CN211041462U - Waste heat recovery trans-critical CO of gas cooler2Refrigeration system - Google Patents
Waste heat recovery trans-critical CO of gas cooler2Refrigeration system Download PDFInfo
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- CN211041462U CN211041462U CN201921839265.5U CN201921839265U CN211041462U CN 211041462 U CN211041462 U CN 211041462U CN 201921839265 U CN201921839265 U CN 201921839265U CN 211041462 U CN211041462 U CN 211041462U
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- 239000007789 gas Substances 0.000 title claims abstract description 71
- 239000002918 waste heat Substances 0.000 title claims abstract description 49
- 238000011084 recovery Methods 0.000 title claims abstract description 40
- 238000005057 refrigeration Methods 0.000 claims abstract description 25
- 238000004781 supercooling Methods 0.000 claims abstract description 20
- 239000003507 refrigerant Substances 0.000 claims abstract description 18
- 230000005494 condensation Effects 0.000 claims description 6
- 238000009833 condensation Methods 0.000 claims description 6
- 230000001737 promoting effect Effects 0.000 abstract 1
- 239000012530 fluid Substances 0.000 description 10
- 230000002427 irreversible effect Effects 0.000 description 4
- 238000001816 cooling Methods 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
- 239000007788 liquid Substances 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 231100000252 nontoxic Toxicity 0.000 description 2
- 230000003000 nontoxic effect Effects 0.000 description 2
- MSSNHSVIGIHOJA-UHFFFAOYSA-N pentafluoropropane Chemical compound FC(F)CC(F)(F)F MSSNHSVIGIHOJA-UHFFFAOYSA-N 0.000 description 2
- CBENFWSGALASAD-UHFFFAOYSA-N Ozone Chemical compound [O-][O+]=O CBENFWSGALASAD-UHFFFAOYSA-N 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 239000003054 catalyst Substances 0.000 description 1
- 238000011278 co-treatment Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 239000013529 heat transfer fluid Substances 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
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Abstract
The utility model provides a gas cooler waste heat recovery trans-critical CO2Refrigeration system comprising transcritical CO2Circulation, gas cooler waste heat recovery circulation and mechanical supercooling circulation; the trans-critical CO2The circulation comprises an evaporator, the outlet of which is communicated with CO in sequence2Compressor, CO2A heat medium side of the gas cooler, a heat medium side of the subcooler, the first throttling unit, and an inlet of the evaporator; the gas cooler waste heat recovery cycle comprises a first condenser, wherein an outlet of the first condenser is sequentially communicated with a pump and CO2The refrigerant side of the gas cooler, the expander, and the inlet of the first condenser. Gas cooler waste heat recovery transcritical CO2Refrigeration system from transcritical CO2Circulation, gas cooler waste heat recovery circulation and mechanical supercooling circulation constitute, recoverable gas cooler waste heat for the performance of system obtains promoting, reduces the total power consumption of compressor.
Description
Technical Field
The utility model belongs to the technical field of refrigeration and heating, heat pump, especially, relate to a gas cooler waste heat recovery transcritical CO2A refrigeration system.
Background
Energy and environmental issues are major factors limiting the development of socio-economic. For the refrigeration and air-conditioning industry, the extensive use of working media such as CFCs, HCFCs, HFCs and the like causes serious ozone holes and greenhouse effect. In order to seek an environmentally friendly refrigerant, natural working substances attract a great deal of attention. CO 22It is a non-toxic and non-flammable refrigerant, and its source is rich, and it is compatible with general lubricating oil, and its refrigerating capacity per unit volume is large. But due to CO2Lower critical temperature and higher critical pressure, resulting in lower refrigeration efficiency, especially when ambient temperature is higher, CO2The outlet temperature of the gas cooler is too high, resulting in CO2The cooling capacity of (2) is drastically reduced and the power consumption is increased. If to CO at the outlet of the gas cooler2Further cooling of the fluid to reduce CO entering the throttle2And the temperature can reduce the irreversible throttling loss, so that the overall energy efficiency of the system is improved. Along with the increase of the supercooling degree, the throttling loss is reduced, the circulating cold quantity is increased, and further the circulating COP can be improved. By auxiliary vapor compression refrigeration cycle, to CO2CO at outlet of transcritical refrigeration cycle gas cooler2The method of cooling is known as mechanical subcooling. Mechanical supercooling can not only increase the refrigerating capacity, but also reduce the operation high pressure of the main circulation, reduce the exhaust pressure of the compressor and prolong the service life of the compressor.
