CN105485949A - Refrigerating system and control method thereof - Google Patents
Refrigerating system and control method thereof Download PDFInfo
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- CN105485949A CN105485949A CN201510973565.2A CN201510973565A CN105485949A CN 105485949 A CN105485949 A CN 105485949A CN 201510973565 A CN201510973565 A CN 201510973565A CN 105485949 A CN105485949 A CN 105485949A
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- 238000000034 method Methods 0.000 title claims abstract description 18
- 230000001502 supplementing effect Effects 0.000 claims abstract description 93
- 238000005057 refrigeration Methods 0.000 claims abstract description 53
- 238000001704 evaporation Methods 0.000 claims description 29
- 230000008020 evaporation Effects 0.000 claims description 29
- 230000006835 compression Effects 0.000 claims description 19
- 238000007906 compression Methods 0.000 claims description 19
- 238000010438 heat treatment Methods 0.000 abstract description 22
- 239000007788 liquid Substances 0.000 abstract description 15
- 239000003507 refrigerant Substances 0.000 description 21
- 230000000694 effects Effects 0.000 description 13
- 239000000203 mixture Substances 0.000 description 6
- 230000001105 regulatory effect Effects 0.000 description 6
- 238000005516 engineering process Methods 0.000 description 4
- 230000007423 decrease Effects 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 2
- 238000009835 boiling Methods 0.000 description 2
- 230000005494 condensation Effects 0.000 description 2
- 238000009833 condensation Methods 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 230000029058 respiratory gaseous exchange Effects 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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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
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/004—Gas cycle refrigeration machines using a compressor of the rotary type
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention provides a refrigerating system which comprises a scroll compressor (101), a flash tank (104) and a high-pressure-level throttling device (103), wherein the flash tank (104) is provided with an exhaust end, the exhaust end is connected to a first medium-pressure air suction end of the compressor through a first air supply branch circuit, and is also connected to a second medium-pressure air suction end of the compressor through a second air supply branch circuit, the pressure of the first medium-pressure air suction end is unequal to that of the second medium-pressure air suction end, and the system further comprises a control valve system for controlling at least one of the two air supply branch circuits to be connected or disconnected. The invention can simultaneously meet two requirements of improving the heating performance of the refrigerating system by supplementing air and increasing enthalpy under the low-temperature condition and reducing the exhaust temperature of the compressor by supplementing air and carrying liquid under the ultralow-temperature condition; the low-temperature heating capacity of the refrigeration system adopting the scroll compressor and the operation reliability of the ultralow-temperature working condition are both considered, and the application working condition range of the refrigeration system adopting the scroll compressor is widened. The invention also relates to a control method of the refrigeration system.
Description
Technical field
The invention belongs to refrigeration technology field, be specifically related to a kind of refrigeration system and control method thereof.
Background technology
Air source heat pump heating capacity is decayed rapidly with outdoor environment temperature decline and cannot meet consumers' demand.Existing employing twin-stage or accurate two-stage compression second vapor injection increase enthalpy technology, comprise in the middle of two-stage throttling and not exclusively cooling and the middle not exclusively cool cycles of one-level throttling, can improve low-temperature heating capacity and COP, have certain help simultaneously to reduction compressor exhaust temperature.Shown in Fig. 1 is the accurate two-stage compression system and the lgP-h figure thereof that adopt band tonifying Qi to increase the screw compressor realization of enthalpy mouth, the position of the tonifying Qi increasing enthalpy mouth of screw compressor is designed according to certain working condition, tonifying Qi increases the position of enthalpy mouth once determine, the effect of its ability and reduction compressor exhaust temperature of improving low-temperature heating capacity just determines.Lay particular emphasis on the tonifying Qi improving low-temperature heating capacity and COP and increase enthalpy mouth, it significantly cannot reduce compressor exhaust temperature under condition of ultralow temperature.
For R32 air source heat pump or Teat pump boiler, under cryogenic, because delivery temperature is relatively not high, need to increase enthalpy by tonifying Qi and improve heating capacity and COP; And under condition of ultralow temperature, because now delivery temperature is very high, far beyond the permission delivery temperature of compressor, reduce compressor exhaust temperature more important than improving heating capacity.Under condition of ultralow temperature, only have adopt mend the mode of gas carrying liquid could at the prerequisite decline low exhaust temperature (ZL201220704004.4) guaranteeing compressor hiigh pressure stage air-breathing mass dryness fraction, and tonifying Qi increases the position direct impact to voltage level air-breathing mass dryness fraction of enthalpy mouth, therefore need the position increasing enthalpy mouth for condition of ultralow temperature design tonifying Qi.And the aforementioned a pair tonifying Qi increasing enthalpy mouth offered on screw compressor cannot meet this two demands simultaneously.
