CN206113384U - Refrigeration or heat pump system - Google Patents
Refrigeration or heat pump system Download PDFInfo
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- CN206113384U CN206113384U CN201621046630.3U CN201621046630U CN206113384U CN 206113384 U CN206113384 U CN 206113384U CN 201621046630 U CN201621046630 U CN 201621046630U CN 206113384 U CN206113384 U CN 206113384U
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Abstract
The utility model discloses a refrigeration or heat pump system contains compressor, condenser, a varied refrigerant volume adjusting device, evaporimeter, still is provided with the reservoir, the reservoir contains barrel, refrigerant inlet piping, liquid refrigerant outlet pipeline, gaseous state refrigerant outlet pipeline, still is provided with the 2nd varied refrigerant volume adjusting device, the compressor mouth the condenser a varied refrigerant volume adjusting device the refrigerant inlet piping of reservoir the liquid refrigerant outlet pipeline of reservoir the 2nd varied refrigerant volume adjusting device the evaporimeter compressor induction port or tonifying qi mouth be serial connectivity in proper order, the gaseous state refrigerant outlet pipeline intercommunication of reservoir the evaporimeter. Through corresponding regulation method, the utility model discloses can control the refrigerant circulation volume of system to reliable, the high -efficient operation of messenger system homoenergetic under various operating modes.
Description
Technical field
This utility model is related to refrigerating field, more particularly to a kind of to freeze or heat pump.
Background technology
Condenser and vaporizer are the core components of refrigeration system, when condenser and vaporizer 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, vaporizer will be in preferable working condition, it is also desirable to which there is preferable coolant to follow in vaporizer
Circular rector, when preferable refrigerant circulation is respectively provided with condenser and vaporizer, refrigeration system just has preferable refrigerant circulation
Amount, so as to possess the condition for making refrigeration system in ideal operation state.
However, prior art there are problems that it is more, such as：
One, in refrigeration system, if condensing pressure is higher, compressor exhaust temperature can rise, and compression ratio increase, refrigerating capacity subtracts
Few, power consumption increase, condensing pressure is higher, is also easy to cause equipment breakage event.If condensing pressure is too low, particularly in the winter time,
Ambient temperature or cooling water temperature are 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, and 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 requires also different.Therefore, it is the reliably working of guarantee refrigeration system and compressor, it is necessary to condensation
Pressure implements control.The control method of condensing pressure, prior art mainly has two kinds：1st, cooling water flow or cooling wind are controlled
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 ambient 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, when even summer in warm season 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, and thus or causes users'comfort to decline, or refrigerating capacity deficiency causes food temperature to rise,
So that the unit for installing bigger ability is needed, but the ability of outdoor heat exchanger is not obtained by system, 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 defrosts 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 coolant 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 coolant 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
Optimum charge also inevitably exists because the filling quantity of working conditions change generation is relatively more or less come the air-conditioner for charging
Problem, so as to affect the Energy Efficiency Ratio of actual motion, cause the waste of energy.
Utility model content
The purpose of this utility model is to solve the above problems.
The technical solution of the utility model is as follows：
One kind refrigeration or heat pump, comprising compressor, condenser, the first cold medium flux adjusting means, vaporizer, 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 vaporizer are sequentially connected in series connection and form, 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, it is 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 vaporizer connects the air entry or gas supplementing opening of the compressor；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, it is cold between vaporizer 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 electronic expansions
Valve.
Further, four-way change-over valve, the total d mouths of the four-way change-over valve, e mouths, s mouths, four connections of c mouths are additionally provided with
Mouthful, when the four-way change-over valve is in first operating position, its d mouth is connected with c mouths and e mouths are connected with s mouths, and the four-way is changed
When being in second operating position to valve, its d mouth is connected with e mouths and c mouths are connected with s mouths；The air vent connection of the compressor
The d mouths of the four-way change-over valve, the air entry of the compressor connects the s mouths of the four-way change-over valve, the gas of the reservoir
Refrigerant passage described in state refrigerant exit pipeline communication between the s mouths 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 is located at the cylinder
The top half in internal space.
