CN112880251A - Refrigeration system and method with hot gas-liquid return separator - Google Patents
Refrigeration system and method with hot gas-liquid return separator Download PDFInfo
- Publication number
- CN112880251A CN112880251A CN202110167756.5A CN202110167756A CN112880251A CN 112880251 A CN112880251 A CN 112880251A CN 202110167756 A CN202110167756 A CN 202110167756A CN 112880251 A CN112880251 A CN 112880251A
- Authority
- CN
- China
- Prior art keywords
- liquid
- refrigerant
- refrigeration system
- hot gas
- closed chamber
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
-
- 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
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention discloses a refrigeration system with a hot gas-liquid return separator and a method thereof, wherein the hot gas-liquid return separator comprises a cylinder body, two ends of the cylinder body are sealed by end covers, and a closed cavity is formed inside the cylinder body; one end cover is provided with an air inlet pipe, an air outlet pipe, a liquid inlet and a liquid outlet; a condensate backheating coil is arranged in the closed chamber; on one hand, the cold energy of the low-temperature liquid-phase refrigerant stored in the gas-liquid separator is recycled to the outlet of the condenser through the hot gas-liquid separator, so that the starting energy efficiency of the system is improved; on the other hand, the migration speed of the refrigerant during the system starting and the liquefaction speed of the refrigerant at the outlet of the condenser are accelerated, and the starting time of the system is shortened. Meanwhile, the energy efficiency of the system in stable operation cannot be reduced, the capacity of preventing the compressor from sucking air and carrying liquid cannot be influenced, an additional control part is not needed, the cost is low, the structure is simple, and the starting speed of the refrigeration system can be effectively increased.
Description
Technical Field
The invention relates to the technical field of air-conditioning refrigeration systems, in particular to a refrigeration system with a hot gas-liquid return separator and a method.
Background
The refrigeration system is widely applied to the conditioning of the room environment and the refrigeration and fresh-keeping of food, however, the refrigeration system has the following problems in practical application:
the seasonal energy efficiency ratio of the fixed-frequency air conditioning system is seriously attenuated. For a constant-frequency air conditioner, the cooling capacity of the air conditioner in continuous and stable operation is larger than the cold load of a room, so that the air conditioner can be periodically started and stopped to keep the temperature in the room constant, and the energy loss caused by frequent starting and stopping of a refrigeration system is a main reason for influencing the Seasonal Energy Efficiency Ratio (SEER) of the system.
The cooling speed of refrigerators and commercial freezers is low. Food quality and food safety issues are receiving increasing attention from people. The shelf-life storage and distribution of food products, particularly perishable food products, has long been one of the most interesting hotspots in the development of the agricultural and food industries. In the food storage of refrigerators and freezers, the aim of keeping freshness by quickly cooling is always desired. The energy attenuation caused in the starting process of the refrigerating system can reduce the temperature reduction speed in the refrigerator and the freezer, increase the food storage corrosion rate and cause great waste.
The variable frequency air conditioner has low cold air supply speed and low thermal comfort. For comfort air conditioners, when the air conditioner is used for adjusting indoor air temperature under hot weather conditions, people generally expect that the air conditioner can have a rapid cooling effect, and particularly, the rapid cooling of the air supply temperature during starting can improve the thermal comfort and the satisfaction degree of users from the practical application perspective.
Therefore, means and schemes capable of effectively improving the dynamic performance of the air-conditioning refrigeration system in the starting process and reducing the starting time of the system are urgently needed to be provided.
Disclosure of Invention
The invention provides a refrigeration system with a hot gas-liquid return separator and a method thereof.
The invention mainly solves the problems of serious seasonal energy efficiency ratio attenuation of a fixed-frequency air conditioning system, slow temperature reduction speed in a refrigerator and a freezer, high food storage corrosion loss rate, low cold air supply speed of a variable-frequency air conditioner and low thermal comfort in the prior art caused by attenuation of refrigerating capacity output in the starting process of the system.
