CN110131912B - Refrigeration power generation device using pneumatic compressor - Google Patents
Refrigeration power generation device using pneumatic compressor Download PDFInfo
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- CN110131912B CN110131912B CN201910465848.4A CN201910465848A CN110131912B CN 110131912 B CN110131912 B CN 110131912B CN 201910465848 A CN201910465848 A CN 201910465848A CN 110131912 B CN110131912 B CN 110131912B
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 99
- 238000010248 power generation Methods 0.000 title claims abstract description 43
- 239000007788 liquid Substances 0.000 claims abstract description 149
- 230000006835 compression Effects 0.000 claims abstract description 33
- 238000007906 compression Methods 0.000 claims abstract description 33
- 238000009833 condensation Methods 0.000 claims abstract description 9
- 230000005494 condensation Effects 0.000 claims abstract description 9
- 239000003507 refrigerant Substances 0.000 claims abstract description 6
- 239000013589 supplement Substances 0.000 claims abstract description 5
- 238000009835 boiling Methods 0.000 claims abstract description 4
- 238000001816 cooling Methods 0.000 claims description 29
- 229920006395 saturated elastomer Polymers 0.000 claims description 25
- 239000000498 cooling water Substances 0.000 claims description 17
- 238000003860 storage Methods 0.000 claims description 8
- 238000010992 reflux Methods 0.000 claims description 7
- 230000001502 supplementing effect Effects 0.000 claims description 5
- 241000353097 Molva molva Species 0.000 claims description 3
- 239000012530 fluid Substances 0.000 claims description 3
- 238000005192 partition Methods 0.000 claims 3
- 238000000605 extraction Methods 0.000 claims 1
- 238000002156 mixing Methods 0.000 abstract description 5
- 239000007789 gas Substances 0.000 description 74
- ATUOYWHBWRKTHZ-UHFFFAOYSA-N Propane Chemical compound CCC ATUOYWHBWRKTHZ-UHFFFAOYSA-N 0.000 description 20
- 239000001294 propane Substances 0.000 description 11
- 238000005265 energy consumption Methods 0.000 description 10
- 238000004781 supercooling Methods 0.000 description 10
- 238000000034 method Methods 0.000 description 7
- 238000000926 separation method Methods 0.000 description 5
- 238000005516 engineering process Methods 0.000 description 4
- 238000005381 potential energy Methods 0.000 description 4
- 230000007423 decrease Effects 0.000 description 3
- 238000009413 insulation Methods 0.000 description 3
- 239000000203 mixture Substances 0.000 description 3
- 239000011555 saturated liquid Substances 0.000 description 3
- 239000013526 supercooled liquid Substances 0.000 description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 3
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 2
- 230000007613 environmental effect Effects 0.000 description 2
- 239000011261 inert gas Substances 0.000 description 2
- 239000012774 insulation material Substances 0.000 description 2
- 238000004321 preservation Methods 0.000 description 2
- 238000005086 pumping Methods 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000003139 buffering effect Effects 0.000 description 1
- 229910002092 carbon dioxide Inorganic materials 0.000 description 1
- 239000001569 carbon dioxide Substances 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 239000011810 insulating material Substances 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 239000004576 sand Substances 0.000 description 1
- 238000001179 sorption measurement Methods 0.000 description 1
- 230000009469 supplementation Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01D15/10—Adaptations for driving, or combinations with, electric generators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
- F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
- F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
- F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
- F04B9/103—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber
- F04B9/105—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber reciprocating movement of the pumping member being obtained by a double-acting liquid motor
-
- 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
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
Abstract
A refrigeration power generation device using a pneumatic compressor comprises a refrigeration cycle and a power generation cycle, wherein the refrigeration cycle can be independently used for refrigeration and can also be used for condensation of exhaust gas of the power generation cycle; the refrigeration cycle consists of 3 cycle subsystems: the pneumatic compression circulation subsystem takes a pneumatic compressor as a core, low-grade heat energy is absorbed through mixing of pressurized liquid and gas, low-pressure gas generated by the cold energy gain circulation subsystem is compressed, the cold energy gain circulation subsystem outputs cold energy and provides energy for the low-pressure cold compensation circulation subsystem, and the low-pressure cold compensation circulation subsystem generates cold energy to supplement the pneumatic compression circulation subsystem; the refrigeration cycle working medium adopts single-component or multi-component natural working medium existing in air, and the power generation cycle refrigerant working medium adopts single-component or multi-component synthetic natural or quasi-natural working medium with low boiling point temperature; the energy required by the refrigeration cycle mainly comes from low-grade heat energy below 40 ℃, and the low-grade heat energy below 80 ℃ which can be utilized by the power generation cycle generates power.
Description
Technical field
The patent application relates to the technical fields of thermal energy power, refrigeration, power generation and the like, and is a technology for refrigerating and power generation by utilizing low-grade thermal energy.
Two background art
The gas compression refrigeration is the most widely used refrigeration mode, the refrigeration coefficient of performance (COP value, which refers to the ratio of the energy received by the system to the refrigerating capacity) is generally below 4, and the unit refrigerating capacity energy consumption of high-grade energy (such as electric energy) of the gas compression refrigeration is relatively large.
Other technologies capable of utilizing low-grade heat energy for refrigeration include steam jet refrigeration, absorption refrigeration, adsorption refrigeration and the like, and combinations of the above refrigeration technologies, wherein the refrigeration performance coefficient is generally below 2, and the unit refrigeration energy consumption of high-grade energy is reduced due to the utilization of low-grade heat energy; thermo-acoustic refrigeration technology is still in experimental stage and has not been applied in large scale industry and commerce.
The low-temperature liquid cold energy recovery mode such as LNG is used for refrigerating, the energy consumption per unit refrigerating capacity is low, the temperature of the output cold energy is also low, but the energy consumption per unit liquid during liquefaction is higher.
Most refrigerants, except for a few refrigerants such as carbon dioxide, have the problems of high environmental protection risk, poor economy, low safety and the like.
The device can utilize low-grade heat energy for refrigeration and power generation, the working medium is generally condensed by adopting natural cooling, air cooling, water cooling and other modes, and the available low-grade heat energy is generally higher than 80 ℃ depending on the environmental temperature.
