchange cycle system and its control method and air-conditionings.
Background technique
Flexible, accurate, unit applicability is good, occupancy construction area is small, installation and maintenance due to controlling for multi-connected machine heat pump system
Favor of the advantages that the facilitating by more and more consumers.
It is identical as traditional air-conditioning system, the heating principle of multi-connected machine heat pump system are as follows: compressor first is by high temperature and pressure
Gas refrigerant heat exchanger sent to the room, which carries out condensation, becomes the liquid refrigerant of high temperature and pressure, and indoor unit is by high temperature and pressure
The heat released after gas refrigerant condensation is sent out；Then the liquid refrigerant of high temperature and pressure flows into room using throttle part
Outer heat-exchanger is evaporated the gas refrigerant become, and last gas refrigerant returns to compressor from outdoor heat exchanger, complete
It is recycled at a heating.When multi-connected machine heat pump system is used for the heating of cold district, lower environment temperature will limit multi-joint
The thermal energy of the exchange capability of heat of machine heat pump system outdoor heat exchanger, multi-connected machine heat pump system is mainly derived from the power consumption of compressor, because
The problems such as this compression ratio that will lead to compressor increases, delivery temperature rises, volumetric efficiency decline.To solve the above-mentioned problems,
One stage of compression is carried out to refrigerant suction pressure to intermediate cavity pressure first by Gas-supplying enthalpy-increasing compressor in the prior art, then
The refrigerant after one stage of compression carries out two-stage compression after mixing with intermediate cavity tonifying Qi refrigerant again.Gas-supplying enthalpy-increasing compressor passes through
The mode of two-stage compression reduces compression ratio, delivery temperature and the volumetric efficiency for improving compressor of compressor.However, by
In being unable to accurately control the multi-connected machine heat pump system increasing enthalpy air compensation with multiple compressors in the prior art, thus it is current more
Online heat pump system is single compressor Gas-supplying enthalpy-increasing system, is limited by number of compressors, compared with running under low ambient temperature
When, multi-connected machine heat pump system still has the problem of heating capacity deficiency.
Summary of the invention
The embodiment of the present invention provides a kind of heat exchange cycle system and its control method and air-conditioning, for solving the prior art
The problem of middle multi-connected machine heat pump system heating capacity deficiency.
In order to achieve the above objectives, the embodiment of the present invention adopts the following technical scheme that
In a first aspect, providing a kind of heat exchange cycle system, comprising: the first compressor, the second compressor, four-way reversing valve,
Gas-liquid separator, subcooler, bypass electric expansion valve, outdoor heat exchange circuit and indoor heat-exchanging loop；
The exhaust outlet of the exhaust outlet of first compressor and second compressor with the four-way reversing valve
Single port connection；The air entry of the air entry of first compressor and second compressor with the gas-liquid separator
The connection of refrigerant output end, the gas supplementing opening of the gas supplementing opening of first compressor and second compressor with the subcooler
First end connection；
The second port of the four-way reversing valve is connected to the first end of the indoor heat-exchanging loop, the four-way reversing valve
Third port be connected to the refrigerant input terminal of the gas-liquid separator, the 4th port of the four-way reversing valve and the outdoor
The first end of heat-exchanging loop is connected to；The second end of the subcooler is connected to the refrigerant output end of the bypass electric expansion valve,
The refrigerant of the second end and the bypass electric expansion valve in the third end of the subcooler and the outdoor heat exchange circuit inputs
End connection, the 4th end of the subcooler are connected to the second end of the indoor heat-exchanging loop；
Wherein, the first electromagnetism is provided between the first end of the subcooler and the refrigerant input terminal of the gas-liquid separator
Valve；Second solenoid valve is provided between the first end of the subcooler and the gas supplementing opening of first compressor；The subcooler
First end and second compressor gas supplementing opening between be provided with third solenoid valve.
Second aspect provides a kind of control method of heat exchange cycle system, for controlling heat exchange cycle described in first aspect
System, which comprises
Determine operating mode；
When the operating mode is refrigeration mode, the first port of four-way reversing valve is connected to the 4th port, second end
Mouth is connected to third port, and the first solenoid valve is opened, and second solenoid valve and third solenoid valve are closed；
When the operating mode is heating mode, obtains environment temperature and judge whether the environment temperature is greater than first
Preset temperature；
When environment temperature is greater than the first preset temperature, the first port of four-way reversing valve is connected to second port, third
Port is connected to the 4th port, and the first solenoid valve is opened, and second solenoid valve and third solenoid valve are closed；
When environment temperature is less than or equal to the first preset temperature, the first port and second port of four-way reversing valve connect
Logical, third port is connected to the 4th port, and the first solenoid valve is closed, and second solenoid valve is opened when the operation of the first compressor,
When the operation of the second compressor, third solenoid valve is opened, when a first compressor and a second compressor is run, second solenoid valve
It is opened with third solenoid valve.
The third aspect provides a kind of air-conditioning, including heat exchange cycle system described in first aspect.
Heat exchange cycle system provided in an embodiment of the present invention include: the first compressor, the second compressor, four-way reversing valve,
Gas-liquid separator, subcooler, bypass electric expansion valve, outdoor heat exchange circuit and indoor heat-exchanging loop, wherein the first compressor
Exhaust outlet and the exhaust outlet of the second compressor be connected to the first port of four-way reversing valve；The air entry of first compressor and
The air entry of second compressor is connected to the refrigerant output end of gas-liquid separator, the gas supplementing opening of the first compressor and the second compression
The gas supplementing opening of machine is connected to the first end of subcooler；The second port of four-way reversing valve and the first end of indoor heat-exchanging loop connect
Logical, the third port of four-way reversing valve is connected to the refrigerant input terminal of gas-liquid separator, the 4th port of four-way reversing valve and room
The first end of outer heat-exchanging loop is connected to；The second end of subcooler is connected to the refrigerant output end of bypass electric expansion valve, subcooler
Third end and the second end in outdoor heat exchange circuit and bypass the refrigerant input terminal of electric expansion valve and be connected to, the 4th of subcooler the
It holds and is connected to the second end of indoor heat-exchanging loop；Wherein, between the first end of subcooler and the refrigerant input terminal of gas-liquid separator
It is provided with the first solenoid valve；The second electromagnetism is provided between the first end of the subcooler of subcooler and the gas supplementing opening of the first compressor
Valve；Third solenoid valve is provided between the first end of the subcooler of subcooler and the gas supplementing opening of the second compressor, because of the invention
It can be controlled by the aperture of the first solenoid valve, second solenoid valve, third solenoid valve and bypass electric expansion valve in embodiment
Make the increasing enthalpy air compensation of multiple compressors, thus heat exchange cycle system provided in an embodiment of the present invention can make the first compressor and
Second compressor works at the same time, therefore solves the problems, such as that multi-connected machine heat pump system heating capacity is insufficient.
