WO2017137012A1 - 对压气能动力系统及动力方法 - Google Patents

对压气能动力系统及动力方法 Download PDF

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Publication number
WO2017137012A1
WO2017137012A1 PCT/CN2017/073459 CN2017073459W WO2017137012A1 WO 2017137012 A1 WO2017137012 A1 WO 2017137012A1 CN 2017073459 W CN2017073459 W CN 2017073459W WO 2017137012 A1 WO2017137012 A1 WO 2017137012A1
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WO
WIPO (PCT)
Prior art keywords
gas
pair
cylinder
piston
inner cavity
Prior art date
Application number
PCT/CN2017/073459
Other languages
English (en)
French (fr)
Inventor
陈威伦
陈泰伦
李慧勤
陈迪夫
Original Assignee
北京艾派可科技有限公司
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by 北京艾派可科技有限公司 filed Critical 北京艾派可科技有限公司
Priority to CN201780011298.8A priority Critical patent/CN108779672B/zh
Priority to EP17749903.5A priority patent/EP3415713A4/en
Publication of WO2017137012A1 publication Critical patent/WO2017137012A1/zh
Priority to US16/103,731 priority patent/US10738613B2/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C1/00—Pressure vessels, e.g. gas cylinder, gas tank, replaceable cartridge
    • F17C1/007—Underground or underwater storage
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B23/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01B23/10—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
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B17/00—Reciprocating-piston machines or engines characterised by use of uniflow principle
    • F01B17/02—Engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B29/00—Machines or engines with pertinent characteristics other than those provided for in preceding main groups
    • F01B29/08—Reciprocating-piston machines or engines not otherwise provided for
    • F01B29/10—Engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/14—Gas-turbine plants having means for storing energy, e.g. for meeting peak loads
    • F02C6/16—Gas-turbine plants having means for storing energy, e.g. for meeting peak loads for storing compressed air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B13/00—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates
    • F03B13/12—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates characterised by using wave or tide energy
    • F03B13/14—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates characterised by using wave or tide energy using wave energy
    • F03B13/16—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates characterised by using wave or tide energy using wave energy using the relative movement between a wave-operated member, i.e. a "wom" and another member, i.e. a reaction member or "rem"
    • F03B13/18—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates characterised by using wave or tide energy using wave energy using the relative movement between a wave-operated member, i.e. a "wom" and another member, i.e. a reaction member or "rem" where the other member, i.e. rem is fixed, at least at one point, with respect to the sea bed or shore
    • F03B13/1805—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates characterised by using wave or tide energy using wave energy using the relative movement between a wave-operated member, i.e. a "wom" and another member, i.e. a reaction member or "rem" where the other member, i.e. rem is fixed, at least at one point, with respect to the sea bed or shore and the wom is hinged to the rem
    • F03B13/181—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates characterised by using wave or tide energy using wave energy using the relative movement between a wave-operated member, i.e. a "wom" and another member, i.e. a reaction member or "rem" where the other member, i.e. rem is fixed, at least at one point, with respect to the sea bed or shore and the wom is hinged to the rem for limited rotation
    • F03B13/1815—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates characterised by using wave or tide energy using wave energy using the relative movement between a wave-operated member, i.e. a "wom" and another member, i.e. a reaction member or "rem" where the other member, i.e. rem is fixed, at least at one point, with respect to the sea bed or shore and the wom is hinged to the rem for limited rotation with an up-and-down movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B17/00—Other machines or engines
    • F03B17/06—Other machines or engines using liquid flow with predominantly kinetic energy conversion, e.g. of swinging-flap type, "run-of-river", "ultra-low head"
    • F03B17/062—Other machines or engines using liquid flow with predominantly kinetic energy conversion, e.g. of swinging-flap type, "run-of-river", "ultra-low head" with rotation axis substantially at right angle to flow direction
    • F03B17/063—Other machines or engines using liquid flow with predominantly kinetic energy conversion, e.g. of swinging-flap type, "run-of-river", "ultra-low head" with rotation axis substantially at right angle to flow direction the flow engaging parts having no movement relative to the rotor during its rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D9/00—Adaptations of wind motors for special use; Combinations of wind motors with apparatus driven thereby; Wind motors specially adapted for installation in particular locations
    • F03D9/008—Adaptations of wind motors for special use; Combinations of wind motors with apparatus driven thereby; Wind motors specially adapted for installation in particular locations the wind motor being combined with water energy converters, e.g. a water turbine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D9/00—Adaptations of wind motors for special use; Combinations of wind motors with apparatus driven thereby; Wind motors specially adapted for installation in particular locations
    • F03D9/10—Combinations of wind motors with apparatus storing energy
    • F03D9/17—Combinations of wind motors with apparatus storing energy storing energy in pressurised fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D9/00—Adaptations of wind motors for special use; Combinations of wind motors with apparatus driven thereby; Wind motors specially adapted for installation in particular locations
    • F03D9/20—Wind motors characterised by the driven apparatus
    • F03D9/28—Wind motors characterised by the driven apparatus the apparatus being a pump or a compressor
    • 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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by wind motors
    • 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
    • F04B41/00—Pumping installations or systems specially adapted for elastic fluids
    • F04B41/02—Pumping installations or systems specially adapted for elastic fluids having reservoirs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C13/00—Details of vessels or of the filling or discharging of vessels
    • F17C13/02—Special adaptations of indicating, measuring, or monitoring equipment
    • F17C13/025—Special adaptations of indicating, measuring, or monitoring equipment having the pressure as the parameter
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C13/00—Details of vessels or of the filling or discharging of vessels
    • F17C13/12—Arrangements or mounting of devices for preventing or minimising the effect of explosion ; Other safety measures
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D16/00—Control of fluid pressure
    • G05D16/028—Controlling a pressure difference
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D16/00—Control of fluid pressure
    • G05D16/04—Control of fluid pressure without auxiliary power
    • G05D16/10—Control of fluid pressure without auxiliary power the sensing element being a piston or plunger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D1/00—Wind motors with rotation axis substantially parallel to the air flow entering the rotor 
    • F03D1/02—Wind motors with rotation axis substantially parallel to the air flow entering the rotor  having a plurality of rotors
    • F03D1/025—Wind motors with rotation axis substantially parallel to the air flow entering the rotor  having a plurality of rotors coaxially arranged
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D1/00—Wind motors with rotation axis substantially parallel to the air flow entering the rotor 
    • F03D1/06—Rotors
    • F03D1/065—Rotors characterised by their construction elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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    • F05B2220/708—Photoelectric means, i.e. photovoltaic or solar cells
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
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    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2221/00—Handled fluid, in particular type of fluid
    • F17C2221/03—Mixtures
    • F17C2221/031—Air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2223/00—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel
    • F17C2223/01—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel characterised by the phase
    • F17C2223/0107—Single phase
    • F17C2223/0123—Single phase gaseous, e.g. CNG, GNC
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2223/00—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel
    • F17C2223/03—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel characterised by the pressure level
    • F17C2223/033—Small pressure, e.g. for liquefied gas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2223/00—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel
    • F17C2223/03—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel characterised by the pressure level
    • F17C2223/035—High pressure (>10 bar)
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2223/00—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel
    • F17C2223/03—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel characterised by the pressure level
    • F17C2223/036—Very high pressure (>80 bar)
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2223/00—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel
    • F17C2223/03—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel characterised by the pressure level
    • F17C2223/038—Subatmospheric pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2225/00—Handled fluid after transfer, i.e. state of fluid after transfer from the vessel
    • F17C2225/01—Handled fluid after transfer, i.e. state of fluid after transfer from the vessel characterised by the phase
    • F17C2225/0107—Single phase
    • F17C2225/0123—Single phase gaseous, e.g. CNG, GNC
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2225/00—Handled fluid after transfer, i.e. state of fluid after transfer from the vessel
    • F17C2225/03—Handled fluid after transfer, i.e. state of fluid after transfer from the vessel characterised by the pressure level
    • F17C2225/033—Small pressure, e.g. for liquefied gas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2225/00—Handled fluid after transfer, i.e. state of fluid after transfer from the vessel
    • F17C2225/03—Handled fluid after transfer, i.e. state of fluid after transfer from the vessel characterised by the pressure level
    • F17C2225/035—High pressure, i.e. between 10 and 80 bars
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2225/00—Handled fluid after transfer, i.e. state of fluid after transfer from the vessel
    • F17C2225/03—Handled fluid after transfer, i.e. state of fluid after transfer from the vessel characterised by the pressure level
    • F17C2225/036—Very high pressure, i.e. above 80 bars
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2225/00—Handled fluid after transfer, i.e. state of fluid after transfer from the vessel
    • F17C2225/03—Handled fluid after transfer, i.e. state of fluid after transfer from the vessel characterised by the pressure level
    • F17C2225/038—Subatmospheric pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2227/00—Transfer of fluids, i.e. method or means for transferring the fluid; Heat exchange with the fluid
    • F17C2227/01—Propulsion of the fluid
    • F17C2227/0128—Propulsion of the fluid with pumps or compressors
    • F17C2227/0157—Compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2250/00—Accessories; Control means; Indicating, measuring or monitoring of parameters
    • F17C2250/04—Indicating or measuring of parameters as input values
    • F17C2250/0404—Parameters indicated or measured
    • F17C2250/043—Pressure
    • F17C2250/0434—Pressure difference
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2260/00—Purposes of gas storage and gas handling
    • F17C2260/01—Improving mechanical properties or manufacturing
    • F17C2260/016—Preventing slosh
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2260/00—Purposes of gas storage and gas handling
    • F17C2260/04—Reducing risks and environmental impact
    • F17C2260/042—Reducing risk of explosion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2270/00—Applications
    • F17C2270/01—Applications for fluid transport or storage
    • F17C2270/0102—Applications for fluid transport or storage on or in the water
    • F17C2270/0118—Offshore
    • F17C2270/0121—Platforms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2270/00—Applications
    • F17C2270/01—Applications for fluid transport or storage
    • F17C2270/0142—Applications for fluid transport or storage placed underground
    • F17C2270/0144—Type of cavity
    • F17C2270/0147—Type of cavity by burying vessels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2270/00—Applications
    • F17C2270/05—Applications for industrial use
    • F17C2270/0581—Power plants
    • 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
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/20—Hydro energy
    • 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
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/30—Energy from the sea, e.g. using wave energy or salinity gradient
    • 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
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/727—Offshore wind turbines

Definitions

  • the invention relates to a gas energy power system and a power method, in particular to a gas energy power system and a power method in the field of gas energy application.
  • Another object of the present invention is to provide a method for compressing gas energy, which is used as a basic energy source for a heat-functional circulation system, and converts gas pressure energy into mechanical torque, thereby generating rotational energy to produce mechanical energy to drive power.
  • the device works.
  • the present invention provides a pair of pressurized gas power systems including:
  • a pressurized gas energy storage device having a high pressure storage gas filled with a high pressure gas, the low pressure storage gas being filled with a low pressure gas, and the pair of compressed gas energy storage devices having a pair of compressed gas energy;
  • a gas-energy engine connected to the low-pressure storage gas and the high-pressure storage gas, respectively, wherein the low-pressure gas in the low-pressure storage gas and the high-pressure gas in the high-pressure storage gas respectively flow through the counter-pressure gas engine, Rotating the rotating shaft of the pair of pressurized gas engines;
  • a power unit connected to the rotating shaft of the pair of pressurized air engines, the power unit passing the pair of compressed air Can be driven by the engine.
  • the present invention also provides a method for compressing gas power, comprising the steps of: providing a high pressure storage gas filled with a high pressure gas and a low pressure storage gas filled with a low pressure gas, between the low pressure storage gas and the high pressure storage gas
  • the utility model has the function of compressing air, and releasing the pair of compressed air energy in an isothermal and equal volume thermal cycle to drive the external power device.
  • the beneficial effect of the invention is that the working process of the gas working medium of the gas-energy power system is an isometric isothermal thermal motion process, and the remarkable features are: zero discharge of working medium; high energy conversion efficiency; structure of component operating components Simple; improved the reliability of the pneumatic system; reduced maintenance costs for the operation process.
  • the invention can use traditional, renewable energy sources; energy efficiency, volume, space and time, and the utilization of necessary resources; achieve zero net emissions of non-environmentally friendly substances in the full power cycle; overall cost of construction, operation, and maintenance Lower; the greatest inheritance to the existing power industrial chain and process materials, and the smallest transition in technology.
  • Figure 1 is a schematic view showing the structure of a pressurized gas power system of the present invention.
  • FIG. 2 is a schematic view showing the structure of an alternative embodiment of a pressurized gas energy storage device of the present invention.
  • 3 to 5 are schematic views showing the structure of an alternative embodiment of a pressure-receiving differential rotor regulator valve according to the present invention.
  • 6 to 8 are schematic views showing the structure of another alternative embodiment of the pressure gas differential rotor regulator valve of the present invention.
  • Figure 9 is a block diagram showing an alternative embodiment of a compression gas engine (i.e., a triangular rotary piston air compressor or engine) of the present invention.
  • a compression gas engine i.e., a triangular rotary piston air compressor or engine
  • Figure 10 is a block diagram showing another alternative embodiment of a pressurized gas engine (i.e., a triangular rotary piston air press or engine) of the present invention.
  • a pressurized gas engine i.e., a triangular rotary piston air press or engine
  • Fig. 11 is a structural schematic view showing the triangular rotary piston of the triangular rotary piston engine of the embodiment shown in Fig. 10 at different rotational positions.
  • Figure 12 is a block diagram showing a further alternative embodiment of a pressurized gas engine (i.e., a rotary cylinder delta piston air compressor or engine) of the present invention.
  • a pressurized gas engine i.e., a rotary cylinder delta piston air compressor or engine
  • Figure 13 is a schematic view showing the structure of the inner cavity of the triangular piston of the present invention.
  • Figure 14 is a schematic view showing the structure of a piston rod (i.e., a first gas delivery piston, a second gas delivery piston or a third gas delivery piston) of the present invention.
  • a piston rod i.e., a first gas delivery piston, a second gas delivery piston or a third gas delivery piston
  • Figure 15 is a view showing the triangular piston of the rotary cylinder delta piston engine of the embodiment shown in Figure 12 at different rotational positions Schematic.
  • Figure 16 is a block diagram showing an alternative embodiment of a pressurized gas engine (i.e., a two arc rotary piston air compressor or engine) of the present invention.
  • a pressurized gas engine i.e., a two arc rotary piston air compressor or engine
  • Figure 17 is a block diagram showing another alternative embodiment of a pressurized gas engine (i.e., a two arc rotary piston air press or engine) of the present invention.
  • a pressurized gas engine i.e., a two arc rotary piston air press or engine
  • FIGS. 18 and 19 are structural views of an alternative embodiment in which an electromagnet or a permanent magnet is provided on the two-arc rotary piston air press or engine of Figs. 16 and 17, respectively.
  • Figure 20 is a schematic view showing the structure of a rotor valve mechanism and a gas valve stem of the present invention.
  • Figure 21 is a block diagram showing an alternative embodiment of a compression gas engine (i.e., a three arc rotary piston air compressor or engine) of the present invention.
  • a compression gas engine i.e., a three arc rotary piston air compressor or engine
  • Figure 22 is a block diagram showing an alternative embodiment of a compression gas engine (i.e., a four arc rotary piston air compressor or engine) of the present invention.
  • a compression gas engine i.e., a four arc rotary piston air compressor or engine
  • Figure 23 is a schematic view showing the structure of the two-arc rotor of the two-arc rotary piston engine of the embodiment shown in Figure 16 at different rotational positions.
  • Fig. 24 is a structural schematic view showing the two arc rotors of the two-arc rotary piston air press of the embodiment shown in Fig. 16 at different rotational positions.
  • Figure 25 is an illustration of an application of the present invention to a pressurized gas energy storage system.
  • Figure 26 is an illustration of an application of the present invention to a pressurized air vehicle.
  • Figure 27 is an illustration of an application of the present invention to a pressurized gas energy storage power plant.
  • the present invention provides a pair of compressed air power system including a pair of compressed air energy storage device 1, a pair of gas pressure energy engine 2 and a power device 3, wherein: the pressure gas energy storage device 1 has a high pressure storage gas 11 And the low-pressure storage gas 12, the high-pressure storage gas 11 is filled with a high-pressure gas, the low-pressure storage gas 12 is filled with a low-pressure gas, the pair of compressed gas energy storage device 1 stores a pair of compressed gas energy; for the compressed gas energy engine 2 respectively Connected with the low-pressure storage gas 12 and the high-pressure storage gas 11, a low-pressure gas in the low-pressure storage gas 12 and a high-pressure gas in the high-pressure storage gas 11
  • the body flows through the pair of compressed air energy engines 2 to drive the rotating shaft 21 of the pair of compressed air energy engines 2; the power unit 3 is connected to the rotating shaft 21 of the pair of compressed air energy engines 2, and the power unit 3 passes the The compressor 2 is driven.
  • the pair of compressed air energy storage devices 1 is composed of a pair of cylinders that are each closed, one cylinder (ie, high pressure storage gas 11) is filled with high pressure gas, and the other cylinder (ie, low pressure storage gas 12) It is filled with low pressure gas.
  • the pair of compressed air energy storage devices 1 includes an inner body 13 and an outer body 14 sleeved outside the inner body 13, and the inner body 13 is filled with a first gas.
  • the cavity 15 formed between the outer body 14 and the inner body 13 is filled with a second gas, and the first gas and the second gas have a pressure difference, that is, a gas pressure difference.
  • the inner body 13 may be a high pressure storage gas 11, the first gas in the inner body 13 is a high pressure gas, the cavity 15 is a low pressure storage gas 12, and the first in the cavity 15
  • the second gas is a low pressure gas; or, in another embodiment, the inner body 13 is a low pressure storage gas 12, the first gas in the inner body 13 is a low pressure gas, and the cavity 15 is a high pressure storage gas. 11.