The invention is realized by the following technical scheme:
the hot gas return separator for the refrigerating system comprises a cylinder body 11, wherein two ends of the cylinder body 11 are sealed by end covers, and a closed cavity 1 is formed inside the cylinder body 11;
one end cover is provided with an air inlet pipe 6, an air outlet pipe 7, a liquid inlet 8 and a liquid outlet 9;
a condensate backheating coil 10 is arranged in the closed chamber 1;
one end of the condensate backheating coil 10 is connected with the liquid inlet 8, and the other end of the condensate backheating coil is connected with the liquid outlet 9.
The refrigerating system comprises a compressor 2, a condenser 3, an expansion valve 4 and an evaporator 5;
the air outlet pipe 7, the compressor 2, the condenser 3 and the liquid inlet 8 are sequentially connected through pipelines;
the liquid outlet 9, the expansion valve 4, the evaporator 5 and the air inlet pipe 6 are connected in sequence through pipelines;
the two-phase refrigerant of 0-10 ℃ from the evaporator 5 enters the closed chamber 1 through the air inlet pipe 6, and the sectional area (or volume) of the closed chamber 1 is far larger than that of the air inlet pipe 6, so the flow speed of the refrigerant in the air inlet pipe 6 is about 30-55 times of that in the closed chamber 1, at the moment, the flow speed of the refrigerant is rapidly reduced, the two-phase refrigerant from the evaporator 5 is subjected to gas-liquid separation, the liquid-phase refrigerant is deposited at the bottom of the closed chamber 1 due to gravity, and the gas-phase refrigerant leaves the closed chamber 1 through the air outlet pipe 7 under the suction action of the compressor 2 and flows to the compressor 2; meanwhile, the 30-40 ℃ refrigerant from the condenser 3 enters the condensate heat recovery coil 10 through the liquid inlet 8, and the refrigerant exchanges heat with the 0-10 ℃ refrigerant deposited at the bottom of the closed chamber 1 at the bottom of the condensate heat recovery coil 10 to absorb the cold energy of the 0-10 ℃ refrigerant so as to accelerate condensation.
The air outlet pipe 7 extends into the bottom of the closed chamber 1, and a pipe orifice at the lower end of the air outlet pipe upwards bypasses the middle upper part of the closed chamber 1.
The condensate backheating coil 10 is in a spiral shape and is positioned at the inner bottom of the closed chamber 1.
The end caps include an upper end cap 12 and a lower end cap 13.
The air inlet pipe 6, the air outlet pipe 7, the liquid inlet 8 and the liquid outlet 9 are all connected with an upper sealing end cover 12 in a welding mode.
The upper sealing end cover 12 and the lower sealing end cover 13 are connected with the cylinder body 11 through threads or welding.
A method for accelerated start-up of a refrigeration system, comprising the steps of:
the refrigerant is evaporated into steam with the pressure of 0.2-0.3MPa and the temperature of 0-10 ℃ by the indoor environment temperature in the evaporator 5, and then enters the closed chamber 1 of the hot gas-liquid separator through the air inlet pipe 6, the gas refrigerant in the closed chamber 1 is sucked by the compressor 2 through the air outlet pipe 7 and is compressed into gas with the pressure of 0.67-0.92 MPa and the temperature of 65-75 ℃, then the refrigerant enters the condenser 3 and is condensed into liquid with the pressure of 0.67-0.92 MPa and the temperature of 30-40 ℃ by the external environment air volume, then the liquid enters the condensate liquid reheating coil 10 through the liquid inlet 8 for reheating, and then the liquid is throttled into liquid with the pressure of 0.2-0.3MPa and the temperature of 0-10 ℃ by the liquid outlet 9 through the expansion valve 4, and finally the liquid enters the evaporator 5 to complete the circulation;
in a closed cavity 1 of the heat-return gas-liquid separator, because the temperature of a refrigerant at the outlet end of a condenser 3 is 30-40 ℃, the refrigerant absorbs a part of cold energy in a condensate heat-return coil 10, the refrigerant in the condensate heat-return coil 10 is liquefied, then the refrigerant enters an evaporator 5 through an expansion valve 4, the dryness of the inlet section of the evaporator 5 is reduced, the liquid refrigerant rapidly flows into the evaporator 5, meanwhile, the heat absorption of the refrigerant in the closed cavity 1 accelerates the evaporation of the liquid refrigerant, so that the gaseous refrigerant in the closed cavity 1 is sucked into a compressor 2 at an accelerated speed, the migration of the refrigerant in the starting process of a refrigeration system is accelerated, and the starting process of the refrigeration system is accelerated.