Detailed description of the invention
In order to more clearly explain the embodiment of the invention or the technical proposal in the existing technology, to embodiment or will show below
There is attached drawing needed in technical description to be briefly described, it should be apparent that, the accompanying drawings in the following description is only this
Some embodiments of invention for those of ordinary skill in the art without creative efforts, can be with
It obtains other drawings based on these drawings.
Fig. 1 is one of the schematic diagram for the heat exchange cycle system that the embodiment of the present invention provides；
Fig. 2 is the schematic diagram for the Gas-supplying enthalpy-increasing compressor that the embodiment of the present invention provides；
Fig. 3 is the two of the schematic diagram for the heat exchange cycle system that the embodiment of the present invention provides；
Fig. 4 is the three of the schematic diagram for the heat exchange cycle system that the embodiment of the present invention provides；
Fig. 5 is the four of the schematic diagram for the heat exchange cycle system that the embodiment of the present invention provides；
Fig. 6 is the schematic diagram for the Y shape threeway that the embodiment of the present invention provides；
Fig. 7 is the step flow chart of the control method for the heat exchange cycle system that the embodiment of the present invention provides；
Fig. 8 is that circulation of the heat exchange cycle system that provides of the embodiment of the present invention in refrigeration is schematically schemed；
Fig. 9 is that circulation of the heat exchange cycle system that provides of the embodiment of the present invention in common heating is schematically schemed；
Figure 10 is that circulation of the heat exchange cycle system that provides of the embodiment of the present invention in low-temperature heating is schematically schemed；
Figure 11 is the step flow chart of the control method for another heat exchange cycle system that the embodiment of the present invention provides.
Specific embodiment
Following will be combined with the drawings in the embodiments of the present invention, and technical solution in the embodiment of the present invention carries out clear, complete
Site preparation description, it is clear that described embodiments are only a part of the embodiments of the present invention, instead of all the embodiments.It is based on
Embodiment in the present invention, it is obtained by those of ordinary skill in the art without making creative efforts every other
Embodiment shall fall within the protection scope of the present invention.
" A and/or B " in the application indicates three kinds of selections: A, alternatively, B, alternatively, A and B.Namely "and/or" can
Indicate " and " relationship, can also indicate the relationship of "or".
It should be noted that the printed words such as " first " in the application, " second " are used for the purpose of to function and effect base
This identical identical entry or similar item distinguish, the printed words such as " first ", " second " be not to quantity and execution order into
Row limits.
The embodiment of the present invention provides a kind of heat exchange cycle system, specifically, shown in referring to Fig.1, the heat exchange cycle system
Include: the first compressor 1, the second compressor 2, four-way reversing valve 3, gas-liquid separator 4, subcooler 5, bypass electric expansion valve 6,
Outdoor heat exchange circuit 7 and indoor heat-exchanging loop 8.
The first compressor 1 and the second compressor equal 2 in the embodiment of the present invention are Gas-supplying enthalpy-increasing compressor.Specifically, ginseng
According to shown in Fig. 2, Gas-supplying enthalpy-increasing compressor includes: air entry 21, exhaust outlet 22, gas supplementing opening 23, oil equalizing pipe 24 and intermediate cavity 25,
Furthermore in order to guarantee that the refrigerant in intermediate cavity 25 is not excluded from gas supplementing opening, gas supplementing opening domestic demand carries check valve (being not shown in Fig. 2).
Its working principle is similar with existing Gas-supplying enthalpy-increasing compressor operating principle, to avoid repeating, is no longer described in detail in the application.This
Outside, it is preferred that the first compressor 1 and the second compressor in the embodiment of the present invention are the identical frequency-changeable compressor of model.
Further, subcooler 5 is specifically as follows plate heat exchanger or double pipe.Outdoor heat exchange circuit 7 and interior
Heat-exchanging loop 8 all can be concatenate the transfer path formed by least one heat exchanger and at least one electric expansion valve.
It should also be noted that, four-way reversing valve 3, gas-liquid separator 4, bypass electric expansion valve in the embodiment of the present invention
6 equal devices can be with the structure and work of the devices such as four-way reversing valve in the prior art, gas-liquid separator, electric expansion valve
Principle is identical.The embodiment of the present invention is done and is not limited to four-way reversing valve 3, gas-liquid separator 4, the structure for bypassing electric expansion valve 6,
Being subject to correspond to realizes it in the function of heat exchange cycle system.
The connection relationship of each device in above-mentioned heat exchange cycle system is described in detail below.
The exhaust outlet of the exhaust outlet of first compressor 1 and the second compressor 2 connects with the first port A of four-way reversing valve 3
It is logical；The air entry of the air entry of first compressor 1 and the second compressor 2 is connected to the refrigerant output end 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 to the first end E of subcooler 5；
The second port B of four-way reversing valve 3 is connected to the first end of indoor heat-exchanging loop, the third end of four-way reversing valve 3
Mouth C is connected to the refrigerant input terminal of gas-liquid separator 4, the first end of the 4th port D and outdoor heat exchange circuit 7 of four-way reversing valve
Connection；The second end F of subcooler 5 is connected to the refrigerant output end of the bypass electric expansion valve 6, the third of the subcooler 5
End G is connected to the refrigerant input terminal of the second end in the outdoor heat exchange circuit 7 and the bypass electric expansion valve 6, the mistake
4th end H of cooler 5 is connected to the second end of the indoor heat-exchanging loop 8；
Wherein, the first solenoid valve 9 is provided between the first end E of subcooler 5 and the refrigerant input terminal of gas-liquid separator 4；
Second solenoid valve 10 is provided between the first end E of subcooler 5 and the gas supplementing opening of the first compressor 1；The first end E of subcooler 5
Third solenoid valve 11 is provided between the gas supplementing opening of the second compressor 2.
Heat exchange cycle system provided in an embodiment of the present invention include: the first compressor, the second compressor, four-way reversing valve,
Gas-liquid separator, subcooler, bypass electric expansion valve, outdoor heat exchange circuit and indoor heat-exchanging loop, wherein the first compressor
Exhaust outlet and the exhaust outlet of the second compressor be connected to the first port of four-way reversing valve；The air entry of first compressor and
The air entry of second compressor is connected to the refrigerant output end of gas-liquid separator, the gas supplementing opening of the first compressor and the second compression
The gas supplementing opening of machine is connected to the first end of subcooler；The second port of four-way reversing valve and the first end of indoor heat-exchanging loop connect
Logical, the third port of four-way reversing valve is connected to the refrigerant input terminal of gas-liquid separator, the 4th port of four-way reversing valve and room
The first end of outer heat-exchanging loop is connected to；The second end of subcooler is connected to the refrigerant output end of bypass electric expansion valve, subcooler
Third end and the second end in outdoor heat exchange circuit and bypass the refrigerant input terminal of electric expansion valve and be connected to, the 4th of subcooler the
It holds and is connected to the second end of indoor heat-exchanging loop；Wherein, the first end of the subcooler of subcooler and the refrigerant of gas-liquid separator are defeated
Enter and is provided with the first solenoid valve between end；It is provided between the first end of the subcooler of subcooler and the gas supplementing opening of the first compressor
Second solenoid valve；Third solenoid valve is provided between the first end of the subcooler of subcooler and the gas supplementing opening of the second compressor, because
For the first solenoid valve, second solenoid valve, third solenoid valve and bypass electric expansion valve can be passed through in the embodiment of the present invention
Aperture controls the increasing enthalpy air compensations of multiple compressors, therefore heat exchange cycle system provided in an embodiment of the present invention can make first
Compressor and the second compressor work at the same time, therefore solve the problems, such as that multi-connected machine heat pump system heating capacity is insufficient.
