CN101555829B - Free piston load response engine - Google Patents
Free piston load response engine Download PDFInfo
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- CN101555829B CN101555829B CN 200810177541 CN200810177541A CN101555829B CN 101555829 B CN101555829 B CN 101555829B CN 200810177541 CN200810177541 CN 200810177541 CN 200810177541 A CN200810177541 A CN 200810177541A CN 101555829 B CN101555829 B CN 101555829B
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- 230000005520 electrodynamics Effects 0.000 claims description 5
- 230000015572 biosynthetic process Effects 0.000 claims description 3
- 230000006835 compression Effects 0.000 abstract description 16
- 238000007906 compression Methods 0.000 abstract description 16
- 239000000446 fuel Substances 0.000 abstract description 10
- 230000000694 effects Effects 0.000 description 9
- 238000006073 displacement reaction Methods 0.000 description 6
- 239000003921 oil Substances 0.000 description 6
- MWUXSHHQAYIFBG-UHFFFAOYSA-N Nitric oxide Chemical group O=[N] MWUXSHHQAYIFBG-UHFFFAOYSA-N 0.000 description 5
- 238000002485 combustion reaction Methods 0.000 description 3
- 230000007613 environmental effect Effects 0.000 description 2
- 239000000295 fuel oil Substances 0.000 description 2
- 239000007789 gas Substances 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000015556 catabolic process Effects 0.000 description 1
- 238000006731 degradation reaction Methods 0.000 description 1
- 238000005474 detonation Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 238000004146 energy storage Methods 0.000 description 1
- 230000005713 exacerbation Effects 0.000 description 1
- 239000002360 explosive Substances 0.000 description 1
- 238000010304 firing Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
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Abstract
The invention discloses a free piston load response engine. The engine comprises cylinders and free pistons. The free pistons are arranged in the cylinders which are coaxially arranged. Backs of the free pistons are connected by connector, an adjustable distance device is arranged between the cylinders coaxially arranged, between the connectors of all the cylinders, between fixtures of the cylinders or between followers of the cylinders, and an adjustable stroke control device is arranged between the free pistons, the connectors of the free pistons, fixtures of the free pistons or followers ofthe free pistons and the cylinders matched with the free pistons, the connectors of all the cylinders, the fixtures of the cylinders or the followers of the cylinders. The engine can regulate air cap acity and compression ratio according to different fuels and load change so as to enhance efficiency, low discharge capacity and applicability of the engine.
Description
Technical field
The present invention relates to engine art.
Background technique
As everyone knows, reciprocating internal combustion engine has had the history in more than 100 year, is a kind of extremely successful hot merit switch machine.But the human energy environment issues that runs into is had higher requirement to the hot merit switch machine at present.For this reason, reciprocating internal combustion engine just seems that volume is large, weight is large, efficient is low, low emission is poor.In the last few years, people began to pay attention to especially the research and development of free piston engine.Compare with reciprocating-piston engine, free piston engine has the advantages such as efficient is high, emission performance good, and volume is little, lightweight.But the stroke of free-piston engine and the control of compression ratio never are resolved, and have also become the huge obstacle of free-piston engine commercial applications.
Need to invent a kind of discharge amount (stroke) and the controllable novel free-piston engine of geometrical compression ratio, to improve efficient, low emission and the applicability of free-piston engine for this reason.
Summary of the invention
The greatest drawback of conventional reciprocating formula motor is that piston does not have moment to bent axle at blast stroke top dead center, and also less in suitable corner moment of resistance, thereby make high temperature and high pressure gas in the cylinder long heat loss that causes of holding time large, nitrogen oxide forms many, and efficient is low, and it is poor to discharge.And free piston engine is quite different, and piston just has very large moment when the blast stroke begins, and gas expansion is fast in the firing chamber, and heat loss is little, and nitrogen oxide forms few, and efficient is high, discharges.But the stroke of free-piston engine and the control of compression ratio are very difficult, are the huge obstacles of free-piston engine commercial applications always.
