CN106642786A - Carbon dioxide refrigerating cycle system adopting intermediate pressure for supplying liquid - Google Patents
Carbon dioxide refrigerating cycle system adopting intermediate pressure for supplying liquid Download PDFInfo
- Publication number
- CN106642786A CN106642786A CN201611059785.5A CN201611059785A CN106642786A CN 106642786 A CN106642786 A CN 106642786A CN 201611059785 A CN201611059785 A CN 201611059785A CN 106642786 A CN106642786 A CN 106642786A
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- Prior art keywords
- gas
- cooler
- pressure compressor
- heat exchanger
- compressor
- 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.)
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Links
- 229910002092 carbon dioxide Inorganic materials 0.000 title claims abstract description 55
- 239000007788 liquid Substances 0.000 title claims abstract description 38
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 title claims abstract description 36
- 239000001569 carbon dioxide Substances 0.000 title claims abstract description 11
- 239000003921 oil Substances 0.000 claims abstract description 31
- 238000005057 refrigeration Methods 0.000 claims description 9
- 239000010725 compressor oil Substances 0.000 claims description 5
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 5
- 238000001704 evaporation Methods 0.000 abstract description 7
- 238000004781 supercooling Methods 0.000 abstract description 4
- 239000012530 fluid Substances 0.000 abstract 5
- 239000010705 motor oil Substances 0.000 abstract 1
- 238000000926 separation method Methods 0.000 abstract 1
- 239000003507 refrigerant Substances 0.000 description 15
- 238000001816 cooling Methods 0.000 description 11
- 238000007906 compression Methods 0.000 description 10
- 230000006835 compression Effects 0.000 description 8
- CBENFWSGALASAD-UHFFFAOYSA-N Ozone Chemical compound [O-][O+]=O CBENFWSGALASAD-UHFFFAOYSA-N 0.000 description 4
- 230000008020 evaporation Effects 0.000 description 4
- 229910052801 chlorine Inorganic materials 0.000 description 2
- 230000007613 environmental effect Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- WKBOTKDWSSQWDR-UHFFFAOYSA-N Bromine atom Chemical compound [Br] WKBOTKDWSSQWDR-UHFFFAOYSA-N 0.000 description 1
- KZBUYRJDOAKODT-UHFFFAOYSA-N Chlorine Chemical compound ClCl KZBUYRJDOAKODT-UHFFFAOYSA-N 0.000 description 1
- GDTBXPJZTBHREO-UHFFFAOYSA-N bromine Substances BrBr GDTBXPJZTBHREO-UHFFFAOYSA-N 0.000 description 1
- 229910052794 bromium Inorganic materials 0.000 description 1
- 125000001246 bromo group Chemical group Br* 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 239000000460 chlorine Substances 0.000 description 1
- 125000001309 chloro group Chemical group Cl* 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 150000008282 halocarbons Chemical class 0.000 description 1
- 230000003434 inspiratory effect Effects 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 239000010721 machine oil Substances 0.000 description 1
- 231100001143 noxa Toxicity 0.000 description 1
- 238000005482 strain hardening Methods 0.000 description 1
- 239000006200 vaporizer Substances 0.000 description 1
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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/10—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point with several cooling stages
-
- 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
- F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
-
- 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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/07—Details of compressors or related parts
- F25B2400/072—Intercoolers therefor
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)
- Lubricants (AREA)
Abstract
The invention discloses a carbon dioxide refrigerating cycle system adopting intermediate pressure for supplying liquid. The carbon dioxide refrigerating cycle system comprises a CO2 low-pressure compressor, a CO2 high-pressure compressor, an oil separator, an oil cooler, an intermediate air cooler, a gas cooler, an intermediate cooler, a heat exchanger, an evaporator and a gas liquid separator. Refrigerating fluid enters the oil separator after being compressed through the CO2 high-pressure compressor. Compressed engine oil separated out flows back to the CO2 compressor after passing through the oil cooler. Output gas of the oil separator enters the gas cooler and enters the intermediate cooler, gas liquid separation is carried out in the intermediate cooler, liquid refrigerating fluid enters the heat exchanger to be subjected to supercooling, after being subjected to supercooling, the liquid refrigerating fluid is divided into two ways, one way enters the evaporator, the liquid refrigerating fluid enters the CO2 low-pressure compressor through the gas liquid separator after being evaporated, the other way enters the heat exchanger, the refrigerating fluid entering the heat exchanger from the intermediate cooler is cooled and turned into gas after being subjected to evaporating and heat absorbing, and the gas enters the CO2 high-pressure compressor after being converged with gas exhausted by the CO2 low-pressure compressor and cooled through the intermediate cooler.
