CN106482376A - Refrigeration or heat pump and its refrigerant circulation amount adjustment method - Google Patents
Refrigeration or heat pump and its refrigerant circulation amount adjustment method Download PDFInfo
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- CN106482376A CN106482376A CN201610813447.XA CN201610813447A CN106482376A CN 106482376 A CN106482376 A CN 106482376A CN 201610813447 A CN201610813447 A CN 201610813447A CN 106482376 A CN106482376 A CN 106482376A
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- heat pump
- adjusting means
- refrigeration
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- 239000003507 refrigerant Substances 0.000 title claims abstract description 183
- 238000005057 refrigeration Methods 0.000 title claims abstract description 68
- 238000000034 method Methods 0.000 title claims abstract description 23
- 239000002826 coolant Substances 0.000 claims abstract description 53
- 230000004907 flux Effects 0.000 claims abstract description 53
- 239000007788 liquid Substances 0.000 claims abstract description 43
- 230000008676 import Effects 0.000 claims abstract description 25
- 230000001502 supplementing effect Effects 0.000 claims abstract description 8
- 238000004781 supercooling Methods 0.000 claims description 64
- 238000001704 evaporation Methods 0.000 claims description 22
- 238000001816 cooling Methods 0.000 claims description 13
- 238000009833 condensation Methods 0.000 claims description 8
- 230000005494 condensation Effects 0.000 claims description 8
- 239000012530 fluid Substances 0.000 claims description 7
- 230000006835 compression Effects 0.000 claims description 2
- 238000007906 compression Methods 0.000 claims description 2
- 238000004891 communication Methods 0.000 abstract description 6
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 24
- 238000010586 diagram Methods 0.000 description 18
- 230000008020 evaporation Effects 0.000 description 14
- 230000005611 electricity Effects 0.000 description 9
- 230000007423 decrease Effects 0.000 description 8
- 238000010257 thawing Methods 0.000 description 7
- 238000010438 heat treatment Methods 0.000 description 6
- 230000000694 effects Effects 0.000 description 5
- 239000008400 supply water Substances 0.000 description 5
- 238000004378 air conditioning Methods 0.000 description 4
- 206010020843 Hyperthermia Diseases 0.000 description 3
- 238000005265 energy consumption Methods 0.000 description 3
- 230000036031 hyperthermia Effects 0.000 description 3
- 102000010637 Aquaporins Human genes 0.000 description 2
- 108010063290 Aquaporins Proteins 0.000 description 2
- 230000033228 biological regulation Effects 0.000 description 2
- 239000000498 cooling water Substances 0.000 description 2
- 238000011084 recovery Methods 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 239000012809 cooling fluid Substances 0.000 description 1
- 239000008358 core component Substances 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
- 239000002699 waste material Substances 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
- F25B41/30—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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/006—Accumulators
-
- 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
-
- 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/029—Control issues
-
- 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
- F25B2600/05—Refrigerant levels
-
- 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)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The invention discloses a kind of refrigeration or heat pump and its refrigerant circulation amount adjustment method, the refrigeration or heat pump include compressor, condenser, first cold medium flux adjusting means, evaporimeter, it is provided with reservoir, the reservoir includes cylinder, refrigerant import pipeline, liquid refrigerants outlet conduit, gaseous coolant outlet pipeline, it is additionally provided with the second cold medium flux adjusting means, the exhaust outlet of compressor, the condenser, the first cold medium flux adjusting means, the refrigerant import pipeline of the reservoir, the liquid refrigerants outlet conduit of the reservoir, the second cold medium flux adjusting means, the evaporimeter, the compressor air suction mouth or gas supplementing opening are sequentially connected in series connection, evaporimeter described in the gaseous coolant outlet pipeline communication of the reservoir.By corresponding control method, the present invention can be controlled to the refrigerant circulation of system, so that system all can reliable, Effec-tive Function under various operating modes.
Description
Technical field
The present invention relates to refrigerating field, more particularly to a kind of refrigeration or heat pump and its refrigerant circulation regulation side
Method.
Background technology
Condenser and evaporimeter are the core components of refrigeration system, when condenser and evaporimeter are in the shape that preferably works
During state, refrigeration system can just be in preferable working condition.Condenser will be in preferable working condition, need tool in condenser
There is preferable refrigerant circulation, evaporimeter will be in preferable working condition, it is also desirable to follow with preferable refrigerant in evaporimeter
Circular rector, when preferable refrigerant circulation is respectively provided with condenser and evaporimeter, refrigeration system just has preferable refrigerant circulation
Amount, so as to possess the condition for making refrigeration system in ideal operation state.
However, there is more problem in prior art, such as：
One, in refrigeration system, if condensing pressure is higher, compressor exhaust temperature can rise, and compression ratio increases, and refrigerating capacity subtracts
Few, power consumption increases, and condensing pressure is higher, is also easy to cause equipment breakage event.If condensing pressure is too low, particularly in the winter time,
Environment temperature or cooling water temperature relatively low, cause condensing pressure too low, so that pressure differential is too little before and after heating power expansion valve, for surging
Power is not enough, causes the refrigerant flow for flowing through heating power expansion valve drastically to reduce, substantially reduces refrigerating capacity, or even refrigerating plant work
Lack of proper care.In addition, the compressor of most producers, also has the use requirement of minimum condensing pressure, or even with evaporating pressure
Difference, minimum condensing pressure require also different.Therefore, it is the reliably working that ensures refrigeration system and compressor, it is necessary to condensation
Pressure implements control.The control method of condensing pressure, prior art mainly have two kinds：1st, control cooling water flow or cooling wind
Amount, for air-cooled, conventional has：A) fan motor speed change；B) air-valve control and regulation cooling air delivery；C) condensation fan
Open, stop control, these methods are applied more effective higher than more than 4 DEG C occasions in long-term environment temperature；2nd, adopt from refrigerant side
Bypass control method controls refrigerant pressure, and concrete connected mode is：One septum valve is installed in condensator outlet, high pressure is adjusted
The other end connection reservoir entrance of section valve, in exhaust outlet of compressor and the indirect bypass pipe of reservoir entrance, on bypass pipe
Differential pressure control valve is installed.