Which kind of explosive motor all is a kind of hot merit switch machine.The core of its efficient is the temperature and pressure after cylinder combustion is burnt, i.e. operating mode after the burning.Operating mode after the burning determines the thermal efficiency of motor, and the operating mode after the burning is to be determined by the operating mode before the burning and air fuel ratio basically.So pressure, temperature and air fuel ratio in the burning front air cylinder have determined the thermal efficiency of motor basically, and the amount of air determines motor power in the cards.In principle, the temperature after the burning more high pressure is also just larger, and efficient is also just higher.Under the prerequisite of the practical factors such as heat load of the intensity of considering detonation, material and material, a kind of fuel only has an optimum condition, i.e. optimum temperature value, optimum pressure value and an optimal air-fuel ratio value, and this optimum value of any one parameter drift-out all can have a strong impact on the efficient of motor in temperature, pressure and the air fuel ratio.Because the throttle effect of the distribution device of motor is very large, so when engine load and rotation speed change, the amount that single suction stroke sucks the air in the cylinder is different, because the geometrical compression ratio of conventional engines is definite value, therefore the temperature and pressure in the cylinder also was different when compression stroke was over.In diesel engine, because there not being closure, the air of the lower suction of rotating speed is more, and the temperature and pressure after the compression is also higher.Load often little the time and rotating speed is low, so can only in cylinder, spray into a small amount of fuel oil, cause the significant off-target value of air fuel ratio and then have a strong impact on the thermal efficiency of motor, and because the existence of a large amount of remaining oxygens causes the generation befouling environment of a large amount of nitrogen oxide.In petrol engine owing to considering that the problem that gasoline is lighted has to arrange closure, but motor air inflow when low speed is reduced so that when spraying into a small amount of fuel oil ignition engine still.Yet, the operating mode substantial deviation optimum value when this causes petrol engine compression stroke is over when slow-speed of revolution low-load, the efficient of motor also therefore and significantly descends.This shows, when rotating speed and load variations, the operating mode of conventional engines and air fuel ratio be significant off-target value all, thereby causes the efficient degradation of motor, the discharging severe exacerbation.When the rotating speed of motor and load variations, such as optimum condition and the optimal air-fuel ratio that can both keep motor, then will increase substantially efficient and the feature of environmental protection of motor.For realizing this purpose, must make the geometrical compression ratio of cylinder and air displacement simultaneously adjustable.
Purpose of the present invention will disclose a kind of air displacement (stroke) and the controllable novel free-piston engine of geometrical compression ratio exactly, but based on fuel is different and load variations is adjusted air displacement (stroke) and compression ratio, be free piston load response engine, to improve efficient, low emission and the applicability of motor.This purpose is achieved in that
A kind of free piston load response engine, comprise: cylinder and free-piston, in the described cylinder of coaxial line setting, described free-piston is set respectively, the back channel link of described free-piston connects, between the described cylinder that described coaxial line arranges, separately between the link of described cylinder, described cylinder separately between the fixed block or described cylinder adjustable distance control device is set between the follower separately, at described free-piston, the separately link of described free-piston, the separately fixed block of described free-piston or the separately follower of described free-piston with described free-piston equipped described cylinder mutually, the separately link of described cylinder, the separately fixed block of described cylinder or described cylinder the adjustable travel control gear is set between the follower separately.
Described adjustable distance control device is made as the mechanical adjustable distance control device, described mechanical adjustable distance control device is made as the adjustable distance control device of the leading screw that is made of controlled leading screw, or be made as the adjustable distance control device of the eccentric shaft that is consisted of by controlled eccentric shaft, or be made as the Cam adjustable distance control device that is consisted of by controlled cam.Realize the adjustment of the distance between two cylinders by the rotation of described controlled leading screw, described controlled eccentric shaft and/or controlled cam.
Described adjustable travel control gear is made as the mechanical adjustable travel control device, described mechanical adjustable travel control device is made as the two connecting bar adjustable travel control devices that are made of connecting rod A, connecting rod B and controlled end bearing pin, or is made as the three connecting bar adjustable travel control devices that are made of described connecting rod A, described connecting rod B, connecting rod C and described controlled end bearing pin.
Described adjustable distance control device is made as the hydraulically adjustable distance control device, and described hydraulically adjustable distance control device is made as the adjustable distance control device of the oil hydraulic cylinder that is made of oil hydraulic cylinder.
Described adjustable travel control gear is made as the hydraulically adjustable travel control device, described hydraulically adjustable travel control device is made as by the end bearing pin, the single hydraulic cylinder two connecting bar adjustable travel control devices that described connecting rod A and hydraulic cylinder connecting rod A consist of, or be made as by the end bearing pin, the double hydraulic cylinder two connecting bar adjustable travel control devices that described hydraulic cylinder connecting rod A and hydraulic cylinder connecting rod B consist of, or be made as by the end bearing pin, the described connecting rod A of described hydraulic cylinder connecting rod A, with the single hydraulic cylinder three connecting bar adjustable travel control devices of described connecting rod B formation, or be made as by the end bearing pin, described hydraulic cylinder connecting rod A, the double hydraulic cylinder three connecting bar adjustable travel control devices that described connecting rod A and hydraulic cylinder connecting rod B consist of.
