CN2864121Y - Positive-displacement engine - Google Patents
Positive-displacement engine Download PDFInfo
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- CN2864121Y CN2864121Y CNU2005200000031U CN200520000003U CN2864121Y CN 2864121 Y CN2864121 Y CN 2864121Y CN U2005200000031 U CNU2005200000031 U CN U2005200000031U CN 200520000003 U CN200520000003 U CN 200520000003U CN 2864121 Y CN2864121 Y CN 2864121Y
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Abstract
A modulation volume engine has the biggest difference with other constant volume engines in that: each cylinder has two mutual installed pistons. The inner piston is linked with the connection pole by the piston pin, while the outer piston has a piston ring and is supported on the inner piston by spring. The engine is charactered in that: the size change of every strokes are differernt. In the exhaust stroke, the outer piston arrives at the highest point of the cylinder, which almost completely exhausts the gas(the theoretical exhaust rate is of 95% to 98%), thereby making it possible to improve the compression ratio (>= 12); In the inspiratory stroke, as the inertia compatibilization displacement of the piston in the inlet end makes the gas input capacity greater than the gas input of the constant volume engine, the self-pressurized punction is relized and the fuel economy and emissions is improved. Because of the elastic energy storage function of the outer piston, the velocity improving of the peak pressure and the peak pressure is lowered, thereby reducing the structure force, and creating conditions to reduce the deadweight of the engine; and the smooth running is enhanced. The engine efficiency is improved because the retracting of the peak pressure increases the output torque. In a word, the performance of the modulation volume engine is greatly improved compared with the constant volume engine.
Description
Technical field:
The present invention relates to explosive motor field, particularly four-stroke spark ignition (as gasoline) motor, also be applicable to diesel oil or two stroke engine.
Background technique:
Explosive motor particularly four-stroke gasoline engine (other fuel that comprise similar work) is the current widely used a kind of motor of most important a kind of power source, particularly light-duty vehicle.
Through 100 years of development, four-stroke gasoline engine is gradually improved at present, and new technology constantly occurs, and its application is also day by day extensive.But all motors all can be described as the constant volume motor up to now, and promptly the swept volume of its four strokes is identical, and this just makes some intrinsic contradictions of this class motor thoroughly solve.
One. compression ratio and waste gas residual quantity: for avoiding gasoline mixture body generation deflagration phenomenon, present compression ratio is controlled at 8～11, promptly be to be about about 1/10 of cylinder capacity at the combustion space of piston head volume, and this residual volume of waste gas behind exhaust stroke terminal point just.But the air pressure during the air inlet terminal point is P
a=0.07～0.09MP, temperature T
aAbout=400 ° of K; And exhaust terminal point air pressure P
bAbout=1.1MP, temperature T
bAbout=1000 ° of K; Thereby residual volume(RV) than K=0.07 about.Reduce the K value to the raising engine power, efficient, reducing pollution emissions all has positive effect.Adopt supercharging technology can improve the K value, but pressurization system is complicated and significantly increase the motor manufacture cost.
Two. improve the highest gas pressure p of expansion space stroke
mContradiction with smoothness, efficient: Fig. 1 is the indicator diagram of four-stroke gasoline engine, but motor work done with crank torque output, thereby " moment of torsion-corner " curve (M-α) more can be represented the indicator diagram of motor exactly than " air pressure-volume " curve (P-V).Fig. 2 is crank-linkage mechanism force analysis figure: the moment of torsion when crank turns over the α angle: M=F*R (sin α+cos α * tan β)
M＝F*R′
In the formula: F-combustion gas is to the gross thrust of piston, F=P*S;
Air pressure in p-cylinder;
S-piston head area;
R-crank radius;
R '-equivalent radius; R '=R (sin α+cos α * tan β)
β＝sin
-1(R/L?sinα)
L-length of connecting rod
According to above-mentioned formula, we roughly calculate " moment of torsion-corner " curve, and shown in curve among Fig. 1 (M-α), the area that obvious M-α curve is surrounded can be represented the merit that single cylinder is done in the whole work cycle more accurately.
Generally (constant volume) motor requires the maximum gaseous-pressure P in the cylinder
mAppear at crank angle α=12～15 ° scope (the d point place among Fig. 1), corresponding at this moment:
M ≈ F
m* R '=P
m* S*R ' { equivalent radius R '=Rsin α }, and be not maximum output torque M
m,, i.e. P
mThe pressure that produces the almost overwhelming majority is born by engine structure (piston Xiao, connecting rod, bent axle, axle journal, body), because the raising speed of pressure P is very fast, thereby it is also more obvious to the percussion of parts, this bears with enough strong structure with regard to requiring, thereby the progressive lightweight of motor is restricted.
