WO2020078258A1 - 一种气压发动机 - Google Patents

一种气压发动机 Download PDF

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Publication number
WO2020078258A1
WO2020078258A1 PCT/CN2019/110444 CN2019110444W WO2020078258A1 WO 2020078258 A1 WO2020078258 A1 WO 2020078258A1 CN 2019110444 W CN2019110444 W CN 2019110444W WO 2020078258 A1 WO2020078258 A1 WO 2020078258A1
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WIPO (PCT)
Prior art keywords
piston
pressure
bolt
seal ring
cavity
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PCT/CN2019/110444
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English (en)
French (fr)
Inventor
焦惠泉
焦建石
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焦惠泉
焦建石
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Application filed by 焦惠泉, 焦建石 filed Critical 焦惠泉
Publication of WO2020078258A1 publication Critical patent/WO2020078258A1/zh

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    • 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
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/007—Reciprocating-piston liquid engines with single cylinder, double-acting piston
    • 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
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders

Definitions

  • the present application relates to the technical field of engines, in particular to a pneumatic engine.
  • the present application provides a pneumatic engine, which can reduce manufacturing and use costs and reduce the impact on the ecological environment.
  • a pneumatic engine is firstly covered by parts; a piston; a first cylinder head; a flexible body; a first liquid; a mounting seat; a first cylinder; a middle cylinder; a first bearing; A gasket; sealing plate; second cylinder; second liquid; second cylinder head; positioning pin; first hood; second cover; filling nozzle; first stroke switch; trigger plate; second stroke switch ; First bolt; Two-position four-way solenoid valve; Barometer; First gas storage tank; Pedal; Second gas storage tank; Third gas storage tank; High-pressure gas; Three-position six-port pressure control valve; Core; Spring; Connecting rod; Lower bearing bush; Second bolt; Upper bearing bush; Bearing cover; Upper hood; Third bolt; Crankshaft; Lower hood; Slide; Slider; Fourth bolt; First shaft cover; Two seals; flywheel; fifth bolt; connecting rod pin; circlip; bushing; first limiting shaft; second limiting shaft; first baffle; sixth bolt; second baffle; third limit Shaft
  • the piston ports of the first cylinder head and the second cylinder head are circular
  • the piston ports of the middle cylinder body are oval
  • the first limiting shaft and the second limiting The gap between the shaft and the surface of the shaft between the third limiting shaft and the fourth limiting shaft is consistent with the width of the oblong piston hole of the middle cylinder.
  • the outer wall of the piston is made of thin-walled seamless round steel pipe; the inner cavity of the piston is filled with the flexible body, and the flexible body is composed of a liquid or an elastomer.
  • the piston cavity is filled with liquid as the flexible body through the liquid filling nozzle installed on the second cover and pressurized So that the pressure value of the flexible body is higher than the maximum pressure value of the high-pressure gas, and reaches a preset duration, and then depressurize, the flexible body is sealed at the pressure of 0.11MP to 0.15MP state of the flexible body Said the inner cavity of the piston.
  • the seamless steel pipe of the piston and the gap between the pipe walls are filled with integral, split or granular elastomers as the flexible body, the flexible body is rubber, silicone or thermoplastic elastomer
  • the first cover, the second cover and the seamless steel pipe are sealed by welding.
  • the pressure value of the high-pressure gas in the first gas storage tank, the second gas storage tank, and the third gas storage tank is from low to high, and the high-pressure gas is air or nitrogen.
  • the air passage of the two-position four-way solenoid valve that is, the liquid return port, is used to fill the first chamber and the second chamber of the hydraulic cylinder assembly with the first liquid and the second liquid, respectively.
  • the liquid levels of the first cavity and the second cavity are higher than the installation heights of the two-position four-way solenoid valve and the three-position six-way pressure control valve.
  • the second space formed by assembling the upper hood and the lower hood is vented to the atmosphere.
  • the piston has a radial circular cross section in the first cavity and the second cavity, and in the first limiting axis, the second limiting axis, and the third limiting axis 1.
  • the surface gap of the fourth limiting shaft gradually deforms into an oblong cross-section, and the cross-sectional area of the piston also gradually decreases, that is, the piston changes in the first cavity and the second cavity.
  • Cross-sectional structure open the cut-off valve, rotate the pedal, turn on the high-pressure gas, when the first cavity intake channel is opened, the atmospheric channel is closed, and the second cavity intake channel is closed, the atmosphere
  • the high-pressure gas exerts a pressure force on the first liquid of the first cavity, and the first liquid transmits the pressure force of the high-pressure gas to the axial projection of the variable cross-section of the piston
  • the piston moves against the resistance, thereby driving the slider, the connecting rod, and the crankshaft to rotate.
  • the two-position four-way electromagnetic The valve reverses the pressure of the first cavity and the second cavity to make the second cavity
  • the gas channel is opened, the atmospheric channel is closed, and at the same time, the air inlet channel of the first cavity is closed, and the atmospheric channel is opened, the high-pressure gas exerts a pressure on the second liquid in the second cavity to make the piston do Reverse motion, forming the piston to reciprocate linear motion, under the inertia of the flywheel, the crankshaft continuously rotates in the same direction, when the trigger plate touches the first stroke switch, repeat the above actions, Forming a cycle, the piston can perform work each time the stroke of the piston moves, and there is no empty stroke.
  • the piston maintains the same volume during the movement of the first cavity and the second cavity.
  • the first liquid, the first The volume of the two liquids does not change, the high-pressure gas, the first liquid, and the second liquid do not flow, and the piston moves under static pressure.
  • the pedal is rotated by human or mechanical force to push the spool of the three-position six-way pressure control valve to sequentially connect the first gas storage tank, the second gas storage tank, and the The high-pressure gas with different pressure values in the third gas storage tank enables the piston to obtain power from small to large, thus making the crankshaft output torque from small to large.
  • FIG. 1 is a front cross-sectional structural diagram of a pneumatic engine provided by an embodiment of the present application
  • FIG. 2 is a top cross-sectional structural diagram of a pneumatic engine provided by an embodiment of the present application
  • FIG. 3 is a partial cross-sectional structure diagram of a pneumatic engine provided by an embodiment of the present application.
  • FIG. 4 is a schematic diagram of a force provided by an embodiment of the present application.
  • First cover 1 First cover 1; Piston 2; First cylinder head 3; Flexible body 4; First liquid 5; Mount 6; First cylinder 7; Middle cylinder 8; first bearing 9; first gasket 10; seal plate 11; second cylinder 12; second liquid 13; second cylinder head 14; positioning pin 15; first hood 16; second cover 17; Liquid filling nozzle 18; first stroke switch 19; trigger plate 20; second stroke switch 21; first bolt 22; two-position four-way solenoid valve 23; barometer 24; first air tank 25; pedal 26; second Gas storage tank 27; third gas storage tank 28; high-pressure gas 29; three-position six-way pressure control valve 30; globe valve 31; spool 32; spring 33; connecting rod 34; lower bearing bush 35; second bolt 36; upper Bearing 37; Bearing cover 38; Upper hood 39; Third bolt 40; Crankshaft 41; Lower hood 42; Slide 43; Slider 44; Fourth bolt 45; First shaft cover 46; Second seal 47; Flywheel 48; fifth bolt 49; connecting rod pin 50
  • This application is composed of hydraulic cylinder assembly; piston assembly; power assembly; power control assembly; crank slider assembly assembly.
  • the second baffle 57; the hood 16 constitutes a hydraulic cylinder assembly having a first cavity A and a second cavity B; except for the hood 16, it is symmetrical with respect to the O-axis structure, in which the first cylinder head 3, the first Two cylinder heads 14; the first cylinder block 7 and the second cylinder block 12; the middle cylinder block 8 is positioned with a positioning pin 15, the first bolt 22 is connected, the material is alloy steel, and the design needs to be calculated to check the outer wall and bolt Tensile strength, the piston ports of the first cylinder head 3, the second cylinder head 14, and the middle cylinder body 8 are provided with grooves, and the first seal ring 60, the fifth seal ring 64, the sixth seal ring 65, the ninth seal are installed Circle 68, the first cylinder head 3, the first The cylinder head 14, two ends of the middle cylinder block 8 and one end of the slideway 43 are provided with grooves on the flange joint surface, and a second sealing ring 61, a third sealing ring 62, a
  • the gap between the shaft surfaces of the second limiting shaft 54 and the third limiting shaft 58 and the fourth limiting shaft 59 is the same as the width of the oblong piston hole of the middle cylinder 8, the first baffle 55, The second baffle 57 is positioned with an outer contour, and the sixth bolt 56 is connected to be fixed in the groove of the piston port at both ends of the middle cylinder block 8.
  • the function is to facilitate the installation of the fifth sealing ring 64 and the sixth sealing ring 65.
  • first gaskets 10 and a sealing plate 11 are connected to the two mounting surfaces of the center cylinder 8 with a fourth bolt 45, which is used to seal the mounting hole of the first bearing 9 ,the first
  • the internal first space C is vented to the atmosphere, and six mounting seats 6 are respectively designed under the first cylinder block 7, the second cylinder block 12, and the lower hood 42 for installing and fixing the pneumatic engine.