Based on above-mentioned technical proposal, this utility model can be controlled to the circulating load of cold-producing medium in refrigeration or heat pump
System, so that refrigeration or heat pump can reliable, Effec-tive Functions under various operating modes.
Description of the drawings
Fig. 1 is the theory of constitution schematic diagram of reservoir first embodiment in this utility model refrigeration or heat pump.
Fig. 2 is the theory of constitution schematic diagram of reservoir second embodiment in this utility model refrigeration or heat pump.
Fig. 3 is the theory of constitution schematic diagram of this utility model refrigeration or heat pump first embodiment.
Fig. 4 is the theory of constitution schematic diagram of this utility model refrigeration or heat pump second embodiment.
Fig. 5 is the theory of constitution schematic diagram of this utility model refrigeration or heat pump 3rd embodiment.
Fig. 6 is the theory of constitution schematic diagram of this utility model refrigeration or heat pump fourth embodiment.
Fig. 7 is the theory of constitution schematic diagram of this utility model refrigeration or the embodiment of heat pump the 5th.
Fig. 8 is the theory of constitution schematic diagram of this utility model refrigeration or heat pump sixth embodiment.
Fig. 9 is the theory of constitution schematic diagram of this utility model refrigeration or the embodiment of heat pump the 7th.
Specific embodiment
Below in conjunction with drawings and Examples, the technical solution of the utility model is described in further detail.
As shown in figure 1, the theory of constitution for reservoir first embodiment in this utility model refrigeration or heat pump is illustrated
Figure.Wherein, 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 liquid
Import of the state refrigerant exit pipe in cylinder 50,530 is import of the gaseous coolant outlet pipe in cylinder 50.
As shown in Fig. 2 the theory of constitution for reservoir second embodiment in this utility model refrigeration or heat pump is illustrated
Figure.Wherein, 50 is cylinder, in 51 and 52：One is refrigerant import pipe, and another is liquid refrigerants outlet, and can be mutual
Change, 53 is gaseous coolant outlet pipe, and 510 is import and export of the pipeline 51 in cylinder 50, and 520 is the entering in cylinder 50 of pipeline 52
Outlet, 530 is import of the gaseous coolant outlet pipe in cylinder 50.
As shown in figure 3, for this utility model refrigeration or heat pump first embodiment theory of constitution schematic diagram.Wherein,
10 is compressor, and 20 is condenser, and 30,31 are electric expansion valve, and 40 is vaporizer, and 5 is that reservoir (adopts above-mentioned reservoir
First embodiment).The air vent of compressor 10, condenser 20, electric expansion valve 30, the refrigerant import pipe 51 of reservoir 5, storage
The liquid refrigerants outlet 52 of liquid device 5, electric expansion valve 31, vaporizer 40, the air entry of compressor 10 are sequentially connected in series connection, storage
The connection vaporizer 40 of gaseous coolant outlet pipe 53 of liquid device 5 is exported and the pipeline between the air entry of compressor 10.
During system operation, the High Temperature High Pressure coolant of the output of compressor 10 initially enters condenser 20, and in condenser 20
Radiating is changed into highly pressurised liquid output, and then Jing electric expansion valves 30 throttle, and are changed into the biphase coolant 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 and further throttles after exporting, and is changed into the biphase coolant of low-temp low-pressure, subsequently into
In vaporizer 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, the middle pressure gaseous coolant in reservoir 5 Jing gaseous coolant outlet pipe 53 output after, with the overheated gas exported from vaporizer 40
Coolant returns to together the air entry of compressor 10.