CO2When the system is applied to the refrigeration field, the heat of the gas cooler is directly discharged to the atmospheric environment, so that the waste of high-grade heat energy is caused. Therefore, the patent proposes a solution for recovering the part of waste heat energy by adopting an organic Rankine cycle technology and utilizing the generated electric energy to carry out CO treatment2The waste heat energy of the system is fully and efficiently utilized, and the overall energy efficiency of the system is improved.
Disclosure of Invention
In view of this, the present invention is directed to a gas cooler waste heat recovery transcritical CO2Refrigeration system to overcome the drawbacks of the prior art, consisting of transcritical CO2The system comprises a cycle, a gas cooler waste heat recovery cycle and a mechanical supercooling cycle, wherein the gas cooler waste heat can be recovered, the waste heat is converted into mechanical work through an expansion machine to be output, and the mechanical work can be transmitted to a common working medium compressor of the mechanical supercooling cycle through a coupler and the like to drive the common working medium compressor to operate, so that the performance of the system is improved, and the total power consumption of the compressor is reduced.
In order to achieve the above purpose, the technical scheme of the utility model is realized like this:
waste heat recovery trans-critical CO of gas cooler2Refrigeration system comprising transcritical CO2Circulation, gas cooler waste heat recovery circulation and mechanical supercooling circulation;
the trans-critical CO2The circulation comprises an evaporator, the outlet of which is communicated with CO in sequence2Compressor, CO2A heat medium side of the gas cooler, a heat medium side of the subcooler, the first throttling unit, and an inlet of the evaporator;
the gas cooler waste heat recovery cycle comprises a first condenser, wherein an outlet of the first condenser is sequentially communicated with a pump and CO2The refrigerant side of the gas cooler, the expander and the inlet of the first condenser;
the mechanical supercooling cycle comprises a second condenser, and an outlet of the second condenser is sequentially communicated with a second throttling unit, a refrigerant side of the subcooler, the common working medium compressor and an inlet of the second condenser.
Further, the first throttling unit and the second throttling unit both adopt throttling valves.
Further, said CO2The gas cooler adopts a counter-flow heat exchanger.
Further, the evaporator adopts a finned tube heat exchanger; the expander is connected with the common working medium compressor through a coupler.
Further, the first condenser and the second condenser are both double-pipe heat exchangers or counter-flow heat exchangers.
Furthermore, the working medium of the gas cooler waste heat recovery circulation and the mechanical supercooling circulation is pure refrigerant or non-azeotropic mixed working medium.
Further, the pure refrigerant is one of R1234ze (Z), R1234ze (E), R1233zd (E), R1224yd (Z), R1336mzz (Z), R365mfc, R1234yf, and R245 fa.
Further, the non-azeotropic mixed working medium is CO2/R1234ze(E)、CO2/R1234ze(Z)、CO2One of R1234yf, R41/R1234ze (E), R41/R1234ze (Z), R41/R1234yf, R32/R1234ze (E), R32/R1234ze (Z), R32/R1234 yf.
Further, CO2The suction temperature range of the compressor is-56-10 ℃, and the exhaust pressure range is 7.5-14 MPa; the air inlet temperature of the expansion machine is 60-120 ℃, and the exhaust temperature is 30-45 ℃; the air suction temperature of the common working medium compressor is-5-25 ℃, and the exhaust temperature is 50-90 ℃.