  • the first hood 16 may be provided with a vent hole, and the first space C may communicate with the atmosphere through the vent hole.
  • the first cover 1, the second cylinder head 17; the piston 2; the flexible body 4; the liquid filling nozzle 18 constitutes the piston assembly; wherein, the outer wall of the piston 2 is made of a thin-walled seamless circular steel pipe, which has high tensile strength, Appropriate elongation rate, good bending and flexure resistance material characteristics, smooth inner and outer surfaces; the inner diameter of the two ends of the piston 2 closely matches the outer diameter of the flange 1 of the first cover 1, the second cover 17, the two ends of the piston 2 The flanges of the first cover 1 and the second cover 17 are welded and sealed; the inner cavity of the piston 2 is filled with a flexible body 4, which is composed of two types of materials, liquid or elastomer, as described below:
  • the material of the flexible body can be rubber, silicone or thermoplastic elastomer, the piston 2
  • the piston assembly components are symmetrical with respect to the O-axis structure except for the filling nozzle 18.
  • the first gas storage tank 25, the second gas storage tank 27, the third gas storage tank 28; the high-pressure gas 29; the barometer 24; the shut-off valve 31 constitutes a power assembly; the high-pressure gas 29 is in the first gas storage tank 25, the first The second gas storage tank 27 and the third gas storage tank 28 have pressure values from low to high, using air or nitrogen, the barometer 24 is used to display the pressure value of the high-pressure gas 29, and the shut-off valve 31 is used to switch the first gas storage tank 25.
  • the second gas storage tank 27 and the third gas storage tank 28 are examples of the first gas storage tank 25.
  • first travel switch 19 By the first travel switch 19, the second travel switch 21; the first liquid 5, the second liquid 13; two-position four-way solenoid valve 23; pedal 26; three-position six-way pressure control valve 30; trigger plate 20; sixth bolt 56 constitutes a power control assembly; the first stroke switch 19 and the first stroke switch 21 are respectively fixed on the first hood 16 and the second cylinder head 14 with a sixth bolt 56, and the trigger plate 20 is fixed on the sixth bolt 56 on the On the end surface of the second cover 17, the first liquid 5 and the second liquid 13 are respectively filled into the first chamber A and the In the second chamber B, in order not to consume high-pressure gas 29, the liquid level is higher than the installation height of the two-position four-way solenoid valve 23 and the three-position six-way pressure control valve 30.
  • the two-position four-way solenoid valve 23 reduces the pressure of the high-pressure gas 29 Strongly connected to the first cavity A and the second cavity B of the first cylinder 7 and the second cylinder 12, the air inlet of the three-position six-way pressure control valve 30 is connected to the first gas storage tank 25, The air outlets of the second gas storage tank 27 and the third gas storage tank 28; the air outlet of the three-position six-way pressure control valve 30 is connected to the air inlet of the two-position four-way solenoid valve 23 through The brake pedal 26 sequentially access a first tank 25, second tank 27, the third high-pressure gas tank 28 and 29.
  • the piston 2 has a radial circular cross section in the first chamber A and the second chamber B, and the first limiting shaft 53, the second limiting shaft 54 and the third limiting shaft 58, the fourth limiting Under the action of the surface clearance of the shape shaft 59, it gradually deforms into an oblong cross-section, and the cross-sectional area of the piston 2 also gradually decreases, that is, the piston 2 has a variable cross-sectional structure in the first chamber A and the second chamber B, and the stop valve 31 is opened and rotated
  • the pedal 26 is connected to the high-pressure gas 29.
  • the liquid 13 exerts a pressure force to make the piston 2 move in a reverse direction, forming a reciprocating linear movement of the piston 2, under the inertia of the flywheel 48, the crankshaft 41 continuously rotates in the same direction, when the trigger plate 20 touches the first stroke switch 19 ,
  • the piston 2 keeps the same volume during the movement of the first chamber A and the second chamber B, therefore, the first liquid 5, the first The volume of the two liquids 13 does not change, the high-pressure gas 29 and the first liquid 5 and the second liquid 13 do not flow, and the piston 2 is moved under static pressure.
  • the pedal 26 is rotated by human or mechanical force to push the spool 32 of the three-position six-way pressure control valve 30 to sequentially connect the different pressures in the first gas storage tank 25, the second gas storage tank 27, and the third gas storage tank 28
  • the high-pressure gas 29 of the value enables the piston 2 to obtain a small to large power, so that the crankshaft 41 outputs a small to large torque, release the pedal 26, and under the action of the spring 33, the spool 32 returns to the closed state, if Increasing the number of gas storage tanks in this application, the high-pressure gas 29 correspondingly increases the pressure value of different size, and the corresponding three-position six-way pressure control valve 30 increases the number of digits and the number of passages, which can make the engine more smoothly from small to
  • the large torque is similar to the control method of the throttle of a gasoline engine used in a car.
  • the first seal ring 60, the fifth seal ring 64, the sixth seal ring 65, and the ninth seal ring 68 are used between the piston 2 and the first cylinder head 3, the second cylinder head 14 and the middle cylinder block 8
  • the liquid 5 and the second liquid 13 are lubricated, and other sports and sports parts are lubricated with lubricating oil or grease.
  • FIGS. 1 and 2 express the structural state of the present application when the piston 2 moves to a half stroke, that is, when the crankshaft 41 rotates to 90 degrees.
  • a, b, c, and d are the force-receiving areas of the axial projection surface of the variable cross-section of the piston 2, when the valve core of the two-position four-way solenoid valve 23 When the left side moves, the pressure force of the high-pressure gas 29 acts on the first liquid 5, and the pressure force of the first liquid 5 acts on the piston 2 of the first chamber A. At this time, the force received by the piston 2 is:
  • the pressure of the first liquid 5 is applied to two areas a of the first chamber A; the direction is the same as the direction of movement of the piston 2;
  • the pressure of the atmosphere on the area a of the second cavity B is opposite to the direction of movement of the piston 2;
  • the area b of the first chamber A is under the pressure of the first liquid 5 on the area b, and the direction is opposite to the direction of movement of the piston 2;
  • the pressure of the atmosphere on the area b of the second cavity B is in the same direction as the movement direction of the piston 2;
  • the area c of the first cavity A is under the pressure of the first liquid 5 on the area c, and the direction is the same as the direction of movement of the piston 2;
  • the area c of the second cavity B is under the pressure of the atmosphere, and the direction is opposite to the direction of movement of the piston 2;
  • the area d of the first chamber A and the second chamber B is not affected by the pressure of the first liquid 5;
  • the flexible body 4 uses liquid, the inner surface of the piston 2 of the second chamber B is subjected to the pressure force transmitted by the first liquid 5 to the flexible body 4, the outer surface is subjected to atmospheric pressure, and there is a relatively large pressure difference between the inside and outside.
  • the piston 2 is made of 20CrMo seamless alloy steel tube; the length is 912mm; the wall thickness is 2mm; the outer circle diameter is 100mm; the cross-sectional area is 78.5 square centimeters; the circumference is 31.4cm; the tensile strength is 885MPa, and the piston 2 stroke is 150mm , That is, the radius of the crankshaft is 75mm.
  • the material of the flexible body 4 be hydraulic oil; the pressure value is 0.12MPa;
  • the high-pressure gas 29 in the third gas storage tank 28 is high-pressure air; the pressure value is 3.5 MPa;
  • the first limiting shaft 53, the second limiting shaft 54 and the third limiting shaft 58, the fourth limiting shaft 59 are made of 45CrMo; the heat treatment hardness is above HRC60; the diameter is 28mm; the length is 212mm; the first limiting shaft 53.
  • the surface clearance of the second limiting shaft 54 and the third limiting shaft 58 and the fourth limiting shaft 59 is 20 mm; the surface is smooth;
  • first cylinder head 3, the second cylinder head 14, the middle cylinder block 8, the first cylinder block 7, the second cylinder block 12 are made of 45CrMo, cast;
  • the slide 43 is made of ductile alloy cast iron, and the first hood 16 is general Cast iron or die castings;
  • the first cover 1 and the second cover 17 are set, and the material of the sealing plate 11 is 45 steel;
  • the two-position four-way solenoid valve 23 is set as a standard part, and the three-position six-way pressure control valve 30 is self-made;
  • the first seal ring 60, the fifth seal ring 64, the sixth seal ring 65, the ninth seal ring 68 are Y-shaped for the shaft, the second seal ring 61, the third seal ring 62, the fourth seal ring 63, the seventh
  • the seal ring 66, the eighth seal ring 67, the tenth seal ring 69, the eleventh seal ring 70 are O-shaped, the first seal pad 10, the second seal pad 47, and the third seal pad 71 are rubber pads;
  • first bearings 9 There are eight first bearings 9 and two second bearings 72, using standard parts; other parts are omitted;
  • the external dimensions excluding the protruding portion of the crankshaft 41 are 1450 mm ⁇ 332 mm ⁇ 272 mm.