Current embodiment require that it is noted that during 31 standard-sized sheet of electric expansion valve, the gaseous coolant in reservoir 5 with vaporizer
The passage that the coolant of 40 outlets is passed through before collecting has relatively small negotiability, during 31 standard-sized sheet of electric expansion valve, needs
Ensure that the gaseous coolant amount under each operating mode from the output of gaseous coolant outlet pipe 53 in reservoir 5 is not more than from refrigerant import pipe 51
The gaseous coolant amount of generation.Certainly, the aperture of electric expansion valve 30 it is larger and mainly by electric expansion valve 31 throttle when, will also
Ensure to be not less than from the gaseous coolant amount of the output of gaseous coolant outlet pipe 53 in reservoir 5 under each operating mode and give birth to from refrigerant import pipe 51
Into gaseous coolant amount, but the now pressure by the flash gas that produces after electric expansion valve 30 seldom and in reservoir 5
Power is higher, so comparatively, it is logical that the gaseous coolant in reservoir 5 is passed through before the coolant exported with vaporizer 40 collects
Road always has relatively small negotiability.
The first operation method of the present embodiment is that the degree of superheat for exporting coolant by vaporizer 40 controls expansion valve 30
Aperture, the degree of supercooling for exporting coolant by condenser 20 controls the aperture of electric expansion valve 31.When the coolant of the outlet of condenser 20
Without degree of supercooling or during degree of supercooling less than normal, increase the aperture of electric expansion valve 31, the reduced pressure in reservoir 5, by gas
The gaseous coolant amount of the output of state refrigerant exit pipe 53 diminishes, and the liquid level in reservoir 5 begins to decline, the coolant of the outlet of condenser 20
Start the supercool or degree of supercooling of appearance increasing.When the coolant degree of supercooling of the outlet of condenser 20 is bigger than normal, reduce electronic expansion
The aperture of valve 31, the pressure in reservoir 5 begins to ramp up, from the gaseous coolant increased flow capacity of the output of gaseous coolant outlet pipe 53,
Liquid level in reservoir 5 begins to ramp up, and the coolant degree of supercooling of the outlet of condenser 20 diminishes.When condenser 20 exports the supercool of coolant
When degree is in target zone or equal to desired value, the aperture of electric expansion valve 31 can be maintained constant.So, condenser 20 goes out
The coolant that the coolant of mouth has preferable degree of supercooling, the outlet of vaporizer 40 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 coolant by vaporizer 40 controls expansion valve 31
Aperture, the degree of supercooling for exporting coolant by condenser 20 controls the aperture of electric expansion valve 30.When the coolant of the outlet of condenser 20
Without degree of supercooling or during degree of supercooling less than normal, reduce the aperture of electric expansion valve 30, the reduced pressure in reservoir 5, by gas
The gaseous coolant amount of the output of state refrigerant exit pipe 53 diminishes, and the liquid level in reservoir 5 begins to decline, the coolant of the outlet of condenser 20
Start the supercool or degree of supercooling of appearance increasing.When the coolant degree of supercooling of the outlet of condenser 20 is bigger than normal, increase electronic expansion
The aperture of valve 30, the pressure in reservoir 5 begins to ramp up, from the gaseous coolant increased flow capacity of the output of gaseous coolant outlet pipe 53,
Liquid level in reservoir 5 begins to ramp up, and the coolant degree of supercooling of the outlet of condenser 20 diminishes.When condenser 20 exports the supercool of coolant
When degree is in target zone or equal to desired value, the aperture of electric expansion valve 30 can be maintained constant.So, condenser 20 goes out
The coolant that the coolant of mouth has preferable degree of supercooling, the outlet of vaporizer 40 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 coolant by condenser 20 controls electric expansion valve
30 and 31 aperture.When the coolant of the outlet of condenser 20 does not have degree of supercooling or degree of supercooling less than normal, reduce electric expansion valve 30