Optionally, referring to shown in Fig. 3, outdoor heat exchange circuit 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 first electric expansion valve 73 concatenation form the first transfer path 31；Second heat exchanger
72 and 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 circuit 7 and the second end in outdoor heat exchange circuit 7.
It should be noted that in Fig. 3 by taking outdoor heat exchange circuit 7 includes two heat exchangers and two electric expansion valves as an example
It is illustrated, but it's not limited to that for the embodiment of the present invention, those skilled in the art can be on the basis of the above embodiments
By in outdoor heat exchange circuit 7 heat exchanger and electric expansion valve be set as other quantity, such as: be set as a heat exchanger and
One electric expansion valve.Again for example: being set as three heat exchangers and three electric expansion valves.It is clear that outdoor heat exchange circuit 7
In include heat exchanger quantity it is more, then outdoor heat exchange circuit exchange capability of heat is stronger, but the manufacture of corresponding heat exchange cycle system
Cost is also higher, therefore those skilled in the art can fully consider outdoor heat exchange ability and manufacturing cost two in actual design
Aspect is because being usually arranged the quantity of heat exchanger and electric expansion valve in outdoor heat exchange circuit 7.In addition, working as outdoor heat exchange circuit 7
In when including multiple heat exchangers, preferably make that the shunt volume of multiple heat exchanger refrigerants is identical and heat exchange area is equal, make multiple change
The shunt volume of hot device refrigerant is identical and heat exchange area is equal to reach capacity to avoid part of heat exchanger exchange capability of heat, and portion
Point heat exchanger is underused, thus can the exchange capability of heat to the greatest extent to outdoor heat exchange circuit utilize.
Optionally, referring to shown in Fig. 4, above-mentioned heat exchange cycle system further include: the first oil separation 41 devices, the second oil eliminator
42, the first oil return capillary 43 and the second oil return capillary 44；
The input terminal of first oil eliminator 41 is connected to the exhaust outlet of the first compressor 1, and the first of the first oil eliminator 41
Output end is connected to the first port of four-way reversing valve 3, the second output terminal of the first oil eliminator 41 and the first oil return capillary
43 first end connection, the second end of the first oil return capillary 43 are connected to the input terminal of gas-liquid separator 4；
The input terminal of second oil eliminator 42 is connected to the exhaust outlet of the second compressor 2, and the first of the second oil eliminator 42
Output end is connected to the first port of four-way reversing valve 4, the second output terminal of the second oil eliminator 42 and the second oil return capillary
44 first end connection, the second end of the second oil return capillary 44 are connected to the input terminal of gas-liquid separator 4.
Below to oil eliminator and oil return capillary by taking the first oil eliminator 41 and the first oil return capillary 43 as an example
Working principle be illustrated.
First compressor, 1 exhaust outlet can export together the lubricating oil in the first compressor 1 while exporting refrigerant, and first
After 41 input terminal of oil eliminator inputs the mixture of refrigerant and lubricating oil, the first oil eliminator 41 is by refrigerant and lubricates oil
From, and refrigerant inputted into the first port A of four-way reversing valve 3 by the first output end of the first oil eliminator 41, by lubricating oil
The first end of the first oil return capillary 43 is inputted by the second output terminal of the first oil eliminator 41, the first oil return capillary 43 is again
Lubricating oil is inputted to the input terminal of gas-liquid separator 4 by output end, last lubricating oil is returned by the output end of gas-liquid separator 4
To inside the first compressor 1.Because can be quickly by lubricating oil by the first oil eliminator 41 and the first oil return capillary 43
Inside defeated time the first compressor 1, therefore the first oil eliminator 41 and the first oil return capillary 43 can guarantee the first compressor 1
Fuel delivery.Similarly, it can guarantee the fuel delivery of the second compressor 2 by the second oil eliminator 42 and the second capillary 44.
Further, since the first compressor 1 and the second compressor 2 be it is preferable to use the identical compressor of model, therefore first time
Oily capillary 42 is with the second oil return capillary 44 it is also preferred that using the identical oil return capillary of model.
Optionally, referring to Figure 5, heat exchange cycle system further include: the first shut-off valve 51 and the second shut-off valve 52；
First shut-off valve 51 is set between the second port B of four-way reversing valve 3 and the first end of indoor heat-exchanging loop 8；
Second shut-off valve 52 is set between the second end of indoor heat-exchanging loop 8 and the 4th end H of subcooler 5.
Optionally, referring to shown in Fig. 6, between the first end E of subcooler 5, second solenoid valve 10 and third solenoid valve 11
It is connected to by Y-shaped three-way pipe 60；
The central axis 61 of Y-shaped three-way pipe 60 is to the distance a of second solenoid valve 10 and the central axis 61 of Y-shaped three-way pipe 60 to the
The distance b of three solenoid valves 11 is equal.That is, a=b.
By making the central axis 61 of Y-shaped three-way pipe 60 to the distance a of second solenoid valve 10 and the central axis of Y-shaped three-way pipe 60
61 to third solenoid valve 11 distance b it is equal can to avoid because the pressure loss it is inconsistent caused by tonifying Qi non-uniform phenomenon.
Yet another embodiment of the invention provides a kind of control method of above-mentioned circulatory system.Specifically, referring to shown in Fig. 7, it should
Method includes the following steps:
S71, the operating mode for determining heat exchange cycle system.
Specifically, the operating mode of heat exchange cycle system is chosen as refrigeration mode or heating mode.When heat exchange cycle system
Operating mode be refrigeration mode when execute step S72, when the operating mode of heat exchange cycle system be heating mode when execute step
Rapid S73.
S72, four-way reversing valve first port be connected to the 4th port, second port is connected to third port, first electricity
Magnet valve is opened, and second solenoid valve and third solenoid valve are closed.
