CN113446751A - Refrigerating system and air supply adjusting method thereof - Google Patents
Refrigerating system and air supply adjusting method thereof Download PDFInfo
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- CN113446751A CN113446751A CN202110721452.9A CN202110721452A CN113446751A CN 113446751 A CN113446751 A CN 113446751A CN 202110721452 A CN202110721452 A CN 202110721452A CN 113446751 A CN113446751 A CN 113446751A
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- 238000000034 method Methods 0.000 title claims abstract description 27
- 238000005057 refrigeration Methods 0.000 claims abstract description 39
- 239000013589 supplement Substances 0.000 claims description 15
- 239000003507 refrigerant Substances 0.000 claims description 14
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 11
- 238000001704 evaporation Methods 0.000 claims description 7
- 238000004781 supercooling Methods 0.000 claims description 7
- 230000005494 condensation Effects 0.000 claims description 6
- 238000009833 condensation Methods 0.000 claims description 6
- 230000008020 evaporation Effects 0.000 claims description 6
- 238000004891 communication Methods 0.000 claims description 4
- 239000004576 sand Substances 0.000 claims description 2
- 230000001105 regulatory effect Effects 0.000 claims 8
- 230000003750 conditioning effect Effects 0.000 claims 1
- 230000001502 supplementing effect Effects 0.000 abstract description 4
- 239000000498 cooling water Substances 0.000 description 5
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 2
- 229910052799 carbon Inorganic materials 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000006386 neutralization reaction Methods 0.000 description 1
- 239000011555 saturated 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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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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
- F25B41/30—Expansion means; Dispositions thereof
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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
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/40—Fluid line arrangements
-
- 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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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The invention discloses a refrigeration system and a gas supplementing adjusting method thereof, wherein the refrigeration system comprises a condenser, an evaporator, a high-pressure compressor, a low-pressure compressor, a first economizer and a second economizer which are arranged between the condenser and the evaporator in parallel, and the first economizer comprises a first gas supplementing flow path; the first air supply flow path is provided with a first expansion valve, and a flow path from the condenser to the second economizer is provided with a second expansion valve. When flash pressure PSPressure of economizer PjWhen the opening degree of the first expansion valve is adjusted once every first preset time period t1, the opening degree of the second expansion valve is unchanged; flash pressure PS = economizer pressure PjWhen the first expansion valve and the second expansion valve are opened, the opening degrees of the first expansion valve and the second expansion valve are unchanged; when flash pressure PS< economizer pressure PjMeanwhile, the opening degree of the first expansion valve is unchanged, and the opening degree of the second expansion valve is adjusted once every second preset time period t 2. Compared with the prior art, the method and the device have the advantage that the optimal performance and capacity of the unit under each working condition are maintained.
Description
Technical Field
The invention relates to the technical field of refrigeration, in particular to a refrigeration system and a gas supplementing adjusting method thereof.
Background
Under the guidance of the targets of carbon neutralization and carbon peak reaching, the centrifugal water chilling unit is greatly advocated by the state at present, becomes the most ideal and environment-friendly refrigerating unit for the large-scale building at present, and the energy efficiency of the centrifugal water chilling unit also becomes a problem which is increasingly concerned by people. The double-stage compression is a refrigeration cycle system commonly adopted by the existing centrifugal water chilling unit, the double-stage compression refrigeration cycle generally adopts an additional economizer to realize intermediate air supplement to improve the cycle efficiency, so that a refrigerant needs to pass through two throttling processes, the refrigeration unit can always operate in a high-efficiency area by changing the throttling circulation area, the conventional double-stage compression refrigeration cycle water chilling unit generally only has one economizer, the intermediate pressure of the economizer is uncontrollable, the intermediate pressure directly influences the power and the efficiency of a compressor, the air supplement amount can be unknown under different working conditions, the condition that the air supplement amount is not proper can occur in the working condition changing process, and the unit energy efficiency is reduced.
Disclosure of Invention
The invention provides a refrigerating system and an air supplement adjusting method thereof, and solves the problem that in the prior art, the energy efficiency of the refrigerating system is low due to the fact that the air supplement amount of a compressor is difficult to accurately adjust.
