CN206847112U - Low filling quantity of refrigerant heat pump assembly - Google Patents
Low filling quantity of refrigerant heat pump assembly Download PDFInfo
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- CN206847112U CN206847112U CN201720558508.2U CN201720558508U CN206847112U CN 206847112 U CN206847112 U CN 206847112U CN 201720558508 U CN201720558508 U CN 201720558508U CN 206847112 U CN206847112 U CN 206847112U
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Abstract
A kind of low filling quantity of refrigerant heat pump assembly, the device includes compressor, compressor refrigerant gas vent is sequentially connected indoor heat exchanger, throttling arrangement and outdoor heat exchanger by four-way reversing valve, outdoor heat exchanger outlet connects reservoir entrance, reservoir outlet connection compressor inlet by four-way reversing valve；Also include bypass line, between compressor and four-way reversing valve, bypass line outlet is located on bypass line between four-way reversing valve and reservoir or positioned at the housing side of reservoir or bottom, bypass solenoid valve for bypass line import；Under heating condition during stable operation, indoor heat exchanger is flowed into through four-way reversing valve from the refrigerant of compressor discharge, then flows back to compressor through throttling arrangement, outdoor heat exchanger, four-way reversing valve, reservoir, forms heating circulation；Stable operation is opposite with heating circulation stream under cooling condition；The utility model also provides the control method of the device；Avoided the occurrence of in Cold Start because a large amount of refrigerants are gathered in reservoir and compressor cause compressor intake pressure too low the problem of.
Description
Technical field
The invention belongs to air-conditioning technical field, and in particular to a kind of low filling quantity of refrigerant heat pump assembly.
Background technology
In the past, the refrigerant of HFC (HFC) class was widely used in domestic air conditioning, middle-size and small-size business air conditioner.But by
It is higher in these refrigerant greenhouse effects indexes (GWP), environment is had a great influence, from control global warming angle,
Various countries' relevant enterprise begins to use the refrigerant of low GWP value in succession.It is therefore proposed use hydrofluoroolefin (HFO)
R1234yf, R290, R600a, R1270 etc. of hydrocarbon class (HC) are to the less refrigerant of influenced by global warming.But with it is conventional
HFC classes refrigerant is different, and these refrigerants all more or less have the problem of flammable (or micro- flammable).
In the air-conditioning system using above-mentioned combustible refrigerant, revealed in the event of refrigerant in room, and concentration
When higher, it is easy to cause the generation of the accidents such as fire.Therefore, in order to solve refrigerant flammability issues, prevent potentially to pacify
Full hidden danger, each enterprise reduce refrigerant filling quantity in systems one after another.As the reduction of filling quantity of refrigerant in system, series are steady
Fixed and integrity problem occurs in succession.
Refrigeration cold start-up refers under cooling condition, is in stopped status before compressor start for a long time so that its temperature
It is equal with environment temperature.Heating cold start-up refers under heating condition, is in stopped status before compressor start for a long time so that
Its temperature is equal with environment temperature.
Under cold start of freezing, if room temperature is relatively low, a large amount of liquid refrigerants are in indoor heat exchanger, with
The startup of compressor, a large amount of liquid refrigerants are inhaled into reservoir.Liquid refrigerant in reservoir can not be changed effectively with environment
It is thermal evaporation, cause suction side gaseous refrigerant insufficient, pressure of inspiration(Pi) further reduces, and (is less than air so as to negative pressure occur
Pressure).Meanwhile initial start stage oil sump temperature is relatively low, if using the preferable lubricating oil of intersolubility, with pressure rise in housing, greatly
Amount refrigerant will be dissolved in oil sump, refrigerant in further reduction system, make pressure of inspiration(Pi) lower.Moreover, refrigerant is in outdoor
Reservoir in evaporation endothermic, reduce system cold, reduce efficiency.
In the case where heating cold start, outdoor temperature is relatively low, and a large amount of liquid refrigerants are in outdoor heat exchanger and are dissolved in
In oil sump, with freezing, cold start-up is similar, and with the startup of compressor, a large amount of liquid refrigerants are inhaled into reservoir and compressor,
Suction side gaseous refrigerant deficiency, pressure of inspiration(Pi) are likely to occur negative pressure；Meanwhile largely dissolving refrigerants will reduce it and glue in oil sump
Degree, influence the reliability of compressor.