Furthermore, the temperature range of the evaporator is-56-10 ℃, the condensation temperature range of the first condenser is 25-55 ℃, and the condensation temperature range of the second condenser is 25-55 ℃.
Compared with the prior art, the utility model relates to a gas cooler waste heat recovery transcritical CO2The refrigeration system has the following advantages:
(1) the waste heat of the gas cooler can be recovered through organic Rankine cycle in the waste heat recovery cycle, the waste heat of the gas cooler is converted into mechanical work through the expansion machine to be output, the mechanical work can be transmitted to the common working medium compressor of the mechanical supercooling cycle through the coupler and the like to drive the common working medium compressor to operate, the performance of the system is improved, and the total power consumption of the compressor is reduced.
(2) CO entering the second throttling unit can be reduced by mechanical subcooling cycle2The temperature increases the refrigerating capacity, the irreversible throttling loss is reduced, and the COP of the system is improved;
(3) transcritical CO2The circulating refrigerant is natural working medium CO2. ODP is 0, GWP is 1, and the catalyst can not be decomposed at high temperature, is safe and nontoxic and is environment-friendly. Gas cooler waste heat recovery cycle and mechanical subcooling cycleThe working medium can adopt pure refrigerants such as R1234ze (Z), R1234ze (E), R1233zd (E), R1224yd (Z), R1336mzz (Z), R365mfc, R1234yf and R245fa, and can also adopt CO2/R1234ze(E)、CO2/R1234ze(Z)、CO2Non-azeotropic mixed working media such as/R1234 yf, R41/R1234ze (E), R41/R1234ze (Z), R41/R1234yf, R32/R1234ze (E), R32/R1234ze (Z), R32/R1234yf and the like. For non-azeotropic mixed working medium, temperature glide and subcooler and CO are selected2The refrigerant with the equivalent temperature difference of the heat exchange fluid inlet and the heat exchange fluid outlet of the gas cooler can reduce the heat transfer temperature difference and is beneficial to reducing the irreversible loss of heat exchange.
Drawings
The accompanying drawings, which form a part hereof, are included to provide a further understanding of the invention, and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention without undue limitation. In the drawings:
FIG. 1 shows a gas cooler waste heat recovery transcritical CO according to an embodiment of the present invention2A simple schematic of a refrigeration system.
Description of reference numerals:
1-CO2a compressor; 2-CO2A gas cooler; 3-a pump; 4-a first condenser; 5-an expander; 6-common working medium compressor; 7-a second condenser; 8-a second throttling unit; 9-a subcooler; 10-a first throttling unit; 11-evaporator.
Detailed Description
It should be noted that, in the present invention, the embodiments and features of the embodiments may be combined with each other without conflict.
In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like, indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are used merely for convenience of description and for simplicity of description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore, should not be construed as limiting the present invention. Furthermore, the terms "first", "second", etc. are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first," "second," etc. may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless otherwise specified.
In the description of the present invention, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art through specific situations.
The present invention will be described in detail below with reference to the accompanying drawings in conjunction with embodiments.
As shown in FIG. 1, a gas cooler waste heat recovery transcritical CO2Refrigeration system comprising transcritical CO2Circulation, gas cooler waste heat recovery circulation and mechanical supercooling circulation; the trans-critical CO2The circulation comprises an evaporator 11, and the outlet of the evaporator 11 is communicated with CO in sequence2Compressor 1, CO2The heat medium side (i.e., CO) of the gas cooler 22Side), heat medium side (i.e., CO) of the subcooler 92Side), the inlet of the first throttling unit 10 and the evaporator 11; the gas cooler waste heat recovery cycle comprises a first condenser 4, wherein an outlet of the first condenser 4 is sequentially communicated with a pump 3 and CO2The refrigerant side (i.e., the common working medium side) of the gas cooler 2, the expander 5, and the inlet of the first condenser 4; the mechanical supercooling cycle comprises a second condenser 7, wherein an outlet of the second condenser 7 is sequentially communicated with a second throttling unit 8 and a refrigerant side of a subcooler 9 (namely a common refrigerantMass side), the inlet of a common working medium compressor 6 and a second condenser 7. The expander 5 is connected with the common working medium compressor 6 through a coupler, the waste heat of the gas cooler can be recovered through organic Rankine cycle in the waste heat recovery cycle of the gas cooler, the waste heat is converted into mechanical power through the expander to be output, the mechanical power can be transmitted to the common working medium compressor with mechanical supercooling cycle through the coupler and the like to drive the common working medium compressor to operate, the performance of the system is improved, and the total power consumption of the compressor is reduced.