Description
Technical field
The present invention relates to cooling cycle system, the carbon dioxide refrigeration circulation of more particularly to a kind of employing intermediate pressure feed flow
System.
Background technology
Chlorine atom and bromine atoms in halogenated hydrocarbons can occur violent chemical reaction with ozone, the ozone destroyed in air
Layer, or even define Ozone hole.Chlorine and bromine major part in air comes from the freon of refrigerating industry discharge, therefore, system
Freon is replaced to become the extremely urgent task of refrigerating industry using other environmentally friendly working medium in cold industry.Carbon dioxide is excellent with its
Environmental-protecting performance and thermophysical property it is of great interest in refrigeration industry.
Under the conditions of big compression ratio, with single-stage refrigeration cycle lower evaporating temperature is produced, it will generation much has noxa
Element：
(1) if compressor exhaust temperature is very high, decline can coefficient of refrigerating performance, and lubricant effect can be deteriorated, affect pressure
The service life of contracting machine and normal operation.
(2) compression ratio increase, under Normal Environmental Temperature, when evaporating temperature declines, compression ratio increases, compressor volume
Efficiency is reduced, and actual inspiratory capacity is reduced, and refrigerating capacity declines, and when compression ratio reaches certain certain value, compressor can not freeze.
(3) restriction loss increases, and cold-producing medium unit mass refrigerating capacity is reduced, and consumes work(and increases, and coefficient of refrigerating performance declines.
In air-cooled, evaporation cold-working is adopted for the general cooling cycle system of condenser, it is usual adopt condensate liquid directly for
Evaporimeter high pressure feed flow, because its condensing pressure is influenced by environmental temperature, causes the liquid supply pressure and cold-producing medium of evaporimeter
Internal circulating load at all seasons in be continually changing, have impact on refrigerating efficiency, improve refrigeration liquid feeding pipeline install and safeguard cost.
The content of the invention
The present invention is directed to above-mentioned technical problem, proposes that one kind effectively evades ozone layer destroying, and evaporimeter liquid supply pressure is stablized, kept away
Exempting from performance of refrigerant systems under big compression ratio reduces, and critical-cross carbon dioxide compression cooling cycle system, installation cost is low, system peace
A kind of carbon dioxide refrigeration circulatory system of the high employing intermediate pressure feed flow of complete and stability.
To reach object above, it is achieved through the following technical solutions：
A kind of carbon dioxide refrigeration circulatory system of employing intermediate pressure feed flow, including：CO2Low pressure compressor, CO2High pressure
Compressor, oil eliminator, oil cooler, gas cooler, intercooler, middle air cooler, heat exchanger, evaporimeter are gentle
Liquid/gas separator；
Wherein, CO2The output pipe of high pressure compressor is connected with oil eliminator intake line, and is provided with only on this pipeline
Inverse valve；
The gas export line of oil eliminator is connected with gas cooler input port, and the oily output pipe of oil eliminator is divided into
Two-way, all the way with CO2The compressor oil entrance connection of low pressure compressor, another road and CO2The compressor oil entrance of high pressure compressor
Connection, and and CO2Magnetic valve I is provided with the pipeline of low pressure compressor connection, with CO2Electricity on the pipeline of high pressure compressor connection
Magnet valve II；
Gas cooler is connected by the pipeline with electric expansion valve I with intercooler gas access；
The drain pipe road of intercooler is connected with the water influent pipeline of heat exchanger；
The drain pipe road of heat exchanger is divided into two-way, and all the way Jing electric expansion valves III are connected with the water influent pipeline of evaporimeter,
Another road Jing electric expansion valves II are connected with the low pressure feed tube of heat exchanger；
The outlet pipe of evaporimeter is connected with gas-liquid separator entrance；
The outlet pipe and CO of gas-liquid separator2Low pressure compressor air intake duct connects；
CO2The exhaust outlet of low pressure compressor is connected by pipeline with the entrance of middle air cooler；
The escaping pipe Jing electric control valve of intercooler and the low pressure outlet pipe of heat exchanger and middle air cooler
Outlet pipe is connected to CO after converging2In the suction line of high pressure compressor.