The control power of the adjustable distance control device of described leading screw, the adjustable distance control device of described eccentric shaft and described Cam adjustable distance control device is made as hydraulic type or electrodynamic type.
Described controlled end bearing pin is made as horizontal moving type controlled end bearing pin or is made as the controlled end of eccentric shaft type bearing pin, and the control power of described controlled end bearing pin is made as hydraulic type or electrodynamic type.
At described two connecting bar adjustable travel control devices, described three connecting bar adjustable travel control devices, described single hydraulic cylinder two connecting bar adjustable travel control devices, described double hydraulic cylinder two connecting bar adjustable travel control devices, on the connecting rod free end of the described push and pull system of described single hydraulic cylinder three connecting bar adjustable travel control devices and described double hydraulic cylinder three connecting bar adjustable travel control devices or the free bearing pin bearing pin spring is set, the inertia body, slip inertia body, rotary inertia body and/or inertia body car, slip inertia body is set between the fixed end of the connecting rod of described slip inertia body and described push and pull system and/or the free end adjusts spring, described rotary inertia body is adjusted spring through the rotary inertia body and is connected with the connecting rod of vicinity, and described inertia body car is connected with vehicle-mounted inertia body through energy-storaging spring.Described adjustable travel control gear partly or entirely is arranged in the vacuum chamber.
Free piston load response engine disclosed in this invention, by between the described cylinder of described coaxial line setting, described cylinder separately between the link, separately between the fixed block or the structure that adjustable distance control device is set between the follower separately of described cylinder of described cylinder, make the distance between two cylinders realize adjustable; And by separately follower and described cylinder, the separately link of described cylinder, the separately fixed block of described cylinder or the mode that the adjustable travel control gear is set between the follower separately of described cylinder at separately fixed block or the described free-piston of the separately link of described free-piston, described free-piston, described free-piston, make the stroke of free-piston realize adjustable.Thereby realize that the geometrical compression ratio of described free-piston engine cylinder and air displacement are simultaneously adjustable.Distance control device and travel control device can be made as various ways, such as mechanical type, hydraulic type and electromagnetic type.But mechanical type and hydraulic type should be more simple and direct effective.Mechanical adjustable distance control device, hydraulically adjustable distance control device, mechanical adjustable travel control device and hydraulically adjustable travel control device can be made as many kinds of forms, and many kinds of implementations are also arranged.
In mechanical type range-adjustable control gear, when the free end of described push and pull system during in collinear point, described free-piston begins reversing motion, this moment, the free end of described push and pull system must leave collinear point as early as possible, otherwise described push and pull system will affect described free-piston leaves the bottom stopper motion of point, affect the external output torque of described free piston engine when the blast stroke begins, and then cause the decrease in efficiency of described free piston load response engine.So-called collinear point are exactly when all bearing pins of push and pull system all are on the same straight line, the position of the residing point of free bearing pin.
For the free end of realizing push and pull system can leave collinear point rapidly, the present invention is provided with all kinds of inertia bodies in push and pull system.When two ends of push and pull system to separately away from the opposite direction motion time, because there is the setting of all kinds of inertia bodies among inertia and the present invention in the part of the freedom in two connecting rods, three connecting rods and the many push and pull system, the two ends of push and pull system will be subject to rightabout pulling force.In like manner, when move to close separately opposite direction in two ends of push and pull system, because there is the setting of all kinds of inertia bodies among inertia and the present invention in the part of the freedom in two connecting rods, three connecting rods and the many push and pull system, the two ends of push and pull system will be subject to rightabout pulling force.Therefore, there is the motion that the push and pull system of inertia can two ends of control link system in free end, makes the motion of two ends more steady, can be so that the motion of described free-piston is more steady.Adjust the length of connecting rod or the link position of adjustment push and pull system end, the just stroke of capable of regulating free-piston.In other words, the push and pull system among the present invention and linkage structure thereof not only can make the stroke of described free piston load response engine and geometrical compression ratio controllable, can also make the motor operation more steady.