On screw compressor, to offer a pair tonifying Qi increase enthalpy mouth owing to existing in prior art and cannot take into account simultaneously increase enthalpy by tonifying Qi under cryogenic conditions and improve the technical problem lowering two demands of compressor exhaust temperature under heating performance and condition of ultralow temperature by mending gas carrying liquid, therefore research and design of the present invention goes out a kind of refrigeration system and control method thereof.
Summary of the invention
Therefore, the technical problem to be solved in the present invention is to overcome in prior art to offer on screw compressor under a pair tonifying Qi increasing enthalpy mouth cannot take into account cryogenic conditions simultaneously and increases by tonifying Qi the defect passing through two demands of mending gas carrying liquid attenuating compressor exhaust temperature under enthalpy improves heating performance and condition of ultralow temperature, thus provides a kind of refrigeration system and control method thereof.
The invention provides a kind of refrigeration system, comprise screw compressor, flash evaporation and hiigh pressure stage throttling arrangement, wherein said flash evaporation is provided with exhaust end, while described exhaust end is connected to and is pressed suction end by the first tonifying Qi branch road in first of described compressor, also be connected in second of described compressor by the second tonifying Qi branch road and press suction end, describedly press the pressure of suction end unequal in first, second, described system also comprises the control valve system controlling at least one road in two-way tonifying Qi branch road and be switched on or switched off.
Preferably, described control valve system comprises the first tonifying Qi magnetic valve be arranged on described first tonifying Qi branch road.
Preferably, described control valve system also comprises the second tonifying Qi magnetic valve be arranged on described second tonifying Qi branch road.
Preferably, the pressure of suction end is pressed to be less than the pressure of pressing suction end in described second in described first.
Preferably, press suction end to comprise in first in described first to press in gas supplementing opening one and first and press gas supplementing opening 2 two gas supplementing openings, and be arranged at the inside of two compression chambers of described compressor along the centre of gyration symmetrically.
Preferably, press suction end to comprise in second in described second to press in gas supplementing opening one and second and press gas supplementing opening 2 two gas supplementing openings, and be arranged at the inside of two compression chambers of described compressor along the centre of gyration symmetrically.
Preferably, press in gas supplementing opening one or described first to press in the angle θ 1 at the main shaft gyration angle of gas supplementing opening two and described second to press in gas supplementing opening one or the second to press between the angle θ 2 at the main shaft gyration angle of gas supplementing opening two in described first and meet θ 1< θ 2.
Preferably, the angle at the main shaft gyration angle of pressing gas supplementing opening two in gas supplementing opening one or described first is pressed in described first to meet 0.5 π≤θ 1≤1.75 π.
Preferably, the angle at the main shaft gyration angle of pressing gas supplementing opening two is pressed in gas supplementing opening one or the second in described second to meet 0.5 π≤θ 2≤4 π.
Preferably, the exhaust end of described flash evaporation comprises the first exhaust end and the second exhaust end, and described first exhaust end is connected in first of described compressor by described first tonifying Qi branch road and presses suction end, described second exhaust end is connected in second of described compressor by described second tonifying Qi branch road and presses suction end.
Preferably, the exhaust end of described flash evaporation is one, described exhaust end is connected to described first tonifying Qi branch road and described second tonifying Qi branch road by a total tonifying Qi branch road branch, the described first tonifying Qi branch road other end is connected in described first of described compressor presses suction end, and the described second tonifying Qi branch road other end is connected in described second of described compressor presses suction end.
Preferably, pipeline between described hiigh pressure stage throttling arrangement and the entrance point of described flash evaporation is also provided with bypass line, described flash evaporation is also provided with another entrance point, described bypass line is connected on another entrance point described, and is also provided with bypass throttle device on described bypass line.
Preferably, described refrigeration system is air source heat pump or Teat pump boiler.
Preferably, adopt R32 as the cold-producing medium of this refrigeration system.
The present invention also provides a kind of control method of refrigeration system, and it utilizes aforesaid refrigeration system to control to adjust it under different regulating working conditions.
Preferably, being switched on or switched off of at least one road in described control valve Systematical control two-way tonifying Qi branch road is used.
Preferably, when described control valve system comprises the first tonifying Qi magnetic valve and the second tonifying Qi magnetic valve, under worst cold case condition, open described first tonifying Qi magnetic valve, close the second tonifying Qi magnetic valve.