That is, when above-mentioned heat exchange cycle system is worked in a chiller mode.Four-way reversing valve 3 does not power on, four-way commutation
First port A and the 4th port the D connection of valve 3, second port B are connected to third port C, and the first solenoid valve 9 is opened, the second electricity
Magnet valve 10 and third solenoid valve 11 are closed.At this point, referring to shown in Fig. 8, the cyclic process of refrigerant in heat exchange cycle system are as follows: from
The high temperature and pressure refrigerant of the exhaust outlet of the exhaust outlet of one compressor 1 and the second compressor 2 output initially enters four-way and changes
To the first port A of valve 3, the 4th port D of reversal valve 3 is then changed by four-way, the first end in outdoor heat exchange circuit 7 enters room
Outer heat-exchanging loop 7, then by heat-exchanging loop outside the second end delivery chamber in outdoor heat exchange circuit 7；Refrigerant in outdoor heat exchange circuit 7
It is divided into two parts between two ends and the third end G of subcooler 5, first part's refrigerant flows by the third end G of subcooler 5, the 4th
Hold F outflow；Second part refrigerant flows into, first end E outflow through bypassing electric expansion valve 6 from the second end F of subcooler 5；And two
Part refrigerant exchanges heat in subcooler 5.Wherein, first part's refrigerant is entered the room 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, the second port B of four-way reversing valve 3, four-way reversing valve 3
Third port C, gas-liquid separator 4 refrigerant input gas-liquid separator 4；First solenoid valve 9 is opened, second solenoid valve 10 is closed
It closes, the closing of third solenoid valve 11, second part refrigerant is bypassed electric expansion valve 6 from the second end F of subcooler 5 inflow, first
The refrigerant input terminal for entering gas-liquid separator 4 after the E outflow of end mixes in gas-liquid separator 4 with first part's refrigerant, finally leads to
The air entry for crossing the refrigerant output end of gas-liquid separator 4, the air entry of the first compressor 1 and the second compressor 2 returns to first
Compressor 1 and the second compressor 2 so far complete a circulation under refrigeration work mode.Wherein, first part's refrigerant is used for room
Interior refrigeration evaporator, therefore first part's refrigerant flows through circuit and is known as main refrigerating circuit, second part refrigerant is straight after subcooler 5
It takes back gas-liquid separator 4 and returns to inside compressor, therefore second part refrigerant flows through circuit and was known as cold loop.
In refrigeration mode, heat exchange cycle system is not in the phenomenon of outdoor heat exchange circuit exchange capability of heat deficiency, therefore
It does not need to carry out tonifying Qi to compressor, second solenoid valve 10 and third solenoid valve 11 is closed.
S73, it obtains environment temperature and judges whether environment temperature is greater than the first preset temperature.
Specifically, obtaining environment temperature can specifically be obtained by the temperature sensor being set in outdoor environment.Certainly,
Those skilled in the art can also obtain environment temperature using other modes in the technology of above-described embodiment, such as: pass through use
Family input etc..However, it is simple and easy and can be improved to obtain environment temperature by the temperature sensor that is set in outdoor environment
The degree of automation of the control method of heat exchange cycle system, it is therefore preferred that heat exchange cycle system provided by the above embodiment is also
Including the temperature sensor being set in outdoor environment.
First preset temperature can be set by those skilled in the art according to the heating capacity of heat exchange cycle system.It is optional
, the first preset temperature is greater than or equal to 5 DEG C and is less than or equal to 10 DEG C.That is, having if the first preset temperature is expressed as Ta
5℃≤Ta≤10℃。
In step S73, if environment temperature is greater than the first preset temperature, common heating control, i.e. execution step are carried out
S74；And if environment temperature is less than or equal to the first preset temperature, carries out low-temperature heating control, i.e. execution step S75.
S74, four-way reversing valve first port be connected to second port, third port is connected to the 4th port, first electricity
Magnet valve is opened, and second solenoid valve and third solenoid valve are closed.
That is, four-way reversing valve 3 powers on, and four-way changes when above-mentioned heat exchange cycle system is worked with common heating mode
It being connected to the first port A of valve 3 with second port B, third port C and the 4th port D connection, the first solenoid valve 9 is opened, and second
Solenoid valve 10 and third solenoid valve 11 are closed.At this point, referring to shown in Fig. 9, the cyclic process of refrigerant in heat exchange cycle system are as follows: from
The high temperature and pressure refrigerant of the exhaust outlet of the exhaust outlet of first compressor 1 and the second compressor 2 output is changed into four-way first
Then the first port A of reversal valve 3 changes the first end entrance of the second port B, indoor heat-exchanging loop 8 of reversal valve 3 by four-way
Outdoor heat exchange circuit 8 passes through again after the heat exchange of indoor heat-exchanging loop 8 and exchanges heat back in the second end delivery chamber of indoor heat-exchanging loop 8
Road 8 after refrigerant is flowed out by indoor 8 second end of heat-exchanging loop, flows into subcooler 5 by the 4th end H of subcooler 5 and by subcooler 5
Third end G flow out subcooler 5, refrigerant from the third end G of subcooler 5 outflow after, changed in third end G and the outdoor of subcooler 5
It is divided into two parts between the second end of hot loop 7, first part's refrigerant enters outdoor by the second end in outdoor heat exchange circuit 7 and changes
Hot loop 7, then pass sequentially through the first end in outdoor heat exchange circuit 7, the 4th port D of four-way reversing valve 3, four-way reversing valve 3
The refrigerant input gas-liquid separator 4 of third port C, gas-liquid separator 4；First solenoid valve 9 is opened, second solenoid valve 10 is closed,
Third solenoid valve 11 is closed, and second part refrigerant is bypassed electric expansion valve 6 from the second end F of subcooler 5 inflow, first end E
Refrigerant input terminal after outflow into gas-liquid separator 4 mixes in gas-liquid separator 4 with first part's refrigerant, finally by gas
The air entry of the refrigerant output end 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 a circulation under common heating operating mode.Wherein, first part's refrigerant is used for room
Outer heating evaporation, therefore first part's refrigerant flows through circuit and is known as main heating circuit, second part refrigerant exchanges heat by subcooler 5
It is returned directly to gas-liquid separator 4 afterwards and returns inside compressor, therefore second part refrigerant flows through circuit and was known as cold loop.
Since in common heating mode, it is insufficient that outdoor heat exchange circuit exchange capability of heat will not occur in heat exchange cycle system
Phenomenon, therefore do not need to carry out tonifying Qi to compressor, the first solenoid valve 10 and second solenoid valve 11 are closed.
S75, four-way reversing valve first port be connected to second port, third port is connected to the 4th port, first electricity
Magnet valve is closed.When the operation of the first compressor, second solenoid valve is opened, and when the operation of the second compressor, third solenoid valve is opened, when
When a first compressor and a second compressor is run, second solenoid valve and third solenoid valve are opened.
Specifically, step S75 may include steps of referring to shown in Fig. 7:
S751, judge compressor operating condition.
