CN201288608Y - Free piston type load response engine - Google Patents
Free piston type load response engine Download PDFInfo
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- CN201288608Y CN201288608Y CNU2008201791081U CN200820179108U CN201288608Y CN 201288608 Y CN201288608 Y CN 201288608Y CN U2008201791081 U CNU2008201791081 U CN U2008201791081U CN 200820179108 U CN200820179108 U CN 200820179108U CN 201288608 Y CN201288608 Y CN 201288608Y
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Abstract
The utility model discloses a free-piston type load response motor which comprises cylinders and free pistons. The free pistons are respectively installed in the cylinders which are coaxially installed. The back parts of free pistons are connected through connectors. Adjustable distance controllers are installed between the cylinders coaxially installed, the connectors of cylinders, the fixers of cylinders or the followers of cylinders. Adjustable stroke controllers are installed between the free pistons, the connectors of free pistons, the fixers of free pistons or the followers of free pistons, the cylinders matched with the free pistons, the connectors of cylinders, the fixers of cylinders or the followers of cylinders. The free-piston type load response motor according to the utility model can adjust the air displacement and compression ratio according to different fuels and load variation thereby increasing the engine efficiency, low discharge property and adaptability.
Description
Technical field
The utility model 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 at present energy environment problem that is run into is had higher requirement to the hot merit switch machine.For this reason, reciprocating internal combustion engine just seems that volume is big, weight is big, 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 advantage such as free piston engine has the efficient height, emission performance is good, and volume is little, in light weight with reciprocating-piston engine.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 big, 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 big moment when the blast stroke begins, and the burning indoor gas expands fast, and heat loss is little, and nitrogen oxide forms few, and the efficient height 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.The thermal efficiency of the operating mode decision motor after the burning, and the operating mode after the burning is to be determined by 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 decision motor power in the cards.Say that in principle the temperature after burning high pressure more is also just big more, efficient is also just high more.Under the prerequisite of the practical factors such as heat load of the intensity of considering detonation, material and material, a kind of fuel has only 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 big, 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 a definite value, so the interior temperature and pressure of cylinder also is different when compression stroke is over.In diesel engine, because of there not being closure, the low more inhaled air of rotating speed is many more, and the temperature and pressure after the compression is also high more.Load often little the time and rotating speed is low, so can only in cylinder, spray into a small amount of fuel oil, cause air fuel ratio to depart from optimum value significantly 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 consider that the problem that gasoline is lighted has to be provided with 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 descends therefore and significantly.This shows that when rotating speed and load variations, the operating mode of conventional engines and air fuel ratio all can depart from optimum value significantly, thereby cause the efficient of motor seriously to descend, the discharging severe exacerbation.When the rotating speed of motor and load variations,, then will increase substantially the efficient and the feature of environmental protection of motor as the optimum condition and the optimal air-fuel ratio that can both keep motor.For realizing this purpose, must make the geometrical compression ratio of cylinder and air displacement simultaneously adjustable.
The purpose of this utility model 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 of described free-piston connects through link, between the described cylinder that described coaxial line is provided with, 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 link separately of described free-piston, the fixed block separately of described free-piston or the follower separately of described free-piston and the described cylinder equipped mutually with described free-piston, the link separately of described cylinder, the fixed block separately 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 mechanical adjustable distance control device, the adjustable distance control device of described machinery 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 constitutes by controlled eccentric shaft, or be made as the adjustable distance control device of the cam that constitutes 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 mechanical adjustable travel control gear, described mechanical adjustable travel control gear is made as the two connecting rod adjustable travel control gear that are made of connecting rod A, connecting rod B and controlled end bearing pin, or is made as the three connecting rod adjustable travel control gear 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 rod adjustable travel control gear that described connecting rod A and oil hydraulic cylinder connecting rod A constitute, or be made as by the end bearing pin, the double hydraulic cylinder two connecting rod adjustable travel control gear that described oil hydraulic cylinder connecting rod A and oil hydraulic cylinder connecting rod B constitute, or be made as by the end bearing pin, the described connecting rod A of described oil hydraulic cylinder connecting rod A, with the single hydraulic cylinder three connecting rod adjustable travel control gear of described connecting rod B formation, or be made as by the end bearing pin, described oil hydraulic cylinder connecting rod A, the double hydraulic cylinder three connecting rod adjustable travel control gear that described connecting rod A and oil hydraulic cylinder connecting rod B constitute.