Using both the above method, the heat-energy transducer of refrigeration system condenser and blower fan (or water pump) when working cold season
Power is not fully used, and Energy Efficiency Ratio is still relatively low, with warm season or even summer when compared with, relatively.Because blower fan
Or the energy consumption of water pump only about accounts for the 10% of system total energy consumption, and the energy consumption of compressor can about account for 90%.
Two, in condensing units refrigeration system, during using heat recovery mode, with being stepped up for hot water temperature, be
Controlling cold progressively declines, thus or cause users'comfort decline, or refrigerating capacity deficiency cause food temperature rise,
So that need the unit of bigger ability is installed, but in system, the ability of outdoor heat exchanger is not obtained by, if outdoor can be made
Heat exchanger becomes subcooler in system operation heat recovery mode, and with the rising of hot water temperature, the refrigerating capacity of system is hardly
Can decline.
Three, for air-conditioning hot water integrated machine (trilogy supply), in the winter time during water heating, with being stepped up for hot water temperature,
The total heating capacity of system hardly increases or progressively declines.
Four, when air-conditioning is defrosted in the winter time, condensing pressure is low, and defrosting effect is bad.Conventional refrigerating refrigeration system
During using reverse hot gas defrosting, condensing pressure is equally low, and defrosting effect is bad.
Five, the impact of the refrigerant filling quantity of air-conditioner refrigerating system to household air-conditioner is very big, varying environment temperature, difference
When running under operating mode and different compressors frequency load, air-conditioner reaches the coolant quantity of optimal energy efficiency state needs and differs,
For example, during high frequency high load capacity, the coolant quantity of needs is more, and during low frequency underload, the coolant quantity of needs is less.But air-conditioner system
Used as the system of a closing, it is certain to be filled in coolant quantity therein to cooling system.The refrigerant filling quantity of air-conditioner is usually
Determined with design conditions, and the operating condition of reality often off-design operating mode, so, even if with design conditions
Also inevitably there is the filling quantity produced because of working conditions change relatively more or less the air-conditioner that charges in Optimum charge
Problem, so as to affect the Energy Efficiency Ratio of actual motion, cause the waste of energy.
Content of the invention
It is an object of the invention to solving the above problems.
Technical scheme is as follows：
A kind of refrigeration or heat pump, comprising compressor, condenser, the first cold medium flux adjusting means, evaporimeter, are arranged
There is reservoir, the reservoir includes cylinder, refrigerant import pipeline, liquid refrigerants outlet conduit, gaseous coolant outlet pipeline, also
It is provided with the second cold medium flux adjusting means；The refrigeration or heat pump are comprising refrigeration or heat pump circuit, the refrigeration or warm
Pump loop at least by the compressor, the condenser, the first cold medium flux adjusting means, the reservoir, described
Two cold medium flux adjusting meanss, the evaporimeter are sequentially connected in series connection and form, and wherein, the first cold medium flux adjusting means sets
Put on the refrigerant import pipeline of the reservoir or with the pipeline of the refrigerant import pipeline communication of the reservoir on, described
Second cold medium flux adjusting means is arranged on the liquid on the liquid refrigerants outlet conduit of the reservoir or with the reservoir
On the pipeline of state refrigerant exit pipeline communication, the evaporimeter connects the air entry of the compressor or gas supplementing opening；The liquid storage
From the second cold medium flux adjusting means to described in refrigeration described in the gaseous coolant outlet pipeline communication of device or heat pump circuit
Refrigerant passage between compressor air suction mouth or gas supplementing opening.
Preferential, cold between evaporimeter and the compressor described in the gaseous coolant outlet pipeline communication of the reservoir
Matchmaker's passage.
Preferential, the first cold medium flux adjusting means and the second cold medium flux adjusting means are all electronic expansions
Valve.
Further, four-way change-over valve is additionally provided with, the four-way change-over valve has d mouth, e mouth, s mouth, four connections of c mouth
Mouthful, when the four-way change-over valve is in first operating position, its d mouth is connected with c mouth and e mouth is connected with s mouth, and the four-way is changed
To valve in second operating position when, its d mouth is connected with e mouth and c mouth is connected with s mouth；The exhaust outlet connection of the compressor
The d mouth of the four-way change-over valve, the air entry of the compressor connect the s mouth of the four-way change-over valve, the gas of the reservoir
Refrigerant passage described in state refrigerant exit pipeline communication between the s mouth of four-way change-over valve and the compressor air suction mouth.
Preferential, the refrigerant import of the liquid refrigerants outlet conduit of the reservoir in the cylinder is located at the cylinder
The latter half in interior space, the refrigerant import of the gaseous coolant outlet pipeline of the reservoir in the cylinder are located at the cylinder
The top half in internal space.
The refrigerant circulation amount adjustment method of refrigeration or heat pump according to any of the above-described is：
During the refrigeration or heat pump are run along the refrigeration or heat pump circuit, when needing to increase the system
During the refrigerant circulation of cold or heat pump, adjust the first cold medium flux adjusting means and second cold medium flux is adjusted
Device at least one so that liquid level in the reservoir declines, when needing to reduce the cold of the refrigeration or heat pump
During matchmaker's internal circulating load, adjust the first cold medium flux adjusting means and the second cold medium flux adjusting means at least within it
One, so that the liquid level in the reservoir rises.
Preferential, control described the according at least to one of them the described parameter of following 7.1,7.2,7.3,7.4 and 7.5
One in one cold medium flux adjusting means and the second cold medium flux adjusting means：7.1) described refrigeration or heat pump circuit in
The degree of supercooling of the condenser to certain between the first cold medium flux adjusting means；7.2) refrigeration or heat pump
Condensing pressure or condensation temperature；7.3) delivery temperature of the compressor or case temperature or internal temperature；7.4) it is described
The fluid temperature (F.T.) of condenser cooling and the condensation temperature of the condenser；7.5) be the condenser cooling fluid temperature (F.T.) and institute
State the outlet temperature of condenser.