The compressor behavior determined in step S751 may include three kinds of situations, be respectively as follows: the 1, first pressure
The operation of contracting machine, the second compressor are closed.2, the operation of the second compressor, the first compressor are closed.3, the first compressor, the second compression
Machine is run.Wherein, step S752 is executed when the operation of the first compressor, the second compressor are closed；When the second compressor run,
Step S753 is executed when first compressor is closed；Step S754 is executed when the first compressor, the second compressor are run.
S752, four-way reversing valve first port be connected to second port, third port is connected to the 4th port, first electricity
Magnet valve is closed, and second solenoid valve is opened, and third solenoid valve is closed.
S753, four-way reversing valve first port be connected to second port, third port is connected to the 4th port, first electricity
Magnet valve is closed, and second solenoid valve is closed, and third solenoid valve is opened.
S754, four-way reversing valve first port be connected to second port, third port is connected to the 4th port, first electricity
Magnet valve is closed, and second solenoid valve is opened, and third solenoid valve is opened.
That is, four-way reversing valve 3 powers on, and four-way changes when above-mentioned heat exchange cycle system is worked with low-temperature heating pattern
Be connected to the first port A of valve 3 with second port B, third port C and the 4th port D are connected to the first solenoid valve 9 and close, when the
Second solenoid valve 10 is opened when one compressor 1 is run, and when the operation of the second compressor 2, third solenoid valve 11 is opened, when the first pressure
When contracting machine 1 and the second compressor 2 are run, second solenoid valve 10 and third solenoid valve 11 are opened.At this point, 0 institute referring to Fig.1
Show, is illustrated so that a first compressor and a second compressor is run as an example in Figure 10.The circulation of refrigerant in heat exchange cycle system
Process are as follows: the high temperature and pressure refrigerant exported from the exhaust outlet of the exhaust outlet of the first compressor 1 and the second compressor 2 first into
Enter the first port A that four-way changes reversal valve 3, then by four-way change the second port B of reversal valve 3, indoor heat-exchanging loop 8 the
One end enters the room heat-exchanging loop, in the second end delivery chamber for passing through indoor heat-exchanging loop 8 again after the heat exchange of indoor heat-exchanging loop 8
Heat-exchanging loop 8 after refrigerant is flowed out by indoor 8 second end of heat-exchanging loop, flows into subcooler 5 by the 4th end H of subcooler 5 and by mistake
The third end G of cooler 5 flows out subcooler 5, and refrigerant is after the third end G of subcooler 5 outflow, in the third end G of subcooler 5 and room
It is divided into two parts between the second end of outer heat-exchanging loop 7, first part's refrigerant enters room by the second end in outdoor heat exchange circuit 7
Outer heat-exchanging loop 7, then pass sequentially through the 4th port D, the four-way reversing valve of the first end in outdoor heat exchange circuit 7, four-way reversing valve 3
3 third port C, the refrigerant of gas-liquid separator 4 input gas-liquid separator 4；It is exported finally by the refrigerant of gas-liquid separator 4
The air entry at 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 solenoid valve 9 is closed, second solenoid valve 10 is opened, third solenoid valve 11 is opened, and second part refrigerant is through bypassing electric expansion valve 6
The tonifying Qi that respectively by second solenoid valve 10 enters first compressor 1 is flowed into after first end E outflow from the second end F of subcooler 5
Mouth carries out tonifying Qi to the first compressor 1, enters the gas supplementing opening of the second compressor 2 by third solenoid valve 11 to the second compressor 2
Carry out tonifying Qi.First part's refrigerant mixes discharge pressure in 1 intermediate cavity of compressor and 2 intermediate cavity of compressor with second part refrigerant
Contracting machine so far completes a circulation under low-temperature heating operating mode.First part's refrigerant is used for outdoor evaporation, therefore first
Divide refrigerant to flow through circuit and be known as main heating circuit, second part refrigerant is after the heat exchange of subcooler 5 to the benefit by the first compressor
The gas supplementing opening of port and the second compressor enters a first compressor and a second compressor and carries out tonifying Qi, therefore second part refrigerant stream
It is known as tonifying Qi circuit through circuit.
Further, when operating mode is refrigeration mode or common heating mode (heating mode and environment temperature is greater than
First preset temperature) when, the control method of heat exchange cycle system provided by the above embodiment, further includes:
A, the delivery temperature of compressor and the pressure at expulsion of compressor are obtained.
Wherein, when the first compressor is run, 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 operation of the second compressor, 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 second compress
When machine is run, the delivery temperature of compressor is the delivery temperature of the first compressor and being averaged for the delivery temperature of the second compressor
Value, the pressure at expulsion of compressor are the refrigerant of the first compressor discharge and the mixed pressure of refrigerant of second compressor discharge
Power；
Illustratively, the delivery temperature for obtaining compressor can be passed by being set to the temperature of the exhaust outlet of the first compressor
The temperature sensor of the exhaust outlet of sensor and the second compressor obtains；The pressure at expulsion for obtaining compressor can be by being set to
The pressure sensor of the exhaust outlet of the pressure sensor of the exhaust outlet of first compressor and the second compressor obtains.Equally, originally
Field technical staff can also obtain the delivery temperature and pressure at expulsion of compressor using other modes, and the embodiment of the present invention is to this
Without limitation.However, by the temperature sensor for the exhaust outlet for being set to the first compressor, pressure sensor and being set to
The temperature sensor of the exhaust outlet of two compressors, the delivery temperature of pressure sensor acquisition compressor and pressure at expulsion are simple and easy
And the degree of automation of the control method of heat exchange cycle system can be improved, it is therefore preferred that heat exchange provided by the above embodiment
The circulatory system further include: be set to the temperature sensor and pressure sensor of the exhaust outlet of the first compressor and be set to second
The temperature sensor and pressure sensor of the exhaust outlet of compressor.
B, the corresponding saturation temperature of pressure at expulsion of compressor is obtained according to the pressure at expulsion of compressor.
C, according to the corresponding saturation temperature of pressure at expulsion of the delivery temperature of compressor and compressor to bypass 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
The aperture of bypass electric expansion valve is adjusted in temperature, can specifically be achieved by the steps of:
D, working as compressor, is obtained according to the corresponding saturation temperature of pressure at expulsion of the delivery temperature of compressor and compressor
The front exhaust degree of superheat.
Discharge superheat is the difference of 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 specifically: obtains pressure
The difference of the delivery temperature of contracting machine and the corresponding saturation temperature of the pressure at expulsion of compressor.
E, judge the discharge superheat of compressor and the size relation of the default degree of superheat.