Under defrosting operating condition, defrost the later stage, because indoor fan is not opened, indoor heat exchanger can not be big due to temperature decline
Amount provides heat, and refrigerant can not effectively absorb heat in heat exchanger evaporation indoors.Compressor can not suck enough gaseous refrigerants
Agent, it can only evaporate the refrigerant of suction side by reducing pressure of inspiration(Pi), this aspect causes pressure of inspiration(Pi) extremely low, or even negative
Pressure, on the other hand also result in the sharp temperature drop of air intake duct, cylinder, oil sump etc..With the decline of oil sump temperature, a large amount of systems
Cryogen is begun to dissolve in oil sump so that when being converted into heating mode, the lack of refrigerant of system, possible pressure pressure of inspiration(Pi) is still
It is too low, or even negative pressure.
The generation of negative pressure may make air-refrigeration system, the generation that on the one hand easily set off an explosion into the air of system,
On the other hand checking influences the reliability of compressor and refrigeration system.
The content of the invention
The present invention is completed at least one in solving the above problems, its object is to, there is provided a kind of low system
Cryogen filling quantity heat pump assembly so that it is avoided the occurrence of in Cold Start because a large amount of refrigerants are gathered in reservoir and compression
Cause compressor intake pressure too low in machine.
A kind of low filling quantity of refrigerant heat pump assembly, including compressor 1, the refrigerant gas outlet of compressor 1 pass through four
Logical reversal valve 2 is sequentially connected indoor heat exchanger 3, throttling arrangement 4 and outdoor heat exchanger 5, and outdoor heat exchanger 5 exports to be changed by four-way
The entrance of reservoir 6, the outlet of the reservoir 6 connection import of compressor 1 are connected to valve 2；Also include bypass line 8, bypass line 8 enters
Mouthful between compressor 1 and four-way reversing valve 2, the outlet of bypass line 8 between four-way reversing valve 2 and reservoir 6 or
Positioned at the housing side of reservoir 6 or bottom, bypass solenoid valve 7 is located on bypass line 8；The stable operation under heating condition
When, indoor heat exchanger 3 is flowed into from the refrigerant that compressor 1 is discharged through four-way reversing valve 2, then through throttling arrangement 4, outdoor heat exchange
Device 5, four-way reversing valve 2, reservoir 6 flow back to compressor 1, form heating circulation；Stable operation circulates with heating under cooling condition
Stream is opposite.
The refrigerant is low charging amount refrigerant.
The low charging amount refrigerant is R290 or R1270.
A kind of control method of the low filling quantity of refrigerant heat pump assembly,
When the outlet of bypass line 8 is between four-way reversing valve 2 and reservoir 6, when cooling condition or heating condition
Cold start-up, or occur during Defrost operation that the inlet pressure of compressor 1 is too low, refrigerant is largely in reservoir 6 and pressure
When assembling in contracting machine 1, bypass solenoid valve 7 is opened, and the part high temperature and high pressure gas that compressor 1 is discharged flow into bypass line 8, through side
After three-way electromagnetic valve 7 throttles, indoor heat exchange is come from from outdoor heat exchanger 5 or refrigeration/defrosting operating condition part with heating condition part
The mixed middle pressure state refrigerant of refrigerant in device 3 is flowed into reservoir 6, is then sucked by compressor 1, so as to improve pressure
The inlet pressure of contracting machine 1 and mass flow, avoid negative pressure；
When the outlet of bypass line 8 is positioned at the housing side or bottom of reservoir 6, when low temperature being present in reservoir 6
During liquid refrigerant, the high temperature refrigerant gas after the throttling of bypass solenoid valve 7 directly heats effect to it, makes its rapid steaming
Saturated vapor is sent out into, improves the inlet pressure of compressor 1, ensures that suction side has the refrigerant of abundance.
The unlatching control mode of bypass solenoid valve 7 is pressure controling method, time control act and temperature control method；
The unlatching control mode one of bypass solenoid valve 7：Pressure controling method, when corresponding specified of the air inlet of compressor 1
When the difference of evaporating pressure is more than preset pressure, starts bypass solenoid valve 7 and open；
The unlatching control mode two of bypass solenoid valve 7：Time control act, bypass solenoid valve 7 is automatically turned on during cold start-up, is reached
Closed automatically after to preset time, preset time length is according to the discharge capacity of compressor 1, the internal volume of indoor heat exchanger 3, outdoor heat exchange
The internal volume of device 5 and ambient temperature conditions determine.
The unlatching control mode three of bypass solenoid valve 7：Temperature control method, oil sump temperature and compression when the bottom of compressor 1
The difference between condensation temperature corresponding to machine (1) pressure at expulsion opens bypass solenoid valve 7 when being less than low preset temperature, reaches high
Bypass solenoid valve 7 is closed automatically after preset temperature.