Further, control according at least to one of them the described parameter of following 8.1,8.2,8.3,8.4,8.5 and 8.6
Another in the first cold medium flux adjusting means and the second cold medium flux adjusting means：8.1) refrigeration or heat
From the evaporator outlet to the degree of supercooling of certain between the compressor in pump loop；8.2) refrigeration or heat pump
Evaporating pressure or evaporating temperature；8.3) it is the fluid temperature (F.T.) of evaporimeter cooling and the evaporating temperature of the evaporimeter；
8.4) it is the fluid temperature (F.T.) of evaporimeter cooling and the outlet temperature of the evaporimeter；8.5) delivery temperature of the compressor
Or case temperature or internal temperature；8.6) discharge superheat of the compressor.
Preferential, when the degree of supercooling of the condensator outlet refrigerant is less than under desired value set in advance or target interval
During limit value, reduce the aperture of the first cold medium flux adjusting means, or increase the second cold medium flux adjusting means
Aperture；When the higher limit that the degree of supercooling of the condensator outlet refrigerant is higher than desired value set in advance or target interval, increase
Plus the aperture of the first cold medium flux adjusting means, or the aperture for reducing the second cold medium flux adjusting means.
Preferential, during the refrigeration or heat pump are run along the refrigeration or heat pump circuit, when needs subtract
Refrigerant circulation in the little condenser and when needing to increase the refrigerant circulation in the evaporimeter, increases described first cold
The aperture of matchmaker's flow regulator；When the refrigerant circulation for needing to reduce in the condenser and need to reduce in the evaporimeter
Refrigerant circulation when, reduce the aperture of the second cold medium flux adjusting means；Cold in the condenser when needing to increase
Matchmaker's internal circulating load and when needing to reduce the refrigerant circulation in the evaporimeter, reduces opening for the first cold medium flux adjusting means
Degree；When the refrigerant circulation for needing to increase in the condenser and when needing to increase the refrigerant circulation in the evaporimeter, increase
Plus the aperture of the second cold medium flux adjusting means.
Based on technique scheme, the present invention can be controlled to the internal circulating load of cold-producing medium in refrigeration or heat pump,
So that refrigeration or heat pump all can reliable, Effec-tive Function under various operating modes.
Description of the drawings
Fig. 1 is the theory of constitution schematic diagram of reservoir first embodiment in present invention refrigeration or heat pump.
Fig. 2 is the theory of constitution schematic diagram of reservoir second embodiment in present invention refrigeration or heat pump.
Fig. 3 is present invention refrigeration or the theory of constitution schematic diagram of heat pump first embodiment.
Fig. 4 is present invention refrigeration or the theory of constitution schematic diagram of heat pump second embodiment.
Fig. 5 is present invention refrigeration or the theory of constitution schematic diagram of heat pump 3rd embodiment.
Fig. 6 is present invention refrigeration or the theory of constitution schematic diagram of heat pump fourth embodiment.
Fig. 7 is present invention refrigeration or the theory of constitution schematic diagram of the 5th embodiment of heat pump.
Fig. 8 is present invention refrigeration or the theory of constitution schematic diagram of heat pump sixth embodiment.
Fig. 9 is present invention refrigeration or the theory of constitution schematic diagram of the 7th embodiment of heat pump.
Specific embodiment
Below in conjunction with drawings and Examples, technical scheme is described in further detail.
As shown in figure 1, the theory of constitution schematic diagram for reservoir first embodiment in present invention refrigeration or heat pump.Its
In, 50 is cylinder, and 51 is refrigerant import pipe, and 52 is liquid refrigerants outlet, and 53 is gaseous coolant outlet pipe, and 520 is that liquid is cold
Import of matchmaker's outlet in cylinder 50,530 is import of the gaseous coolant outlet pipe in cylinder 50.
As shown in Fig. 2 the theory of constitution schematic diagram for reservoir second embodiment in present invention refrigeration or heat pump.Its
In, 50 is cylinder, in 51 and 52：One is refrigerant import pipe, and another is liquid refrigerants outlet, and can exchange, 53
For gaseous coolant outlet pipe, 510 is import and export of the pipeline 51 in cylinder 50, and 520 is import and export of the pipeline 52 in cylinder 50,
530 is import of the gaseous coolant outlet pipe in cylinder 50.
As shown in figure 3, for the present invention freeze or heat pump first embodiment theory of constitution schematic diagram.Wherein, 10 are
Compressor, 20 is condenser, and 30,31 are electric expansion valve, and 40 is evaporimeter, and 5 is reservoir (the using above-mentioned reservoir
One embodiment).The exhaust outlet of compressor 10, condenser 20, electric expansion valve 30, the refrigerant import pipe 51, reservoir of reservoir 5
5 liquid refrigerants outlet 52, electric expansion valve 31, evaporimeter 40, the air entry of compressor 10 are sequentially connected in series connection, reservoir
5 gaseous coolant outlet pipe 53 connects evaporimeter 40 and exports and the pipeline between 10 air entry of compressor.
During system operation, the HTHP refrigerant that compressor 10 is exported initially enters condenser 20, and in condenser 20
Radiating is changed into highly pressurised liquid output, then throttles through electric expansion valve 30, is changed into the two-phase refrigerant of middle pressure, then through refrigerant import
Pipe 51 enters reservoir 5, and in reservoir 5, in bottom, on top, the liquid refrigerants of middle pressure is from liquid for gaseous coolant for liquid refrigerants
Refrigerant exit pipe 52 enters electric expansion valve 31 after exporting and throttles further, is changed into the two-phase refrigerant of low-temp low-pressure, subsequently into
In evaporimeter 40, and evaporation of absorbing heat in heat exchanger 40 indoors is changed into overheated gas output, then returns to the air-breathing of compressor 10
Mouthful, after the middle pressure gaseous coolant in reservoir 5 is exported through gaseous coolant outlet pipe 53, with the overheated gas exported from evaporimeter 40
Refrigerant returns to the air entry of compressor 10 together.