Three summary of the invention
Object of the present patent application: the low-grade heat energy can be utilized for refrigeration, the energy consumption per refrigeration capacity is low, the temperature of the cold output by the device is low, the cold can be used for refrigeration or low-grade heat energy power generation, and the cycle working medium is safe, environment-friendly and economical.
The power generation circulation refrigerant working medium adopts a single-component or multi-component synthesized natural or quasi-natural working medium with low boiling point temperature, and the refrigeration circulation working medium adopts a single-component or multi-component natural working medium existing in the air. The refrigeration cycle consists of 3 cycle subsystems: a pneumatic compression circulation subsystem, a cold energy gain circulation subsystem and a low-pressure cold compensation circulation subsystem; the pneumatic compression circulation subsystem adopts a pneumatic compressor to replace a traditional gas compressor, wet saturated steam obtained by mixing low-temperature liquid and superheated gas with the same pressure is used for doing work to compress low-pressure gas working medium, the wet saturated steam is subjected to gas-liquid separation, and the liquid and the gas are respectively pressurized and then recycled; the energy of the cold energy gain circulation subsystem is from pressure potential energy generated by the pneumatic compression circulation subsystem and low-grade heat energy brought by heat exchange, and cold energy is generated by the expansion of a pressurizing and heating working medium; the low-pressure cold-supplementing circulation subsystem is used for supplementing cold energy generated by low-pressure gas compression and expansion to the pneumatic compression circulation subsystem, and the energy of gas compression is from the energy recovered after the gas expansion of the subsystem and the energy generated by the gas expansion of the cold energy gain circulation subsystem; the cold energy output by the cold energy gain circulation subsystem has low temperature, can be independently operated for refrigeration, and can also be used for condensing working medium in low-grade heat energy power generation circulation; and in the power generation cycle, the final stage exhaust condensation, the middle-pumping exhaust condensation and the circulating cooling water of the steam turbine are cooled, and the cooling capacity is repeatedly utilized in a stepwise manner.
The refrigeration performance coefficient of the patent application is higher than that of the common gas compression refrigeration; natural or quasi-natural working media are adopted, so that the method is safe, environment-friendly and economical; the available low-grade heat energy below 40 ℃ is used for refrigeration, and the available low-grade heat energy below 80 ℃ is used for power generation.
Description of the four drawings
FIG. 1 is a schematic view of the process flow of the present patent application, wherein the devices and components of the marked parts are respectively: an adiabatic cryogenic liquid storage tank (01), a cryogenic liquid delivery pump (02), a refrigeration cycle gas-liquid separator (03), a subcooler (04), a refrigeration cycle cryogenic pump (05), a motor (06), a cryogenic fan (07), a medium-pressure buffer tank (08), an upper cylinder one-way valve (09), a lower cylinder one-way valve (10), a pneumatic compressor (11), a switching device (12), an upper cylinder outlet valve (13), a lower cylinder outlet valve (14), a switching device exhaust valve (16), a gas-liquid mixer liquid supply valve (17), a gas-liquid mixer (18), a low-pressure expander (19), a primary compressor (20), a primary cooler (21), a medium-pressure expander (22), a secondary compressor (23), a secondary cooler (24), an intermediate cooler (25), a low-pressure buffer tank (26), a circulating cooling water splitter valve (27), a refrigeration cycle gas-liquid separator throttle valve (28), a reflux valve (29), a heat exchanger (31), a pre-buffer tank (32), a heat exchanger (33), a low-pressure gas-liquid separator (34), a primary pump (35), a low-pressure separator (36), a booster (37), a gas-liquid separator (37), a jet separator (38), and a jet separator (38), the low-pressure buffer tank air supplementing valve (41), the humidity-adjusting heat exchanger bypass valve (42), the low-pressure buffer tank exhaust valve (43), the humidity-adjusting heat exchanger (44), the humidity-adjusting heat exchanger air inlet valve (45), the residual Leng Huanre device (50), the heater (51), the steam turbine (56), the generator (57), the power generation grid-connected device (58), the main cooling box (60), the medium-pressure expansion machine cooling box (61), the low-pressure expansion machine cooling box (62), the pneumatic compressor cooling box (63) and the power generation circulation cooling box (66).
Fig. 2 is a schematic view of temperature entropy of refrigeration cycle in the process flow, and nodes marked in the figure are respectively: the device comprises a switching device, a liquid level (102) of an exhaust valve of the switching device, a refrigerating cycle gas-liquid separator, a refrigerating cycle low-temperature pump outlet (104), a saturated liquid point (105), a refrigerating cycle gas-liquid separator exhaust port (106), a low-temperature fan outlet (107), a gas-liquid mixer gas inlet (108), assumed pneumatic intracavity wet saturated steam (109), actual pneumatic intracavity wet saturated steam (110), a medium-pressure expander inlet (111), a medium-pressure expander outlet (112), a low-pressure buffer tank air inlet and outlet (113), an upper cylinder air inlet and a lower cylinder air inlet (114) of a pneumatic compressor before compression, a supercharging gas outlet humidity-regulating heat exchanger (115), a reflux valve back (118), a refrigerating cycle gas-liquid separator air inlet (119), a secondary cooler outlet (121), a low-pressure expander inlet (122), a low-pressure expander outlet (123), a subcooler outlet (124) and a primary compressor inlet (125).
Fig. 3 is a schematic structural diagram of a pneumatic compressor, and the devices and the components of the parts marked in the drawing are respectively: the air inlet and outlet device comprises an upper cylinder air inlet pipe (201), a lower cylinder air inlet pipe (202), an upper cylinder air outlet pipe (203), a lower cylinder air outlet pipe (204), an upper cylinder (205), a lower cylinder (206), an upper cylinder pneumatic cavity (207), a lower cylinder pneumatic cavity (208), an upper cylinder pneumatic cavity air inlet and outlet pipe (209), a lower cylinder pneumatic cavity air inlet and outlet pipe (210), a switching device air inlet pipe (211), a switching device air outlet pipe (212), an upper cylinder piston (213), a lower cylinder piston (214), a buffer cushion (215), a piston guide wheel and air seal assembly (216), a central piston rod air seal (217), an intermediate baffle (218), a pneumatic compressor shell (220), a hollow piston rod (221) and a switching device (12).
Five embodiments
The specific embodiments are described by taking propane (R290) as the power generation cycle working medium and liquid air (air) as the refrigeration cycle working medium as examples with reference to the technical scheme and the attached drawings in the invention.
