CN104315750B - The system and method for cooling gas compressor inlet gas - Google Patents
The system and method for cooling gas compressor inlet gas Download PDFInfo
- Publication number
- CN104315750B CN104315750B CN201410583979.XA CN201410583979A CN104315750B CN 104315750 B CN104315750 B CN 104315750B CN 201410583979 A CN201410583979 A CN 201410583979A CN 104315750 B CN104315750 B CN 104315750B
- Authority
- CN
- China
- Prior art keywords
- gas
- orc
- refrigerant
- compressor
- pressure evaporator
- 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.)
- Active
Links
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
- Y02A30/00—Adapting or protecting infrastructure or their operation
- Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
- Y02A30/274—Relating to heating, ventilation or air conditioning [HVAC] technologies using waste energy, e.g. from internal combustion engine
Landscapes
- Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
Abstract
The invention discloses a kind of system and method cooling down gas compressor inlet gas, the system of described cooling gas compressor inlet gas includes high pressure evaporator, carries out heat exchange in high pressure evaporator, thus realizing the cooling to compressor outlet gas；And by the heat promotion ORC turbine rotation that high pressure evaporator exchanges, ORC turbine drives the motion of ORC compressor, so that refrigerant gas to be compressed；The higher pressure refrigerant gas that refrigerant gas after compression and ORC turbine exhaust mouth are discharged is after condenser condenses, liquid refrigerant is admitted to high pressure evaporator through force (forcing) pump on the one hand, it is admitted to low pressure evaporator on the one hand, to realize the cooling to described compressor inlet gas through air relief valve；In described low pressure evaporator, the liquid refrigeration device of gasification is sent back to refrigeration compressor, thus realizing the periodic duty of cold-producing medium；The visible present invention adopts turbogenerator that waste heat after the level of compressor is utilized, and energy recovery efficiency is high.
Description
Technical field
The present invention relates to the auxiliary equipment of a kind of compressor, particularly relate to a kind of system and method cooling down gas compressor inlet gas.
Background technology
The power consumption of the every one-level of compressor of air or other working medium when pressure ratio is certain with import PTAT；As inlet temperature reduces by 10%, then energy consumption reduces by 10%.This is that any pneumatic design is improved, driven compressor system optimization is all difficult to.Conventional multistage industrial compressors level final vacuum temperature is generally about 100 DEG C, and the energy consumption in order to reduce next stage is generally adopted interstage cooling system.Existing cooling system adopts Environmental Water that upper level delivery temperature is reduced to ambient temperature, and then the gas after cooling enters into next stage, is further compressed.
After existing level, waste heat is generally discharged in air, not only causes energy waste, and causes thermal pollution.Adopting ORC cogeneration is a kind of method currently utilizing ultralow temperature waste heat (waste heat supply temperature is between 90～110 DEG C), but generating efficiency is extremely low, disposable input cost high (being about 15000 yuan/kW).The electricity sent is due to instability, it is difficult to be incorporated to bulk power grid, is commonly referred to as rubbish electricity.
A kind of alternative reducing compressor inlet gas temperature is to utilize motor-driven refrigeration plant to realize, but owing to refrigeration compressor needs at high-speed cruising, it is necessary to step-up gear could drive compressor after being improved by the rotating speed of power frequency motor.This mode causes two problems, and one is the mechanical gearing losses of gear-box and high gear rotates the windage loss causing lubricating oil to rotate；Two is that lubricating oil entrance cold-producing medium causes heat exchanger performance to reduce, in addition it is also necessary to extra equipment carries out cold-producing medium and lubrication oil separating.
The another kind of method utilizing waste heat is lithium bromide absorbing type refrigeration.The COP of absorption refrigeration is very low, and when said temperature, COP is difficult to reach 1.0 (under ARI operating mode, the COP of centrifugal water chiller alreadys more than 7.0).Lithium bromide belongs to salt, and heat exchanger has corrosiveness, it is necessary to adopting expensive material, maintenance cycle is short.The life-span of frequent Absorption Refrigerator is also shorter than compressor.
In summary it can be seen, prior art there is not yet the method and system that waste heat after the level of compressor can carry out effectively utilization.
Summary of the invention
It is an object of the present invention to provide a kind of system and method cooling down gas compressor inlet gas, it can reduce gas compressor gas inlet temperature at different levels, and when not consuming extra power, the inlet temperatures at different levels of gas compressor can be reduced to the temperature of lower pressure environment, significantly reduce the power consumption of compressor.
This invention address that technical problem adopts the following technical scheme that a kind of system cooling down gas compressor inlet gas, including high pressure evaporator, ORC turbine, ORC compressor, condenser, high-pressure pressure-reducing valve, low-pressure relief valve, low pressure evaporator, economizer and force (forcing) pump；
Described high pressure evaporator, low pressure evaporator and economizer all include refrigerant inlet, refrigerant outlet, cooled medium inlet and cooled media outlet；
Described condenser includes refrigerant inlet, refrigerant outlet, cooling medium entrance and cooling medium outlet；
The cooled medium inlet of described high pressure evaporator is connected to the air vent of described gas compressor；
The refrigerant outlet of described high pressure evaporator is connected to the air inlet of described ORC turbine；
The air vent of described ORC turbine is connected to the refrigerant inlet of described condenser；
Described ORC turbine drives described ORC compressor to rotate；
The air vent of described ORC compressor is connected to the refrigerant inlet of described condenser；
The refrigerant outlet of described condenser is connected to the entrance of described high-pressure pressure-reducing valve and the entrance of force (forcing) pump；
Described pressurization delivery side of pump is connected to the refrigerant inlet of described high pressure evaporator；
The outlet of described high-pressure pressure-reducing valve is connected to the refrigerant inlet of described economizer；
The refrigerant outlet of described economizer is connected to the entrance of described low-pressure relief valve；
The refrigerant outlet of described economizer is also attached to the air inlet of described ORC compressor；
The outlet of described low-pressure relief valve is connected to the refrigerant inlet of described low pressure evaporator；
The refrigerant outlet of described low pressure evaporator is connected to the air inlet of described ORC compressor；
The cooled media outlet of described economizer is connected to the cooled medium inlet of described low pressure evaporator；
The cooled media outlet of described low pressure evaporator is connected to the air inlet of described gas compressor.
