CN111288675A - Mixed working medium refrigerating system and air conditioner - Google Patents
Mixed working medium refrigerating system and air conditioner Download PDFInfo
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- CN111288675A CN111288675A CN202010124846.1A CN202010124846A CN111288675A CN 111288675 A CN111288675 A CN 111288675A CN 202010124846 A CN202010124846 A CN 202010124846A CN 111288675 A CN111288675 A CN 111288675A
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- 238000001704 evaporation Methods 0.000 claims abstract description 149
- 230000008020 evaporation Effects 0.000 claims abstract description 149
- 239000003507 refrigerant Substances 0.000 claims abstract description 131
- 239000007788 liquid Substances 0.000 claims abstract description 79
- 238000000926 separation method Methods 0.000 claims abstract description 48
- 239000012530 fluid Substances 0.000 claims abstract description 16
- 238000011084 recovery Methods 0.000 claims description 25
- 238000005057 refrigeration Methods 0.000 claims description 21
- 238000000034 method Methods 0.000 claims description 16
- 238000001816 cooling Methods 0.000 claims description 12
- 238000011144 upstream manufacturing Methods 0.000 claims description 6
- 238000007664 blowing Methods 0.000 claims description 4
- 230000000694 effects Effects 0.000 abstract description 11
- 238000009833 condensation Methods 0.000 abstract description 8
- 230000005494 condensation Effects 0.000 abstract description 8
- 239000000306 component Substances 0.000 description 27
- 238000009835 boiling Methods 0.000 description 20
- 230000001965 increasing effect Effects 0.000 description 20
- 239000002184 metal Substances 0.000 description 16
- 230000008569 process Effects 0.000 description 14
- 230000002427 irreversible effect Effects 0.000 description 7
- 230000008859 change Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 6
- 230000002708 enhancing effect Effects 0.000 description 5
- 230000006872 improvement Effects 0.000 description 4
- 239000000203 mixture Substances 0.000 description 4
- 238000004781 supercooling Methods 0.000 description 4
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 229920006395 saturated elastomer Polymers 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 239000012533 medium component Substances 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000001172 regenerating effect Effects 0.000 description 1
- 239000013526 supercooled liquid Substances 0.000 description 1
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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
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
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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
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
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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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/06—Superheaters
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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
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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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/02—Details of evaporators
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention provides a mixed working medium refrigerating system and an air conditioner, wherein the mixed working medium refrigerating system comprises: the air conditioner comprises a compressor, a condenser, a throttling device, a first evaporator and a second evaporator, wherein the inlet of the first evaporator can be communicated with the throttling device or the condenser, and the outlet end of the second evaporator can be communicated to the air suction end of the compressor; a gas-liquid separation device is further arranged between the outlet end of the first evaporator and the inlet end of the second evaporator and provided with a refrigerant inlet end, a gas outlet end and a liquid outlet end, the refrigerant inlet end is communicated with the outlet end of the first evaporator, the gas outlet end is communicated to the air suction end of the compressor, and the liquid outlet end is communicated to the inlet end of the second evaporator. The invention effectively increases the integral evaporation sliding temperature of the mixed working medium, realizes the step heat exchange between the refrigerant and the heat exchange fluid, improves the heat exchange effect, does not cause the increase of the condensation temperature, reduces the pressure drop of the system and effectively improves the energy efficiency of the system.
Description
Technical Field
The invention belongs to the technical field of refrigeration, and particularly relates to a mixed working medium refrigeration system and an air conditioner.
Background
The dual-temperature cycle can improve the energy efficiency of the system due to the fact that irreversible loss in the heat exchange process can be reduced, and cascade utilization of energy can be achieved to a certain extent, so that the dual-temperature cycle is widely concerned. Aiming at the problem of complex system of the traditional pure working medium double-temperature circulation, a patent with the patent number of 201811351926.X discloses a novel double-temperature circulation scheme based on the component separation characteristic of a mixed working medium, the scheme adopts a conventional single-stage compressor to realize double evaporation temperature, the system energy efficiency is effectively improved by increasing the sliding temperature in the evaporation process, and the structure is simple; however, there is a disadvantage in that the slip temperature during condensation increases to the detriment of performance improvement.
Because the small temperature difference heat exchange effect in the evaporation process of the dual-temperature mixed working medium system in the prior art is not obvious (the temperature slippage is small), the heat exchange efficiency is low, and the pressure drop of the evaporator is large; and the method of separating working medium at the condenser side is adopted to improve the sliding temperature in the evaporation process, so that the condensation temperature is increased, the compression ratio is increased, the compression power consumption is increased, the effect improvement effect is greatly reduced and the like, so that the mixed working medium refrigeration system and the air conditioner are researched and designed.