Current embodiment require that it is noted that during 31 standard-sized sheet of electric expansion valve, the gaseous coolant in reservoir 5 with evaporimeter
The passage passed through before collecting by the refrigerant of 40 outlets has relatively small negotiability, during 31 standard-sized sheet of electric expansion valve, needs
Ensure that the gaseous coolant amount exported from gaseous coolant outlet pipe 53 in reservoir 5 under each operating mode is not more than from refrigerant import pipe 51
The gaseous coolant amount of generation.Certainly, 30 aperture of electric expansion valve larger and mainly by electric expansion valve 31 throttle when, will also
Ensure that the gaseous coolant amount exported from gaseous coolant outlet pipe 53 in reservoir 5 under each operating mode is not less than to give birth to from refrigerant import pipe 51
The gaseous coolant amount for becoming, but now by the pressure in the little and reservoir 5 of flash gas produced after electric expansion valve 30
Power is higher, so comparatively, it is logical that the gaseous coolant in reservoir 5 is passed through before the refrigerant exported with evaporimeter 40 is collected
Road always has relatively small negotiability.
The first operation method of the present embodiment is that the degree of superheat for exporting refrigerant by evaporimeter 40 controls expansion valve 30
Aperture, the degree of supercooling for exporting refrigerant by condenser 20 control the aperture of electric expansion valve 31.When the refrigerant that condenser 20 is exported
Without degree of supercooling or degree of supercooling less than normal when, increase electric expansion valve 31 aperture, the reduced pressure in reservoir 5, by gas
The gaseous coolant amount that state refrigerant exit pipe 53 is exported diminishes, and the liquid level in reservoir 5 begins to decline, the refrigerant that condenser 20 is exported
Start supercooling occur or degree of supercooling is increasing.When the refrigerant degree of supercooling that condenser 20 is exported is bigger than normal, reduce electronic expansion
The aperture of valve 31, the pressure in reservoir 5 begin to ramp up, from the gaseous coolant increased flow capacity that gaseous coolant outlet pipe 53 is exported,
Liquid level in reservoir 5 begins to ramp up, and the refrigerant degree of supercooling that condenser 20 is exported diminishes.When condenser 20 exports the supercooling of refrigerant
Degree can maintain the aperture of electric expansion valve 31 constant in target zone or when being equal to desired value.So, condenser 20 goes out
The refrigerant of mouth has preferable degree of supercooling, and the refrigerant that evaporimeter 40 is exported has the preferable degree of superheat, and system can be run with high efficient and reliable.
Second operation method of the present embodiment is that the degree of superheat for exporting refrigerant by evaporimeter 40 controls expansion valve 31
Aperture, the degree of supercooling for exporting refrigerant by condenser 20 control the aperture of electric expansion valve 30.When the refrigerant that condenser 20 is exported
Without degree of supercooling or degree of supercooling less than normal when, reduce electric expansion valve 30 aperture, the reduced pressure in reservoir 5, by gas
The gaseous coolant amount that state refrigerant exit pipe 53 is exported diminishes, and the liquid level in reservoir 5 begins to decline, the refrigerant that condenser 20 is exported
Start supercooling occur or degree of supercooling is increasing.When the refrigerant degree of supercooling that condenser 20 is exported is bigger than normal, increase electronic expansion
The aperture of valve 30, the pressure in reservoir 5 begin to ramp up, from the gaseous coolant increased flow capacity that gaseous coolant outlet pipe 53 is exported,
Liquid level in reservoir 5 begins to ramp up, and the refrigerant degree of supercooling that condenser 20 is exported diminishes.When condenser 20 exports the supercooling of refrigerant
Degree can maintain the aperture of electric expansion valve 30 constant in target zone or when being equal to desired value.So, condenser 20 goes out
The refrigerant of mouth has preferable degree of supercooling, and the refrigerant that evaporimeter 40 is exported has the preferable degree of superheat, and system can be run with high efficient and reliable.
The third operation method of the present embodiment is that the degree of supercooling for exporting refrigerant by condenser 20 controls electric expansion valve
30 and 31 aperture.When the refrigerant that condenser 20 is exported does not have degree of supercooling or degree of supercooling is less than normal, reduce electric expansion valve 30
Aperture and increase the aperture of electric expansion valve 31, the reduced pressure in reservoir 5, exported by gaseous coolant outlet pipe 53
Gaseous coolant amount diminishes, and the liquid level in reservoir 5 begins to decline, and the refrigerant that condenser 20 is exported starts supercooling occur or is subcooled
Degree is increasing.When the refrigerant degree of supercooling that condenser 20 is exported is bigger than normal, increases the aperture of electric expansion valve 30 and reduce electronics
The aperture of expansion valve 31, the pressure in reservoir 5 begin to ramp up, and the gaseous coolant flow exported from gaseous coolant outlet pipe 53 adds
Greatly, the liquid level in reservoir 5 begins to ramp up, and the refrigerant degree of supercooling that condenser 20 is exported diminishes.When condenser 20 exports refrigerant
Degree of supercooling can maintain the aperture of electric expansion valve 30 and 31 constant in target zone or when being equal to desired value.So, cold
The refrigerant that condenser 20 is exported has preferable degree of supercooling, and system can be run with high efficient and reliable.
The 4th kind of operation method of the present embodiment is to export the degree of superheat of refrigerant by evaporimeter 40 and condenser 20 is exported
The degree of supercooling of refrigerant comes together to control the aperture of electric expansion valve 30 and 31, when the degree of supercooling of the outlet refrigerant of condenser 20 is higher
When, increase the aperture of electric expansion valve 30 and reduce the aperture of electric expansion valve 31, when condenser 20 exports the degree of supercooling of refrigerant
When low, reduce the aperture of electric expansion valve 30 and increase the aperture of electric expansion valve 31, refer to the third operation side above-mentioned
Method；When the degree of superheat that evaporimeter 40 exports refrigerant is higher, the aperture of electric expansion valve 30 and 31 is synchronously increased, when evaporimeter 40
When the degree of superheat of outlet refrigerant is low, the aperture of electric expansion valve 30 and 31 synchronously reduces；When condenser 20 exports the mistake of refrigerant
When the degree of superheat of cold degree higher and evaporimeter 40 outlet refrigerant is higher, increase the aperture of electric expansion valve 30；When condenser 20 goes out
When the degree of superheat of the degree of supercooling higher and evaporimeter 40 outlet refrigerant of mouth refrigerant is low, reduce the aperture of electric expansion valve 31；When
When the degree of superheat of the degree of supercooling low and evaporimeter 40 outlet refrigerant of the outlet refrigerant of condenser 20 is low, reduce electric expansion valve 30
Aperture；When the degree of superheat that the low and evaporimeter 40 of degree of supercooling that condenser 20 exports refrigerant exports refrigerant is higher, increase electricity
The aperture of sub- expansion valve 31.As such, it is possible to the refrigerant for exporting condenser 20 has preferable degree of supercooling, it is cold that evaporimeter 40 is exported
Matchmaker has the preferable degree of superheat, and system can be run with high efficient and reliable.