This invention address that technical problem also adopts the following technical scheme that a kind of system cooling down compound compressor inlet gas, including high pressure evaporator, ORC turbine, ORC compressor, condenser, high-pressure pressure-reducing valve, low-pressure relief valve, low pressure evaporator, economizer, force (forcing) pump and water cooler；
Described high pressure evaporator, low pressure evaporator and economizer all include refrigerant inlet, refrigerant outlet, cooled medium inlet and cooled media outlet；
Described condenser includes refrigerant inlet, refrigerant outlet, cooling medium entrance and cooling medium outlet；
Described water cooler includes cooled medium inlet, cooled media outlet, cooling medium entrance and cooling medium outlet；
The cooled medium inlet of described high pressure evaporator is connected to the level outlet of compound compressor；
The cooled media outlet of described high pressure evaporator is connected to the entrance of the cooled medium of described water cooler；
The refrigerant outlet of described high pressure evaporator is connected to the air inlet of described ORC turbine；
The air vent of described ORC turbine is connected to the refrigerant inlet of described condenser；
Described ORC turbine drives described ORC compressor to rotate；
The air vent of described ORC compressor is connected to the refrigerant inlet of described condenser；
The refrigerant outlet of described condenser is connected to the entrance of described high-pressure pressure-reducing valve and the entrance of force (forcing) pump；
Described pressurization delivery side of pump is connected to the refrigerant inlet of described high pressure evaporator；
The outlet of described high-pressure pressure-reducing valve is connected to the refrigerant inlet of described economizer；
The refrigerant outlet of described economizer is connected to the entrance of described low-pressure relief valve；
The refrigerant outlet of described economizer is also attached to the air inlet of described ORC compressor；
The outlet of described low-pressure relief valve is connected to the refrigerant inlet of described low pressure evaporator；
The refrigerant outlet of described low pressure evaporator is connected to the air inlet of described ORC compressor；
The cooled medium inlet of described economizer is connected to the cooled media outlet of described water cooler；
The cooled media outlet of described economizer is connected to the cooled medium inlet of described low pressure evaporator；
The cooled media outlet of described low pressure evaporator is connected to the level import of the next stage of described compound compressor.
Optionally, described gas compressor is multistage gas compressors, the cooled medium inlet of described high pressure evaporator is connected to the level outlet of compound compressor, and the cooled media outlet of described low pressure evaporator is connected to the level air inlet of the upper level of described multistage gas compressors.
Optionally, described ORC compressor is twin-stage ORC refrigeration compressor, the refrigerant outlet of described economizer is connected to the second level air inlet of described twin-stage ORC refrigeration compressor, and the refrigerant outlet of described low pressure evaporator is connected to the first order air inlet of described twin-stage ORC refrigeration compressor.
Optionally, described twin-stage ORC refrigeration compressor and described ORC turbine are structure as a whole, forming ORC turbine refrigerant compression all-in-one, described ORC turbine refrigerant compression all-in-one includes intermediate, main shaft, turbine volute, one-level spiral case, two grades of spiral cases, turbine wheel, one stage impeller, sencond stage impeller, central dividing plate, thrust disc and sealing member；
The two ends of described intermediate are for having reeded flange, and described main shaft is rotatablely arranged in described intermediate by bearing；
Described turbine volute is fixed on the left end of described intermediate, and described two grades of spiral cases are fixed on the right-hand member of described intermediate, and described one-level spiral case is fixed on described two grades of spiral cases；
Described turbine wheel is fixed on the left end of described main shaft, and is positioned at described turbine volute；Described sencond stage impeller is fixed on the right-hand member of described main shaft, and is positioned at described two grades of spiral cases；Described one stage impeller is fixed on the right-hand member of described main shaft, and is positioned at the right side of described sencond stage impeller, and is positioned at described one-level spiral case；
The right-hand member of described main shaft is additionally provided with central dividing plate, and described central dividing plate is between described one stage impeller and sencond stage impeller；
The left end of described main shaft is also arranged with thrust disc, and described thrust disc is arranged with sealing member, and described sealing member 212 is fixed on the left end of described intermediate.
This invention address that technical problem also adopts the following technical scheme that a kind of method cooling down gas compressor inlet gas, including:
S10, gas compressor institute expellant gas is discharged after high pressure evaporator cools down, and its heat discharged by high pressure evaporator is for heating and cooling agent liquid, and described refrigerant liquid gasify in described high pressure evaporator, formation refrigerant gas；
S20, described refrigerant gas drive ORC turbine to rotate, and described ORC turbine drives twin-stage ORC refrigeration compressor to rotate；And the refrigerant gas that described ORC turbine is discharged is delivered to condenser；
S30, described refrigerant gas become refrigerant liquid after described condenser condenses, and described refrigerant liquid is delivered to high pressure evaporator in part through force (forcing) pump, is delivered to economizer in part through high-pressure pressure-reducing valve；
The gas entering described gas compressor is cooled down by S40, described economizer, and the refrigerant gas of its discharge is transported to the second level of twin-stage ORC refrigeration compressor, after the second level of described twin-stage ORC refrigeration compressor is compressed, is delivered to described condenser；Remaining refrigerant liquid is delivered to described low pressure evaporator through low-pressure relief valve；
The gas entering described gas compressor that described economizer is discharged by S50, described low pressure evaporator cools down, and the gas entering described gas compressor is delivered to described gas compressor；
The refrigerant gas that S60, described low pressure evaporator are discharged is delivered to the first order of twin-stage ORC refrigeration compressor, and after described twin-stage ORC refrigeration compressor compresses, is delivered to described condenser.
This invention address that technical problem also adopts the following technical scheme that a kind of method cooling down multistage gas compressors inlet gas, including:
S10, described multistage gas compressors corresponding levels institute expellant gas, after high pressure evaporator cools down, are delivered to described water cooler, and by, after the cooling of described water cooler, being delivered to economizer；And the heat that described multistage gas compressors institute expellant gas discharges through high pressure evaporator is for heating and cooling agent liquid, described refrigerant liquid gasifies in described high pressure evaporator, forms refrigerant gas；
S20, described refrigerant gas drive ORC turbine to rotate, and described ORC turbine drives twin-stage ORC refrigeration compressor to rotate；The refrigerant gas that described ORC turbine is discharged is delivered to condenser；
S30, described refrigerant gas become refrigerant liquid after described condenser condenses, and described refrigerant liquid is delivered to high pressure evaporator in part through force (forcing) pump, is delivered to economizer in part through high-pressure pressure-reducing valve；
S40, described economizer in S10 step through water cooler cool down after gas cool down further, and the refrigerant gas of its discharge is transported to the second level of twin-stage ORC refrigeration compressor, after the second level of described twin-stage ORC refrigeration compressor is compressed, it is delivered to described condenser；Remaining refrigerant liquid is delivered to described low pressure evaporator through low-pressure relief valve；
The gas entering described multistage gas compressors that described economizer is discharged by S50, described low pressure evaporator cools down, and the gas entering described multistage gas compressors is delivered to the next stage of described multistage gas compressors；
The refrigerant gas that S60, described low pressure evaporator are discharged is delivered to the first order of twin-stage ORC refrigeration compressor, and after described twin-stage ORC refrigeration compressor compresses, is delivered to described condenser.