Disclosure of Invention
Therefore, the technical problem to be solved by the invention is to overcome the defects that the dual-temperature mixed working medium system in the prior art cannot improve the sliding temperature in the evaporation process, simultaneously can ensure that the condensation temperature cannot be increased, and the energy efficiency cannot be obviously improved, thereby providing the mixed working medium refrigeration system and the air conditioner.
The invention provides a mixed working medium refrigerating system, which comprises:
the air conditioner comprises a compressor, a condenser, a throttling device, a first evaporator and a second evaporator, wherein the inlet of the first evaporator can be communicated with the throttling device or the condenser, and the outlet end of the second evaporator can be communicated to the air suction end of the compressor;
a gas-liquid separation device is further arranged between the outlet end of the first evaporator and the inlet end of the second evaporator, the gas-liquid separation device is provided with a refrigerant inlet end, a gas outlet end and a liquid outlet end, the refrigerant inlet end is communicated with the outlet end of the first evaporator, the gas outlet end is communicated to the suction end of the compressor, and the liquid outlet end is communicated to the inlet end of the second evaporator.
Preferably, the first and second electrodes are formed of a metal,
the first evaporator comprises a first evaporation passage a and a first evaporation passage b, wherein a refrigerant flows through the first evaporation passage a, the inlet end of the first evaporation passage a is communicated with the throttling device, the outlet end of the first evaporation passage a is communicated with the refrigerant inlet end of the gas-liquid separation device, and a fluid to be cooled flows through the first evaporation passage b;
the second evaporator includes a second evaporation passage a through which a refrigerant flows, an inlet of the second evaporation passage a being communicated with the liquid outlet end of the gas-liquid separation device, an outlet end of the second evaporation passage a being communicated with a suction end of the compressor, and a second evaporation passage b through which the fluid to be cooled flows; and the first evaporation passage b is communicated with the second evaporation passage b, and the fluid to be cooled firstly enters the second evaporation passage b for cooling and then enters the first evaporation passage b for cooling.
Preferably, the first and second electrodes are formed of a metal,
the first evaporator further includes a first evaporation passage c through which a refrigerant flows, an inlet of the first evaporation passage c being communicable with the condenser, an outlet thereof being communicable with the throttle device, the other end of the throttle device being communicable with an inlet end of the first evaporation passage a, an outlet thereof being communicable with the refrigerant inlet end of the gas-liquid separation device.
Preferably, the first and second electrodes are formed of a metal,
the first evaporator comprises a first evaporation passage a ', refrigerant flows through the first evaporation passage a', the inlet of the first evaporation passage a 'is communicated with the throttling device, and the outlet end of the first evaporation passage a' is communicated with the refrigerant inlet end of the gas-liquid separation device;
the second evaporator comprises a second evaporation passage a ', refrigerant flows through the second evaporation passage a', and the inlet of the second evaporation passage a 'is communicated with the liquid outlet end of the gas-liquid separation device, and the outlet end of the second evaporation passage a' is communicated with the suction end of the compressor;
the air conditioner also comprises a fan, and the fan can firstly flow air through the second evaporator for heat exchange through blowing or air suction and then flow air through the first evaporator for heat exchange.
Preferably, the first and second electrodes are formed of a metal,
the fan is arranged on the upstream side of the air flow of the first evaporator and the second evaporator, the second evaporator is positioned on the upstream of the first evaporator along the air flow path, the fan blows air into the second evaporator firstly in a blowing mode for heat exchange, and the air after the heat exchange of the second evaporator enters the first evaporator for heat exchange.
Preferably, the first and second electrodes are formed of a metal,
the heat regenerator is arranged between the condenser and the throttling device and comprises a first heat recovery passage and a second heat recovery passage, heat exchange can be carried out between the first heat recovery passage and the second heat recovery passage, the inlet end of the first heat recovery passage is communicated to the outlet end of the condenser, the outlet end of the first heat recovery passage can be communicated to the throttling device or the first evaporator, the inlet end of the second heat recovery passage is communicated to the gas outlet end of the gas-liquid separation device, and the outlet end of the second heat recovery passage is communicated to the gas suction end of the compressor.
Preferably, the first and second electrodes are formed of a metal,
when the first evaporator includes only a first evaporation passage a and a first evaporation passage b, the outlet end of the first recuperation passage is communicated to the throttling device;
when the first evaporator includes a first evaporation passage a, a first evaporation passage b, and a first evaporation passage c at the same time, the outlet end of the first recuperation passage is communicated to the inlet end of the first evaporation passage c of the first evaporator.
Preferably, the first and second electrodes are formed of a metal,
the refrigerant discharged from the gas outlet end of the gas-liquid separation device is mixed with the refrigerant discharged from the refrigerant outlet end of the second evaporator through a pipeline and then enters the compressor, and a pressure balance device is arranged at the mixing position, so that the refrigerant discharged from the gas outlet end and the refrigerant discharged from the refrigerant outlet end of the second evaporator are mixed in the pressure balance device.