Certainly, the present embodiment runs far deeper than and operates above control method, and here will not enumerate.
In addition, for the refrigeration system of year round cooling, if air-cooled condenser, with the outdoor that condenser 20 is located
Environment temperature reduces, and condensing pressure can be than relatively low, the minimum pressure of even below compressor producer suggestion.At this moment, need to cold
Solidifying pressure is controlled.During system operation, if electric expansion valve 30 is only used for the degree of superheat for controlling evaporimeter 40 to export refrigerant,
So when condensing pressure is low, increase the aperture of electric expansion valve 31, the reduced pressure in reservoir 5, by gaseous coolant
The gaseous coolant amount that outlet 53 is exported diminishes, and the liquid level in reservoir 5 begins to decline, and condensing pressure is increasing.Work as condensation
Pressure is in minimum target zone or when being equal to minimum setting value, if the degree of supercooling that condenser 20 exports refrigerant is not less than mesh
When the lower limit or desired value of mark scope, the aperture of electric expansion valve 31 can be maintained constant.When condensing pressure is beyond minimum
Target zone or when being higher by minimum setting value, exports the degree of supercooling of refrigerant to control electric expansion valve 31 according to condenser 20
Aperture.As such, it is possible to make year round cooling system various complex conditions efficiently, reliability service.
As shown in figure 4, for the present invention freeze or heat pump second embodiment theory of constitution schematic diagram.The present embodiment with
A upper embodiment is very close to difference is：In the present embodiment, the connection electronics of gaseous coolant outlet pipe 53 of reservoir 5 is swollen
Connecting pipe between swollen valve 31 and evaporimeter 40.Ruuning situation may be referred to an embodiment.
As shown in figure 5, for the present invention freeze or heat pump 3rd embodiment theory of constitution schematic diagram.Wherein, 10 are
Compressor (with exhaust outlet, air entry and gas supplementing opening), 20 is condenser, and 30,31 are electric expansion valve, and 40 is evaporation supercooling
Device, 41 is main evaporator, and 5 is reservoir (using the first embodiment of above-mentioned reservoir), and 32 is expansion valve.The row of compressor 10
Gas port, condenser 20, electric expansion valve 30, the refrigerant import pipe 51 of reservoir 5, the liquid refrigerants outlet 52 of reservoir 5, electricity
Sub- expansion valve 31, the evaporation side of evaporation subcooler 40, the gas supplementing opening of compressor 10 are sequentially connected in series connection, and the gaseous state of reservoir 5 is cold
Matchmaker's outlet 53 connects evaporation subcooler 40 and evaporates the pipeline between side outlet and 10 gas supplementing opening of compressor.From condenser 20 and electricity
Connecting pipe between sub- expansion valve 30 also separates a pipeline, and the pipeline is sequentially connected in series the supercooling of connection evaporation subcooler 40
Side, expansion valve 32, after main evaporator 41, connect the air entry of compressor 10.
In the present embodiment, expansion valve 32 controls main evaporator 41 to export the degree of superheat of refrigerant, can make electric expansion valve 30
Control evaporation subcooler 40 evaporates the degree of superheat of side outlet refrigerant, and electric expansion valve 31 controls condenser 20 to export the supercooling of refrigerant
Degree, same the invention described above refrigeration or heat pump first embodiment, it is also possible to make the control evaporation subcooler of electric expansion valve 31
The degree of superheat of 40 evaporation side outlet refrigerants, electric expansion valve 30 control condenser 20 to export the degree of supercooling of refrigerant.
For year round cooling system, when the environment temperature residing for condenser 20 is relatively low, can equally control condenser 20
Condensing pressure or condensation temperature.
As shown in fig. 6, for the present invention freeze or heat pump fourth embodiment theory of constitution schematic diagram.The present embodiment with
The difference of the invention described above refrigeration or heat pump first embodiment is：In the present embodiment, compressor 10 also has second vapor injection
Mouthful, expansion valve 33 and evaporation subcooler 42 is therefore also provided with the present embodiment, the outlet of condenser 20 is divided into two-way, the first via
Mistake cold side through evaporating subcooler 42 connects electric expansion valve 30, and the second tunnel sequentially passes through expansion valve 33 and evaporation subcooler 42
Evaporation side connection compressor 10 intermediate fill gas mouth.
In the present embodiment, expansion valve 33 controls evaporation subcooler 42 to evaporate the degree of superheat of side outlet refrigerant, and other are with above-mentioned
Present invention refrigeration or heat pump first embodiment.
As shown in fig. 7, for the present invention freeze or the 5th embodiment of heat pump theory of constitution schematic diagram.The present embodiment with
The difference of the invention described above refrigeration or heat pump first embodiment is：Double-tube heat exchanger 21 is increased in the present embodiment, set
The refrigerant passage of heat exchange of heat pipe 21 is serially connected in the connecting pipe between compressor 10 and condenser 20, and its aquaporin is serially connected with confession
Water pump 71.
When water pump 71 does not run, the present embodiment has the operation mould of the invention described above refrigeration or heat pump first embodiment
Formula, its operation can also be freezed with reference to the invention described above or heat pump first embodiment.