The technical scheme adopted by the invention is as follows: a refrigeration system comprising a condenser, an evaporator and a compressor, further comprising: a first economizer and a second economizer disposed in parallel in a flow path from the condenser to the evaporator, the first economizer including a first make-up air flow path in communication with the compressor, the second economizer including a second make-up air flow path in communication with the compressor.
Further, a first throttling device is respectively arranged on the flow paths from the condenser to the first economizer and from the first economizer to the evaporator.
Further, the first throttling device is a throttling orifice plate.
Furthermore, a first expansion valve is arranged on the first air supply flow path.
Furthermore, a second throttling device is respectively arranged on the flow path from the condenser to the second economizer and the flow path from the second economizer to the evaporator, the second throttling device on the flow path from the condenser to the second economizer is a second expansion valve, and the second throttling device on the flow path from the second economizer to the evaporator is a throttling orifice plate.
Further, the refrigerating system comprises a high-pressure compressor and a low-pressure compressor, and the first air replenishing flow path and the second air replenishing flow path are communicated with the high-pressure compressor.
A method of air make-up regulation for a refrigeration system comprising: and when the refrigeration system is started to operate, the air compensation amount of the first economizer and the second economizer is automatically adjusted according to the operation parameters of the refrigeration system.
Further, when the refrigeration system is started up from the shutdown state, the opening degree of the first expansion valve is 0%, and the opening degree of the second expansion valve is increased to 100%.
Further, the flash pressure P is comparedSAnd economizer pressure PjAnd respectively adjusting the air supplement amount of the first economizer through the first expansion valve and adjusting the air supplement amount of the second economizer through the second expansion valve.
Further, when the flash pressure P is reachedSPressure of economizer PjIn the meantime, the opening degree of the first expansion valve is adjusted once every first preset time period t1, and the opening degree of the second expansion valve is not changed.
Further, the adjustment amplitude D% of the first expansion valve is determined according to the temperature parameter of the refrigeration system.
Further, D = D1+ D2+ D3 in the adjustment amplitude D% of the first expansion valve, wherein: d1=0.5 (Δ Tsc-3) when the refrigerant supercooling degree Δ Tsc in the condenser is greater than or equal to 3 ℃, and D1=0.9 (3- Δ Tsc) when the refrigerant supercooling degree Δ Tsc in the condenser is less than 3 ℃;
d2=0.3 (1.5- Δ Tc) when the temperature difference Δ Tc between the condensation temperature of the condenser (1) and the temperature of the cooled effluent is equal to or less than 1.5 ℃, D2=0.6 (Δ Tc-1.5) when the condenser Δ Tc >1.5 ℃;
d3=0.2 (Δ Td-4) when the exhaust superheat degree Δ Td is equal to or greater than 4 ℃, and D3=1 (4- Δ Td) when the exhaust superheat degree Δ Td is less than 4 ℃.
Further, when the flash pressure PS = the economizer pressure PjIn this case, the opening degrees of the first expansion valve and the second expansion valve are not changed.
Further, when the flash pressure P is reachedS< economizer pressure PjMeanwhile, the opening degree of the first expansion valve is unchanged, and the opening degree of the second expansion valve is adjusted once every second preset time period t 2.
Further, the adjustment amplitude d% of the second expansion valve is determined according to the temperature parameter of the refrigeration system.
Further, d =1- (d 1+ d 2) of the adjustment amplitude d% of the second expansion valve, wherein:
d1=0.3 × Δ Te when the temperature difference Δ Te between the chilled water temperature and the evaporation temperature of the evaporator (2) is less than or equal to 1.5 ℃, and d1=0.2 × Δ Te-1.5 when the Δ Te of the evaporator (2) is greater than 1.5 ℃;
d2=0.28 (Δ Td-4) when the exhaust superheat degree Δ Td is equal to or greater than 4 ℃, and d1=0.41 Δ Td when the exhaust superheat degree Δ Td is less than 4 ℃.
Further, the adjustment range D% of the first expansion valve and the adjustment range D% of the second expansion valve are not more than 3%.
Compared with the prior art, this application sets up parallelly connected first economic ware and second economic ware on the flow path between condenser to the evaporimeter, adopts two economic wares to carry out two way tonifying qi to the compressor, comes to carry out the tonifying qi regulation to refrigerating system through detecting system's operating parameter, through the tonifying qi volume of controlling first economic ware and second economic ware respectively, even make the system can stably tonify the air, make the unit all can obtain the best tonifying qi volume in this operating mode under different operating modes simultaneously, and then keep the best performance and the ability of unit under every operating mode.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the embodiments or the prior art descriptions will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without inventive exercise.