There is advantages that the ORC of the system of described cooling gas compressor inlet gas circulation includes high pressure evaporator, the cooled medium of the high temperature that compressor higher level (for compound compressor) discharges in high pressure evaporator carries out heat exchange with cold-producing medium, cold-producing medium heats up and gasifies, and cooled medium temperature reduces；The system of described cooling gas compressor inlet gas can also include water cooler；Cooled medium from described high pressure evaporator is cooled down for the second time in water cooler, and heat is taken away by the water；The kind of refrigeration cycle of the system of described cooling gas compressor inlet gas includes economizer, from working medium (the i.e. cooled medium of the gas compressor of water cooler in economizer, can be air) carry out heat exchange with cold-producing medium, cold-producing medium heats up and gasifies, and cooled medium is cooled down for the third time；The kind of refrigeration cycle of the system of described cooling gas compressor inlet gas also includes low pressure evaporator, low pressure evaporator carries out heat exchange from the cooled medium of economizer and cold-producing medium, cold-producing medium heats up and gasifies, cooled medium is cooled down by the 4th time, it is subsequently returned to compound compressor, continues compression；The ORC circulation of the system of described cooling gas compressor inlet gas also includes ORC turbine, and the high temperature liquid refrigerant from described high pressure evaporator expands in ORC turbine, drives described ORC turbine to rotate；The kind of refrigeration cycle of the system of described cooling gas compressor inlet gas also includes twin-stage ORC refrigeration compressor, and gaseous refrigerant is compressed；Gaseous refrigerant and the gaseous refrigerant of ORC turbine exhaust mouth discharge after compression are admitted to condenser, and the liquid refrigerant part after condensation is admitted to high pressure evaporator through force (forcing) pump, and remainder is admitted to economizer through air relief valve；Some liquid refrigerant endothermic gasification in described economizer, is sucked by the second level of twin-stage ORC refrigeration compressor together with entering the gaseous refrigerant that air relief valve produces；In economizer, all the other liquid refrigerants are by entering low pressure evaporator after air relief valve；In described low pressure evaporator, liquid refrigerant endothermic gasification is sucked by twin-stage ORC refrigeration compressor, thus realizing the periodic duty of cold-producing medium；The visible present invention adopts ORC turbine that waste heat after the level of gas compressor is utilized, compared with traditional lithium bromide refrigerating, it is possible to gas compressor is discharged gas and is reduced to lower temperature.
Accompanying drawing explanation
Fig. 1 is the structural representation of the system of the cooling gas compressor inlet gas of the present invention；
Fig. 2 is the structural representation of the system of the cooling multistage gas compressors inlet gas of the present invention；
Fig. 3 is the structural representation of the ORC turbine refrigerant compression all-in-one of the present invention.
In figure, labelling is illustrated as: 101-high pressure evaporator；102-ORC turbine；103-ORC compressor；104-condenser；105-high-pressure pressure-reducing valve；106-low-pressure relief valve；107-low pressure evaporator；108-economizer；109-force (forcing) pump；111-water cooler；201-intermediate；202-main shaft；203-turbine volute；204-one-level spiral case；Bis-grades of spiral cases of 205-；206-turbine wheel；207-one stage impeller；208-sencond stage impeller；209-central dividing plate；210-axle sleeve；211-thrust disc；212-sealing member；213-locknut.
Detailed description of the invention
Below in conjunction with embodiment and accompanying drawing, technical scheme is further elaborated.Shown in figure " → " circulate circuit to indicate entry into described gas compressor institute expellant gas (cooled medium),Represent cold-producing medium circulation circuit；Represent the heat being discharged in environment.
Embodiment 1
With reference to Fig. 1, present embodiments provide a kind of system cooling down gas compressor inlet gas, including high pressure evaporator 101, ORC turbine 102, ORC compressor 103, condenser 104, high-pressure pressure-reducing valve 105, low-pressure relief valve 106, low pressure evaporator 107, economizer 108 and force (forcing) pump 109；Described high pressure and low pressure are meant that by the fluid pressure within described vaporizer or air relief valve or technical term are made a distinction；
Described high pressure evaporator 101, low pressure evaporator 107 and economizer 108 all include refrigerant inlet, refrigerant outlet, cooled medium inlet and cooled media outlet；Described cooled medium is the working medium of described gas compressor, it is possible to for air or other gas；
Described condenser 104 includes refrigerant inlet, refrigerant outlet, cooling medium entrance and cooling medium outlet；Described cooling medium can be Environmental Water, with by described condenser 104 by heat dissipation to environment；
The cooled medium inlet of described high pressure evaporator 101 is connected to the air vent of described gas compressor；When described gas compressor is single-stage gas compressors, the cooled medium inlet of described high pressure evaporator 101 is connected to the air vent of described single-stage gas compressors；When described gas compressor is multistage gas compressors, described multistage gas compressors has multiple grades of outlets, and one of them grade of outlet is connected to the cooled medium inlet of described high pressure evaporator 101；
The cooled media outlet of described high pressure evaporator 101 is as the air vent of described gas compressor；Namely the cooled media outlet of described high pressure evaporator discharges by the gases at high pressure after compressing；
The refrigerant outlet of described high pressure evaporator 101 is connected to the air inlet of described ORC turbine 102；
The air vent of described ORC turbine 102 is connected to the refrigerant inlet of described condenser 104；
Described ORC turbine 102 drives described ORC compressor 103 to rotate；
The air vent of described ORC compressor 103 is connected to the refrigerant inlet of described condenser 104；After the cold-producing medium with pressure that the air vent of the cold-producing medium with pressure that namely air vent of described ORC compressor 103 is discharged and described ORC turbine 102 is discharged converges, the refrigerant inlet of input extremely described condenser 104；
The refrigerant outlet of described condenser 104 is connected to the entrance of described high-pressure pressure-reducing valve 105 and the entrance of force (forcing) pump 109；
The outlet of described force (forcing) pump 109 is connected to the refrigerant inlet of described high pressure evaporator 101；
The outlet of described high-pressure pressure-reducing valve 105 is connected to the refrigerant inlet of described economizer 108；
The refrigerant outlet of described economizer 108 is connected to the entrance of described low-pressure relief valve 106；
The refrigerant outlet of described economizer 108 is also attached to the air inlet of described ORC compressor 103；Preferably, described ORC compressor 103 is twin-stage ORC refrigeration compressor, and the refrigerant outlet of described economizer is also attached to the second level air inlet of described twin-stage ORC refrigeration compressor；
The outlet of described low-pressure relief valve 106 is connected to the refrigerant inlet of described low pressure evaporator 107；
The refrigerant outlet of described low pressure evaporator 107 is connected to the air inlet of described ORC compressor 103, described ORC compressor 103 can be twin-stage ORC refrigeration compressor, and the refrigerant outlet of described low pressure evaporator 107 is connected to the air inlet (air inlet of the first order) of described twin-stage ORC refrigeration compressor；
The cooled medium inlet of described economizer 108 is as the gas suction inlet of described gas compressor；
The cooled media outlet of described economizer 108 is connected to the cooled medium inlet of described low pressure evaporator 107；
The cooled media outlet of described low pressure evaporator 107 is connected to the air inlet of described gas compressor, when described gas compressor is single-stage gas compressors, the cooled media outlet of described low pressure evaporator 107 is connected to the air inlet of described single-stage gas compressors；When described gas compressor is multistage gas compressors, the cooled media outlet of described low pressure evaporator 107 is connected to the level air inlet of the upper level of described multistage gas compressors (exhaust stage relative to described multistage gas compressors).