  • the force calculation of the piston 2 is calculated as follows: the area values of the axial projection of the piston 2; a: 58.9cm 2 ; b: 8.34cm 2 ; c: 6.4cm 2 ; / cm 2 .
  • the pressure of the first liquid 5 on the area a of the first chamber A is 2061 kg; the direction is the same as the direction of movement of the piston 2;
  • the pressure of the atmosphere on the area a of the second cavity B is 58.9 kg, and the direction is opposite to the direction of movement of the piston 2;
  • the pressure of the first liquid 5 on the area b of the first chamber A is 292kg, and the direction is opposite to the direction of movement of the piston 2;
  • the pressure of the atmosphere on the area b of the second cavity B is 8.34 kg, and the direction is the same as the direction of movement of the piston 2;
  • the pressure of the first liquid 5 on the area c of the first cavity A is 224kg, and the direction is the same as the direction of the piston 2;
  • the pressure of the atmosphere on the area c of the second cavity B is 6.4kg, and the direction is opposite to the direction of movement of the piston 2;
  • the sixth sealing ring 65 and the ninth sealing ring 68 are subjected to the pressure force of the first liquid 5 in the first chamber A and the sliding friction force with the piston 2, and the contact area of the sealing lip and the piston 2 is 31.4cm 2 ; Take the sliding friction resistance coefficient as 0.3; then the sliding friction resistance is 330kg, the direction is opposite to the movement direction of the piston 2;
  • the maximum force of the piston 2 to the left is 1606kg, that is, the piston 2 outputs 1606kg of power, and the radius of the crankshaft 41 is 0.075 meters, the output torque of the crankshaft 41 is 120.45kgm, or 1205Nm.
  • the total output torque is 2410Nm.
  • the first cylinder head 3, the second cylinder head 14, the first cylinder body 7, the second cylinder body 12, and the middle cylinder body 8 all need to check the allowable stress of the cylinder wall, and the number of bolts and the first cylinder need to be considered in the design
  • the thickness and structure of the cover 3, the second cylinder head 14, the first cylinder 7, the second cylinder 12, and the middle cylinder 8 are strengthened. In this embodiment, the calculation and verification process is omitted.
  • FIG. 3 is a partial cross-sectional structural diagram of a dual-cylinder pneumatic engine provided by an embodiment of the present application.
  • a single-cylinder pneumatic engine can be obtained.
  • a multi-cylinder pneumatic engine can be obtained.
  • This application uses a single-cylinder pneumatic engine as an example for description.
  • the piston 2 is made of 20CrMo seamless alloy steel tube; the length is 912mm; the wall thickness is 2mm; the outer circle diameter is 100mm; the cross-sectional area is 78.5 square centimeters; the circumference is 31.4cm; the tensile strength is 885MPa, and the piston 2 stroke is 150mm , That is, the radius of the crankshaft is 75mm.
  • the flexible body 4 is made of granular polyurethane rubber; the particle size is 3mm ⁇ 3mm;
  • the high-pressure gas 29 in the third gas storage tank 28 is high-pressure air; the pressure value is 10 MPa;
  • the first limiting shaft 53, the second limiting shaft 54 and the third limiting shaft 58, the fourth limiting shaft 59 are made of 45CrMo; the heat treatment hardness is above HRC60; the diameter is 28mm; the length is 212mm; the first limiting shaft 53.
  • the surface clearance of the second limiting shaft 54 and the third limiting shaft 58 and the fourth limiting shaft 59 is 30 mm; the surface is smooth;
  • first cylinder head 3, the second cylinder head 14, the middle cylinder block 8, the first cylinder block 7, the second cylinder block 12 are made of 45CrMo, cast;
  • the slide 43 is made of ductile alloy cast iron, and the first hood 16 is general Cast iron or die castings;
  • the first cover 1 and the second cover 17 are set, and the material of the sealing plate 11 is 45 steel;
  • the two-position four-way solenoid valve 23 is set as a standard part, and the three-position six-way pressure control valve 30 is self-made;
  • the first seal ring 60, the fifth seal ring 64, the sixth seal ring 65, the ninth seal ring 68 are Y-shaped for the shaft, the second seal ring 61, the third seal ring 62, the fourth seal ring 63, the seventh
  • the seal ring 66, the eighth seal ring 67, the tenth seal ring 69, the eleventh seal ring 70 are O-shaped, the first seal pad 10, the second seal pad 47, and the third seal pad 71 are rubber pads;
  • first bearings 9 There are eight first bearings 9 and two second bearings 72, using standard parts; other parts are omitted;
  • the external dimensions excluding the protruding portion of the crankshaft 41 are 1450 mm ⁇ 350 mm ⁇ 290 mm.
  • the force calculation of the piston 2 in this embodiment is calculated as follows: the area values of the axial projection of the piston 2; a: 49.25cm 2 ; b: 10.6cm 2 ; c: 5.6cm 2 ; cm 2 .
  • the pressure of the first liquid 5 on the area a of the first chamber A is 4925kg; the direction is the same as the movement direction of the piston 2;
  • the pressure of the atmosphere on the area a of the second cavity B is 49.25 kg, and the direction is opposite to the direction of movement of the piston 2;
  • the pressure force of the first liquid 5 on the area b of the first chamber A is 1060 kg, and the direction is opposite to the direction of movement of the piston 2;
  • the pressure of the atmosphere on the area b of the second cavity B is 10.6 kg, and the direction is the same as the direction of movement of the piston 2;
  • the pressure of the first liquid 5 on the area c of the first chamber A is 560kg, and the direction is the same as the direction of movement of the piston 2;
  • the pressure of the atmosphere on the area c of the second cavity B is 5.6kg, and the direction is opposite to the direction of movement of the piston 2;
  • the sixth sealing ring 65 and the ninth sealing ring 68 are subjected to the pressure force of the first liquid 5 in the first chamber A and the sliding friction force with the piston 2, and the contact area of the sealing lip and the piston 2 is 31.4cm 2 ;
  • the sliding friction resistance coefficient is 0.3; then the sliding friction resistance is 942 kg, and the direction is opposite to the movement direction of the piston 2;
  • the maximum force of the piston 2 to the left is 3439kg, that is, the output power of the piston 2 is 3439kg, and the radius of the crankshaft 41 is 0.075 meters, the output torque of the crankshaft 41 is 258kgm, that is, 2580Nm. If it is a double cylinder structure, the output The total torque is 5160Nm.
  • the flexible body 4 of this embodiment uses urethane rubber particles as a solid, and does not need to check the allowable stress of the internal cavity of the seamless steel pipe of the piston 2.
  • the pressure value of the high-pressure gas 29 is 10 MP, when the liquid is used relative to the flexible body 4
  • the pressure value of the high-pressure gas 29 in the third gas storage tank 28 is 100 kg / cm 2
  • the pressure value of the high-pressure gas 29 in the second gas storage tank 27 is set to 60 kg / cm 2
  • the first gas storage tank 25 The pressure value of the high-pressure gas 29 inside is set to 20 kg / cm 2 .
  • the first cylinder head 3, the second cylinder head 14, the first cylinder body 7, the second cylinder body 12, and the middle cylinder body 8 all need to check the allowable stress of the cylinder wall, and the number of bolts and the first cylinder need to be considered in the design
  • the wall thickness and structure of the cover 3, the second cylinder head 14, the first cylinder 7, the second cylinder 12, and the middle cylinder 8 are strengthened. In this embodiment, the calculation and verification process is omitted.
  • the material technology and process technology of the large-diameter thin-wall seamless steel pipe and the flexible body 4 used for manufacturing the piston 2 in this application are the key core technologies for implementing this application.
  • the beneficial effects of this application are: integrating the development and use of energy, inputting quantitative high-pressure gas energy, and continuously converting the pressure energy of the gas into mechanical energy.
  • the structure is simple, the manufacturing and use costs are low, and the volume can be miniaturized or large.