As an optional embodiment of the present invention, the first throttling unit 10 and the second throttling unit 8 both employ a throttling valve.
As an alternative embodiment of the present invention, the CO is2The gas cooler 2 employs a counter-flow heat exchanger. The evaporator 11 is a finned tube heat exchanger. The first condenser 4 and the second condenser 7 are both double pipe heat exchangers or counter-flow heat exchangers, preferably double pipe heat exchangers.
As an optional implementation manner of the present invention, the working medium of the gas cooler waste heat recovery cycle and the mechanical supercooling cycle can adopt pure refrigerants such as R1234ze (Z), R1234ze (E), R1233zd (E), R1224yd (Z), R1336mzz (Z), R365mfc, R1234yf and R245fa, and can also adopt CO2/R1234ze(E)、CO2/R1234ze(Z)、CO2Non-azeotropic mixed working media such as/R1234 yf, R41/R1234ze (E), R41/R1234ze (Z), R41/R1234yf, R32/R1234ze (E), R32/R1234ze (Z), R32/R1234yf and the like. For non-azeotropic mixed working medium, temperature glide and subcooler and CO are selected2The refrigerant with the equivalent temperature difference of the heat exchange fluid inlet and the heat exchange fluid outlet of the gas cooler can reduce the heat transfer temperature difference and is beneficial to reducing the irreversible loss of heat exchange.
As a more preferable embodiment of the invention, the working medium of the gas cooler waste heat recovery cycle and the mechanical supercooling cycle can adopt R1234yf or R41/R1234 yf.
As an alternative embodiment of the invention, CO2The air suction temperature of the compressor 1 ranges from-56 ℃ to 10 ℃, and the exhaust pressure ranges from 7.5 MPa to 14 MPa; the air inlet temperature of the expansion machine 5 is 60-120 ℃, and the exhaust temperature is 30-45 ℃; compression of common working mediaThe air suction temperature of the machine 6 is-5-25 ℃, and the exhaust temperature is 50-90 ℃. The temperature range of the evaporator 11 is-56-10 ℃, the condensation temperature range of the first condenser 4 is 25-55 ℃, and the condensation temperature range of the second condenser is 25-55 ℃.
Use the gas cooler waste heat recovery transcritical CO2The working principle of the refrigerating system for refrigerating is as follows:
the first step is as follows: heat transfer fluid CO2Low temperature and low pressure CO flowing through the evaporator 11, the outlet of the evaporator 112Fluid ingress into CO2The compressor 1 is compressed to a high temperature and high pressure gas, which is then fed to the CO2The gas cooler 2 heats the common working medium of the organic Rankine cycle (namely, the waste heat recovery cycle of the gas cooler), and the CO is discharged2The temperature is reduced, then the mixture flows through a subcooler 9 to exchange heat with a common working medium, and CO2And then the mixture is cooled to obtain a larger supercooling degree (10-30 ℃). Then flows into the first throttling unit 10 for throttling and pressure reduction to be gas-liquid two-phase fluid, and then flows into CO2The evaporator 11 absorbs heat and is finally heated by CO2The compressor 1 sucks in the gas to compress the gas to complete the transcritical CO2And (4) a refrigeration cycle.