When being worked using the present invention of above-mentioned technical proposal：
Cold-producing medium Jing CO2Oil eliminator is entered after high pressure compressor compression；Compressor in oil eliminator, in cold-producing medium
Oil is separated, and Jing after oil cooler cooling by two branches of oily output pipe, all the way Jing magnetic valves I are back to CO2Low pressure
Compressor, another road Jing magnetic valves II are back to CO2High pressure compressor；The detached high temperature and high pressure gaseous refrigerant of oil eliminator enters
Enter gas cooler, the reducing pressure by regulating flow of Jing electric expansion valves I enters intercooler after cooling；The cold-producing medium gas in intercooler
Liquid is separated, and liquid refrigerant is subcooled into heat exchanger, and the cold-producing medium after supercooling is divided into two-way, all the way Jing electric expansion valves
III enters evaporimeter, and another road liquid refrigerant Jing electric expansion valves II enter heat exchanger low pressure feed tube, to cold from centre
But device is cooled down into the liquid refrigerant of heat exchanger, and liquid refrigerant becomes gas after evaporation endothermic in a heat exchanger
State；Gaseous refrigerant Jing after evaporator evaporation enters CO through gas-liquid separator again2The air entry of low pressure compressor is pressed
Contracting, CO2Cold-producing medium is input in middle air cooler and cools down after low pressure compressor compression, the cold-producing medium after the cooling of middle air cooler with
The outlet of heat exchanger and the low pressure outlet of intercooler finally converge input to CO2Compression, is followed in high pressure compressor
Ring.
To sum up, the invention has the advantages that：
1st, due to present invention employs double-stage compressor, compressor exhaust temperature can be effectively reduced, improves compressor
Operating efficiency, it is ensured that the stability of compressor operating.
2nd, due to present invention employs intermediate pressure as the liquid supply pressure of evaporimeter, it is thus possible to effectively reduce evaporimeter
Liquid supply pressure, and make liquid supply pressure tend to be steady throughout the year, and then ensure that vaporizer side circulating mass of refrigerant is stablized.
3rd, due to present invention employs intermediate pressure as the liquid supply pressure of evaporimeter, pipeline installation cost is reduced.
Described above is only the general introduction of technical solution of the present invention, in order to better understand the technological means of the present invention,
And can be practiced according to the content of specification, and in order to allow the present invention above and other objects, features and advantages can
Become apparent, below especially exemplified by preferred embodiment, and coordinate accompanying drawing, describe in detail as follows.
Description of the drawings
Totally 1 width accompanying drawing of the invention, wherein：
Fig. 1 is the system structure diagram of the present invention.