Aperture and increase the aperture of electric expansion valve 31, the reduced pressure in reservoir 5 is exported by gaseous coolant outlet pipe 53
Gaseous coolant amount diminishes, and the liquid level in reservoir 5 begins to decline, and it is supercool or supercool that the coolant that condenser 20 is exported starts appearance
Degree is increasing.When the coolant degree of supercooling of the outlet of condenser 20 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 begins to ramp up, and adds from the gaseous coolant flow of the output of gaseous coolant outlet pipe 53
Greatly, the liquid level in reservoir 5 begins to ramp up, and the coolant degree of supercooling of the outlet of condenser 20 diminishes.When condenser 20 exports coolant
When degree of supercooling is in target zone or equal to desired value, the aperture of electric expansion valve 30 and 31 can be maintained constant.So, it is cold
The coolant of the outlet of condenser 20 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 that the degree of superheat and condenser 20 for exporting coolant by vaporizer 40 is exported
The degree of supercooling of coolant come together control electric expansion valve 30 and 31 aperture, when condenser 20 export coolant degree of supercooling it 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 coolant
When low, reduce the aperture of electric expansion valve 30 and increase the aperture of electric expansion valve 31, refer to above-mentioned the third operation side
Method；When the degree of superheat that vaporizer 40 exports coolant is higher, the aperture of electric expansion valve 30 and 31 is synchronously increased, when vaporizer 40
When the degree of superheat of outlet coolant is low, the aperture of electric expansion valve 30 and 31 synchronously reduces；When condenser 20 exports the mistake of coolant
When the degree of superheat of cold degree higher and vaporizer 40 outlet coolant is higher, increase the aperture of electric expansion valve 30；When condenser 20 goes out
The degree of supercooling of mouthful coolant is higher and during the low degree of superheat of the outlet coolant of vaporizer 40, reduces the aperture of electric expansion valve 31；When
When degree of supercooling is low and the degree of superheat of the outlet coolant of vaporizer 40 is low of the outlet coolant of condenser 20, reduces electric expansion valve 30
Aperture；When the degree of supercooling that condenser 20 exports coolant is low and the degree of superheat of the outlet coolant of vaporizer 40 is higher, increase electricity
The aperture of sub- expansion valve 31.As such, it is possible to make the coolant that condenser 20 is exported have preferable degree of supercooling, it is cold that vaporizer 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, using air-cooled condenser, with the outdoor that condenser 20 is located
Ambient temperature is reduced, and condensing pressure can be than relatively low, the minimum pressure that even below compressor producer advises.At this moment, need to cold
Solidifying pressure is controlled.During system operation, if electric expansion valve 30 is only used for controlling the degree of superheat that vaporizer 40 exports coolant,
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 of the output of outlet 53 diminishes, and the liquid level in reservoir 5 begins to decline, and condensing pressure is increasing.Work as condensation
When pressure is in minimum target zone or equal to minimum setting value, if the degree of supercooling of the outlet coolant of condenser 20 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, the degree of supercooling of coolant is exported according to condenser 20 to control electric expansion valve 31
Aperture.As such, it is possible to make year round cooling system various complex conditions efficiently, reliability service.
As shown in figure 4, for this utility model refrigeration or heat pump second embodiment theory of constitution schematic diagram.This enforcement
Example is with a upper embodiment very close to difference is：In the present embodiment, the gaseous coolant outlet pipe 53 of reservoir 5 connects electricity
Connecting pipe between sub- expansion valve 31 and vaporizer 40.Ruuning situation may be referred to an embodiment.