FIG. 1 is a schematic diagram of the refrigeration system of the present invention;
FIG. 2 is a flow diagram of the operation of the refrigeration system of the present invention;
fig. 3 is a schematic view showing the adjustment flow of the first and second expansion valves according to the present invention.
1. A condenser; 2. an evaporator; 3. a low pressure compressor; 4. a high pressure compressor; 5. a first economic device; 6. a second economizer; 7. a first air supply flow path; 8. a second air supply flow path; 9. a restriction orifice plate; 10. a first expansion valve; 11. a second expansion valve; 12. a condensing pressure sensor; 13. a cooling water inlet temperature sensor; 14. a condensation temperature sensor; 15. a cooling water outlet temperature sensor; 16. a first pressure sensor; 17. a second pressure sensor; 18. an evaporation pressure sensor; 19. an evaporation temperature sensor; 20. a chilled water inlet temperature sensor; 21. a chilled water outlet temperature sensor; 22. an intermediate pressure sensor; 23. an exhaust pressure sensor.
Detailed Description
The principles and construction of the present invention will be described in detail below with reference to the drawings and examples.
The application discloses a refrigeration system, as shown in fig. 1, the refrigeration system comprises a condenser 1 and an evaporator 2, the condenser 1 and the evaporator 2 are connected through a flow path to form a circulation loop, and a compressor is arranged on the flow path from the evaporator 2 to the condenser 1, the refrigeration system in the application is a two-stage compression refrigeration cycle, so that two compressors are arranged in the application, and a low-pressure compressor 3 and a high-pressure compressor 4 are arranged on the flow path from the evaporator 2 to the condenser 1 in sequence.
Furthermore, this application still is provided with two economizers on the flow path from condenser 1 to evaporimeter 2, is first economic ware 5 and second economic ware 6 respectively, and parallelly connected between first economic ware 5, the second economic ware 6, and these two economizers all are connected to the tonifying qi mouth of high pressure compressor 4 through the tonifying qi flow path and carry out the tonifying qi simultaneously, and what correspond with first economic ware 5 is first tonifying qi flow path 7, what correspond with second economic ware 6 is second tonifying qi flow path 8.
The first economizer 5 has a large volume, the second economizer 6 has a small volume, and therefore the circulation volume of the first economizer 5 is correspondingly larger than that of the second economizer 6, and on the premise, the centrifuge is a large-capacity refrigerating unit, the first economizer 5 is used as a main air supply economizer, and the second economizer 6 is used as an auxiliary air supply economizer.
Specifically, the flow paths from the condenser 1 to the first economizer 5 and from the first economizer 5 to the evaporator 2 are respectively provided with a first throttling device, based on the larger circulation volume and the larger circulation amount of the first economizer 5, the first throttling device is set as a throttling orifice plate 9 to adapt to the first economizer 5 with large circulation amount, the high-pressure liquid refrigerant flowing out of the condenser 1 flows through the throttling orifice plate 9 to enter the first economizer 5 after being throttled and depressurized, the gaseous refrigerant is separated from the liquid refrigerant in the first economizer 5, the saturated liquid refrigerant is throttled and depressurized again through the throttling orifice plate 9 to enter the evaporator 2, and the gaseous refrigerant separated from the first economizer 5 directly enters the compressor through the first air replenishing flow path 7 to complete air replenishing; the first air supply passage 7 is provided with a first expansion valve 10, which is an electronic expansion valve and can control the amount of air supplied to the high-pressure compressor 4 to be stable.
Specifically, the second throttling device is respectively arranged on the flow paths from the condenser 1 to the second economizer 6 and from the second economizer 6 to the evaporator 2, and based on the small flow volume of the second throttling device, the second throttling device on the flow path from the condenser 1 to the second economizer 6 is set as a second expansion valve 11, the second throttling device on the flow path from the second economizer 6 to the evaporator 2 is a throttling orifice plate 9, the second expansion valve 11 is an electronic expansion valve, so as to control the flow rate of the second economizer 6, wherein the working principle of the second economizer 6 and the second throttling device is the same as that of the first economizer 5, the gaseous refrigerant separated from the second economizer 6 directly enters the compressor through a second air replenishing flow path 8 to complete air replenishing, and the air replenishing amount of the high-pressure compressor 4 can be adjusted by adjusting the second expansion valve 11.