What heat pump assembly of the present invention and control method can reach has the beneficial effect that：
1st, avoid pressure of inspiration(Pi) too low.During cold start-up, a large amount of liquid refrigerants make a large amount of liquid in low-pressure side, suddenly startup
Refrigerant enters reservoir, does not have enough liquid refrigerants in low pressure heat exchanger.Because reservoir and environment can not effectively exchange heat, because
And low-pressure side gaseous refrigerant is insufficient, pressure of inspiration(Pi) further reduces.
2nd, liquid hammer is avoided.During cold start-up, a large amount of liquid refrigerants enter a large amount of liquid refrigerants in low-pressure side, suddenly startup
Enter reservoir, when liquid refrigerant is excessive, reservoir may be overflowed, into compressor, cause liquid hammer.The use one of by-passing valve
Aspect avoids during cold start-up a large amount of liquid refrigerants from entering reservoir, in another aspect hyperthermia and superheating state refrigerant heat reservoir
Liquid refrigerant (if there is), make its volatilization.
3rd, the quick oil sump temperature for improving compression motor spindle, reduces the refrigerant amount dissolved in oil sump, improves oil viscosity.
4th, refrigerant amount in quick raising system, avoids pressure of inspiration(Pi) from further reducing.As refrigerant is from compressor bottom
Volatilized in the oil sump in portion, compressor housing inner refrigerant content is reduced, and refrigerant increases in system, so as to avoid pressure of inspiration(Pi)
Further reduce.
5th, start-up course evaporating temperature is improved, avoids lubricating oil from residing in heat exchanger inner surface, avoids lubricating oil from residing in
Capillary inner surface, cause blocking.
Brief description of the drawings
Fig. 1 is the form of implementation structural representation of heat pump assembly one of the present invention.
Fig. 2 is another form of implementation structural representation of heat pump assembly of the present invention.
Specific embodiment
The present invention is described in further details below according to the drawings and specific embodiments.
Fig. 1 show a kind of embodiment of the low filling quantity of refrigerant heat pump assembly of the present invention.(the solid line under heating condition
The direction of arrow) stable operation when, from compressor 1 discharge refrigerant gas through four-way reversing valve 2 flow into indoor heat exchanger 3, and
Compressor 1 is flowed back to by throttling arrangement 4, outdoor heat exchanger 6, four-way reversing valve 2, reservoir 6, forms heating circulation.Freeze/remove
(Fig. 1 dotted arrows direction) stable operation is opposite with this circulation stream under white operating mode.
Between compressor 1 and four-way reversing valve 2, the outlet of bypass line 8 is changed positioned at four-way for the import of bypass line 8
To between valve 2 and reservoir 6, bypass solenoid valve 7 is located on bypass line 8.When cooling condition or heating condition cold start-up, or
Occur that the inlet pressure of compressor 1 is too low, refrigerant largely gathers in reservoir 6 and compressor 1 during Defrost operation etc.
During collection, bypass solenoid valve 7 is opened, and the part high temperature and high pressure gas that compressor 1 is discharged flow into bypass line 8, through bypass solenoid valve 7
After throttling, with refrigerant of the part in outdoor heat exchanger 5 (heating condition) or indoor heat exchanger 3 (refrigeration/defrosting operating condition)
Mixed middle pressure state refrigerant is flowed into reservoir 6, is then sucked by compressor 1, so as to improve the air inlet pressure of compressor 1
Power and air-mass flow, avoid the inlet pressure subatmospheric of compressor 1.
The unlatching control mode of bypass solenoid valve 7 is pressure-control valve, time control act and temperature control method.
The opening ways one of bypass solenoid valve 7：Pressure controling method, when the air inlet of compressor 1 and corresponding specified steaming
When the difference of hair pressure is more than preset pressure (such as 0.15MPa), starts bypass solenoid valve 7 and open, preset pressure size is according to compression
The discharge capacity of machine 1, the internal volume of interior heat exchanger 3, the internal volume of outdoor heat exchanger 5 and ambient temperature conditions determine.
The opening ways two of bypass solenoid valve 7：Time control act, bypass solenoid valve 7 is automatically turned on during cold start-up, reaches pre-
If the time (such as 1min), automatic closing, preset time length were changed according to the discharge capacity of compressor 1, the internal volume of interior heat exchanger 3, outdoor afterwards
The hot internal volume of device 5 and ambient temperature conditions determine.
The opening ways three of bypass solenoid valve 7：Temperature control method, when oil sump temperature and the compressor (1) of the bottom of compressor 1
The difference between condensation temperature corresponding to pressure at expulsion opens bypass solenoid valve 7 when being less than bottom preset temperature (such as 5 DEG C), reaches
High preset temperature (such as 15 DEG C) afterwards close automatically by bypass solenoid valve 7, discharge capacity of the preset temperature size according to compressor 1, refrigerant
Determined with conditions such as lubricating oil charging amount and environment temperatures.