As shown in figure 5, for this utility model refrigeration or heat pump 3rd embodiment theory of constitution schematic diagram.Wherein,
10 is compressor (having air vent, air entry and gas supplementing opening), and 20 is condenser, and 30,31 are electric expansion valve, and 40 are evaporation
Subcooler, 41 is main evaporator, and 5 is reservoir (using the first embodiment of above-mentioned reservoir), and 32 is expansion valve.Compressor 10
Air vent, condenser 20, electric expansion valve 30, the refrigerant import pipe 51 of reservoir 5, the liquid refrigerants outlet of reservoir 5
52nd, electric expansion valve 31, the evaporation side of evaporation subcooler 40, the gas supplementing opening of compressor 10 are sequentially connected in series connection, the gas of reservoir 5
Pipeline between the connection of state refrigerant exit pipe 53 evaporation subcooler 40 evaporation side outlet and the gas supplementing opening of compressor 10.From condenser 20
And the connecting pipe between electric expansion valve 30 also separates a pipeline, the pipeline is sequentially connected in series the mistake of connection evaporation subcooler 40
After cold side, expansion valve 32, main evaporator 41, the air entry of compressor 10 is connected.
In the present embodiment, the control main evaporator 41 of expansion valve 32 exports the degree of superheat of coolant, can make electric expansion valve 30
Control evaporation subcooler 40 evaporates the degree of superheat of side outlet coolant, and the control condenser 20 of electric expansion valve 31 exports the supercool of coolant
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 coolant, the control condenser 20 of electric expansion valve 30 exports the degree of supercooling of coolant.
For year round cooling system, when the ambient temperature residing for condenser 20 is relatively low, condenser 20 can be equally controlled
Condensing pressure or condensation temperature.
As shown in fig. 6, for this utility model refrigeration or heat pump fourth embodiment theory of constitution schematic diagram.This enforcement
Example is freezed with above-mentioned this utility model or the difference of heat pump first embodiment is：Compressor 10 also has in the present embodiment
Expansion valve 33 and evaporation subcooler 42 are also provided with intermediate fill gas mouth, therefore the present embodiment, the outlet of condenser 20 is divided into two
Road, through the mistake cold side connection electric expansion valve 30 of evaporation subcooler 42, the second tunnel sequentially passes through expansion valve 33 and steams the first via
The evaporation side for sending out subcooler 42 connects the intermediate fill gas mouth of compressor 10.
In the present embodiment, the control evaporation subcooler 42 of expansion valve 33 evaporates the degree of superheat of side outlet coolant, and other are with above-mentioned
This utility model freezes or heat pump first embodiment.
As shown in fig. 7, for this utility model refrigeration or the embodiment of heat pump the 5th theory of constitution schematic diagram.This enforcement
Example is freezed with above-mentioned this utility model or the difference of heat pump first embodiment is：Sleeve heat exchange is increased in the present embodiment
Device 21, the refrigerant passage of double-tube heat exchanger 21 is serially connected in the connecting pipe between compressor 10 and condenser 20, its aquaporin
It is serially connected with feed pump 71.
When water pump 71 does not run, the present embodiment has the fortune of above-mentioned this utility model refrigeration or heat pump first embodiment
Row mode, its operation can also be with reference to above-mentioned this utility model refrigeration or heat pump first embodiment.
But, many operational modes of a recuperation of heat of the present embodiment, under the pattern, feed pump 71 runs, electronic expansion
The aperture of valve 30 or 31 is controlled according to the coolant degree of supercooling of the refrigerant passage of double-tube heat exchanger 21 outlet, and details are referred to
The explanation that condenser 20 exports coolant degree of supercooling is controlled in above-mentioned refrigeration or heat pump first embodiment.At this moment, sleeve heat exchange
Device 21 is substantially increased as condenser, condenser 20 as subcooler (heat exchange blower fan or water pump of condenser 20 will be opened)
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 is freezed or heat pump first embodiment, but feed pump 71 is to open, as such, it is possible to be discharged with compressor 10
Hyperthermia and superheating coolant the water in double-tube heat exchanger 21 is heated, produce high-temperature-hot-water.