In figure：1、CO2Low pressure compressor, 2, middle air cooler, 3, CO2High pressure compressor, 4, check (non-return) valve, 5, oil eliminator,
6th, oil cooler, 7, gas cooler, 8, electric expansion valve I, 9, intercooler, 10, electric control valve, 11, heat exchanger,
12nd, electric expansion valve II, 13, electric expansion valve III, 14, evaporimeter, 15, gas-liquid separator, 16, magnetic valve I, 17, magnetic valve
Ⅱ。
Specific embodiment
A kind of carbon dioxide refrigeration circulatory system of employing intermediate pressure feed flow as shown in Figure 1, including：CO2Low pressure pressure
Contracting machine 1, CO2High pressure compressor 3, oil eliminator 5, oil cooler 6, gas cooler 7, intercooler 9, middle air cooler 2,
Heat exchanger 11, evaporimeter 14 and gas-liquid separator 15；
Wherein, CO2The output pipe of high pressure compressor 3 is connected with the intake line of oil eliminator 5, and is provided with this pipeline
Check (non-return) valve 4；
The gas export line of oil eliminator 5 is connected with the input port of gas cooler 7, the oily output pipe of oil eliminator 5
It is divided into two-way, all the way with CO2The compressor oil entrance connection of low pressure compressor 1, another road and CO2The compressor of high pressure compressor 3
Oil-in connects, and and CO2Magnetic valve I 16 is provided with the pipeline of the connection of low pressure compressor 1, with CO2High pressure compressor 3 connects
Pipeline solenoid II 17；
Gas cooler 7 is connected by the pipeline with electric expansion valve I 8 with the gas access of intercooler 9；
The drain pipe road of intercooler 9 is connected with the water influent pipeline of heat exchanger 11；
The drain pipe road of heat exchanger 11 is divided into two-way, all the way the water influent pipeline of Jing electric expansion valves III 13 and evaporimeter 14
It is connected, another road Jing electric expansion valves II 12 are connected with the low pressure feed tube of heat exchanger 11；
The outlet pipe of evaporimeter 14 is connected with the entrance of gas-liquid separator 15；
The outlet pipe and CO of gas-liquid separator 152The air intake duct of low pressure compressor 1 connects；
CO2The exhaust outlet of low pressure compressor 1 is connected by pipeline with the entrance of middle air cooler 2；
The escaping pipe Jing electric control valve 10 of intercooler 9 and the low pressure outlet pipe of heat exchanger 11 and middle air cooling
The outlet pipe of device 2 is connected to CO after converging2In the suction line of high pressure compressor 3.
When being worked using the present invention of above-mentioned technical proposal：
Cold-producing medium Jing CO2High pressure compressor 3 enters oil eliminator 5 after compressing；Pressure in oil eliminator 5, in cold-producing medium
Contracting machine oil is separated, and Jing after oil cooler 6 is cooled down by two branches of oily output pipe, all the way Jing magnetic valves I 16 are back to
CO2Low pressure compressor 1, another road Jing magnetic valves II 17 are back to CO2High pressure compressor 3；The detached HTHP of oil eliminator 5
Gaseous refrigerant enters gas cooler 7, and the reducing pressure by regulating flow of Jing electric expansion valves I 8 enters intercooler 9 after cooling；In centre
Refrigerant air-liquid is separated in cooler 9, and liquid refrigerant is subcooled into heat exchanger 11, and the cold-producing medium after supercooling is divided into two
Road, all the way into evaporimeter 14, another road liquid refrigerant Jing electric expansion valves II 12 enter heat friendship to Jing electric expansion valves III 13
The low pressure feed tube of parallel operation 11, to cooling down from intercooler 9 into the liquid refrigerant of heat exchanger 11, liquid refrigerant
Become gaseous state after evaporation endothermic in a heat exchanger 11；Gaseous refrigerant Jing after evaporimeter 14 evaporates is again through gas-liquid separator
15 enter CO2The air entry of low pressure compressor 1 is compressed, CO2Cold-producing medium is input to middle air cooling after low pressure compressor 1 compresses
Cool down in device 2, the outlet and the low pressure outlet of intercooler 9 of cold-producing medium and heat exchanger 11 after the cooling of middle air cooler 2
Finally converge input to CO2Compression, is circulated in high pressure compressor 3.
The above, is only presently preferred embodiments of the present invention, and any pro forma restriction is not made to the present invention, though
So the present invention is disclosed above with preferred embodiment, but is not limited to the present invention, any to be familiar with this professional technology people
Member in the range of without departing from technical solution of the present invention, when using the technology contents of the disclosure above make it is a little change or be modified to
The Equivalent embodiments of equivalent variations, as long as being the content without departing from technical solution of the present invention, according to the technical spirit pair of the present invention
Any simple modification made for any of the above embodiments, equivalent variations and modification, still fall within the range of technical solution of the present invention.