Described three bar linkage structures can make the free end of the described push and pull system that is in collinear point leave quickly collinear point than described two bar linkage structures, but described three bar linkage structures are more complicated than described two bar linkage structures, and manufacture cost is also high.No matter in two-stroke or at the described free piston load response engine of four-stroke, a described free piston load response engine can arrange a plurality of described push and pull system, to satisfy the needs of each free-piston of control.Described bearing pin spring, described inertia are adjusted spring, described inertia body, described slip inertia body, described slip inertia body spring, described rotary inertia body, described rotary inertia body adjustment spring, described inertia car, described through energy-storaging spring and described vehicle-mounted inertia body, can arrange according to situation one or morely, also can according to circumstances use separately or use simultaneously.
Described bearing pin spring just is arranged on the spring on the bearing pin, arranging of it can make the push and pull system operation more steady, also can make described free bearing pin can leave more quickly collinear point with the end bearing pin, thereby described free-piston the blast stroke when beginning external moment larger, improve the efficient of motor.
Described inertia body is exactly the object with certain inertia, described inertia body also can be arranged on the free end of connecting rod, thereby realize that the geometrical compression ratio of described free-piston engine cylinder and air displacement are simultaneously adjustable, by adjusting the quality of described inertia body, can make the push and pull system operation more steady.
Described slip inertia body adjustment spring is arranged on the spring on the connecting rod, slip inertia body is adjusted an end of spring and the fixed end of connecting rod, also can be connected with the free end of connecting rod, as long as it is that the fixed end direction of described slip inertia body to connecting rod moved that described slip inertia body is adjusted the effect of spring, the other end that described slip inertia body is adjusted spring acts on described slip inertia body, and described slip inertia body is had away from the free-ended trend of connecting rod.Because the effect of inertial force, this structure can make the free end of connecting rod have larger inertia away from collinear point the time, has less inertia near collinear point.For this reason, can make described connecting rod free end can leave more quickly collinear point, thus described free-piston the blast stroke when beginning external moment larger, improve the efficient of motor.
Described rotary inertia body is arranged on the connecting rod free end or the rotary eccentric inertia body on the described free bearing pin.Described rotary inertia body is adjusted spring with described rotary inertia body and is connected.Because the effect of inertial force, this structure can make the free end of connecting rod when being in collinear point, is subject to described rotary inertia body is adjusted spring through described rotary inertia body indirectly-acting acquisition continuation thrust forward.For this reason, can make described connecting rod free end can leave more quickly collinear point, thus described free-piston the blast stroke when beginning external moment larger, improve the efficient of motor.
Described inertia body car is arranged on the inertia body carrier member on the connecting rod free end or on the described free bearing pin.Described inertia body car is provided with described energy-storaging spring, and an end of described energy-storaging spring is connected with described inertia body car, and the other end of described energy-storaging spring is connected with described vehicle-mounted inertia body.Because the effect of inertial force, this structure can make the free end of connecting rod when being in collinear point, is subject to described vehicle-mounted inertia body and obtains continuation thrust forward through the indirectly-acting of described energy-storaging spring.For this reason, can make described connecting rod free end can leave more quickly collinear point, thus described free-piston the blast stroke when beginning external moment larger, improve the efficient of motor.
Described adjustable travel control gear partly or entirely is arranged in the vacuum chamber, because when described free piston load response engine operation, the free end meeting high-speed motion of described push and pull system, the resistance of the free end high-speed motion that can reduce described push and pull system by arranging of vacuum chamber improves the efficient of motor.
The present invention has the following advantages:
1, the present invention is simple in structure, and the discharge amount of controllable free-piston engine (stroke) and geometrical compression ratio are so that the commercialized development of free-piston engine becomes possibility;
2, the present invention can increase substantially efficient and the feature of environmental protection of motor.