  • the second gas in the chamber 15 is a high pressure gas.
  • the inner body 13 at this time is a high pressure storage gas 11
  • the cavity 15 is a low pressure storage gas 12
  • the inner body 13 at this time is a low-pressure storage gas 12
  • the cavity 15 is a high-pressure storage gas 11, which is beneficial for reducing the stress on the wall of the outer body 14 and offsetting the contraction of the outer body 14. pressure.
  • the pressure of the high pressure gas is stronger than the pressure of the low pressure gas, and the pressure difference between the high pressure gas and the low pressure gas is the opposite pressure energy.
  • the pressure of the high pressure gas may be 0.1 MPa to 100 MPa, and the pressure of the low pressure gas may be 100 Pa to 30 MPa.
  • the high-pressure gas and the low-pressure gas may be selected from a mixture of air, or nitrogen gas, or helium gas or other gases; and the mixture of the other gases may be, for example, a mixture of nitrogen gas and helium gas.
  • the pair of compressed air engines 2 may be multiple, and the plurality of pairs of pressurized gas engines 2 are connected in series to the power device 3 and the compressed gas energy storage. Between the devices 1, for example, two, three or more pairs of the compressed air energy engines 2 can be connected between the power unit 3 and the gas pressure energy storage device 1 according to actual needs, which is not limited herein. Of course, in another possible embodiment, only one pair of compressed air engines 2 may be connected between the power unit 3 and the pair of pressurized energy storage devices 1.
  • a regenerator 4 is connected between the pair of compressed air engines 2 and the pair of compressed air energy storage devices 1, and the regenerator 4 is used for the gas flowing out of the high pressure storage gas 11 and flowing into the low pressure storage gas.
  • the gas in 12 is exchanged for cold heat.
  • the regenerator 4 can be provided with a serpentine or spiral coiled double pipe, wherein one of the pipes has a high inflow
  • the gas is pressurized, and the other pipe flows into the low-pressure gas, and the heat in each pipe can be exchanged through the double pipes which are in contact with each other on the outer surface, that is, the amount of cold and gas generated when the gas is discharged from the high-pressure storage gas 11 is compressed.
  • the heat generated when entering the low pressure storage gas 12 is exchanged so that the overall cooling capacity and heat are compensated in a balanced manner in the regenerator 4 during gas release and expansion.
  • the working process of the pressurized gas power system of the present invention is as follows: the high pressure gas in the high pressure storage gas 11 of the compressed gas energy storage device 1 flows into the pressure gas energy engine 2 through the regenerator 4, thereby making the pressure gas engine 2
  • the rotating shaft 21 rotates to drive the power unit 3 to operate; after the work is performed on the high-pressure gas in the gas-energy engine 2, the gas pressure is lowered, and then discharged into the low-pressure storage gas 12 of the pressurized energy storage device 1.
  • the above process can be continued until the gas pressure in the high pressure storage gas 11 is equal to the gas pressure in the low pressure storage gas 12, that is, the gas pressure difference between the gas in the high pressure storage gas 11 and the low pressure storage gas 12 is equal to zero.
  • the working process of the closed gas working fluid of the pressurized gas power system of the invention is an isothermal isothermal thermal motion process, and the remarkable features are: zero discharge of working medium; high energy conversion efficiency; simple structure of the running parts of the mechanism; The reliability of the pneumatic system; no consumables; reduced maintenance costs for the operating process.
  • a pressure-competent differential rotor regulator valve 5 is provided between the regenerator 4 and the gas-pressure energy storage device 1, and the pair of pressurized gas differential rotor regulator valves 5 are used for low pressure.
  • the pressure of the inlet gas source of the storage gas 12 is reduced to a required outlet gas source pressure, and the energy of the gas source working medium itself can be relied on, so that the outlet gas source pressure of the high pressure storage gas 11 is automatically maintained stable.
  • the pair of pressurized gas differential rotor regulator valve 5 is used to depressurize the pressure of the gas source flowing out of the pressure gas engine 2 to the inlet source pressure of the low pressure storage gas 12, and the outlet gas source that flows out of the high pressure storage gas 11
  • the pressure is reduced to the inlet air source pressure required for the compressor 2, and can rely on the pressure difference of the gas source engine 2 and the spring 552 or torsion spring in the differential pressure regulator valve 5 of the pressure gas. 5531, the pressure difference between the inlet and outlet gas source of the compressor can be automatically stabilized.
  • the pair of compressed air energy differential rotor regulator valve 5 includes a first duct 51, a second duct 52, a differential cylinder 53 and a linkage mechanism 54, wherein: one end 511 of the first duct 51 is The high-pressure storage gas 11 is connected, and the other end 512 is connected to the gas-energy engine 2, and the first rotor valve 513 is rotatably disposed in one end 511 of the first pipe 51, and the first rotor valve 513 has a first rotor.
  • valve passage 5131 an end 521 of the second conduit 52 is connected to the low-pressure storage gas 12, and the other end 522 is connected to the gas-energy engine 2, and the second rotor valve is rotatably disposed at one end 521 of the second conduit 52.
  • the second rotor air valve 523 has a second rotor valve passage 5231;
  • the differential cylinder 53 is connected between the other end 512 of the first duct 51 and the other end 522 of the second duct 52.
  • the differential cylinder 53 is inside.
  • a differential piston 531 is movably provided.
  • the differential cylinder 53 is divided into a first cylinder 532 and a second cylinder 533 by a differential piston 531.
  • the first cylinder 532 is in communication with a first conduit 51, the second cylinder 533 Connected with the second duct 52; the linkage mechanism 54
  • the differential piston 531 is connected to the first rotor valve 513 and the second rotor valve 523 according to the movement of the differential piston 531.
  • the pair of compressed air differential rotor regulator valves 5 further includes a drive mechanism 55 that can drive the differential piston 531 to move within the differential cylinder 53.
  • the drive mechanism 55 includes a connecting rod 551 and a spring 552, one end of which is connected to a spring 552, and the other end of the connecting rod 551
  • the linkage mechanism 54 includes a first linkage rod 541 and a second linkage rod 542.
  • the two ends of the first linkage rod 541 are rotatably connected to the connecting rod 551 and the first rotor air valve 513, respectively.
  • Both ends of the linkage lever 542 are rotatably connected to the connecting rod 551 and the second rotor air valve 523, respectively.
  • the first rotor air valve 513 and the second rotor air valve 523 are rotated by the movement of the differential piston 531 under the action of the linkage mechanism 54, thereby causing the first rotor gas of the first rotor air valve 513
  • the valve passage 5131 is gradually rotated to communicate with the first conduit 51
  • the second rotor valve passage 5231 of the second rotor air valve 523 is gradually rotated to communicate with the second conduit 52, that is, at the first rotor valve passage 5131 and In a state where the duct 51 is in communication, the second rotor valve passage 5231 communicates with the second duct 52.
  • the high pressure storage gas 11 communicates with the first duct 51
  • the low pressure storage gas 12 communicates with the second duct 52.
  • the high-pressure gas flowing into the first duct 51 from the high-pressure storage gas 11 flows into the first cylinder 532.
  • the other end 522 of the second duct 52 communicates with the second cylinder 533 of the differential cylinder 53
  • the gas flowing into the second duct 52 from the pressurized air energy engine 2 flows into the second cylinder 533, which is poor.
  • the two sides of the movable piston 531 are respectively subjected to the air flow of different pressures. To maintain the pressure balance, the differential piston 531 is automatically moved in the differential cylinder 53 until the tension of the spring 552 and the differential pressure of the differential piston 531 are obtained. Balance, the differential piston 531 stops moving.
  • the driving mechanism 55 includes a driving gear 553 and two driven gears 554 respectively meshing with the driving gear 553, and the two driven gears 554 are respectively Connected to the first rotor valve 513 and the second rotor air valve 523, the drive gear 553 is provided with a torsion spring 5531;
  • the linkage mechanism 54 includes a first linkage rod 541 and a second linkage rod 542, the first linkage rod 541 The two ends are respectively rotatably connected to the first rotor valve 513 and the differential piston 531.
  • the two ends of the second linkage rod 542 are rotatably connected to the second rotor valve 523 and the differential piston 531, respectively.
  • the working process of the pressure-receiving differential rotor regulator valve 5 in this embodiment is similar to the operation of the pressure-to-pressure differential rotor regulator valve 5 in the above-described feasible embodiment, and will not be described herein.
  • the movement of the differential piston 531 is dependent on the rotational drive gear 553 to respectively drive the two coupled to the first rotor valve 513 and the second rotor valve 523.
  • the driven gears 554 are rotated, and the differential piston 531 is moved by the first linkage rod 541 and the second linkage rod 542 according to the rotation of the first rotor air valve 513 and the second rotor air valve 523.
  • the pair of compressed air engines 2 are triangular rotary piston air compressors or engines having a cylinder 22 and a triangular rotary piston 23 rotatably disposed in the cylinder 22, the triangular rotary piston 23
  • the cross section is triangular, and the cylinder 22 is provided with a plurality of inlet and outlet ports connected to the compressed air energy storage device 1.
  • the rotating shaft 21 of the pair of compressed air engines 2 is connected to the triangular rotating piston 23; as shown in FIG. 10, in another possible embodiment, the triangular rotating piston
  • the air press or the engine further has a power gear shaft 24 that is bored in the triangular rotary piston 23 and the inner peripheral wall of the triangular rotary piston 23
  • An engaging convex tooth 234 is provided to cooperate with the power gear shaft 24, and the rotating shaft 21 of the compressed air engine 2 is connected to the power gear shaft 24.
  • the axial center of the triangular rotating piston 23 has a certain distance from the axial center of the power gear shaft 24,
  • the triangular rotary piston 23 is eccentrically rotatable about the power gear shaft 24.
  • the cross section of the cylinder 22 is substantially elliptical
  • the cross section of the triangular rotary piston 23 is substantially triangular
  • the three side walls of the triangular rotary piston 23 are respectively designed to have a slightly outwardly curved shape.
  • the triangular rotary piston 23 has a first end angle 231, a second end angle 232, and a third end angle 233 in sliding contact with the inner wall of the cylinder block 22, the first end angle 231, the second end angle 232, and the third end angle 233 is disposed in a clockwise direction, and the cylinder 22 is divided into a first inner cavity 221, a second inner cavity 222 and a third inner cavity 223 by a first end angle 231, a second end angle 232 and a third end angle 233.
  • the inner cavity of the cylinder 22 between the first end angle 231 and the second end angle 232 is the first inner cavity 221
  • the inner cavity of the cylinder 22 between the second end angle 232 and the third end angle 233 is the second cavity.
  • the inner cavity 222, the inner cavity of the cylinder 22 between the third end angle 233 and the first end angle 231 is a third inner cavity 223;
  • the plurality of inlet and outlet ports on the cylinder 22 include two first air ports 224 and two
  • the second air port 225 is provided with a first air port 224 and a second air port 225 on opposite sides of the cylinder block 22, and the first air port 225 on the side of the cylinder block 22 is located at the cylinder block 22.
  • the second port 225 disposed opposite side.
  • the first air port 224 is connected to the high pressure storage gas 11, and the second air port 225 is connected to the low pressure storage gas 12, which is a triangular rotary piston. engine.
  • the triangular rotary piston 23 is pushed against the cylinder by the high pressure gas flowing into the first air port 224.
  • FIG. 11 in which the position of the triangular rotary piston 23 in the cylinder 22 during the rotation of the power gear shaft 24 one clockwise (ie, 360° rotation) is plotted.
  • the arrow on the triangular rotating piston 23 is the direction of rotation of the triangular rotating piston 23 with respect to the cylinder 22, and is located at the first port 224 and the second port 225.
  • the hollow arrows indicate intake and exhaust respectively.
  • a position state at this time, the triangular rotary piston 23 and the power gear shaft 24 are both at the 0° coordinate position with respect to the cylinder 22; in the B position state, the triangular rotary piston 23 is opposite to the cylinder.
  • the body 22 is rotated to a 20° coordinate position, and the power gear shaft 24 is rotated relative to the cylinder 22 to a coordinate position of 60°; in a C position state, at which time the triangular rotary piston 23 is rotated to a 40° coordinate position, and the power gear shaft 24 is rotated to At the 120° coordinate position; the D position state, at which time the triangular rotary piston 23 is rotated to the 60° coordinate position, the power gear shaft 24 is rotated to the 180° coordinate position; the E position is state, and the triangular rotary piston 23 is rotated to 80°.
  • the power gear shaft 24 is rotated to 240° coordinates At the position; the F position state, at which time the triangular rotary piston 23 is rotated to the 100° coordinate position, and the power gear shaft 24 is rotated to the 300° coordinate position.
  • the first air port 224 on one side of the cylinder 22 is closed, and the first air port 224 on the other side of the cylinder 22 is in the intake state, and is located in the cylinder 22
  • the second air port 225 on one side is closed, and the second air port 225 on the side of the cylinder 22 is in an air outlet state; at this time, the first inner chamber 221 is connected to the high pressure storage gas 11 through the first air port 224, and the first inner chamber 221 The high pressure gas is filled therein, and the second inner chamber 222 is connected to the low pressure storage gas 12 through the second gas port 225.
  • the gas in the second inner chamber 222 is discharged into the low pressure storage gas 12, which is due to the first
  • the radial eccentric thrust generated by the pressure difference formed in the inner cavity 221 and the second inner cavity 222 can push the triangular rotary piston 23 to rotate clockwise, while the pressure in the low pressure storage gas 12 is smaller than the pressure in the second inner cavity 222.
  • the direction of the second port 225 forms a radial eccentric attraction, and the triangular rotary piston 23 rotates clockwise; at this time, no gas enters and exits from the third inner cavity 223, and the eccentric force distance to the triangular rotary piston 23 is zero.
  • the rotational thrust of the triangular rotary piston 23 is not generated.
  • the triangular rotary piston 23 When moving from the A position state to the B position state, the triangular rotary piston 23 is rotated clockwise by 20°, the power gear shaft 24 is rotated clockwise by 60°, and in the B position state, unlike the A position state, The third inner chamber 223 is rotated to be connected to the second port 225 located on the other side of the cylinder 22, and at this time, the gas in the third inner chamber 223 is discharged into the low-pressure storage gas 12 while forming a radial eccentric attraction. The triangular rotary piston 23 is caused to continue to obtain a force for clockwise rotation.
  • the triangular rotary piston 23 When moving from the B position state to the C position state, the triangular rotary piston 23 is rotated clockwise by 40°, and the power gear shaft 24 is rotated clockwise by 120°; at this time, since the first inner cavity 221 is still passing through the cylinder
  • the first port 224 on the other side turns on the high-pressure storage gas 11, the first inner chamber 221 continues to be filled with high-pressure gas, and the second port 225 on the side of the cylinder 22 is blocked by the triangular-rotating piston 23.
  • the second inner chamber 222 is rotated to communicate with the first air port 224 on one side of the cylinder 22, at which time the high pressure gas is introduced into the second inner chamber 222; meanwhile, the third inner chamber 223 is still in the same position as the cylinder 22 In a state where the second port 225 on one side is in communication, the gas therein is discharged into the low-pressure reservoir gas 12 through the second port 225.
  • the triangular rotary piston 23 When in the D position state, the triangular rotary piston 23 is rotated clockwise by 60°, and the power gear shaft 24 is rotated clockwise by 180°; at this time, the first end angle 231 of the triangular rotary piston 23 is rotated through the cylinder 22
  • the first port 224 on the other side, the second end angle 232 of the triangular rotary piston 23 has not been rotated through the second port 225 on the side of the cylinder 22, and at this time, the first cavity 221 is in a state of no gas in and out
  • the second inner chamber 222 is still in communication with the first air port 224 on the side of the cylinder 22, the second inner chamber 222 continues to be filled with high pressure gas, and the third inner chamber 223 is also located on the other side of the cylinder 22.
  • the gas in the third chamber 223 continues to be discharged into the low-pressure reservoir gas 12 through the second port 225.
  • the triangular rotary piston 23 is rotated clockwise by 80° and 100°, respectively, and the power gear shaft 24 is respectively rotated clockwise by 240° and 300°; at this time, the first inner cavity 221 is rotated to communicate with the second port 225 located on one side of the cylinder 22, the gas in the first inner chamber 221.
  • the second inner chamber 222 is discharged into the low pressure storage gas 12, the second inner chamber 222 is still in communication with the first air port 224 on the side of the cylinder 22, and the second inner chamber 222 is continuously filled with high pressure gas.
  • the inner chamber 223 is rotated from a state of being communicated with the second port 225 located on the other side of the cylinder 22 to a state of being communicated with the first port 224 located on the other side of the cylinder 22. Finally, return to the A position state again.
  • the power gear shaft 24 rotates 360° clockwise
  • the triangular rotary piston 23 rotates 120°
  • the first inner cavity 221, the second inner cavity 222, and the third inner cavity 223 complete a complete
  • the intake stroke or the exhaust stroke after the triangular rotary piston 23 rotates 360°
  • the first inner chamber 221, the second inner chamber 222, and the third inner chamber 223 complete three complete intake strokes and exhaust strokes, respectively.
  • Each of the strokes can work on the triangular rotary piston 23, and the power gear shaft 24 performs a total of three 360° clockwise rotations.
  • the first port 224 is connected to the low pressure storage gas 12
  • the second port 225 is connected to the high pressure storage gas 11
  • the pressure gas engine 2 is a triangular rotary piston air press. According to the rotation of the triangular rotary piston 23, the low-pressure gas in the low-pressure storage gas 12 flows into the first inner cavity 221, the second inner cavity 222 or the third inner cavity 223 through the first gas port 224, respectively, and the rotating shaft 21 is rotated by the external power device.
  • the low pressure gas in the first inner chamber 221, the low pressure gas in the second inner chamber 222 or the low pressure gas in the third inner chamber 223 are respectively compressed into the high pressure through the second air port 225.