  • the output energy density is high, can be industrialized production, replace the existing fuel oil, gas engine, does not affect the ecological environment, can provide power for a variety of mobile machinery, ships, cars, can also provide power for fixed large machinery, but also for the energy industry Provide motivation.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Abstract

一种气压发动机，将薄壁无缝圆形钢管作为活塞（2），两端用封盖密封，内腔填充柔性体（4），装配在具有第一腔（A）和第二腔（B）的液压缸内，其径向圆形截面，在限形轴间隙作用下，逐渐变形为长圆形截面，面积也随之变小，当高压气体（29）对第一腔（A）中第一液体（5）施加压强力，同时第二腔（B）中液体（13）处于大气压状态时，第一腔（A）中液体（5）将压强力作用在活塞变截面的轴向投影面上，使活塞（2）运动，活塞（2）在第一腔（A）、第二腔（B）运动过程中保持体积不变，通过电磁阀（23）将第一腔（A）、第二腔（B）压力换向，使活塞（2）做往复直线运动，驱动曲轴（41）转动做功，该气压发动机集开发和使用能源为一体，可以取代燃油、燃气发动机，结构简单，制造及使用成本低，降低对生态环境的影响。

Description

一种气压发动机
本申请要求于2018年10月18日提交中国专利局、申请号为201811281174.4发明名称为“气压发动机”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本申请涉及发动机技术领域，尤其涉及一种气压发动机。
背景技术
目前，不可再生能源如煤炭，石油，核能等开发成本高，污染环境，开采存量日益枯竭。可再生能源如太阳能，风能，水利发电等开发受环境、地理等因素影响，开发成本高。
燃油、燃气发动机污染环境，新能源发动机开发成本高，能量密度低。
发明内容
本申请提供一种气压发动机，能够降低制造及使用成本，降低对生态环境的影响。
根据本申请实施例的一种气压发动机，是由零件第一封盖；活塞；第一缸盖；柔性体；第一液体；安装座；第一缸体；中缸体；第一轴承；第一密封垫；封板；第二缸体；第二液体；第二缸盖；定位销；第一机罩；第二封盖；充液嘴；第一行程开关；触发板；第二行程开关；第一螺栓；二位四通电磁阀；气压表；第一储气罐；踏板；第二储气罐；第三储气罐；高压气体；三位六通控压阀；截止阀；阀芯；弹簧；连杆；下轴瓦；第二螺栓；上轴瓦；轴瓦盖；上机罩；第三螺栓；曲轴；下机罩；滑道；滑块；第四螺栓；第一轴盖；第二密封垫；飞轮；第五螺栓；连杆销；卡簧片；轴套；第一限形轴；第二限形轴；第一挡板；第六螺栓；第二挡板；第三限形轴；第四限形轴；第一密封圈；第二密封圈；第三密封圈；第四密封圈；第五密封圈；第六密封圈；第七密封圈；第八密封圈；第九密封圈；第十密封圈；第十一密封圈；第三密封垫；第二轴承；防尘圈；第七螺栓；第二轴盖构成的装置，是由液 压缸总成、活塞总成、动力总成、动力控制总成和曲柄滑块总成部件装配构成；由所述第一缸盖、所述第二缸盖、所述第一缸体、所述第二缸体、所述中缸体、所述第一密封圈、所述第二密封圈、所述第三密封圈、所述第四密封圈、所述第五密封圈、所述第六密封圈、所述第七密封圈、所述第八密封圈、所述第九密封圈、所述第十密封圈、所述第十一密封圈、所述第一限形轴、所述第二限形轴、所述第三限形轴、所述第四限形轴、所述第一轴承、所述第一密封垫、所述封板、所述定位销、所述第一螺栓、所述第二螺栓、所述第一挡板、所述第二挡板、所述第一机罩构成具有第一腔、第二腔的所述液压缸总成；其中，所述第一缸盖、所述第二缸盖、所述第一缸体、所述第二缸体和所述中缸体之间用所述定位销定位，所述第一螺栓连接，所述第一缸盖、所述第二缸盖、所述中缸体的活塞口设有凹槽，安装所述第一密封圈、所述第五密封圈、所述第六密封圈、所述第九密封圈，所述第一缸盖、所述第二缸盖，所述中缸体的两端、所述滑道的一端法兰接合面设有凹槽，安装所述第二密封圈、所述第三密封圈、所述第四密封圈、所述第七密封圈、所述第八密封圈、所述第十密封圈，所述第十一密封圈，所述第一限形轴、所述第二限形轴、所述第三限形轴、所述第四限形轴两端装配有所述第一轴承，安装在所述中缸体的安装孔内，所述第一挡板、所述第二挡板用外轮廓定位，所述第六螺栓连接，固定在所述中缸体两端的活塞口的凹槽内，所述第一密封垫和所述封板，用所述螺栓连接在所述中缸体的两个安装面上；由所述第一封盖、所述第二封盖、所述活塞、所述柔性体和所述充液嘴构成所述活塞总成；所述活塞两端面内径与所述第一封盖、所述第二封盖法兰凸台外径紧密配合，所述活塞两端面与所述第一封盖、所述第二封盖的法兰面焊接密封；由所述第一储气罐、所述第二储气罐、所述第三储气罐、所述高压气体、所述气压表和所述截止阀构成所述动力总成；由所述第一行程开关、所述第二行程开关、所述第一液体、所述第二液体、所述二位四通电磁阀、所述踏板、所述三位六通控压阀、所述触发板和所述第六螺栓构成所述动力控制总成；所述第一行程开关、所述第二行程开关分别用所述第六螺栓固定在所述第一机罩上和所述第二缸盖上，所述触发板用所述第六螺栓固定在所述第二封盖的端面上，所述二位四通电磁阀将所述高压气体的压强力接入到 所述第一缸体、所述第二缸体的第一腔、第二腔内，所述三位六通控压阀的进气口，分别连接到所述第一储气罐、所述第二储气罐、所述第三储气罐的出气口上；所述三位六通控压阀的出气口，连接到所述二位四通电磁阀的进气口上，通过转动所述踏板顺序接入所述第一储气罐、所述第二储气罐和所述第三储气罐的所述高压气体，由所述连杆、所述下轴瓦、所述第二螺栓、所述上轴瓦、所述轴瓦盖、所述上机罩、所述第三螺栓；所述曲轴、所述下机罩、所述滑道、所述滑块、所述第四螺栓、所述第一轴盖、所述第二密封垫、所述飞轮、所述第五螺栓、所述连杆销、所述卡簧片、所述轴套、所述第三密封垫、所述第二轴承、所述防尘圈、所述第七螺栓和所述第二轴盖构成所述曲柄滑块总成；所述滑块用所述第四螺栓连接在所述活塞的所述第一封盖端面上，所述飞轮的内径与所述曲轴的外径过渡配合，用所述飞轮的止口定位，用所述第五螺栓连接固定在所述曲轴上，所述上机罩和所述下机罩，用所述第一螺栓与所述滑道连接，用所述第三螺栓相互连接，所述第一轴盖、所述第二轴盖、所述第二密封垫、所述第三密封垫用所述第七螺栓固定在所述上机罩和所述下机罩上。
可选的，所述第一缸盖、所述第二缸盖的活塞口为圆形，所述中缸体的活塞口为长圆形，所述第一限形轴、第二所述限形轴及所述第三限形轴、所述第四限形轴之间的轴表面之间的间隙，与所述中缸体长圆活塞孔的宽度一致，所述第一机罩装配后，内部第一空间通大气，在所述第一缸体、所述第二缸体及所述下机罩下面分别设计有六处所述安装座，用于安装固定所述气压发动机。
可选的，所述活塞外壁由薄壁无缝圆形钢管制造；所述活塞内腔填充所述柔性体，所述柔性体由液体或者弹性体构成。
可选的，所述活塞与液压缸总成装配后，通过在所述第二封盖上安装的所述充液嘴，向所述活塞腔内充入液体作为所述柔性体，并且加压，使所述柔性体的压强值高于高压气体的最大压强值，并且达到预设时长，然后减压，在所述柔性体压强0.11MP至0.15MP状态下，将所述柔性体密封在所述活塞的内腔。
可选的，所述活塞的无缝钢管内，以及管壁之间无间隙装入有整体、分 体或者颗粒状弹性体，作为所述柔性体，所述柔性体为橡胶、硅胶或热塑性弹性体，所述第一封盖、所述第二封盖与无缝钢管通过焊接进行密封。
可选的，所述高压气体在所述第一储气罐、所述第二储气罐、所述第三储气罐内的压强值由低到高，所述高压气体为空气或者氮气。
可选的，所述二位四通电磁阀的通大气通道即回液口，用于分别将所述第一液体、所述第二液体充入液压缸总成的所述第一腔、所述第二腔内，所述第一腔和所述第二腔的液面高度高于所述二位四通电磁阀和所述三位六通控压阀的安装高度。
可选的，由所述上机罩和所述下机罩装配后形成的第二空间通大气。