As shown in figure 8, for this utility model refrigeration or heat pump sixth embodiment theory of constitution schematic diagram.Wherein,
10 is compressor, and 20 is outdoor heat exchanger, and 30,31 are electric expansion valve, and 40 is indoor heat exchanger, and 5 is that reservoir (is adopted upper
State the second embodiment of reservoir), 81 is four-way change-over valve, and 82 is gas-liquid separator.Four-way change-over valve 81 has d mouths, e mouths, s
Mouth, four connectors of c mouths, during 81 power-off of four-way change-over valve, d mouths are connected with c mouths and e mouths are connected with s mouths, on four-way change-over valve 81
When electric, d mouths are connected with e mouths and c mouths are connected with s mouths.The air vent of compressor 10 connects the d mouths of four-way change-over valve 81, and four-way is changed
The air-breathing of compressor 10 is connected through gas-liquid separator 82 together with the gaseous coolant outlet pipe 53 of reservoir 5 to the s mouths of valve 81
Mouthful, the c mouths of four-way change-over valve 81, outdoor heat exchanger 20, electric expansion valve 30, the connecting tube 51 of reservoir 5, the company of reservoir 5
Adapter 52, electric expansion valve 31, indoor heat exchanger 40, the e mouths of four-way change-over valve 81 are sequentially connected in series connection.
During system operation, the High Temperature High Pressure coolant for giving the power-off of four-way change-over valve 81, the output of compressor 10 sequentially passes through four-way
The d mouths of reversal valve 81, c mouths enter outdoor heat exchanger 20, and radiating is changed into highly pressurised liquid output in outdoor heat exchanger 20, then
Jing electric expansion valves 30 throttle, and are changed into the biphase coolant of middle pressure, then enter reservoir 5, reservoir 5 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 further throttles, and is changed into the biphase coolant of low-temp low-pressure, subsequently into indoor heat exchanger 40 in, and change indoors
Evaporation of absorbing heat in hot device 40 is changed into overheated gas output, then sequentially passes through e mouths, s mouths, the gas-liquid separator of four-way change-over valve 81
82, eventually pass back to the air entry of compressor 10, the gaseous coolant in reservoir 5 Jing after the output of gaseous coolant outlet pipe 53, with from
The overheated gas coolant exported in the s mouths of four-way change-over valve 81 returns to together the air-breathing of compressor 10 through gas-liquid separator 82
Mouthful.
Wherein it is possible to the degree of superheat for exporting coolant according to indoor heat exchanger 40 controls the aperture of electric expansion valve 30, according to
The degree of supercooling of the outlet coolant of outdoor heat exchanger 20 controls the aperture of electric expansion valve 31.When the coolant of the outlet of outdoor heat exchanger 20 does not have
When having degree of supercooling or degree of supercooling less than normal, increase the aperture of electric expansion valve 31, the reduced pressure in reservoir 5, by gaseous state
The gaseous coolant amount of the output of refrigerant exit pipe 53 diminishes, and the liquid level in reservoir 5 begins to decline, and it is cold that outdoor heat exchanger 20 is exported
It is increasing that matchmaker starts the supercool or degree of supercooling of appearance.When the coolant degree of supercooling of the outlet of outdoor heat exchanger 20 is bigger than normal, reduce electricity
The aperture of sub- expansion valve 31, the pressure in reservoir 5 begins to ramp up, from the gaseous coolant flow of the output of gaseous coolant outlet pipe 53
Increase, the liquid level in reservoir 5 begins to ramp up, the coolant degree of supercooling of the outlet of outdoor heat exchanger 20 diminishes.When outdoor heat exchanger 20
When the degree of supercooling of outlet coolant is in target zone or equal to setting value, the aperture of electric expansion valve 31 can be maintained constant.This
Sample, the coolant that the coolant of the outlet of outdoor heat exchanger 20 has preferable degree of supercooling, the outlet of indoor heat exchanger 40 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 the degree of superheat control electronic expansion of coolant is exported according to indoor heat exchanger 40
The aperture of valve 31, the degree of supercooling for exporting coolant according to outdoor heat exchanger 20 controls the aperture of electric expansion valve 30, and makes system high
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
Vaporizer is used, and at this moment, can control the degree of superheat that outdoor heat exchanger 20 exports coolant by electric expansion valve 31, and by electronics
The control indoor heat exchanger 40 of expansion valve 30 exports the degree of supercooling of coolant, it is also possible to control outdoor heat exchanger by electric expansion valve 30
The degree of superheat of 20 outlet coolant, and the degree of supercooling that indoor heat exchanger 40 exports coolant is controlled by electric expansion valve 31, details can
With reference to the explanation of the preceding paragraph.