  • the storage gas 11 Within the storage gas 11.
  • the triangular rotary piston air press of this embodiment is exactly opposite to the operation of the triangular rotary piston engine of the above embodiment, and the specific operation thereof will not be described herein.
  • the triangular rotary piston 23 of the triangular rotary piston air press of this embodiment is rotated counterclockwise with respect to the cylinder 22 under the driving of the rotary shaft 21 of the compressed air engine 2 to compress the low pressure gas in the low pressure storage gas 12 into the high pressure storage.
  • the gas chamber 11 is such that a pressure difference between the low pressure storage gas 12 and the high pressure storage gas 11 is formed, and the pair of compressed gas energy storage devices 1 form a pair of compressed gas energy.
  • the roller set 220 includes an inner roller 25 and an outer roller 26.
  • the outer roller 26 has a circular cross-sectional shape
  • the inner roller 25 has a circular cross-sectional shape. Shape, or rectangle, or other shape.
  • the first end angle 231, the second end angle 232, and the third end angle 233 are respectively provided with two rolling bars, and the two rolling bars are respectively an inner rolling bar 25 and an outer rolling bar 26, and the outer rolling bar 26 can be rolled.
  • the ground is disposed between the inner roller 25 and the inner wall of the cylinder block 22.
  • the inner roller 25 may be a cylindrical rod or a coil; the outer roller 26 is a cylindrical rod to achieve sliding contact between the triangular rotating piston 23 and the inner wall of the cylinder 22.
  • the pair of compressed air engines 2 are a pair of compression air cylinders, a triangular piston air compressor or an engine having a rotatable cylinder 22 and a cylinder 22 disposed therein.
  • the inner non-rotating triangular piston 23' has a triangular cross section, and the triangular piston 23' is provided with a first air port 235 and a second air port 236 connected to the compressed air energy storage device 1, the triangular piston
  • the inner cavity of 23' can communicate with the inner cavity of the cylinder 22.
  • the cross section of the cylinder 22 is substantially elliptical
  • the cross section of the triangular piston 23' is substantially triangular
  • the three side walls of the triangular piston 23' are respectively designed to have a slightly convex shape.
  • the triangular piston 23' has a first end angle 231, a second end angle 232, and a third end angle 233 in sliding contact with the inner wall of the cylinder block 22, the first end angle 231, the second end angle 232, and the third end angle 233 is disposed in a clockwise direction, and the cylinder 22 is divided into a first inner cavity 221, a second inner cavity 222, and a third inner cavity 223 by a first end angle 231, a second end angle 232, and a third end angle 233.
  • the inner cavity of the cylinder 22 between the end angle 231 and the second end angle 232 is the first inner cavity 221
  • the inner cavity of the cylinder 22 between the second end angle 232 and the third end angle 233 is the second inner cavity.
  • the cavity 222, the inner cavity of the cylinder 22 between the third end angle 233 and the first end angle 231 is a third inner cavity 223.
  • the rotating shaft 21 of the compressed air engine 2 is connected to the cylinder block 22;
  • the inner cavity of the triangular piston 23' includes a first piston inner chamber 237 and a second piston inner chamber 238, and the first piston inner chamber
  • the second piston chamber 238 is in communication with the first port 235.
  • the triangular piston 23' is provided with a first gas delivery piston 271, a second gas delivery piston 272 and a third gas delivery piston 273.
  • the first gas delivery piston 271, the second gas delivery piston 272 and the third gas delivery piston 273 are along The first gas delivery piston 271 is disposed opposite to the first inner cavity 221, the second gas delivery piston 272 is disposed opposite to the second inner cavity 222, and the third gas delivery piston 273 and the third inner cavity 223 are disposed in the clockwise direction. Relative settings.
  • the first gas delivery piston 271, the second gas delivery piston 272, and the third gas delivery piston 273 are both piston rods 27 that are axially rotatably disposed on the triangular pistons, and the piston rods 27 are along the same
  • a plurality of first passages 274 are arranged in the axial direction, and a second passage 275 is disposed between the adjacent first passages 274.
  • the second passage 275 has an angle with the first passage 274.
  • the first passage 274 and the second passage 275 are perpendicular to each other, that is, the angle between the second passage 275 and the first passage 274 is 90°.
  • the triangular piston 23' is composed of an inner cylinder 231' and an outer cylinder 232' sleeved outside the inner cylinder 231'.
  • the inner cavity of the inner cylinder 231' is the first piston inner cavity 237.
  • the annular space formed between the outer cylinder 232' and the inner cylinder 231' is a second piston inner chamber 238, and the first piston inner chamber 237 can pass through the plurality of first passages 274 and the first inner chamber 221 and the second inner chamber, respectively.
  • the second inner chamber 223 is in communication with the first inner chamber 221, the second inner chamber 222, or the third inner chamber 223, respectively.
  • the side wall of the inner cylinder 231' is provided with three rows of side cavity channels 2371 in the circumferential direction, and each column side cavity channel 2371 includes a plurality of side cavity ports 2372 which are axially spaced apart, and the position of the side cavity ports 2372 is
  • the plurality of side cavity channels 2381 are disposed in a circumferential direction of the outer tube 232', and each of the side cavity channels 2381 includes a plurality of side cavity ports 2382 which are axially spaced apart, and the side cavity The position of the port 2382 is set to be in communication with the second passage 275.
  • a gear shaft 239 is disposed at the axial center of the cylinder block 22.
  • the opposite sides of the inner wall of the cylinder block 22 are respectively provided with inner protruding teeth 226, and each of the piston rods 27 is provided with a transmission tooth 276.
  • the 276 can be coupled with the gear shaft 239 and the inner protruding teeth 226 to rotate the transmission teeth 276 under the driving of the gear shaft 239 and the inner protruding teeth 226 to drive the rotation of the piston rod 27 To achieve the purpose of the airflow through the piston rod 27 in both directions.
  • the first port 235 is connected to the high pressure storage gas 11
  • the second port 236 is connected to the low pressure storage gas 12
  • the compressor 2 is a rotary cylinder.
  • Triangle piston engine In a state where the first port 235 is in communication with the first inner cavity 221, the second inner cavity 222 or the third inner cavity 223, the high-pressure gas that is introduced from the first gas port 235 can flow into the first inner cavity 221, respectively.
  • the cylinder 22 rotates relative to the triangular piston 23' under the push of high pressure gas; and the second inner port 221 and the first inner cavity 221, the second inner cavity 222 or the third In a state where the inner chamber 223 is in communication, the gas in the first inner chamber 221, the gas in the second inner chamber 222, or the gas in the third inner chamber 223 can be discharged to the second air port 236, respectively, according to the rotation of the cylinder 22.
  • FIG. 15 in which the first gas delivery piston 271 , the second gas delivery piston 272 and the third gas transmission on the triangular piston 23 ′ are drawn in the process of rotating the cylinder 22 by 180°.
  • the arcuate arrow in the cylinder 22 in the figure indicates the direction in which the cylinder 22 rotates.
  • Figure 15 is divided into six position states: A position state, at which time the cylinder 22 is at the 0° coordinate position; B position state, at which time the cylinder 22 is rotated relative to the triangular piston 23' to the 30° coordinate position; State, at this time, the cylinder 22 rotates to the 60° coordinate position with respect to the triangular piston 23'; in the D position state, the cylinder 22 rotates to the 90° coordinate position with respect to the triangular piston 23'; the E position state, at this time, the cylinder 22 is rotated relative to the triangular piston 23' to the 120° coordinate position; in the F position state, the cylinder 22 is rotated relative to the triangular piston 23' to the 150° coordinate position.
  • a position state at which time the cylinder 22 is at the 0° coordinate position
  • B position state at which time the cylinder 22 is rotated relative to the triangular piston 23' to the 30° coordinate position
  • State at this time, the cylinder 22 rotates to the 60° coordinate position with respect to the triangular
  • the cylinder 22 In the A position state, the cylinder 22 is at a position of 0° with respect to the triangular piston 23'; the second gas delivery piston 272 is in a closed state, that is, it does not communicate with the inner cavity of the triangular piston 23' and the second inner cavity 222; At this time, the second passage 275 of the third gas delivery piston 273 communicates with the second piston inner chamber 238, and the second piston inner chamber 238 communicates with the second gas port 236 that connects the low pressure storage gas 12, and the third inner chamber 223 The gas can discharge the second port 236; at the same time, the first passage 274 of the first gas delivery piston 271 is in communication with the first piston chamber 237, and the first piston chamber 237 is connected to the first port 235 to which the high pressure storage gas 11 is connected.
  • the first inner chamber 221 is filled with high-pressure gas, and the radial eccentric thrust generated by the difference in the gas pressure between the cylinder 22 and the triangular piston 23' can push the cylinder 22 to rotate counterclockwise.
  • the cylinder 22 is moved to the B position state, the cylinder 22 is rotated by 30° with respect to the triangular piston 23'; the second gas delivery piston 272 is rotated by the convex teeth 226 of the cylinder 22, and the first passage 274 is rotated to In communication with the first piston inner chamber 237, the second inner chamber 222 is filled with high pressure gas; at this time, the second passage 275 of the third gas delivery piston 273 is still in communication with the second piston inner chamber 238, and the third inner chamber 223 The gas continues to exit the second port 236; and the first gas delivery piston 271 is rotated by the gear shaft 239 to a closed state.
  • the cylinder 22 When the cylinder 22 is moved to the C position state, the cylinder 22 is rotated by 60° with respect to the triangular piston 23'; at this time, the first gas delivery piston 271 is rotated by the gear shaft 239 to communicate with the first piston inner chamber 237.
  • the gas in the first inner chamber 221 is discharged to the second port 236; the first passage 274 of the second gas delivery piston 272 is still in communication with the first piston inner chamber 237.
  • the second inner chamber 222 continues to be filled with high pressure gas; at this time, the third air transfer piston 273 is rotated to the closed state by the inner protruding teeth 226 of the cylinder block 22.
  • the cylinder 22 When the cylinder 22 is moved to the D position state, the cylinder 22 is rotated by 90° with respect to the triangular piston 23'; the second gas delivery piston 272 is rotated by the gear shaft 239 to a closed state, and is located in the second inner cavity 222.
  • the gas does not perform work on the rotation of the cylinder 22; the third gas delivery piston 273 is rotated by the convex teeth 226 in the cylinder 22 to connect the first passage 274 with the first piston inner chamber 237, and the third inner chamber 223
  • the high pressure gas is filled therein; at this time, the second passage 275 of the first gas delivery piston 271 is still in communication with the second piston inner chamber 238, and the gas in the first inner chamber 221 is discharged from the second gas port 236.
  • the cylinder 22 When the cylinder 22 is moved to the E position state, the cylinder 22 is rotated by 120° with respect to the triangular piston 23'; the first gas delivery piston 271 is rotated to the closed state by the convex teeth 226 in the cylinder 22; the third gas transmission
  • the first passage 274 of the piston 273 is still in communication with the first piston inner chamber 237, and the third inner chamber 223 continues to be filled with high pressure gas; at this time, the second gas delivery piston 272 is rotated by the gear shaft 239 to the second thereof.
  • the passage 275 is in communication with the second piston bore 238 and the gas in the second bore 222 exits the second port 236.
  • the cylinder 22 When the cylinder 22 is moved to the F position state, the cylinder 22 is rotated by 150° with respect to the triangular piston 23'; the third gas delivery piston 273 is rotated by the gear shaft 239 to a closed state; the first gas delivery piston 271 is in the cylinder.
  • the inner tooth 226 of the body 22 is rotated downward to connect the first passage 274 with the first piston inner chamber 237, and the first inner chamber 221 is filled with high-pressure gas; at this time, the second passage 275 of the second gas delivery piston 272 Still communicating with the second piston inner chamber 238, the gas in the second inner chamber 222 will discharge the second air port 236, and at this time, under the action of the gas energy difference between the second inner chamber 222 and the first inner chamber 221, the cylinder The body 22 continues to rotate counterclockwise to the A position state.
  • the cylinder is rotated 180° counterclockwise, and the first inner chamber 221, the second inner chamber 222, and the third inner chamber 223 each complete a complete intake and exhaust process, that is, the three cylinders are completed completely.
  • the intake stroke and the exhaust stroke, and each stroke can work on the rotation of the cylinder.
  • the first port 235 is connected to the low pressure storage gas 12
  • the second port 236 is connected to the high pressure storage gas 11
  • the compressed air engine 2 is a rotary cylinder delta piston.
  • the low pressure gas in the low pressure storage gas 12 can flow into the first inner cavity 221, the second inner cavity 222 or the third inner cavity 223 through the first gas port 235, respectively, in the first inner cavity 221, the second inner cavity 222 or the first
  • the gas in the first inner chamber 221, the gas in the second inner chamber 222, or the gas in the third inner chamber 223 can be respectively passed through the second air port 236. It is compressed into the high pressure storage gas 11.
  • the rotary cylinder delta piston air press of this embodiment is opposite to the operation of the rotary cylinder delta piston engine (the embodiment shown in FIG. 12) of the above embodiment, and the specific operation thereof will not be described herein.
  • the cylinder 22 of the rotary cylinder delta piston air compressor of this embodiment is rotated clockwise with respect to the triangular piston 23' under the driving of the rotating shaft 21 of the compressed air engine 2 to compress the low pressure gas in the low pressure storage gas 12 into the high pressure.
  • the gas is stored 11 to form a gas pressure difference between the low pressure storage gas 12 and the high pressure storage gas chamber 11, and the pair of compressed gas energy storage devices 1 form a pair of compressed gas energy.
  • the pair of compressed air engines 2 are a multi-arc rotary piston air compressor or an engine having a cylinder 22 and a multi-arc rotor 28 rotatably disposed in the cylinder 22, a plurality of arcs
  • the rotor 28 has a plurality of curved outer walls 281 disposed in the circumferential direction.
  • the cylinder 22 has a plurality of curved inner walls 227 disposed in the circumferential direction.
  • the curved outer walls 281 and the curved inner walls 227 are in contact with each other, and the cylinder 22 is disposed on the cylinder 22.
  • a plurality of inlet and outlet ports are connected to the gas energy storage device 1.
  • the number of the curved outer walls 281 is n
  • the number of the curved inner walls 227 is n+1
  • the number of the inlet and outlet ports is n+1.
  • the rotating shaft 21 of the pair of compressed air engines 2 is connected to the multi-arc rotor 28.
  • the pair of compressed air multi-arc rotary piston air compressors or engines further have a power gear shaft 24, and the power gear shaft 24 is disposed in the multi-arc rotor 28.
  • the inner peripheral wall of the multi-arc rotor 28 is provided with engaging teeth 282 that cooperate with the power gear shaft 24, and the rotating shaft 21 of the compressed air engine 2 is connected to the power gear shaft 24.
  • the cylinder 22 is divided into a first inner cavity 221, a second inner cavity 222 and a third inner cavity 223 by a multi-arc rotor 28; a plurality of inlet and outlet ports on the cylinder 22 can be respectively associated with the first inner cavity 221, The second inner chamber 222 or the third inner chamber 223 are in communication.
  • each of the inlet and outlet ports includes a plurality of first channels 291 and a plurality of second channels 292.
  • the first passage 291 is connected to the high pressure storage gas 11
  • the second passage 292 is connected to the low pressure storage gas 12
  • the gas-energy engine 2 is a multi-arc rotary piston engine with a compression air energy.
  • a valve stem 29 is rotatably disposed in each of the inlet and outlet ports, and the valve stem 29 is spaced apart from each other in the axial direction by a plurality of first passages 291 which are parallel to each other, adjacent to each other.
  • a second passage 292 is disposed between the first passages 291, and the first passage 291 and the second passage 292 have an angle therebetween; in the embodiment, the first passage 291 and the second passage 292 are perpendicular to each other, that is, The angle between the first passage 291 and the second passage 292 is 90°.
  • a rotor valve mechanism 283 is connected to the multi-arc rotor 28, and the rotor valve mechanism 283 is used to open or close the plurality of first passages 291 and the plurality of second passages 292 of the inlet and outlet ports.
  • the rotor valve mechanism 283 includes a valve swivel 2831.
  • the valve swivel 2831 is provided with a plurality of long convex teeth 2832 and a plurality of short convex teeth 2833 along the circumferential direction thereof, and two adjacent short convex teeth 2833 are disposed between the two.
  • n+1 there is a long convex tooth 2832; a gas gear rod 29 is connected with a rod gear 293, and the short convex teeth 2833 and the long convex teeth 2832 can be respectively driven and connected with the rod gear 293, and the number of the long convex teeth 2832 and the number of the short convex teeth 2833 are respectively It is n+1.
  • the first passage 291 is connected to the low-pressure storage gas 12
  • the second passage 292 is connected to the high pressure storage gas 12, which is a multi-arc rotary piston air compressor.
  • a second channel 292 is disposed between the adjacent first channels 291, and the plurality of first channels 291 and the plurality of second channels 292 are disposed in parallel with each other, and the first channel 291 is provided with a first one-way valve.
  • a second check valve 2921 is disposed in the second passage 292.
  • the second check valve 2922 can open the second passage 292 without high pressure storage.
  • the gas in the gas 11 is returned to the inner cavity of the cylinder 22.
  • two rollers are disposed at three contact points of the cylinder 22 and the multi-arc rotor 28 to form a roller group 220.
  • the roller set 220 includes an inner roller 25 and an outer roller 26.
  • the outer roller 26 has a circular cross-sectional shape, and the inner roller 25 may have a circular cross-sectional shape, or a rectangular shape, or other shapes.
  • the cylinder 22 has four arcuate inner walls 227 connected in series, the curved outer wall 281 mating with an arcuate inner wall 227 having four inlet and outlet ports.
  • the cylinder 22 has five curved inner walls 227 connected in series, the curved outer wall 281 cooperating with an arcuate inner wall 227 having five inlet and outlet ports.