The control power of the adjustable distance control device of described leading screw, the adjustable distance control device of described eccentric shaft and the adjustable distance control device of described cam 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 rod adjustable travel control gear, described three connecting rod adjustable travel control gear, described single hydraulic cylinder two connecting rod adjustable travel control gear, described double hydraulic cylinder two connecting rod adjustable travel control gear, on the connecting rod free end of the described push and pull system of described single hydraulic cylinder three connecting rod adjustable travel control gear and described double hydraulic cylinder three connecting rod adjustable travel control gear 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 the utility model, 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, make the stroke of free-piston realize adjustable by follower separately and described cylinder, the link separately of described cylinder, the fixed block separately of described cylinder or the mode that the adjustable travel control gear is set between the follower separately of described cylinder at the fixed block separately or the described free-piston of the link separately of described free-piston, described free-piston, described free-piston.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, as mechanical type, hydraulic type and electromagnetic type.But mechanical type and hydraulic type should be more simple and direct effective.The adjustable distance control device of machinery, hydraulically adjustable distance control device, mechanical adjustable travel control gear 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 influence the motion that described free-piston leaves lower dead center, influence 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 apace, the utility model 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 in inertia and the utility model in the free part in two connecting rods, three connecting rods and the many push and pull system, the two ends of push and pull system will be subjected to rightabout pulling force.In like manner, when two ends of push and pull system during to close separately opposite direction motion, because there is the setting of all kinds of inertia bodies in inertia and the utility model in the free part in two connecting rods, three connecting rods and the many push and pull system, the two ends of push and pull system will be subjected 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, just can adjust the stroke of free-piston.In other words, push and pull system in the utility model 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 collinear point quickly than described two bar linkage structures, but described three bar linkage structures are than described two bar linkage structure complexity, and manufacture cost is also high.No matter in two-stroke still at the described free piston load response engine of four-stroke, a described free piston load response engine can be provided with 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 be provided with one or morely according to situation, also can according to circumstances use separately or use simultaneously.
Described bearing pin spring just is arranged on the spring on the bearing pin, being provided with of it can make the push and pull system operation more steady, also can make described free bearing pin can leave collinear point with the end bearing pin more quickly, thereby described free-piston the blast stroke when beginning external moment bigger, 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 described slip inertia body is moved to the fixed end direction of connecting rod 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 big inertia away from collinear point the time, have less inertia near collinear point.For this reason, can make described connecting rod free end can leave collinear point more quickly, thus described free-piston the blast stroke when beginning external moment bigger, 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 subjected 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 collinear point more quickly, thus described free-piston the blast stroke when beginning external moment bigger, 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 subjected 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 collinear point more quickly, thus described free-piston the blast stroke when beginning external moment bigger, 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 moves, 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 being provided with of vacuum chamber improves the efficient of motor.
The utlity model has following advantage:
1, the utility model is simple in structure, and discharge amount of controllable free-piston engine (stroke) and geometrical compression ratio make the commercialized development of free-piston engine become possibility;
2, the utility model can increase substantially the 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 a structural representation;
Fig. 4 is the adjustable distance control device embodiment's of eccentric shaft a structural representation;
Fig. 5 is the adjustable distance control device embodiment's of cam a structural representation;
Fig. 6 is two connecting rod adjustable travel control gear embodiments' a structural representation;
Fig. 7 is three connecting rod adjustable travel control gear embodiments' a structural representation;
Fig. 8 is hydraulically adjustable distance control device embodiment's a structural representation;
Fig. 9 is the structural representation of single hydraulic cylinder two connecting rod adjustable travel control gear;
Figure 10 is the structural representation of double hydraulic cylinder two connecting rod adjustable travel control gear;
Figure 11 is another structural representation of double hydraulic cylinder two connecting rod adjustable travel control gear;
Figure 12 is the structural representation of single hydraulic cylinder three connecting rod adjustable travel control gear;
Figure 13 is the structural representation of double hydraulic cylinder three connecting rod adjustable travel control gear;
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 gear
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. the adjustable distance control device of controlled cam 113. cams
2101. connecting rod A 2102. connecting rod B 2103. controlled end bearing pins 2104. connecting rod C
211. two connecting rod adjustable travel control gear, 212. three connecting rod adjustable travel control gear