Wherein, the default degree of superheat can require to set according to the use environment of heat exchange 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 greater than the default degree of superheat, increase the aperture of 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,
The aperture for reducing bypass electric expansion valve, the aperture by reducing bypass electric expansion valve can reduce the refrigerant for flowing through subcooler
Amount increases the delivery temperature of compressor, and then promotes the discharge superheat of compressor；As Δ Td (n) > b, increase bypass electricity
The aperture of sub- expansion valve, the aperture by increasing bypass electric expansion valve can increase the coolant quantity for flowing through subcooler, reduce pressure
The delivery temperature of contracting machine, and then reduce the discharge superheat of compressor.In addition it is also necessary to explanation, when the exhaust 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, specifically the aperture of bypass electric expansion valve is adjusted the embodiment of the invention also provides a kind of
Method.According to the corresponding saturation temperature of pressure at expulsion of the delivery temperature of compressor and 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 adjustment parameter
Wherein, Δ EVB is adjustment parameter；Kp, Ki are PID (full name in English: Proportion Integration
Differentiation, Chinese name: proportional-integral-differential) control constant；Δ Td (n) is the compressor that n-th obtains
Discharge superheat, Δ Td (n)=Td (n)-Tdo (n), Td (n) are the delivery temperature for the compressor that n-th obtains；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 obtains
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 positive
Integer.
That is, obtaining adjustment parameter Δ EVB process in above-described embodiment are as follows:
Firstly, the target that the corresponding saturation temperature of pressure at expulsion of the compressor obtained according to n-th obtains compressor is arranged
Temperature degree.That is, Td_slv (n) is substituted into formula: Tdo (n)=Td_slv (n)+B obtains Tdo (n).Illustratively, B be greater than or
Equal to 30 DEG C and it is less than or equal to 35 DEG C.
Secondly, the delivery temperature n-th of the compressor obtained according to the target exhaust temperature of compressor and n-th obtains
The discharge superheat of compressor.Δ is calculated that is, Tdo (n), Td (n) are substituted into formula Δ Td (n)=Td (n)-Tdo (n)
Td(n)。
Finally, according to the exhaust of the discharge superheat of the compressor of n-th acquisition and the compressor of (n-1)th acquisition
Temperature obtains adjustment parameter, that is, Δ Td (n), Δ Td (n-1) are substituted into formula Δ EVB=Kp × { Δ Td (n)-Δ Td (n-1) }
Δ EVB is calculated in+Ki × Δ Td (n).
Wherein, n-th and (n-1)th interval time lengths are TS, and the setting of TS should meet to bypass electric expansion valve
Aperture rear heat exchange cycle system is adjusted can reach stable state in TS time span, to TS in the embodiment of the present invention
Specific length without limitation, the aperture to bypass electric expansion valve can be made rear heat exchange cycle system be adjusted to can achieve
Subject to stable state.
I, according to adjustment parameter and formula: EVB (n)=EVB (n-1)+Δ EVB adjusts the aperture of electric expansion valve
Section；
Wherein, EVB (n) is the aperture of electric expansion valve after n-th is adjusted, and EVB (n-1) is electronics after (n-1)th adjusting
The aperture of expansion valve.
That is, the aperture regulation amplitude of bypass electric expansion valve is Δ EVB, thus will bypass the aperture of electric expansion valve by
EVB (n-1) is adjusted to EVB (n).
Optionally, the embodiment of the invention also provides a kind of low-temperature heating, (operating mode is heating mode and environment temperature
Less than or equal to the first preset temperature) when to the method that is adjusted of bypass electronic expansion valve opening.Specifically, 1 institute referring to Fig.1
Show, this method comprises the following steps:
S101, the actual measurement degree of superheat is calculated.
Wherein, when the first compressor is run, the actual measurement degree of superheat is the tonifying Qi degree of superheat of the intermediate cavity of the first compressor, when
When second compressor is run, the actual measurement degree of superheat is the tonifying Qi degree of superheat of the intermediate cavity of the second compressor, when the first compressor and the
When two compressors are run, the actual measurement degree of superheat is the tonifying Qi degree of superheat of the intermediate cavity of the first compressor and the centre of the second compressor
Smaller value in the tonifying Qi degree of superheat of chamber.That is, needing to first determine whether that heat exchange cycle system is single before calculating the actual measurement degree of superheat
Compressor operation (operation of the first compressor or the operation of the second compressor) or double-compressor (operation of the first compressor and the second pressure
Contracting machine is run).
Referring to Fig.1 shown in 1, step S101 can be specifically achieved by the steps of:
The tonifying Qi degree of superheat of the first compressor intermediate cavity is calculated when the operation of the first compressor as the actual measurement degree of superheat；When
Two compressors calculate the tonifying Qi degree of superheat of the second compressor intermediate cavity as the actual measurement degree of superheat when running；When the first compressor,
Two compressors judge whether the tonifying Qi degree of superheat of the first compressor intermediate cavity is greater than the intermediate cavity of the second compressor when running
The tonifying Qi degree of superheat, if so, the second compressor intermediate cavity tonifying Qi degree of superheat is calculated as the actual measurement degree of superheat, if it is not, calculating the first pressure
The contracting machine intermediate cavity tonifying Qi degree of superheat is as the actual measurement degree of superheat.In addition it is also necessary to explanation, when the benefit of the first compressor intermediate cavity
When the gas degree of superheat is equal to the tonifying Qi degree of superheat of the intermediate cavity of the second compressor, the benefit of the intermediate cavity of any compressor can be calculated
The gas degree of superheat is as the actual measurement degree of superheat.
In addition, the tonifying Qi degree of superheat of intermediate cavity is the difference of the temperature saturation temperature corresponding with the pressure of intermediate cavity of intermediate cavity
Value.Therefore before calculating the actual measurement degree of superheat, the temperature and pressure of the intermediate cavity of compressor should also first be obtained.Specifically, can be with
The temperature and pressure of the intermediate cavity of compressor is obtained by the temperature sensor and pressure sensor being set in intermediate cavity.Cause
This is preferred, and heat exchange cycle system provided by the above embodiment further includes being set to the intermediate cavity and the second pressure of the first compressor
The tonifying Qi temperature sensor and superfeed pressure sensor of the intermediate cavity of contracting machine.
The size relation of S102, judgement the actual measurement degree of superheat and target superheat degree.
Wherein, target superheat degree can be set as arbitrary value according to actual needs.Illustratively, the default degree of superheat can be
0℃。
In step S102, if the actual measurement degree of superheat is equal to target superheat degree, S103 is thened follow the steps.
S103, judge whether throttle temperature difference is greater than or equal to the second preset temperature.
Wherein, throttle temperature difference is the first refrigerant temperature and bypass electric expansion valve section before bypassing electric expansion valve throttling
The temperature difference of the second refrigerant temperature after stream.
Specifically, obtaining the first refrigerant temperature can be passed by being set to the temperature of bypass electric expansion valve refrigerant input terminal
Sensor obtains, and obtaining the second refrigerant temperature can be obtained by being set to the temperature sensor of bypass electric expansion valve refrigerant output end
It takes.It is therefore preferred that heat exchange cycle system provided by the above embodiment further includes being set to bypass electric expansion valve refrigerant output
The temperature sensor at end and the temperature sensor for being set to bypass electric expansion valve refrigerant output end.