  • the multi-arc rotary piston air compressor or the engine may also be a counter-pressure gas engine having a five-arc rotor, a six-arc rotor, or the like, which is not limited herein.
  • an electromagnet or a permanent magnet 228 may be respectively disposed on the cylinder 22 and the multi-arc rotor 28.
  • the purpose of driving the multi-arc rotor 28 to rotate within the cylinder 22 is achieved by an electromagnet or permanent magnet 228.
  • FIG. 23 is a working flow chart of a two-arc rotary piston engine.
  • the figure shows the inflow and outflow of the first gas delivery piston 271, the second gas delivery piston 272 and the third gas delivery piston 273 on the triangular rotary piston 23 during the rotation of the two arc rotors relative to the cylinder body by 0° to 180°. status.
  • Position C position state, the coordinate position of the two arc rotors after rotating to the cylinder block 22 to 60°; the position of the D position, the coordinate position of the two arc rotors after rotating to the cylinder block 22 to 90°; At this time, the two arc rotors are rotated relative to the cylinder 22 to a coordinate position after 120°; in the F position state, the two arc rotors are rotated relative to the cylinder 22 to a coordinate position after 150°.
  • the two arc rotors are located at 0° with respect to the cylinder 22; the air passages of the valve stem 29 opposite to the second inner chamber 222 are in a closed state, and the gas in the second inner chamber 222 is not Performing work on the rotation of the two-arc rotor; the plurality of first passages 291 of the valve stem 29 opposite to the first inner chamber 221 are in communication with the high-pressure storage gas 11, and the first inner chamber 221 is filled with high-pressure gas;
  • the second passage 292 of the gas valve rod 29 opposite to the third inner chamber 223 is in communication with the low pressure storage gas 12, and the gas in the third inner chamber 223 can be discharged into the low pressure storage gas 12, in the first inner chamber 221 and the third inner chamber Under the action of the gas pressure difference in the chamber 223, the two arc rotors rotate clockwise with respect to the cylinder block 22.
  • the two-arc rotor In the B-position state, the two-arc rotor is rotated relative to the cylinder 22 to a position at 30°; under the action of the elongated teeth 2832 of the rotor valve mechanism 283, on the valve stem 29 opposite the second inner chamber 222
  • the rod gear 293 is rotated, the second passage 292 on the valve stem 29 is in communication with the second inner chamber 222, and the gas in the second inner chamber 222 is discharged into the low-pressure storage gas 12;
  • the plurality of first passages 291 of the gas valve rod 29 opposite to the inner chamber 221 are still in communication with the high pressure storage gas 11, the first inner chamber 221 continues to be filled with high pressure gas; and the third inner chamber 223 is replaced by two arc rotors.
  • One of the curved outer walls 281 is filled, and the rod gear 293 of the valve stem 29 opposite to the third inner chamber 223 is rotated by the short convex teeth 2833 of the rotor valve mechanism 283 to be in a closed state, in the first inner cavity.
  • the two arc rotors continue to rotate clockwise with respect to the cylinder 22 under the action of the gas pressure differential in the second inner chamber 222.
  • the two arc rotors are rotated relative to the cylinder 22 to a position at 60°; under the action of the short convex teeth 2833 of the rotor valve mechanism 283, on the valve stem 29 opposite to the third inner chamber 223
  • the rod gear 293 is rotated, and the first passage 291 on the valve stem 29 is in communication with the third inner chamber 223, and the third inner chamber 223 is filled with high-pressure gas; at this time, opposite to the first inner chamber 221
  • the rod gear 293 on the valve stem 29 is rotated by the elongated teeth 2832, the valve stem 29 is in a closed state, and the first inner chamber 221 has no gas in and out; at this time, the valve stem 29 opposite to the second inner chamber 222
  • the plurality of second passages 292 are still in communication with the low pressure storage gas 12, and the gas in the second inner chamber 222 can be discharged into the low pressure storage gas 12, and the gases in the third inner chamber 223 and the second inner chamber 222 Under the pressure difference, the two arc
  • the two arc rotors are rotated relative to the cylinder 22 to a position at 90°; under the action of the short teeth 2833 of the rotor valve mechanism 283, on the valve stem 29 opposite the second inner chamber 222
  • the lever gear 293 is rotated, and the valve stem 29 is in a closed state; at this time, the valve stem 29 opposite to the first inner chamber 221
  • the second passage 292 of the air valve rod 29 communicates with the first inner chamber 221, and the gas in the first inner chamber 221 is discharged into the low pressure storage gas 12;
  • the plurality of first passages 292 of the valve stem 29 opposite to the third inner chamber 223 are still in communication with the high pressure storage gas 11, and the third inner chamber 223 continues to be filled with high pressure gas, in the third inner chamber 223 and the first Under the action of the gas pressure difference in the inner chamber 221, the two arc rotors continue to rotate clockwise with respect to the cylinder block 22.
  • the two-arc rotor In the E-position state, the two-arc rotor is rotated relative to the cylinder 22 to a position of 120°; under the action of the short convex teeth 2833 of the rotor valve mechanism 283, on the valve stem 29 opposite the second inner chamber 222
  • the rod gear 293 is rotated, the first passage 291 of the valve stem 29 is in communication with the second inner chamber 222, and the second inner chamber 222 is filled with high-pressure gas; at this time, the valve stem opposite to the first inner chamber 221
  • the second passage 292 on 29 is still in communication with the first inner chamber 221, and the gas in the first inner chamber 221 continues to be discharged into the low pressure storage gas 12; at the same time, the long convex teeth 2832 in the rotor valve mechanism 283
  • the gas valve rod 29 opposite to the third inner chamber 223 is rotated to be in a closed state.
  • the two arc rotors are opposed to the cylinder block 22 Continue to rotate clockwise.
  • the two arc rotors are rotated relative to the cylinder 22 to a position of 150°; under the action of the elongated teeth 2832 of the rotor valve mechanism 283, on the valve stem 29 opposite the third inner chamber 223
  • the rod gear 293 is rotated, the second passage 292 of the valve stem 29 is in communication with the third inner chamber 223, and the gas in the third inner chamber 223 can be discharged into the low pressure storage gas 12; at this time, with the first inner chamber
  • the opposite valve stem 29 is rotated by the short convex teeth 2833 to the closed state, and one of the curved outer walls 281 of the two arc rotors enters the first inner cavity 221; meanwhile, the gas valve stem opposite to the second inner cavity 222
  • the first passage 291 of the 29 is still in communication with the second inner chamber 222, and the
  • each cylinder completed a complete intake stroke or exhaust stroke; after the two arc rotors rotated 360° clockwise, the three cylinders completed two complete The intake stroke and the exhaust stroke, and each stroke can work on the rotation of the two arc pistons.
  • FIG. 24 it is a working flow chart of a two-arc rotary piston air press, and the two-arc rotary piston air press of the embodiment and the two-arc rotary piston engine of the above embodiment (the embodiment shown in FIG. 16) The process is just the opposite, and the specific work process will not be repeated here.
  • the two-arc rotor 28 of the two-arc rotary piston air press of this embodiment is rotated counterclockwise with respect to the cylinder 22 under the driving of the rotating shaft 21 of the gas-energy engine 2 to compress the low-pressure gas in the low-pressure storage gas 12 into a high pressure.
  • the gas is filled 11 to form a pressure difference between the low pressure storage gas 12 and the high pressure storage gas 11 to form a pair of compressed gas energy in the pair of compressed gas energy storage devices 1.
  • the power unit 3 can be a generator, an elevator, a pneumatic tool, a vehicle, a ship or an aircraft.
  • the pneumatic energy engine can be, for example, a pneumatic machine or an engine of an aircraft.
  • the system includes five pairs of pressurized gas engines connected in series (pressure The gas energy engine 2a, the counter pressure energy engine 2b, the counter pressure gas engine 2c, the counter pressure gas engine 2d and the counter pressure gas engine 2e), and a pair of pressurized gas energy storage devices 1.
  • the pair of compressed air energy storage devices 1 are connected to the gas pressure energy engine 2c, which may be a triangular rotary piston engine or a multi-arc rotary piston engine; a pair of compressed air engine 2a, a pair of pressurized gas engines 2b, a pair The compressed air engine 2d and the pair of compressed air engines 2e are respectively coupled to the rotating shaft 21 of the counter pressure energy engine 2c.
  • the pair of the compressed air engine 2a, the compressed air engine 2b, the compressed air engine 2d and the pair connected to the rotating shaft 21 are driven.
  • the gas-energy engine 2e is activated, wherein the pair of the gas-energy engine 2a, the pair of the gas-energy engine 2b, the pair of the gas-energy engine 2d, and the counter-pressure gas engine 2e are respectively a triangular rotary piston air compressor or a multi-arc rotary piston air compressor.
  • the mechanical energy can be generated by the compressor 2c to drive the compressor 2a, the compressor 2b, the compressor 2d, and the compressor 2e.
  • the gas source of the system is derived from the closed pressurized gas energy storage device 1, and is not in contact with the atmosphere of the external environment in almost any place.
  • the space of the entire airflow is limited and isometric; in the storage pressurization, each The pressure gas engine is placed adjacent to each other, so that the heat generated by each pair of gas-energy engines in the process of being a pneumatic machine can be used as heat absorbed in the engine process, and the heat energy is completely complementary to each other in total amount;
  • the gas pipelines are arranged side by side. Through the heat dissipation arrangement of the regenerator 4, the heat energy in the pipelines is completely complementary to each other in the total amount, without the need for additional thermal energy storage recovery measures, which embodies the gas pressure energy.
  • the system comprises five pairs of pressurized gas engines connected in series (for a compressed air engine 2f, a pressurized gas engine 2g, a pressurized gas engine 2h, a pressurized gas engine 2i and a pair) The pneumatic energy engine 2j) and a pair of compressed gas energy storage devices 1.
  • the pair of compressed air energy storage devices 1 are connected to the gas pressure energy engine 2c, wherein the five pairs of pressurized gas engines are triangular rotary piston engines or multi-arc rotary piston engines, and five pairs of pressurized gas engines are connected in series on the rotating shaft 21 .
  • the system transmits the high pressure gas in the high pressure storage gas 11 of the compressed gas energy storage device 1 to the pressure gas energy engine 2j, and the gas pressure after the work is reduced, and then is sent to the pressure gas engine 2g, and the gas is again transported.
  • the gas after the work is supplied to the pressure gas engine for 2 hours, and the gas after the work is again supplied to the pressure gas engine 2i, and finally to the pressure gas engine 2f, and the gas discharged from the pressure gas engine 2f is sent to the low pressure reservoir in the gas pressure energy storage device 1.
  • the rotating shaft 21 is rotated to drive the two wheels 61 connected to both sides of the rotating shaft 21 to rotate.
  • the pair of compressed air engines 2h are also combined with two other pressure gas engines (for the pressure gas engine 2k) And communicating with the gas path of the gas-energy engine 2s), so that the gas flowing through the gas-energy engine 2h is respectively charged into the pressure-energy engine 2k and the counter-pressure engine 2s to drive the wheel connected to the gas-energy engine 2k. 62. Rotation of the wheel 63 connected to the compressed air engine 2s. This process is terminated until the pressure difference between the gas pressure in the high pressure storage gas 11 and the gas pressure in the low pressure storage gas 12 is zero.
  • this is an exchange process of heat, work, and energy.
  • the work is released to each pair of the pressure gas engine step by step, and the generated mechanical energy drives the wheel.
  • Rotation, the exchange process of heat, work and energy in the release of gas energy is based on the isothermal and equal volume decompression process, which can achieve higher exchange efficiency.
  • the gas source of the system is derived from the closed pressurized gas energy storage device 1, and is not in contact with the atmosphere of the external environment in almost any place.
  • the space of the entire airflow is limited and isometric; in the work of releasing gas energy, each pair of gas pressure energy
  • the engines are arranged adjacent to each other, and the heat energy is mutually complementary in the total amount; and the two air pressure gas pipelines are arranged side by side, and the heat energy in the pipeline is exactly the same in the total amount through the heat dissipation arrangement of the regenerator 4
  • the ground can be completely complemented by each other, without the need for additional thermal energy storage recovery measures, reflecting the advantages of the isothermal and equal-release energy of the gas-energy kinetic energy system.
  • the system is an embodiment of a power grid energy storage power station, and is a system for exchanging electric energy and the pressure gas energy in the gas energy storage device 1 with the grid power, from the viewpoint of thermodynamics.
  • the system is a process of exchange of heat, electricity, and pressure gas.
  • the pressure reduction or the number of pressurization stages is arranged by equal pressure difference between the high pressure gas and the low pressure gas in the compressed gas energy storage device 1.
  • the compressed air energy is stepped up to the compressed air energy storage device 1.
  • the compressed air energy is gradually released from the compressed air energy storage device 1 in a stepwise manner. Electric energy comes.
  • the exchange process of heat, electricity and pressure gas is based on the isothermal and equal volume decompression process, and high exchange efficiency can be obtained.
  • the electric energy storage condition process of the power grid the synchronous motor 7 connected to the power grid is set to the synchronous motor operating mode, and the electrical energy of the grid is converted into the mechanical torque energy on the rotating shaft 21, thereby driving the six pairs of compressed air engines on the rotating shaft 21 (2m for compressed air engine, 2n for compressed air engine, 2t for pressurized gas engine, 2p for pressurized gas engine, 2p for pressurized gas engine 2k and 2x for pressurized gas engine), where 2m for pressurized gas engine and for pressurized gas engine 2n, the pressure gas engine 2t, the pressure gas engine 2p, the pressure gas engine 2q and the pressure gas engine 2r are respectively a triangular rotary piston air compressor or a multi-arc rotary piston air compressor, at this time, the exchange valve 81 and the exchange valve 82 It is set to the air compressor air supply mode.
  • the low-pressure gas in the gas-pressure energy storage device 1 is firstly connected to the gas-energy engine 2t through the exchange valve 81, and the pressurized gas is then connected to the gas-energy engine 2n, and the gas is pressurized.
  • the finally pressurized gas is again sent to the compressed gas energy storage device 1 through the exchange valve 81; the other is connected to the compressed air energy engine 2p via the exchange valve 82, and the pressurized gas is re-accessed.
  • the gas-energy engine 2q, the re-pressurized gas is connected to the gas-energy engine 2r, and the finally pressurized gas is again sent to the pressurized gas energy storage device 1 through the exchange valve 82.
  • the development of this process makes the pressure difference of the gas in the gas energy storage device 1 gradually increase after six stages of pressurization, that is, the energy of the gas pressure energy increases, which means that the electric energy is converted into a form of pressure gas. Store it.
  • the power recovery process of the power grid the synchronous motor 7 connected to the power grid is set to the synchronous generator operating mode, wherein the compressed air engine 2m, the compressed air engine 2n, the compressed air engine 2t, the pressurized gas engine 2p,
  • the pressure air energy engine 2q and the counter pressure gas engine 2r are respectively a triangular rotary piston engine or a multi-arc rotary piston engine;
  • the exchange valve 81 and the exchange valve 82 are set to the engine air delivery mode.
  • the high-pressure gas in the gas-pressure energy storage device 1 is firstly connected to the gas-energy engine 2m through the exchange valve 81, and the decompressed gas is then connected to the gas-energy engine 2n, and the decompressed gas is connected to the gas-pressure energy.
  • the engine 2t, the finally decompressed gas is again sent to the pressurized gas energy storage device 1 through the exchange valve 81; the other is connected to the compressed air energy engine 2r via the exchange valve 82, and the decompressed gas is reconnected to the compressed air energy engine.
  • the decompressed gas is connected to the pressure gas engine 2p, and the finally decompressed gas is again sent to the pressurized gas energy storage device 1 through the exchange valve 82.
  • the six pairs of gas-energy engines push the shaft 21 to rotate, which in turn drives the generator 7 to generate electricity to the grid.
  • the development of this process causes the pressure difference of the gas in the gas-energy storage device 1 to gradually decrease, meaning that the form in which the gas can be converted into electric energy is gradually recovered.
  • the gas source of the system is derived from the closed pressurized gas energy storage device 1, and is not in contact with the atmosphere of the external environment in almost any place, and the space of the entire airflow is closed and equal volume; in the work of releasing the gas energy, each pair of gas pressure energy
  • the engine is adjacently staggered, and the heat and cooling generated in the system operation are exactly complementary to each other in the total amount; and the two air pressure gas pipelines are arranged side by side, through the heat dissipation arrangement of the regenerator 4, the pipeline
  • the thermal energy in the total amount is completely complementary to each other naturally, without the need for additional heat and cooling storage and recovery measures, reflecting the gas energy and electric energy exchange mode of the isothermal and equal volume structure of the gas kinetic energy system. Efficiency and cost advantages.
  • the present invention also provides a method for compressing gas power, comprising the steps of: providing a high pressure storage gas 11 filled with a high pressure gas and a low pressure storage gas 12 filled with a low pressure gas, the low pressure.
  • the stored gas 12 and the high-pressure storage gas 11 have a pair of compressed gas energy, and the pair of pressurized gas is released in an isothermal, equal-volume thermal cycle to drive the external power unit 3.
  • the compression air energy can be released by the isothermal and equal-capacity thermal cycle of the compressor, and the rotating shaft of the compression air engine is connected to the power device.
  • the method for compressing gas energy of the embodiment is implemented by the gas-energy power system of the present invention.
  • the structure, working principle and beneficial effects of the gas-powered power system have been described in detail above, and will not be described herein.