Compared with the prior art, the invention has the following advantages and effects:
the invention adds a heat recovery gas-liquid separator in the refrigeration system, and a condensate heat recovery coil is arranged in the heat recovery gas-liquid separator; because the temperature of the refrigerant at the outlet end of the condenser is higher, the refrigerant absorbs part of cold energy of the liquid-phase refrigerant deposited at the bottom of the gas-liquid separator in the heat regenerator, the liquefaction speed of the refrigerant at the outlet of the condenser is accelerated, and then the refrigerant enters the evaporator through the expansion valve. Meanwhile, the liquid-phase refrigerant in the gas-liquid separator absorbs heat and is evaporated quickly, so that the liquid-phase refrigerant in the gas-liquid separator is quickly converted into a gaseous refrigerant and is sucked into the compressor quickly, the migration of the refrigerant in the starting process of the refrigeration system is accelerated, and the starting process of the refrigeration system is accelerated.
Moreover, the invention not only accelerates the starting process of the refrigerating system under the condition of not reducing the energy efficiency of the original stable operation of the system, but also does not need additional control parts, has simple and effective technical means, low manufacturing cost and outstanding effect, and has positive popularization and application values.
Drawings
FIG. 1 is a schematic view of the configuration of the hot gas-liquid separator according to the present invention.
Fig. 2 is a schematic diagram of the construction of the refrigeration system with the return gas-liquid separator of the present invention.
FIG. 3 is a graph comparing the start-up times obtained in the experiments of the present invention.
Detailed Description
The present invention will be described in further detail with reference to specific examples.
Examples
As shown in fig. 1-3. The invention discloses a hot gas return separator for a refrigerating system, which comprises a cylinder body 11, wherein two ends of the cylinder body 11 are sealed by end covers, and a closed cavity 1 is formed inside the cylinder body 11;
one end cover is provided with an air inlet pipe 6, an air outlet pipe 7, a liquid inlet 8 and a liquid outlet 9;
a condensate backheating coil 10 is arranged in the closed chamber 1;
one end of the condensate backheating coil 10 is connected with the liquid inlet 8, and the other end of the condensate backheating coil is connected with the liquid outlet 9.
The refrigerating system comprises a compressor 2, a condenser 3, an expansion valve 4 and an evaporator 5;
the air outlet pipe 7, the compressor 2, the condenser 3 and the liquid inlet 8 are sequentially connected through pipelines;
the liquid outlet 9, the expansion valve 4, the evaporator 5 and the air inlet pipe 6 are connected in sequence through pipelines;
the expansion valve 4 may be a capillary tube, a thermostatic expansion valve or an electronic expansion valve, and is used to throttle the medium-temperature high-pressure liquid refrigerant into low-temperature low-pressure wet vapor, and then the refrigerant absorbs heat in the evaporator 5 to achieve a refrigeration effect.
The compressor 2 can be a positive displacement compressor, a screw compressor, a scroll compressor, a fixed frequency compressor or a variable frequency compressor, and is used for compressing low-temperature and low-pressure refrigerant at the outlet of the evaporator into high-temperature and high-pressure refrigerant.