Fig. 2 is another form of implementation of the low filling quantity of refrigerant heat pump assembly of the present invention.
The structure of this form of implementation and Fig. 1 forms of implementation is essentially identical, and different structure is, the outlet of bypass line 8
Positioned at the housing side of reservoir 6 or bottom.Such effect is the warp when low temperature liquid refrigerant in reservoir 6 be present
High temperature refrigerant gas after bypass solenoid valve 7 throttles directly heats effect to it, it is rapidly evaporated to saturated vapor, carries
Pressure in high reservoir 6, ensure that the air inlet of compressor 1 has the refrigerant of abundance.The control mode of bypass solenoid valve 7 and upper one
Embodiment is identical.
The present invention is illustrated according to form of implementation above, it is apparent that the present invention does not limit to and these forms of implementation.
Claims (3)
- A kind of 1. low filling quantity of refrigerant heat pump assembly, it is characterised in that：Including compressor (1), the refrigerant gas of compressor (1) Body outlet is sequentially connected indoor heat exchanger (3), throttling arrangement (4) and outdoor heat exchanger (5) by four-way reversing valve (2), outdoor Heat exchanger (5) outlet connects reservoir (6) entrance by four-way reversing valve (2), and reservoir (6) outlet connection compressor (1) enters Mouthful；Also include bypass line (8), the import of bypass line (8) is located between compressor (1) and four-way reversing valve (2), bypass pipe The outlet on road (8) is located between four-way reversing valve (2) and reservoir (6) or positioned at the housing side of reservoir (6) or bottom, Bypass solenoid valve (7) is located on bypass line (8)；Under heating condition during stable operation, from the refrigerant of compressor (1) discharge Indoor heat exchanger (3) is flowed into through four-way reversing valve (2), then through throttling arrangement (4), outdoor heat exchanger (5), four-way reversing valve (2), reservoir (6) flows back to compressor (1), forms heating circulation；Stable operation is opposite with heating circulation stream under cooling condition.
- A kind of 2. low filling quantity of refrigerant heat pump assembly according to claim 1, it is characterised in that：The refrigerant is low Charging amount refrigerant.
- A kind of 3. low filling quantity of refrigerant heat pump assembly according to claim 2, it is characterised in that：The low charging amount system Cryogen is R290 or R1270.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201720558508.2U CN206847112U (en) | 2017-05-19 | 2017-05-19 | Low filling quantity of refrigerant heat pump assembly |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201720558508.2U CN206847112U (en) | 2017-05-19 | 2017-05-19 | Low filling quantity of refrigerant heat pump assembly |
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| Publication Number | Publication Date |
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| CN206847112U true CN206847112U (en) | 2018-01-05 |
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ID=60796205
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| Application Number | Title | Priority Date | Filing Date |
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| CN201720558508.2U Active CN206847112U (en) | 2017-05-19 | 2017-05-19 | Low filling quantity of refrigerant heat pump assembly |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107036322A (en) * | 2017-05-19 | 2017-08-11 | 西安交通大学 | Low filling quantity of refrigerant heat pump assembly and its control method |
| CN109297148A (en) * | 2018-09-04 | 2019-02-01 | 珠海格力电器股份有限公司 | Heat pump unit, its cooling activation low-voltage variation method, computer equipment and storage medium |
| CN111536637A (en) * | 2019-02-07 | 2020-08-14 | 三星电子株式会社 | Air conditioning system comprising a refrigerant circulation circuit for oil flow blocking |
-
2017
- 2017-05-19 CN CN201720558508.2U patent/CN206847112U/en active Active
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107036322A (en) * | 2017-05-19 | 2017-08-11 | 西安交通大学 | Low filling quantity of refrigerant heat pump assembly and its control method |
| CN109297148A (en) * | 2018-09-04 | 2019-02-01 | 珠海格力电器股份有限公司 | Heat pump unit, its cooling activation low-voltage variation method, computer equipment and storage medium |
| CN109297148B (en) * | 2018-09-04 | 2019-11-08 | 珠海格力电器股份有限公司 | Heat pump unit, its cooling activation low-voltage variation method, computer equipment and storage medium |
| CN111536637A (en) * | 2019-02-07 | 2020-08-14 | 三星电子株式会社 | Air conditioning system comprising a refrigerant circulation circuit for oil flow blocking |
| US11378315B2 (en) | 2019-02-07 | 2022-07-05 | Samsung Electronics Co., Ltd. | Air conditioner system including refrigerant cycle circuit for oil flow blocking |
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