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Abstract

一种对压气能动力系统，包括：对压气能贮存装置（1），其具有高压贮气体（11）和低压贮气体（12），高压贮气体（11）中填充有高压气体，低压贮气体（12）中填充有低压气体，对压气能贮存装置（1）具有对压气能；对压气能发动机（2），其分别与低压贮气体（12）和高压贮气体（11）相连，低压贮气体（12）内的低压气体与高压贮气体（11）内的高压气体分别流经对压气能发动机（2），以驱动对压气能发动机（2）的转轴（21）旋转；动力装置（3），其与对压气能发动机（2）的转轴相连，动力装置（3）通过对压气能发动机（2）驱动。该对压气能动力系统以对压气能作为热功能循环系统的基础能源，通过对压气能发动机（2）将对压气能转变为机械转矩能量，以驱动动力装置工作，或用以驱动发电机产生电能。还公开了一种对压气能动力方法。

Description

对压气能动力系统及动力方法 技术领域
本发明有关于一种气能动力系统及动力方法，尤其有关于一种气体能源应用领域中的对压气能动力系统及动力方法。
背景技术
随着人类文明由工业文明向着生态文明的发展，人类对地球环境的保护行动日益加强，可再生、低排放、甚至零排放的生态友好型的动力方法的开发和利用日益得到高度的重视和持续的努力。
工业文明早期，是蒸汽机的时代。到了十九世纪，由于能源的利用率，动力效率诉求，发展到极盛的蒸汽机被内燃机永久地取代，出现了第二次动力革命。至今，内燃机也是工业化高度成熟、能效利用率高度完善的主流动力方法，为人类的工业文明的发展做出了划时代的贡献。
然而，无论蒸气机还是内燃机都天生存在能源利用率低，环境不友好物质的大量排放等问题。
发明内容
本发明的目的是提供一种对压气能动力系统，通过对压气能发动机将对压气能转变为机械转矩，进而产生转动能量而生产机械能，以驱动动力装置工作。
本发明的另一目的是提供一种对压气能动力方法，以对压气能作为热功能循环系统的基础能源，将对压气能转变为机械转矩，进而产生转动能量而生产机械能，以驱动动力装置工作。
本发明提供了一种所述对压气能动力系统，其包括：
对压气能贮存装置，其具有高压贮气体和低压贮气体，所述高压贮气体中填充有高压气体，所述低压贮气体中填充有低压气体，所述对压气能贮存装置具有对压气能；
对压气能发动机，其分别与所述低压贮气体和所述高压贮气体相连，所述低压贮气体内的低压气体与所述高压贮气体内的高压气体分别流经所述对压气能发动机，以驱动所述对压气能发动机的转轴旋转；
动力装置，其与所述对压气能发动机的转轴相连，所述动力装置通过所述对压气 能发动机驱动。
本发明还提供了一种对压气能动力方法，其包括如下步骤：提供填充有高压气体的高压贮气体和填充有低压气体的低压贮气体，所述低压贮气体与所述高压贮气体之间具有对压气能，将所述对压气能以等温、等容的热工循环做功方式释放以驱动外部动力装置。
本发明的有益效果是：该对压气能动力系统的气体工质的做功过程为等容等温的热工运动过程，其显著的特点是：工质零排放；能量转换效率高；机构运行部件结构简单；提升了气动系统的可靠性；降低了运行过程的维护成本。本发明能使用传统的、可再生的能源；能效，体积，时空场所，以及必须资源的利用率更高；实现全动力周期中非环境友好物质的净零排放；建设，运行，维护的总体成本更低；对现有的动力工业链和制程材料上有最大的继承性，技术上有最小的过渡性。
附图说明
下面结合附图对本发明的实施例作进一步描述：
图1本发明的对压气能动力系统的结构示意图。
图2为本发明的对压气能贮存装置的可选实施例的结构示意图。
图3至图5为本发明的对压气能差动转子稳压阀的一可选实施例的结构示意图。
图6至图8为本发明的对压气能差动转子稳压阀的另一可选实施例的结构示意图。
图9为本发明的对压气能发动机(也即三角旋转活塞气压机或发动机)的一可选实施例的结构示意图。
图10为本发明的对压气能发动机(也即三角旋转活塞气压机或发动机)的另一可选实施例的结构示意图。
图11为图10所示实施例的三角旋转活塞发动机的三角旋转活塞处于不同转动位置处的结构示意图。
图12为本发明的对压气能发动机(也即旋缸三角活塞气压机或发动机)的再一可选实施例的结构示意图。
图13为本发明的三角活塞的内腔的结构示意图。
图14为本发明的活塞柱(即第一输气活塞、第二输气活塞或第三输气活塞)的结构示意图。
图15为图12所示实施例的旋缸三角活塞发动机的三角活塞处于不同转动位置处的 结构示意图。
图16为本发明的对压气能发动机(也即两弧旋转活塞气压机或发动机)的一可选实施例的结构示意图。
图17为本发明的对压气能发动机(也即两弧旋转活塞气压机或发动机)的另一可选实施例的结构示意图。
图18和图19分别为图16和图17中的两弧旋转活塞气压机或发动机上设有电磁体或永磁体的可选实施例的结构示意图。
图20为本发明的转子气阀机构与气阀杆的结构示意图。
图21为本发明的对压气能发动机(也即三弧旋转活塞气压机或发动机)的一可选实施例的结构示意图。
图22为本发明的对压气能发动机(也即四弧旋转活塞气压机或发动机)的一可选实施例的结构示意图。
图23为图16所示实施例的两弧旋转活塞发动机的两弧转子处于不同转动位置处的结构示意图。
图24为图16所示实施例的两弧旋转活塞气压机的两弧转子处于不同转动位置处的结构示意图。
图25为本发明应用于对压气能储能系统的实例。
图26为本发明应用于对压气能车辆的实例。
图27为本发明应用于对压气能储能电站的实例。
具体实施方式
下面将结合本发明实施例中的附图，对本发明实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本发明一部分实施例，而不是全部的实施例。基于本发明中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例，都属于本发明保护的范围。
如图1所示，本发明提供了一种对压气能动力系统，其包括对压气能贮存装置1、对压气能发动机2和动力装置3，其中：对压气能贮存装置1具有高压贮气体11和低压贮气体12，所述高压贮气体11中填充有高压气体，所述低压贮气体12中填充有低压气体，所述对压气能贮存装置1贮存有对压气能；对压气能发动机2分别与所述低压贮气体12和所述高压贮气体11相连，所述低压贮气体12内的低压气体与所述高压贮气体11内的高压气 体分别流经所述对压气能发动机2，以驱动所述对压气能发动机2的转轴21旋转；动力装置3与所述对压气能发动机2的转轴21相连，所述动力装置3通过所述对压气能发动机2得以驱动。
在一可行实施例中，该对压气能贮存装置1由一对各自封闭的气缸组成，一个气缸(也即高压贮气体11)内填充有高压气体，另一气缸(也即低压贮气体12)内填充有低压气体。
在另一可行实施例中，如图2所示，该对压气能贮存装置1包括内体13和套设在内体13外的外体14，该内体13中填充有第一气体，该外体14与内体13之间形成的腔体15中填充有第二气体，第一气体与第二气体之间具有压强差，也即气能压差。在一具体实施例中，所述的内体13可为高压贮气体11，内体13中的第一气体为高压气体，所述的腔体15为低压贮气体12，腔体15中的第二气体为低压气体；或者，在另一具体实施例中，所述的内体13为低压贮气体12，内体13中的第一气体为低压气体，所述的腔体15为高压贮气体11，腔体15中的第二气体为高压气体。其中，当该对压气能贮存装置1位于地面上时，此时的内体13为高压贮气体11，该腔体15为低压贮气体12；当该对压气能贮存装置1位于水下或地下时，由于水下或地下压力环境为高压，此时的内体13为低压贮气体12，该腔体15为高压贮气体11，利于减轻外体14壁上的应力，抵消外体14的收缩压力。
在本发明中，该高压气体的压强大于低压气体的压强，该高压气体与低压气体之间具有气能压差，该气能压差即为所述的对压气能。其中，该高压气体的压强可为0.1MPa～100MPa，低压气体的压强可为100Pa～30MPa。进一步的，该高压气体和低压气体可选择空气、或氮气、或氦气、或其它气体的混合体；其中，该其它气体的混合体，例如可为氮气与氦气的混合体等。
根据本发明的一个实施方式，如图1所示，在一可行实施例中，该对压气能发动机2可为多个，多个对压气能发动机2串联连接于动力装置3与对压气能贮存装置1之间，例如，根据实际需要，在动力装置3与对压气能贮存装置1之间可连接有两个、三个或更多数量的对压气能发动机2，在此不作限制。当然，在另一可行实施例中，在动力装置3与对压气能贮存装置1之间可仅连接有一个对压气能发动机2。
根据本发明的一个实施方式，该对压气能发动机2与对压气能贮存装置1之间连接有回热器4，该回热器4用于对流出高压贮气体11的气体与流入低压贮气体12内的气体进行冷热量交换。
具体的，该回热器4内可设有蛇形或螺旋形盘绕的双管道，其中一个管道内流入高 压气体，另一管道内流入低压气体，通过外表面相互接触的双管道，使各管道内的热量可相互交换，也即，从高压贮气体11内排出气体时产生的冷量与气体被压缩入低压贮气体12时产生的热量进行交换，从而达到在气体释放和膨胀过程中，总体的冷量和热量在回热器4中得以平衡地补偿而抵消。
因此，本发明的对压气能动力系统的工作过程如下：对压气能贮存装置1的高压贮气体11内的高压气体经回热器4流入对压气能发动机2内，从而使对压气能发动机2的转轴21旋转而带动动力装置3工作；在对压气能发动机2内的高压气体做功后气体压强降低，而后排入对压气能贮存装置1的低压贮气体12内。上述过程可持续进行，直至高压贮气体11中的气体压力等于低压贮气体12中的气体压力，即高压贮气体11内的气体与低压贮气体12内的气体压差等于零为止。
本发明的对压气能动力系统，其封闭气体工质的做功过程为等容等温的热工运动过程，其显著的特点是：工质零排放；能量转换效率高；机构运行部件结构简单；提升了气动系统的可靠性；没有耗材；降低了运行过程的维护成本。
根据本发明的一个实施方式，在回热器4与对压气能贮存装置1之间设有对压气能差动转子稳压阀5，该对压气能差动转子稳压阀5用于将低压贮气体12的进口气源的压力减至某一需要的出口气源压力，并能依靠气源工质本身的能量，使高压贮气体11的出口气源压力自动保持稳定。也即，该对压气能差动转子稳压阀5用于将流出对压气能发动机2的气源压力减压至低压贮气体12的进口气源压力，将流出高压贮气体11的出口气源压力减压至对压气能发动机2需要的进口气源压力，并能依靠对压气能发动机2气源工质本身的压差和对压气能差动转子稳压阀5中的弹簧552或扭簧5531，使对压气能发动机2进出气源工质压力差自动保持稳定。
具体的，如图3所示，该对压气能差动转子稳压阀5包括第一管道51、第二管道52、差动气缸53和联动机构54，其中：第一管道51的一端511与高压贮气体11相连，其另一端512与对压气能发动机2相连，该第一管道51的一端511内可转动地设有第一转子气阀513，该第一转子气阀513具有第一转子气阀通道5131；第二管道52的一端521与低压贮气体12相连，其另一端522与对压气能发动机2相连，该第二管道52的一端521内可转动地设有第二转子气阀523，该第二转子气阀523具有第二转子气阀通道5231；差动气缸53连接在第一管道51的另一端512与第二管道52的另一端522之间，该差动气缸53内可移动地设有差动活塞531，该差动气缸53通过差动活塞531分为第一气缸532和第二气缸533，该第一气缸532与第一管道51相连通，该第二气缸533与第二管道52相连通；联动机构54 与差动活塞531相连，该联动机构54能根据差动活塞531的移动而带动第一转子气阀513、第二转子气阀523旋转。
进一步的，该对压气能差动转子稳压阀5还包括驱动机构55，该驱动机构55能驱动差动活塞531在差动气缸53内移动。
在驱动机构55的一可行实施例中，如图3至图5所示，该驱动机构55包括连接杆551和弹簧552，该连接杆551的一端与弹簧552相连，该连接杆551的另一端与差动活塞531相连；联动机构54包括第一联动杆541和第二联动杆542，第一联动杆541的两端分别与连接杆551、第一转子气阀513可转动地相连，第二联动杆542的两端分别与连接杆551、第二转子气阀523可转动地相连。
该实施例中的对压气能差动转子稳压阀5的工作过程如下：
如图3所示，当差动活塞531位于差动气缸53的一端时，第一转子气阀513和第二转子气阀523处于封闭第一管道51和第二管道52的状态，高压贮气体11与第一管道51不连通，低压贮气体12与第二管道52不连通，该对压气能差动转子稳压阀5处于无输出状态，弹簧552处于松弛状态；
如图4所示，当弹簧552在外力(如脚踏动作)的作用下推动连接杆551时，也即连接杆551带动差动活塞531从差动气缸53的一端向差动气缸53的另一端移动时，第一转子气阀513和第二转子气阀523在联动机构54的作用下，会随着差动活塞531的移动而转动，从而使得第一转子气阀513的第一转子气阀通道5131逐渐转动至与第一管道51连通，第二转子气阀523的第二转子气阀通道5231逐渐转动至与第二管道52连通，也即，在第一转子气阀通道5131与第一管道51相连通的状态下，第二转子气阀通道5231与第二管道52相连通，此时，高压贮气体11与第一管道51连通，低压贮气体12与第二管道52连通。在此状态下，由于第一管道51的另一端512与差动气缸53的第一气缸532相连通，因此，自高压贮气体11流入第一管道51内的高压气体会流入第一气缸532内；另外，由于第二管道52的另一端522与差动气缸53的第二气缸533相连通，因此，自对压气能发动机2流入第二管道52内的气体会流入第二气缸533内，差动活塞531的两侧分别受到不同压力的气流作用，为保持压力平衡，差动活塞531会自动地在差动气缸53内移动，直至弹簧552的张力与差动活塞531受到的差动压力取得平衡，差动活塞531停止移动。
当第一管道51的另一端512的气体压力或第二管道52的另一端522的气体压力波动而增大时，会造成差动气缸53的第一气缸532、第二气缸533之间的压差增大，此时，差动活塞531因感应到差动推力大于弹簧552的张力而向第二气缸533的方向运动，从而通 过联动机构54使得第一转子气阀513、第二转子气阀523朝着关闭第一管道51、第二管道52的方向转动。这一负反馈的作用使得第一管道51的另一端512的气体压力和第二管道52的另一端522的气体压力同时趋于减少，使得气体的压力基本又回到原来值。
当第一管道51的另一端512的气体压力或第二管道52的另一端522的气体压力波动而减少时，会造成差动气缸53的第一气缸532、第二气缸533之间的压差减少，差动活塞531因感应到差动推力小于弹簧552的张力而向第一气缸532的方向运动，从而通过联动机构54使得第一转子气阀513、第二转子气阀523朝着开启第一管道51、第二管道52的方向转动。这一负反馈的作用使得第一管道51的另一端512的气体压力和第二管道52的另一端522的气体压力同时趋于增加，使得气体的压力基本又回到原来值。
如图5所示，此时，对压气能差动转子稳压阀5处于最大输出状态。
在驱动机构55的另一可行实施例中，如图6至图8所示，该驱动机构55包括驱动齿轮553和分别与驱动齿轮553相啮合的两个被动齿轮554，两个被动齿轮554分别连接在第一转子气阀513和第二转子气阀523上，该驱动齿轮553内设有扭簧5531；联动机构54包括第一联动杆541和第二联动杆542，第一联动杆541的两端分别与第一转子气阀513、差动活塞531可转动地相连，第二联动杆542的两端分别与第二转子气阀523、差动活塞531可转动地相连。
该实施例中的对压气能差动转子稳压阀5的工作过程与上述可行实施例中的对压气能差动转子稳压阀5的工作过程类似，在此不再赘述。在该实施例中，在外力驱动差动活塞531时，该差动活塞531的运动是依靠旋转驱动齿轮553，以分别带动连接在第一转子气阀513和第二转子气阀523上的两个被动齿轮554转动，并根据第一转子气阀513和第二转子气阀523的转动而通过第一联动杆541和第二联动杆542带动差动活塞531运动。当第一管道51的另一端512的气体压力或第二管道52的另一端522的气体压力有波动时，第一转子气阀513的转动和第二转子气阀523的转动是通过差动活塞531带动联动机构54实现的。
根据本发明的一个实施方式，该对压气能发动机2为三角旋转活塞气压机或发动机，其具有缸体22和可转动地设置在缸体22内的三角旋转活塞23，该三角旋转活塞23的横截面为三角形，缸体22上设有连接对压气能贮存装置1的多个进出气口。
具体的，在一可行实施例中，如图9所示，该对压气能发动机2的转轴21与三角旋转活塞23相连；如图10所示，在另一可行实施例中，该三角旋转活塞气压机或发动机还具有动力齿轮轴24，该动力齿轮轴24穿设在三角旋转活塞23内，三角旋转活塞23的内周壁 设有与动力齿轮轴24相配合的啮合凸齿234，对压气能发动机2的转轴21与动力齿轮轴24相连，该三角旋转活塞23的轴心与动力齿轮轴24的轴心具有一定距离，该三角旋转活塞23能绕动力齿轮轴24进行偏心旋转。