The peak value M of the torque curve of general as can be seen from Figure 1 (constant volume) motor
mNot with cylinder in maximum combustion gas air pressure peak value P
mOverlap, this show " air pressure-volume " curve (P-V curve) of general motor be not the motor work done best curve.
Three. the piston structure complexity, operating conditions is abominable, and operating life is short: the operating conditions of piston is extremely abominable in all motors at present.In per 1 work cycle, to bear the effect of 1 high temperature, high-pressure gas.Gaseous-pressure should be passed to the sealing that the crank work done realizes cylinder again, and require inertial force little, these be mutually related require to make piston almost without exception employing light metal material (as aluminum alloy) make, amount of deformation is also bigger under high temperature, high pressure effect; Because it is very inhomogeneous that piston Xiao's supporting structure distributes piston mass, thereby increased the weight of the distortion that the temperature difference causes.Become very complicated for reducing the shape that its influence can only make piston, thereby difficulty of processing is also big.This outside connecting rod-crank mechanism makes piston have a kind of opposite cross component force when work done and compression, makes piston press to casing wall, thereby makes the generation uneven wear of piston, thereby further influenced the working life of piston.
Though more than these problems for many years motor-dom never stopped the improvement paces, carried out many researchs from aspects such as structure, material, processing, the problems referred to above thoroughly solve or basic the solution.
Summary of the invention:
The present invention discloses a kind of new positive-displacement engine design for this reason, addresses the above problem preferably.
The object of the present invention is achieved like this:
A kind of positive-displacement engine, by cylinder, cylinder head and on intake and exhaust mechanism, spark plug, piston, connecting rod, bent axle etc. form, itself and maximum different being of general constant volume motor: its piston is made up of outer piston and inner carrier, and piston ring is installed on the outer piston; Have piston Xiao hole in the inner carrier, piston Xiao and the connecting rod that matches with it; The outer piston diameter of bore is slightly larger than the inner carrier outside diameter, and promptly inner carrier is sleeved in the outer piston slidably; Outer piston end face inwall is supported on the inner carrier with elastic element, promptly between outer piston end face inwall and inner carrier top one compressible space is arranged under free state.
The piston inner hole lower end is shaped on annular groove outside, and snap ring is housed in the groove, in the snap ring circular diameter less than the inner carrier outside diameter, thereby inner carrier can not be deviate from from the outer piston endoporus.
Described elastic element can be one or more helical springs, butterfly spring, volute spring or equidistant spring, also can be the cluster spring that is no less than two mutual fits, and wherein the rigidity of interior short spring is greater than the rigidity of foreign minister's spring.Removable (compression) spatial altitude after (outward) spring height assembles greater than inside and outside piston is not so that there is free clearance in piston set assembling back between inside and outside piston, spring, snap ring.
No piston Xiao hole on the outer piston, its shape is radial symmetric structure, has eliminated the temperature deformation that causes because of the mass distribution inequality, and this makes its inside and outside surface can be positive circle, thereby has saved complicated ellipsoid processing.Can fully cool off outer piston for making, in its end face inwall bossed shunting cone of central authorities and continuous water conservancy diversion cambered surface from the cutting oil of connecting rod small end oilhole ejection.
Because inner carrier does not contact combustion gas, thereby its end face can not seal, this makes the structural design of inner carrier can take into full account the manufacturability of structural rigidity and processing, all there is gusset to be connected between the seat side, two-piston Xiao hole thereon and between side and the inner carrier inner hole wall, thereby reduced the stress deformation of inner carrier significantly.Because inner carrier does not contact high-temperature fuel gas, and the abundant cooling of cutting oil is arranged, thereby the inner carrier temperature rise is not high, thereby can make the piston Xiao bore dia on it be slightly less than piston Xiao diameter, be that piston Xiao hole and piston Xiao realize drive fit, avoid the wearing and tearing in piston Xiao hole, prolonged the working life of piston.
The lubricant oil that scrapes for the oil ring that makes on the outer piston has the return flow line, is shaped on oil guide slot on inner carrier periphery top, is shaped on the spill port that communicates with the inner carrier endoporus in the oil guide slot bottom.
In order to guarantee the stability of spring when the reciprocating motion of the pistons, on the inner carrier top board, be shaped on location hole of the spring, and on the bottom in hole or sidewall, be shaped on the return port of cutting oil, so that can flow back to oil sump swimmingly from the cutting oil of connecting rod small end oilhole ejection.