In fig. 1 and fig. 2, the external liquid air is sent into an adiabatic low-temperature liquid storage tank 01, and when the device needs to be started, the external liquid air is sent to a refrigeration cycle gas-liquid separator 03 through a low-temperature liquid delivery pump 02, and part of cold energy is consumed for the needs of precooling and supercooling of the device; during normal operation of the device, the liquid in the heat-insulating low-temperature liquid storage tank 01 is only used for supplementing the conditions of leakage of the device, interruption of operation, cold supplementation and the like; the external refrigerant-propane liquid is fed to the low pressure gas-liquid separator 34 of the power generation cycle for storage, and is recycled during normal operation of the unit, only to be replenished when there is a leak in the unit.
In fig. 1 and fig. 2, the refrigeration cycle is composed of a pneumatic compression subsystem, a refrigeration capacity gain circulation subsystem and a low-pressure cold-supplementing circulation subsystem, and in fig. 2, the three circulation subsystems are respectively positioned in the middle of a saturated steam zone (crossing a supercooled liquid zone, a wet saturated steam zone and a superheated gas zone) wrapped by a saturated liquid curve and a saturated gas curve, and are positioned at the upper right and lower right; the pneumatic compression subsystem mainly comprises a refrigeration cycle gas-liquid separator 03, a subcooler 04, a refrigeration cycle low-temperature pump 05, a low-temperature fan 07, a medium-pressure buffer tank 08, a pneumatic compressor 11, a switching device 12, a gas-liquid mixer 18, a low-pressure buffer tank 26, a humidifying heat exchanger 44 and related valves, the pneumatic compressor is used as a core, low-temperature liquid is mixed with superheated gas with the same pressure to compress a low-pressure gas working medium generated by the refrigeration cycle gain circulation subsystem, the low-temperature liquid is mixed with the superheated gas serving as a heat source to become wet saturated steam, the volume is continuously increased, the constant temperature and constant pressure expansion is performed, work is performed on a compression cavity and heat energy dissipated by the compressed gas is absorbed, part of enthalpy value of the wet saturated steam is converted into work, the humidity is not up to 109 points of figure 2, but up to 110 points, the wet saturated steam is subjected to gas-liquid separation, the liquid is subjected to supercharging circulation by the refrigeration cycle low-temperature pump 05 after being subjected to cooling, and the gas is subjected to supercharging circulation by the low-temperature fan 07. The cold energy gain circulation subsystem mainly comprises a medium-pressure expander 22, a low-pressure buffer tank 26, a pneumatic compressor body 11, a heat booster 31, a pre-machine buffer tank 32, a refrigeration heat exchanger 33 and related valves, and generates cold energy through heat exchange after expansion due to pressure potential energy generated by the pneumatic compression subsystem and low-grade heat energy brought by heat exchange. The low-pressure cold-supplementing circulation subsystem mainly comprises a low-pressure expansion machine 19, a first-stage compressor 20, a first-stage cooler 21, a medium-pressure expansion machine 22, a second-stage compressor 23, a second-stage cooler 24, an intercooler 25, a subcooler 04 and related valves, the low-pressure gas is compressed and expanded to generate cold energy to supplement the pneumatic compression circulation subsystem, and the energy of the low-pressure expansion gas is recovered by the medium-pressure expansion machine 22 and the low-pressure expansion machine 19.
In fig. 1 and fig. 2, the liquid space at the bottom of the refrigeration cycle gas-liquid separator 03 before the establishment of the cycle is higher than the adiabatic low-temperature liquid storage tank 01, the liquid level is high, the supercooling degree is increased, and cavitation during the cyclic pressurization of the refrigeration cycle low-temperature pump 05 can be reduced; after the precooling is completed and the circulation is established, the upper part of the gas-liquid separator 03 of the refrigeration cycle is saturated gas, the middle lower part of the gas-liquid separator is liquid, the liquid is cooled by the subcooler 04, and the proper supercooling degree is maintained from 102 to 103 points in fig. 2.
In fig. 1 and fig. 2, the outlet pressure of the refrigeration cycle cryopump 05 is increased, part of energy output by a motor is converted into heat energy due to pump efficiency, the liquid-air temperature is increased, the motor does work and is converted into liquid-air enthalpy increase, and in fig. 2, the liquid-air enthalpy increases from 103 to 104.
In fig. 1 and fig. 2, medium-pressure low-temperature liquid air sent by the refrigeration cycle low-temperature pump 05 passes through the liquid supply valve 17 of the gas-liquid mixer, is mixed with superheated gas with the same pressure from the bypass valve 42 of the humidifying heat exchanger and the humidifying heat exchanger 44 in the gas-liquid mixer 18, the constant pressure and the temperature increase are changed from supercooled liquid to saturated liquid, namely 105 point of fig. 2, then the constant pressure and the constant temperature and the enthalpy are changed into wet saturated steam, the dryness and the volume are increased, and the wet saturated steam is used as a power source of the pneumatic compressor 11 to 110 point of fig. 2; the other path of the exhaust gas sent by the refrigeration cycle cryopump 05 is mixed with the exhaust gas of the switching device 12 through the reflux valve 29 and returned to the refrigeration cycle gas-liquid separator 03, and is mainly used for buffering and adjusting the humidity of the wet saturated steam entering the refrigeration cycle gas-liquid separator 03 when the load of the refrigeration cycle cryopump 05 changes.
In fig. 1 and fig. 2, saturated gas at the upper part of the refrigeration cycle gas-liquid separator 03 is sucked into the low-temperature fan 07, and the energy consumption of the motor 06 is low due to low air inlet temperature and small compression ratio; the pressurized superheated gas is fed to the intermediate pressure buffer tank 08 to 107 in fig. 2: one path of gas from the medium pressure buffer tank 08 is sent to the low pressure buffer tank 26 through the low pressure buffer tank air compensating valve 41 and is used as a gas source of the cold energy gain circulation subsystem; the other two paths are respectively converged after passing through the humidifying heat exchanger bypass valve 42, the humidifying heat exchanger air inlet valve 45 and the humidifying heat exchanger 44, moderately absorb the heat energy of the compressed gas, and are used for increasing the superheat degree of the medium-pressure superheated gas, so as to be used for adjusting the humidity or enthalpy value of the wet saturated steam entering the pneumatic compressor 11; the superheated gas with increased temperature after mixing enters the gas-liquid mixer 18 as a heat source and is primarily mixed with the supercooled liquid and then enters the pneumatic cavity of the pneumatic compressor 11 through the switching device 12 for complete mixing.
