CN102031993B - Two-stage expansion piston air motor device - Google Patents
Two-stage expansion piston air motor device Download PDFInfo
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- CN102031993B CN102031993B CN 201010622654 CN201010622654A CN102031993B CN 102031993 B CN102031993 B CN 102031993B CN 201010622654 CN201010622654 CN 201010622654 CN 201010622654 A CN201010622654 A CN 201010622654A CN 102031993 B CN102031993 B CN 102031993B
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Abstract
The invention discloses a two-stage expansion piston air motor device. A reducing valve is connected with an air tank through a hose; one end of a throttling valve is connected with the reducing valve, and the other end of the throttling valve is connected with a valve port at the lower end of an electromagnetic reversing valve; the other valve port is connected with a transition air tank and a heat exchange system; two valve ports at the upper end of the electromagnetic reversing valve are connected with a first-stage cylinder; a piston rod in the first-stage cylinder is connected with the right end of a rack; the left end of the rack is connected with a second-stage cylinder; an upper cylindrical gear is arranged above the rack, and a lower cylindrical gear is arranged below the rack; the rack forms two pairs of gear pairs with the upper gear and the lower gear; two valve ports at the upper end of the electromagnetic reversing valve are connected with two working cavities of the second-stage cylinder through hoses; and a valve port at the lower end of the electromagnetic reversing valve is connected with the transition air tank and the heat exchange system through hoses, and the other valve port is connected with the external environment through a hose. An automobile power device which takes compressed air as a power source can drive a vehicle to run instead of petroleum, diesel oil or liquefied petroleum gas fuel, so that real zero emission of tail gas of automobiles is realized.
Description
Technical field
The present invention relates to use pressurized air as power source, can drive the power plant of Vehicle Driving Cycle, particularly a kind of double expansion piston type pneumatic engine device.
Background technique
According to statistics, at present whole world consumption of petroleum amount every day is about 50,000,000 barrels, accounts for 50% and wherein be used for the communications and transportation aspect, therein, automobile account for 80% with oil.The verified oil reserves in the whole world, calculate only available about 40 years by present consumption of petroleum amount at present.Therefore, if still with the unique energy of oil as automobile power, automotive industry will be walked to be at the end soon.On the other hand, vehicle exhaust has become the first pollution sources of the pollutant such as CO, NOx and CH in China big city.The great amount of carbon dioxide gas that burning is discharged is the main cause that causes global greenhouse effect.The incomplete combustion of automotive fuel also becomes one of reason that in air, suspending particulate matter increases.
In order to solve or postpone the aspect problems such as the energy that automobile industry development brings, environment, Modern Engine is employed new technology and is reduced discharging and fuel consumption rate.But, no matter be the advanced electron spraying system motor of employing, install TWC Three Way Catalyst System additional, adopt the technology such as EGR, mixed power, still adopt the replacing fuel oil motors such as compressed natural gas, liquefied petroleum gas (LPG), automobile power is all take internal-combustion engine as the basis, can only reduce the discharge amount of dusty gas, can not realize truly " zero-emission ".
Chinese patent CN1851260A has proposed a kind of vehicle motor that uses compressed air, utilizes clean energy resource---and pressurized air promotes steam-cylinder piston, and is similar to ordinary internal combustion engine by the slidercrank mechanism outputting power.Also conduct in-depth research for this driving structure in Zhejiang University's thesis for the doctorate " air motor working procedure and key components and parts optimization research ", and transform the expansion experimental study on the water-cooled diesel engine basis.Although they have utilized pressurized gas to carry out expansion working, but still adopt slidercrank mechanism on drive mechanism, just work done during its chamber expansion pushing piston, and not work done when the piston revesal is moved, and the not work done of lateral force of crank countercylinder affects system works efficient.
Summary of the invention
The object of the present invention is to provide a kind of automotive powerplant that uses the compressed air source, the pressurized air of use can replace gasoline, diesel oil or LP gas fuel, drives Vehicle Driving Cycle, can realize real " zero-emission " of vehicle exhaust.