But, many operational modes of a recuperation of heat of the present embodiment, under the pattern, supply-water pump 71 runs, electronic expansion
The aperture of valve 30 or 31 be according to the outlet of double-tube heat exchanger 21 refrigerant passage refrigerant degree of supercooling controlling, details are referred to
In above-mentioned refrigeration or heat pump first embodiment, control condenser 20 exports the explanation of refrigerant degree of supercooling.At this moment, sleeve heat exchange
Device 21 is substantially increased as subcooler (heat exchange blower fan of condenser 20 or water pump will be opened) as condenser, condenser 20
System effectiveness.
Additionally, the present embodiment can also increase a pattern for producing high-temperature-hot-water, under this kind of pattern, ruuning situation reference
The invention described above refrigeration or heat pump first embodiment, but supply-water pump 71 is to open, as such, it is possible to be discharged with compressor 10
Hyperthermia and superheating refrigerant the water in double-tube heat exchanger 21 is heated, produce high-temperature-hot-water.
As shown in figure 8, for the present invention freeze or heat pump sixth embodiment theory of constitution schematic diagram.Wherein, 10 are
Compressor, 20 is outdoor heat exchanger, and 30,31 are electric expansion valve, and 40 is indoor heat exchanger, and 5 is reservoir (using above-mentioned storage
The second embodiment of liquid device), 81 is four-way change-over valve, and 82 is gas-liquid separator.Four-way change-over valve 81 has d mouth, e mouth, s mouth, c
Four connectors of mouth, during 81 power-off of four-way change-over valve, d mouth is connected with c mouth and e mouth is connected with s mouth, electricity on four-way change-over valve 81
When, d mouth is connected with e mouth and c mouth is connected with s mouth.The d mouth of the exhaust outlet connection four-way change-over valve 81 of compressor 10, four-way commutate
The s mouth of valve 81 connects the air entry of compressor 10 together with the gaseous coolant outlet pipe 53 of reservoir 5 through gas-liquid separator 82,
The c mouth of four-way change-over valve 81, outdoor heat exchanger 20, electric expansion valve 30, the connecting tube 51 of reservoir 5, the connecting tube of reservoir 5
52nd, electric expansion valve 31, indoor heat exchanger 40, the e mouth of four-way change-over valve 81 are sequentially connected in series connection.
During system operation, to 81 power-off of four-way change-over valve, the HTHP refrigerant that compressor 10 is exported sequentially passes through four-way
The d mouth of reversal valve 81, c mouth enter outdoor heat exchanger 20, and radiating is changed into highly pressurised liquid output in outdoor heat exchanger 20, then
Throttle through electric expansion valve 30, be changed into the two-phase refrigerant of middle pressure, then reservoir 5, reservoir 5 entered through refrigerant import pipe 51
In, liquid refrigerants enters electricity in top, the liquid refrigerants of middle pressure in bottom, gaseous coolant from after the output of liquid refrigerants outlet 52
Sub- expansion valve 31 is throttled further, is changed into the two-phase refrigerant of low-temp low-pressure, subsequently in indoor heat exchanger 40, and is changed indoors
In hot device 40, heat absorption evaporation is changed into overheated gas output, then sequentially passes through the e mouth of four-way change-over valve 81, s mouth, gas-liquid separator
82, eventually pass back to the air entry of compressor 10, the gaseous coolant in reservoir 5 through gaseous coolant outlet pipe 53 output after, with from
The overheated gas refrigerant exported in the s mouth of four-way change-over valve 81 returns to the air-breathing of compressor 10 together through gas-liquid separator 82
Mouthful.
Wherein it is possible to the aperture of the degree of superheat control electric expansion valve 30 of refrigerant is exported according to indoor heat exchanger 40, according to
Outdoor heat exchanger 20 exports the aperture of the degree of supercooling control electric expansion valve 31 of refrigerant.When the refrigerant that outdoor heat exchanger 20 is exported does not have
Have degree of supercooling or degree of supercooling less than normal when, increase electric expansion valve 31 aperture, the reduced pressure in reservoir 5, by gaseous state
The gaseous coolant amount that refrigerant exit pipe 53 is exported diminishes, and the liquid level in reservoir 5 begins to decline, and it is cold that outdoor heat exchanger 20 is exported
Matchmaker starts supercooling occur or degree of supercooling is increasing.When the refrigerant degree of supercooling that outdoor heat exchanger 20 is exported is bigger than normal, reduce electricity
The aperture of sub- expansion valve 31, the pressure in reservoir 5 begin to ramp up, from the gaseous coolant flow that gaseous coolant outlet pipe 53 is exported
Increase, the liquid level in reservoir 5 begins to ramp up, the refrigerant degree of supercooling that outdoor heat exchanger 20 is exported diminishes.When outdoor heat exchanger 20
When the degree of supercooling of outlet refrigerant is in target zone or equal to setting value, the aperture of electric expansion valve 31 can be maintained constant.This
Sample, the refrigerant that outdoor heat exchanger 20 is exported have preferable degree of supercooling, and the refrigerant that indoor heat exchanger 40 is exported has the preferable degree of superheat,
System can be run with high efficient and reliable.In the same manner, it is also possible to which electronic expansion is controlled according to the degree of superheat that indoor heat exchanger 40 exports refrigerant
The aperture of valve 31, exports the aperture of the degree of supercooling control electric expansion valve 30 of refrigerant, and makes system high according to outdoor heat exchanger 20
Effect reliability service.
During system operation, to electricity on four-way change-over valve 81, then indoor heat exchanger 40 does condenser use, and outdoor heat exchanger 20 does
Evaporimeter is used, and at this moment, outdoor heat exchanger 20 can be controlled to export the degree of superheat of refrigerant by electric expansion valve 31, and be passed through electronics
Expansion valve 30 controls indoor heat exchanger 40 to export the degree of supercooling of refrigerant, it is also possible to control outdoor heat exchanger by electric expansion valve 30
The degree of superheat of 20 outlet refrigerants, and control indoor heat exchanger 40 to export the degree of supercooling of refrigerant by electric expansion valve 31, details can
Explanation with reference to the preceding paragraph.