Wherein, the second preset temperature can be set as arbitrary value according to actual needs.Illustratively, 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 is greater than or equal to the second preset temperature, Current electronic expansion valve is kept
Aperture is constant, intermediate cavity target temperature is constant, and this time adjusting terminates；If throttle temperature difference is executed less than the second preset temperature
Step S104.
S104, intermediate cavity target temperature promote preset value.
It is promoted in intermediate cavity target temperature and rejudges the actual measurement degree of superheat and target after preset value in return step S102
The size relation of the degree of superheat.
Preset value is the range value that intermediate cavity target temperature is promoted each time.Illustratively, preset value is greater 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 promotion preset value in return step S102.
Further, in step s 102, if the actual measurement degree of superheat is less than target superheat degree, S105 is thened follow the steps.
S105, the aperture for reducing bypass electric expansion valve.
Judge whether throttle temperature difference is greater than or equal to the second preset temperature after the aperture for reducing bypass electric expansion valve.
That is, returning to step S103 after step S105.
In step s 103, if throttle temperature difference is less than the second preset temperature, intermediate cavity target temperature promotes preset value
And rejudge the size relation of the actual measurement degree of superheat and target superheat degree.That is, if throttle temperature difference less than the second preset temperature,
In return 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 remains unchanged, and return step S102.
In step s 103, if throttle temperature difference is greater than or equal to the second preset temperature, intermediate cavity target temperature is constant
And rejudge the size relation of the actual measurement degree of superheat and target superheat degree.That is, being preset if throttle temperature difference is greater than or equal to second
Temperature then rejudges the size relation of the actual measurement degree of superheat and target superheat degree in return step S102.
Further, in step s 102, if the actual measurement degree of superheat is greater than target superheat degree, S106 is thened follow the steps.
S106, the aperture for increasing bypass electric expansion valve.
It is default to judge whether throttle temperature difference is greater than or equal to second again after the aperture for increasing bypass electric expansion valve
Temperature.That is, returning to step S103 after step s 106.
In step s 103, if throttle temperature difference is less than the second preset temperature, intermediate cavity target temperature promotes preset value
And rejudge the size relation of the actual measurement degree of superheat and target superheat degree.That is, if throttle temperature difference less than the second preset temperature,
In return 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 remains unchanged and return step S102.
In step s 103, if throttle temperature difference is greater than or equal to the second preset temperature, intermediate cavity target temperature is constant
And rejudge the size relation of the actual measurement degree of superheat and target superheat degree.That is, being preset if throttle temperature difference is greater than or equal to second
Temperature, then in return step S102.
Further, the embodiment of the invention also provides a kind of aperture for reducing bypass electric expansion valve or increase bypass
The method of the aperture of electric expansion valve, specifically, reducing the aperture of bypass electric expansion valve or increasing bypass electric expansion valve
Aperture include the following steps:
According to formula: Δ EVB=Kp × { Δ Tdm (n)-Δ Tdm (n-1) }+Ki × Δ Tdm (n) obtains adjustment parameter；
Wherein, Δ EVB is adjustment parameter；Kp, Ki be PID control constant；Δ Tdm (n) is the compressor that n-th obtains
The degree of superheat is surveyed, Δ Tdm (n)=Tdm (n)-Tdmo (n), Tdm (n) are the compressor intermediate cavity temperature that n-th obtains, Tdmo
(n) target intermediate cavity temperature；Tdmo (n)=Tdm_slv (n)+D, Tdm_slv (n) are the compressor intermediate cavity pressure that n-th obtains
The corresponding saturation temperature of power, D are 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 adjustment parameter Δ EVB process in above-described embodiment are as follows:
Firstly, the corresponding saturation temperature of intermediate cavity pressure of the compressor obtained according to n-th obtains target intermediate cavity temperature
Degree.That is, Tdm_slv (n) is substituted into formula: Tdmo (n)=Tdm_slv (n)+D obtains Tdmo (n).Illustratively, D be greater than or
Equal to 0 DEG C and it is less than or equal to 2 DEG C.
Secondly, obtaining compressor according to the compressor intermediate cavity temperature n-th that target intermediate cavity temperature and n-th obtain
The actual measurement degree of superheat.Δ is calculated that is, Tdmo (n), Tdm (n) are substituted into formula Δ Tdm (n)=Tdm (n)-Tdmo (n)
Tdm(n)。
Finally, according to the actual measurement of the actual measurement degree of superheat of the compressor of n-th acquisition and the compressor of (n-1)th acquisition
Temperature obtains adjustment parameter, that is, Δ Tdm (n), Δ Tdm (n-1) are substituted into formula Δ EVB=Kp × { Δ Tdm (n)-Δ Tdm
(n-1) } Δ EVB is calculated in+Ki × Δ T dm (n).
Wherein, n-th and (n-1)th interval time lengths are TS, and the setting of TS should meet to bypass electric expansion valve
Aperture rear heat exchange cycle system is adjusted can reach stable state in TS time span, to TS in the embodiment of the present invention
Specific length without limitation, the aperture to bypass electric expansion valve can be made rear heat exchange cycle system be adjusted to can achieve
Subject to stable state.
According to formula: EVB (n)=EVB (n-1)+Δ EVB reduces the aperture of bypass electric expansion valve or increases bypass electricity
The aperture of sub- expansion valve；
Wherein, the aperture of electric expansion valve after wherein EVB (n) is adjusted for n-th, after EVB (n-1) is adjusted for (n-1)th time
The aperture of electric expansion valve.
That is, the aperture regulation amplitude of bypass electric expansion valve is Δ EVB, thus will bypass the aperture of electric expansion valve by
EVB (n-1) is adjusted to EVB (n).
Yet another embodiment of the invention provides a kind of air-conditioning, which includes the heat exchange cycle system that any of the above-described embodiment provides
System.
Specifically, the air-conditioning in the embodiment of the present invention can be domestic air conditioning, i.e. one-to-one；It can also be multi-gang air-conditioner
System, i.e., one drag it is more.One-to-one refers to that an outdoor unit passes through the air-conditioning system of piping one indoor unit of connection；One drags mostly finger
To be an outdoor unit pass through the air-conditioning system of piping connection two or more (i.e. at least two) indoor units.No matter for small-sized family
It may include heat exchange cycle system provided by the above embodiment with air-conditioning or multi-online air-conditioning system.
The above description is merely a specific embodiment, but scope of protection of the present invention is not limited thereto, any
In the technical scope disclosed by the present invention, any changes or substitutions that can be easily thought of by those familiar with the art, all answers
It is included within the scope of the present invention.Therefore, protection scope of the present invention should be subject to the protection scope in claims.