In fig. 1 and 3, the initial states of the pneumatic compressor 11 and the switching device 12 are: the lower cylinder piston 214 in fig. 3 falls to the bottom, the upper cylinder 205 and the upper cylinder pneumatic chamber 207 are emptied, the upper cylinder pneumatic chamber air inlet and outlet pipe 209 on both sides of the switching device 12 are communicated with the switching device air inlet pipe 211, and the lower cylinder pneumatic chamber air inlet and outlet pipe 210 is communicated with the switching device air outlet pipe 212.
In fig. 1, fig. 2 and fig. 3, the exhaust valve 43 of the low-pressure buffer tank is opened, and the gas in the low-pressure buffer tank 26 enters the upper cylinder 205 of the pneumatic compressor 11 through the upper cylinder check valve 09; after full filling, the humidity-regulating heat exchanger bypass valve 42, the humidity-regulating heat exchanger air inlet valve and the liquid supply valve 17 of the gas-liquid mixer are opened, mixed medium-pressure wet saturated steam enters the upper cylinder pneumatic cavity 207 through the switching device air inlet pipe 211, the switching device 12 and the upper cylinder pneumatic cavity air inlet and outlet pipe 209, the volume of the upper cylinder pneumatic cavity 207 is increased, work is done, the upper cylinder piston 213 is pushed to move upwards, medium-pressure gas in the upper cylinder 205 is compressed, the lower cylinder piston 214 synchronously moves upwards while the upper cylinder piston 213 moves upwards, and the heat of the compressed gas, which is dissipated on the cylinder body and the piston, is partially used for doing work by the wet saturated steam in the piston movement process; the upper cylinder check valve 09 is closed, the lower cylinder check valve 10 is opened, and the lower cylinder 206 is charged; after the pressure of the gas compressed by the upper cylinder 205 increases to a pressure corresponding to 115 in fig. 2, the upper cylinder outlet valve 13 opens and stabilizes the pressure, and after passing through the humidity-controlling heat exchanger 44, the temperature decreases to 115 in fig. 2; the superheated gas flowing in the reverse direction of the humidity-controlling heat exchanger rises in temperature, is mixed with the gas passing through the bypass valve 42 of the humidity-controlling heat exchanger to the point 108 of fig. 2, the energy in the gas-liquid mixer 18 increases, the dryness of the medium-pressure wet saturated steam increases, and the amount of liquid required in the gas-liquid mixer 18 decreases to the point 110 of fig. 2 under the condition that the work is not changed.
In fig. 1, fig. 2 and fig. 3, after the upper cylinder 205 moves to the top dead center and the lower cylinder 206 is full, the switching device 12 acts, the upper cylinder pneumatic cavity air inlet and outlet pipe 209 is communicated with the switching device air outlet pipe 212, the lower cylinder pneumatic cavity air inlet and outlet pipe 210 is communicated with the switching device air inlet pipe 211, and the large return valve 29 is opened simultaneously to avoid severe fluctuation of liquid pressure during switching: the exhaust valve 16 of the switching device is opened, the upper cylinder pneumatic cavity 207 is exhausted, the lower cylinder pneumatic cavity 208 is charged, the piston moves downwards as a whole, the lower cylinder one-way valve 10 is closed, and the wet saturated steam absorbs the heat dissipated by the compressed gas on the cylinder body and the piston in the movement process of the piston, and part of the heat is used for acting; the exhaust of the upper cylinder pneumatic cavity 207 is regulated by the switching device exhaust valve 16, and the pressure after the valve is kept stable, namely from 109 to 101 in the figure 2; then mixing the mixture with the working medium from the reflux valve 29, from 118 point, 101 point to 119 point in the figure 2; sending the mixture into a refrigeration cycle gas-liquid separator 03 for gas-liquid separation; after the residual air of the upper cylinder 205 is expanded and depressurized, the upper cylinder inlet one-way valve 09 is opened, the upper cylinder 205 is charged with air, the cold energy temperature of the low-pressure gas absorption cylinder body is reduced, and the temperature is from 113 to 114 in the drawing; after the pressure of the compressed gas in the lower cylinder 206 increases to a pressure corresponding to 115 in fig. 2, the lower cylinder outlet valve 14 opens and stabilizes the pressure, and after passing through the humidity-controlling heat exchanger 44, the temperature decreases to 115 in fig. 2.
In fig. 1, fig. 2, and fig. 3, after the lower cylinder 206 moves to the bottom dead center, the switching device 12 acts, and except for increasing the expansion and depressurization of the residual air of the lower cylinder 206 and the exhaust of the pneumatic cavity 208 of the lower cylinder, other actions are repeated as described in section [ 0021 ]; the pneumatic compressor 11 reciprocates to realize supercharging.
In fig. 3, to increase the efficiency of the pneumatic compressor 11, a piston guide wheel and seal assembly 216, a center piston rod gas seal 217 are employed to reduce friction and leakage losses; adjusting the position of the guide wheels in the piston guide wheel and air seal assembly 216 may be used to position the upper and lower pistons and facilitate air seal gap adjustment.
In fig. 1, 2 and 3, energy of the pneumatic compressor 11 comes from a low-temperature liquid delivery pump 02 (pressure potential energy), a low-temperature fan 07 (containing pressure potential energy and heat energy) and heat energy of compressed gas obtained through heat exchange (including heat energy absorbed by a cylinder and a piston in a pressurizing process and heat energy absorbed by a humidifying heat exchanger 44 after pressurizing), and heat energy of the compressed gas comes from outside of the system for heat exchange.