Preferably, the first and second electrodes are formed of a metal,
the first evaporator is a finned tube heat exchanger, a sleeve type heat exchanger or a plate type heat exchanger; and/or the second evaporator is a finned tube heat exchanger, a double-tube heat exchanger or a plate heat exchanger; and/or the condenser is a finned tube heat exchanger, a double-tube heat exchanger or a plate heat exchanger; and/or the mixed working medium comprises R32 and R134 a.
The invention also provides an air conditioner which comprises the mixed working medium refrigerating system.
The mixed working medium refrigerating system and the air conditioner provided by the invention have the following beneficial effects:
the invention arranges two evaporators in series, a gas-liquid separating device is arranged between the two evaporators, liquid separated from gas and liquid is introduced into the second evaporator for heat exchange, the separated gas is introduced to the air suction end of the compressor, so that the mixed working medium is firstly mixed, evaporated and absorbed in the first evaporator and then passes through the gas-liquid separating device for gas-liquid separation before entering the second evaporator, the low boiling point working medium easy to evaporate evaporates into gas after passing through the first evaporator after absorbing heat, the high boiling point working medium is less evaporated and still liquid, so the gas refrigerant rich in the low boiling point working medium is separated and discharged from the gas outlet, the liquid refrigerant rich in the high boiling point working medium is discharged from the liquid outlet and enters the second evaporator for further evaporation, the integral evaporation slip temperature of the mixed working medium is effectively increased, and the heat exchange between the refrigerant and the heat exchange fluid is effectively realized along the flow direction of the refrigerant, Namely, the heat exchange with small temperature difference (the temperature difference is smaller), thereby improving the heat exchange effect and reducing the irreversible loss in the heat exchange process; the saturation temperature of the evaporation outlet end of the compressor is effectively increased through the increase of the evaporation slip temperature, the suction pressure of the inlet end of the compressor is increased, and the condensation temperature of the condenser end is kept unchanged, so that the condensation temperature cannot be increased, the power consumption of the compressor is effectively reduced, and the energy efficiency of the system is obviously improved; meanwhile, the evaporated gas refrigerant is separated in advance, so that the pressure loss of the refrigerant of the evaporator can be reduced, and the energy efficiency of the system is further improved.
Drawings
FIG. 1 is a schematic structural diagram of embodiment 1 of the mixed working medium refrigeration system of the present invention;
FIG. 2 is a schematic structural diagram of embodiment 2 of the mixed working medium refrigeration system of the present invention;
FIG. 3 is a schematic structural diagram of embodiment 3 of the mixed refrigerant refrigeration system of the present invention;
FIG. 4 is a schematic structural diagram of embodiment 4 of the mixed refrigerant refrigeration system of the present invention;
FIG. 5 is a schematic structural diagram of embodiment 5 of the mixed refrigerant refrigeration system of the present invention;
fig. 6 is a schematic structural diagram of embodiment 6 of the mixed working medium refrigeration system of the invention.
The reference numbers in the figures denote:
1. a compressor; 2. a condenser; 3. a throttling device; 41. a first evaporator; 41a, a first evaporation passage a; 41b, a first evaporation passage b; 41c, a first evaporation passage c; 41a ', a first evaporation passage a'; 42. a second evaporator; 42a, a second evaporation passage a; 42b, a second evaporation passage b; 5. a gas-liquid separation device; 51. a refrigerant inlet end; 52. a gas outlet end; 53. a liquid outlet end; 6. a fan; 7. a heat regenerator; 71. a first recuperation path; 72. a second regenerative path; 8. a pressure balancing device.
Detailed Description
As shown in fig. 1 to 6, the present invention provides a mixed refrigerant refrigerating system, which comprises:
the system comprises a compressor 1, a condenser 2, a throttling device 3, a first evaporator 41 and a second evaporator 42, wherein the inlet of the first evaporator 41 can be communicated with the throttling device 3 or the condenser 2, and the outlet end of the second evaporator 42 can be communicated to the suction end of the compressor 1; (the first evaporator and the second evaporator can be two flow paths of a heat exchanger, the refrigerant temperature of the flow path of the first evaporator is lower than that of the flow path of the second evaporator, the heat exchange medium firstly passes through a high-temperature flow path and then passes through a low-temperature flow path, the evaporation temperatures of the two flow paths are different, one is high temperature and the other is low temperature, and the key point is that the heat exchange medium (air, water and the like) firstly passes through the high-temperature flow path and then passes through the low-temperature flow path.) the refrigerant used in the system circulation is non-azeotropic mixed refrigerant. The dryness of the refrigerant at the inlet of the gas-liquid separation device is 0.35-0.85;
a gas-liquid separation device 5 is further disposed between the outlet end of the first evaporator 41 and the inlet end of the second evaporator 42, the gas-liquid separation device 5 has a refrigerant inlet end 51, a gas outlet end 52 and a liquid outlet end 53, the refrigerant inlet end 51 is communicated with the outlet end of the first evaporator 41, the gas outlet end 52 is communicated to the suction end of the compressor 1, and the liquid outlet end 53 is communicated to the inlet end of the second evaporator 42.