To make the space between outer piston end face and the cylinder head be that the stroke volume will become with each working stroke condition to the elastic support dual-piston structure of this positive-displacement engine (designing suitable spring rate value) as can be seen:
1) in the compression stroke top dead center position, because the pressure of mixed gas makes the outer piston pressure spring, then make the space between outer piston end face and the cylinder head, satisfy combustion condition (pressure P, the temperature T) requirement that sets compression ratio, this is one of basic design of this positive-displacement engine.(as compression ratio ε=10 of setting, the pressure in this moment cylinder is about about 1MP, combustion chamber volume be about cylinder capacity 1/10th);
2) at the exhaust stroke terminal point, the pressure in the cylinder is about about 0.1MP, and outer piston makes the residual space of waste gas between outer piston end face and the cylinder head become very little, thereby the waste gas residual quantity is obviously reduced away from inner carrier under spring force and inertial force effect;
3) in intake stroke, because its starting point (top dead center) is located, outer piston is positioned at the cylinder extreme higher position, and locate at terminal point (lower dead center), inner carrier stop motion this moment, but outer piston continues to move down under the inertial force effect, thus enlarged admission space effectively.
4) in expansion space stroke, when mixed gas is lighted, when gas pressure sharply rose, outer piston overcomes spring (high stiffness region) under this pressure effect continued to move down on a small quantity, enlarged combustion chamber volume, thereby slowed down velocity of combustion, the gas pressure rate of climb that promptly slowed down, and the gaseous-pressure peak of curve is moved to right, as previously mentioned, then can increase output torque, promptly increase useful horsepower output, and improve the stress of each structure member of motor.
Description of drawings:
Fig. 1: indicated diagram of engine;
Fig. 2: connecting rod-crank mechanism force analysis figure
Fig. 3: this positive-displacement engine piston structure schematic representation
(left side is the front view of this piston structure, and the right is the side view of this piston structure)
Fig. 4: volume-variation schematic representation in four strokes of this positive-displacement engine
Fig. 5: this positive-displacement engine outer piston structural representation
Fig. 6: this positive-displacement engine outer piston and valve relativeness structural representation
Fig. 7: this positive-displacement engine inner carrier structural representation
Fig. 8: this positive-displacement engine piston spring rigidity and structural representation
Marginal data:
1. outer piston: 101. end faces, 102. compressions, 103. oil ring grooves, 104. head peripheries
105. annular groove 106. inner top surfaces 107 inner headed faces 108 shunting cones
109. water conservancy diversion cambered surface 110. skirt section peripheries 111. valve pits
112. loss of weight groove 113. return ports
2. inner carrier: 21. upper surfaces, 22. spring mounting holes, 23. return ports
24. 27. piston Xiao holes, piston Xiao hole seat 25. peripheries, 26. bottom surfaces
28. Xiao's hole end surface 29. gussets 210. inside ceiling panels 211. oil traps
212. spill port 213, the loss of weight groove
3. spring
4. connecting rod: 41. shafts, 42. oil spout roads, 43. connecting rod small end
44. Xiao microcephaly hole 45. nozzle openings
5. Xiao hole lining: 51. annular oil grooves, 52. oilholes, 53. lining peripheries
54. lining inner headed face 55. lining exterior edge faces
6. piston Xiao: 61. peripheries, 62. endoporus
7. snap ring:
8. bent axle
9. cylinder
10. cylinder head
11. outlet valve
12. spark plug
13. suction valve
Specific embodiments:
Shown in Figure 3 is a kind of embodiment's schematic representation of the present invention's " positive-displacement engine ", and the piston of positive-displacement engine is made up of outer piston 1 and inner carrier 2 and spring 3 as seen from the figure.Outer piston 1 head periphery 104 has the piston gas ring of installation and the compression 102 and the oil ring groove 103 of oil ring; Outer piston 1 endoporus 107 is cylindrical holes, and there is an annular groove 105 at its lower end mouth place, and snap ring 7 is installed in the groove 105, and snap ring 7 internal diameters are less than periphery 25 diameters of inner carrier 2.