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. oil hydraulic cylinder connecting rod A 2203. oil hydraulic cylinder connecting rod B
221. single hydraulic cylinder two connecting rod adjustable travel control gear
222. double hydraulic cylinder two connecting rod adjustable travel control gear
223. single hydraulic cylinder three connecting rod adjustable travel control gear
224. double hydraulic cylinder three connecting rod adjustable travel control gear
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 the purpose of this utility model 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 of described free-piston 2 connects through link 3, between the described cylinder 1 that described coaxial line is provided with, 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 link separately 3 of described free-piston 2, the fixed block separately of described free-piston 2 or the follower separately of described free-piston 2 and the described cylinder 1 equipped mutually with described free-piston 2, the link separately of described cylinder 1, the fixed block separately 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, the adjustable distance control device 11 of described machinery 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 constitutes by controlled eccentric shaft 1102, or be made as the adjustable distance control device 113 of the cam that constitutes 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 gear 21, described mechanical adjustable travel control gear 21 is made as the two connecting rod adjustable travel control gear 211 that are made of connecting rod A2101, connecting rod B2102 and controlled end bearing pin 2103, or is made as the three connecting rod adjustable travel control gear 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 rod adjustable travel control gear 221 that described connecting rod A2101 and oil hydraulic cylinder connecting rod A2202 constitute, or be made as by end bearing pin 2201, the double hydraulic cylinder two connecting rod adjustable travel control gear 222 that described oil hydraulic cylinder connecting rod A2202 and oil hydraulic cylinder connecting rod B2203 constitute, or be made as by end bearing pin 2201, the described connecting rod A2101 of described oil hydraulic cylinder connecting rod A2202, with the single hydraulic cylinder three connecting rod adjustable travel control gear 223 of described connecting rod B2102 formation, or be made as by end bearing pin 2201, described oil hydraulic cylinder connecting rod A2202, the double hydraulic cylinder three connecting rod adjustable travel control gear 224 that described connecting rod A2101 and oil hydraulic cylinder connecting rod B2203 constitute.
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 rod adjustable travel control gear 211, described three connecting rod adjustable travel control gear 212, described single hydraulic cylinder two connecting rod adjustable travel control gear 221, described double hydraulic cylinder two connecting rod adjustable travel control gear 222 are provided with 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 rod adjustable travel control gear 223 and described double hydraulic cylinder three connecting rod adjustable travel control gear 224 or the free bearing pin 123.Described bearing pin spring just is arranged on the spring on the bearing pin, being provided with of it can make the push and pull system operation more steady, also can make described free bearing pin can leave collinear point with the end bearing pin more quickly, thereby described free-piston the blast stroke when beginning external moment bigger, 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, on the connecting rod free end 122 of the described push and pull system of described adjustable travel control gear or free bearing pin 123, 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, on the connecting rod free end 122 of the described push and pull system of described adjustable travel control gear or free bearing pin 123, slip inertia body 12303 is set 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 described slip inertia body is moved to the fixed end direction of connecting rod 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 big inertia away from collinear point the time, have less inertia near collinear point.For this reason, can make described connecting rod free end can leave collinear point more quickly, thus described free-piston the blast stroke when beginning external moment bigger, improve the efficient of motor.
Please refer to Figure 22, on the connecting rod free end 122 of the described push and pull system of described adjustable travel control gear or free bearing pin 123, rotary inertia body 12304 is set 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 subjected 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 collinear point more quickly, thus described free-piston the blast stroke when beginning external moment bigger, improve the efficient of motor.
Please refer to Figure 23, on the connecting rod free end 122 of the described push and pull system of described adjustable travel control gear or free bearing pin 123 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 subjected 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 collinear point more quickly, thus described free-piston the blast stroke when beginning external moment bigger, 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 being provided with 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 is provided with, described free-piston (2) is set respectively, the back of described free-piston (2) connects through link (3), between the described cylinder (1) that described coaxial line is provided with, 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 link separately (3) of described free-piston (2), the follower separately of the fixed block separately of described free-piston (2) or described free-piston (2) and the described cylinder (1) equipped mutually with described free-piston (2), the link separately of described cylinder (1), the fixed block separately 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 according to claim 1, it is characterized in that: described adjustable distance control device (10) is made as mechanical adjustable distance control device (11), the adjustable distance control device of described machinery (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 constitutes by controlled eccentric shaft (1102), or be made as the adjustable distance control device of cam (113) that constitutes by controlled cam (1103).