Preferably, when described control valve system comprises the first tonifying Qi magnetic valve and the second tonifying Qi magnetic valve, under ultralow-temperature operation conditions condition, open described second tonifying Qi magnetic valve, close described first tonifying Qi magnetic valve.
Preferably, when described control valve system comprises the first tonifying Qi magnetic valve and the second tonifying Qi magnetic valve, described first tonifying Qi magnetic valve and the second tonifying Qi magnetic valve are closed simultaneously.
Refrigeration system provided by the invention and control method thereof have following beneficial effect:
1. can meet refrigeration system simultaneously and be increased two demands of passing through to mend gas carrying liquid attenuating compressor exhaust temperature under enthalpy improves heating performance and condition of ultralow temperature under cryogenic by tonifying Qi;
2. take into account the low-temperature heating capacity of refrigeration system (especially R32 air source heat pump and Teat pump boiler) and the operational reliability of ultralow-temperature operation conditions that adopt screw compressor, widen the application condition range adopting the refrigeration system (especially R32 air source heat pump and Teat pump boiler) of screw compressor.
Accompanying drawing explanation
Fig. 1 is structural representation and the lgP-h figure thereof of the accurate two-stage compression system of prior art:
Wherein (1a) represents the structural representation of this accurate two-stage compression system; (1b) the lgP-h figure of this accurate two-stage compression system is represented;
Fig. 2 is structural representation and the lgP-h figure thereof of refrigeration system of the present invention (embodiment one):
Wherein (2a) represents the structural representation of refrigeration system of the present invention; (2b) the lgP-h figure of inventive refrigeration system is represented;
Fig. 3 is the structural representation for screw compressor tonifying Qi increasing enthalpy mouth position of the present invention;
Fig. 4 is the structural representation of another embodiment (embodiment two) of refrigeration system of the present invention.
In figure, Reference numeral is expressed as:
101-screw compressor, 102-condenser, 103-hiigh pressure stage throttling arrangement, 104-flash evaporation (also known as flash vessel), 105-low-pressure stage throttling arrangement, 106-evaporimeter, 107-the first tonifying Qi magnetic valve, 108-the second tonifying Qi magnetic valve, 109-bypass throttle device (also known as tonifying Qi branch road throttling arrangement), 110-Intermediate Heat Exchanger, gas supplementing opening one is pressed in 11-the first, press gas supplementing opening two in 12-the first, in 21-the second, press gas supplementing opening one, in 22-the second, press gas supplementing opening two.
Detailed description of the invention
As shown in Figure 1, the invention provides a kind of refrigeration system, comprise screw compressor 101, flash evaporation 104 and hiigh pressure stage throttling arrangement 103, wherein said flash evaporation 104 is provided with exhaust end, while described exhaust end is connected to and is pressed suction end by the first tonifying Qi branch road in first of described compressor, also be connected in second of described compressor by the second tonifying Qi branch road and press suction end, describedly press the pressure of suction end unequal in first, second, described system also comprises the control valve system controlling at least one road in two-way tonifying Qi branch road and be switched on or switched off.
Pressing suction end by two different pressures arranging two tonifying Qi branch roads and respectively two tonifying Qi branch roads are connected to described compressor, suction end can be pressed to carry out tonifying Qi effect to pressing in suction end or second in first of compressor according to the difference of actual conditions by control valve system simultaneously.Particularly: when system cloud gray model, at worst cold case, (worst cold case is for conventional air-conditioning operating mode herein, generally speaking worst cold case is lower than 10 DEG C, lower same) under, the suction end that centering pressure pressure is lower carries out tonifying Qi, and now intermediate pressure is relatively low, making hiigh pressure stage throttling mass dryness fraction, higher (pressure is lower, boiling point is lower, then gas can be more, then mass dryness fraction is higher), thus system tonifying Qi increases enthalpy successful, can significantly improve heating capacity and COP value, when system cloud gray model, at ultralow-temperature operation conditions, (ultralow-temperature operation conditions is for conventional air-conditioning operating mode herein, generally speaking lower than equaling-15 DEG C for ultralow-temperature operation conditions, lower same) under, the suction end that centering pressure pressure is higher carries out tonifying Qi, now intermediate pressure is relatively high, making hiigh pressure stage throttling mass dryness fraction, lower (pressure is higher, boiling point is higher, then gas can be fewer, then mass dryness fraction is lower), evaporator specific enthalpy raises (because increasing when entering the liquid relative low temperature in evaporimeter) simultaneously, make the lifting DeGrain of system heating capacity, but enter compressor because some refrigerant gas (state point 4 ') and/or refrigerant liquid (state point 8 ') increase enthalpy mouth by tonifying Qi, reduce hiigh pressure stage suction temperature, screw compressor hiigh pressure stage delivery temperature (state point 5 ') is significantly reduced.