The maximum that structure of the present invention is brought to motor changes: four stroke capacitys do not wait, being about to originally is that the constant volume motor becomes " positive-displacement engine ", though inner carrier is still by the work of constant volume engine characteristics, but, see also Fig. 4 in four strokes thereby make cylinder volume and performance characteristic that obvious variation take place because outer piston 1 usefulness spring 3 is supported on the top of inner carrier 2:
The starting point of design is the original state that guarantees expansion space stroke (III stroke): light the temperature T that is compressed the required burning of mixed gas
CAnd pressure P
C, promptly control the proper compression ratio, its main points are the control of spring rate, make motor when compression stroke (II stroke) terminal point (top dead center), the combustion chamber volume V of outer piston top 101 and 10 formation of cylinder head
CMeet the compression ratio requirement of design.For example choose compression ratio ε=10, at compression terminal point inner cylinder pressure P
cAbout=1MP, outer piston is in pressure P
cMove down the l2 distance under the effect, make the combustion chamber volume V of formation
cBe about cylinder 9 total measurement (volume) V
oAbout 1/10.(cylinder capacity V in the present invention
oBe defined as: at compression stroke lower dead center place, the cylinder volume that outer piston 1 end face is above.Because when this trip original state, inner carrier 2 is positioned at the lower dead center place, because inner cylinder pressure P approximates barometric pressure, thereby outer piston 1 is in free state under spring 3 effects; This moment, cylinder volume was suitable substantially with the constant volume motor).
The compression ratio ε of the positive-displacement engine of structure of the present invention also is subjected to outer piston 1 The Effect of Inertia Force.Because pistons reciprocating has motional inertia, the inertial force of outer piston 1 is inequality under the motor different rotating speeds, when low speed (as idling mode), because piston inertia power is little, also less because of the compression volume variation that inertial force causes, promptly compression ratio ε is also smaller; And when high speed because outer piston 1 inertial force increases, the additional compression amount that then causes thus also slightly increases, and has promptly increased compression ratio, thus the combustion condition when having improved high speed, and this just at present constant volume motor make great efforts the technical problem that solves.
At exhaust stroke (IV stroke), outlet valve 11 is opened, and high pressure, high-temp waste gas efflux rapidly; Move the realization forced-ventilated immediately on the piston, this is identical with the constant volume motor.But at exhaust stroke terminal point A
4Position (inner carrier 2 is positioned at the top dead center place) is owing to residual gas pressure P this moment
rVery low (being slightly larger than 0.1MP), move on will continuing at outer piston 1 under inertial force and the spring force effect (with inner carrier 2 axially at a distance of farthest), make the residual SPACE V between outer piston 1 and the cylinder head 10
rMinimum.This shows the residual quantity of the waste gas residual quantity of this positive-displacement engine in its cylinder of exhaust terminal point much smaller than the constant volume motor.
When entering suction stroke (I stroke), suction valve 13 is opened, and is descending at the pulling lower piston of crank-connecting rod, sucks incoming mixture, when inner carrier 2 moves to lower dead center B
1The time, outer piston 1 is owing to inertial force continues to move down l with pressure spring 3
1Stroke is then because the increase-volume V that outer piston 1 inertial force causes
1=l
1* S (S-outer piston 1 top area is approximately equal to the sectional area of cylinder 9) and l
1(V1) size is proportional to the rotating speed of motor: promptly the piston reciprocating speed is little during low speed, and promptly outer piston 1 inertial force is little, l
1(V1) also less; Outer piston 1 inertial force is big during high speed, thereby l
1(V1) also increase.Admission space when admission space is greater than low speed when being high speed, thereby the problem of under-inflation when having compensated high engine speeds preferably.For example establish: outer piston diameter D=7cm, quality m=1kg, working stroke L0=10cm, compression ratio ε=10; When engine speed n=3000rpm, can calculate: can l
1≈ l
2Be V
1≈ V
C).
This positive-displacement engine has very high charging efficiency as can be seen:
1) owing to move the residual space of compressed exhaust gas on the inertia of outer piston 1 when the exhaust stroke terminal point, can reach 95%～98% toxic emission efficient, thereby the waste gas residual quantity is significantly less than the constant volume motor.
2) outer piston 1 moves down stroke l at the inertia of suction stroke terminal point
1Increased the aspirated volume (V of cylinder
1), promptly this positive-displacement engine aspirated volume is greater than the constant volume motor of identical reciprocating stroke amount.The charging efficiency η of this positive-displacement engine is much larger than 0.7～0.8 numerical value of constant volume motor as can be seen, and promptly this positive-displacement engine has from pressurization.
Reduce significantly owing to the high temperature residual volume(RV) in addition, thereby the temperature rise of the fresh mix gas that sucks also reduces (decline of air inlet finishing temperature), for example: establishing toxic emission efficient is 96%, it is 1/25th (and the constant volume motor is about 1/10th or bigger) that the waste gas residual quantity is about total air inflow, then waste gas obviously reduces the heat effect that newly advances mixed gas, calculating shows the gas temperature of air inlet terminal point 30 °～50 ° K that will descend, this has created condition for raising compression ratio ε, promptly compression ratio ε can be brought up to 12 or higher, and unlikelyly cause quick-fried right phenomenon, thereby improved engine efficiency; And, make positive-displacement engine that good power character be arranged, fuel economy and better emission performance because the minimizing of exhausted air quantity improves combustion condition, thereby improved output power, moment of torsion.