The first economizer 5 and the second economizer 6 which are arranged on a flow path from the condenser 1 to the evaporator 2 in parallel can realize stable supply of the air supplement amount of the compressor, and meanwhile, in the process of changing working conditions, the air supplement amount is adjusted to be stable in a macroscopic mode, and the air supplement amount is adjusted to be optimal in a microscopic mode, so that the energy efficiency of a unit is kept in an optimal running state all the time.
Further, in the present application, a condensation pressure sensor 12, a cooling water inlet temperature sensor 13, a condensation temperature sensor 14, and a cooling water outlet temperature sensor 15 are also provided on the condenser 1; a first pressure sensor 16 is also arranged on the first economizer 5; a second pressure sensor 17 is also arranged on the second economizer 6; an evaporation pressure sensor 18, an evaporation temperature sensor 19, a chilled water inlet temperature sensor 20 and a chilled water outlet temperature sensor 21 are arranged on the evaporator 2; an intermediate pressure sensor 22 is arranged at the air supplementing opening of the high-pressure compressor 4; a discharge pressure sensor 23 is further provided in the flow path from the high-pressure compressor 4 to the condenser 1; the above sensors are used to detect various operating parameters of the refrigeration system, and the adjustment ranges of the first and second expansion valves 11 are adjusted according to the parameter values.
Further, the present application also discloses an air supply adjusting method of a refrigeration system, referring to fig. 2, the air supply adjusting method mainly includes:
step one, when the refrigerating unit is started, the opening degree of the first expansion valve 10 is increased from 0% to 100%, the process lasts for 3min, and meanwhile, the opening degree of the second expansion valve 11 is continuously maintained at 0% and also lasts for 3 min.
And step two, after the refrigeration system is started for 3min, the first expansion valve 10 and the second expansion valve 11 are in an automatic adjusting mode according to the operation parameters of the refrigeration system.
And step three, shutting down the refrigerating unit, wherein the opening degrees of the first expansion valve 10 and the second expansion valve 11 are both 0%.
Referring to fig. 3, the automatic adjustment mode of the first expansion valve 10 and the second expansion valve 11 includes the following steps: comparing the flash pressure PS to the economizer pressure Pj, the comparison comprising: the flash pressure PS is greater than the economizer pressure Pj, the flash pressure PS is equal to the economizer pressure Pj, and the flash pressure PS is less than the economizer pressure Pj.
Example 1: when the flash pressure PS is greater than the economizer pressure Pj, the opening degree of the first expansion valve 10 is adjusted once every first preset time period t1, and the opening degree of the second expansion valve 11 is kept unchanged; the adjustment amplitude D% of the first expansion valve 10 needs to be determined according to the temperature parameters of the refrigeration system.
Specifically, D = D1+ D2+ D3 in the adjustment amplitude D% of the first expansion valve 10.
Wherein, when the supercooling degree of the refrigerant in the condenser 1 is more than or equal to 3 ℃, D1=0.5 (Δ Tsc-3), and when the supercooling degree of the refrigerant in the condenser 1 is less than 3 ℃, D1=0.9 (3- Δ Tsc).
D2=0.3 (1.5- Δ Tc) when the condenser 1 end temperature difference Δ Tc ≦ 1.5 ℃, and D2=0.6 (Δ Tc-1.5) when the condenser 1 end temperature difference Δ Tc >1.5 ℃.
D3=0.2 (Δ Td-4) when the exhaust superheat degree Δ Td is equal to or greater than 4 ℃, and D3=1 (4- Δ Td) when the exhaust superheat degree Δ Td is less than 4 ℃.
Based on the calculation, the adjustment range D% of the first expansion valve 10 is obtained, the opening degree of the first expansion valve 10 is adjusted once every first preset time period t1, and the first preset time period t1 is 5 s.
Example 2: when the flash pressure PS = the economizer pressure Pj, the opening degrees of both the first expansion valve 10 and the second expansion valve 11 are kept constant.