Upper two sections of explanation, more satisfactory for household air conditioning device.In addition, the domestic air conditioning of routine, in the winter time
When defrosting to outdoor heat exchanger, the condensing pressure in outdoor heat exchanger is very low, and defrosting effect is bad, and in the present embodiment,
The condensing pressure of outdoor heat exchanger 20 when winter is defrosted to outdoor heat exchanger 20, can be controlled, defrosting effect is lifted, specifically
Operation method is as follows：During defrosting, to during 81 power-off of four-way change-over valve in the circulation route of cold-producing medium and the present embodiment in system
Circulation route is the same, if electric expansion valve 30 is only used for the degree of superheat for controlling indoor heat exchanger 40 to export refrigerant, then, when cold
When solidifying pressure is low, increase the aperture of electric expansion valve 31, the reduced pressure in reservoir 5, by gaseous coolant outlet pipe 53
The gaseous coolant amount of output diminishes, and the liquid level in reservoir 5 begins to decline, and the condensing pressure in outdoor heat exchanger 20 becomes big.When
Condensing pressure in outdoor heat exchanger 20 is in target zone or when being equal to setting value, if outdoor heat exchanger 20 exports refrigerant
Degree of supercooling be not less than lower limit or the desired value of target zone, the aperture of electric expansion valve 31 can be maintained constant.When cold
When solidifying pressure exceeds target zone or is higher by setting value, electronic expansion is controlled according to the degree of supercooling of the outlet refrigerant of condenser 20
The aperture of valve 31, referring to the present embodiment preceding sections.As such, it is possible to make system efficient, reliability service under various operating modes.
As shown in figure 9, for the present invention freeze or the 7th embodiment of heat pump theory of constitution schematic diagram.The present embodiment with
The difference of a upper embodiment is：Double-tube heat exchanger 21, the refrigerant passage of double-tube heat exchanger 21 is increased in the present embodiment
It is serially connected in the connecting pipe between the exhaust outlet of compressor 10 and the d mouth of four-way change-over valve 81, its aquaporin is serially connected with water supply
Pump 71.
When the sheet 71 that supplies water is not run, the present embodiment has and upper embodiment identical operational mode, and its operation can also
With reference to a upper embodiment.
But, when to 81 power-off of four-way change-over valve, the operational mode of a recuperation of heat more than the present embodiment, the pattern
Under, supply-water pump 71 runs, and the aperture of electric expansion valve 30 or 31 is the refrigerant mistake according to the outlet of 21 refrigerant passage of double-tube heat exchanger
Come controlled, details are referred to the explanation that control condenser 20 in an embodiment exports refrigerant degree of supercooling to cold degree.At this moment, cover
Heat exchange of heat pipe 21 as condenser, outdoor heat exchanger 20 as subcooler (heat exchange blower fan of heat exchanger 20 or water pump will be opened),
Substantially increase system effectiveness.
Additionally, when to 81 power-off of four-way change-over valve, the present embodiment can also be further added by a pattern for producing high-temperature-hot-water,
Under this kind of pattern, ruuning situation is with reference to the explanation in a upper embodiment to 81 power-off of four-way change-over valve, but supply-water pump 71 is to open
, as such, it is possible to the hyperthermia and superheating refrigerant that is discharged with compressor 10 is heated to the water in double-tube heat exchanger 21, produce high temperature
Hot water.
Equally, when to electricity on four-way change-over valve 81, many one of the present embodiment heats the pattern for adding hot water, the pattern
Under, supply-water pump 71 runs, and the aperture of electric expansion valve 30 or 31 is the refrigerant mistake according to the outlet of 21 refrigerant passage of double-tube heat exchanger
Controlling, at this moment, used as condenser, indoor heat exchanger 40 is used as subcooler (the changing of heat exchanger 40 for double-tube heat exchanger 21 for cold degree
Air-heater will be opened), substantially increase heating capacity and the efficiency of system.
Additionally, on to four-way change-over valve 81 during electricity, the present embodiment can also be further added by a pattern for producing high-temperature-hot-water,
Under this kind of pattern, refrigerant degree of supercooling that the aperture of electric expansion valve 30 or 31 is exported according to indoor heat exchanger 40 is controlling, but supplies
Water pump 71 is to open, as such, it is possible to the hyperthermia and superheating refrigerant that is discharged with compressor 10 is carried out to the water in double-tube heat exchanger 21
Heating, produces high-temperature-hot-water.
Finally it should be noted that：Above example is merely to illustrate technical scheme rather than a limitation, institute
Category technical field it is to be appreciated by one skilled in the art that still can be to the specific embodiment of the present invention and application scenario or field
Modify or equivalence replacement is carried out to some technical characteristics.So, without departing from the spirit of technical solution of the present invention, all
Should cover in the middle of the technical scheme scope that the present invention is claimed.
Claims (10)
1. one kind is freezed or heat pump, comprising compressor (10), condenser (20,21,40), the first cold medium flux adjusting means
(30,31), evaporimeter (40,20), it is characterised in that：
Reservoir (5) is provided with, described reservoir (5) go out comprising cylinder (50), refrigerant import pipeline (51,52), liquid refrigerants
Mouth pipeline (52,51), gaseous coolant outlet pipeline (53)；
It is provided with the second cold medium flux adjusting means (31,30)；
Comprising refrigeration or heat pump circuit, the refrigeration or heat pump circuit at least by the compressor (10), the condenser (20,
21st, 40), described first cold medium flux adjusting means (30,31), the reservoir (5), the second cold medium flux adjusting means
(31,30), the evaporimeter (40,20) are sequentially connected in series connection and form, wherein, the first cold medium flux adjusting means (30,
31) the upper or refrigerant import pipe with the reservoir (5) of refrigerant import pipeline (51,52) of the reservoir (5) is arranged on
On the pipeline that road (51,52) is connected, the second cold medium flux adjusting means (31,30) are arranged on the liquid of the reservoir (5)
The pipeline for connecting on state refrigerant exit pipeline (52,51) or with the liquid refrigerants outlet conduit (52,51) of the reservoir (5)
On, described evaporimeter (40,20) connect the air entry of compressor (10) or gas supplementing opening；
The gaseous coolant outlet pipeline (53) of reservoir (5) is connected in the refrigeration or heat pump circuit from second refrigerant
Flow regulator (31,30) is to the refrigerant passage of compressor (10) between air entry or gas supplementing opening.