So refrigeration system can be met by said structure and means to be increased two demands of passing through to mend gas carrying liquid attenuating compressor exhaust temperature under enthalpy improves heating performance and condition of ultralow temperature under cryogenic by tonifying Qi simultaneously; And taken into account the low-temperature heating capacity of refrigeration system (especially R32 air source heat pump and Teat pump boiler) and the operational reliability of ultralow-temperature operation conditions that adopt screw compressor, widen the application condition range adopting the refrigeration system (especially R32 air source heat pump and Teat pump boiler) of screw compressor.
Preferably, described control valve system comprises the first tonifying Qi magnetic valve 107 be arranged on described first tonifying Qi branch road.Effectively control action can be carried out to the break-make of this first tonifying Qi branch road by the first tonifying Qi magnetic valve be arranged on the first tonifying Qi branch road.
Preferably, described control valve system also comprises the second tonifying Qi magnetic valve 108 be arranged on described second tonifying Qi branch road.Effectively control action can be carried out to the break-make of this second tonifying Qi branch road by the second tonifying Qi magnetic valve be arranged on the second tonifying Qi branch road.
Preferably, the pressure of suction end is pressed to be less than the pressure of pressing suction end in described second in described first.This be one preferred embodiment, thus tonifying Qi when making to press in first suction end to carry out worst cold case increases enthalpy, and tonifying Qi when pressing suction end to carry out ultralow-temperature operation conditions in second increases enthalpy.(can certainly make in first, to press the pressure of suction end to be greater than the pressure of pressing suction end in described second, tonifying Qi when now just making to press in second suction end to carry out worst cold case increases enthalpy, and tonifying Qi when pressing suction end to carry out ultralow-temperature operation conditions in first increases enthalpy).
Preferably, press suction end to comprise in first in described first to press in gas supplementing opening 1 and first and press gas supplementing opening 2 12 two gas supplementing openings.Such object is to carry out tonifying Qi effect between two different minimum cylinder volumes to compression while of screw compressor simultaneously, improves efficiency and effect that tonifying Qi increases enthalpy.
Preferably, press suction end to comprise in second in described second to press in gas supplementing opening 1 and second and press gas supplementing opening 2 22 two gas supplementing openings.Such object be in order to press pressure of inspiration(Pi) different in relative first second in press pressure of inspiration(Pi) time, carry out tonifying Qi effect between two of compression while in screw compressor different minimum cylinder volumes simultaneously, improve in second efficiency and the effect of pressing suction end tonifying Qi to increase enthalpy.
Preferably, (pressing in first in gas supplementing opening 1 and first presses gas supplementing opening 2 12 to be arranged in two compression chambers of screw compressor inside respectively to press the angle θ 1 at the main shaft gyration angle of pressing gas supplementing opening 2 12 respective in gas supplementing opening 1 and described first in described first, and be symmetrical arranged along the centre of gyration) and described second in press and press the angle θ 2 of the position of gas supplementing opening 2 22 in gas supplementing opening 1 and second (pressing in second in gas supplementing opening 1 and second presses gas supplementing opening 2 22 to be arranged in two compression chambers of screw compressor inside respectively, and be symmetrical arranged along the centre of gyration) between meet θ 1< θ 2 (particularly, press in first in the angle θ 1 to the second at the main shaft gyration angle of gas supplementing opening 1 to press the angle θ 2 at the main shaft gyration angle of gas supplementing opening 1 little, or press in first in the angle θ 1 to the second at the main shaft gyration angle of gas supplementing opening 2 12 press the angle θ 2 at the main shaft gyration angle of gas supplementing opening 2 22 little).The object of such setting and effect press the pressure of inspiration(Pi) of gas supplementing opening (one and two) high in ensureing to press the pressure of inspiration(Pi) of gas supplementing opening (one and two) than first in second, thus in first, when making low temperature, press gas supplementing opening (one and two) tonifying Qi to increase enthalpy, in second, press gas supplementing opening (one and two) tonifying Qi to increase enthalpy during ultralow temperature.
Because scroll compressor compresses volume is
Wherein, P is involute pitch, mm; T is vortex wall thickness, mm; H is vortex height, mm; θ be main shaft gyration angle (main shaft gyration angle terminates to be 0 moment from breathing process, along with the rotation of dynamic vortex, the center of circle that main shaft (X-axis) crosses around X, Y and rotate the angle of formation and the position obtained).