Description of drawings
Fig. 1 is the structural representation of the corresponding motor of free piston load;
Fig. 2 is another structural representation of the corresponding motor of free piston load;
Fig. 3 is the adjustable distance control device embodiment's of leading screw structural representation;
Fig. 4 is the adjustable distance control device embodiment's of eccentric shaft structural representation;
Fig. 5 is Cam adjustable distance control device embodiment's structural representation;
Fig. 6 is two connecting bar adjustable travel control device embodiments' structural representation;
Fig. 7 is three connecting bar adjustable travel control device embodiments' structural representation;
Fig. 8 is hydraulically adjustable distance control device embodiment's structural representation;
Fig. 9 is the structural representation of single hydraulic cylinder two connecting bar adjustable travel control devices;
Figure 10 is the structural representation of double hydraulic cylinder two connecting bar adjustable travel control devices;
Figure 11 is another structural representation of double hydraulic cylinder two connecting bar adjustable travel control devices;
Figure 12 is the structural representation of single hydraulic cylinder three connecting bar adjustable travel control devices;
Figure 13 is the structural representation of double hydraulic cylinder three connecting bar adjustable travel control devices;
Figure 14 is the structural representation of the controlled end of horizontal moving type bearing pin;
Figure 15 is the structural representation of the controlled end of eccentric shaft type bearing pin;
Figure 16 is the structural representation that is provided with the bearing pin spring;
Figure 17 is another structural representation that is provided with the bearing pin spring;
Figure 18 is the structural representation that is provided with inertia body embodiment;
Figure 19 is provided with the first structure embodiment that inertia is adjusted spring and slide block inertia body;
Figure 20 is provided with the second structure embodiment that inertia is adjusted spring and slide block inertia body;
Figure 21 is provided with the 3rd structure embodiment that inertia is adjusted spring and slide block inertia body;
Figure 22 is the structural representation that is provided with rotary inertia body embodiment;
Figure 23 is the structural representation that is provided with inertia body car embodiment;
Figure 24 is that the adjustable travel control gear is arranged on the structural representation in the vacuum chamber;
Embodiment
Accompanying drawing number:
1. cylinder 2. free-pistons 3. links
10. adjustable distance control device 20. adjustable travel control gear
11. mechanical adjustable distance control device 21. mechanical adjustable travel control devices
1101. the adjustable distance control device of controlled leading screw 111. leading screws
1102. controlled eccentric wheel 112. eccentric shaft type distance control devices
1103. controlled cam 113. Cam adjustable distance control devices
2101. connecting rod A 2102. connecting rod B 2103. controlled end bearing pins 2104. connecting rod C
211. two connecting bar adjustable travel control devices, 212. three connecting bar adjustable travel control devices
12. hydraulically adjustable distance control device 1201. oil hydraulic cylinders
121. the adjustable distance control device 22. hydraulically adjustable travel control devices of oil hydraulic cylinder
2201. end bearing pin 2202. hydraulic cylinder connecting rod A 2203. hydraulic cylinder connecting rod B
221. single hydraulic cylinder two connecting bar adjustable travel control devices
222. double hydraulic cylinder two connecting bar adjustable travel control devices
223. single hydraulic cylinder three connecting bar adjustable travel control devices
224. double hydraulic cylinder three connecting bar adjustable travel control devices
21031. the controlled end of bearing pin 21032. eccentric shaft types, the controlled end of horizontal moving type bearing pin
122. connecting rod free end 123. free bearing pin 12301. bearing pin springs
12302. inertia body 12303. slip inertia bodies 12304. rotary inertia bodies
12305. inertia body car 12306. slip inertia bodies are adjusted spring
12307. the rotary inertia body is adjusted spring
12308. energy storage spring 12309. vehicle-mounted inertia body 12310. vacuum chambers
Below in conjunction with the drawings and specific embodiments purpose of the present invention is elaborated:
Please refer to free piston load response engine illustrated in figures 1 and 2, comprise: cylinder 1 and free-piston 2, described free-piston 2 is set in the described cylinder 1 of coaxial line setting respectively, the back channel link 3 of described free-piston 2 connects, between the described cylinder 1 that described coaxial line arranges, separately between the link of described cylinder 1, described cylinder 1 separately between the fixed block or described cylinder 1 adjustable distance control device 10 is set between the follower separately, at described free-piston 2, the separately link 3 of described free-piston 2, the separately fixed block of described free-piston 2 or the separately follower of described free-piston 2 with described free-piston 2 equipped described cylinder 1 mutually, the separately link of described cylinder 1, the separately fixed block of described cylinder 1 or described cylinder 1 adjustable travel control gear 20 is set between the follower separately.
Please refer to Fig. 3, Fig. 4 and Fig. 5, described adjustable distance control device 10 is made as mechanical adjustable distance control device 11, described mechanical adjustable distance control device 11 is made as the adjustable distance control device 111 of the leading screw that is made of controlled leading screw 1101, or be made as the adjustable distance control device 112 of the eccentric shaft that is consisted of by controlled eccentric shaft 1102, or be made as the Cam adjustable distance control device 113 that is consisted of by controlled cam 1103.
Please refer to Fig. 6 and Fig. 7, described adjustable travel control gear 20 is made as mechanical adjustable travel control device 21, described mechanical adjustable travel control device 21 is made as the two connecting bar adjustable travel control devices 211 that are made of connecting rod A2101, connecting rod B2102 and controlled end bearing pin 2103, or is made as the three connecting bar adjustable travel control devices 212 that are made of described connecting rod A2101, described connecting rod B2102, connecting rod C2104 and described controlled end bearing pin 2103.