Upper two sections of explanation, it is 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,
When winter defrosts to outdoor heat exchanger 20, the condensing pressure of outdoor heat exchanger 20 can be controlled, lift defrosting effect, 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 controlling the degree of superheat that indoor heat exchanger 40 exports coolant, 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
When condensing pressure in outdoor heat exchanger 20 is in target zone or equal to setting value, if the outlet coolant of outdoor heat exchanger 20
Degree of supercooling be not less than the lower limit or 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 coolant 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 this utility model refrigeration or the embodiment of heat pump the 7th theory of constitution schematic diagram.This enforcement
Example be with the difference of a upper embodiment：Double-tube heat exchanger 21, the coolant of double-tube heat exchanger 21 are increased in the present embodiment
Passage is serially connected in the connecting pipe between the air vent of compressor 10 and the d mouths of four-way change-over valve 81, and its aquaporin is serially connected with
Feed 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, feed pump 71 runs, and the aperture of electric expansion valve 30 or 31 is the coolant mistake according to the outlet of the refrigerant passage of double-tube heat exchanger 21
Come what is controlled, details are referred to control the explanation that condenser 20 exports coolant degree of supercooling in an embodiment cold degree.At this moment, cover
Heat exchange of heat pipe 21 as condenser, outdoor heat exchanger 20 as subcooler (heat exchange blower fan or water pump of heat exchanger 20 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 the power-off of four-way change-over valve 81, but feed pump 71 is to open
, as such, it is possible to the hyperthermia and superheating coolant 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, the present embodiment it is many one heat plus water heating pattern, the pattern
Under, feed pump 71 runs, and the aperture of electric expansion valve 30 or 31 is the coolant mistake according to the outlet of the refrigerant passage of double-tube heat exchanger 21
Controlling, at this moment, used as condenser, used as subcooler, (heat exchanger 40 is changed indoor heat exchanger 40 double-tube heat exchanger 21 cold degree
Hot-air blower will be opened), substantially increase the heating capacity and efficiency of system.
Additionally, when to electricity on four-way change-over valve 81, the present embodiment can also be further added by a pattern for producing high-temperature-hot-water,
Under this kind of pattern, the aperture of electric expansion valve 30 or 31 is controlled according to the coolant degree of supercooling of the outlet of indoor heat exchanger 40, but is supplied
Water pump 71 is to open, as such, it is possible to the hyperthermia and superheating coolant 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 the technical solution of the utility model rather than it is limited
System, person of an ordinary skill in the technical field should be appreciated that still can be to specific embodiment of the present utility model and application
Occasion or field are modified or carry out equivalence replacement to some technical characteristics.So, without departing from this utility model skill
The spirit of art scheme, should cover in the middle of the technical scheme scope being claimed in this utility model.