可选的，所述活塞在所述第一腔、所述第二腔的径向圆形截面，在所述第一限形轴、所述第二限形轴和所述第三限形轴、所述第四限形轴的表面间隙作用下，逐渐变形为长圆形截面，所述活塞的截面面积也逐渐减少，即所述活塞在所述第一腔、所述第二腔为变截面结构，开启所述截止阀，旋转所述踏板，接通所述高压气体，当所述第一腔进气通道打开，通大气通道关闭，同时所述第二腔进气通道关闭，通大气通道打开时，所述高压气体对所述第一腔的所述第一液体施加压强力，所述第一液体将所述高压气体的压强力，传递作用在所述活塞变截面的轴向投影面上，使所述活塞克服阻力运动，进而带动所述滑块、所述连杆、所述曲轴转动，当所述触发板触碰所述第二行程开关时，所述二位四通电磁阀将所述第一腔、所述第二腔压力换向，使所述第二腔进气通道打开，通大气通道关闭，同时所述第一腔进气通道关闭，通大气通道打开，所述高压气体对所述第二腔的所述第二液体施加压强力，使所述活塞做反向运动，形成所述活塞做往复直线运动，在所述飞轮的惯性作用下，使所述曲轴连续同方向转动，当所述触发板触碰所述第一行程开关时，重复以上动作，形成循环，每次所述活塞运动行程均可以做功，没有空行程，所述活塞在所述第一腔、所述第二腔运动过程中保持体积不变，所述第一液体、所述第二液体体积也不发生变化，所述高压气体和所述第一液体、所述第二液体没有流动，在静压状态下推动所述活塞运动。
可选的，通过人力或机械力转动所述踏板，推动所述三位六通控压阀的所述阀芯，顺序接通所述第一储气罐、所述第二储气罐、所述第三储气罐中 的不同压强值的所述高压气体，使所述活塞获得由小到大的动力，因而使所述曲轴输出由小到大的扭矩。
附图说明
为了更清楚地说明本申请实施例和现有技术的技术方案，下面对实施例和现有技术中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图仅仅是本申请的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图获得其他的附图。
图1是本申请实施例提供的一种气压发动机的主视剖面结构图；
图2是本申请实施例提供的一种气压发动机的俯视剖面结构图；
图3是本申请实施例提供的一种气压发动机的局部剖面结构图；
图4是本申请实施例提供的一种的受力示意图。
图1、图2中各零件的名称和标号：第一封盖1；活塞2；第一缸盖3；柔性体4；第一液体5；安装座6；第一缸体7；中缸体8；第一轴承9；第一密封垫10；封板11；第二缸体12；第二液体13；第二缸盖14；定位销15；第一机罩16；第二封盖17；充液嘴18；第一行程开关19；触发板20；第二行程开关21；第一螺栓22；二位四通电磁阀23；气压表24；第一储气罐25；踏板26；第二储气罐27；第三储气罐28；高压气体29；三位六通控压阀30；截止阀31；阀芯32；弹簧33；连杆34；下轴瓦35；第二螺栓36；上轴瓦37；轴瓦盖38；上机罩39；第三螺栓40；曲轴41；下机罩42；滑道43；滑块44；第四螺栓45；第一轴盖46；第二密封垫47；飞轮48；第五螺栓49；连杆销50；卡簧片51；轴套52；第一限形轴53；第二限形轴54；第一挡板55；第六螺栓56；第二挡板57；第三限形轴58；第四限形轴59；第一密封圈60；第二密封圈61；第三密封圈62；第四密封圈63；第五密封圈64；第六密封圈65；第七密封圈66；第八密封圈67；第九密封圈68；第十密封圈69；第十一密封圈70；第三密封垫71；第二轴承72；防尘圈73；第七螺栓74；第二轴盖75；第一腔A；第二腔B；第一空间C；第二空间D。
具体实施方式
为使本申请的目的、技术方案、及优点更加清楚明白，以下参照附图并举实施例，对本申请进一步详细说明。显然，所描述的实施例仅仅是本申请一部分实施例，而不是全部的实施例。基于本申请中的实施例，本领域普通技术人员在没有作出创造性劳动前提下所获得的所有其他实施例，都属于本申请保护的范围。
下面结合图1，图2，图3对本申请结构做说明：
本申请是由液压缸总成；活塞总成；动力总成；动力控制总成；曲柄滑块总成部件装配构成。
由第一缸盖3、第二缸盖14；第一缸体7、第二缸体12；中缸体8；第一密封圈60、第二密封圈61、第三密封圈62、第四密封圈63、第五密封圈64、第六密封圈65、第七密封圈66、第八密封圈67、第九密封圈68、第十密封圈69、第十一密封圈70；第一限形轴53、第二限形轴54、第三限形轴58、第四限形轴59；轴承9；密封垫10；封板11；定位销15；螺栓22；螺栓56；第一挡板55、第二挡板57；机罩16构成具有第一腔A、第二腔B的液压缸总成；除机罩16以外，相对于O轴结构对称，其中，第一缸盖3、第二缸盖14；第一缸体7、第二缸体12；中缸体8之间用定位销15定位，第一螺栓22连接，材质采用合金钢，设计时需要计算校核外壁及螺栓的抗拉强度，第一缸盖3、第二缸盖14、中缸体8的活塞口设有凹槽，安装第一密封圈60、第五密封圈64、第六密封圈65、第九密封圈68，第一缸盖3、第二缸盖14，中缸体8的两端、滑道43的一端法兰接合面设有凹槽，安装第二密封圈61、第三密封圈62、第四密封圈63、第七密封圈66、第八密封圈67、第十密封圈69，第十一密封圈70，第一缸盖3、第二缸盖14的活塞口为圆形，中缸体8的活塞口为长圆形，第一限形轴53、第二限形轴54、第三限形轴58、第四限形轴59两端装配有轴承9，安装在中缸体8的安装孔内，第一限形轴53、第二限形轴54及第三限形轴58、第四限形轴59之间的轴表面之间的间隙，与中缸体8长圆活塞孔的宽度一致，第一挡板55、第二挡板57用外轮廓定位，第六螺栓56连接，固定在中缸体8两端的活塞口的凹槽内，作用是方便第五密封圈64、第六密封圈65的安装，也方便对中缸体8密封槽的加工，两个第 一密封垫10和封板11，用第四螺栓45连接在中缸体8的两个安装面上，作用是将第一轴承9安装孔密封，第一机罩16装配后，内部第一空间C通大气，在第一缸体7、第二缸体12及下机罩42下面分别设计有六处安装座6，用于安装固定本气压发动机。第一机罩16中可以设置有通气孔，第一空间C可以通过该通气孔与大气相通。
由第一封盖1、第二缸盖17；活塞2；柔性体4；充液嘴18构成活塞总成；其中，活塞2外壁由薄壁无缝圆形钢管制造，具有抗拉强度高、延展率适当、抗弯耐曲挠性能好的材料特点，内外表面光滑；活塞2两端面内径与第一封盖1、第二封盖17法兰凸台外径紧密配合，活塞2两端面与第一封盖1、第二封盖17的法兰面焊接密封；活塞2内腔填充柔性体4，柔性体4由液体或者弹性体两类材质构成，说明如下：
1、活塞2与液压缸总成装配后，通过在第二封盖17上安装的充液嘴18，向活塞2腔内充入液体作为柔性体4，并且加压，使柔性体4的压强值高于高压气体29的最大压强值，并且保压预设时长，以使活塞2的无缝钢管充分变形，然后减压，在柔性体4压强0.11MP至0.15MP状态下，将柔性体4密封在活塞2的内腔，利用液体体积不被压缩的物理特点，使活塞2既具有刚性又具有柔性。
2、在活塞2的无缝钢管内，与管壁之间无间隙装入整体、分体或者颗粒状弹性体作为柔性体4，柔性体的材质可以选用橡胶、硅胶或者热塑性弹性体，将活塞2和柔性体4与液压缸总成装配后，对柔性体4加预压的状态下，再将第一封盖1、第二封盖17与无缝钢管焊接密封。
活塞总成部件除充液嘴18以外，相对于O轴结构对称。
由第一储气罐25、第二储气罐27、第三储气罐28；高压气体29；气压表24；截止阀31构成动力总成；高压气体29在第一储气罐25，第二储气罐27，第三储气罐28内的压强值由低到高，采用空气或者氮气，气压表24用于显示高压气体29的压强值，截止阀31用于开关第一储气罐25、第二储气罐27、第三储气罐28。
由第一行程开关19、第二行程开关21；第一液体5、第二液体13；二位四通电磁阀23；踏板26；三位六通控压阀30；触发板20；第六螺栓56构成 动力控制总成；第一行程开关19、第一行程开关21分别用第六螺栓56固定在第一机罩16上和第二缸盖14上，触发板20用第六螺栓56固定在第二封盖17的端面上，通过二位四通电磁阀23的通大气通道即回液口，分别将第一液体5、第二液体13充入液压缸总成的第一腔A、第二腔B内，为了不消耗高压气体29，液面高度高于二位四通电磁阀23和三位六通控压阀30的安装高度，二位四通电磁阀23将高压气体29的压强力接入到第一缸体7、第二缸体12的第一腔A、第二腔B内，三位六通控压阀30的进气口，分别连接到第一储气罐25、第二储气罐27、第三储气罐28的出气口上；三位六通控压阀30的出气口，连接到二位四通电磁阀23的进气口上，通过转动踏板26顺序接入第一储气罐25，第二储气罐27，第三储气罐28的高压气体29。