The technical solution that realizes the object of the invention is: a kind of double expansion piston type pneumatic engine device comprises gas tank, one-level cylinder, secondary cylinder, reduction valve, throttle valve, solenoid directional control valve, tooth bar, cogs, lower gear and transition gas tank and heat-exchange system; Reduction valve is connected with gas tank by flexible pipe, one end of throttle valve connects reduction valve, the other end of throttle valve is connected with a valve port of solenoid directional control valve lower end, another valve port is connected to transition gas tank and heat-exchange system, two valve ports of solenoid directional control valve upper end are connected to the one-level cylinder, piston rod in the one-level cylinder directly is connected with the right-hand member of tooth bar, and the left end of tooth bar directly is connected with secondary cylinder; The top of tooth bar is provided with a cylinder and cogs, and the below of tooth bar is provided with a cylinder lower gear, tooth bar with cog and lower gear formed two pairs of gear pairs; Two valve ports of solenoid directional control valve upper end are connected with two active chambers of secondary cylinder respectively by flexible pipe, and a valve port of solenoid directional control valve lower end is connected with transition gas tank and heat-exchange system by flexible pipe, and another valve port is connected to external environment by flexible pipe.
The present invention compared with prior art, its remarkable advantage: (1) the present invention adopts two-stage cylinder expansion working, the exhaust that is the one-level cylinder utilizes dump energy again as the source of the gas of secondary cylinder, wherein absorbs extraneous portion of energy through over-heat-exchanger again, has improved the energy utilization efficiency.(2) the ouput force direction of cylinder is identical with tooth bar moving direction, and without the lateral force loss, energy transfer efficiency is higher than the piston crank structure of traditional combustion engine.Two side cavity of (3) cylinders are all as active chamber, the two-way power that provides of to-and-fro motion, and the power output of output shaft is comparatively steady, compact structure.
Description of drawings
Fig. 1 is the pressure control loop system schematic of the double expansion piston type pneumatic motor of proposition according to the present invention.
Fig. 2 is mechanical transmission output system schematic diagram of the present invention.
Fig. 3, Fig. 4, Fig. 5 and Fig. 6 are that gear unidirectional power of the present invention transmits schematic diagram.
Embodiment
Below in conjunction with accompanying drawing, the present invention is described in further detail.
Be illustrated in figure 1 as pressure control loop system schematic of the present invention.Comprising a gas tank 1 is arranged, the pressurized gas of 30Mpa is arranged in gas tank, reduction valve 2 is connected with 1 by flexible pipe, and its effect is the pressurized gas of the 30Mpa 1Mpa that reduces pressure.After throttle valve 3 is connected to reduction valve 2, the effect of throttle valve 3 be can adjustments of gas uninterrupted.A valve port of the lower end of the first solenoid directional control valve 4 is connected to throttle valve 3, the effect that another valve port is connected to transition gas tank and heat- exchange system 10,10 be can make through the heat of GAS ABSORPTION external environment.Two valve ports of 4 upper ends are connected to one-level cylinder 5.The piston rod that the one-level cylinder is 5 li directly is connected with the right-hand member of tooth bar 6, and the left end of tooth bar 6 directly is connected with secondary cylinder 8.Tooth bar 6 a cylindrical gears 7 respectively arranged up and down, tooth bar 6 has formed two pairs of gear pairs with cog 7-1 and lower gear 7-2.Two valve ports of the upper end of the second solenoid directional control valve 9 are connected with two active chambers of secondary cylinder 8 by flexible pipe, and a valve port of 9 lower end is connected with transition gas tank and heat-exchange system 10 by flexible pipe, and another valve port is connected to external environment by flexible pipe.After device is started working, pressurized gas are filled with the right side active chamber of one-level cylinder 5 from gas tank 1 by reduction valve 2 and throttle valve 3 by the first solenoid directional control valve 4, after gas in the left side active chamber of one-level cylinder 5 absorbs external heat by heat exchanger 10 simultaneously, be filled with the right side active chamber of secondary cylinder 8, pressurized gas while pushing piston bar in one-level cylinder 5 and secondary cylinder 8 and tooth bar 6 are to left movement, and the gas in the left side active chamber of secondary cylinder 8 is discharged in external environment.