进一步的，该缸体22的横截面大体呈长椭圆形，该三角旋转活塞23的横截面大体呈三角形，该三角旋转活塞23的三个侧壁分别设计为稍向外凸出的弧形形状，该三角旋转活塞23具有与缸体22内壁滑动接触的第一端角231、第二端角232和第三端角233，该第一端角231、第二端角232和第三端角233沿顺时针依次设置，该缸体22内通过第一端角231、第二端角232和第三端角233分割为第一内腔221、第二内腔222和第三内腔223，第一端角231与第二端角232之间的缸体22的内腔为第一内腔221，第二端角232与第三端角233之间的缸体22的内腔为第二内腔222，第三端角233与第一端角231之间的缸体22的内腔为第三内腔223；缸体22上的多个进出气口包括两个第一气口224和两个第二气口225，缸体22的相对两侧分别设有一个第一气口224和一个第二气口225，位于缸体22一侧的第一气口225与位于缸体22另一侧的第二气口225相对设置。
在该三角旋转活塞气压机或发动机的一可行实施例中，该第一气口224与高压贮气体11相连，该第二气口225与低压贮气体12相连，该对压气能发动机2为三角旋转活塞发动机。在第一气口224分别与第一内腔221、第二内腔222或第三内腔223相连通的状态下，三角旋转活塞23在流入第一气口224的高压气体的推动下而相对缸体22旋转；在第二气口225分别与第一内腔221、第二内腔222或第三内腔223相连通的状态下，根据三角旋转活塞23的旋转，第一内腔221内的气体、第二内腔222内的气体或第三内腔223内的气体排出第二气口225。
具体的，请配合参阅图11所示，图中绘制出了动力齿轮轴24顺时针旋转一圈(也即旋转360°)的过程中，三角旋转活塞23在缸体22内的各位置状态以及两个第一气口224、两个第二气口225进出气的示意图，图中三角旋转活塞23上的箭头为三角旋转活塞23相对缸体22的旋转方向，位于第一气口224、第二气口225的空心箭头分别表示进气和出气。图11中共分为六个位置状态：A位置状态，此时三角旋转活塞23和动力齿轮轴24均相对于缸体22处于0°坐标位置处；B位置状态，此时三角旋转活塞23相对缸体22旋转至20°坐标位置处，动力齿轮轴24相对缸体22旋转至60°坐标位置处；C位置状态，此时三角旋转活塞23旋转至40°坐标位置处，动力齿轮轴24旋转至120°坐标位置处；D位置状态，此时三角旋转活塞23旋转至60°坐标位置处，动力齿轮轴24旋转至180°坐标位置处；E位置状态，此时三角旋转活塞23旋转至80°坐标位置处，动力齿轮轴24旋转至240°坐标 位置处；F位置状态，此时三角旋转活塞23旋转至100°坐标位置处，动力齿轮轴24旋转至300°坐标位置处。
在A位置状态时，请参见图中空心箭头所示，位于缸体22一侧的第一气口224封闭，位于缸体22另一侧的第一气口224处于进气状态，位于缸体22另一侧的第二气口225封闭，位于缸体22一侧的第二气口225处于出气状态；此时第一内腔221由于通过第一气口224接通高压贮气体11，该第一内腔221中充入高压气体，而第二内腔222由于通过第二气口225与低压贮气体12接通，此时第二内腔222中的气体会排入低压贮气体12内，这是由于第一内腔221和第二内腔222中所形成的压差产生的径向偏心推力能推动三角旋转活塞23顺时针转动，同时低压贮气体12内的压力小于第二内腔222中的压力，在第二气口225的方向处形成径向偏心吸引力，而使三角旋转活塞23顺时针转动；而此时第三内腔223中无气体进出，其对于三角旋转活塞23的偏心力距为零，不产生对三角旋转活塞23的旋转推力。当从A位置状态运动至B位置状态时，三角旋转活塞23顺时针转动了20°，动力齿轮轴24被带动顺时针转动了60°，在B位置状态时，与A位置状态不同的是，第三内腔223旋转至与位于缸体22另一侧的第二气口225接通，此时第三内腔223中的气体会排入低压贮气体12内，同时形成径向偏心吸引力，使三角旋转活塞23继续获得顺时针旋转的力。当从B位置状态运动至C位置状态时，三角旋转活塞23顺时针转动了40°，动力齿轮轴24被带动顺时针转动了120°；此时，由于第一内腔221仍然通过位于缸体22另一侧的第一气口224接通高压贮气体11，该第一内腔221中继续充入高压气体，而位于缸体22一侧的第二气口225已被三角旋转活塞23封堵，该第二内腔222旋转至与缸体22一侧的第一气口224连通，此时，第二内腔222中通入高压气体；同时，第三内腔223仍然处于与位于缸体22另一侧的第二气口225连通的状态，其内的气体会通过第二气口225排入低压贮气体12内。当处于D位置状态时，三角旋转活塞23顺时针转动了60°，动力齿轮轴24被带动顺时针转动了180°；此时，三角旋转活塞23的第一端角231转过位于缸体22另一侧的第一气口224，三角旋转活塞23的第二端角232还未转过位于缸体22一侧的第二气口225，此时，第一内腔221处于无气体进出状态，第二内腔222仍然处于与位于缸体22一侧的第一气口224连通的状态，第二内腔222中继续充入高压气体，而第三内腔223也处于与位于缸体22另一侧的第二气口225连通的状态，第三内腔223中的气体继续通过第二气口225排入低压贮气体12内。当经过E位置状态和F位置状态时，三角旋转活塞23顺时针分别转动了80°和100°，动力齿轮轴24分别被带动顺时针转动了240°和300°；此时，第一内腔221旋转至与位于缸体22一侧的第二气口225连通，第一内腔221中的气体 通过第二气口225排入低压贮气体12内，第二内腔222仍然处于与位于缸体22一侧的第一气口224连通的状态，第二内腔222中继续充入高压气体，第三内腔223从与位于缸体22另一侧的第二气口225连通的状态旋转至与位于缸体22另一侧的第一气口224连通的状态。最后再次回到A位置状态。结果是，该动力齿轮轴24共顺时针旋转了360°，三角旋转活塞23共旋转了120°，该第一内腔221、第二内腔222和第三内腔223分别完成了一次完整的进气冲程或排气冲程；当三角旋转活塞23旋转360°后，该第一内腔221、第二内腔222和第三内腔223分别完成了三次完整的进气冲程与排气冲程，而每一个冲程都能对三角旋转活塞23做功，动力齿轮轴24共完成了三个360°的顺时针旋转。
在三角旋转活塞气压机或发动机的另一可行实施例中，第一气口224与低压贮气体12相连，第二气口225与高压贮气体相连11，对压气能发动机2为三角旋转活塞气压机。根据三角旋转活塞23的旋转，低压贮气体12内的低压气体通过第一气口224分别流入第一内腔221、第二内腔222或第三内腔223中，在外部动力装置带动转轴21旋转而带动三角旋转活塞23旋转的过程中，第一内腔221中的低压气体、第二内腔222中的低压气体或第三内腔223中的低压气体分别通过第二气口225被压缩入高压贮气体内11。
该实施例的三角旋转活塞气压机与上述实施例的三角旋转活塞发动机的工作过程恰好相反，其具体工作过程在此不再赘述。此实施例的三角旋转活塞气压机的三角旋转活塞23是在对压气能发动机2的转轴21的带动下而相对缸体22逆时针旋转，以将低压贮气体12内的低压气体压缩入高压贮气体内11，以使低压贮气体12与高压贮气体内11之间形成对压气能差，该对压气能贮存装置1内形成对压气能。
在本发明中，该三角旋转活塞23与缸体22的三个接触处各设置了两个滚条，形成一滚条组220。如图9和图10所示，该滚条组220包括内滚条25和外滚条26，该外滚条26的横截面形状仅为圆形，内滚条25的横截面形状可为圆形，或长方形，或其他形状。其中，第一端角231、第二端角232和第三端角233内分别设有两个滚条，两个滚条分别为内滚条25和外滚条26，外滚条26可滚动地设置在内滚条25和缸体22的内壁之间。
具体的，在本实施例中，该内滚条25可为圆柱杆或簧圈；该外滚条26为圆柱杆，以实现三角旋转活塞23与缸体22内壁的滑动接触。
在本发明的一实施方式中，如图12所示，该对压气能发动机2为对压气能旋缸三角活塞气压机或发动机，其具有可转动的缸体22和设置在所述缸体22内的不转动的三角活塞23'，该三角活塞23'的横截面为三角形，该三角活塞23'上设有连接对压气能贮存装置1的第一气口235和第二气口236，该三角活塞23'的内腔能与缸体22的内腔相连通。
具体的，该缸体22的横截面大体呈长椭圆形，该三角活塞23'的横截面大体呈三角形，该三角活塞23'的三个侧壁分别设计为稍向外凸出的弧形形状，该三角活塞23'具有与缸体22内壁滑动接触的第一端角231、第二端角232和第三端角233，该第一端角231、第二端角232和第三端角233沿顺时针依次设置，缸体22内通过第一端角231、第二端角232和第三端角233分割为第一内腔221、第二内腔222和第三内腔223，第一端角231与第二端角232之间的缸体22的内腔为第一内腔221，第二端角232与第三端角233之间的缸体22的内腔为第二内腔222，第三端角233与第一端角231之间的缸体22的内腔为第三内腔223。
进一步的，如图13所示，对压气能发动机2的转轴21与缸体22相连；三角活塞23'的内腔包括第一活塞内腔237和第二活塞内腔238，第一活塞内腔237与第一气口235相连通，第二活塞内腔238与第二气口236相连通。该三角活塞23'上设有第一输气活塞271、第二输气活塞272和第三输气活塞273，第一输气活塞271、第二输气活塞272和第三输气活塞273沿顺时针方向依次上设置，该第一输气活塞271与第一内腔221相对设置，第二输气活塞272与第二内腔222相对设置，第三输气活塞273与第三内腔223相对设置。
如图14所示，该第一输气活塞271、第二输气活塞272和第三输气活塞273均为可轴向转动地设置在三角活塞上的活塞柱27，该活塞柱27沿其轴向方向间隔设有相互平行的多个第一通道274，两两相邻的第一通道274之间设有第二通道275，第二通道275与第一通道274之间具有夹角，在一可行实施例中，第一通道274与第二通道275相互垂直设置，也即第二通道275与第一通道274之间的夹角为90°。
配合参阅图13所示，三角活塞23'由内筒231'和套设在内筒231'外的外筒232'组成，其中，内筒231'的内腔为该第一活塞内腔237，外筒232'与内筒231'之间形成的环空为第二活塞内腔238，该第一活塞内腔237能通过多个第一通道274分别与第一内腔221、第二内腔222或第三内腔223相连通，该第二活塞内腔238能通过多个第二通道275分别与第一内腔221、第二内腔222或第三内腔223相连通。在本发明中，内筒231'的侧壁上沿圆周方向开设有三列侧腔通道2371，每列侧腔通道2371包括轴向间隔设置的多个侧腔口2372，侧腔口2372的位置被设置为与第一通道274相对连通；外筒232'的侧壁上沿圆周方向开设有三列侧腔通道2381，每列侧腔通道2381包括轴向间隔设置的多个侧腔口2382，侧腔口2382的位置被设置为与第二通道275相对连通。
请配合参阅图12所示，缸体22轴心处设有齿轮轴239，缸体22内壁的相对两侧分别设有内凸齿226，各活塞柱27上均设有传动齿276，传动齿276能与齿轮轴239、内凸齿226传动配合，从而在齿轮轴239及内凸齿226的带动下转动传动齿276，带动活塞柱27的转 动，达到气流可两个方向通过活塞柱27的目的。
如图15所示，在对压气能发动机2的一可行实施例中，该第一气口235与高压贮气体11相连，第二气口236与低压贮气体12相连，对压气能发动机2为旋缸三角活塞发动机。在第一气口235分别与第一内腔221、第二内腔222或第三内腔223相连通的状态下，自第一气口235通入的高压气体能分别流入第一内腔221、第二内腔222或第三内腔223中，缸体22在高压气体的推动下而相对三角活塞23'旋转；在第二气口236分别与第一内腔221、第二内腔222或第三内腔223相连通的状态下，根据缸体22的旋转，第一内腔221中的气体、第二内腔222中的气体或第三内腔223的气体能分别排出第二气口236。
具体的，请配合参阅图15所示，图中绘制出了缸体22旋转180°的过程中，三角活塞23'上的第一输气活塞271、第二输气活塞272和第三输气活塞273的进出气的状态，图中缸体22内的弧形箭头表示缸体22旋转的方向。图15中共分为六个位置状态：A位置状态，此时缸体22处于0°坐标位置处；B位置状态，此时缸体22相对三角活塞23'旋转至30°坐标位置处；C位置状态，此时缸体22相对三角活塞23'旋转至60°坐标位置处；D位置状态，此时缸体22相对三角活塞23'旋转至90°坐标位置处；E位置状态，此时缸体22相对三角活塞23'旋转至120°坐标位置处；F位置状态，此时缸体22相对三角活塞23'旋转至150°坐标位置处。
在A位置状态时，缸体22相对于三角活塞23'处于0°位置处；第二输气活塞272处于封闭状态，也即其不连通三角活塞23'的内腔与第二内腔222；此时，第三输气活塞273的第二通道275与第二活塞内腔238连通，该第二活塞内腔238与连接低压贮气体12的第二气口236相连通，第三内腔223中的气体能排出第二气口236；同时，第一输气活塞271的第一通道274与第一活塞内腔237连通，该第一活塞内腔237与连接高压贮气体11的第一气口235相连通，第一内腔221中充入高压气体，此时在缸体22与三角活塞23'之间所形成的气能压差产生的径向偏心推力能推动缸体22作逆时针转动。在缸体22运动至B位置状态时，缸体22相对三角活塞23'转动了30°；第二输气活塞272在缸体22内凸齿226的作用下旋转，其第一通道274旋转至与第一活塞内腔237连通，第二内腔222充入高压气体；此时，第三输气活塞273的第二通道275仍然与第二活塞内腔238连通，第三内腔223中的气体继续排出第二气口236；而第一输气活塞271在齿轮轴239的带动下旋转至封闭状态。在缸体22运动至C位置状态时，缸体22相对三角活塞23'转动了60°；此时，第一输气活塞271在齿轮轴239的带动下旋转至与第一活塞内腔237连通的状态，第一内腔221中的气体会排出第二气口236；第二输气活塞272的第一通道274仍然与第一活塞内腔237连通， 第二内腔222中继续充入高压气体；此时，第三输气活塞273在缸体22的内凸齿226的带动下旋转至封闭状态。在缸体22运动至D位置状态时，缸体22相对三角活塞23'转动了90°；第二输气活塞272在齿轮轴239的带动下旋转至封闭状态，位于第二内腔222中的气体不会对缸体22的旋转进行做功；第三输气活塞273在缸体22内凸齿226的带动下旋转至其第一通道274与第一活塞内腔237连通，第三内腔223中充入高压气体；此时，第一输气活塞271的第二通道275仍然与第二活塞内腔238连通，第一内腔221中的气体会排出第二气口236。在缸体22运动至E位置状态时，缸体22相对三角活塞23'转动了120°；第一输气活塞271在缸体22内凸齿226的带动下旋转至封闭状态；第三输气活塞273的第一通道274仍然与第一活塞内腔237连通，第三内腔223中继续充入高压气体；此时，第二输气活塞272在齿轮轴239的带动下旋转至其第二通道275与第二活塞内腔238连通，第二内腔222中的气体会排出第二气口236。在缸体22运动至F位置状态时，缸体22相对三角活塞23'转动了150°；第三输气活塞273在齿轮轴239的带动下旋转至封闭状态；第一输气活塞271在缸体22内凸齿226的带动下旋转至其第一通道274与第一活塞内腔237连通，第一内腔221中充入高压气体；此时，第二输气活塞272的第二通道275仍然与第二活塞内腔238连通，第二内腔222中的气体会排出第二气口236，此时在第二内腔222与第一内腔221之间的气能压差作用下，缸体22继续逆时针旋转至A位置状态。结果是，缸体逆时针转动了180°，第一内腔221、第二内腔222和第三内腔223各自完成了完整的进气过程和出气过程，即三个气缸各自完成了完整的进气冲程和排气冲程，而每一个冲程都能对气缸的转动做功。
在对压气能发动机2的一可行实施例中，该第一气口235与低压贮气体12相连，第二气口236与高压贮气体11相连，对压气能发动机2为旋缸三角活塞气压机。该低压贮气体内12的低压气体能通过第一气口235分别流入第一内腔221、第二内腔222或第三内腔223内，在第一内腔221、第二内腔222或第三内腔223分别与第二气口236相连通的状态下，第一内腔221中的气体、第二内腔222中的气体或第三内腔223中的气体能分别通过第二气口236被压缩入高压贮气体11内。
该实施例的旋缸三角活塞气压机与上述实施例的旋缸三角活塞发动机(图12所示实施例)的工作过程恰好相反，其具体工作过程在此不再赘述。此实施例的旋缸三角活塞气压机的缸体22是在对压气能发动机2的转轴21的带动下而相对三角活塞23'顺时针旋转，以将低压贮气体12内的低压气体压缩入高压贮气体内11，以使低压贮气体12与高压贮气体内11之间形成气压差，该对压气能贮存装置1内形成对压气能。
根据本发明的一个实施方式，该对压气能发动机2为对压气能多弧旋转活塞气压机或发动机，其具有缸体22及可转动地设置在缸体22内的多弧转子28，多弧转子28具有沿圆周方向设置的多个弧形外壁281，缸体22具有沿圆周方向设置的多个弧形内壁227，弧形外壁281与弧形内壁227相互接触配合，缸体22上设有连接对压气能贮存装置1的多个进出气口，弧形外壁281的数量为n个，弧形内壁227的数量为n+1个，进出气口的数量为n+1个。