由连杆34；下轴瓦35；第二螺栓36；上轴瓦37；轴瓦盖38；上机罩39；第三螺栓40；曲轴41；下机罩42；滑道43；滑块44；第四螺栓45；轴盖46；第二密封垫47；飞轮48；第五螺栓49；连杆销50；卡簧片51；轴套52；第三密封垫71；第二轴承72；防尘圈73；第七螺栓74；第二轴盖75构成曲柄滑块总成；滑块44用第四螺栓45连接在活塞2的第一封盖1端面上，飞轮48的内径与曲轴41的外径过渡配合，用飞轮48的止口定位，用第五螺栓49连接固定在曲轴41上，上机罩39和下机罩42，用第一螺栓22与滑道43连接，用第三螺栓40相互连接，第一轴盖46、第二轴盖75、第一密封垫47、第二密封垫71用第七螺栓74固定在上机罩39和下机罩42上，由上机罩39和下机罩42装配后形成的第二空间D通大气，连杆34；下轴瓦35；上轴瓦37；轴瓦盖38；曲轴41；滑道43；滑块44；连杆销50；卡簧片51；轴套52；第二轴承72；防尘圈73；参照汽油发动机相似的零件制造安装。上机罩39中可以设置有通气孔，第二空间D可以通过该通气孔与大气相通。
本申请的原理是：活塞2在第一腔A、第二腔B的径向圆形截面，在第一限形轴53、第二限形轴54和第三限形轴58、第四限形轴59的表面间隙作用下，逐渐变形为长圆形截面，活塞2的截面面积也逐渐减少，即活塞2在第一腔A、第二腔B为变截面结构，开启截止阀31，旋转踏板26，接通高压气体29，当第一腔A进气通道打开，通大气通道关闭，同时第二腔B进气通道关闭，通大气通道打开时，高压气体29对第一腔A的第一液体5施加压强 力，第一液体5将高压气体29的压强力，传递作用在活塞2变截面的轴向投影面上，使活塞2克服阻力运动，进而带动滑块44、连杆34、曲轴41转动，当触发板20触碰第二行程开关21时，二位四通电磁阀23将第一腔A、第二腔B压力换向，使第二腔B进气通道打开，通大气通道关闭，同时第一腔A进气通道关闭，通大气通道打开，高压气体29对第二腔B液体13施加压强力，使活塞2做反向运动，形成活塞2做往复直线运动，在飞轮48的惯性作用下，使曲轴41连续同方向转动，当触发板20触碰第一行程开关19时，重复以上动作，形成循环，每次活塞2运动行程均可以做功，没有空行程，活塞2在第一腔A、第二腔B运动过程中保持体积不变，因此，第一液体5、第二液体13体积也不发生变化，高压气体29和第一液体5、第二液体13没有流动，在静压状态下推动活塞2运动。
通过人力或机械力转动踏板26，推动三位六通控压阀30的阀芯32，顺序接通第一储气罐25、第二储气罐27、第三储气罐28中的不同压强值的高压气体29，使活塞2获得由小到大的动力，因而使曲轴41输出由小到大的扭矩，放开踏板26，在弹簧33的作用下，阀芯32复位到关闭状态，如果增加本申请中储气罐的数量，高压气体29再对应增加大小不同的压强值，相应的三位六通控压阀30增加位数和通路数量，可以更加平顺地使本发动机获得由小到大的扭矩，类似汽车使用的汽油发动机油门的控制方式。
本申请活塞2与第一缸盖3、第二缸盖14及中缸体8的第一密封圈60、第五密封圈64、第六密封圈65、第九密封圈68之间采用第一液体5、第二液体13润滑，其它运动与运动付零件采用润滑油或油脂润滑。
图1、图2表达的是活塞2运动到二分之一行程时，即曲轴41旋转到90度时，本申请的结构状态。
下面结合图4对本申请装置的受力状况做说明：a、b、c、d是活塞2变截面的轴向投影面上的各受力面积，当二位四通电磁阀23的阀芯向左侧移动时，高压气体29的压强力，作用在第一液体5上，第一液体5的压强力作用在第一腔A活塞2上，此时，活塞2受到的力有：
1、第一腔A两处a面积上受第一液体5的压强力；方向与活塞2运动方向一致；
2、第二腔B两处a面积上大气的压强力，方向与活塞2运动方向相反；
3、第一腔A两处b面积上受第一液体5的压强力，方向与活塞2运动方向相反；
4、第二腔B两处b面积上大气的压强力，方向与活塞2运动方向一致；
5、第一腔A四处c面积上受第一液体5的压强力，方向与活塞2运动方向一致；
6、第二腔B四处c面积上受大气的压强力，方向与活塞2运动方向相反；
7、第一腔A、第二腔B的d面积不受第一液体5的压强作用；
8、与第一密封圈60、第五密封圈64、第六密封圈65、第九密封圈68的滑动摩擦阻力；方向与活塞2运动方向相反；
9、如果柔性体4选用液体，则第一腔A活塞2内表面受第一液体5传递给柔性体4的压强力，外表面受第一液体5的压强力；内外压强力互相抵消；
10、如果柔性体4选用液体，则第二腔B活塞2内表面受第一液体5传递给柔性体4的压强力，外表面受大气压力，内外有比较大的压强值差，设计时需要校核活塞2薄壁无缝钢管的许用应力；如果柔性体4选择弹性体，第二腔B活塞2的无缝钢管内表面压强没有变化，外表面受大气压力，设计时不需要校核薄壁无缝钢管的许用应力；因此，可以加大高压气体29的压强力；
11、八处第一轴承9产生的滚动摩擦阻力，数值很小忽略不计；
12、第一限形轴53、第二限形轴54和第三限形轴58、第四限形轴59的径向阻力，相互抵消。
下面结合图1、图2、图3、图4对本申请柔性体4选用液体时的一种实施方式做说明：
设活塞2材质为20CrMo无缝合金钢管；长度为912mm；壁厚为2mm；外圆直径为100mm；截面面积为78.5平方厘米；周长为31.4厘米；抗拉强度885MPa，设活塞2行程为150mm，即曲轴半径为75mm。
设柔性体4材质为液压油；压强值为0.12MPa；
设第一液体5、第二液体13材质为液压油；
设第三储气罐28内的高压气体29为高压空气；压强值3.5MPa；
设第三储气罐28耐压强度不低于6MPa；
设第一限形轴53、第二限形轴54及第三限形轴58、第四限形轴59材质为45CrMo；热处理硬度HRC60以上；直径为28mm；长度为212mm；第一限形轴53、第二限形轴54和第三限形轴58、第四限形轴59表面间隙为20mm；表面光滑；
设第一缸盖3、第二缸盖14，中缸体8，第一缸体7、第二缸体12材质为45CrMo，铸造；滑道43为球墨合金铸铁，第一机罩16为一般铸铁或为压铸件；
设第一封盖1、第二封盖17，封板11材质为45号钢；
设二位四通电磁阀23为标准件，三位六通控压阀30自制；
设第一密封圈60、第五密封圈64、第六密封圈65、第九密封圈68为轴用Y型，第二密封圈61、第三密封圈62、第四密封圈63、第七密封圈66、第八密封圈67、第十密封圈69，第十一密封圈70为O型，第一密封垫10、第二密封垫47、第三密封垫71为橡胶垫；
第一轴承9共八个，第二轴承72共两个，采用标准件；其它各零部件略；
将各零部件装配，本实施方式装配后，不包括曲轴41突出部分的外形尺寸为1450mm×332mm×272mm。
本实施方式活塞2受力计算如下：活塞2轴向投影各面积数值；a:58.9cm 2；b:8.34cm 2；c:6.4cm 2；高压气体29选最大压强值为3.5MPa,即35kg/cm 2。
1、第一腔A两处a面积上受第一液体5的压强力为2061kg；方向与活塞2运动方向一致；
2、第二腔B两处a面积上大气的压强力为58.9kg，方向与活塞2运动方向相反；
3、第一腔A两处b面积上受第一液体5的压强力为292kg，方向与活塞2运动方向相反；
4、第二腔B两处b面积上大气的压强力为8.34kg，方向与活塞2运动方向一致；
5、第一腔A四处c面积上受第一液体5的压强力为224kg，方向与活塞2运动方向一致；
6、第二腔B四处c面积上受大气的压强力为6.4kg，方向与活塞2运动方向相反；
7、第六密封圈65、第九密封圈68受第一腔A中第一液体5的压强力，与活塞2的滑动摩擦力，设密封唇与活塞2的接触面积共为31.4cm 2；取滑动摩擦阻力系数为0.3；则滑动摩擦阻力为330kg，方向与活塞2运动方向相反；
由以上数据计算出：活塞2受到向左侧最大力为1606kg，即活塞2输出动力1606kg，曲轴41的半径0.075米，则曲轴41输出扭矩为120.45kgm,即1205Nm,如果为双缸结构，则输出总扭矩为2410Nm。
校核第二腔B活塞2内表面受第一液体5传递给柔性体4压强力的许用应力：根据薄壁无缝钢管许用应力校核公式δ＝钢管壁厚×2×钢管材质的抗拉强度/钢管外径×系数，δ＝2×2×885/100×8＝4.425MPa，取δ＝3.5MPa，即第三储气罐28内的高压气体29的压强值为35kg/cm 2，第二储气罐27内的高压气体29的压强值设为20kg/cm 2；第一储气罐25内的高压气体29的压强值设为10kg/cm 2，因此，柔性体4的最大压强值为3.62MPa。