nullProblem for the low pressure evaporator inefficiency that the pressure of cold-producing medium solving to discharge due to the refrigerant outlet of described economizer brings more than the refrigerant pressure that the refrigerant outlet of described low pressure evaporator is discharged，In the present embodiment，Described ORC compressor 103 is twin-stage ORC refrigeration compressor，It includes first order air inlet and second level air inlet，The refrigerant outlet of described economizer 108 is connected to the second level air inlet of described twin-stage ORC refrigeration compressor，The refrigerant outlet of described low pressure evaporator 107 is connected to the first order air inlet of described twin-stage ORC refrigeration compressor，Adopt this connected mode，After the refrigerant gas that described low pressure evaporator 107 is discharged being compressed by the first order of described twin-stage ORC refrigeration compressor，The refrigerant gas discharged with the refrigerant outlet of described economizer 108 converges，Input is compressed further to the second level of described twin-stage ORC refrigeration compressor，Improve the work efficiency of described low pressure evaporator，And also improve the work efficiency of described twin-stage ORC refrigeration compressor.
In the present embodiment, for multistage gas compressors, the interstage cooler between they are at different levels can adopt the system of embodiment 2.
Embodiment 2
With reference to Fig. 2, present embodiments provide a kind of system cooling down multistage gas compressors inlet gas, including high pressure evaporator 101, ORC turbine 102, ORC compressor 103, condenser 104, high-pressure pressure-reducing valve 105, low-pressure relief valve 106, low pressure evaporator 107, economizer 108, force (forcing) pump 109 and water cooler 111；
Described high pressure evaporator 101, low pressure evaporator 107 and economizer 108 all include refrigerant inlet, refrigerant outlet, cooled medium inlet and cooled media outlet；
Described condenser 104 includes refrigerant inlet, refrigerant outlet, cooling medium entrance and cooling medium outlet；
Described water cooler 111 includes cooled medium inlet, cooled media outlet, cooling medium entrance and cooling medium outlet；
The cooled medium inlet of described high pressure evaporator 101 is connected to the level outlet of multistage gas compressors；
The cooled media outlet of described high pressure evaporator 101 is connected to described water cooler 111 and is cooled the entrance of medium；
The refrigerant outlet of described high pressure evaporator 101 is connected to the air inlet of described ORC turbine 102；
The air vent of described ORC turbine 102 is connected to the refrigerant inlet of described condenser 104；
Described ORC turbine 102 drives described ORC compressor 103 to rotate；
The air vent of described ORC compressor 103 is connected to the refrigerant inlet of described condenser 104；
The refrigerant outlet of described condenser 104 is connected to the entrance of described high-pressure pressure-reducing valve 105 and the entrance of force (forcing) pump 109；
The outlet of described force (forcing) pump 109 is connected to the refrigerant inlet of described high pressure evaporator 101；
The outlet of described high-pressure pressure-reducing valve 105 is connected to the refrigerant inlet of described economizer 108；
The refrigerant outlet of described economizer 108 is connected to the entrance of described low-pressure relief valve 106；
The refrigerant outlet of described economizer 108 is also attached to the air inlet of described ORC compressor 103；
The outlet of described low-pressure relief valve 106 is connected to the refrigerant inlet of described low pressure evaporator 107；
The refrigerant outlet of described low pressure evaporator 107 is connected to the air inlet of described ORC compressor 103；
The cooled medium inlet of described economizer 108 is connected to the cooled media outlet of described water cooler 111；
The cooled media outlet of described economizer 108 is connected to the cooled medium inlet of described low pressure evaporator 107；
The cooled media outlet of described low pressure evaporator 107 is connected to the level import of the next stage of described compound compressor.
In the present embodiment, described ORC compressor 103 is twin-stage ORC refrigeration compressor, the refrigerant outlet of described economizer 108 is connected to the second level air inlet of described twin-stage ORC refrigeration compressor, and the refrigerant outlet of described low pressure evaporator 107 is connected to the first order air inlet of described twin-stage ORC refrigeration compressor.
In the present embodiment, the inlet gas of the first order of described multistage gas compressors can adopt the system cooling down gas compressor inlet gas as described in Example 1 to cool down.