Preferably, the angle of pressing the position of gas supplementing opening 2 12 in gas supplementing opening 1 and described first is pressed in described first to meet 0.5 π≤θ 1≤1.75 π.(shown in accompanying drawing 3)
Therefore being arranged within the scope of this by θ 1 is suction location in order to ensure good mesolow.
Further preferably, the angle of pressing the position of gas supplementing opening 2 12 in gas supplementing opening 1 and described first is pressed in described first to meet 0.5 π≤θ 1≤1.5 π.
Preferably, pressing in described second in gas supplementing opening 1 and second presses the angle of the position of gas supplementing opening 2 22 to meet 0.5 π≤θ 2≤4 π.Being arranged within the scope of this by θ 2 is suction location in order to ensure good mesohigh.
Further preferably, pressing in described second in gas supplementing opening 1 and second presses the angle of the position of gas supplementing opening 2 22 to meet 1.5 π≤θ 2≤3 π.
Further preferably, pressing in described second in gas supplementing opening 1 and second presses the angle of the position of gas supplementing opening 2 22 to meet 2 π≤θ 2≤3.75 π.
Preferably, the exhaust end of described flash evaporation 104 comprises the first exhaust end and the second exhaust end, and described first exhaust end is connected in first of described compressor by described first tonifying Qi branch road and presses suction end, described second exhaust end is connected in second of described compressor by described second tonifying Qi branch road and presses suction end.This is the concrete structure of the tonifying Qi increasing enthalpy of embodiments of the present invention one, and as shown in Figure 2, this is a kind of preferred structure and embodiment.
Preferably, the exhaust end of described flash evaporation 104 is one, described exhaust end is connected to described first tonifying Qi branch road and described second tonifying Qi branch road by a total tonifying Qi branch road branch, the described first tonifying Qi branch road other end is connected in described first of described compressor presses suction end, and the described second tonifying Qi branch road other end is connected in described second of described compressor presses suction end.This is the concrete structure of the tonifying Qi increasing enthalpy of embodiments of the present invention two, and as shown in Figure 4, this is another kind of preferred structure and embodiment.
Preferably, pipeline between described hiigh pressure stage throttling arrangement 103 and the entrance point of described flash evaporation (also known as making Intermediate Heat Exchanger 110) is also provided with bypass line, described flash evaporation is also provided with another entrance point, described bypass line is connected on another entrance point described, and on described bypass line, be also provided with bypass throttle device 109 (also known as making tonifying Qi branch road throttling arrangement 109).Make cold-producing medium by having 109 branch roads by reducing pressure by regulating flow by above-mentioned bypass throttle device and corresponding annexation, and play the effect of heat exchange between the cold-producing medium without 109 branch roads, effective reduction does not have the heat of the cold-producing medium in the branch road of 109, reaching cold degree, and making flash evaporation (here also known as making Intermediate Heat Exchanger 110) play the effect of intermediate heat transfer.Here preferably the Intermediate Heat Exchanger 110 at this place for being exactly dividing wall type Intermediate Heat Exchanger, as double-tube heat exchanger or the plate type heat exchanger of water and refrigerant heat exchanger.
Preferably, described refrigeration system is air source heat pump or Teat pump boiler.This is preferred kind and the structure of refrigeration system.
Preferably, adopt R32 as the cold-producing medium of this refrigeration system.This is the preferred refrigerant of inventive refrigeration system.
The present invention also provides a kind of control method of refrigeration system, and it utilizes aforesaid refrigeration system to control to adjust it under different working condition.By utilizing aforesaid refrigeration system to control to adjust it under different working condition, can reach to meet under refrigeration system increases enthalpy raising heating performance and condition of ultralow temperature by tonifying Qi under cryogenic simultaneously and passing through to mend two demands that gas carrying liquid lowers compressor exhaust temperature; And taken into account the low-temperature heating capacity of refrigeration system (especially R32 air source heat pump and Teat pump boiler) and the operational reliability of ultralow-temperature operation conditions that adopt screw compressor, widen the application condition range adopting the refrigeration system (especially R32 air source heat pump and Teat pump boiler) of screw compressor.
Preferably, use being switched on or switched off of at least one road in described control valve Systematical control two-way tonifying Qi branch road, control raising system heating capacity and COP to be reached by control valve system; Or reduce object and the effect of compressor exhaust temperature.
Preferably, when described control valve system comprises the first tonifying Qi magnetic valve 107 and the second tonifying Qi magnetic valve 108, described first tonifying Qi magnetic valve 1 is opened under worst cold case condition, close the second tonifying Qi magnetic valve 108, by the control operation method that this is concrete, to reach the object and effect that improve system heating capacity and COP under this working condition.