The two-phase refrigerant of 0-10 ℃ from the evaporator 5 enters the closed chamber 1 through the air inlet pipe 6, and the sectional area (or volume) of the closed chamber 1 is far larger than that of the air inlet pipe 6, so the flow speed of the refrigerant in the air inlet pipe 6 is about 30-55 times (or 20-70 times) that of the refrigerant in the closed chamber 1, at the moment, the flow speed of the refrigerant is rapidly reduced, the two-phase refrigerant from the evaporator 5 is subjected to gas-liquid separation, the liquid-phase refrigerant is deposited at the bottom of the closed chamber 1 due to gravity, and the gas-phase refrigerant leaves the closed chamber 1 through the air outlet pipe 7 under the suction action of the compressor 2 and flows to the compressor 2; meanwhile, the 30-40 ℃ refrigerant from the condenser 3 enters the condensate heat recovery coil 10 through the liquid inlet 8, and the refrigerant exchanges heat with the 0-10 ℃ refrigerant deposited at the bottom of the closed chamber 1 at the bottom of the condensate heat recovery coil 10 to absorb the cold energy of the 0-10 ℃ refrigerant so as to accelerate condensation.
Of course, the ratio of the cross-sectional area of the inlet pipe 6 to the closed chamber 1 may be 1: 10-1: 70. In addition, the ratio can be adjusted experimentally accordingly, taking into account the specific flow rate requirements of the refrigerant in the inlet pipe 6.
The air outlet pipe 7 extends into the bottom of the closed chamber 1, a pipe orifice at the lower end of the air outlet pipe upwards circuitously returns to the middle upper area of the closed chamber 1, and the air outlet pipe 7 is integrally of a U-shaped structure.
The condensate backheating coil 10 is in a spiral shape and is positioned at the inner bottom of the closed chamber 1.
The spiral condensate liquid heat-returning coil 10 not only increases the heat exchange area, but also can increase the time of the refrigerant at the outlet of the condenser 3 participating in heat returning; the reheated refrigerant leaves the condensate reheating coil through the liquid outlet 9 and further flows to the expansion valve 4.
The end caps include an upper end cap 12 and a lower end cap 13.
The air inlet pipe 6, the air outlet pipe 7, the liquid inlet 8 and the liquid outlet 9 are all connected with an upper sealing end cover 12 in a welding mode.
The upper sealing end cover 12 and the lower sealing end cover 13 are connected with the cylinder body 11 through threads or welding.
A method for accelerated start-up of a refrigeration system, comprising the steps of:
the refrigerant is evaporated into steam with the pressure of 0.2-0.3MPa and the temperature of 0-10 ℃ by the indoor environment temperature in the evaporator 5, and then enters the closed chamber 1 of the hot gas-liquid separator through the air inlet pipe 6, the gas refrigerant in the closed chamber 1 is sucked by the compressor 2 through the air outlet pipe 7 and is compressed into gas with the pressure of 0.67-0.92 MPa and the temperature of 65-75 ℃, then the refrigerant enters the condenser 3 and is condensed into liquid with the pressure of 0.67-0.92 MPa and the temperature of 30-40 ℃ by the external environment air volume, then the liquid enters the condensate liquid reheating coil 10 through the liquid inlet 8 for reheating, and then the liquid is throttled into liquid with the pressure of 0.2-0.3MPa and the temperature of 0-10 ℃ by the liquid outlet 9 through the expansion valve 4, and finally the liquid enters the evaporator 5 to complete the circulation;
in a closed cavity 1 of the heat-return gas-liquid separator, because the temperature of a refrigerant at the outlet end of a condenser 3 is 30-40 ℃, the refrigerant absorbs a part of cold energy in a condensate heat-return coil 10, the refrigerant in the condensate heat-return coil 10 is liquefied, then the refrigerant enters an evaporator 5 through an expansion valve 4, the dryness of the inlet section of the evaporator 5 is reduced, the liquid refrigerant rapidly flows into the evaporator 5, meanwhile, the heat absorption of the refrigerant in the closed cavity 1 accelerates the evaporation of the liquid refrigerant, so that the gaseous refrigerant in the closed cavity 1 is sucked into a compressor 2 at an accelerated speed, the migration of the refrigerant in the starting process of a refrigeration system is accelerated, and the starting process of the refrigeration system is accelerated.