When moving, tooth bar 6 arrives the end of movement travel left, the first solenoid directional control valve 4 and the second solenoid directional control valve 9 intake and exhaust commutations, post-decompression gas is filled with the left side active chamber of one-level cylinder 5, the gas that in the right side active chamber of one-level cylinder 5, the lastrow journey is filled with simultaneously is filled with the left side active chamber of secondary cylinder 8 through heat exchanger 10, pressurized gas while pushing piston bar and tooth bar 6 in one-level cylinder 5 and secondary cylinder 8 move right, and the gas in secondary cylinder 8 right side active chambers is discharged in external environment.
When cylinder piston moves to end of travel, again make the solenoid directional control valve commutation, continue to repeat said process, circulation and so forth drives tooth bar 6 to-and-fro motion.
When moving, tooth bar 6 arrives the end of movement travel left, the first solenoid directional control valve 4 and the second solenoid directional control valve 9 intake and exhaust commutations.Cylinder 5 and 8 push rod promote tooth bar 6 and move right.When tooth bar 6 arrives the movement travel of right-hand member, the first solenoid directional control valve 4 and the second solenoid directional control valve 9 intake and exhaust commutations, tooth bar reversing motion.Whole working procedure circulates and so forth.
In conjunction with Fig. 2,3,4,5,6, when cylinder 5 and 8 push rod promote tooth bar 6 motion, drive cog 7-1 and lower gear 7-2 rotation, the 7-1 that cogs connects with unilateral bearing 16 by flat key 18, flat key 17 connection unilateral bearing 16 and transmission shaft 11-1.Gear 12-1 is arranged on the other end of transmission shaft 11-1, and gear 12-1 connects with unilateral bearing 19 by flat key 21, and flat key 20 connects unilateral bearing 19 and transmission shaft 11-1.Lower gear 7-2 connects with unilateral bearing 22 by flat key 24, and flat key 23 connects unilateral bearing 22 and transmission shaft 11-2.Gear 12-2 is arranged on the other end of transmission shaft 12-2, and gear 12-2 connects with unilateral bearing 25 by flat key 27, and flat key 26 connects unilateral bearing 25 and transmission shaft 11-2.Unilateral bearing 16,19,22 and 25 effect are the transferring power that can only turn clockwise, and another direction can only dally can not transferring power., drive the 7-1 that cogs and turn clockwise during to left movement when tooth bar 6, the 7-1 that cogs turns clockwise by transmission shaft 11-1 driven gear 12-1, and driven gear 13 is rotated counterclockwise, and gear 13 is connected with pto＝power take-off 15 by flat key 14.Gear 13 is rotated counterclockwise, and drives pto＝power take-off 15 rotations, output mechanical energy.Simultaneously lower gear 7-2 is rotated counterclockwise, but due to unilateral bearing 25 transferring power that can only turn clockwise, transmission shaft 11-2 is motionless.When tooth bar 6 moved right, lower gear 7-2 turned clockwise, and drove transmission shaft 11-2 and gear 12-2 rotation, and then gear 12-2 driven gear 13 and pto＝power take-off 15 are rotated counterclockwise, output mechanical energy.Cog 7-1 when tooth bar moves right, can not transferring power because of the effect of unilateral bearing 16, transmission shaft 11-1 is motionless.When tooth bar 6 moved back and forth, whole power transmission process circulated and so forth.
Adopt the present invention program to carry out theoretical calculating: to establish the pressurized gas 0.3m that has stored 30Mpa in gas tank
3, weight is that the dolly of 1000kg is with the speed per hour of 60km/h per hour.Rolling coefficient in road surface is 0.01, and coefficient of air resistance is 0.5, wind-exposuring area 1.5/m
2, air density is 1.2258kg/m
3, machinery driving efficiency is 0.9.
Adiabatic expansion acting makes the automobile 69.4km that can travel, and the isothermal expansion acting can make automobile running 188.5km.The general gas flow acting is between adiabatic expansion acting and isothermal expansion acting, is also that the distance of travelling of automobile is between 69.4～188.5km.