Please refer to Fig. 8, described adjustable distance control device 10 is made as hydraulically adjustable distance control device 12, and described hydraulically adjustable distance control device 12 is made as the adjustable distance control device 121 of the oil hydraulic cylinder that is made of oil hydraulic cylinder 1201.
Please refer to Fig. 9, Figure 10, Figure 11, Figure 12 and Figure 13, described adjustable travel control gear 20 is made as hydraulically adjustable travel control device 22, described hydraulically adjustable travel control device 22 is made as by end bearing pin 2201, the single hydraulic cylinder two connecting bar adjustable travel control devices 221 that described connecting rod A2101 and hydraulic cylinder connecting rod A2202 consist of, or be made as by end bearing pin 2201, the double hydraulic cylinder two connecting bar adjustable travel control devices 222 that described hydraulic cylinder connecting rod A2202 and hydraulic cylinder connecting rod B2203 consist of, or be made as by end bearing pin 2201, the described connecting rod A2101 of described hydraulic cylinder connecting rod A2202, with the single hydraulic cylinder three connecting bar adjustable travel control devices 223 of described connecting rod B2102 formation, or be made as by end bearing pin 2201, described hydraulic cylinder connecting rod A2202, the double hydraulic cylinder three connecting bar adjustable travel control devices 224 that described connecting rod A2101 and hydraulic cylinder connecting rod B2203 consist of.
Please refer to Figure 14 and Figure 15, described controlled end bearing pin 2103 is made as the controlled end of horizontal moving type bearing pin 21031 or is made as the controlled end of eccentric shaft type bearing pin 21032, and the control power of described controlled end bearing pin 2103 is made as hydraulic type or electrodynamic type.
Please refer to Figure 16 and Figure 17, at described two connecting bar adjustable travel control devices 211, described three connecting bar adjustable travel control devices 212, described single hydraulic cylinder two connecting bar adjustable travel control devices 221, described double hydraulic cylinder two connecting bar adjustable travel control devices 222 arrange bearing pin spring 12301 on the connecting rod free end 122 of the described push and pull system of described single hydraulic cylinder three connecting bar adjustable travel control devices 223 and described double hydraulic cylinder three connecting bar adjustable travel control devices 224 or the free bearing pin 123.Described bearing pin spring just is arranged on the spring on the bearing pin, arranging of it can make the push and pull system operation more steady, also can make described free bearing pin can leave more quickly collinear point with the end bearing pin, thereby described free-piston the blast stroke when beginning external moment larger, improve the efficient of motor.So-called collinear point are exactly when all bearing pins of push and pull system all are on the same straight line, the position of the residing point of free bearing pin.
Please refer to Figure 18, at connecting rod free end 122 or the free bearing pin 123 of the described push and pull system of described adjustable travel control gear inertia body 12302 is set.Described inertia body is exactly the object with certain inertia, described inertia body also can be arranged on the free end of connecting rod, thereby realize that the geometrical compression ratio of described free-piston engine cylinder and air displacement are simultaneously adjustable, by adjusting the quality of described inertia body, can make the push and pull system operation more steady.
Please refer to Figure 19, Figure 20 and Figure 21, at the connecting rod free end 122 of the described push and pull system of described adjustable travel control gear or free bearing pin 123 arranges slip inertia body 12303 and slip inertia body is adjusted spring 12306.Described slip inertia body adjustment spring is arranged on the spring on the connecting rod, slip inertia body is adjusted an end of spring and the fixed end of connecting rod, also can be connected with the free end of connecting rod, as long as it is that the fixed end direction of described slip inertia body to connecting rod moved that described slip inertia body is adjusted the effect of spring, the other end that described slip inertia body is adjusted spring acts on described slip inertia body, and described slip inertia body is had away from the free-ended trend of connecting rod.Because the effect of inertial force, this structure can make the free end of connecting rod have larger inertia away from collinear point the time, has less inertia near collinear point.For this reason, can make described connecting rod free end can leave more quickly collinear point, thus described free-piston the blast stroke when beginning external moment larger, improve the efficient of motor.