Embodiment 3
With reference to Fig. 3, present embodiments provide a kind of ORC turbine refrigerant compression all-in-one, including intermediate 201, main shaft 202, turbine volute 203,204, two grades of spiral cases 205 of one-level spiral case, turbine wheel 206, one stage impeller 207, sencond stage impeller 208, central dividing plate 209, axle sleeve 210, thrust disc 211, sealing member 212 and locknut 213；
The two ends of described intermediate 201, for having reeded flange, described intermediate 201 offer the dead in line of through hole, the axis of described through hole and described intermediate 201, and described main shaft 202 is rotatablely arranged in the through hole of described intermediate 201 by bearing；
Described turbine volute 203 is fixed on the left end of described intermediate 201, and described two grades of spiral cases 205 are fixed on the right-hand member of described intermediate 201, and described one-level spiral case 204 is fixed on described two grades of spiral cases 205；Described one-level spiral case 204 connects with described two grades of spiral cases 205, and described one-level spiral case 204 includes air inlet and air vent, and its air vent is communicated in the air inlet of described two grades of spiral cases 205；Described two grades of spiral cases 205 include air inlet and air vent；
Described turbine wheel 206 is fixed on the left end of described main shaft 202, and is positioned at described turbine volute 203；Described sencond stage impeller 208 is fixed on the right-hand member of described main shaft 202, and is positioned at described two grades of spiral cases 205；Described one stage impeller 207 is fixed on the right-hand member of described main shaft 202, and is positioned at the right side of described sencond stage impeller 208, and is positioned at described one-level spiral case 204；Described turbine wheel 206 drives described main shaft 202 to rotate, and described main shaft 202 drives described sencond stage impeller 208 and one stage impeller 207 to rotate；
The right-hand member of described main shaft 202 is additionally provided with central dividing plate 209, described central dividing plate 209 between described one stage impeller 207 and sencond stage impeller 208, described central dividing plate 209 and described one stage impeller 207 and sencond stage impeller 208 synchronous axial system；In the present embodiment, it is preferable that described central dividing plate 209 is arranged on described main shaft 202 by axle sleeve 210；
The left end of described main shaft 202 is also arranged with thrust disc 211, and described thrust disc 211 is arranged with sealing member 212, and described sealing member 212 is fixed on the left end of described intermediate 201；
Offering multiple blow vent on described intermediate 201, described bearing is air-bearing, can be supplied to described air-bearing by described blow vent；
The two ends, left and right of described main shaft 201 are respectively arranged with locknut 213, so that described turbine wheel 206 to be fixed on the left end of described main shaft 202, and described one stage impeller 207 and sencond stage impeller 208 are fixed on the right-hand member of described main shaft 202.
In the present embodiment, it is preferable that described sealing member 212 is arranged in the groove of described intermediate 201.
Embodiment 4
Present embodiments provide a kind of method cooling down gas compressor inlet gas, including:
S10, gas compressor institute expellant gas is discharged after high pressure evaporator cools down, and its heat discharged by high pressure evaporator is for heating and cooling agent liquid, and described refrigerant liquid gasify in described high pressure evaporator, formation refrigerant gas；
S20, described refrigerant gas drive ORC turbine to rotate, and described ORC turbine drives twin-stage ORC refrigeration compressor to rotate；And the refrigerant gas that described ORC turbine is discharged is delivered to condenser；
S30, described refrigerant gas become refrigerant liquid after described condenser condenses, and described refrigerant liquid is delivered to high pressure evaporator in part through force (forcing) pump, is delivered to economizer in part through high-pressure pressure-reducing valve；
The gas entering described gas compressor is cooled down by S40, described economizer, and the refrigerant gas of its discharge is transported to the second level of twin-stage ORC refrigeration compressor, after the second level of described twin-stage ORC refrigeration compressor is compressed, is delivered to described condenser；Remaining refrigerant liquid is delivered to described low pressure evaporator through low-pressure relief valve；
The gas entering described gas compressor that described economizer is discharged by S50, described low pressure evaporator cools down, and the gas entering described gas compressor is delivered to described gas compressor；
The refrigerant gas that S60, described low pressure evaporator are discharged is delivered to the first order of twin-stage ORC refrigeration compressor, and after described twin-stage ORC refrigeration compressor compresses, is delivered to described condenser.
Embodiment 5
Present embodiments provide a kind of method cooling down multistage gas compressors inlet gas, including:
S10, described multistage gas compressors corresponding levels institute expellant gas, after high pressure evaporator cools down, are delivered to described water cooler, and by, after the cooling of described water cooler, being delivered to economizer；And the heat that described multistage gas compressors institute expellant gas discharges through high pressure evaporator is for heating and cooling agent liquid, described refrigerant liquid gasifies in described high pressure evaporator, forms refrigerant gas；
S20, described refrigerant gas drive ORC turbine to rotate, and described ORC turbine drives twin-stage ORC refrigeration compressor to rotate；The refrigerant gas that described ORC turbine is discharged is delivered to condenser；
S30, described refrigerant gas become refrigerant liquid after described condenser condenses, and described refrigerant liquid is delivered to high pressure evaporator in part through force (forcing) pump, is delivered to economizer in part through high-pressure pressure-reducing valve；
S40, described economizer in S10 step through water cooler cool down after gas cool down further, and the refrigerant gas of its discharge is transported to the second level of twin-stage ORC refrigeration compressor, after the second level of described twin-stage ORC refrigeration compressor is compressed, it is delivered to described condenser；Remaining refrigerant liquid is delivered to described low pressure evaporator through low-pressure relief valve；
The gas entering described multistage gas compressors that described economizer is discharged by S50, described low pressure evaporator cools down, and the gas entering described multistage gas compressors is delivered to the next stage of described multistage gas compressors；
The refrigerant gas that S60, described low pressure evaporator are discharged is delivered to the first order of twin-stage ORC refrigeration compressor, and after described twin-stage ORC refrigeration compressor compresses, is delivered to described condenser.
Referring to Fig. 1-3, the ultimate principle of the present invention is: after utilizing gas compressor (can be multistage gas compressors) level, waste heat reduces the gas inlet temperature of level.Being directed to multistage gas compressors, its every one-level can be used alone the cooling system of oneself, it is also possible to shares a cooling system.After the level of gas compressor, hot-air progressively cools down in four heat exchangers (high pressure evaporator, water cooler, economizer and low pressure evaporator).Hot-air after gas compressor level heats in high pressure evaporator and makes refrigerant liquid gasify, the refrigerant gas of High Temperature High Pressure expands generation mechanical power in ORC turbine, subsequently into the cooled liquefaction of condenser, refrigerant liquid is pressurized is pumped back to high pressure evaporator, completes a Rankine cycle.Because working media is macromolecule organic media, this process is also referred to as organic Rankine bottoming cycle (OrganicRankineCycle).The mechanical power that ORC turbine produces drives ORC compressor, gaseous refrigerant in low pressure evaporator is sucked by it, send into condenser after compression cool down and liquefy, refrigerant liquid reduces pressure after air relief valve and forms gas liquid mixture entrance low pressure evaporator, refrigerant liquid is absorbed into the heat of the inlet gas of gas compressor in low pressure evaporator and gasifies, and completes kind of refrigeration cycle.Therefore, in ORC circulates, the heat of gas compressor exit gas is absorbed and used and cools down, and in kind of refrigeration cycle, compressor outlet gas is further cooled, and temperature drops below the temperature of atmospheric environment.