具体的，在一可行实施例中，请配合参阅图16、图18、图21和图22所示，该对压气能发动机2的转轴21与多弧转子28相连。在另一可行实施例中，请配合参阅图17和图19所示，该对压气能多弧旋转活塞气压机或发动机还具有动力齿轮轴24，动力齿轮轴24穿设在多弧转子28内，多弧转子28的内周壁设有与动力齿轮轴24相配合的啮合凸齿282，对压气能发动机2的转轴21与动力齿轮轴24相连。
进一步的，缸体22通过多弧转子28被分割为第一内腔221、第二内腔222和第三内腔223；缸体22上的多个进出气口能分别与第一内腔221、第二内腔222或第三内腔223相连通。
在本发明的一实施方式中，各所述进出气口均包括多个第一通道291和多个第二通道292。
在一可行实施例中，请配合参阅图16至图19、图21和图22所示，该第一通道291与高压贮气体11相连，该第二通道292与低压贮气体12相连，该对压气能发动机2为对压气能多弧旋转活塞发动机。
具体的，如图20所示，在各进出气口内可转动地设有气阀杆29，气阀杆29沿其轴向方向间隔具有相互平行的多个第一通道291，两两相邻的第一通道291之间设有第二通道292，第一通道291与第二通道292之间具有夹角；在本实施例中，该第一通道291与第二通道292相互垂直设置，也即第一通道291与第二通道292之间的夹角为90°。
进一步的，该多弧转子28上连接有转子气阀机构283，该转子气阀机构283用于打开或关闭各进出气口的多个第一通道291和多个第二通道292。该转子气阀机构283包括气阀转环2831，气阀转环2831沿其圆周方向设有多个长凸齿2832和多个短凸齿2833，两两相邻的短凸齿2833之间设有一个长凸齿2832；气阀杆29上连接有杆齿轮293，短凸齿2833、长凸齿2832能分别与杆齿轮293驱动相连，长凸齿2832的数量和短凸齿2833的数量分别为n+1个。
在另一可行实施例中，请配合参阅图24所示，该第一通道291与低压贮气体12相连， 该第二通道292与高压贮气体12相连，该对压气能发动机2为对压气能多弧旋转活塞气压机。
具体的，两两相邻的第一通道291之间设有第二通道292，多个第一通道291与多个第二通道292相互平行设置，第一通道291内设有第一单向阀2911，第二通道292内设有第二单向阀2921。当低压贮气体12内的气体通过第一通道291注入缸体22的内腔时，该第一单向阀2911可开启第一通道291，而不会使缸体22的内腔中的气体回流至低压贮气体12内；当缸体22内腔中的气体通过第二通道292压缩入高压贮气体11内时，该第二单向阀2922可开启第二通道292，而不会使高压贮气体11中的气体回流至缸体22的内腔。
图16至图19所示为本发明的多弧旋转活塞气压机或发动机的一个可行实施例，其中，多弧转子28为两弧转子，该两弧转子具有相对设置的两个弧形外壁281，也即n＝2；缸体22具有依次相连的三个弧形内壁227，该弧形外壁281与弧形内壁227相配合，该缸体22具有三个进出气口。在本实施例中，如图16、图17所示，该缸体22与多弧转子28的三个接触处各设置了两个滚条，形成一滚条组220。该滚条组220包括内滚条25和外滚条26，该外滚条26的横截面形状仅为圆形，内滚条25的横截面形状可为圆形，或长方形，或其他形状。
图21为本发明的多弧旋转活塞发动机的一个可行实施例，其中，多弧转子28为三弧转子，该三弧转子具有沿圆周方向设置的三个弧形外壁281，也即n＝3；缸体22具有依次相连的四个弧形内壁227，该弧形外壁281与弧形内壁227相配合，该缸体22具有四个进出气口。
图22为本发明的多弧旋转活塞发动机的一个可行实施例，其中，多弧转子28为四弧转子，该四弧转子具有沿圆周方向设置的四个弧形外壁281，也即n＝4；缸体22具有依次相连的五个弧形内壁227，该弧形外壁281与弧形内壁227相配合，该缸体22具有五个进出气口。
当然在其他的实施例中，该多弧旋转活塞气压机或发动机也可为具有五弧转子、六弧转子等的对压气能发动机，在此不作限制。
在本发明的一实施方式中，请配合参阅图18和图19所示，该缸体22上及多弧转子28上可分别设有电磁体或永磁体228。通过电磁体或永磁体228实现驱动多弧转子28在缸体22内旋转的目的。
下面以两弧旋转活塞气压机或发动机为例，说明其具体工作过程：
在一可行实施例中，请配合参阅图23所示，为两弧旋转活塞发动机的工作流程图， 图中绘制出了两弧转子相对缸体旋转0°至180°的过程中，三角旋转活塞23上的第一输气活塞271、第二输气活塞272和第三输气活塞273的进出气的状态。图23中共分为六个位置状态：A位置状态，此时两弧转子相对缸体22处于0°坐标位置处；B位置状态，此时两弧转子相对缸体22旋转至30°后的坐标位置；C位置状态，此时两弧转子相对缸体22旋转至60°后的坐标位置；D位置状态，此时两弧转子相对缸体22旋转至90°后的坐标位置；E位置状态，此时两弧转子相对缸体22旋转至120°后的坐标位置；F位置状态，此时两弧转子相对缸体22旋转至150°后的坐标位置。
在A位置状态时，两弧转子相对于缸体22位于0°位置处；与第二内腔222相对的气阀杆29的各气道处于封闭状态，第二内腔222中的气体不会对两弧转子的旋转进行做功；与第一内腔221相对的气阀杆29的多个第一通道291与高压贮气体11连通，第一内腔221中充入高压气体；此时，与第三内腔223相对的气阀杆29的第二通道292与低压贮气体12连通，第三内腔223中的气体能排入低压贮气体12内，在第一内腔221和第三内腔223中的气体压差作用下，两弧转子相对缸体22顺时针旋转。在B位置状态时，两弧转子相对于缸体22旋转至位于30°位置处；在转子气阀机构283的长凸齿2832的作用下，与第二内腔222相对的气阀杆29上的杆齿轮293被转动，该气阀杆29上的第二通道292与第二内腔222形成连通状态，第二内腔222中的气体会排入低压贮气体12内；此时，与第一内腔221相对的气阀杆29的多个第一通道291仍然处于与高压贮气体11连通的状态，第一内腔221中继续充入高压气体；而第三内腔223被两弧转子的其中一个弧形外壁281填充，且与该第三内腔223相对的气阀杆29的杆齿轮293被转子气阀机构283的短凸齿2833带动而转动至封闭状态，在第一内腔221和第二内腔222中的气体压差作用下，两弧转子相对缸体22继续顺时针旋转。在C位置状态时，两弧转子相对于缸体22旋转至位于60°位置处；在转子气阀机构283的短凸齿2833的作用下，与第三内腔223相对的气阀杆29上的杆齿轮293被转动，该气阀杆29上的第一通道291与第三内腔223形成连通状态，该第三内腔223中充入高压气体；此时，与第一内腔221相对的气阀杆29上的杆齿轮293被长凸齿2832转动，该气阀杆29处于封闭状态，第一内腔中221无气体进出；此时与第二内腔222相对的气阀杆29的多个第二通道292仍然处于与低压贮气体12连通的状态，第二内腔222中的气体能排入低压贮气体12内，在第三内腔223和第二内腔222中的气体压差作用下，两弧转子相对缸体22继续顺时针旋转。在D位置状态时，两弧转子相对于缸体22旋转至位于90°位置处；在转子气阀机构283的短凸齿2833的作用下，与第二内腔222相对的气阀杆29上的杆齿轮293被转动，该气阀杆29处于封闭状态；此时，与第一内腔221相对的气阀杆29 上的杆齿轮293被长凸齿2832转动后，该气阀杆29的第二通道292与第一内腔221连通，第一内腔221中的气体会排入低压贮气体12内；同时，与第三内腔223相对的气阀杆29的多个第一通道292仍然处于与高压贮气体11连通的状态，第三内腔223中继续充入高压气体，在第三内腔223和第一内腔221中的气体压差作用下，两弧转子相对缸体22继续顺时针旋转。在E位置状态时，两弧转子相对于缸体22旋转至120°位置处；在转子气阀机构283的短凸齿2833的作用下，与第二内腔222相对的气阀杆29上的杆齿轮293被转动，该气阀杆29的第一通道291与第二内腔222形成连通状态，第二内腔222中注入高压气体；此时，与第一内腔221相对的气阀杆29上的第二通道292仍然处于与第一内腔中221连通的状态，第一内腔221中的气体继续排入低压贮气体12内；同时，在转子气阀机构283的长凸齿2832的作用下，与第三内腔223相对的气阀杆29被旋转而处于封闭状态，在第二内腔222和第一内腔221中的气体压差作用下，两弧转子相对缸体22继续顺时针旋转。在F位置状态时，两弧转子相对于缸体22旋转至150°位置处；在转子气阀机构283的长凸齿2832的作用下，与第三内腔223相对的气阀杆29上的杆齿轮293被转动，该气阀杆29的第二通道292与第三内腔223形成连通状态，第三内腔223中的气体能排入低压贮气体12；此时，与第一内腔221相对的气阀杆29被短凸齿2833带动而转动至封闭状态，两弧转子的其中一个弧形外壁281进入第一内腔221中；同时，与第二内腔222相对的气阀杆29的第一通道291仍然处于与第二内腔222连通的状态，第二内腔222中继续充入高压气体，在第二内腔222和第三内腔223中的气体压差作用下，两弧转子相对缸体22继续顺时针旋转，最后回到A位置状态。结果是，两弧转子顺时针转动了180°，每个气缸完成了一次完整的进气冲程或排气冲程；在两弧转子顺时针转动360°后，三个气缸整体完成了两次完整的进气冲程与排气冲程，而每一个冲程都能对两弧活塞的转动做功。
请配合参阅图24所示，为两弧旋转活塞气压机的工作流程图，该实施例的两弧旋转活塞气压机与上述实施例的两弧旋转活塞发动机(图16所示实施例)的工作过程恰好相反，其具体工作过程在此不再赘述。此实施例的两弧旋转活塞气压机的两弧转子28是在对压气能发动机2的转轴21的带动下而相对缸体22逆时针旋转，以将低压贮气体12内的低压气体压缩入高压贮气体内11，以使低压贮气体12与高压贮气体内11之间形成对压气能差，该对压气能贮存装置1内形成对压气能。
根据本发明的一个实施方式，该动力装置3可为发电机、升降机、气动工具、车辆、轮船或飞行器。其中，对压气能发动机例如可为飞行器的气动机或发动机。
如图25所示的一可行实施例中，该系统包括五个串联连接的对压气能发动机(对压 气能发动机2a、对压气能发动机2b、对压气能发动机2c、对压气能发动机2d和对压气能发动机2e)和一个对压气能储存装置1。其中，该对压气能储存装置1与对压气能发动机2c相接，该对压气能发动机2c可为三角旋转活塞发动机或多弧旋转活塞发动机；对压气能发动机2a、对压气能发动机2b、对压气能发动机2d和对压气能发动机2e分别连接在对压气能发动机2c的转轴21上。
该实施例中，通过对压气能储存装置1带动对压气能发动机2c的转轴21旋转，从而带动与该转轴21相连的对压气能发动机2a、对压气能发动机2b、对压气能发动机2d和对压气能发动机2e启动，其中，对压气能发动机2a、对压气能发动机2b、对压气能发动机2d和对压气能发动机2e可分别为三角旋转活塞气压机或多弧旋转活塞气压机。通过压气能发动机2c产生机械转矩能而带动对压气能发动机2a、对压气能发动机2b、对压气能发动机2d和对压气能发动机2e工作。
该系统的对压气能气源来源于封闭的对压气能储存装置1，几乎任何地方都都不与外界环境的气体接触，整个气流的空间是有限、等容的；在储存增压中，各对压气能发动机相邻安置，使各对压气能发动机在作为气压机过程中产生的热量能够作为发动机过程中所需吸收的热量，热能在总量上正好相互得以完全互为补充；两种气压的输气管路并列安排，通过回热器4的散热安排，管路中的热能在总量上正好相互自然地得以完全互为补充，而无需额外的热能储存的恢复措施，体现了对压气能储能系统等温、等容压缩储能的优势。
如图26所示的一可行实施例中，该系统包括五个串联连接的对压气能发动机(对压气能发动机2f、对压气能发动机2g、对压气能发动机2h、对压气能发动机2i和对压气能发动机2j)和一个对压气能储存装置1。其中，该对压气能储存装置1与对压气能发动机2c相接，该五个对压气能发动机均为三角旋转活塞发动机或多弧旋转活塞发动机，五个对压气能发动机串联连接在转轴21上。
该系统是通过将对压气能储存装置1的高压贮气体11中的高压气体输送给对压气能发动机2j，做功后的气体压力得到降低，再输送给对压气能发动机2g，气体再次做过后输送给对压气能发动机2h，再次做功后的气体输送给对压气能发动机2i，最后输送至对压气能发动机2f，自压气能发动机2f排出的气体被输送至对压气能储存装置1中的低压贮气体12中。在五个对压气能发动机做功的过程中会带动转轴21旋转，从而带动连接在转轴21两侧的两个车轮61转动。
进一步的，该对压气能发动机2h还与另外两个对压气能发动机(对压气能发动机2k 和对压气能发动机2s)的气路相连通，从而使流经对压气能发动机2h的气体分别充入对压气能发动机2k和对压气能发动机2s中，以带动与压气能发动机2k相连的车轮62、与对压气能发动机2s相连的车轮63转动。这一过程直至高压贮气体11内的气体压强与低压贮气体12内的气体压强的压差为零而终止。
从热力学的观点来看，这是一个热、功、能的交换过程。为了使系统有较高的做功效率，通过将对压气能贮存装置1中的高压气体与低压气体，按等比压差，逐级释放给各对压气能发动机做功，由所产生的机械能带动车轮转动，气能释放中热、功、能的交换过程是基于等温，等容的减压过程，能够获得较高的交换效率。
该系统的气源来源于封闭的对压气能贮存装置1，几乎任何地方都不与外界环境的气体接触，整个气流的空间是有限、等容的；在释放气能做功中，各对压气能发动机相邻交错安置，热能在总量上正好相互得以互为补充；且两种气压的输气管路并列安排，通过回热器4的散热安排，管路中的热能在总量上正好相互自然地得以完全互为补充，而无需额外的热能储存的恢复措施，体现了对压气能动能系统等温、等容释能做功的优势。
如图27所示的一可行实施例中，该系统是电力网储能电站的实施例，是电能与对压气能贮存装置1中的对压气能与电网电能发生交换的系统，从热力学的观点来看，该系统是一个热、电量、对压气能的交换过程。为了使系统有较高的交换效率，通过将对压气能贮存装置1中的高压气体与低压气体，按等比压差安排减压或增压级数。在储存电能过程中，对压气能被逐级地增压到对压气能贮存装置1中，在恢复电能过程中，对压气能被逐级地从对压气能贮存装置1中减压而释放出电能来。对压气能的气压增压、释放中，热、电量、对压气能的交换过程是基于等温，等容的减压过程，能够获得较高的交换效率。
电力网的电能储存工况过程：与电力网连接的同步电机7被设置为同步电动机运行模式，将电网的电能转换为转轴21上的机械转矩能，从而带动转轴21上的六个对压气能发动机(对压气能发动机2m、对压气能发动机2n、对压气能发动机2t、对压气能发动机2p、对压气能发动机2q和对压气能发动机2r)，其中，对压气能发动机2m、对压气能发动机2n、对压气能发动机2t、对压气能发动机2p、对压气能发动机2q和对压气能发动机2r分别为三角旋转活塞气压机或多弧旋转活塞气压机，此时，交换阀81和交换阀82被设置为气压机输气模式。对压气能贮存装置1中的低压气体，一路经过交换阀81首先接入对压气能发动机2t，增压出来的气体再接入对压气能发动机2n，再增压出来的气体接入 对压气能发动机2m，最终增压出来的气体再次通过交换阀81送入对压气能贮存装置1中；另一路经过交换阀82接入对压气能发动机2p，增压出来的气体再接入对压气能发动机2q，再增压出来的气体接入对压气能发动机2r，最终增压出来的气体再次通过交换阀82送入对压气能贮存装置1中。这一过程的发展，使得对压气能贮存装置1中的气能压差，经过六级增压而逐渐增大，即对压气能的能量增加，意味着电能被转变为对压气能的形式逐渐地储存起来。
电力网的电能恢复工况过程：与电力网连接的同步电机7被设置为同步发电机运行模式，其中，对压气能发动机2m、对压气能发动机2n、对压气能发动机2t、对压气能发动机2p、对压气能发动机2q和对压气能发动机2r分别为三角旋转活塞发动机或多弧旋转活塞发动机；交换阀81和交换阀82被设置为发动机输气模式。对压气能贮存装置1中的高压气体，一路经过交换阀81首先接入对压气能发动机2m，减压出来的气体再接入对压气能发动机2n，再减压出来的气体接入对压气能发动机2t，最终减压出来的气体再次通过交换阀81送入对压气能贮存装置1中；另一路经过交换阀82接入对压气能发动机2r，减压出来的气体再接入对压气能发动机2q，再减压出来的气体接入对压气能发动机2p，最终减压出来的气体再次通过交换阀82送入对压气能贮存装置1中。六个对压气能发动机推动转轴21旋转，进而带动发电机7向电网发出电力。这一过程的发展，使得对压气能贮存装置1中的气能压差逐渐减小，意味着对压气能被转变为电能的形式逐渐地恢复出来。
该系统气源来源于封闭的对压气能贮存装置1，几乎任何地方都都不与外界环境的气体接触，整个气流的空间是有封闭等容的；在释放气能做功中，各对压气能发动机相邻交错安置，系统运行中所产生的热量和冷量在总量上正好相互得以完全互为补充；且两种气压的输气管路并列安排，通过回热器4的散热安排，管路中的热能在总量上正好相互自然地得以完全互为补充，而无需额外的热量和冷量的储存和恢复措施，体现了对压气能动能系统等温、等容结构的气能、电能交换方式的效率和成本优势。