In fig. 1, fig. 2 and fig. 3, the pressure of the gas discharged from the upper cylinder and the lower cylinder of the pneumatic compressor 11 is kept stable after being regulated by the upper cylinder outlet valve 13 and the lower cylinder outlet valve 14, and the gas enters the heater 31 through the humidity-regulating heat exchanger 44 and the pre-machine buffer tank 32 from the point 115 to the point 111 in fig. 2; the medium-pressure superheated gas with temperature and enthalpy increased enters a medium-pressure expander 22 to expand and do work to drive a secondary compressor 23 to work from 111 point to 112 point in the attached figure 2; the low-pressure gas with reduced pressure, temperature and enthalpy after expansion is output through the refrigeration heat exchanger 33, from 112 to 113 in the attached figure 2; the low-pressure gas with temperature increase and enthalpy increase enters the low-pressure buffer tank 26, and enters the upper cylinder and the lower cylinder of the pneumatic compressor 11 through the low-pressure buffer tank exhaust valve 43, the upper cylinder one-way valve 09 or the lower cylinder one-way valve 10, so as to absorb the cold energy remained on the cylinder body by the wet saturated steam in the pneumatic cavity and cool down, and the cold energy is from 113 point to 114 point in the attached figure 2; the low-pressure gas is circularly used after being pressurized.
In fig. 1 and 2, the initial gas source and the supplementary gas source of the low-pressure supplementary cooling circulation subsystem in the refrigeration cycle come from the refrigeration cycle gas-liquid separator 03, and are integrated into the exhaust gas of the low-pressure expander 19 through the refrigeration cycle gas-liquid separator throttle valve 28; in normal operation, the refrigeration cycle gas-liquid separator throttle valve 28 is closed at other times than when working fluid is replenished due to leakage or the like.
In fig. 1 and fig. 2, low-pressure air at the inlet of the low-pressure expander 19 in the air compression and expansion cycle expands to do work to drive the first-stage compressor 20 to work, and the point 122 in fig. 2 is combined to the point 123; the pressure of the expanded low-pressure expansion air is close to the atmospheric pressure, and the temperature is lower than the liquid-air temperature in the refrigeration cycle gas-liquid separator 03; the low-pressure expansion air passes through the cooler 4, the liquid air is cooled, the liquid air in the refrigeration cycle gas-liquid separator 03 forms a temperature gradient from the bottom to the liquid level, the temperature corresponds to the temperature of 103 points and 102 points in the attached drawing 2, the gas-liquid separation process is indirectly influenced, and the liquid amount is increased; the low pressure expanded air increases in temperature from point 123 to point 124 of fig. 2; the low-pressure expansion air is sent into the intercooler 25 after leaving the subcooler 4 and used as a reverse flow working medium to cool the forward flow working medium from the secondary cooler 24, the low-pressure expansion air is reheated, the forward flow working medium is combined from the point 121 to the point 122 in the attached figure 2, the temperature of the reverse flow working medium is from the point 124 to the point 125, and the temperature of the point 124 is close to the temperature of the point 102.
In fig. 1 and fig. 2, the reheated low-pressure expansion air is sent to a first-stage compressor 20 for pressurization, the pressurized air is cooled by circulating cooling water through a first-stage cooler 21 and then enters a second-stage compressor 23 for pressurization, the re-pressurized air is cooled by circulating cooling water through a second-stage cooler 24, and the two-stage pressurization and cooling are carried out from 125 to 121 in fig. 2; the cold energy generated by the expansion of the gas is used for starting a compression circulation subsystem in refrigeration cycle, and the cold energy is supplemented by the subcooler 4.
In fig. 1, the height and moderate supercooling of the propane liquid at the bottom of the low-pressure gas-liquid separator 34 of the power generation cycle meet the requirement of the supercooling degree of the liquid at the inlet of the first-stage circulating pump 35, the propane liquid is sent into the medium-pressure gas-liquid separator by the first-stage circulating pump 35, the supercooling amount of the propane liquid is used for condensing the medium-pumping exhaust gas from the steam turbine 56, and the medium-pressure gas-liquid separator 39 is also a hybrid heat exchanger or reheater; the gas at the upper part of the medium-pressure gas-liquid separator 39 enters the ejector 37 through the medium-pressure gas-liquid separator exhaust valve 38 to be used as working fluid, and the gas or gas-liquid mixture at the upper part of the low-pressure gas-liquid separator 34 enters the ejector 37 through the low-pressure gas-liquid separator exhaust valve 36 to be used as drainage working medium; when the low-pressure gas-liquid separator 34 is cooled entirely and the upper part is free of gas, the low-pressure gas-liquid separator exhaust valve 36 is closed, the ejector 37 is only a conveying passage, and the medium-pressure gas-liquid separator exhaust valve 38 is used for throttling: when the whole supercooling upper part of the intermediate-pressure gas-liquid separator 39 is also free of gas, the exhaust valve 38 of the intermediate-pressure gas-liquid separator is closed, and the ejector 37 does not work; the exhaust of the ejector 37 is incorporated into the final exhaust of the turbine 56.
In fig. 1, the height and moderate supercooling of the propane liquid at the bottom of the medium-pressure gas-liquid separator 39 meet the requirement of the supercooling degree of the liquid at the inlet of the secondary circulating pump 40, the temperature of the medium-pressure propane liquid after the pressurization of the secondary circulating pump 40 is lower than that of the inlet water of the circulating cooling water, the heat exchange is carried out by the residual Leng Huanre device 50, the temperature of the circulating cooling water is reduced, the medium-pressure propane liquid is heated up and enters the heater 51 to absorb the heat of an external heat source, then the temperature is continuously raised, evaporated and overheated, and the enthalpy-increased medium-pressure propane gas is sent to the turbine 56 to expand and do work to drive the generator 57 to work, and the electric energy is sent out by the power generation grid-connected device 58; the final exhaust gas is mixed with the exhaust gas of the ejector 37, enters the refrigeration heat exchanger 33 to finish cooling, condensation and supercooling, and is sent into the low-pressure gas-liquid separator 34; the temperature of the medium-pressure exhaust gas is reduced in the heat booster 31, and the medium-pressure exhaust gas enters the medium-pressure gas-liquid separator 39 for further condensation and gas-liquid separation after condensation.
In fig. 1, after the inlet water temperature of the circulating cooling water is reduced, the circulating cooling water is divided into two paths, one path is sent to the secondary cooler 24, the other path is sent to the primary cooler 21 through the circulating cooling water diverter valve 27, and backwaters after exiting the coolers are converged and returned to an external circulating cooling system.