In compression stroke (III stroke) starting point (lower dead center), because the cylinder internal air pressure is about about 0.1MP, outer piston 1 is returned to free position under spring 3 effects, promptly be in the B2 position that compression stroke begins, because inlet and outlet this moment valve 13,11 is all closed, along with inner carrier 2 rises, outer piston 1 mixed gas that gradually reduces, in-cylinder pressure P rises; Be subjected to the effect of P simultaneously, outer piston 1 spring 3 that also gradually reduces.When inner carrier 2 walked to top dead center A2 position, the pressure P of compressed mixed gas rose to the initial combustion condition (P that motor requires in the firing chamber at this moment
C, T
C).At this pressure P
CUnder the effect, outer piston 1 pressure spring 3 moves down l2, forms necessary combustion space V
C(rigidity Design of spring can satisfy above-mentioned requirement).But the combustion space V that positive-displacement engine of the present invention forms at the compression stroke terminal point
CBe not definite value, except that above-mentioned condition, V
CAlso be subjected to outer piston 1 inertia effects: when high speed, outer piston 1 inertial force is big, and the inertia decrement that causes also increases, i.e. combustion space V when high speed
CTo slightly reduce, promptly improve compression ratio; Outer piston 1 inertial force is little during opposite low speed, combustion space V
CTo increase be arranged slightly, promptly compression ratio diminishes.And this has just in time satisfied the needs that when the motor high, low speed is moved compression ratio changed, and has realized becoming certainly the function of compression ratio.
When expansion space stroke (III stroke), because compression ratio is controlled in the setting range, thereby it is basic identical to light the condition and the constant volume motor of compressed mixed gas.But because positive-displacement engine charging efficiency height, residual gas is than low, thereby combustion condition is better.Along with inner pressure of air cylinder P
3Rise rapidly, outer piston is at P
3Effect lower compression spring 3 and moving down (as l among the figure
3), thereby enlarged the bags, slowed down velocity of combustion, reduced the rate of climb of air pressure, promptly slightly reduced peak value air pressure P
mWith peak temperature T
m, and make the surge pressure P of positive-displacement engine
mMove to right, as the P ' among Fig. 1-V ' curve.Because engine output is proportional to rotation speed n and changes apart from M, and change apart from the M direct proportaion in gas pressure P and bent axle effective radius R ' (R '=R sin α), because the surge pressure P of positive-displacement engine
mMove to right, promptly P '-V ' curve moves to right, surge pressure P
mCorresponding corner α is bigger, thereby R ' obviously increases, the output M of positive-displacement engine is increased, the output that is positive-displacement engine is changeed apart from bigger, under same rotational speed, output power is also big more, shown in the commentaries on classics distance-volume curve of positive-displacement engine (M '-V ') (also can explain this variation from the energy conservation principle).This explanation positive-displacement engine has better volumetric efficiency, simultaneously owing to reduced the rate of climb and the surge pressure P of cylinder internal air pressure P
mEngine structure (piston, connecting rod, bearing, bent axle, body etc.) stressing conditions is had greatly improved, thereby can design these stressed other, modular construction lighter and handier, thereby can alleviate the weight of motor, help the oil consumption reduction of car load and make engine running more steady, its longer service life.
Excessive for combustion condition is changed, thereby outer piston 1 is at P
3Effect bottom offset amount l
3Can not be excessive, promptly require spring 3 this moment rigidity very high (in compression stroke, outer piston 1 is at P
2Effect bottom offset amount l
2The time, require the rigidity of spring 3 lower), so medi-spring of the present invention 3 is to adopt variable rate spring (as cluster spring, volute spring or displacement spring).