Preferably, when described control valve system comprises the first tonifying Qi magnetic valve 107 and the second tonifying Qi magnetic valve 108, described second tonifying Qi magnetic valve 108 is opened under ultralow-temperature operation conditions condition, close described first tonifying Qi magnetic valve 107, by the control operation method that this is concrete, to reach in the object of this working condition decline low compression machine delivery temperature and effect.
Preferably, when described control valve system comprises the first tonifying Qi magnetic valve 107 and the second tonifying Qi magnetic valve 108, described first tonifying Qi magnetic valve 107 and the second tonifying Qi magnetic valve 108 are closed simultaneously.By the control operation method that this is concrete, to realize not tonifying Qi, realize object and the effect of conventional refrigerant operation.
Preferably, described first tonifying Qi magnetic valve 107 and the second tonifying Qi magnetic valve 108 can not be opened simultaneously, if this is because the part of the words of opening so in compressor between these two gas supplementing openings cannot realize compression simultaneously, and may produce other problems.
Introduce the preferred embodiments of the present invention below
Embodiment one
The present invention proposes a kind of refrigerating plant, described refrigerating plant is made up of screw compressor 101, condenser 102, hiigh pressure stage throttling arrangement 103, flash evaporation 104, low-pressure stage throttling arrangement 105, evaporimeter 106 and the first tonifying Qi magnetic valve 107 and the second tonifying Qi magnetic valve 108 etc., described screw compressor offers two pairs of gas supplementing openings, wherein press gas supplementing opening 1 in first and press gas supplementing opening 2 12 in first and be connected with the first tonifying Qi magnetic valve 107, press gas supplementing opening 1 in second and press gas supplementing opening 2 22 in second and be connected with the second tonifying Qi magnetic valve 108.
Under normal temperature and worst cold case condition, first tonifying Qi magnetic valve 107 is opened, second tonifying Qi magnetic valve 108 cuts out, system major cycle is: screw compressor sucks the refrigerant superheat gas (corresponding lgP-h figure state point 1) of low-temp low-pressure, the refrigerant superheat gas (state point 2) of medium temperature and medium pressure is become after low-pressure stage compression, the refrigerant superheat gas (state point 5) becoming HTHP after (state point 3) compresses by hiigh pressure stage is mixed with the refrigerant gas covered through gas supplementing opening, then be discharged in condenser, condensation heat release within the condenser, become the cold-producing medium subcooled liquid (state point 6) of HTHP, after hiigh pressure stage throttling arrangement reducing pressure by regulating flow, become the cold-producing medium two-phase mixture (state point 7) of pressing in low temperature enter flash evaporation, cold-producing medium in flash evaporation is divided into two parts, the cold-producing medium two-phase mixture (state point 9) that wherein refrigerant liquid (state point 8) becomes low-temp low-pressure after low-pressure stage throttling arrangement reducing pressure by regulating flow enters evaporimeter, evaporation endothermic in evaporimeter, the refrigerant superheat gas (state point 1) becoming low-temp low-pressure enters screw compressor, complete a circulation.Tonifying Qi branch road is: (intermediate pressure that pressure is relatively low) tonifying Qi that another part refrigerant gas (state point 4) in flash evaporation enters screw compressor through the first tonifying Qi magnetic valve 107 increases enthalpy mouth, the refrigerant superheat gas (state point 2) compressed with low-pressure stage mixes (state point 3), then continues compression until discharge compressor (state point 5).Now intermediate pressure is relatively low, makes one-level throttling mass dryness fraction higher, and system tonifying Qi increases enthalpy successful, can significantly improve heating capacity and COP.