In the attached figures 1 and 2, the air compression in the low-pressure cold-supplementing circulation subsystem reduces the air inlet and outlet temperatures of the compressor by means of inter-stage cooling, circulating cooling water temperature reduction and the like, so that the compression coefficient of the air is reduced, and the compression energy consumption is reduced; the energy of the compressor is from the expander, and the energy of the expander is mainly from low-grade heat energy (low-grade heat energy below 40 ℃) which is not calculated in general.
In fig. 1 and fig. 2, the quality (temperature is low) of the refrigerating capacity of the low-pressure cold-compensating circulation subsystem in the refrigerating cycle is higher than that of the cold capacity gain circulation subsystem, the total refrigerating capacity is smaller than that of the cold capacity gain circulation subsystem, the refrigerating capacity of the low-pressure cold-compensating circulation subsystem is transmitted to the cold capacity gain circulation low-pressure cold-compensating circulation subsystem through the pneumatic compression circulation subsystem and amplified, and the total output refrigerating capacity of the refrigerating cycle is increased.
In fig. 1 and fig. 2, the low-grade heat energy which is basically ignored is utilized for the gas compression of the refrigeration gain cycle in the refrigeration cycle, and the high-grade energy consumption is low; the pneumatic compressor 11 has less intermediate links and higher energy conversion efficiency; the wet saturated steam in the pneumatic cavity of the pneumatic compressor 11 can absorb heat generated by compressed gas, so that the temperature rise of the pneumatic compressor 11 is controlled, the temperature rise of the compressed gas can be slowed down, the heat release and entropy are reduced in the process of compressing the gas, and the compression energy consumption is reduced; the temperature of the compressed gas entering the upper cylinder and the lower cylinder is low, the compression coefficient is small, and the compression energy consumption is low; the wet saturated steam in the pneumatic cavity is beneficial to self-lubrication and leakage reduction, and can improve the compression efficiency; the temperature of the compressed gas is low, the temperature rise is restrained, and the compressed gas has a larger compression ratio.
In fig. 1 and 3, the pneumatic compressor 11 adopts a vertical structure, is simple to manufacture and convenient to maintain, and can be enlarged; the running speed of the piston of the pneumatic compressor 11 is lower than that of a hydraulic compressor and a common gas piston compressor, the running is relatively stable, and the impact on the system is small; the same medium is arranged on two sides of the piston of the pneumatic compressor 11, so that the problem of working medium loss caused by leakage is avoided.
In fig. 1 and 2, the opening of the exhaust valve 16 of the switching device is mainly adjusted, the exhaust amount of the switching device 12 is adjusted, the movement speed of the piston is controlled, and the compression capacity of the pneumatic compressor 11 is dynamically adjusted within a certain range.
In fig. 1 and fig. 2, the refrigerating capacity of the refrigerating cycle or the power generation capacity of the whole device can be adjusted within a certain range, the adjustment is mainly realized by adjusting the capacities of the cryogenic liquid delivery pump 02 and the cryogenic fan 07, namely the flow and the outlet pressure, and the adjustment of the humidity of the wet saturated steam entering the pneumatic cavity of the pneumatic compressor 11 can be used as an auxiliary means.
In fig. 1, the main cooling box 60, the high-pressure expansion machine cooling box 61, the low-pressure expansion machine cooling box 62, the pneumatic compressor cooling box 63 and the power generation circulation cooling box 66 are relatively independent, so that the maintenance is convenient; adopting a box-type heat insulation structure, and filling heat insulation materials such as pearlitic sand and the like; the cold box is filled with inert gas to keep positive pressure, so that moisture is prevented from penetrating into the cold box to influence the heat preservation effect; the heat-insulating low-temperature liquid storage tank 01 is heat-insulating and preserving by filling pearlitic heat insulating materials, vacuum heat insulation, filling inert gases and the like; the low-temperature liquid pipeline outside the cold box adopts a vacuum heat-insulating pipe; the low-temperature liquid delivery pump 02 adopts a long shaft to connect a pump body with a motor and the pump body is provided with an insulation box; the device or the part of the power generation cycle which is lower than the ambient temperature can also adopt a mode of wrapping heat insulation materials to replace a cold box for heat preservation.
In fig. 1,2 and 3, the power required for the up-and-down movement of the pneumatic compressor is different when the up-and-down cylinder is switched due to the dead weight of the piston, and the air intake and exhaust amount or pressure of the switching device 12 is properly adjusted accordingly.
In fig. 1 and fig. 2, the inlet temperature of the steam turbine 56 is higher than the temperature of the circulating cooling water, the outlet pressure of the secondary circulating pump 40 is increased correspondingly as the temperature of the external heat source is higher, more heat energy can be obtained through the evaporation of liquid propane, and the power generation capacity is increased; the middle exhaust temperature and the final exhaust temperature of the steam turbine 56 have obvious step difference, the middle exhaust temperature is lower than the ambient temperature and higher than 0 ℃, and the final exhaust temperature is higher than the boiling point of propane by-42.1 ℃ and lower than 0 ℃; the amount and pressure of the medium-pressure exhaust gas are appropriate, and the condensation and liquefaction should be completed through the heat booster 31 and the medium-pressure gas-liquid separator 39.