As can be seen, the abominable operating conditions that dual-piston structure will bear the single piston of former cause (bearing high temperature, high-pressure gas and high-speed transfer power) is shared by inside and outside piston respectively: as 1 of outer piston bear high temperature, high-pressure gas pressure and realize and cylinder between sealing, but the pressure of cylinder passes to inner carrier 2 by outer piston 1 by spring 3; Inner carrier 2 becomes this pressure the power output of motor through piston Xiao 6---connecting rod 4---crank 8.Though so inner carrier 2 structures and stressed and single piston (constant volume) motor are similar substantially, inner carrier 2 does not bear high temperature action (especially when adopting forced oil cooling) basically and bears the cylinder sealing, thereby the thermal distortion of piston is little; Be convenient to adopt reasonable force structure with the minimizing stress deformation simultaneously, thereby greatly improved the operating conditions of baroque inner carrier.Outside piston must be processed into ellipse in the constant volume motor, and up-small and down-big taper or other complicated shapes, and to making difficulty of processing big, piston life is short.And in the dual-piston structure of positive-displacement engine, the problems referred to above exist hardly, and outer piston 1 is owing to can adopt simple round column structure, thereby easy processing; In addition when to-and-fro motion because compression, the side pressure that alternately exists in the expansion space stroke, can make outer piston 1 that rotation takes place, can make the wearing and tearing homogenization of outer piston 1 like this, prolonged piston life effectively, and the eccentric wear of constant volume engine piston be inevitable.
Below relation between functional parameter and structure characteristic further is discussed:
The axial clearance of the maximum between outer piston 1 and the inner carrier 2 is l0 as can be seen from Figure 3, can be when making the exhaust stroke terminal point with waste gas discharge as much as possible, outer piston end face 101 be positioned at the cylinder extreme higher position (because exhaust terminal point cylinder internal air pressure approximates barometric pressure, outer piston 1 under the effect of spring 3 and 21 at inner carrier top at a distance of being l for the maximal clearance
0); And give compression ratio (ε) scope of establishing in the space that the compression destination county must be controlled between outer piston top and the cylinder head, because the interior air pressure of cylinder this moment is P
C, then act on the gas pressure on the outer piston 2:
F
C=P
C* S (S-outer piston top area)
This F
CForce compresses spring 3 makes outer piston 2 decline l
2Distance,
l
2=F
C/ K
2=P
C* S/K
2(K
2---the rigidity of spring 3 these sections)
Even the spatial volume V that forms between outer piston end face 101 and the cylinder head 10
C, meet spatial volume requirement in the compression ratio ε lower combustion chamber that sets.As: getting compression ratio is ε, ε=V
C/ V
0(V
0---cylinder capacity V
oBe defined as: at compression stroke lower dead center place, the cylinder volume that outer piston 1 end face is above).If the rigidity of spring 3 these sections is K
2, then can solve:
K
2＝ε(S*P
C/V
0)
As previously mentioned, for reaching the velocity of combustion that suitably slows down, to reduce combustion peak air pressure P
mAnd the purpose of the gaseous-pressure P rate of climb that slows down, then require outer piston 1 at burning air pressure p
3Effect continues decline l down
3With suitable expansion combustion space, because P
m＞＞P
C, change the excessive normal combustion process that influences for not making combustion condition, must control l
3The size of value, general desirable l
3≤ l
2, promptly this moment spring 3 rigidity: K3 〉=K
2(P
m/ P
C)
On structure, this shows that spring 3 must have the change rigidity characteristic, satisfies above-mentioned requirements as adopting helical spring and multi-disc butterfly spring suit, shown in Fig. 8 (I), also can adopt volute spring, not equidistant spring to satisfy above-mentioned requirements in addition, shown in Fig. 8 (II, III).
Fig. 5 is the structural representation of outer piston 1.By there not being piston Xiao hole thereon, thus compression 102 apart from end face 106 and mutual spacing from can be more farther, this can reduce through the vent flow of piston ring otch and heat distortion amount.Its head 104 (compression 102 is with top) diameter is slightly less than the skirt section diameter, contact the thermal distortion that high temperature causes with compensation, its end face 101 shapes depend mainly on cylinder head design, and (chamber structure, air valve are arranged, spark-plug locations etc.), Fig. 6 is a kind of hemispherical combustion chamber layout of a kind of symmetrical inclined overhead valve, mid-spark plug.For waste gas is drained as far as possible, outer piston 1 is extremely pressed close to cylinder head at the exhaust terminal point, collides for avoiding valve and outer piston end face 101, processes the valve pit 111 identical with the valve number on end face 101, as shown in Figure 6.