Under ultralow-temperature operation conditions condition, first tonifying Qi magnetic valve 107 cuts out, second magnetic valve 108 is opened, system major cycle is: screw compressor sucks the refrigerant superheat gas (corresponding lgP-h figure state point 1) of low-temp low-pressure, the refrigerant superheat gas (state point 2 ') of medium temperature and medium pressure is become after low-pressure stage compression, the refrigerant superheat gas (state point 5 ') becoming HTHP after (state point 3 ') compresses by hiigh pressure stage is mixed with the cold-producing medium two-phase mixture covered through gas supplementing opening, then be discharged in condenser, condensation heat release within the condenser, become the cold-producing medium subcooled liquid (state point 6) of HTHP, after hiigh pressure stage throttling arrangement reducing pressure by regulating flow, become the cold-producing medium two-phase mixture (state point 7 ') of pressing in low temperature enter flash evaporation, cold-producing medium in flash evaporation is divided into two parts, the cold-producing medium two-phase mixture (state point 9 ') that wherein refrigerant liquid (state point 8 ') becomes low-temp low-pressure after low-pressure stage throttling arrangement reducing pressure by regulating flow enters evaporimeter, evaporation endothermic in evaporimeter, the refrigerant superheat gas (state point 1) becoming low-temp low-pressure enters screw compressor, complete a circulation.Tonifying Qi branch road is: the tonifying Qi that another part refrigerant liquid (state point 8 ') in flash evaporation and gas (state point 4 ') enter screw compressor (intermediate pressure that pressure is relatively high) through magnetic valve 2 increases enthalpy mouth, the refrigerant superheat gas (state point 2 ') compressed with low-pressure stage mixes (state point 3 '), then continues compression until discharge compressor (state point 5 ').Now intermediate pressure is relatively high, make one-level throttling mass dryness fraction lower, evaporator specific enthalpy raises simultaneously, make the lifting DeGrain of system heating capacity, but enter compressor because some refrigerant liquid (state point 8 ') increases enthalpy mouth by tonifying Qi, reduce hiigh pressure stage suction temperature, screw compressor hiigh pressure stage delivery temperature is significantly reduced.
Scroll compressor compresses volume is
Wherein: P is involute pitch, mm; T is vortex wall thickness, mm; H is vortex height, mm; θ is main shaft gyration angle.
The angle of pressing the position of gas supplementing opening 2 12 in gas supplementing opening 1 and first is pressed to meet 0.5 π≤θ 1≤1.75 π in described first
Further, pressing in described first in gas supplementing opening 1 and first presses the angle of the position of gas supplementing opening 2 12 to meet 0.5 π≤θ 1≤1.5 π
The angle of pressing the position of gas supplementing opening 2 22 in gas supplementing opening 1 and second is pressed to meet 0.5 π≤θ 2≤4 π in described second
Further, pressing in described second in gas supplementing opening 1 and second presses the angle of the position of gas supplementing opening 2 22 to meet 1.5 π≤θ 2≤3 π
Further, pressing in described second in gas supplementing opening 1 and second presses the angle of the position of gas supplementing opening 2 22 to meet 2 π≤θ 2≤3.75 π
Further, pressing in described first in gas supplementing opening 1 and first to press in the angle θ 1 of the position of gas supplementing opening 2 12 and described second to press in gas supplementing opening 1 and second presses the angle θ 2 of the position of gas supplementing opening 2 22 to meet θ 1< θ 2.
Embodiment two
As shown in Figure 4, the present invention proposes a kind of refrigerating plant, described refrigerating plant is by screw compressor 101, condenser 102, hiigh pressure stage throttling arrangement 103, tonifying Qi branch road throttling arrangement 109, Intermediate Heat Exchanger 110, low-pressure stage throttling arrangement 105, evaporimeter 106 and the composition such as the first tonifying Qi magnetic valve 107 and the second tonifying Qi magnetic valve 108, described screw compressor offers two pairs of gas supplementing openings, wherein press gas supplementing opening 1 in first and press gas supplementing opening 2 12 in first and be connected with the first tonifying Qi magnetic valve 107, press gas supplementing opening 1 in second and press gas supplementing opening 2 22 in second and be connected with the second tonifying Qi magnetic valve 108.
Those skilled in the art will readily understand, under the prerequisite of not conflicting, above-mentioned each advantageous manner freely can combine, superpose.
The foregoing is only preferred embodiment of the present invention, not in order to limit the present invention, all any amendments done within the spirit and principles in the present invention, equivalent replacement and improvement etc., all should be included within protection scope of the present invention.The above is only the preferred embodiment of the present invention; it should be pointed out that for those skilled in the art, under the prerequisite not departing from the technology of the present invention principle; can also make some improvement and modification, these improve and modification also should be considered as protection scope of the present invention.
Claims (19)
1. a refrigeration system, comprise screw compressor (101), flash evaporation (104) and hiigh pressure stage throttling arrangement (103), it is characterized in that: described flash evaporation (104) is provided with exhaust end, while described exhaust end is connected to and is pressed suction end by the first tonifying Qi branch road in first of described compressor, also be connected in second of described compressor by the second tonifying Qi branch road and press suction end, describedly press the pressure of suction end unequal in first, second, described system also comprises the control valve system controlling at least one road in two-way tonifying Qi branch road and be switched on or switched off.