Claims (10)
1. A refrigeration and power generation device using a pneumatic compressor, the device comprising: an adiabatic cryogenic liquid storage tank (01), a cryogenic liquid delivery pump (02), a refrigeration cycle gas-liquid separator (03), a subcooler (04), a refrigeration cycle cryogenic pump (05), a motor (06), a cryogenic fan (07), a medium-pressure buffer tank (08), an upper cylinder one-way valve (09), a lower cylinder one-way valve (10), a pneumatic compressor (11), a switching device (12), an upper cylinder outlet valve (13), a lower cylinder outlet valve (14), a switching device exhaust valve (16), a gas-liquid mixer liquid supply valve (17), a gas-liquid mixer (18), a low-pressure expander (19), a primary compressor (20), a primary cooler (21), a medium-pressure expander (22), a secondary compressor (23), a secondary cooler (24), an intermediate cooler (25), a low-pressure buffer tank (26), a circulating cooling water splitter valve (27), a refrigeration cycle gas-liquid separator throttle valve (28), a reflux valve (29), a heat exchanger (31), a pre-buffer tank (32), a heat exchanger (33), a low-pressure gas-liquid separator (34), a primary pump (35), a low-pressure separator (36), a booster (37), a gas-liquid separator (37), a jet separator (38), and a jet separator (38), A low-pressure buffer tank air supplementing valve (41), a humidity-adjusting heat exchanger bypass valve (42), a low-pressure buffer tank exhaust valve (43), a humidity-adjusting heat exchanger (44), a humidity-adjusting heat exchanger air inlet valve (45), a residual Leng Huanre device (50), a heater (51), a steam turbine (56), a generator (57), a power generation grid-connected device (58), a main cold box (60), a medium-pressure expansion machine cold box (61), a low-pressure expansion machine cold box (62), a pneumatic compressor cold box (63) and a power generation circulation cold box (66),
The heat-insulating low-temperature liquid storage tank (01) is communicated with the refrigeration cycle gas-liquid separator (03) through the low-temperature liquid delivery pump (02), the upper part of the refrigeration cycle gas-liquid separator (03) is communicated with the outlet of the low-pressure expansion machine (19) and the subcooler (04) through the throttle valve (28) of the refrigeration cycle gas-liquid separator, the bottom of the refrigeration cycle gas-liquid separator (03) is communicated with the liquid supply valve (17) of the gas-liquid mixer and the liquid inlet of the gas-liquid mixer (18) through the refrigeration cycle low-temperature pump (05) in sequence, the other path of the outlet of the refrigeration cycle low-temperature pump (05) is respectively connected with the exhaust valve (16) of the switching device and the air inlet of the refrigeration cycle gas-liquid separator (03) through the reflux valve (29), the air outlet of the refrigeration cycle gas-liquid separator (03) is communicated with the medium-pressure buffer tank (08) through the low-temperature fan (07), the low-temperature fan (07) is connected with the motor (06) in a shaft way, the subcooler (04) is fixed inside the refrigeration cycle gas-liquid separator (03),
The outlet of the medium pressure buffer tank (08) is divided into three paths, one path is connected with the low pressure buffer tank (26) through a low pressure buffer tank air compensating valve (41), the second path is connected with a humidity-adjusting heat exchanger (44) through a humidity-adjusting heat exchanger air inlet valve (45), the third path is communicated with the outlet of the humidity-adjusting heat exchanger (44) through a humidity-adjusting heat exchanger bypass valve (42) and then is communicated with the air inlet of the gas-liquid mixer (18),
An air inlet of the switching device (12) is communicated with an outlet of the gas-liquid mixer (18), an air outlet of the switching device (12) is connected with an air outlet valve (16) of the switching device, two air inlet and air outlet of the switching device (12) are communicated with a pneumatic cavity in the middle of the pneumatic compressor (11),
The upper and lower cylinder air outlets of the pneumatic compressor (11) are respectively connected with the front buffer tank (32) through the humidity-adjusting heat exchanger (44) after passing through the upper cylinder outlet valve (13) and the lower cylinder outlet valve (14), the upper and lower cylinder air inlets of the pneumatic compressor (11) are respectively connected with the air outlet of the low-pressure buffer tank (26) through the upper cylinder one-way valve (09) and the lower cylinder one-way valve (10) after passing through the low-pressure buffer tank air outlet valve (43),
An air inlet of the medium-pressure expansion machine (22) is communicated with an air outlet of a buffer tank (32) in front of the machine through a heat booster (31), the air outlet of the medium-pressure expansion machine (22) is connected with a low-pressure buffer tank (26) through a refrigeration heat exchanger (33), the medium-pressure expansion machine (22) is connected with a shaft of a secondary compressor (23),
The outlet of the low-pressure expansion machine (19) is connected with the outlet of a throttle valve (28) of a gas-liquid separator of the refrigeration cycle, and then sequentially passes through a cooler (04), an intercooler (25), a primary compressor (20), a primary cooler (21), a secondary compressor (23), a secondary cooler (24) and the intercooler (25) to be connected with the inlet of the low-pressure expansion machine (19), the low-pressure expansion machine (19) is connected with the primary compressor (20) through a shaft,
The turbine (56) is connected with the generator (57) through a shaft, the generator (57) is connected with a power generation grid-connected device (58) through a wire, the last-stage exhaust port of the turbine (56) is connected with the low-pressure gas-liquid separator (34) through the refrigerating heat exchanger (33) and the outlet of the ejector (37), the exhaust port of the turbine (56) is connected with the medium-pressure gas-liquid separator (39) through the heat booster (31),
The low-pressure gas-liquid separator (34) is connected with an externally input refrigerant pipeline, a liquid outlet at the bottom of the low-pressure gas-liquid separator (34) is connected with the medium-pressure gas-liquid separator (39) through a primary circulating pump (35), an exhaust port at the upper part of the low-pressure gas-liquid separator (34) is connected with a drainage port of the ejector (37) through an exhaust valve (36) of the low-pressure gas-liquid separator,
The upper exhaust port of the medium-pressure gas-liquid separator (39) is connected with the working fluid port of the ejector (37) through the exhaust valve (38) of the medium-pressure gas-liquid separator, the bottom liquid outlet of the medium-pressure gas-liquid separator (39) is connected with the air inlet of the steam turbine (56) through the secondary circulating pump (40) sequentially through the residual heat exchanger (50) and the heater (51),
The circulating cooling water inlet pipeline is divided into two paths after passing through the circulating water channel of the residual cooling heat exchanger (50), one path is communicated with the circulating cooling water return pipe after passing through the circulating water channel of the secondary cooler (24), the other path is communicated with the circulating cooling water return pipe after passing through the circulating cooling water flow dividing valve (27) and the circulating water channel of the primary cooler (21) in sequence, the external heat source is connected with the heat source channel of the heater (51),
The main cooling box (60), the medium-pressure expansion machine cooling box (61), the low-pressure expansion machine cooling box (62), the pneumatic compressor cooling box (63) and the power generation circulation cooling box (66) are connected through box walls,
A refrigeration cycle gas-liquid separator (03) a refrigeration cycle cryopump (05) a low-temperature fan (07), a refrigeration cycle intercooler (25) a throttle valve (28) of a gas-liquid separator of the refrigeration cycle the reflux valve (29) is fixed in the main cooling box (60),
The medium-pressure expander (22) is fixed in the medium-pressure expander cold box (61), the low-pressure expander (19) is fixed in the low-pressure expander cold box (62),
The medium pressure buffer tank (08), the upper cylinder one-way valve (09), the lower cylinder one-way valve (10), the pneumatic compressor (11), the switching device (12), the upper cylinder outlet valve (13), the lower cylinder outlet valve (14), the switching device exhaust valve (16), the gas-liquid mixer liquid supply valve (17), the gas-liquid mixer (18), the low pressure buffer tank (26), the pre-machine buffer tank (32), the low pressure buffer tank air supplementing valve (41), the humidifying heat exchanger bypass valve (42), the low pressure buffer tank exhaust valve (43), the humidifying heat exchanger (44) and the humidifying heat exchanger air inlet valve (45) are fixed in the pneumatic compressor cold box (63),
The heat booster (31), the refrigeration heat exchanger (33), the low-pressure gas-liquid separator (34), the primary circulating pump (35), the low-pressure gas-liquid separator exhaust valve (36), the ejector (37), the medium-pressure gas-liquid separator exhaust valve (38), the medium-pressure gas-liquid separator (39) and the secondary circulating pump (40) are fixed in the power generation circulating cold box (66).