Example 3: when the flash pressure PS is less than the economizer pressure Pj, the opening degree of the first expansion valve 10 is unchanged, while the opening degree of the second expansion valve 11 is adjusted every second preset time period t2, and the adjustment amplitude d% of the second expansion valve 11 needs to be determined according to the temperature parameter of the refrigeration system.
Specifically, d =1- (d 1+ d 2) in the adjustment amplitude d% of the second expansion valve 11.
Wherein: d1=0.3 × Δ Te when the temperature difference Δ Te at the evaporator 2 end is equal to or less than 1.5 ℃, and d1=0.2 × Δ Te (Δ Te-1.5) when the temperature difference Δ Te at the evaporator 2 end is greater than 1.5 ℃.
D2=0.28 (Δ Td-4) when the exhaust superheat degree Δ Td is equal to or greater than 4 ℃, and d1=0.41 Δ Td when the exhaust superheat degree Δ Td is less than 4 ℃.
Based on the above calculation, the adjustment range d% of the second expansion valve 11 is calculated, the opening degree of the second expansion valve 11 is adjusted once every second preset time period t2, and the second preset time period t2 is 5 s.
Where, 4 above, the economizer pressure Pj = Pd + PX (Pd measured by the first pressure sensor 16, PX measured by the second pressure sensor 17); the supercooling degree delta Tsc = condensation temperature Tc-condenser 1 effluent temperature Tsc; exhaust superheat degree Δ Td = exhaust temperature Td — condensing temperature Tc; the temperature difference delta Te at the 2 end of the evaporator = the frozen water outlet temperature Teo-evaporation temperature Te; the condenser 1-end temperature difference Δ Tc = condensing temperature Tc — cooling water outlet temperature Tco.
It should be noted that the absolute values of the adjustment range D% of the first expansion valve 10 and the adjustment range D% of the second expansion valve 11 do not exceed 3%, and if the adjustment range is greater than 3%, the adjustment is performed according to 3%; the intermediate pressure Pv (measured by the intermediate pressure sensor 22) should be less than the economizer pressure, otherwise the air make-up process cannot be completed, and it is true that the intermediate pressure Pv should be less than the economizer pressure due to the piping pressure loss and the electronic expansion valve pressure loss.
The opening degrees of the first expansion valve 10 and the second expansion valve 11 are dynamically adjusted through the operation parameters of the refrigeration system, and then the proper air supplement amount and the proper air supplement pressure are controlled, so that the refrigeration system can adapt to load changes under different working conditions, and the unit achieves better energy efficiency.
The above specific embodiments are only intended to illustrate the inventive concept and many modifications and variations may be made by those skilled in the art within the spirit of the invention, which are included within the scope of the invention.
Claims (17)
1. A method for make-up regulation of a refrigeration system comprising a first (5) and a second (6) economizer arranged in parallel in a flow path from a condenser (1) to an evaporator (2), the first (5) and second (6) economizers being connected to a compressor make-up port for make-up air, characterized in that the method comprises: when the refrigeration system is started to operate, the air supplement amounts of the first economizer (5) and the second economizer (6) are automatically adjusted according to the operation parameters of the refrigeration system.
2. The method for adjusting air make-up according to claim 1, wherein the first economizer (5) comprises a first air make-up flow path (7) in communication with the compressor, a first expansion valve (10) is provided on the first air make-up flow path (7), a second expansion valve (11) is provided on the flow path from the condenser (1) to the second economizer (6), the opening degree of the first expansion valve (10) is maintained at 0% and the opening degree of the second expansion valve (11) is increased to 100% before adjusting the air make-up amount of the first economizer (5) and the second economizer (6).
3. The method for regulating qi according to claim 2, wherein the flash pressure P is comparedSAnd economizer pressure PjAnd respectively adjusting the air supplement amount of the first economizer (5) through a first expansion valve (10) and adjusting the air supplement amount of the second economizer (6) through a second expansion valve (11) according to the comparison result.
4. The method of regulating qi supply of claim 3, wherein the flash pressure P is setSPressure of economizer PjIn the meantime, the opening degree of the first expansion valve (10) is adjusted once every first preset time period t1, and the opening degree of the second expansion valve (11) is not changed.
5. The gas make-up regulation method according to claim 4, characterized in that the adjustment amplitude D% of the first expansion valve (10) is determined according to the temperature parameters of the refrigeration system.