Outer piston 1 top inner surface 106 middle parts have cooling-lubricant to divide flow cone 108 and water conservancy diversion cambered surface 109, so that can cool off the entire top internal surface 106 of outer piston 1 well by the lubricant oil of connecting rod small end 43 ejection, prevent that the temperature rise of outer piston end face 101 is too high.Can use sand blast for improving cooling effect internal surface 106, so that its rough surface.Internal surface 106 should be the plane corresponding to contact spring 3 positions, so as with the upper surface excellent contact of spring 3.There is groove 105 outer piston endoporus 107 lower ends in order to snap ring 7 to be installed, and deviate from from outer piston endoporus 107 to stop inner carrier 2.Do not link to each other owing to piston Xiao as can be seen with outer piston 1, thereby outer piston 1 can be made the uniform axially symmetric structure of thickness, avoided like this because of the uneven inhomogeneous thermal distortion that causes of mass distribution, promptly will periphery 104,109 are processed into ellipse, make easily simple that the processing of outer piston becomes like this, promptly cut down finished cost significantly, and because no inhomogeneous thermal distortion, the outer piston operating conditions is improved, not only helps to improve the cylinder operating conditions and also alleviated wearing and tearing, prolonged the working life of piston and cylinder sleeve, for weight reduction and minimizing finish surface, outer piston skirt section 109 intermediate portion diameters can be reduced.
Fig. 7 is the structural drawing of inner carrier 2, as can be seen inner carrier 2 and conventional piston have one very big different: the axial Open architecture of employing that is inner carrier 2, this is because inner carrier 2 does not contact the high temperature in the cylinder, pressurized gas, this make inner carrier 2 structure Design and make to become easily: by stiffening rib 29 is set, the radial rigidity of inner carrier 2 is greatly improved, and this inhomogeneous deformation that the lateral pressure of inner carrier 2 when transferring power caused reduces to very little; Simultaneously since inner carrier 2 from high-temperature gas, and adopt again and force the oil spout cooling and lubricating so thermal distortion is also reduced, thereby make the periphery 25 of inner carrier 2 also need not be processed into ellipse, this has not only simplified processing, and has improved the quality of fit of inside and outside piston.Groove 22 is in order to mounting spring 3, and the hole 23 of its bottom or side is the return flow line of the lubricant oil of above-mentioned cooling outer piston 1 internal surface.Because the inner carrier temperature is left lessly, the diameter in the piston Xiao hole 27 on piston Xiao seat 23 is slightly less than piston Xiao 6 outside diameters, thereby piston Xiao 6 is pressed in piston Xiao hole 27, thereby can effectively prolong the life-span of inner carrier.Cylindrical necking down 211 is the lubricant oil scrape off from the oil ring groove 103 of outer piston 1 for collecting, and 212 is back in the oil sump through the hole, the necking down of bottom be for reduce finish surface and improve in outer piston quality of fit and process.
Total the above as can be seen this positive-displacement engine in, outer piston structure and constant volume engine piston structurally have very big-difference, its structure and technology capability are greatly improved,
Can find out and adopt elasticity double-piston positive-displacement engine to have the following advantages:
1. reduce the waste gas residual quantity, increase air inflow, the residual ratio of waste gas is reduced greatly, charging efficiency is remarkable Increase, the combustion position of engine is improved, and compression ratio ε can be brought up to 12 or more Height, thus engine efficiency improved; Fuel economy and exhaust emissions all improve;
2. because suction stroke has pressurization, effectively output torque increases in addition, thereby has improved and rise merit The rate ratio under the equal-wattage output condition, alleviates engine weight, thereby further reduces oil consumption.
3. the stressed improvement of engine structure then can reduce inner carrier, piston Xiao, company during owing to expansion space stroke The physical dimension of bar, bearing, bent axle, body, thus make the engine lightweight, more be conducive to into one Step reduces the fuel consume of car load.
Since the elastic piston system have buffering, energy-absorbing function, it is unlikely too fast that the cylinder combustion atmospheric pressure is risen, thereby make engine operation more steady, and engine behavior is further improved.
Because in, the condition of work of outer piston is greatly improved, and its processability of product structure also is greatly improved, Thereby reduced manufacturing cost, prolonged service life.
Positive-displacement engine is compared very big variation with the constant volume engine and is changed from the principle to the structure in a word Advance, be worth further research and extension.
Claims (7)
1. positive-displacement engine, by cylinder, cylinder head and on intake and exhaust mechanism, spark plug, piston, connecting rod, bent axle etc. form, it is characterized in that: its piston is made up of outer piston and inner carrier, and piston ring is installed on the outer piston; The connecting rod that has piston Xiao hole, piston Xiao in the inner carrier and match with it; The outer piston diameter of bore is slightly larger than the inner carrier outside diameter; Outer piston end face inwall is supported on the inner carrier with elastic element.
2. positive-displacement engine according to claim 1 is characterized in that: be shaped on annular groove in described outer piston endoporus lower end, snap ring is housed in the groove, circular diameter is less than the inner carrier outside diameter in the snap ring.