第一缸盖3、第二缸盖14；中缸体8；第一缸体7、第二缸体12，相互连接第一螺栓22，封板11与中缸体8的连接第四螺栓45，均需要校核许用应力。本申请使用的各种螺栓均采用高强度材质制造，例如45CrMo。第一缸盖3、第二缸盖14，第一缸体7、第二缸体12，中缸体8均需要校核缸壁的许用应力，设计时需要考虑螺栓的数量和第一缸盖3、第二缸盖14，第一缸体7、第二缸体12，中缸体8的壁厚及结构加强，本实施方式省略计算校核过程。
图3为本申请实施例提供的一种双缸气压发动机的局部剖面结构图，在图3中，如果取消EF轴之间的结构再合并为整体，则可以得到单缸结构的气压发动机，如果增加图3中EF轴之间的结构数量，则可以得到多缸结构的气 压发动机，本申请以单缸结构的气压发动机为例进行说明。
下面结合图1、图2、图3、图4对本申请柔性体4选用弹性体时的一种实施方式做说明：
设活塞2材质为20CrMo无缝合金钢管；长度为912mm；壁厚为2mm；外圆直径为100mm；截面面积为78.5平方厘米；周长为31.4厘米；抗拉强度885MPa，设活塞2行程为150mm，即曲轴半径为75mm。
设柔性体4材质为颗粒状聚氨酯橡胶；颗粒大小选3mm×3mm；
设第一液体5、第二13材质为液压油；
设第三储气罐28内的高压气体29为高压空气；压强值10MPa；
设第三储气罐28耐压强度不低于15MPa；
设第一限形轴53、第二限形轴54及第三限形轴58、第四限形轴59材质为45CrMo；热处理硬度HRC60以上；直径为28mm；长度为212mm；第一限形轴53、第二限形轴54和第三限形轴58、第四限形轴59表面间隙为30mm；表面光滑；
设第一缸盖3、第二缸盖14，中缸体8，第一缸体7、第二缸体12材质为45CrMo，铸造；滑道43为球墨合金铸铁，第一机罩16为一般铸铁或为压铸件；
设第一封盖1、第二封盖17，封板11材质为45号钢；
设二位四通电磁阀23为标准件，三位六通控压阀30自制；
设第一密封圈60、第五密封圈64、第六密封圈65、第九密封圈68为轴用Y型，第二密封圈61、第三密封圈62、第四密封圈63、第七密封圈66、第八密封圈67、第十密封圈69，第十一密封圈70为O型，第一密封垫10、第二密封垫47、第三密封垫71为橡胶垫；
第一轴承9共八个，第二轴承72共两个，采用标准件；其它各零部件略；
将各零部件装配，本实施方式装配后，不包括曲轴41突出部分的外形尺寸为1450mm×350mm×290mm。
本实施方式活塞2受力计算如下：活塞2轴向投影各面积数值；a:49.25cm 2；b:10.6cm 2；c:5.6cm 2；高压气体29选最大压强值为10MPa,即 100kg/cm 2。
1、第一腔A两处a面积上受第一液体5的压强力为4925kg；方向与活塞2运动方向一致；
2、第二腔B两处a面积上大气的压强力为49.25kg，方向与活塞2运动方向相反；
3、第一腔A两处b面积上受第一液体5的压强力为1060kg，方向与活塞2运动方向相反；
4、第二腔B两处b面积上大气的压强力为10.6kg，方向与活塞2运动方向一致；
5、第一腔A四处c面积上受第一液体5的压强力为560kg，方向与活塞2运动方向一致；
6、第二腔B四处c面积上受大气的压强力为5.6kg，方向与活塞2运动方向相反；
7、第六密封圈65、第九密封圈68受第一腔A第一液体5的压强力，与活塞2的滑动摩擦力，设密封唇与活塞2的接触面积共为31.4cm 2；取滑动摩擦阻力系数为0.3；则滑动摩擦阻力为942kg，方向与活塞2运动方向相反；
由以上数据计算出：活塞2受到向左侧最大力为3439kg，即活塞2输出动力3439kg，曲轴41的半径0.075米，则曲轴41输出扭矩为258kgm,即2580Nm,如果为双缸结构，则输出总扭矩为5160Nm。
本实施方式的柔性体4采用聚氨酯橡胶颗粒为固体，不需要校核活塞2无缝钢管内腔的许用应力，设计时，高压气体29的压强值为10MP，相对于柔性体4采用液体时加大，第三储气罐28内的高压气体29的压强值为100kg/cm 2，第二储气罐27内的高压气体29的压强值设为60kg/cm 2；第一储气罐25内的高压气体29的压强值设为20kg/cm 2。
第一缸盖3、第二缸盖14；中缸体8；第一缸体7、第二缸体12，相互连接第一螺栓22，封板11与中缸体8的连接第四螺栓45，均需要校核许用应力。本申请使用的各种螺栓均采用高强度材质制造，例如45CrMo。第一缸盖3、第二缸盖14，第一缸体7、第二缸体12，中缸体8均需要校核缸壁的许用应力，设计时需要考虑螺栓的数量和第一缸盖3、第二缸盖14，第一缸体7、 第二缸体12，中缸体8的壁厚及结构加强，本实施方式省略计算校核过程。
本申请用于制造活塞2的大直径薄壁无缝钢管和柔性体4的材料技术、工艺技术，是实施本申请的关键核心技术，无缝钢管和柔性体4材料的抗拉强度越高、延展性、耐曲挠性越好，本申请的使用寿命越长。
本申请的有益效果是：集开发和使用能源为一体，输入定量高压气体能量，持续把气体的压力能转换为机械能，结构简单，制造及使用成本低，体积可以小型化，也可以大型化，输出能量密度高，可以工业化生产，取代现有燃油、燃气发动机，不影响生态环境，可以为各种移动机械，舰船，汽车提供动力，也可以为固定大型机械提供动力，还可以为能源工业提供原动力。
以上所述仅为本申请的较佳实施例而已，并不用以限制本申请，凡在本申请的精神和原则之内，所做的任何修改、等同替换、改进等，均应包含在本申请保护的范围之内。

Claims (10)

  1. 一种气压发动机，其特征在于，是由零件第一封盖(1)；活塞(2)；第一缸盖(3)；柔性体(4)；第一液体(5)；安装座(6)；第一缸体(7)；中缸体(8)；第一轴承(9)；第一密封垫(10)；封板(11)；第二缸体(12)；第二液体(13)；第二缸盖(14)；定位销(15)；第一机罩(16)；第二封盖(17)；充液嘴(18)；第一行程开关(19)；触发板(20)；第二行程开关(21)；第一螺栓(22)；二位四通电磁阀(23)；气压表(24)；第一储气罐(25)；踏板(26)；第二储气罐(27)；第三储气罐(28)；高压气体(29)；三位六通控压阀(30)；截止阀(31)；阀芯(32)；弹簧(33)；连杆(34)；下轴瓦(35)；第二螺栓(36)；上轴瓦(37)；轴瓦盖(38)；上机罩(39)；第三螺栓(40)；曲轴(41)；下机罩(42)；滑道(43)；滑块(44)；第四螺栓(45)；第一轴盖(46)；第二密封垫(47)；飞轮(48)；第五螺栓(49)；连杆销(50)；卡簧片(51)；轴套(52)；第一限形轴(53)；第二限形轴(54)；第一挡板(55)；第六螺栓(56)；第二挡板(57)；第三限形轴(58)；第四限形轴(59)；第一密封圈(60)；第二密封圈(61)；第三密封圈(62)；第四密封圈(63)；第五密封圈(64)；第六密封圈(65)；第七密封圈(66)；第八密封圈(67)；第九密封圈(68)；第十密封圈(69)；第十一密封圈(70)；第三密封垫(71)；第二轴承(72)；防尘圈(73)；第七螺栓(74)；第二轴盖(75)构成的装置，是由液压缸总成、活塞总成、动力总成、动力控制总成和曲柄滑块总成部件装配构成；由所述第一缸盖(3)、所述第二缸盖(14)、所述第一缸体(7)、所述第二缸体(12)、所述中缸体(8)、所述第一密封圈(60)、所述第二密封圈(61)、所述第三密封圈(62)、所述第四密封圈(63)、所述第五密封圈(64)、所述第六密封圈(65)、所述第七密封圈(66)、所述第八密封圈(67)、所述第九密封圈(68)、所述第十密封圈(69)、所述第十一密封圈(70)、所述第一限形轴(53)、所述第二限形轴(54)、所述第三限形轴58)、所述第四限形轴(59)、所述第一轴承(9)、所述第一密封垫(10)、所述封板(11)、所述定位销(15)、所述第一螺栓(22)、所述第二螺栓(56)、所述第一挡板(55)、所述第二挡板(57)、所述第一机罩(16)构成具有第一腔(A)、第二腔(B)的所述液压缸总成；其中，所述第一缸盖(3)、所述第二缸盖(14)、 