As shown in fig. 3. In order to verify the effect of accelerating the starting speed, a group of comparison experiments are carried out, and a common refrigeration cycle and a refrigeration cycle with a hot gas-liquid return separator are respectively carried out under the same working conditions (the condenser inlet water temperature is 30 ℃, the evaporator inlet water temperature is 30 ℃, the evaporation end water flow is 25g/s, and the condensation end water flow is 70 g/s).
According to experimental results, when the refrigeration capacity of 180W is achieved, the time consumed for starting the heat return mode is 190s, the time consumed for starting the common mode is 420s, the starting time of the refrigeration cycle with the heat return gas-liquid separator is shortened by 230s compared with that of the common mode, and the starting speed is greatly improved.
As mentioned above, the refrigeration capacity of the low-temperature liquid-phase refrigerant stored in the refrigeration system is recycled to the outlet of the condenser through the hot gas-liquid return separator, so that the starting energy efficiency of the refrigeration system is improved; on the other hand, the migration speed of the refrigerant when the refrigeration system is started and the liquefaction speed of the refrigerant at the outlet of the condenser are accelerated, and the starting time of the system is shortened. Meanwhile, the energy efficiency of the system in stable operation can not be reduced, the capacity of preventing the compressor from sucking air and carrying liquid can not be influenced, an additional control part is not needed, the construction cost is low, the structure is simple and practical, and the starting speed of the refrigerating system is effectively increased.
As described above, the present invention can be preferably realized.
The embodiments of the present invention are not limited to the above-described embodiments, and any other changes, modifications, substitutions, combinations, and simplifications which do not depart from the spirit and principle of the present invention should be construed as equivalents thereof, and they are included in the scope of the present invention.
Claims (9)
1. A return gas-liquid separator for a refrigeration system, characterized by: the hot gas-liquid return separator comprises a cylinder body (11), two ends of the cylinder body (11) are sealed by end covers, and a closed cavity (1) is formed inside the cylinder body (11);
one end cover is provided with an air inlet pipe (6), an air outlet pipe (7), a liquid inlet (8) and a liquid outlet (9);
a condensate backheating coil (10) is arranged in the closed chamber (1);
one end of the condensate backheating coil (10) is connected with the liquid inlet (8), and the other end of the condensate backheating coil is connected with the liquid outlet (9).
2. The returned hot gas-liquid separator for a refrigeration system as set forth in claim 1, wherein: the refrigeration system comprises a compressor (2), a condenser (3), an expansion valve (4) and an evaporator (5);
the air outlet pipe (7), the compressor (2), the condenser (3) and the liquid inlet (8) are sequentially connected through pipelines;
the liquid outlet (9), the expansion valve (4), the evaporator (5) and the air inlet pipe (6) are connected in sequence through pipelines;
the two-phase refrigerant of 0-10 ℃ from the evaporator (5) enters the closed chamber (1) through the air inlet pipe (6), and because the cross-sectional area of the closed chamber (1) is larger than that of the air inlet pipe (6), the flow rate of the refrigerant is slowed down at this time, so that the two-phase refrigerant from the evaporator (5) is separated into gas and liquid, the liquid-phase refrigerant is deposited at the bottom of the closed chamber (1) due to gravity, and the gas-phase refrigerant leaves the closed chamber (1) through the air outlet pipe (7) under the suction action of the compressor (2) and flows to the compressor (2); meanwhile, the 30-40 ℃ refrigerant from the condenser (3) enters the condensate heat recovery coil (10) through the liquid inlet (8), and the refrigerant exchanges heat with the 0-10 ℃ refrigerant deposited at the bottom of the closed chamber (1) at the bottom of the condensate heat recovery coil (10) to absorb the cold energy of the 0-10 ℃ refrigerant so as to accelerate condensation.