Referring to Fig. 3, same main shaft shared by the ORC turbine refrigerant compression all-in-one of the present invention, is transferred on twin-stage ORC refrigeration compressor by the moment of torsion that ORC turbine produces, has been automatically obtained the dynamic equilibrium of system.Concrete equilibrium process describes as follows:
1., when gas compressor has just started or pressure ratio is relatively low, level final vacuum temperature is relatively low.Force (forcing) pump low cruise, makes high pressure evaporator be in relatively low saturation pressure, and some liquid refrigerant gasifies, and ORC turbine starts to rotate.
2.ORC turbine drives twin-stage ORC refrigeration compressor to start low speed rotation, gaseous refrigerant in low pressure evaporator is drawn in refrigeration compressor by twin-stage ORC refrigeration compressor, cause the reduction of the saturation pressure in low pressure evaporator and temperature, more refrigerant liquid is gasified, and the gas inlet temperature of gas compressor is lowered simultaneously.
3. when gas compressor enters into normal operating conditions, level final vacuum temperature improves, and force (forcing) pump speed-raising enters normal operating condition.High pressure evaporator saturation pressure and temperature improve, and ORC turbine accelerates to produce more merit, and twin-stage ORC refrigeration compressor produces more refrigerating capacity, and the gas inlet temperature of gas compressor is reduced by a step to the greatest extent.
4. the force (forcing) pump of the present embodiment carries out rotating speed control by the height of the liquid level of the refrigerant liquid in high pressure evaporator；Particularly as follows: the rotating speed of described force (forcing) pump makes the highly stable of the liquid level of the refrigerant liquid in described high pressure evaporator, namely the amount of its liquid refrigerant pumped is identical with the amount of the liquid refrigerant that described high pressure evaporator evaporates.
The direct effect of the present invention is the temperature gas inlet temperature of gas compressor being fallen below environment (kind of refrigeration cycle), and gas inlet temperature can only be dropped to ambient temperature at most by existing water cooling system.Assuming that compressor stage final vacuum temperature is 110 DEG C, temperature after water cooler is 35 DEG C, as adopted R134a as cold-producing medium, it is all 85% at ORC turbine and twin-stage ORC refrigerant compression engine efficiency, high pressure and low pressure evaporator close to temperature be all 5 DEG C when, if gas compressor gas inlet temperature is 25 DEG C (first order), then the present invention can be reduced to 12 DEG C gas inlet temperature, the interstage cooler of the present invention can drop to 16 DEG C gas temperature, therefore, the power consumption of compound compressor can decrease beyond 5%.
The indirect effect of the present invention is a simplified the design of large centrifugal gas compressor.The key factor of decision centrifugal gas compressor size is import volume flow, and flow is more big, and impeller inlet diameter is more big.Due to the restriction of impeller material intensity, not can exceed that higher limit at certain rotating speed lower inlet diameter.Due to this restriction, the first order of large centrifugal gas compressor has to adopt higher specific speed design to sacrifice performance.After adopting the present invention, the reduction of gas inlet temperature causes the minimizing of import volume flow, thus reduces specific speed, improves the performance of air compressor.
The sequencing of above example only for ease of describing, does not represent the quality of embodiment.
Last it is noted that above example is only in order to illustrate technical scheme, it is not intended to limit；Although the present invention being described in detail with reference to previous embodiment, it will be understood by those within the art that: the technical scheme described in foregoing embodiments still can be modified by it, or wherein portion of techniques feature is carried out equivalent replacement；And these amendments or replacement, do not make the essence of appropriate technical solution depart from the spirit and scope of various embodiments of the present invention technical scheme.
Claims (9)
1. the system cooling down gas compressor inlet gas, it is characterised in that include high pressure evaporator, ORC turbine, ORC compressor, condenser, high-pressure pressure-reducing valve, low-pressure relief valve, low pressure evaporator, economizer and force (forcing) pump；
Described high pressure evaporator, low pressure evaporator and economizer all include refrigerant inlet, refrigerant outlet, cooled medium inlet and cooled media outlet；
Described condenser includes refrigerant inlet, refrigerant outlet, cooling medium entrance and cooling medium outlet；
The cooled medium inlet of described high pressure evaporator is connected to the air vent of described gas compressor；
The refrigerant outlet of described high pressure evaporator is connected to the air inlet of described ORC turbine；
The air vent of described ORC turbine is connected to the refrigerant inlet of described condenser；
Described ORC turbine drives described ORC compressor to rotate；
The air vent of described ORC compressor is connected to the refrigerant inlet of described condenser；
The refrigerant outlet of described condenser is connected to the entrance of described high-pressure pressure-reducing valve and the entrance of force (forcing) pump；
Described pressurization delivery side of pump is connected to the refrigerant inlet of described high pressure evaporator；
The outlet of described high-pressure pressure-reducing valve is connected to the refrigerant inlet of described economizer；
The refrigerant outlet of described economizer is connected to the entrance of described low-pressure relief valve；
The refrigerant outlet of described economizer is also attached to the air inlet of described ORC compressor；
The outlet of described low-pressure relief valve is connected to the refrigerant inlet of described low pressure evaporator；
The refrigerant outlet of described low pressure evaporator is connected to the air inlet of described ORC compressor；
The cooled media outlet of described economizer is connected to the cooled medium inlet of described low pressure evaporator；
The cooled media outlet of described low pressure evaporator is connected to the air inlet of described gas compressor.
2. the system of cooling gas compressor inlet gas according to claim 1, it is characterized in that, described gas compressor is multistage gas compressors, the cooled medium inlet of described high pressure evaporator is connected to the level outlet of compound compressor, and the cooled media outlet of described low pressure evaporator is connected to the level air inlet of the upper level of described multistage gas compressors.
3. the system of cooling gas compressor inlet gas according to claim 1, it is characterized in that, described ORC compressor is twin-stage ORC refrigeration compressor, the refrigerant outlet of described economizer is connected to the second level air inlet of described twin-stage ORC refrigeration compressor, and the refrigerant outlet of described low pressure evaporator is connected to the first order air inlet of described twin-stage ORC refrigeration compressor.