2.A refrigeration and power generation apparatus using a pneumatic compressor as set forth in claim 1, wherein the pneumatic compressor includes: an upper cylinder air inlet pipe (201), a lower cylinder air inlet pipe (202), an upper cylinder air outlet pipe (203), a lower cylinder air outlet pipe (204), an upper cylinder (205), a lower cylinder (206), an upper cylinder pneumatic cavity (207), a lower cylinder pneumatic cavity (208), an upper cylinder pneumatic cavity air inlet and outlet pipe (209), a lower cylinder pneumatic cavity air inlet and outlet pipe (210), a switching device air inlet pipe (211), a switching device air outlet pipe (212), an upper cylinder piston (213), a lower cylinder piston (214), a buffer cushion (215), a piston guide wheel and seal assembly (216), a central piston rod air seal (217), a middle partition plate (218), a pneumatic compressor shell (220), a hollow piston rod (221) and a switching device (12),
An upper cylinder air inlet pipe (201), a lower cylinder air inlet pipe (202), an upper cylinder air outlet pipe (203), a lower cylinder air outlet pipe (204), an upper cylinder (205), a lower cylinder (206), an upper cylinder pneumatic cavity (207), a lower cylinder pneumatic cavity (208), an upper cylinder pneumatic cavity air inlet and outlet pipe (209), a lower cylinder pneumatic cavity air inlet and outlet pipe (210), a middle partition plate (218) and a buffer cushion (215) are connected with a pneumatic compressor shell (220),
An upper cylinder air inlet pipe (201) is communicated with an upper cylinder (205), a lower cylinder air inlet pipe (202) is communicated with a lower cylinder (206), an upper cylinder pneumatic cavity (207) is communicated with an upper cylinder pneumatic cavity air inlet and outlet pipe (209), a lower cylinder pneumatic cavity (208) is communicated with a lower cylinder pneumatic cavity air inlet and outlet pipe (210),
An upper cylinder pneumatic cavity air inlet and outlet pipe (209), a lower cylinder pneumatic cavity air inlet and outlet pipe (210), a switching device air inlet pipe (211) and a switching device air outlet pipe (212) are communicated with the switching device (12),
The upper cylinder piston (213) and the lower cylinder piston (214) are connected with a hollow piston rod (221), the upper cylinder piston (213) and the lower cylinder piston (214) are connected with a piston guide wheel and an air seal assembly (216), an intermediate baffle (218) is connected with a central piston rod air seal (217), the upper cylinder piston (213) and the lower cylinder piston (214) are arranged in a pneumatic compressor shell (220) and are connected with the shell through the guide wheel,
The upper cylinder pneumatic cavity (207), the lower cylinder pneumatic cavity (208) are isolated and connected through a middle partition plate (218), a central piston rod air seal (217), a piston rod (221) and a pneumatic compressor shell (220), the upper cylinder (205) and the upper cylinder pneumatic cavity (207) are isolated and connected through an upper cylinder piston (213) and a piston guide wheel and air seal assembly (216), and the pneumatic compressor shell (220), and the lower cylinder (206) and the lower cylinder pneumatic cavity (208) are isolated and connected through a lower cylinder piston (214), a piston guide wheel and air seal assembly (216) and the pneumatic compressor shell (220).
3. A refrigeration and power generation apparatus using a pneumatic compressor as set forth in claim 1, wherein: the refrigeration cycle working medium adopts single-component and multi-element natural working medium existing in the air.
4. A refrigeration and power generation apparatus using a pneumatic compressor as set forth in claim 1, wherein: the power generation circulating refrigerant working medium adopts a single-component and multi-component synthesized natural and quasi-natural working medium with low boiling point temperature.
5. A refrigeration-power generating apparatus using a pneumatic compressor as recited in claim 1, wherein the refrigeration cycle includes: the pneumatic compression circulation subsystem provides energy for the cold quantity gain circulation subsystem, the cold quantity gain circulation subsystem outputs cold quantity and provides energy for the low-pressure cold supplement circulation subsystem, and the low-pressure cold supplement circulation subsystem generates cold quantity to supplement the pneumatic compression circulation subsystem.
6. A refrigeration-power-generation device using a pneumatic compressor as claimed in claim 1, wherein the refrigeration cycle is operated for condensing the working medium in the refrigeration and low-grade thermal power generation cycles.
7. The refrigeration and power generation device using a pneumatic compressor according to claim 1, wherein the low-grade heat energy of 40 ℃ or less is used for refrigeration and the low-grade heat energy of 80 ℃ or less is used for power generation.
8. The refrigeration and power generation device using a pneumatic compressor according to claim 1, wherein the final stage exhaust gas condensation, the middle extraction exhaust gas condensation and the cooling of circulating cooling water of a turbine in the power generation cycle are performed, and the cooling capacity is repeatedly used in a stepwise manner.
9. A refrigeration and power generation device using a pneumatic compressor as claimed in claim 1 or 2, wherein the pneumatic compressor (11) uses the heat energy of the compressed gas to make the wet saturated vapor after the gas and liquid are mixed work to compress the low-pressure gas working medium.
10. A refrigeration and power generation device using a pneumatic compressor according to claim 1 or 2, wherein the pneumatic compressor (11) is of a vertical, double-cylinder, double-pneumatic-cavity structure.
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