The invention arranges two evaporators in series, a gas-liquid separating device is arranged between the two evaporators, liquid separated from gas and liquid is introduced into the second evaporator for heat exchange, the separated gas is introduced to the air suction end of the compressor, so that the mixed working medium is firstly mixed, evaporated and absorbed in the first evaporator and then passes through the gas-liquid separating device for gas-liquid separation before entering the second evaporator, the low boiling point working medium easy to evaporate evaporates into gas after passing through the first evaporator after absorbing heat, the high boiling point working medium is less evaporated and still liquid, so the gas refrigerant rich in the low boiling point working medium is separated and discharged from the gas outlet, the liquid refrigerant rich in the high boiling point working medium is discharged from the liquid outlet and enters the second evaporator for further evaporation, the integral evaporation slip temperature of the mixed working medium is effectively increased, and the heat exchange between the refrigerant and the heat exchange fluid is effectively realized along the flow direction of the refrigerant, Namely, the heat exchange with small temperature difference (the temperature difference is smaller), thereby improving the heat exchange effect and reducing the irreversible loss in the heat exchange process; the saturation temperature of the evaporation outlet end of the condenser is effectively increased through the increase of the evaporation slip temperature, the suction pressure of the inlet end of the compressor is increased, and the condensation temperature of the condenser end is kept unchanged, so that the condensation temperature cannot be increased, the power consumption of the compressor is effectively reduced, and the energy efficiency of the system is remarkably improved; meanwhile, the evaporated gas refrigerant is separated in advance, so that the pressure loss of the refrigerant of the evaporator can be reduced, and the energy efficiency of the system is further improved.
Fig. 1 shows an operation mode of a refrigeration apparatus, a high-temperature high-pressure mixed refrigerant coming out of an exhaust port of a compressor 1 is condensed into a supercooled liquid by outdoor air through a condenser 2 and enters a heat regenerator 7, the mixed refrigerant further cooled in the heat regenerator 7 enters a first evaporator 41 to exchange heat with a low-temperature refrigerant again, then enters a throttling device 3 to be throttled into a low-temperature low-pressure two-phase refrigerant, and then is evaporated into a high-dryness two-phase refrigerant through the first evaporator 41 to enter a gas-liquid separation device 5, and low-boiling-point components in the mixed refrigerant are easy to evaporate; in the gas-liquid separation device 5, the mixed refrigerant is in a phase equilibrium state, wherein the gas refrigerant is rich in the low boiling point component, and the liquid refrigerant is rich in the high boiling point component; the refrigerant liquid rich in the high boiling point component is branched and fed into the second evaporator 42 to be evaporated into a saturated or superheated gas, and this part of the refrigerant is mixed with the gaseous refrigerant rich in the low boiling point component, which is heated from the gas-liquid separation device 5, by the pressure equalizing device 8, and the mixed refrigerant is fed into the suction port of the compressor 1. When the flow direction of the heat exchange fluid is seen, the heat exchange fluid is cooled by the second evaporator 42 and then further cooled by the first evaporator 41, so that high-temperature chilled water and low-temperature chilled water can be supplied to different occasions. Since the components of the mixed refrigerant in the two evaporators are different from each other, and the high boiling point component in the second evaporator 42 is larger in the first evaporator 41 than in the second evaporator 42, the temperature at which the phase change occurs in the second evaporator 42 is higher, that is, the evaporation temperature is high, at the same pressure; in addition, the mixed refrigerant is arranged in the evaporator, so that the evaporation temperature of the refrigerant is increased along the flowing direction of the refrigerant, the heat exchange with the heat exchange fluid is realized to be small-temperature-difference heat exchange, and the irreversible loss of the heat exchange is reduced.
The evaporated low boiling point component is separated in advance through gas-liquid separation in the evaporation process, the high boiling point component refrigerant is further evaporated, the pressure loss in the evaporation process is reduced, the heat exchange coefficient is improved, meanwhile, the temperature slippage of the mixed working medium is improved, namely, the temperature difference of high-temperature evaporation temperature and low-temperature evaporation temperature is increased (for a specific mixed refrigerant, the temperature slippage is certain, namely, the phase change temperature difference between an evaporator inlet and an evaporator outlet is certain when the evaporation pressure is constant, but the system provided by the invention changes the components of one evaporator through component separation, further improves the phase change temperature of the evaporator outlet, namely, increases the temperature difference), realizes the step temperature reduction of the air side and the small temperature difference heat exchange, reduces the irreversible loss in the heat exchange process, meanwhile, the suction pressure of the compressor is improved, the power consumption of the compressor is reduced, and the energy efficiency of the system is finally improved. The arrangement of the three-channel heat exchanger and the heat regenerator not only increases the supercooling degree, reduces the inlet dryness of the evaporator, improves the evaporation performance, but also increases the temperature slippage of the mixed working medium.