如图1至图27所示，本发明还提供一种对压气能动力方法，其包括如下步骤：提供填充有高压气体的高压贮气体11和填充有低压气体的低压贮气体12，所述低压贮气体12与所述高压贮气体11之间具有对压气能，将所述对压气能以等温、等容的热工循环做功方式释放以驱动外部动力装置3。
其中，通过对压气能发动机2能实现将所述对压气能以等温、等容的热工循环做功方式释放，所述对压气能发动机的转轴与所述动力装置相连。
该实施方式的对压气能动力方法是采用本发明的对压气能动力系统实施的，对压气能动力系统的结构、工作原理和有益效果已在上文中详细说明，在此不再赘述。
最后说明的是，以上实施例仅用以说明本发明的技术方案而非限制，尽管参照较佳实施例对本发明进行了详细说明，本领域的普通技术人员应当理解，可以对本发明的技术方案进行修改或者等同替换，而不脱离本发明技术方案的宗旨和范围，其均应涵盖在本发明的权利要求范围当中。

Claims (51)

  1. 一种对压气能动力系统，其中，所述对压气能动力系统包括：
    对压气能贮存装置，其具有高压贮气体和低压贮气体，所述高压贮气体中填充有高压气体，所述低压贮气体中填充有低压气体，所述对压气能贮存装置具有对压气能；
    对压气能发动机，其分别与所述低压贮气体和所述高压贮气体相连，所述低压贮气体内的低压气体与所述高压贮气体内的高压气体分别流经所述对压气能发动机，以驱动所述对压气能发动机的转轴旋转；
    动力装置，其与所述对压气能发动机的转轴相连，所述动力装置通过所述对压气能发动机驱动。
  2. 如权利要求1所述的对压气能动力系统，其中，所述对压气能贮存装置包括内体和套设在所述内体外的外体，所述内体中填充有第一气体，所述外体与所述内体之间形成的腔体中填充有第二气体，所述第一气体与所述第二气体之间具有气压差，所述气压差为所述对压气能。
  3. 如权利要求2所述的对压气能动力系统，其中，所述内体为所述高压贮气体，所述外体与所述内体之间形成的腔体为所述低压贮气体；或所述内体为所述低压贮气体，所述外体与所述内体之间形成的腔体为所述高压贮气体。
  4. 如权利要求1所述的对压气能动力系统，其中，所述对压气能发动机为多个，多个所述对压气能发动机依次连接于所述动力装置与所述对压气能贮存装置之间。
  5. 如权利要求1所述的对压气能动力系统，其中，所述对压气能发动机与所述对压气能贮存装置之间连接有回热器，所述回热器用于对流出所述高压贮气体的气体与流入所述低压贮气体内的气体进行冷热量交换。
  6. 如权利要求5所述的对压气能动力系统，其中，所述回热器与所述对压气能贮存装置之间设有对压气能差动转子稳压阀，所述对压气能差动转子稳压阀用于将所述低压贮气体的进口气源的压力减至某一需要的出口气源压力，并能依靠气源工质本身的能量，使所述高压贮气体的出口气源压力自动保持稳定。
  7. 如权利要求6所述的对压气能动力系统，其中，所述对压气能差动转子稳压阀包括：
    第一管道，其一端与所述高压贮气体相连，其另一端与所述对压气能发动机相连，所述第一管道的一端内可转动地设有第一转子气阀，所述第一转子气阀具有第一转子气阀通道；
    第二管道，其一端与所述低压贮气体相连，其另一端与所述对压气能发动机相连，所述第二管道的一端内可转动地设有第二转子气阀，所述第二转子气阀具有第二转子气阀通道；
    差动气缸，其连接在所述第一管道的另一端与所述第二管道的另一端之间，所述差动气缸内可移动地设有差动活塞，所述差动气缸通过所述差动活塞分为第一气缸和第二气缸，所述第一气缸与所述第一管道相连通，所述第二气缸与所述第二管道相连通；
    联动机构，其与所述差动活塞相连，所述联动机构能根据所述差动活塞的移动，而带动所述第一转子气阀、所述第二转子气阀旋转。
  8. 如权利要求7所述的对压气能动力系统，其中，在所述第一转子气阀通道与所述第一管道相连通的状态下，所述第二转子气阀通道与所述第二管道相连通。
  9. 如权利要求7所述的对压气能动力系统，其中，所述对压气能差动转子稳压阀还包括驱动机构，所述驱动机构能驱动所述差动活塞在所述差动气缸内移动。
  10. 如权利要求9所述的对压气能动力系统，其中，所述驱动机构包括连接杆和弹簧，所述连接杆的一端与所述弹簧相连，所述连接杆的另一端与所述差动活塞相连；所述联动机构包括第一联动杆和第二联动杆，所述第一联动杆的两端分别与所述连接杆、所述第一转子气阀可转动地相连，所述第二联动杆的两端分别与所述连接杆、所述第二转子气阀可转动地相连。
  11. 如权利要求9所述的对压气能动力系统，其中，所述驱动机构包括驱动齿轮和分别与所述驱动齿轮相啮合的两个被动齿轮，两个所述被动齿轮分别连接在所述第一转子气阀和所述第二转子气阀上，所述驱动齿轮内设有扭簧；所述联动机构包括第一联动杆和第二联动杆，所述第一联动杆的两端分别与所述第一转子气阀、所述差动活塞可转动地相连，所述第二联动杆的两端分别与所述第二转子气阀、所述差动活塞可转动地相连。
  12. 如权利要求1所述的对压气能动力系统，其中，所述对压气能发动机为三角旋转活塞气压机或发动机，其具有缸体和可转动地设置在所述缸体内的三角旋转活塞，所述三角旋转活塞的横截面为三角形，所述缸体上设有连接所述对压气能贮存装置的多个进出气口。
  13. 如权利要求12所述的对压气能动力系统，其中，所述对压气能发动机的转轴与所述三角旋转活塞相连。
  14. 如权利要求12所述的对压气能动力系统，其中，所述三角旋转活塞气压机或发 动机还具有动力齿轮轴，所述动力齿轮轴穿设在所述三角旋转活塞内，所述三角旋转活塞的内周壁设有与所述动力齿轮轴相配合的啮合凸齿，所述对压气能发动机的转轴与所述动力齿轮轴相连。
  15. 如权利要求13或14所述的对压气能动力系统，其中，所述三角旋转活塞具有与所述缸体内壁滑动接触的第一端角、第二端角和第三端角，所述缸体内通过所述第一端角、所述第二端角和所述第三端角分割为第一内腔、第二内腔和第三内腔，所述第一端角与所述第二端角之间的所述缸体的内腔为所述第一内腔，所述第二端角与所述第三端角之间的所述缸体的内腔为所述第二内腔，所述第三端角与所述第一端角之间的所述缸体的内腔为所述第三内腔；所述缸体上的多个进出气口包括两个第一气口和两个第二气口，所述缸体的相对两侧分别设有一个所述第一气口和一个所述第二气口，位于所述缸体一侧的所述第一气口与位于所述缸体另一侧的所述第二气口相对设置。
  16. 如权利要求15所述的对压气能动力系统，其中，所述第一气口与所述高压贮气体相连，所述第二气口与所述低压贮气体相连，所述对压气能发动机为三角旋转活塞发动机。
  17. 如权利要求16所述的对压气能动力系统，其中，在所述第一气口分别与所述第一内腔、所述第二内腔或所述第三内腔相连通的状态下，所述三角旋转活塞在流入所述第一气口的所述高压气体的推动下而相对所述缸体旋转；在所述第二气口分别与所述第一内腔、所述第二内腔或所述第三内腔相连通的状态下，根据所述三角旋转活塞的旋转，所述第一内腔内的气体、所述第二内腔内的气体或所述第三内腔内的气体排出所述第二气口。
  18. 如权利要求15所述的对压气能动力系统，其中，所述第一气口与所述低压贮气体相连，所述第二气口与所述高压贮气体相连，所述对压气能发动机为三角旋转活塞气压机。
  19. 如权利要求18所述的对压气能动力系统，其中，根据所述三角旋转活塞的旋转，所述低压贮气体内的低压气体通过所述第一气口分别流入所述第一内腔、所述第二内腔或所述第三内腔中，且所述第一内腔中的低压气体、所述第二内腔中的低压气体或所述第三内腔中的低压气体分别通过所述第二气口被压缩入所述高压贮气体内。
  20. 如权利要求15所述的对压气能动力系统，其中，所述三角旋转活塞与所述缸体的三个接触处各设置了两个滚条。
  21. 如权利要求20所述的对压气能动力系统，其中，所述第一端角、所述第二端角 和所述第三端角内分别设有两个所述滚条，两个所述滚条分别为内滚条和外滚条，所述外滚条可滚动地设置在所述内滚条和所述缸体的内壁之间。
  22. 如权利要求21所述的对压气能动力系统，其中，所述内滚条为圆柱杆或簧圈；所述外滚条为圆柱杆。
  23. 如权利要求1所述的对压气能动力系统，其中，所述对压气能发动机为对压气能旋缸三角活塞气压机或发动机，其具有可转动的缸体和设置在所述缸体内的三角活塞，所述三角活塞的横截面为三角形，所述三角活塞上设有连接所述对压气能贮存装置的第一气口和第二气口，所述三角活塞的内腔能与所述缸体的内腔相连通。
  24. 如权利要求23所述的对压气能动力系统，其中，所述对压气能发动机的转轴与所述缸体相连；所述三角活塞的内腔包括第一活塞内腔和第二活塞内腔，所述第一活塞内腔与所述第一气口相连通，所述第二活塞内腔与所述第二气口相连通。
  25. 如权利要求24所述的对压气能动力系统，其中，所述三角活塞具有与所述缸体内壁滑动接触的第一端角、第二端角和第三端角，所述缸体内通过所述第一端角、所述第二端角和所述第三端角分割为第一内腔、第二内腔和第三内腔，所述第一端角与所述第二端角之间的所述缸体的内腔为所述第一内腔，所述第二端角与所述第三端角之间的所述缸体的内腔为所述第二内腔，所述第三端角与所述第一端角之间的所述缸体的内腔为所述第三内腔；所述三角活塞上设有第一输气活塞、第二输气活塞和第三输气活塞，所述第一输气活塞与所述第一内腔相对设置，所述第二输气活塞与所述第二内腔相对设置，所述第三输气活塞与所述第三内腔相对设置。
  26. 如权利要求25所述的对压气能动力系统，其中，所述第一输气活塞、所述第二输气活塞和所述第三输气活塞均为可轴向转动地设置在所述三角活塞上的活塞柱，所述活塞柱沿其轴向方向间隔设有相互平行的多个第一通道，两两相邻的所述第一通道之间设有第二通道，所述第二通道与所述第一通道之间具有夹角；所述第一活塞内腔能通过多个所述第一通道分别与所述第一内腔、所述第二内腔或所述第三内腔相连通，所述第二活塞内腔能通过多个所述第二通道分别与所述第一内腔、所述第二内腔或所述第三内腔相连通。
  27. 如权利要求26所述的对压气能动力系统，其中，所述第一通道与所述第二通道相互垂直设置。
  28. 如权利要求26所述的对压气能动力系统，其中，所述缸体轴心上设有齿轮轴，所述缸体内壁的相对两侧分别设有内凸齿，所述活塞柱上设有传动齿，所述传动齿能与 所述齿轮轴、所述内凸齿传动配合。
  29. 如权利要求26所述的对压气能动力系统，其中，所述第一气口与所述高压贮气体相连，所述第二气口与所述低压贮气体相连，所述对压气能发动机为旋缸三角活塞发动机。
  30. 如权利要求29所述的对压气能动力系统，其中，在所述第一气口分别与所述第一内腔、所述第二内腔或所述第三内腔相连通的状态下，自所述第一气口通入的所述高压气体能分别流入所述第一内腔、所述第二内腔或所述第三内腔中，所述缸体在所述高压气体的推动下而相对所述三角活塞旋转；在所述第二气口分别与所述第一内腔、所述第二内腔或所述第三内腔相连通的状态下，根据所述缸体的旋转，所述第一内腔中的气体、所述第二内腔中的气体或所述第三内腔的气体能分别排出所述第二气口。
  31. 如权利要求26所述的对压气能动力系统，其中，所述第一气口与所述低压贮气体相连，所述第二气口与所述高压贮气体相连，所述对压气能发动机为旋缸三角活塞气压机。
  32. 如权利要求31所述的对压气能动力系统，其中，根据所述缸体的旋转，所述低压贮气体内的低压气体能通过所述第一气口分别流入所述第一内腔、所述第二内腔或所述第三内腔内，在所述第一内腔、所述第二内腔或所述第三内腔分别与所述第二气口相连通的状态下，所述第一内腔中的气体、所述第二内腔中的气体或所述第三内腔中的气体能分别通过所述第二气口被压缩入所述高压贮气体内。
  33. 如权利要求1所述的对压气能动力系统，其中，所述对压气能发动机为对压气能多弧旋转活塞气压机或发动机，其具有缸体及可转动地设置在所述缸体内的多弧转子，所述多弧转子具有沿圆周方向设置的多个弧形外壁，所述缸体具有沿圆周方向设置的多个弧形内壁，所述弧形外壁与所述弧形内壁相配合，所述缸体上设有连接所述对压气能贮存装置的多个进出气口，所述弧形外壁的数量为n个，所述弧形内壁的数量为n+1个，所述进出气口的数量为n+1个。
  34. 如权利要求33所述的对压气能动力系统，其中，所述对压气能发动机的转轴与所述多弧转子相连。
  35. 如权利要求33所述的对压气能动力系统，其中，所述对压气能多弧旋转活塞气压机或发动机还具有动力齿轮轴，所述动力齿轮轴穿设在所述多弧转子内，所述多弧转子的内周壁设有与所述动力齿轮轴相配合的啮合凸齿，所述对压气能发动机的转轴与所述动力齿轮轴相连。
  36. 如权利要求34或35所述的对压气能动力系统，其中，所述缸体通过所述多弧转子被分割为第一内腔、第二内腔和第三内腔；所述缸体上的多个进出气口能分别与所述第一内腔、所述第二内腔或所述第三内腔相连通。
  37. 如权利要求36所述的对压气能动力系统，其中，各所述进出气口均包括多个第一通道和多个第二通道。
  38. 如权利要求37所述的对压气能动力系统，其中，所述第一通道与所述高压贮气体相连，所述第二通道与所述低压贮气体相连，所述对压气能发动机为对压气能多弧旋转活塞发动机。
  39. 如权利要求38所述的对压气能动力系统，其中，所述进出气口内可转动地设有气阀杆，所述气阀杆沿其轴向方向间隔设有相互平行的多个所述第一通道，两两相邻的所述第一通道之间设有所述第二通道，所述第一通道与所述第二通道之间具有夹角。
  40. 如权利要求39所述的对压气能动力系统，其中，所述第一通道与所述第二通道相互垂直设置。
  41. 如权利要求39所述的对压气能动力系统，其中，所述多弧转子上连接有转子气阀机构，所述转子气阀机构用于打开或关闭各所述进出气口的多个所述第一通道和多个所述第二通道。
  42. 如权利要求41所述的对压气能动力系统，其中，所述转子气阀机构包括气阀转环，所述气阀转环沿其圆周方向设有多个长凸齿和多个短凸齿，两两相邻的所述短凸齿之间设有一个所述长凸齿；所述气阀杆上连接有杆齿轮，所述短凸齿、所述长凸齿能分别与所述杆齿轮驱动相连，所述长凸齿的数量和所述短凸齿的数量分别为n+1个。
  43. 如权利要求37所述的对压气能动力系统，其中，所述第一通道与所述低压贮气体相连，所述第二通道与所述高压贮气体相连，所述对压气能发动机为对压气能多弧旋转活塞气压机。
  44. 如权利要求43所述的对压气能动力系统，其中，两两相邻的所述第一通道之间设有所述第二通道，多个所述第一通道与多个所述第二通道相互平行设置，所述第一通道内设有第一单向阀，所述第二通道内设有第二单向阀。
  45. 如权利要求33所述的对压气能动力系统，其中，所述对压气能发动机为对压气能两弧旋转活塞气压机或发动机，其具有缸体及可转动地设置在所述缸体内的两弧转子，所述两弧转子具有相对设置的两个弧形外壁，所述缸体的内腔具有依次相连的三个弧形内壁，所述弧形外壁与所述弧形内壁相配合。
  46. 如权利要求33所述的对压气能动力系统，其中，所述对压气能发动机为对压气能三弧旋转活塞气压机或发动机，其具有缸体及可转动地设置在所述缸体内的三弧转子，所述三弧转子具有沿圆周方向设置的三个弧形外壁，所述缸体的内腔具有依次相连的四个弧形内壁，所述弧形外壁与所述弧形内壁相配合。
  47. 如权利要求33所述的对压气能动力系统，其中，所述对压气能发动机为对压气能四弧旋转活塞气压机或发动机，其具有缸体及可转动地设置在所述缸体内的四弧转子，所述四弧转子具有沿圆周方向设置的四个弧形外壁，所述缸体的内腔具有依次相连的五个弧形内壁，所述弧形外壁与所述弧形内壁相配合。
  48. 如权利要求33所述的对压气能动力系统，其中，所述缸体上及所述多弧转子上分别设有电磁体或永磁体。
  49. 如权利要求1所述的对压气能动力系统，其中，所述动力装置为发电机、升降机、气动工具、车辆、轮船或飞行器。
  50. 一种对压气能动力方法，其中，其包括如下步骤：提供填充有高压气体的高压贮气体和填充有低压气体的低压贮气体，所述低压贮气体与所述高压贮气体之间具有对压气能，将所述对压气能以等温、等容的热工循环做功方式释放以驱动外部动力装置。
  51. 如权利要求50所述的对压气能动力方法，其中，通过对压气能发动机实现将所述对压气能以等温、等容的热工循环做功方式释放，所述对压气能发动机的转轴与所述动力装置相连。
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US10883367B2 (en) 2021-01-05
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US20180363463A1 (en) 2018-12-20
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EP3415715B1 (en) 2022-08-31
EP3415713A4 (en) 2020-03-11
US20180355721A1 (en) 2018-12-13
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CN108779672B (zh) 2020-12-25
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