Please refer to Figure 22, at the connecting rod free end 122 of the described push and pull system of described adjustable travel control gear or free bearing pin 123 arranges rotary inertia body 12304 and the rotary inertia body is adjusted spring 12307.Described rotary inertia body is arranged on the connecting rod free end or the rotary eccentric inertia body on the described free bearing pin.Described rotary inertia body is adjusted spring with described rotary inertia body and is connected.Because the effect of inertial force, this structure can make the free end of connecting rod when being in collinear point, is subject to described rotary inertia body is adjusted spring through described rotary inertia body indirectly-acting acquisition continuation thrust forward.For this reason, can make described connecting rod free end can leave more quickly collinear point, thus described free-piston the blast stroke when beginning external moment larger, improve the efficient of motor.
Please refer to Figure 23, at connecting rod free end 122 or the free bearing pin 123 of the described push and pull system of described adjustable travel control gear inertia body car 12305 is set, described inertia body car 12305 is connected with vehicle-mounted inertia body 12309 through energy-storaging spring 12308.Described inertia body car is arranged on the inertia body carrier member on the connecting rod free end or on the described free bearing pin.Described inertia body car is provided with described energy-storaging spring, and an end of described energy-storaging spring is connected with described inertia body car, and the other end of described energy-storaging spring is connected with described vehicle-mounted inertia body.Because the effect of inertial force, this structure can make the free end of connecting rod when being in collinear point, is subject to described vehicle-mounted inertia body and obtains continuation thrust forward through the indirectly-acting of described energy-storaging spring.For this reason, can make described connecting rod free end can leave more quickly collinear point, thus described free-piston the blast stroke when beginning external moment larger, improve the efficient of motor.
Please refer to Figure 24, described adjustable travel control gear 20 all or part of being arranged in the vacuum chamber 12310.Because when the operation of described free piston load response engine, the free end of described push and pull system can high-speed motion, and the resistance of the free end high-speed motion that can reduce described push and pull system by arranging of vacuum chamber improves the efficient of motor.
Claims (9)
1. free piston load response engine, comprise: cylinder (1), free-piston (2), it is characterized in that: in the described cylinder (1) that coaxial line arranges, described free-piston (2) is set respectively, the back channel link (3) of described free-piston (2) connects, between the described cylinder (1) that described coaxial line arranges, separately between the link of described cylinder (1), described cylinder (1) separately between the fixed block or described cylinder (1) adjustable distance control device (10) is set between the follower separately, in described free-piston (2), the separately link (3) of described free-piston (2), the separately follower of the separately fixed block of described free-piston (2) or described free-piston (2) with described free-piston (2) equipped described cylinder (1) mutually, the separately link of described cylinder (1), the separately fixed block of described cylinder (1) or described cylinder (1) adjustable travel control gear (20) is set between the follower separately.
2. free piston load response engine as claimed in claim 1, it is characterized in that: described adjustable distance control device (10) is made as mechanical adjustable distance control device (11), described mechanical adjustable distance control device (11) is made as the adjustable distance control device of leading screw (111) that is made of controlled leading screw (1101), or be made as the adjustable distance control device of eccentric shaft (112) that is consisted of by controlled eccentric shaft (1102), or be made as the Cam adjustable distance control device (113) that is consisted of by controlled cam (1103).
3. free piston load response engine as claimed in claim 1, it is characterized in that: described adjustable travel control gear (20) is made as mechanical adjustable travel control device (21), described mechanical adjustable travel control device (21) is made as by connecting rod A (2101), the two connecting bar adjustable travel control devices (211) that connecting rod B (2102) and controlled end bearing pin (2103) consist of, or be made as by described connecting rod A (2101), described connecting rod B (2102), the three connecting bar adjustable travel control devices (212) that connecting rod C (2104) and described controlled end bearing pin (2103) consist of.
4. free piston load response engine as claimed in claim 1, it is characterized in that: described adjustable distance control device (10) is made as hydraulically adjustable distance control device (12), and described hydraulically adjustable distance control device (12) is made as the adjustable distance control device of oil hydraulic cylinder (121) that is made of oil hydraulic cylinder (1201).
5. free piston load response engine as claimed in claim 1, it is characterized in that: described adjustable travel control gear (20) is made as hydraulically adjustable travel control device (22), described hydraulically adjustable travel control device (22) is made as by end bearing pin (2201), the single hydraulic cylinder two connecting bar adjustable travel control devices (221) that described connecting rod A (2101) and hydraulic cylinder connecting rod A (2202) consist of, or be made as by end bearing pin (2201), the double hydraulic cylinder two connecting bar adjustable travel control devices (222) that described hydraulic cylinder connecting rod A (2202) and hydraulic cylinder connecting rod B (2203) consist of, or be made as by end bearing pin (2201), the described connecting rod A of described hydraulic cylinder connecting rod A (2202) (2101), with the single hydraulic cylinder three connecting bar adjustable travel control devices (223) of described connecting rod B (2102) formation, or be made as by end bearing pin (2201), described hydraulic cylinder connecting rod A (2202), the double hydraulic cylinder three connecting bar adjustable travel control devices (224) that described connecting rod A (2101) and hydraulic cylinder connecting rod B (2203) consist of.