6. The gas compensation regulating method according to claim 5, wherein D = D1+ D2+ D3 of the adjustment amplitude D% of the first expansion valve (10), wherein:
d1=0.5 (Δ Tsc-3) when the refrigerant supercooling degree Δ Tsc in the condenser (1) is greater than or equal to 3 ℃, and D1=0.9 (3- Δ Tsc) when the refrigerant supercooling degree Δ Tsc in the condenser (1) is less than 3 ℃;
d2=0.3 (1.5- Δ Tc) when the temperature difference Δ Tc between the condensation temperature of the condenser (1) and the temperature of the cooled effluent is equal to or less than 1.5 ℃, D2=0.6 (Δ Tc-1.5) when the condenser Δ Tc >1.5 ℃;
d3=0.2 (Δ Td-4) when the exhaust superheat degree Δ Td is equal to or greater than 4 ℃, and D3=1 (4- Δ Td) when the exhaust superheat degree Δ Td is less than 4 ℃.
7. The method of regulating qi supply of claim 3, wherein the flash pressure P is setS= economizer pressure PjWhen the opening degree of the first expansion valve (10) and the opening degree of the second expansion valve (11) are not changed.
8. The method of regulating qi supply of claim 3, wherein the flash pressure P is setS< economizer pressure PjThe opening degree of the first expansion valve (10) is not changed, and the opening degree of the second expansion valve (11) is adjusted once every second preset time period t 2.
9. Method for regulating air make-up according to claim 8, characterized in that the adjustment amplitude d% of said second expansion valve (11) is determined according to the temperature parameters of the refrigeration system.
10. The gas compensation regulating method according to claim 9, wherein d =1- (d 1+ d 2) of the adjustment amplitude d% of the second expansion valve (11), wherein:
d1=0.3 × Δ Te when the temperature difference Δ Te between the chilled water temperature and the evaporation temperature of the evaporator (2) is less than or equal to 1.5 ℃, and d1=0.2 × Δ Te-1.5 when the Δ Te of the evaporator (2) is greater than 1.5 ℃;
d2=0.28 (Δ Td-4) when the exhaust superheat degree Δ Td is equal to or greater than 4 ℃, and d1=0.41 Δ Td when the exhaust superheat degree Δ Td is less than 4 ℃.
11. The gas compensation regulating method according to claim 3, wherein the amplitude of each adjustment of the first expansion valve (10) and the amplitude of each adjustment of the second expansion valve (11) do not exceed 3%.
12. A refrigeration system, characterized in that it employs the method of conditioning with make-up air as claimed in claims 1 to 11.
13. A refrigeration system according to claim 12, characterized in that a first throttle device is provided in each of the flow paths from the condenser (1) to the first economizer (5) and from the first economizer (5) to the evaporator (2).
14. A refrigeration system according to claim 13, characterized in that the first throttle device is an orifice plate (9).
15. A refrigeration system according to claim 12, characterized in that an orifice (9) is provided in the flow path from the second economizer (6) to the evaporator (2).
16. The refrigeration system of claim 12, comprising a high pressure compressor (4) and a low pressure compressor (3), the first and second economizers being in communication with a charge port of the high pressure compressor (4).
17. The refrigerant system as set forth in claim 12, wherein the flow area of said first economizer is greater than the flow area of said second economizer.
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| CN105485949A (en) * | 2015-12-21 | 2016-04-13 | 珠海格力电器股份有限公司 | Refrigeration system and control method thereof |
| CN110332635A (en) * | 2019-07-09 | 2019-10-15 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of more tonifying Qi refrigeration heat pump systems of Two-stage Compression, control method and air conditioner |
| CN112097424A (en) * | 2020-09-17 | 2020-12-18 | 珠海格力电器股份有限公司 | Refrigerating system, air supply control method and device and air conditioning equipment |
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Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105485949A (en) * | 2015-12-21 | 2016-04-13 | 珠海格力电器股份有限公司 | Refrigeration system and control method thereof |
| CN110332635A (en) * | 2019-07-09 | 2019-10-15 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of more tonifying Qi refrigeration heat pump systems of Two-stage Compression, control method and air conditioner |
| CN112097424A (en) * | 2020-09-17 | 2020-12-18 | 珠海格力电器股份有限公司 | Refrigerating system, air supply control method and device and air conditioning equipment |
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