4. the system of cooling gas compressor inlet gas according to claim 3, it is characterized in that, described twin-stage ORC refrigeration compressor and described ORC turbine are structure as a whole, forming ORC turbine refrigerant compression all-in-one, described ORC turbine refrigerant compression all-in-one includes intermediate, main shaft, turbine volute, one-level spiral case, two grades of spiral cases, turbine wheel, one stage impeller, sencond stage impeller, central dividing plate, thrust disc and sealing member；
The two ends of described intermediate are for having reeded flange, and described main shaft is rotatablely arranged in described intermediate by bearing；
Described turbine volute is fixed on the left end of described intermediate, and described two grades of spiral cases are fixed on the right-hand member of described intermediate, and described one-level spiral case is fixed on described two grades of spiral cases；
Described turbine wheel is fixed on the left end of described main shaft, and is positioned at described turbine volute；Described sencond stage impeller is fixed on the right-hand member of described main shaft, and is positioned at described two grades of spiral cases；Described one stage impeller is fixed on the right-hand member of described main shaft, and is positioned at the right side of described sencond stage impeller, and is positioned at described one-level spiral case；
The right-hand member of described main shaft is additionally provided with central dividing plate, and described central dividing plate is between described one stage impeller and sencond stage impeller；
The left end of described main shaft is also arranged with thrust disc, and described thrust disc is arranged with sealing member, and described sealing member is fixed on the left end of described intermediate.
5. the system cooling down compound compressor inlet gas, it is characterised in that include high pressure evaporator, ORC turbine, ORC compressor, condenser, high-pressure pressure-reducing valve, low-pressure relief valve, low pressure evaporator, economizer, force (forcing) pump and water cooler；
Described high pressure evaporator, low pressure evaporator and economizer all include refrigerant inlet, refrigerant outlet, cooled medium inlet and cooled media outlet；
Described condenser includes refrigerant inlet, refrigerant outlet, cooling medium entrance and cooling medium outlet；
Described water cooler includes cooled medium inlet, cooled media outlet, cooling medium entrance and cooling medium outlet；
The cooled medium inlet of described high pressure evaporator is connected to the level outlet of compound compressor；
The cooled media outlet of described high pressure evaporator is connected to the entrance of the cooled medium of described water cooler；
The refrigerant outlet of described high pressure evaporator is connected to the air inlet of described ORC turbine；
The air vent of described ORC turbine is connected to the refrigerant inlet of described condenser；
Described ORC turbine drives described ORC compressor to rotate；
The air vent of described ORC compressor is connected to the refrigerant inlet of described condenser；
The refrigerant outlet of described condenser is connected to the entrance of described high-pressure pressure-reducing valve and the entrance of force (forcing) pump；
Described pressurization delivery side of pump is connected to the refrigerant inlet of described high pressure evaporator；
The outlet of described high-pressure pressure-reducing valve is connected to the refrigerant inlet of described economizer；
The refrigerant outlet of described economizer is connected to the entrance of described low-pressure relief valve；
The refrigerant outlet of described economizer is also attached to the air inlet of described ORC compressor；
The outlet of described low-pressure relief valve is connected to the refrigerant inlet of described low pressure evaporator；
The refrigerant outlet of described low pressure evaporator is connected to the air inlet of described ORC compressor；
The cooled medium inlet of described economizer is connected to the cooled media outlet of described water cooler；
The cooled media outlet of described economizer is connected to the cooled medium inlet of described low pressure evaporator；
The cooled media outlet of described low pressure evaporator is connected to the level import of the next stage of described compound compressor.
6. the system of cooling compound compressor inlet gas according to claim 5, it is characterized in that, described ORC compressor is twin-stage ORC refrigeration compressor, the refrigerant outlet of described economizer is connected to the second level air inlet of described twin-stage ORC refrigeration compressor, and the refrigerant outlet of described low pressure evaporator is connected to the first order air inlet of described twin-stage ORC refrigeration compressor.
7. the system of cooling compound compressor inlet gas according to claim 6, it is characterized in that, described twin-stage ORC refrigeration compressor and described ORC turbine are structure as a whole, forming ORC turbine refrigerant compression all-in-one, described ORC turbine refrigerant compression all-in-one includes intermediate, main shaft, turbine volute, one-level spiral case, two grades of spiral cases, turbine wheel, one stage impeller, sencond stage impeller, central dividing plate, thrust disc and sealing member；
The two ends of described intermediate are for having reeded flange, and described main shaft is rotatablely arranged in described intermediate by bearing；
Described turbine volute is fixed on the left end of described intermediate, and described two grades of spiral cases are fixed on the right-hand member of described intermediate, and described one-level spiral case is fixed on described two grades of spiral cases；
Described turbine wheel is fixed on the left end of described main shaft, and is positioned at described turbine volute；Described sencond stage impeller is fixed on the right-hand member of described main shaft, and is positioned at described two grades of spiral cases；Described one stage impeller is fixed on the right-hand member of described main shaft, and is positioned at the right side of described sencond stage impeller, and is positioned at described one-level spiral case；
The right-hand member of described main shaft is additionally provided with central dividing plate, and described central dividing plate is between described one stage impeller and sencond stage impeller；
The left end of described main shaft is also arranged with thrust disc, and described thrust disc is arranged with sealing member, and described sealing member is fixed on the left end of described intermediate.
8. the method cooling down gas compressor inlet gas, it is characterised in that including:
S10, gas compressor institute expellant gas is discharged after high pressure evaporator cools down, and its heat discharged by high pressure evaporator is for heating and cooling agent liquid, and described refrigerant liquid gasify in described high pressure evaporator, formation refrigerant gas；
S20, described refrigerant gas drive ORC turbine to rotate, and described ORC turbine drives twin-stage ORC refrigeration compressor to rotate；And the refrigerant gas that described ORC turbine is discharged is delivered to condenser；
S30, described refrigerant gas become refrigerant liquid after described condenser condenses, and described refrigerant liquid is delivered to high pressure evaporator in part through force (forcing) pump, is delivered to economizer in part through high-pressure pressure-reducing valve；
The gas entering described gas compressor is cooled down by S40, described economizer, and the refrigerant gas of its discharge is transported to the second level of twin-stage ORC refrigeration compressor, after the second level of described twin-stage ORC refrigeration compressor is compressed, is delivered to described condenser；Remaining refrigerant liquid is delivered to low pressure evaporator through low-pressure relief valve；
The gas entering described gas compressor that described economizer is discharged by S50, described low pressure evaporator cools down, and the gas entering described gas compressor is delivered to described gas compressor；
The refrigerant gas that S60, described low pressure evaporator are discharged is delivered to the first order of twin-stage ORC refrigeration compressor, and after described twin-stage ORC refrigeration compressor compresses, is delivered to described condenser.