6. free piston load response engine as claimed in claim 1, it is characterized in that: the control power of the adjustable distance control device of described leading screw (111), the adjustable distance control device of described eccentric shaft (112) and described Cam adjustable distance control device (113) is made as hydraulic type or electrodynamic type.
7. free piston load response engine as claimed in claim 1, it is characterized in that: described controlled end bearing pin (2103) is made as the controlled end of horizontal moving type bearing pin (21031) or is made as the controlled end of eccentric shaft type bearing pin (21032), and the control power of described controlled end bearing pin (2103) is made as hydraulic type or electrodynamic type.
8. free piston load response engine as claimed in claim 1, it is characterized in that: at described two connecting bar adjustable travel control devices (211), described three connecting bar adjustable travel control devices (212), described single hydraulic cylinder two connecting bar adjustable travel control devices (221), described double hydraulic cylinder two connecting bar adjustable travel control devices (222), on the connecting rod free end (122) of the described push and pull system of described single hydraulic cylinder three connecting bar adjustable travel control devices (223) and described double hydraulic cylinder three connecting bar adjustable travel control devices (224) or the free bearing pin (123) bearing pin spring (12301) is set, inertia body (12302), slip inertia body (12303), rotary inertia body (12304) and/or inertia body car (12305), slip inertia body is set between the fixed end of the connecting rod of described slip inertia body (12303) and described push and pull system and/or the free end adjusts spring (12306), described rotary inertia body (12304) is adjusted spring (12307) through the rotary inertia body and is connected with the connecting rod of vicinity, and described inertia body car (12305) is connected with vehicle-mounted inertia body (12309) through energy-storaging spring (12308).
9. free piston load response engine as claimed in claim 1, it is characterized in that: described adjustable travel control gear (20) is all or part of to be arranged in the vacuum chamber (12310).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200810177541 CN101555829B (en) | 2008-11-21 | 2008-11-21 | Free piston load response engine |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200810177541 CN101555829B (en) | 2008-11-21 | 2008-11-21 | Free piston load response engine |
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| CN101555829A CN101555829A (en) | 2009-10-14 |
| CN101555829B true CN101555829B (en) | 2013-02-20 |
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| CN 200810177541 Active CN101555829B (en) | 2008-11-21 | 2008-11-21 | Free piston load response engine |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN102052149B (en) * | 2011-01-11 | 2013-01-30 | 北京理工大学 | Passive air-inlet mode diesel linear electromagnetic energy conversion device |
| CN103603745B (en) * | 2012-09-24 | 2016-03-30 | 摩尔动力(北京)技术股份有限公司 | Liquid piston heat engine |
| CN103306810A (en) * | 2012-10-16 | 2013-09-18 | 张海兵 | Microcomputer-controlled one-way valve-matched piston pressure-storing crankless internal-combustion engine |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1210532A (en) * | 1966-10-06 | 1970-10-28 | Anton Braun | Free piston engine |
| WO1981000019A1 (en) * | 1979-06-25 | 1981-01-08 | Benaroya Henry | Machine with multi tandem free pistons |
| WO2006091682A2 (en) * | 2005-02-24 | 2006-08-31 | Fitzgerald John W | Variable stroke premixed charge compression ignition engine |
| CN201288608Y (en) * | 2008-11-21 | 2009-08-12 | 靳北彪 | Free piston type load response engine |
-
2008
- 2008-11-21 CN CN 200810177541 patent/CN101555829B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1210532A (en) * | 1966-10-06 | 1970-10-28 | Anton Braun | Free piston engine |
| WO1981000019A1 (en) * | 1979-06-25 | 1981-01-08 | Benaroya Henry | Machine with multi tandem free pistons |
| WO2006091682A2 (en) * | 2005-02-24 | 2006-08-31 | Fitzgerald John W | Variable stroke premixed charge compression ignition engine |
| CN201288608Y (en) * | 2008-11-21 | 2009-08-12 | 靳北彪 | Free piston type load response engine |
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| CN101555829A (en) | 2009-10-14 |
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