Preferably, the first and second electrodes are formed of a metal,
the first evaporator 41 comprises a first evaporation passage a41a and a first evaporation passage b41b, wherein refrigerant circulates in the first evaporation passage a41a, the inlet of the first evaporation passage a41a is communicated with the throttling device 3, the outlet end of the first evaporation passage a41a is communicated with the refrigerant inlet end 51 of the gas-liquid separation device 5, and fluid to be cooled circulates in the first evaporation passage b41 b;
the second evaporator 42 includes a second evaporation passage a42a and a second evaporation passage b42b, refrigerant flows through the second evaporation passage a42a, an inlet of the second evaporation passage a42a communicates with the liquid outlet end 53 of the gas-liquid separation device 5, an outlet of the second evaporation passage a42a communicates with a suction end of the compressor 1, and the fluid to be cooled flows through the second evaporation passage b42 b; and the first evaporation passage b41b is communicated with the second evaporation passage b42b, and the fluid to be cooled firstly enters the second evaporation passage b42b to be cooled and then enters the first evaporation passage b41b to be cooled.
This is the preferred structure form in embodiments 1, 2, 3, 5 of the present invention, as shown in fig. 1, 2, 3, 5, that is, heat is released to the refrigerant of the two evaporators by the fluid to be cooled, the mixed working medium flows through the first evaporation passage a of the first evaporator and evaporates therein, the liquid to be cooled flowing through the first evaporation passage b is subjected to the secondary cooling effect, the mixed working medium rich in high boiling point component flows through the second evaporation passage a of the second evaporator and evaporates therein, and the liquid to be cooled flowing through the second evaporation passage b is subjected to the primary cooling effect, thereby effectively realizing the step small temperature difference heat transfer and cooling, improving the evaporation temperature glide, and enhancing the heat exchange efficiency.
Preferably, the first and second electrodes are formed of a metal,
the first evaporator 41 further includes a first evaporation passage c41c, refrigerant flows through the first evaporation passage c41c, an inlet of the first evaporation passage c41c is connectable to the condenser 2, an outlet thereof is connected to the expansion device 3, and the other end of the expansion device 3 is connected to an inlet of the first evaporation passage a41a, and an outlet of the first evaporation passage a41a is connected to the refrigerant inlet 51 of the gas-liquid separator 5. This is a further preferable configuration of the present invention, that is, embodiments 1 and 2, and as shown in fig. 1 and 2, the refrigerant before entering the first evaporation passage a can be further cooled by the additional first evaporation passage c, so that the degree of supercooling of the refrigerant is further increased, and the evaporation heat exchange efficiency and the evaporation amount are further increased.
Preferably, the first and second electrodes are formed of a metal,
the first evaporator 41 includes a first evaporation passage a '41 a', through which refrigerant flows, and an inlet of the first evaporation passage a '41 a' communicates with the throttle device 3 and an outlet thereof communicates with the refrigerant inlet port 51 of the gas-liquid separation device 5;
the second evaporator 42 includes a second evaporation passage a '42 a', through which refrigerant flows, and an inlet of the second evaporation passage a '42 a' is communicated with the liquid outlet end 53 of the gas-liquid separation device, and an outlet thereof is communicated with a suction end of the compressor 1;
the air conditioner also comprises a fan 6, wherein the fan 6 can blow air or suck air to firstly flow through the second evaporator 42 for heat exchange and then flow through the first evaporator 41 for heat exchange.
This is the preferred structure form of embodiments 4 and 6 of the present invention, as shown in fig. 4 and 6, that is, the cooled medium is air, the mixed working medium flows through the first evaporation passage a 'of the first evaporator and evaporates therein, and performs the secondary cooling function on the air flowing through the first evaporator, and the mixed working medium rich in high boiling point component flows through the second evaporation passage a' of the second evaporator and evaporates therein, and performs the primary cooling function on the air flowing through the second evaporator, thereby effectively realizing the step small heat transfer temperature difference cooling, improving the evaporation temperature glide, and enhancing the heat exchange efficiency.
Preferably, the first and second electrodes are formed of a metal,
the fan 6 is disposed on the upstream side of the first evaporator 41 and the second evaporator 42 in the air flow, the second evaporator 42 is located on the upstream side of the first evaporator 41 along the air flow path, the fan 6 blows the air into the second evaporator 42 in a blowing manner to exchange heat, and the air after the heat exchange of the second evaporator 42 enters the first evaporator 41 to exchange heat. This is a further preferred structural form of embodiments 4 and 6 of the present invention, that is, a preferred arrangement form of the fan and the two evaporators, such a structural form enables the two evaporators to be arranged together, and the air is sequentially cooled down and cooled by sequential cascade cooling in the second evaporator and the first evaporator while saving space, thereby improving the heat exchange effect with small temperature difference, enhancing the evaporation temperature glide, reducing the pressure drop, increasing the pressure at the air suction port end of the compressor, reducing the power consumption, and improving the energy efficiency.
Preferably, the first and second electrodes are formed of a metal,
the heat regenerator 7 is arranged between the condenser 2 and the throttling device 3, the heat regenerator 7 comprises a first heat recovery passage 71 and a second heat recovery passage 72, heat exchange can be carried out between the first heat recovery passage and the second heat recovery passage, the inlet end of the first heat recovery passage 71 is communicated to the outlet end of the condenser 2, the outlet end of the first heat recovery passage 71 is communicated to the throttling device 3 or the first evaporator 41, the inlet end of the second heat recovery passage 72 is communicated to the gas outlet end 52 of the gas-liquid separation device 5, and the outlet end of the second heat recovery passage 72 is communicated to the suction end of the compressor 1.
This is the preferred structure form in embodiments 1, 3, and 4 of the present invention, as shown in fig. 1, 3, and 4, that is, by setting the structure form of the heat regenerator, the gas coming out of the gas-liquid separation device absorbs heat, and the refrigerant coming out of the condenser is further cooled, so as to further effectively increase the supercooling degree of the refrigerant of the refrigeration system, thereby improving the evaporation capacity for the low-temperature and low-pressure refrigerant entering the evaporator, and enhancing the evaporation capacity and the evaporation efficiency.
Preferably, the first and second electrodes are formed of a metal,
when the first evaporator 41 includes only the first evaporation passage a41a and the first evaporation passage b41b, the outlet end of the first recuperation passage 71 is communicated to the throttle device 3;
when the first evaporator 41 includes the first evaporation passage a41a, the first evaporation passage b41b, and the first evaporation passage c41c at the same time, the outlet end of the first recuperation passage 71 is communicated to the inlet end of the first evaporation passage c41c of the first evaporator 41.
This is a further preferable structure form in embodiments 1, 3, and 4 of the present invention, that is, the outlet port of the first heat recovery passage of the heat regenerator is determined according to whether the first evaporation passage c is provided in the first evaporator, so that the reheated refrigerant can enter the throttling device either directly for throttling and then enter the first evaporation passage a for heat absorption and evaporation, or enter the throttling device after being cooled down further in the first evaporation passage c, thereby further increasing the supercooling degree of the refrigerant by combining the heat regenerator and the first evaporation passage c, and enhancing the evaporation capacity and the evaporation efficiency.
Preferably, the first and second electrodes are formed of a metal,
the refrigerant discharged from the gas outlet end 52 of the gas-liquid separation device 5 is mixed with the refrigerant discharged from the refrigerant outlet end of the second evaporator 42 through a pipe, and then enters the compressor 1, and a pressure balance device 8 is disposed at the mixing position, so that the refrigerant discharged from the gas outlet end 52 and the refrigerant discharged from the refrigerant outlet end of the second evaporator 42 are mixed in the pressure balance device 8. In a further preferred structure form of the present invention, the refrigerant liquid rich in the high boiling point component is branched and enters the second evaporator 42 to be evaporated into a saturated or superheated gas, the part of the refrigerant is mixed with the gaseous refrigerant rich in the low boiling point component, which is heated from the gas-liquid separation device 5, through the pressure balancing device 8, and the mixed refrigerant enters the suction port of the compressor 1, so as to ensure the pressure stability of the suction gas of the compressor.
Preferably, the first and second electrodes are formed of a metal,
the first evaporator 41 is a finned tube heat exchanger, a double-tube heat exchanger or a plate heat exchanger; and/or the second evaporator 42 is a finned tube heat exchanger, a double tube heat exchanger or a plate heat exchanger; and/or the condenser 2 is a finned tube heat exchanger, a double-tube heat exchanger or a plate heat exchanger; and/or the mixed working medium comprises R32 and R134 a. This is a preferred embodiment of the first and second evaporator and condenser according to the invention and a preferred type of working mixture.
The invention also provides an air conditioner which comprises the mixed working medium refrigerating system.
The invention provides a double-temperature circulation scheme that the gaseous refrigerant after gas-liquid separation in the evaporation process directly enters a compressor and the liquid refrigerant further evaporates and then enters the compressor by utilizing the separation characteristic and the heat exchange characteristic of the mixed working medium components, and the scheme has the following beneficial effects:
based on the characteristics of component separation and temperature slippage of a non-azeotropic mixed refrigerant in a phase equilibrium state, double evaporation temperatures can be realized by adopting one compressor, the heat exchange medium is subjected to gradient cooling, small temperature difference heat exchange of the refrigerant and the heat exchange medium can be realized, the irreversible loss in the heat exchange process is greatly reduced, the suction pressure is effectively improved, the power consumption of the compressor is reduced, and the system efficiency is improved;
through the separation of different components, the evaporation temperature slippage of the mixed working medium is increased, and the effect improvement effect is enhanced;
through separating the gas in the evaporation in advance, the heat exchange coefficient is strengthened, the system pressure drop is reduced, the flow distribution is improved unevenly, the evaporation performance is improved, and the system energy efficiency is further improved.
Taking a mixed working medium of R32 and R134a (mass fraction R32: R134a is 0.5:0.5) as an example, the refrigerant before entering the first evaporator 41 is an original component, i.e., R32: R134a is 0.5:0.5, after passing through the first evaporator 41, the low-boiling-point component R32 is easily evaporated, and in the gas-liquid separation device 5, the refrigerant components are separated, wherein the gas refrigerant component at the top of the gas-liquid separation device 5 is rich in the refrigerant R32 which is easily evaporated (the ratio of R32/R134a is 0.65/0.35), and the liquid refrigerant component at the bottom of the gas-liquid separation device is rich in the high-boiling-point component R134a which is easily condensed (the ratio of R32/R134a is 0.35/0.75). Then, the refrigerant discharged from the second evaporator 42 is mixed with the refrigerant discharged from the gas-liquid separation device 5, and the refrigerant composition is changed back to the original composition (R32/R134a is 0.5/0.5), and is sucked into the compressor 1. From the perspective of temperature glide, neglecting pressure loss, the refrigerant temperature glide in the second evaporator 41 is 3.4 ℃, the refrigerant temperature glide in the third evaporator 42 is 6.1 ℃ and the total temperature glide in the evaporation process is 9.5 ℃ under a specific pressure (temperature glide refers to the temperature difference of the phase change of the refrigerant mixture with different boiling points under a certain constant pressure, specifically, the temperature of the phase change of the refrigerant gradually increases along the refrigerant flowing direction in the evaporator, and the difference of the phase change of the outlet and the inlet is temperature glide), which is the result of component separation; and if the components are not separated, the temperature slip of the mixed working medium of the original components is only 4.5 ℃ under the same pressure, the heat exchange of the refrigerant and the air side is more matched due to the larger slip temperature of the refrigerant side, the irreversible loss in the heat exchange process is reduced, and the energy efficiency is further improved.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents and improvements made within the spirit and principle of the present invention are intended to be included within the scope of the present invention. The above description is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, several modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations should also be regarded as the protection scope of the present invention.
Claims (10)
1. A mixed working medium refrigerating system is characterized in that: the method comprises the following steps:
the air conditioner comprises a compressor (1), a condenser (2), a throttling device (3), a first evaporator (41) and a second evaporator (42), wherein the inlet of the first evaporator (41) can be communicated with the throttling device (3) or the condenser (2), and the outlet end of the second evaporator (42) can be communicated to the air suction end of the compressor (1);
a gas-liquid separation device (5) is further arranged between the outlet end of the first evaporator (41) and the inlet end of the second evaporator (42), the gas-liquid separation device (5) is provided with a refrigerant inlet end (51), a gas outlet end (52) and a liquid outlet end (53), the refrigerant inlet end (51) is communicated with the outlet end of the first evaporator (41), the gas outlet end (52) is communicated to the suction end of the compressor (1), and the liquid outlet end (53) is communicated to the inlet end of the second evaporator (42).
2. The mixed refrigerant refrigeration system of claim 1 wherein:
the first evaporator (41) comprises a first evaporation passage a (41a) and a first evaporation passage b (41b), wherein a refrigerant flows through the first evaporation passage a (41a), the inlet of the first evaporation passage a (41a) is communicated with the throttling device (3), the outlet end of the first evaporation passage a is communicated with the refrigerant inlet end (51) of the gas-liquid separation device (5), and a fluid to be cooled flows through the first evaporation passage b (41 b);
the second evaporator (42) includes a second evaporation passage a (42a) through which a refrigerant flows, an inlet of the second evaporation passage a (42a) being communicated with the liquid outlet end (53) of the gas-liquid separation device (5), an outlet end of the second evaporation passage a (42a) being communicated with a suction end of the compressor (1), and a second evaporation passage b (42b) through which the fluid to be cooled flows; and the first evaporation passage b (41b) is communicated with the second evaporation passage b (42b), and the fluid to be cooled firstly enters the second evaporation passage b (42b) for cooling and then enters the first evaporation passage b (41b) for cooling.
3. The mixed refrigerant refrigeration system of claim 2 wherein:
the first evaporator (41) further comprises a first evaporation passage c (41c), wherein refrigerant flows through the first evaporation passage c (41c), the inlet of the first evaporation passage c (41c) can be communicated with the condenser (2), the outlet end of the first evaporation passage c is communicated with the throttling device (3), the other end of the throttling device (3) is communicated with the inlet end of the first evaporation passage a (41a), and the outlet end of the first evaporation passage a (41a) is communicated with the refrigerant inlet end (51) of the gas-liquid separation device (5).