Claims (9)
1. double expansion piston type pneumatic engine device, comprise gas tank (1), one-level cylinder (5), secondary cylinder (8), it is characterized in that: comprise also that reduction valve (2), throttle valve (3), the first solenoid directional control valve (4), the second solenoid directional control valve (9), tooth bar (6), cylinder cog (7-1), cylinder lower gear (7-2) and transition gas tank and heat-exchange system (10); reduction valve (2) is connected with gas tank (1) by flexible pipe, one end of throttle valve (3) connects reduction valve (2), the other end of throttle valve (3) is connected with a valve port of the first solenoid directional control valve (4) lower end, another valve port of the first solenoid directional control valve (4) lower end is connected to transition gas tank and heat-exchange system (10), two valve ports of the first solenoid directional control valve (4) upper end are connected to one-level cylinder (5), the inner piston rod of one-level cylinder (5) directly is connected with the right-hand member of tooth bar (6), the left end of tooth bar (6) directly is connected with secondary cylinder (8), the top of tooth bar (6) is provided with a cylinder cog (7-1), the below of tooth bar (6) is provided with a cylinder lower gear (7-2), and tooth bar (6) cogs (7-1) with cylinder and cylinder lower gear (7-2) has formed two pairs of gear pairs, two valve ports of the second solenoid directional control valve (9) upper end are connected with two active chambers of secondary cylinder (8) respectively by flexible pipe, a valve port of the second solenoid directional control valve (9) lower end is connected with transition gas tank and heat-exchange system (10) by flexible pipe, and another valve port is connected to external environment by flexible pipe, cylinder cog (7-1) be connected with the first unilateral bearing (16) by flat key (18), flat key (17) connects the first unilateral bearing (16) and the first transmission shaft (11-1), and the first gear (12-1) is arranged on the other end of the first transmission shaft (11-1), the first gear (12-1) connects with the second unilateral bearing (19) by flat key (21), flat key (20) connects the second unilateral bearing (19) and the first transmission shaft (11-1), cylinder lower gear (7-2) connects with the 3rd unilateral bearing (22) by flat key (24), flat key (23) connects the 3rd unilateral bearing (22) and second driving shaft (11-2), and the second gear (12-2) is arranged on the other end of second driving shaft (11-2), the second gear (12-2) connects with the 4th unilateral bearing (25) by flat key (27), flat key (26) connects the 4th unilateral bearing (25) and second driving shaft (11-2), the first gear (12-1) and the second gear (12-2) and gear (13) engagement, gear (13) is connected with pto＝power take-off (15) by flat key (14).
2. double expansion piston type pneumatic engine device according to claim 1, it is characterized in that: valve port in the valve port of the first solenoid directional control valve (4) two of upper ends and the right active chamber of one-level cylinder (5) are connected, and the left active chamber of another valve port and one-level cylinder (5) is connected.
3. double expansion piston type pneumatic engine device according to claim 1, it is characterized in that: a right active chamber with secondary cylinder (8) in the valve port of the second solenoid directional control valve (9) two of upper ends is connected, and the left active chamber of another valve port and secondary cylinder (8) is connected.
4. double expansion piston type pneumatic engine device according to claim 1, it is characterized in that: the piston rod of one-level cylinder (5) connects by the screw thread drive fit with the right-hand member of tooth bar (6), and the piston rod of secondary cylinder (8) connects by the screw thread drive fit with the left end of tooth bar (6).
5. double expansion piston type pneumatic engine device according to claim 1, it is characterized in that: the upper and lower surface of tooth bar (6) all has tooth, and the left and right end respectively has a tapped hole.
6. double expansion piston type pneumatic engine device according to claim 2, it is characterized in that: respectively there is a chute in the interior outside of each unilateral bearing.
7. double expansion piston type pneumatic engine device according to claim 1 and 2, it is characterized in that: cylinder cogs (7-1), respectively there is a chute cylinder lower gear (7-2), the first gear (12-1) and the second gear (12-2) upper inboard, connects with unilateral bearing by flat key.