3. positive-displacement engine according to claim 1 is characterized in that: described elastic element can be one or more helical springs, butterfly spring, volute spring, not equidistant spring etc. or its combination; It also can be the cluster spring that is no less than two mutual fits.
4. positive-displacement engine according to claim 1 is characterized in that: described outer piston shape is radial symmetric structure, bossed cutting oil shunting cone of its end face inwall central authorities and the water conservancy diversion cambered surface that links to each other.
5. positive-displacement engine according to claim 1 is characterized in that: the end face of described inner carrier does not seal, and all has gusset to be connected between the seat side, two-piston Xiao hole on the inner carrier and between side and the inner carrier inner hole wall; Piston Xiao bore dia on the inner carrier is slightly less than piston Xiao diameter.
6. positive-displacement engine according to claim 5 is characterized in that: described inner carrier periphery top is shaped on oil guide slot, is shaped on the spill port that communicates with endoporus in the oil guide slot bottom.
7. positive-displacement engine according to claim 5 is characterized in that: be shaped on location hole of the spring on the described inner carrier top board, be shaped on the return port of cutting oil on the bottom in hole or sidewall.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2005200000031U CN2864121Y (en) | 2005-01-04 | 2005-01-04 | Positive-displacement engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2005200000031U CN2864121Y (en) | 2005-01-04 | 2005-01-04 | Positive-displacement engine |
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| Publication Number | Publication Date |
|---|---|
| CN2864121Y true CN2864121Y (en) | 2007-01-31 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2005200000031U Expired - Fee Related CN2864121Y (en) | 2005-01-04 | 2005-01-04 | Positive-displacement engine |
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| CN (1) | CN2864121Y (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103233824A (en) * | 2013-04-28 | 2013-08-07 | 李宜平 | Capacity-controlling constant pressure system of engine |
| CN104005875A (en) * | 2014-05-15 | 2014-08-27 | 陈光明 | Combined pressure adjusting piston |
| CN104564403A (en) * | 2014-12-08 | 2015-04-29 | 陈光明 | Combined pressure regulating piston based on elastic silencing and impact-resistant cylinder gasket |
| CN105840267A (en) * | 2016-05-06 | 2016-08-10 | 陈光明 | Controllable elastic internal combustion engine |
| CN105840338A (en) * | 2016-05-06 | 2016-08-10 | 陈光明 | Controllable elastic internal combustion engine |
| CN105840337A (en) * | 2016-05-06 | 2016-08-10 | 陈光明 | Controllable elastic internal combustion engine |
| CN109869229A (en) * | 2019-04-02 | 2019-06-11 | 上海智御动力技术有限公司 | Alterable compression ratio formula piston rod device |
| CN111425313A (en) * | 2020-03-20 | 2020-07-17 | 唐为民 | Combined piston with variable compression ratio |
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2005
- 2005-01-04 CN CNU2005200000031U patent/CN2864121Y/en not_active Expired - Fee Related
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103233824A (en) * | 2013-04-28 | 2013-08-07 | 李宜平 | Capacity-controlling constant pressure system of engine |
| CN103233824B (en) * | 2013-04-28 | 2015-08-26 | 李宜平 | A kind of Capacity-controllingconstant constant pressure system of engine |
| CN104005875A (en) * | 2014-05-15 | 2014-08-27 | 陈光明 | Combined pressure adjusting piston |
| CN104564403A (en) * | 2014-12-08 | 2015-04-29 | 陈光明 | Combined pressure regulating piston based on elastic silencing and impact-resistant cylinder gasket |
| CN105840267A (en) * | 2016-05-06 | 2016-08-10 | 陈光明 | Controllable elastic internal combustion engine |
| CN105840338A (en) * | 2016-05-06 | 2016-08-10 | 陈光明 | Controllable elastic internal combustion engine |
| CN105840337A (en) * | 2016-05-06 | 2016-08-10 | 陈光明 | Controllable elastic internal combustion engine |
| CN105840338B (en) * | 2016-05-06 | 2018-05-25 | 陈光明 | Controlled elasticity internal combustion engine |
| CN105840267B (en) * | 2016-05-06 | 2018-05-25 | 陈光明 | Controlled elasticity internal combustion engine |
| CN105840337B (en) * | 2016-05-06 | 2018-05-25 | 陈光明 | Controlled elasticity internal combustion engine |
| CN109869229A (en) * | 2019-04-02 | 2019-06-11 | 上海智御动力技术有限公司 | Alterable compression ratio formula piston rod device |
| CN111425313A (en) * | 2020-03-20 | 2020-07-17 | 唐为民 | Combined piston with variable compression ratio |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20070131 Termination date: 20110104 |