Claims (1)
1. a kind of carbon dioxide refrigeration circulatory system of employing intermediate pressure feed flow, it is characterised in that include：CO2Low pressure compressor
(1)、CO2High pressure compressor (3), oil eliminator (5), oil cooler (6), gas cooler (7), intercooler (9), centre
Air cooler (2), heat exchanger (11), evaporimeter (14) and gas-liquid separator (15)；
Wherein, CO2The output pipe of high pressure compressor (3) is connected with oil eliminator (5) intake line, and is provided with this pipeline
Check (non-return) valve (4)；
The gas export line of oil eliminator (5) is connected with gas cooler (7) input port, the oily efferent duct of oil eliminator (5)
Road is divided into two-way, all the way with CO2The compressor oil entrance connection of low pressure compressor (1), another road and CO2High pressure compressor (3)
Compressor oil entrance is connected, and and CO2Magnetic valve I (16) is provided with the pipeline of low pressure compressor (1) connection, with CO2High pressure pressure
The pipeline solenoid II (17) of contracting machine (3) connection；
Gas cooler (7) is connected by the pipeline with electric expansion valve I (8) with intercooler (9) gas access；
The drain pipe road of intercooler (9) is connected with the water influent pipeline of heat exchanger (11)；
The drain pipe road of heat exchanger (11) is divided into two-way, all the way the feed tube of Jing electric expansion valves III (13) and evaporimeter (14)
Road is connected, and another road Jing electric expansion valves II (12) are connected with the low pressure feed tube of heat exchanger (11)；
The outlet pipe of evaporimeter (14) is connected with gas-liquid separator (15) entrance；
The outlet pipe and CO of gas-liquid separator (15)2Low pressure compressor (1) air intake duct connects；
CO2The exhaust outlet of low pressure compressor (1) is connected by pipeline with the entrance of middle air cooler (2)；
The escaping pipe Jing electric control valve (10) of intercooler (9) is empty with the low pressure outlet pipe of heat exchanger (11) and centre
The outlet pipe of cooler (2) is connected to CO after converging2In the suction line of high pressure compressor (3).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611059785.5A CN106642786A (en) | 2016-11-24 | 2016-11-24 | Carbon dioxide refrigerating cycle system adopting intermediate pressure for supplying liquid |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611059785.5A CN106642786A (en) | 2016-11-24 | 2016-11-24 | Carbon dioxide refrigerating cycle system adopting intermediate pressure for supplying liquid |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN106642786A true CN106642786A (en) | 2017-05-10 |
Family
ID=58812166
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201611059785.5A Pending CN106642786A (en) | 2016-11-24 | 2016-11-24 | Carbon dioxide refrigerating cycle system adopting intermediate pressure for supplying liquid |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106642786A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110259666A (en) * | 2019-07-25 | 2019-09-20 | 海格尔压缩机(青岛)有限公司 | A kind of cooling device and air compressor machine |
| CN111006412A (en) * | 2019-12-30 | 2020-04-14 | 松下冷机系统（大连）有限公司 | Low-pressure exhaust air-cooled wide-ring-temperature CO2Air source heat pump system |
| CN111059788A (en) * | 2019-12-27 | 2020-04-24 | 天津商业大学 | A Novel CO2 Ice Storage System |
| CN111306827A (en) * | 2019-12-30 | 2020-06-19 | 松下冷机系统（大连）有限公司 | Wide-ring-temperature CO2Air source heat pump system |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110259666A (en) * | 2019-07-25 | 2019-09-20 | 海格尔压缩机(青岛)有限公司 | A kind of cooling device and air compressor machine |
| CN110259666B (en) * | 2019-07-25 | 2024-09-17 | 海格尔压缩机(青岛)有限公司 | Cooling device and air compressor |
| CN111059788A (en) * | 2019-12-27 | 2020-04-24 | 天津商业大学 | A Novel CO2 Ice Storage System |
| CN111006412A (en) * | 2019-12-30 | 2020-04-14 | 松下冷机系统（大连）有限公司 | Low-pressure exhaust air-cooled wide-ring-temperature CO2Air source heat pump system |
| CN111306827A (en) * | 2019-12-30 | 2020-06-19 | 松下冷机系统（大连）有限公司 | Wide-ring-temperature CO2Air source heat pump system |
| CN111006412B (en) * | 2019-12-30 | 2023-08-29 | 冰山冷热科技股份有限公司 | Wide-ring temperature type CO with low-pressure exhaust air cooling 2 Air source heat pump system |
| CN111306827B (en) * | 2019-12-30 | 2023-08-29 | 冰山冷热科技股份有限公司 | Wide-ring temperature type CO 2 Air source heat pump system |
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