4. The mixed refrigerant refrigeration system of claim 1 wherein:
the first evaporator (41) includes a first evaporation passage a '(41 a'), through which a refrigerant flows, and an inlet of the first evaporation passage a '(41 a') communicates with the throttle device (3) and an outlet thereof communicates with the refrigerant inlet (51) of the gas-liquid separation device (5);
the second evaporator (42) includes a second evaporation passage a '(42 a'), through which refrigerant flows, and an inlet of which is communicated with the liquid outlet end (53) of the gas-liquid separation device and an outlet of which is communicated with a suction end of the compressor (1);
the air conditioner also comprises a fan (6), wherein the fan (6) can blow air or suck air to flow through the second evaporator (42) for heat exchange and then flow through the first evaporator (41) for heat exchange.
5. The mixed refrigerant refrigeration system of claim 4 wherein:
the fan (6) is arranged on the upstream side of the air flow of the first evaporator (41) and the second evaporator (42), the second evaporator (42) is located on the upstream side of the first evaporator (41) along the air flow path, the fan (6) blows wind into the second evaporator (42) firstly in a blowing mode for heat exchange, and the wind after heat exchange of the second evaporator (42) enters the first evaporator (41) for heat exchange.
6. The mixed refrigerant refrigeration system according to any one of claims 1 to 5, wherein:
the heat regenerator (7) is arranged between the condenser (2) and the throttling device (3), the heat regenerator (7) comprises a first heat recovery passage (71) and a second heat recovery passage (72), heat exchange can be carried out between the first heat recovery passage and the second heat recovery passage, the inlet end of the first heat recovery passage (71) is communicated to the outlet end of the condenser (2), the outlet end of the first heat recovery passage (71) is communicated to the throttling device (3) or the first evaporator (41), the inlet end of the second heat recovery passage (72) is communicated to the gas outlet end (52) of the gas-liquid separation device (5), and the outlet end of the second heat recovery passage (72) is communicated to the suction end of the compressor (1).
7. The mixed refrigerant refrigeration system of claim 6 wherein:
when the first evaporator (41) includes only a first evaporation passage a (41a) and a first evaporation passage b (41b), the outlet end of the first recuperation passage (71) is communicated to the throttling means (3);
when the first evaporator (41) includes a first evaporation passage a (41a), a first evaporation passage b (41b), and a first evaporation passage c (41c) at the same time, the outlet end of the first recuperation passage (71) is communicated to the inlet end of the first evaporation passage c (41c) of the first evaporator (41).
8. The mixed refrigerant refrigeration system according to any one of claims 1 to 7, wherein:
refrigerant discharged from a gas outlet end (52) of the gas-liquid separation device (5) is mixed with refrigerant discharged from a refrigerant outlet end of the second evaporator (42) through a pipeline, and then enters the compressor (1), and a pressure balancing device (8) is arranged at a mixed position, so that the refrigerant discharged from the gas outlet end (52) and the refrigerant discharged from the refrigerant outlet end of the second evaporator (42) are mixed in the pressure balancing device (8).
9. The mixed refrigerant refrigeration system according to any one of claims 1 to 8, wherein:
the first evaporator (41) is a finned tube heat exchanger, a double-tube heat exchanger or a plate heat exchanger; and/or the second evaporator (42) is a finned tube heat exchanger, a double tube heat exchanger or a plate heat exchanger; and/or the condenser (2) is a finned tube heat exchanger, a double-tube heat exchanger or a plate heat exchanger; and/or the mixed working medium comprises R32 and R134 a.
10. An air conditioner, characterized in that: a mixed refrigerant refrigeration system including any of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN202010124846.1A CN111288675A (en) | 2020-02-27 | 2020-02-27 | Mixed working medium refrigerating system and air conditioner |
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| CN202010124846.1A CN111288675A (en) | 2020-02-27 | 2020-02-27 | Mixed working medium refrigerating system and air conditioner |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112268321A (en) * | 2020-10-26 | 2021-01-26 | 珠海格力电器股份有限公司 | Mixed working medium refrigerating system and dehumidifier |
| CN113915787A (en) * | 2021-09-27 | 2022-01-11 | 河南科技大学 | Low-temperature mixed working medium refrigerating system with double evaporation temperature positions |
-
2020
- 2020-02-27 CN CN202010124846.1A patent/CN111288675A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112268321A (en) * | 2020-10-26 | 2021-01-26 | 珠海格力电器股份有限公司 | Mixed working medium refrigerating system and dehumidifier |
| CN113915787A (en) * | 2021-09-27 | 2022-01-11 | 河南科技大学 | Low-temperature mixed working medium refrigerating system with double evaporation temperature positions |
| CN113915787B (en) * | 2021-09-27 | 2023-03-03 | 河南科技大学 | Low-temperature mixed working medium refrigerating system with double evaporation temperature positions |
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