3. free piston load response engine according to claim 1, it is characterized in that: described adjustable travel control gear (20) is made as mechanical adjustable travel control gear (21), described mechanical adjustable travel control gear (21) is made as by connecting rod A (2101), the two connecting rod adjustable travel control gear (211) that connecting rod B (2102) and controlled end bearing pin (2103) constitute, or be made as by described connecting rod A (2101), described connecting rod B (2102), the three connecting rod adjustable travel control gear (212) that connecting rod C (2104) and described controlled end bearing pin (2103) constitute.
4. free piston load response engine according to 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 according to 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 rod adjustable travel control gear (221) that described connecting rod A (2101) and oil hydraulic cylinder connecting rod A (2202) constitute, or be made as by end bearing pin (2201), the double hydraulic cylinder two connecting rod adjustable travel control gear (222) that described oil hydraulic cylinder connecting rod A (2202) and oil hydraulic cylinder connecting rod B (2203) constitute, or be made as by end bearing pin (2201), the described connecting rod A of described oil hydraulic cylinder connecting rod A (2202) (2101), with the single hydraulic cylinder three connecting rod adjustable travel control gear (223) of described connecting rod B (2102) formation, or be made as by end bearing pin (2201), described oil hydraulic cylinder connecting rod A (2202), the double hydraulic cylinder three connecting rod adjustable travel control gear (224) that described connecting rod A (2101) and oil hydraulic cylinder connecting rod B (2203) constitute.
6. free piston load response engine according to 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 the adjustable distance control device of described cam (113) is made as hydraulic type or electrodynamic type.
7. free piston load response engine according to 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 according to claim 1, it is characterized in that: at described two connecting rod adjustable travel control gear (211), described three connecting rod adjustable travel control gear (212), described single hydraulic cylinder two connecting rod adjustable travel control gear (221), described double hydraulic cylinder two connecting rod adjustable travel control gear (222), on the connecting rod free end (122) of the described push and pull system of described single hydraulic cylinder three connecting rod adjustable travel control gear (223) and described double hydraulic cylinder three connecting rod adjustable travel control gear (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 according to 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 |
|---|---|---|---|
| CNU2008201791081U CN201288608Y (en) | 2008-11-21 | 2008-11-21 | Free piston type load response engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008201791081U CN201288608Y (en) | 2008-11-21 | 2008-11-21 | Free piston type load response engine |
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| Publication Number | Publication Date |
|---|---|
| CN201288608Y true CN201288608Y (en) | 2009-08-12 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2008201791081U Expired - Lifetime CN201288608Y (en) | 2008-11-21 | 2008-11-21 | Free piston type load response engine |
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| Country | Link |
|---|---|
| CN (1) | CN201288608Y (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101845992A (en) * | 2010-05-06 | 2010-09-29 | 靳北彪 | Vibrator energy storage free piston engine |
| CN101555829B (en) * | 2008-11-21 | 2013-02-20 | 靳北彪 | Free piston load response engine |
| CN103010037A (en) * | 2012-07-20 | 2013-04-03 | 同济大学 | Automotive range extender based on linear ISG(Integrated Starter and Generator) motor/engine |
| CN104806354A (en) * | 2015-05-05 | 2015-07-29 | 北京理工大学 | Free piston internal combustion generation power system with adjustable compression ratio |
-
2008
- 2008-11-21 CN CNU2008201791081U patent/CN201288608Y/en not_active Expired - Lifetime
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101555829B (en) * | 2008-11-21 | 2013-02-20 | 靳北彪 | Free piston load response engine |
| CN101845992A (en) * | 2010-05-06 | 2010-09-29 | 靳北彪 | Vibrator energy storage free piston engine |
| WO2011137659A1 (en) * | 2010-05-06 | 2011-11-10 | Jin Beibiao | Vibrator energy storage free piston engine |
| CN103010037A (en) * | 2012-07-20 | 2013-04-03 | 同济大学 | Automotive range extender based on linear ISG(Integrated Starter and Generator) motor/engine |
| CN103010037B (en) * | 2012-07-20 | 2015-04-15 | 同济大学 | Automotive range extender based on linear ISG(Integrated Starter and Generator) motor/engine |
| CN104806354A (en) * | 2015-05-05 | 2015-07-29 | 北京理工大学 | Free piston internal combustion generation power system with adjustable compression ratio |
| CN104806354B (en) * | 2015-05-05 | 2017-12-22 | 北京理工大学 | The adjustable free-piston internal combustion power generation power system of compression ratio |
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