所述第一缸体(7)、所述第二缸体(12)和所述中缸体(8)之间用所述定位销(15)定位，所述第一螺栓(22)连接，所述第一缸盖(3)、所述第二缸盖(14)、所述中缸体(18)的活塞口设有凹槽，安装所述第一密封圈(60)、所述第五密封圈(64)、所述第六密封圈(65)、所述第九密封圈(68)，所述第一缸盖(3)、所述第二缸盖(14)，所述中缸体(8)的两端、所述滑道(43)的一端法兰接合面设有凹槽，安装所述第二密封圈(61)、所述第三密封圈(62)、所述第四密封圈(63)、所述第七密封圈(66)、所述第八密封圈(67)、所述第十密封圈(69)，所述第十一密封圈(70)，所述第一限形轴(53)、所述第二限形轴(54)、所述第三限形轴(58)、所述第四限形轴(59)两端装配有所述第一轴承(9)，安装在所述中缸体(8)的安装孔内，所述第一挡板(55)、所述第二挡板(57)用外轮廓定位，所述第六螺栓(56)连接，固定在所述中缸体(8)两端的活塞口的凹槽内，所述第一密封垫(10)和所述封板(11)，用所述第四螺栓(45)连接在所述中缸体(8)的两个安装面上；由所述第一封盖(1)、所述第二封盖(17)、所述活塞(2)、所述柔性体(4)和所述充液嘴(18)构成所述活塞总成；所述活塞(2)两端面内径与所述第一封盖(1)、所述第二封盖(17)法兰凸台外径紧密配合，所述活塞(2)两端面与所述第一封盖(1)、所述第二封盖(17)的法兰面焊接密封；由所述第一储气罐(25)、所述第二储气罐(27)、所述第三储气罐(28)、所述高压气体(29)、所述气压表(24)和所述截止阀(31)构成所述动力总成；由所述第一行程开关(19)、所述第二行程开关(21)、所述第一液体(5)、所述第二液体(13)、所述二位四通电磁阀(23)、所述踏板(26)、所述三位六通控压阀(30)、所述触发板(20)和所述第六螺栓(56)构成所述动力控制总成；所述第一行程开关(19)、所述第二行程开关(21)分别用所述第六螺栓(56)固定在所述第一机罩(16)上和所述第二缸盖(14)上，所述触发板(20)用所述第六螺栓(56)固定在所述第二封盖(17)的端面上，所述二位四通电磁阀(23)将所述高压气体(29)的压强力接入到所述第一缸体(7)、所述第二缸体(12)的所述第一腔(A)、所述第二腔(B)内，所述三位六通控压阀(30)的进气口，分别连接到所述第一储气罐(25)、所述第二储气罐(27)、所述第三储气罐(28)的出气口上；所述三位六通控压阀(30)的出气口，连接到所述 二位四通电磁阀(23)的进气口上，通过转动所述踏板(26)顺序接入所述第一储气罐(25)、所述第二储气罐(27)和所述第三储气罐(28)的所述高压气体(29)，由所述连杆(34)、所述下轴瓦(35)、所述第二螺栓(36)、所述上轴瓦(37)、所述轴瓦盖(38)、所述上机罩(39)、所述第三螺栓(40)；所述曲轴(41)、所述下机罩(42)、所述滑道(43)、所述滑块(44)、所述第四螺栓(45)、所述第一轴盖(46)、所述第二密封垫(47)、所述飞轮(48)、所述第五螺栓(49)、所述连杆销(50)、所述卡簧片(51)、所述轴套(52)、所述第三密封垫(71)、所述第二轴承(72)、所述防尘圈(73)、所述第七螺栓(74)和所述第二轴盖(75)构成所述曲柄滑块总成；所述滑块(44)用所述第四螺栓(45)连接在所述活塞(2)的所述第一封盖(1)端面上，所述飞轮(48)的内径与所述曲轴(41)的外径过渡配合，用所述飞轮(48)的止口定位，用所述第五螺栓(49)连接固定在所述曲轴(41)上，所述上机罩(39)和所述下机罩(42)，用所述第一螺栓(22)与所述滑道(43)连接，用所述第三螺栓(40)相互连接，所述第一轴盖(46)、所述第二轴盖(75)、所述第二密封垫(47)、所述第三密封垫(71)用所述第七螺栓(74)固定在所述上机罩(39)和所述下机罩(42)上。
  2. 根据权利要求1所述的气压发动机，其特征在于，所述第一缸盖(3)、所述第二缸盖(14)的活塞口为圆形，所述中缸体(8)的活塞口为长圆形，所述第一限形轴(53)、第二所述限形轴(54)及所述第三限形轴(58)、所述第四限形轴(59)之间的轴表面之间的间隙，与所述中缸体(8)长圆活塞孔的宽度一致，所述第一机罩(16)装配后，内部第一空间(C)通大气，在所述第一缸体(7)、所述第二缸体(12)及所述下机罩(42)下面分别设计有六处所述安装座(6)，用于安装固定所述气压发动机。
  3. 根据权利要求1所述的气压发动机，其特征在于，所述活塞(2)外壁由薄壁无缝圆形钢管制造；所述活塞(2)内腔填充所述柔性体(4)，所述柔性体(4)由液体或者弹性体构成。
  4. 根据权利要求1所述的气压发动机，其特征在于，所述活塞(2)与液压缸总成装配后，通过在所述第二封盖(17)上安装的所述充液嘴(18)，向所述活塞(2)腔内充入液体作为所述柔性体(4)，并且加压，使所述柔性 体(4)的压强值高于高压气体(29)的最大压强值，并且达到预设时长，然后减压，在所述柔性体(4)压强0.11MP至0.15MP状态下，将所述柔性体(4)密封在所述活塞(2)的内腔。
  5. 根据权利要求1所述的气压发动机，其特征在于，所述活塞(2)的无缝钢管内，以及管壁之间无间隙装入有整体、分体或者颗粒状弹性体，作为所述柔性体(4)，所述柔性体(4)为橡胶、硅胶或热塑性弹性体，所述第一封盖(1)、所述第二封盖(17)与无缝钢管通过焊接进行密封。
  6. 根据权利要求1所述的气压发动机，其特征在于，所述高压气体(29)在所述第一储气罐(25)、所述第二储气罐(27)、所述第三储气罐(28)内的压强值由低到高，所述高压气体(29)为空气或者氮气。
  7. 根据权利要求1所述的气压发动机，其特征在于，所述二位四通电磁阀(23)的通大气通道即回液口，用于分别将所述第一液体(5)、所述第二液体(13)充入液压缸总成的所述第一腔(A)、所述第二腔(B)内，所述第一腔(A)和所述第二腔(B)的液面高度高于所述二位四通电磁阀(23)和所述三位六通控压阀(30)的安装高度。
  8. 根据权利要求1所述的气压发动机，其特征在于，由所述上机罩(39)和所述下机罩(42)装配后形成的第二空间(D)通大气。
  9. 根据权利要求1所述的气压发动机，其特征在于，所述活塞(2)在所述第一腔(A)、所述第二腔(B)的径向圆形截面，在所述第一限形轴(53)、所述第二限形轴(54)和所述第三限形轴(58)、所述第四限形轴(59)的表面间隙作用下，逐渐变形为长圆形截面，所述活塞(2)的截面面积也逐渐减少，即所述活塞(2)在所述第一腔(A)、所述第二腔(B)为变截面结构，开启所述截止阀(31)，旋转所述踏板(26)，接通所述高压气体(29)，当所述第一腔(A)进气通道打开，通大气通道关闭，同时所述第二腔(B)腔进气通道关闭，通大气通道打开时，所述高压气体(29)对所述第一腔(A)的所述第一液体(5)施加压强力，所述第一液体(5)将所述高压气体(29)的压强力，传递作用在所述活塞(2)变截面的轴向投影面上，使所述活塞(2)克服阻力运动，进而带动所述滑块(44)、所述连杆(34)、所述曲轴(41)转动，当所述触发板(20)触碰所述第二行程开关(21)时，所述二位四通 电磁阀(23)将所述第一腔(A)、所述第二腔(B)腔压力换向，使所述第二腔(B)进气通道打开，通大气通道关闭，同时所述第一腔(A)进气通道关闭，通大气通道打开，所述高压气体(29)对所述第二腔(B)的所述第二液体(13)施加压强力，使所述活塞(2)做反向运动，形成所述活塞(2)做往复直线运动，在所述飞轮(48)的惯性作用下，使所述曲轴(41)连续同方向转动，当所述触发板(20)触碰所述第一行程开关(19)时，重复以上动作，形成循环，每次所述活塞(2)运动行程均可以做功，没有空行程，所述活塞(2)在所述第一腔(A)、所述第二腔(B)运动过程中保持体积不变，所述第一液体(5)、所述第二液体(13)体积也不发生变化，所述高压气体(29)和所述第一液体(5)、所述第二液体(13)没有流动，在静压状态下推动所述活塞(2)运动。
  10. 根据权利要求1所述的气压发动机，其特征在于，通过人力或机械力转动所述踏板(26)，推动所述三位六通控压阀(30)的所述阀芯(32)，顺序接通所述第一储气罐(25)、所述第二储气罐(27)、所述第三储气罐(28)中的不同压强值的所述高压气体(29)，使所述活塞(2)获得由小到大的动力，因而使所述曲轴(41)输出由小到大的扭矩。
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