The second step is that: the common working medium flows into the working medium pump 3 for pressurization and then flows through the gas cooler 2 for absorbing CO2The released heat is changed into gas state, and then flows into the expansion machine 5 to do work through expansion, and the pressure is reduced. The work generated by the expander 5 can be transmitted to the common working medium compressor 6 through a coupling and the like to assist in driving the operation of the common working medium compressor. And the common working medium at the outlet of the expansion machine 5 flows into the first condenser 4 to release heat, the fluid is condensed to be in a liquid state and then enters the working medium pump 3, and the steps are repeated so as to complete the waste heat recovery circulation of the gas cooler.
The third step: the common working medium compressor 6 compresses the working medium at the outlet of the common working medium side of the subcooler 9 to high-temperature high-pressure superheated gas, then the high-temperature high-pressure superheated gas enters the second condenser 7 to exchange heat with the external environment, the temperature is reduced, the high-pressure fluid at the outlet of the second condenser 7 is throttled and reduced in pressure by the second throttling unit 8, and then the high-pressure fluid flows into the common working medium side of the subcooler 9 and CO2CO at the outlet of the gas cooler 22Carrying out heat exchange, CO2The temperature is reduced, and the common working medium after heat exchange flows to the compressor 6The mechanical auxiliary supercooling circulation is formed.
The above description is only a preferred embodiment of the present invention, and should not be taken as limiting the invention, and any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (10)
1. Waste heat recovery trans-critical CO of gas cooler2A refrigeration system, characterized by: involving transcritical CO2Circulation, gas cooler waste heat recovery circulation and mechanical supercooling circulation;
the trans-critical CO2The circulation comprises an evaporator (11), and the outlet of the evaporator (11) is communicated with CO in sequence2Compressor (1), CO2The heat medium side of the gas cooler (2), the heat medium side of the subcooler (9), the first throttling unit (10) and the inlet of the evaporator (11);
the gas cooler waste heat recovery cycle comprises a first condenser (4), wherein an outlet of the first condenser (4) is sequentially communicated with a pump (3) and CO2The refrigerant side of the gas cooler (2), the expander (5) and the inlet of the first condenser (4);
the mechanical supercooling cycle comprises a second condenser (7), wherein an outlet of the second condenser (7) is sequentially communicated with a second throttling unit (8), a refrigerant side of a subcooler (9), a common working medium compressor (6) and an inlet of the second condenser (7).
2. The gas cooler waste heat recovery transcritical CO of claim 12A refrigeration system, characterized by: the first throttling unit (10) and the second throttling unit (8) both adopt throttling valves.
3. The gas cooler waste heat recovery transcritical CO of claim 12A refrigeration system, characterized by: the CO is2The gas cooler (2) adopts a counter-flow heat exchanger.
4. The gas cooler waste heat recovery bypass according to claim 1Boundary CO2A refrigeration system, characterized by: the evaporator (11) adopts a finned tube heat exchanger; the expansion machine (5) is connected with the common working medium compressor (6) through a coupler.
5. The gas cooler waste heat recovery transcritical CO of claim 12A refrigeration system, characterized by: the first condenser (4) and the second condenser (7) are both double-pipe heat exchangers or counter-flow heat exchangers.
6. The gas cooler waste heat recovery transcritical CO of claim 12A refrigeration system, characterized by: the working medium of the gas cooler waste heat recovery circulation and the mechanical supercooling circulation is pure refrigerant or non-azeotropic mixed working medium.
7. Gas cooler waste heat recovery transcritical CO according to claim 1 or 62A refrigeration system, characterized by: the pure refrigerant is one of R1234ze (Z), R1234ze (E), R1233zd (E), R1224yd (Z), R1336mzz (Z), R365mfc, R1234yf, R245 fa.
8. The gas cooler waste heat recovery transcritical CO of claim 62A refrigeration system, characterized by: the non-azeotropic mixed working medium is CO2/R1234ze(E)、CO2/R1234ze(Z)、CO2One of R1234yf, R41/R1234ze (E), R41/R1234ze (Z), R41/R1234yf, R32/R1234ze (E), R32/R1234ze (Z), R32/R1234 yf.