Claims (6)
1. a kind of heat exchange cycle system characterized by comprising the first compressor, the second compressor, four-way reversing valve, gas-liquid
Separator, subcooler, bypass electric expansion valve, outdoor heat exchange circuit and indoor heat-exchanging loop；
First end of the exhaust outlet of the exhaust outlet of first compressor and second compressor with the four-way reversing valve
Mouth connection；Refrigerant of the air entry of the air entry of first compressor and second compressor with the gas-liquid separator
Output end connection, the gas supplementing opening of the gas supplementing opening of first compressor and second compressor with the subcooler first
End connection；
The second port of the four-way reversing valve is connected to the first end of the indoor heat-exchanging loop, and the of the four-way reversing valve
Three ports are connected to the refrigerant input terminal of the gas-liquid separator, the 4th port of the four-way reversing valve and the outdoor heat exchange
The first end in circuit is connected to；The second end of the subcooler is connected to the refrigerant output end of the bypass electric expansion valve, described
The refrigerant input terminal of the second end and the bypass electric expansion valve in the third end of subcooler and the outdoor heat exchange circuit connects
Logical, the 4th end of the subcooler is connected to the second end of the indoor heat-exchanging loop；
Wherein, the first solenoid valve is provided between the first end of the subcooler and the refrigerant input terminal of the gas-liquid separator；
Second solenoid valve is provided between the first end of the subcooler and the gas supplementing opening of first compressor；The of the subcooler
Third solenoid valve is provided between one end and the gas supplementing opening of second compressor；
The outdoor heat exchange circuit includes First Heat Exchanger, the second heat exchanger, the first electric expansion valve and the second electronic 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 are connected to
Between the first end in the outdoor heat exchange circuit and the second end in the outdoor heat exchange circuit；
The operating mode for determining heat exchange cycle system, when the operating mode is refrigeration mode, the first end of four-way reversing valve
Mouth is connected to the 4th port, second port is connected to third port, and the first solenoid valve is opened, second solenoid valve and third solenoid valve
It closes；
When the operating mode is heating mode, obtains environment temperature and judge whether the environment temperature is greater than first and presets
Temperature；
When environment temperature is greater than the first preset temperature, the first port of four-way reversing valve is connected to second port, third port
It is connected to the 4th port, the first solenoid valve is opened, and second solenoid valve and third solenoid valve are closed；
When environment temperature is less than or equal to the first preset temperature, the first port of four-way reversing valve is connected to second port, the
Three ports are connected to the 4th port, and the first solenoid valve is closed, and second solenoid valve is opened when the operation of the first compressor, when second
Third solenoid valve is opened when compressor is run, when a first compressor and a second compressor is run, second solenoid valve and third
Solenoid valve is opened；
When the operating mode be refrigeration mode or the operating mode to be that heating mode and environment temperature are greater than first default
When temperature, the delivery temperature of compressor and the pressure at expulsion of compressor are obtained；Wherein, when first compressor is run, institute
The delivery temperature for stating compressor is the delivery temperature of first compressor, and the pressure at expulsion of the compressor is first pressure
The pressure at expulsion of contracting machine；When second compressor operation, the delivery temperature of the compressor is second compressor
Delivery temperature, the pressure at expulsion of the compressor are the pressure at expulsion of second compressor；When first compressor and institute
When stating the second compressor and running, the delivery temperature of the compressor is the delivery temperature and described second of first compressor
The average value of the delivery temperature of compressor, the pressure at expulsion of the compressor be first compressor discharge refrigerant with it is described
The mixed pressure of refrigerant of second compressor discharge；
The corresponding saturation temperature of pressure at expulsion for obtaining the compressor according to the pressure at expulsion of the compressor；
According to the corresponding saturation temperature of the pressure at expulsion of the delivery temperature of the compressor and the compressor to bypass electronics
The aperture of expansion valve is adjusted；
The corresponding saturation temperature of pressure at expulsion of the delivery temperature and the compressor according to the compressor is to bypass electricity
The aperture of sub- expansion valve is adjusted, comprising: according to formula: Δ EVB=Kp × { Δ Td (n)-Δ Td (n-1) }+Ki × Δ Td
(n) adjustment parameter is obtained；
Wherein, Δ EVB is adjustment parameter；Kp, Ki are PID control constant；Δ Td (n) is the current of the compressor that n-th obtains
Difference between delivery temperature and target exhaust temperature, Δ Td (n)=Td (n)-Tdo (n), Td (n) are the compression that n-th obtains
The delivery temperature of machine；Tdo (n) is the target exhaust temperature of compressor, and Tdo (n)=Td_slv (n)+B, Td_slv (n) are n-th
The corresponding saturation temperature of the pressure at expulsion of the compressor of secondary acquisition, B are preset constant；Δ Td (n-1) is the pressure of (n-1)th acquisition
Difference between the current exhaust gas temperature and target exhaust temperature of contracting machine, n are positive integer；
According to the adjustment parameter and formula: EVB (n)=EVB (n-1)+Δ EVB carries out the aperture of the electric expansion valve
It adjusts；
Wherein, EVB (n) is the aperture of the electric expansion valve after n-th is adjusted, after the EVB (n-1) is adjusted for (n-1)th time
The aperture of the electric expansion valve.
2. heat exchange cycle system according to claim 1, which is characterized in that the heat exchange cycle system further include: first
Oil eliminator, the second oil eliminator, the first oil return capillary and the second oil return capillary；
The input terminal of first oil eliminator is connected to the exhaust outlet of first compressor, and the of first oil eliminator
One output end is connected to the first port of the four-way reversing valve, the second output terminal of first oil eliminator and described first
The first end of oil return capillary is connected to, and the second end of the first oil return capillary and the input terminal of the gas-liquid separator connect
It is logical；
The input terminal of second oil eliminator is connected to the exhaust outlet of second compressor, and the of second oil eliminator
One output end is connected to the first port of the four-way reversing valve, the second output terminal of second oil eliminator and described second
The first end of oil return capillary is connected to, and the second end of the second oil return capillary and the input terminal of the gas-liquid separator connect
It is logical.
3. heat exchange cycle system according to claim 1, which is characterized in that the heat exchange cycle system further include: first
Shut-off valve and the second shut-off valve；
First shut-off valve be set to the four-way reversing valve second port and the indoor heat-exchanging loop first end it
Between；
Second shut-off valve is set between the second end of the indoor heat-exchanging loop and the 4th end of the subcooler.
4. heat exchange cycle system according to claim 1, which is characterized in that the first end of the subcooler, described second
It is connected between solenoid valve and third solenoid valve by Y-shaped three-way pipe；
The central axis of the Y-shaped three-way pipe is to the distance of the second solenoid valve and the central axis of the Y-shaped three-way pipe described in
Third solenoid valve is equidistant.
5. heat exchange cycle system according to claim 1, which is characterized in that first preset temperature is greater than or equal to 5
DEG C and be less than or equal to 10 DEG C.
6. a kind of air-conditioning, which is characterized in that including the described in any item heat exchange cycle systems of claim 1-3.
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