Claims (5)
1. it is a kind of to freeze or heat pump, comprising compressor (10), condenser (20,21,40), the first cold medium flux adjusting means
(30,31), vaporizer (40,20), it is characterised in that：
Reservoir (5) is provided with, the reservoir (5) goes 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), the first cold medium flux adjusting means (30,31), the reservoir (5), the second cold medium flux adjusting means
(31,30), the vaporizer (40,20) are sequentially connected in series connection and form, wherein, the first cold medium flux adjusting means (30,
31) it is arranged on the refrigerant import pipe on the refrigerant import pipeline of the reservoir (5) (51,52) or with the reservoir (5)
On the pipeline of road (51,52) connection, the second cold medium flux adjusting means (31,30) is arranged on the liquid of the reservoir (5)
The pipeline connected on state refrigerant exit pipeline (52,51) or with the liquid refrigerants outlet conduit (52,51) of the reservoir (5)
On, the vaporizer (40,20) connects the air entry or gas supplementing opening of the compressor (10)；
From second coolant in gaseous coolant outlet pipeline (53) the connection refrigeration of the reservoir (5) or heat pump circuit
Flow regulator (31,30) is to refrigerant passage of the 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) of the reservoir (5) connects the vaporizer (40,20) and the compressor (10)
Between refrigerant passage.
3. one kind according to claim 2 is freezed or heat pump, it is characterised in that：
The first cold medium flux adjusting means (30,31) and the second cold medium flux adjusting means (31,30) are 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, the total d mouths of the four-way change-over valve (81), e mouths, s mouths, four connectors of c mouths are described
Four-way change-over valve (81) in first operating position when, its d mouth is connected with c mouths and e mouths are connected with s mouths, four-way commutation
Valve (81) in second operating position when, its d mouth is connected with e mouths and c mouths are connected with s mouths；
The air vent of the compressor (10) connects the d mouths of the four-way change-over valve (81), the air entry of the compressor (10)
Connect the s mouths of the four-way change-over valve (81)；
The gaseous coolant outlet pipeline (53) of the reservoir (5) connects the s mouths of the 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 the 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 the reservoir (5) is in the cylinder
Top half of the refrigerant import (530) in body (50) positioned at the interior space of the cylinder (50).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201621046630.3U CN206113384U (en) | 2016-09-10 | 2016-09-10 | Refrigeration or heat pump system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201621046630.3U CN206113384U (en) | 2016-09-10 | 2016-09-10 | Refrigeration or heat pump system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN206113384U true CN206113384U (en) | 2017-04-19 |
Family
ID=58519727
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201621046630.3U Expired - Fee Related CN206113384U (en) | 2016-09-10 | 2016-09-10 | Refrigeration or heat pump system |
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| Country | Link |
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| CN (1) | CN206113384U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107576094A (en) * | 2017-07-31 | 2018-01-12 | 宁波奥克斯电气股份有限公司 | A kind of source pump and its operation method |
| CN108007005A (en) * | 2017-11-08 | 2018-05-08 | 西安交通大学 | Flash evaporation refrigeration system, the refrigerator and its control method with the refrigeration system |
| CN109162967A (en) * | 2018-11-06 | 2019-01-08 | 珠海格力电器股份有限公司 | Bearing cooler, compressor and bearing cooling control method |
-
2016
- 2016-09-10 CN CN201621046630.3U patent/CN206113384U/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107576094A (en) * | 2017-07-31 | 2018-01-12 | 宁波奥克斯电气股份有限公司 | A kind of source pump and its operation method |
| CN107576094B (en) * | 2017-07-31 | 2023-04-18 | 宁波奥克斯电气股份有限公司 | Heat pump unit and operation method thereof |
| CN108007005A (en) * | 2017-11-08 | 2018-05-08 | 西安交通大学 | Flash evaporation refrigeration system, the refrigerator and its control method with the refrigeration system |
| CN108007005B (en) * | 2017-11-08 | 2019-10-29 | 西安交通大学 | Flash evaporation refrigeration system, the refrigerator with the refrigeration system and its control method |
| CN109162967A (en) * | 2018-11-06 | 2019-01-08 | 珠海格力电器股份有限公司 | Bearing cooler, compressor and bearing cooling control method |
| CN109162967B (en) * | 2018-11-06 | 2024-01-02 | 珠海格力电器股份有限公司 | Bearing cooling device, compressor, and bearing cooling control method |
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