9. The gas cooler waste heat recovery transcritical CO according to any one of claims 1 to 62A refrigeration system, characterized by: CO 22The suction temperature range of the compressor (1) is-56-10 ℃, and the exhaust pressure range is 7.5-14 MPa; the air inlet temperature of the expansion machine (5) is 60-120 ℃, and the exhaust temperature is 30-45 ℃; the air suction temperature of the common working medium compressor (6) is-5-25 ℃, and the exhaust temperature is 50-90 ℃.
10. The gas cooler waste heat recovery transcritical CO according to any one of claims 1 to 62A refrigeration system, characterized by: the temperature range of the evaporator (11) is-56-10 ℃, the condensation temperature range of the first condenser (4) is 25-55 ℃, and the condensation temperature range of the second condenser is 25-55 ℃.
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| CN201921839265.5U CN211041462U (en) | 2019-10-29 | 2019-10-29 | Waste heat recovery trans-critical CO of gas cooler2Refrigeration system |
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| CN201921839265.5U CN211041462U (en) | 2019-10-29 | 2019-10-29 | Waste heat recovery trans-critical CO of gas cooler2Refrigeration system |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN113381443A (en) * | 2021-05-24 | 2021-09-10 | 中国能源建设集团山西省电力勘测设计院有限公司 | Working method of new energy power generation power grid load fluctuation compensation system |
| CN113956850A (en) * | 2021-10-18 | 2022-01-21 | 珠海格力电器股份有限公司 | Environment-friendly mixed refrigerant, preparation method thereof and refrigeration system |
| CN114608215A (en) * | 2022-05-14 | 2022-06-10 | 中国能源建设集团山西省电力勘测设计院有限公司 | High-energy-efficiency transcritical carbon dioxide two-stage compression cold-heat combined supply system |
| CN114608216A (en) * | 2022-05-14 | 2022-06-10 | 中国能源建设集团山西省电力勘测设计院有限公司 | Defrosting method of high-energy-efficiency transcritical carbon dioxide double-stage compression cold-hot combined supply system |
| CN117469839A (en) * | 2023-12-22 | 2024-01-30 | 上海优华系统集成技术股份有限公司 | Overhead gas waste heat full recovery system and full recovery method |
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2019
- 2019-10-29 CN CN201921839265.5U patent/CN211041462U/en not_active Expired - Fee Related
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113381443A (en) * | 2021-05-24 | 2021-09-10 | 中国能源建设集团山西省电力勘测设计院有限公司 | Working method of new energy power generation power grid load fluctuation compensation system |
| CN113381443B (en) * | 2021-05-24 | 2022-11-11 | 中国能源建设集团山西省电力勘测设计院有限公司 | Working method of new energy power generation power grid load fluctuation compensation system |
| CN113956850A (en) * | 2021-10-18 | 2022-01-21 | 珠海格力电器股份有限公司 | Environment-friendly mixed refrigerant, preparation method thereof and refrigeration system |
| CN114608215A (en) * | 2022-05-14 | 2022-06-10 | 中国能源建设集团山西省电力勘测设计院有限公司 | High-energy-efficiency transcritical carbon dioxide two-stage compression cold-heat combined supply system |
| CN114608216A (en) * | 2022-05-14 | 2022-06-10 | 中国能源建设集团山西省电力勘测设计院有限公司 | Defrosting method of high-energy-efficiency transcritical carbon dioxide double-stage compression cold-hot combined supply system |
| CN117469839A (en) * | 2023-12-22 | 2024-01-30 | 上海优华系统集成技术股份有限公司 | Overhead gas waste heat full recovery system and full recovery method |
| CN117469839B (en) * | 2023-12-22 | 2024-03-26 | 上海优华系统集成技术股份有限公司 | Overhead gas waste heat full recovery system and full recovery method |
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Granted publication date: 20200717 |