3. The returned hot gas-liquid separator for a refrigeration system as set forth in claim 2, wherein: the flow velocity of the refrigerant is that the flow velocity of the refrigerant in the air inlet pipe (6) is 30-55 times faster than the flow velocity of the refrigerant entering the closed cavity (1).
4. The returned hot gas-liquid separator for a refrigeration system as set forth in claim 3, wherein: the air outlet pipe (7) extends into the bottom of the closed chamber (1), and a pipe orifice at the lower end of the air outlet pipe upwards circuitously returns to the middle upper part of the closed chamber (1).
5. The returned hot gas-liquid separator for a refrigeration system as set forth in claim 4, wherein: the condensate liquid heat return coil (10) is in a spiral shape and is positioned at the inner bottom of the closed chamber (1).
6. The returned hot gas-liquid separator for a refrigeration system as set forth in claim 5, wherein: the end covers comprise an upper sealing end cover (12) and a lower sealing end cover (13).
7. The returned hot gas-liquid separator for a refrigeration system as set forth in claim 6, wherein: the gas inlet pipe (6), the gas outlet pipe (7), the liquid inlet (8) and the liquid outlet (9) are all connected with the upper sealing end cover (12) in a welding mode.
8. The returned hot gas-liquid separator for a refrigeration system as set forth in claim 6, wherein: the upper sealing end cover (12) and the lower sealing end cover (13) are connected with the cylinder body (11) in a threaded or welding mode.
9. A method for accelerating the start-up of a refrigeration system, which is characterized by being realized by the hot gas-liquid return separator for the refrigeration system as claimed in any one of claims 1 to 4, and comprises the following steps:
after the refrigerant is evaporated into steam with the pressure of 0.2-0.3MPa and the temperature of 0-10 ℃ by the indoor environment temperature in the evaporator (5), enters the closed chamber (1) of the hot gas-liquid return separator through the air inlet pipe (6), the compressor (2) sucks the gaseous refrigerant in the closed chamber (1) through the air outlet pipe (7), compressing into gas with pressure of 0.67-0.92 MPa and temperature of 65-75 deg.C, then the refrigerant enters into the condenser (3), is condensed into liquid with the pressure of 0.67MPa to 0.92MPa and the temperature of 30 ℃ to 40 ℃ by the air quantity of the external environment, then enters a condensate backheating coil (10) through a liquid inlet (8) to be backheated, is throttled into the liquid with the pressure of 0.2 MPa to 0.3MPa and the temperature of 0 ℃ to 10 ℃ through an expansion valve (4) from a liquid outlet (9), and finally enters an evaporator (5) to finish circulation;
in a closed cavity (1) of the heat-return gas-liquid separator, because the temperature of a refrigerant at the outlet end of a condenser (3) is 30-40 ℃, the refrigerant absorbs a part of cold energy in a condensate heat-return coil (10), the refrigerant in the condensate heat-return coil (10) is liquefied, then the refrigerant enters an evaporator (5) through an expansion valve (4), the dryness of the inlet section of the evaporator (5) is reduced, the liquid refrigerant rapidly flows into the evaporator (5), meanwhile, the heat absorption of the refrigerant in the closed cavity (1) can accelerate the evaporation of the liquid refrigerant, and the gaseous refrigerant in the closed cavity (1) is accelerated to be sucked into a compressor (2), so that the migration of the refrigerant in the starting process of a refrigeration system is accelerated, and the starting process of the refrigeration system is accelerated.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110167756.5A CN112880251A (en) | 2021-02-07 | 2021-02-07 | Refrigeration system and method with hot gas-liquid return separator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110167756.5A CN112880251A (en) | 2021-02-07 | 2021-02-07 | Refrigeration system and method with hot gas-liquid return separator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112880251A true CN112880251A (en) | 2021-06-01 |