8. double expansion piston type pneumatic engine device according to claim 1 and 2, it is characterized in that: the first transmission shaft (11-1), second driving shaft (11-2) a keyway each side arranged, by flat key cog with cylinder (7-1) respectively, cylinder lower gear (7-2), the first gear (12-1) and the second gear (12-2) connect.
9. double expansion piston type pneumatic engine device according to claim 2, it is characterized in that: there is a keyway on the right side of output shaft (15), connects with gear (13) by flat key (14).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201010622654 CN102031993B (en) | 2010-12-30 | 2010-12-30 | Two-stage expansion piston air motor device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201010622654 CN102031993B (en) | 2010-12-30 | 2010-12-30 | Two-stage expansion piston air motor device |
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| Publication Number | Publication Date |
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| CN102031993A CN102031993A (en) | 2011-04-27 |
| CN102031993B true CN102031993B (en) | 2013-06-05 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN 201010622654 Expired - Fee Related CN102031993B (en) | 2010-12-30 | 2010-12-30 | Two-stage expansion piston air motor device |
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Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102031993B (en) * | 2010-12-30 | 2013-06-05 | 南京理工大学 | Two-stage expansion piston air motor device |
| CN102493967A (en) * | 2011-11-21 | 2012-06-13 | 三一汽车起重机械有限公司 | Crane, rotation control system thereof and rotation buffering valve of crane |
| CN104154204B (en) * | 2014-07-31 | 2016-06-01 | 炬荣（三明)农业科技有限公司 | A kind of oil pressure promotes device |
| CN104295322B (en) * | 2014-10-13 | 2016-08-24 | 太原理工大学 | A kind of air motor using screw rod transmission |
| CN104819285A (en) * | 2015-03-26 | 2015-08-05 | 成都力鑫科技有限公司 | Piston for pneumatic engine |
| CN104806295A (en) * | 2015-03-26 | 2015-07-29 | 成都力鑫科技有限公司 | Double-cylinder pneumatic engine driving device |
| CN106196869B (en) * | 2016-07-15 | 2019-05-03 | 青岛海尔股份有限公司 | Slide mechanism of drawer and refrigerator with it |
| CN106812603A (en) * | 2017-01-11 | 2017-06-09 | 浙江大学 | A kind of pancake engine |
| CN107387168B (en) * | 2017-08-03 | 2018-12-18 | 冯袖幅 | Pneumoelectric power device |
| CN109838353A (en) * | 2019-03-27 | 2019-06-04 | 吉林大学 | A kind of novel hydrogen cell automobile high-pressure hydrogen storing pressure tank energy recyclable device |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1184205A (en) * | 1997-09-18 | 1998-06-10 | 姚保民 | Pneumatic engine |
| US7121232B1 (en) * | 1999-10-25 | 2006-10-17 | Timo Tapani Janhunen | Method in an internal combustion engine and an internal combustion engine |
| CN101476490A (en) * | 2009-01-16 | 2009-07-08 | 华南理工大学 | Expansion ratio adjustable pneumatic engine for automobile and its exhaust pressure control method |
| CN102031993A (en) * | 2010-12-30 | 2011-04-27 | 南京理工大学 | Two-stage expansion piston air motor device |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN202125319U (en) * | 2010-12-30 | 2012-01-25 | 南京理工大学 | Two-stage expansion piston type pneumatic engine device |
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2010
- 2010-12-30 CN CN 201010622654 patent/CN102031993B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1184205A (en) * | 1997-09-18 | 1998-06-10 | 姚保民 | Pneumatic engine |
| US7121232B1 (en) * | 1999-10-25 | 2006-10-17 | Timo Tapani Janhunen | Method in an internal combustion engine and an internal combustion engine |
| CN101476490A (en) * | 2009-01-16 | 2009-07-08 | 华南理工大学 | Expansion ratio adjustable pneumatic engine for automobile and its exhaust pressure control method |
| CN102031993A (en) * | 2010-12-30 | 2011-04-27 | 南京理工大学 | Two-stage expansion piston air motor device |
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| CN102031993A (en) | 2011-04-27 |
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