2. refrigeration system according to claim 1, is characterized in that: described control valve system comprises the first tonifying Qi magnetic valve (107) be arranged on described first tonifying Qi branch road.
3. refrigeration system according to claim 2, is characterized in that: described control valve system also comprises the second tonifying Qi magnetic valve (108) be arranged on described second tonifying Qi branch road.
4. according to the refrigeration system one of claim 1-3 Suo Shu, it is characterized in that: in described first, press the pressure of suction end to be less than the pressure of pressing suction end in described second.
5. refrigeration system according to claim 4, it is characterized in that: press suction end to comprise in first in described first to press in gas supplementing opening one (11) and first and press gas supplementing opening two (12) two gas supplementing openings, and be arranged at the inside of two compression chambers of described compressor along the centre of gyration symmetrically.
6. refrigeration system according to claim 5, it is characterized in that: press suction end to comprise in second in described second to press in gas supplementing opening one (21) and second and press gas supplementing opening two (22) two gas supplementing openings, and be arranged at the inside of two compression chambers of described compressor along the centre of gyration symmetrically.
7. refrigeration system according to claim 6, is characterized in that: press in described first in gas supplementing opening one (11) or described first to press in the angle θ 1 at the main shaft gyration angle of gas supplementing opening two (12) and described second to press in gas supplementing opening one (21) or second to press between the angle θ 2 at the main shaft gyration angle of gas supplementing opening two (22) and meet θ 1< θ 2.
8. according to the refrigeration system one of claim 5-7 Suo Shu, it is characterized in that: in described first, press the angle of pressing the main shaft gyration angle of gas supplementing opening two (12) in gas supplementing opening one (11) or described first to meet 0.5 π≤θ 1≤1.75 π.
9. according to the refrigeration system one of claim 6-7 Suo Shu, it is characterized in that: in described second, press the angle of pressing the main shaft gyration angle of gas supplementing opening two (22) in gas supplementing opening one (21) or second to meet 0.5 π≤θ 2≤4 π.
10. according to the refrigeration system one of claim 1-9 Suo Shu, it is characterized in that: the exhaust end of described flash evaporation (104) comprises the first exhaust end and the second exhaust end, and described first exhaust end is connected in first of described compressor by described first tonifying Qi branch road and presses suction end, described second exhaust end is connected in second of described compressor by described second tonifying Qi branch road and presses suction end.
11. according to the refrigeration system one of claim 1-9 Suo Shu, it is characterized in that: the exhaust end of described flash evaporation (104) is one, described exhaust end is connected to described first tonifying Qi branch road and described second tonifying Qi branch road by a total tonifying Qi branch road branch, the described first tonifying Qi branch road other end is connected in described first of described compressor presses suction end, and the described second tonifying Qi branch road other end is connected in described second of described compressor presses suction end.
12. refrigeration systems according to claim 11, it is characterized in that: the pipeline between described hiigh pressure stage throttling arrangement (103) and the entrance point of described flash evaporation (104) is also provided with bypass line, described flash evaporation is also provided with another entrance point, described bypass line is connected on another entrance point described, and on described bypass line, be also provided with bypass throttle device (109).
13., according to the refrigeration system one of claim 1-12 Suo Shu, is characterized in that: described refrigeration system is air source heat pump or Teat pump boiler.
14., according to the refrigeration system one of claim 1-13 Suo Shu, is characterized in that: adopt R32 as the cold-producing medium of this refrigeration system.
The control method of 15. 1 kinds of refrigeration systems, is characterized in that: utilize the described refrigeration system of one of claim 1-14 to control to adjust it under different working condition.
16. control methods according to claim 15, is characterized in that: use being switched on or switched off of at least one road in described control valve Systematical control two-way tonifying Qi branch road.
17. control methods according to claim 16, it is characterized in that: when described control valve system comprises the first tonifying Qi magnetic valve (107) and second tonifying Qi magnetic valve (108), under worst cold case condition, open described first tonifying Qi magnetic valve (107), close the second tonifying Qi magnetic valve (108).
18. control methods according to claim 16, it is characterized in that: when described control valve system comprises the first tonifying Qi magnetic valve (107) and second tonifying Qi magnetic valve (108), under ultralow-temperature operation conditions condition, open described second tonifying Qi magnetic valve (108), close described first tonifying Qi magnetic valve (107).
19. control methods according to claim 16, it is characterized in that: when described control valve system comprises the first tonifying Qi magnetic valve (107) and second tonifying Qi magnetic valve (108), described first tonifying Qi magnetic valve (107) and the second tonifying Qi magnetic valve (108) are closed simultaneously.
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