Family
ID=76056009
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110167756.5A Pending CN112880251A (en) | 2021-02-07 | 2021-02-07 | Refrigeration system and method with hot gas-liquid return separator |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112880251A (en) |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001174092A (en) * | 1999-12-20 | 2001-06-29 | Fujitsu General Ltd | Air conditioner |
| CN201297813Y (en) * | 2008-10-31 | 2009-08-26 | 青岛海信日立空调系统有限公司 | Novel regenerative gas-liquid separator |
| CN201344687Y (en) * | 2009-02-12 | 2009-11-11 | 珠海格力电器股份有限公司 | Gas-liquid separator |
| CN105865064A (en) * | 2015-01-20 | 2016-08-17 | 青岛海尔特种电冰柜有限公司 | Refrigerator refrigeration circulation system |
-
2021
- 2021-02-07 CN CN202110167756.5A patent/CN112880251A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001174092A (en) * | 1999-12-20 | 2001-06-29 | Fujitsu General Ltd | Air conditioner |
| CN201297813Y (en) * | 2008-10-31 | 2009-08-26 | 青岛海信日立空调系统有限公司 | Novel regenerative gas-liquid separator |
| CN201344687Y (en) * | 2009-02-12 | 2009-11-11 | 珠海格力电器股份有限公司 | Gas-liquid separator |
| CN105865064A (en) * | 2015-01-20 | 2016-08-17 | 青岛海尔特种电冰柜有限公司 | Refrigerator refrigeration circulation system |
Non-Patent Citations (1)
| Title |
|---|
| 陆振曦等: "《食品机械原理与设计》", 31 May 1995, 中国轻工业出版社 * |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| KR102262722B1 (en) | Cooling Cycle Apparatus for Refrigerator | |
| CN108106048B (en) | Ejector expansion self-cascade refrigeration cycle system and working process | |
| KR102406775B1 (en) | Refrigeration cycle system | |
| CN109737624B (en) | Double-temperature refrigerating system and control method thereof | |
| CN113983710B (en) | Refrigerant circulation flow self-adaptive adjusting system | |
| CN111895689A (en) | Refrigerating system supercooling degree device for improving wide temperature zone application | |
| Luo et al. | Performance Analysis of High-temperature Two-stage Compression Heat Pump with Vapor Injection Dynamic Control. | |
| CN110822755A (en) | Heat pump system using non-azeotropic refrigerant mixture | |
| CN204154039U (en) | Aircondition | |
| CN211552102U (en) | Multi-connected air conditioning system | |
| CN211120091U (en) | Cascade refrigeration system with supercooling and injection depressurization | |
| CN112325496A (en) | Cold and hot matching unit for meat processing and control method | |
| CN109520163B (en) | Wide-temperature-zone small-sized refrigerating and refrigerating unit with rapid pulse defrosting function | |
| CN112880251A (en) | Refrigeration system and method with hot gas-liquid return separator | |
| CN206593361U (en) | A kind of vehicle-mounted energy-saving refrigerator | |
| CN115420039A (en) | Extremely cold cascade type heat pump control method | |
| CN115560496A (en) | Enhanced vapor injection heat pump cold water system and control method | |
| CN211552134U (en) | Ultralow temperature single-machine refrigeration heating temperature control system | |
| CN114739037A (en) | Double-ejector multi-loop evaporation vapor compression circulation system and working method | |
| CN113790525A (en) | Enhanced vapor injection variable-frequency air source heat pump hot water system and operation control method | |
| CN111595047A (en) | Refrigerating system of refrigerator car and control method thereof | |
| CN218764104U (en) | Novel hot gas and liquid return separator for refrigerating system | |
| CN104941707A (en) | Refrigeration system applied to constant-temperature and constant-humidity test box | |
| KR200300268Y1 (en) | refrigeration system | |
| CN216204427U (en) | Refrigerant circulation flow self-adaptive adjusting device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20210601 |