2. one kind according to claim 1 is freezed or heat pump, it is characterised in that：
The gaseous coolant outlet pipeline (53) connection evaporimeter (40,20) and the compressor (10) of reservoir (5)
Between refrigerant passage.
3. one kind according to claim 2 is freezed or heat pump, it is characterised in that：
First cold medium flux adjusting means (30,31) and the second cold medium flux adjusting means (31,30) are all electronics
Expansion valve.
4. one kind according to claim 3 is freezed or heat pump, it is characterised in that：
Four-way change-over valve (81) is provided with, described four-way change-over valve (81) have d mouth, e mouth, s mouth, four connectors of c mouth, described
When four-way change-over valve (81) is in first operating position, its d mouth is connected with c mouth and e mouth is connected with s mouth, the four-way commutation
When valve (81) is in second operating position, its d mouth is connected with e mouth and c mouth is connected with s mouth；
The exhaust outlet of compressor (10) connects the d mouth of four-way change-over valve (81)；
The air entry of compressor (10) connects the s mouth of four-way change-over valve (81)；
The gaseous coolant outlet pipeline (53) of reservoir (5) connects the s mouth of four-way change-over valve (81) and the compression
Refrigerant passage between machine (10) air entry.
5. the one kind according to any one of Claims 1-4 is freezed or heat pump, it is characterised in that：
Refrigerant import (520,510) of the liquid refrigerants outlet conduit (52,51) of reservoir (5) in the cylinder (50)
Positioned at the latter half in the interior space of the cylinder (50), the gaseous coolant outlet pipeline (53) of reservoir (5) is in the cylinder
Refrigerant import (530) in body (50) is located at the top half in cylinder (50) interior space.
6. the refrigerant circulation amount adjustment method of a kind of refrigeration based on described in 1 to 5 any one of the claims or heat pump,
It is characterized in that：
During the refrigeration or heat pump are run along the refrigeration or heat pump circuit：
When the refrigerant circulation for needing to increase the refrigeration or heat pump, the first cold medium flux adjusting means is adjusted
(30,31) and the second cold medium flux adjusting means (31,30) at least one so that the liquid in the reservoir (5)
Position declines；
When the refrigerant circulation for needing to reduce the refrigeration or heat pump, the first cold medium flux adjusting means is adjusted
(30,31) and the second cold medium flux adjusting means (31,30) at least one so that the liquid in the reservoir (5)
Position rises.
7. according to claim 6 a kind of refrigeration or heat pump refrigerant circulation amount adjustment method, it is characterised in that：
Control first cold medium flux according at least to one of them the described parameter of following 7.1,7.2,7.3,7.4 and 7.5
One in adjusting means (30,31) and the second cold medium flux adjusting means (31,30)：
7.1) condenser (20,21,40) described in the refrigeration or heat pump circuit is to the first cold medium flux adjusting means
The degree of supercooling of certain between (30,31)；
7.2) condensing pressure or the condensation temperature of the refrigeration or heat pump；
7.3) delivery temperature described compressor (10) or case temperature or internal temperature；
7.4) fluid temperature (F.T.) for cooling down for condenser (20,21,40) and the condensation temperature of the condenser (20,21,40)；
7.5) fluid temperature (F.T.) for cooling down for condenser (20,21,40) and the outlet temperature of the condenser (20,21,40).
8. according to claim 7 a kind of refrigeration or heat pump refrigerant circulation amount adjustment method, it is characterised in that：
Control first refrigerant according at least to one of them the described parameter of following 8.1,8.2,8.3,8.4,8.5 and 8.6
Another in flow regulator (30,31) and the second cold medium flux adjusting means (31,30)：
8.1) described refrigeration or heat pump circuit described in evaporimeter (40,20) be exported to certain between the compressor (10)
The degree of superheat；
8.2) evaporating pressure or the evaporating temperature of the refrigeration or heat pump；
8.3) fluid temperature (F.T.) for cooling down for evaporimeter (40,20) and the evaporating temperature of the evaporimeter (40,20)；
8.4) fluid temperature (F.T.) for cooling down for evaporimeter (40,20) and the outlet temperature of the evaporimeter (40,20)；
8.5) delivery temperature described compressor (10) or case temperature or internal temperature；
8.6) discharge superheat described compressor (10).
9. according to claim 6 a kind of refrigeration or heat pump refrigerant circulation amount adjustment method, it is characterised in that：
When the degree of supercooling of the condenser (20,21,40) outlet refrigerant is less than under desired value set in advance or target interval
During limit value, reduce the aperture of the first cold medium flux adjusting means (30,31), or increase by second cold medium flux and adjust
The aperture of device (31,30)；
When the degree of supercooling of the condenser (20,21,40) outlet refrigerant is upper higher than desired value set in advance or target interval
During limit value, increase the aperture of the first cold medium flux adjusting means (30,31), or reduce second cold medium flux and adjust
The aperture of device (31,30).
10. according to claim 6 a kind of refrigeration or heat pump refrigerant circulation amount adjustment method, it is characterised in that：
During the refrigeration or heat pump are run along the refrigeration or heat pump circuit：
When the refrigerant circulation for needing to reduce in the condenser (20,21,40) and need to increase in the evaporimeter (40,20)
Refrigerant circulation when, increase the first cold medium flux adjusting means (30,31) aperture；
When the refrigerant circulation for needing to reduce in the condenser (20,21,40) and need to reduce in the evaporimeter (40,20)
Refrigerant circulation when, reduce the second cold medium flux adjusting means (31,30) aperture；
When the refrigerant circulation for needing to increase in the condenser (20,21,40) and need to reduce in the evaporimeter (40,20)
Refrigerant circulation when, reduce the first cold medium flux adjusting means (30,31) aperture；
When the refrigerant circulation for needing to increase in the condenser (20,21,40) and need to increase in the evaporimeter (40,20)
Refrigerant circulation when, increase the second cold medium flux adjusting means (31,30) aperture.
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Application publication date: 20170308 |