9. the method cooling down multistage gas compressors inlet gas, it is characterised in that including:
S10, described multistage gas compressors corresponding levels institute expellant gas, after high pressure evaporator cools down, are delivered to water cooler, and by, after the cooling of described water cooler, being delivered to economizer；And the heat that described multistage gas compressors institute expellant gas discharges through high pressure evaporator is for heating and cooling agent liquid, described refrigerant liquid gasifies in described high pressure evaporator, forms refrigerant gas；
S20, described refrigerant gas drive ORC turbine to rotate, and described ORC turbine drives twin-stage ORC refrigeration compressor to rotate；The refrigerant gas that described ORC turbine is discharged is delivered to condenser；
S30, described refrigerant gas become refrigerant liquid after described condenser condenses, and described refrigerant liquid is delivered to high pressure evaporator in part through force (forcing) pump, is delivered to economizer in part through high-pressure pressure-reducing valve；
S40, described economizer in S10 step through water cooler cool down after gas cool down further, and the refrigerant gas of its discharge is transported to the second level of twin-stage ORC refrigeration compressor, after the second level of described twin-stage ORC refrigeration compressor is compressed, it is delivered to described condenser；Remaining refrigerant liquid is delivered to low pressure evaporator through low-pressure relief valve；
The gas entering described multistage gas compressors that described economizer is discharged by S50, described low pressure evaporator cools down, and the gas entering described multistage gas compressors is delivered to the next stage of described multistage gas compressors；
The refrigerant gas that S60, described low pressure evaporator are discharged is delivered to the first order of twin-stage ORC refrigeration compressor, and after described twin-stage ORC refrigeration compressor compresses, is delivered to described condenser.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410583979.XA CN104315750B (en) | 2014-10-27 | 2014-10-27 | The system and method for cooling gas compressor inlet gas |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410583979.XA CN104315750B (en) | 2014-10-27 | 2014-10-27 | The system and method for cooling gas compressor inlet gas |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104315750A CN104315750A (en) | 2015-01-28 |
| CN104315750B true CN104315750B (en) | 2016-07-27 |
Family
ID=52371019
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410583979.XA Active CN104315750B (en) | 2014-10-27 | 2014-10-27 | The system and method for cooling gas compressor inlet gas |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104315750B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3507494A4 (en) * | 2016-09-01 | 2020-05-13 | Norlin, Petrus | A apparatus for compressing gas using heat as energy source |
| CN108167040B (en) * | 2017-11-17 | 2020-05-15 | 昆明理工大学 | Double-pressure expansion organic Rankine cycle recovery medium-low temperature waste heat power generation system |
| CN108150376A (en) * | 2018-01-31 | 2018-06-12 | 福建双环能源科技股份有限公司 | A kind of plunger pump for pumping ultra-low temperature liquid nitrogen |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20040104034A (en) * | 2003-06-02 | 2004-12-10 | 삼성테크윈 주식회사 | Compressor cooled by turbine |
| CN1910347A (en) * | 2004-01-23 | 2007-02-07 | 约克国际公司 | Integrated adaptive capacity control for a steam turbine powered chiller unit |
| CN101027468A (en) * | 2002-11-13 | 2007-08-29 | 开利公司 | Combined rankine and vapor compression cycles |
| JP2009204201A (en) * | 2008-02-27 | 2009-09-10 | Panasonic Corp | Refrigeration cycle device |
| CN101688702A (en) * | 2007-05-22 | 2010-03-31 | 安吉尔安东尼工业股份公司 | Refrigerating device and method for circulating a refrigerating fluid associated with it |
| CN204268753U (en) * | 2014-10-27 | 2015-04-15 | 势加透博（北京）科技有限公司 | The system of refrigerating gas compressor or compound compressor inlet gas |
-
2014
- 2014-10-27 CN CN201410583979.XA patent/CN104315750B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101027468A (en) * | 2002-11-13 | 2007-08-29 | 开利公司 | Combined rankine and vapor compression cycles |
| KR20040104034A (en) * | 2003-06-02 | 2004-12-10 | 삼성테크윈 주식회사 | Compressor cooled by turbine |
| CN1910347A (en) * | 2004-01-23 | 2007-02-07 | 约克国际公司 | Integrated adaptive capacity control for a steam turbine powered chiller unit |
| CN101688702A (en) * | 2007-05-22 | 2010-03-31 | 安吉尔安东尼工业股份公司 | Refrigerating device and method for circulating a refrigerating fluid associated with it |
| JP2009204201A (en) * | 2008-02-27 | 2009-09-10 | Panasonic Corp | Refrigeration cycle device |
| CN204268753U (en) * | 2014-10-27 | 2015-04-15 | 势加透博（北京）科技有限公司 | The system of refrigerating gas compressor or compound compressor inlet gas |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104315750A (en) | 2015-01-28 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP2035711B1 (en) | Multistage compressor device | |
| CN210345951U (en) | Gas suspension heat pump unit | |
| CN101105346A (en) | Frequency conversion magnetic levitation compression expansion engine set | |
| CA3074392C (en) | A combined heat recovery and chilling system and method | |
| CN101072935A (en) | Combined rankine and vapor compression cycles | |
| CN101473174A (en) | System and method for reducing windage losses in compressor motors | |
| WO2016058365A1 (en) | Air conditioning unit and operation method | |
| US9372022B2 (en) | Compressor waste heat driven cooling system | |
| JP2009270745A (en) | Refrigerating system | |
| US20150176485A1 (en) | Dual-end drive gas turbine | |
| CN103775148A (en) | Self-cooled thermal power acting method | |
| AU2011217609B2 (en) | Apparatus for air conditioning or water production | |
| CN105698434A (en) | Compressed air refrigerating and hot water producingdevice | |
| CN104315750B (en) | The system and method for cooling gas compressor inlet gas | |
| JPH11503223A (en) | Cooling system | |
| CN101963161A (en) | Turbocompressor and refrigerating machine | |
| WO2014076508A1 (en) | Improvements in refrigeration | |
| CN108120043A (en) | A kind of air vacuum spray penetration refrigerating plant and its method for realizing deep refrigerating | |
| JP6064489B2 (en) | Turbo refrigerator | |
| CN204268753U (en) | The system of refrigerating gas compressor or compound compressor inlet gas | |
| US8833102B2 (en) | Turbo compressor and refrigerator | |
| CN205619622U (en) | Compressed air refrigeration and preparation hot water system | |
| CN105339743A (en) | Turbo refrigerator | |
| CN211261360U (en) | Compressor system and air conditioning unit | |
| CN209671023U (en) | The refrigeration power supply combined system that natural gas waste cold utilizes |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |