CN104179591A - Piston structure capable of realizing variable compression ratio of engine - Google Patents
Piston structure capable of realizing variable compression ratio of engine Download PDFInfo
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- CN104179591A CN104179591A CN201410394724.9A CN201410394724A CN104179591A CN 104179591 A CN104179591 A CN 104179591A CN 201410394724 A CN201410394724 A CN 201410394724A CN 104179591 A CN104179591 A CN 104179591A
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Abstract
A piston structure capable of realizing the variable compression ratio of an engine comprises a piston pin boss, wherein a piston pin boss hole is formed in the piston pin boss; a barrel-shaped piston pin is arranged in the piston pin boss hole in a full floating manner, a leaf spring body is mounted in the piston pin; inner check rings are respectively arranged at the two ends of the piston pin: leaf spring pressing blocks are respectively arranged on the outer sides of the two inner check rings; the two ends of the leaf spring body are propped against the piston pin boss hole through the leaf spring pressing blocks with set pre-tightening force; a clearance delta(h) is reserved between the top of the piston pin and the top of the piston pin boss hole; the upper limit value and the lower limit value of the variable compression ratio are determined by the size of the clearance delta(h); outer check rings are respectively arranged on the outer sides of the leaf spring pressing blocks at the two ends of the leaf spring body; a connecting rod is fixedly mounted and arranged on the outer side of the piston pin. The piston structure is simple, the compression ratio of the engine can be changed effectively through the deformation of the leaf spring body, and the engine is enabled to have good power performance, fuel economy and good emission performance under different load working conditions.
Description
Technical field
The present invention relates to piston of automobile formula motor, particularly a kind of piston structure of realizing variable compression ratio of engines that is adapted to petrol engine and aviation piston engine.
Background technique
The compression ratio of motor refers to the ratio of its piston cylinder internal volume and piston cylinder internal volume in the time of top dead center position in the time of bottom dead center position, is also the ratio of cylinder operation total measurement (volume) and combustion chamber volume, improves compression ratio and will improve the thermal efficiency of motor.
At present in world wide, passenger vehicle engine mainly with petrol engine as power plant.Because the cost of petrol engine is low, power per liter is high, lightweight, and exhaust aftertreatment is easy, and petrol engine will be the major impetus device of passenger car in the future for a long period of time.But uniform-charge Otto-engine is compared with diesel engine for automobile, for fear of producing phenomenon of detonation, compression ratio numerical value is lower and immobilize, and when this just makes it work under partial load condition, the thermal efficiency is lower and oil consumption is higher.And in urban road, the passenger car overwhelming majority time is all operated under partial load condition.Therefore, improve the thermal efficiency of petrol engine under partial load condition, improve its fuel economy and become very important problem in current vehicle energy saving research, one of approach addressing this problem is to adopt changeable compression ratio technique.When changeable compression ratio technique can make motor work under operating mode at full capacity, adopt lower compression ratio to prevent pinking; And while working under partial load condition, adopt higher compression ratio to reduce fuel consumption rate.
Existing research shows, adopts lean homogeneous charge burning and improves the technology such as heat management and can reduce oil consumption about 5%; Adopt the technology such as miniaturization technology and variable valve timing can reduce oil consumption about 10%; Adopt gasoline direct technology can reduce oil consumption about 15%; But, adopt the miniaturization technology of variable compression ratio and high level but can reduce about 26% left and right of oil consumption, this and the diesel engine thermal efficiency are very approaching.
Typical case's model machine example:
1.6 liters of SVC variable compression ratios of Sa Bo company of Sweden (compression ratio can change between 8～14) motor adopts mechanical supercharger, 166 kilowatts of peak outputs, Maximum Torque 305 Newton meters, power and the moment of torsion of 3.0 liters of naturally aspirated engine are reached, its comprehensive oil consumption has reduced by 30% than fixing compression ratio formula motor, and meets European IV emission standard.
France 1.5 liters of MCE5 VCRi (compression ratio can change between 7～20) maximum power is 162 kilowatts, Maximum Torque is 420 Newton meters, its moment of torsion has reached now the torque level of V8 motor (as benz G500,5L V8 Maximum Torque 460 Newton meters; Toyota patrols LC200 in land, 4.7L V8 Maximum Torque 410 Newton meters), per 100 km oil consumption is only 6.7 liters, and fuel economy improves 35%, and the discharge amount of carbon dioxide is 158 grams/kilometer.
Current state-of-the-art motor adopts turbosupercharging to combine with in-cylinder direct injection technology, has outstanding power performance and the economy performance.As 2013 sections of Mondeo 1.5L GTDi180 motors, compression ratio is 10, and peak output is 133 kilowatts, and Maximum Torque is 240 Newton meters, and the comprehensive oil consumption of Ministry of Industry and Information is 6.9 liters, and actual measurement oil consumption is 7.9 liters; And for example 2012 sections of benz B2001.6 rise motor, and compression ratio is 10.3, and peak output is 115 kilowatts, and Maximum Torque is 250 Newton meters, and the comprehensive oil consumption of Ministry of Industry and Information is 6.6 liters, and actual measurement oil consumption is 7.8 liters; In addition, in 2014 " annual international motor Grand Prix " competition, France PSA Peugeot Citroen 1.6THP turbo-charged direct injection motor is won the championship in 1.4L-1.8L gold discharge capacity group, again surmount with absolute predominance the germany volkswagen 1.8TFSI motor that is considered to turbogenerator " mark post ", continue to hold a post or title this group first place for eight times, the peak output of this motor is 123 kilowatts, and Maximum Torque can reach 245 Newton meters.By comparing visible with the model machine example related data of above-mentioned employing variable compression ratio engine, aspect power performance and the economy performance, adopt the motor of changeable compression ratio technique to have larger technical advantage than the current state-of-the-art motor that adopts turbosupercharging to combine with in-cylinder direct injection technology, this technology also meets the development trend of society energy-conserving and environment-protective.
Changeable compression ratio technique and supercharging technology are in conjunction with the engines fuel-economizing 20-40% that can make same displacement, power increases more than 50%, discharge improves, the weight and volume of motor diminishes, can adapt to fuel oil and the pluralities of fuel of different labels, the design that therefore meets motor is little, lightweight to volume, power to weight ratio is high and the trend of the future development of energy-conserving and environment-protective.
The realization of variable compression ratio of engines has a lot of technological schemes and Patents both at home and abroad at present, but mostly all there is complicated in mechanical structure, variable compression ratio numerical control difficulty, be difficult to the problems such as the volume and weight increase that solves dynamic balancing and make motor, its development difficulty and cost are increased greatly.For example French MCE5 variable compression ratio engine, owing to having adopted the structures such as brand-new bent axle, connecting rod, piston and hydraulic controller, because having dropped into greatly, development difficulty reaches tens00000000 Euros for development of new component and a large amount of relevant production technology process of exploitation; And for example the SVC of Sa Bo company variable compression ratio engine is compared with conventional engines, it has been divided into upper and lower two parts, upper half part is made up of cylinder head and five cylinder integrated cylinders cast in block, lower half portion is made up of crankcase, the crankshaft and piston of motor, piece cylinder head can rotate round crankcase, because the quality of this motor pivotable parts is large, it rotates needs very large energy, makes the volume of motor and quality greatly increase simultaneously; In addition, many push and pull system VCR motor that Japanese Nissan company adopts, makes motor boundary dimension increase, vibrate increase, causes the corresponding increase of frictional loss because movable part increases.Because the existing variable compression ratio of engines technology that realizes lacks practicability, only there is prototype design at present and cannot realize commercialization, the passenger car volume production of so far there are no equipment variable compression ratio engine is sold.
Summary of the invention
The object of the invention is, for prior art deficiency, provide a kind of simple in structure, variable compression ratio control is simple, motor volume and weight are increased to the little piston structure of realizing variable compression ratio of engines, power character, fuel economy that it has all had motor by changing engine compression ratio under different load operating mode.
First illustrate, " at full capacity " mentioned is herein the maximum planned load of mean engine; " the precompression load " mentioned is herein to instigate leaf spring body to be held in piston pin boss hole, load when leaf spring body generation precompression distortion; " its pre-compressed state " mentioned is herein to instigate leaf spring body to be held in piston pin boss hole, the state of leaf spring body generation precompression distortion.
For achieving the above object, solution of the present invention is: a kind of piston structure of realizing variable compression ratio of engines, comprise piston pin boss, and in this piston pin boss, be provided with piston pin boss hole, a cartridge type wrist pin is arranged in this piston pin boss hole with wholly floating; One leaf spring body is arranged in this wrist pin, the two ends of this wrist pin arrange respectively inner shield ring, the outside of two ends inner shield ring arranges respectively leaf spring briquetting, the two ends of described leaf spring body are held in piston pin boss hole through described leaf spring briquetting with the pretightening force of setting, and make there is a gap △ h between the top of described wrist pin and the top in described piston pin boss hole; The two end plates spring lock block outside of described leaf spring body is provided with outer back-up ring; The outside of this wrist pin is fixedly equiped with connecting rod; When engine operation load is less than 20%～30% at full capacity time, in the time of cylinder compression stroke terminal, this leaf spring body is only in its pre-compressed state, and its effective deformation amount is zero, and compression ratio reaches maximum value ε
max; When engine operation load is at full capacity time, in the time of compression stroke terminal, this leaf spring body is compressed into the maximum effective deformation amount △ h of generation, and this wrist pin top contacts with top, piston pin boss hole, and compression ratio reaches minimum value ε
min; Be 20%～30% during at full capacity to operating mode between at full capacity at engine operation load, in the time of compression stroke terminal, this leaf spring body is compressed into and produces and the corresponding effective deformation amount of load, corresponding the reducing of gap width between this wrist pin top and this top, piston pin boss hole, this leaf spring body effective deformation amount is greater than zero and be less than △ h, and corresponding compression ratio is with the load ε that do not coexist
minand ε
maxbetween change.
The middle part of the radial cross section in this piston pin boss hole is that length is the straightway of △ h, and upper and lower two ends are radius R
1semicircle.
This piston structure is in the time of free state, and this wrist pin contacts with the bottom in this piston pin boss hole, and the size of the gap △ h between this wrist pin top and this top, piston pin boss hole has determined CLV ceiling limit value and the lower limit of variable compression ratio.
The supporting surface of this leaf spring body is plane or arc surface, and the longitudinal section of leaf spring body deformability section is prismatic shapes or variable cross section shape.
This wrist pin is drum, and the lower shape of this leaf spring body is the arc surface that radius is slightly less than wrist pin internal diameter.
The geometrical shape of this leaf spring briquetting bottom requires to match with the supporting surface geometrical shape of this leaf spring body, rotates in this leaf spring briquetting with the end of limiting this leaf spring body; The external shape of this leaf spring briquetting and external geometric overall dimension require to coordinate with geometrical shape and the physical dimension in this piston pin boss hole, the length that makes this leaf spring briquetting and this piston pin boss hole is that the straightway of the △ h confinement plate spring lock block that closely cooperates rotates in piston pin boss, guarantees that this leaf spring body can only move up and down.Such as, the supporting surface of this leaf spring body is plane, deformation section longitudinal section is variable cross section shape, and the bottom of this leaf spring body is the arc surface that radius is slightly less than this wrist pin internal diameter; The top shape of this leaf spring briquetting is the arc surface that radius is slightly less than this piston pin boss pore radius, and the hypomere of this leaf spring briquetting is that length is the straightway of △ h, and the bottom of this leaf spring briquetting is the groove matching with the section of supporting of this plate body.
The radial cross section in this piston pin boss hole is shaped as: centre is that length is the straightway of △ h, and two ends are respectively radius and equal the semicircle of piston pin boss pore radius.
The length of this wrist pin is consistent with the bottom lengths of this leaf spring body.
Compared with prior art, the present invention is in the situation that motor remaining part remains unchanged substantially, design a kind of new piston structure, this piston by arranging wrist pin in piston pin boss hole, leaf spring body is set in this wrist pin again, this leaf spring body is held in this piston pin boss hole with certain pretightening force through leaf spring briquetting, this wrist pin, the outside of leaf spring body and leaf spring briquetting arranges respectively back-up ring to limit its axial float, just can reach the object that changes engine compression ratio by the effective deformation of leaf spring body, not only realize the variable of engine compression ratio by simple structure, and due under different load situation, car engine function adopts optimal compression ratio, thereby its power is increased, fuel economy improves, exhaust emissions also obtains corresponding improvement.
Brief description of the drawings
Fig. 1 is piston structure figure of the present invention.
Fig. 2 is piston connecting rod structure figure of the present invention.
Fig. 3 is leaf spring body structure figure of the present invention.
Fig. 4 is the left view of Fig. 3.
Fig. 5 is leaf spring briquette structure figure of the present invention.
Fig. 6 is the A-A sectional view of Fig. 5.
Fig. 7 is back-up ring structural drawing of the present invention.
Fig. 8 is the B-B sectional view of Fig. 7.
Fig. 9 is the axial cross section shape figure in the seat hole of piston pin boss of the present invention.
Figure 10 is wrist pin structural drawing of the present invention.
Figure 11 is the left view of Figure 10.
Figure 12 is that piston of the present invention is in bottom dead center position schematic diagram.
Figure 13 be piston of the present invention in the time that motor is less than precompression load condition in top dead center position schematic diagram.
Figure 14 be piston of the present invention motor at full capacity when operating mode in top dead center position schematic diagram.
Figure 15 be piston of the present invention engine operation in precompression load condition (left figure) and at full capacity when operating mode (right figure) in relatively schematic diagram of top dead center position.
In figure: 1-wrist pin; 2-leaf spring body; 3-leaf spring briquetting; 4-inner shield ring; 5-piston pin boss; 6-connecting rod; 7-piston pin boss hole; The outer back-up ring of 8-; 9-cylinder liner; 10-cylinder head; 11-intake valve; 12-exhaust valve; △ h-maximum effective deformation amount; R
1-piston pin boss circular hole part radius; R
2-wrist pin exradius.
Embodiment
As shown in Figure 1, piston structure one embodiment of the present invention comprises the piston pin boss 5 of hollow, in this piston pin boss 5, is provided with piston pin boss hole 7, the radial cross section (as shown in Figure 9) in this piston pin boss hole 7 be with straightway and two radiuses that length is △ h be R
1the semicircle of (piston pin boss circular hole part radius) is joined together to form.The wrist pin 1 of one cylinder type is arranged in this piston pin boss hole 7 with wholly floating.One leaf spring body 2 is arranged in this wrist pin 1, the two ends of this wrist pin 1 arrange respectively inner shield ring 4, the outside of two inner shield rings 4 arranges respectively leaf spring briquetting 3, the two ends of this leaf spring body 2 are held in piston pin boss hole 7 through leaf spring briquetting 3 with the pretightening force of setting, and make between the top of this wrist pin 1 and the top in this piston pin boss hole 7, there is a gap △ h.The outside of two leaf spring briquettings 3 is provided with outer back-up ring 8.This inner shield ring 4 is for stoping wrist pin 1 and leaf spring body 2 axial floats, and this inside and outside back-up ring 4,8 stops leaf spring briquetting 3 axial floats jointly.
In Fig. 1, piston of the present invention is in free state, and wrist pin 1 contacts with the bottom in piston pin boss hole 7.Now, have a gap △ h between wrist pin top and top, piston pin boss hole, the size of this gap width has determined CLV ceiling limit value and the lower limit (concrete analysis is asked for an interview hereinafter) of variable compression ratio.The design load of △ h can be taken as several millimeters.Can be set in engine operation load and be less than a certain less load (as 20%～30% at full capacity) time, end in compression stroke, leaf spring body 2 is only in its pre-compressed state, its effective deformation amount is zero (effective deformation amount refers to the poor of leaf spring body maximum deformation quantity and leaf spring body precompression amount of deformation), now, compression ratio reaches maximum value ε
max; And at full capacity time, end in compression stroke, leaf spring body is compressed into and produces maximum effective deformation amount △ h, and now, wrist pin top contacts with top, piston pin boss hole, and compression ratio reaches minimum value ε
min; And at this smaller portions load to other load condition between at full capacity, end in compression stroke, leaf spring body is compressed into the generation corresponding effective deformation amount of loading therewith, corresponding the reducing of gap width between wrist pin top and top, piston pin boss hole, leaf spring body effective deformation amount is greater than zero and be less than △ h, and corresponding compression ratio is with the load ε that do not coexist
minand ε
maxbetween change, this has just reached the object that compression ratio changes with payload.
In Fig. 1, the pretightening force that leaf spring body 2 is provided with when mounted, can be set in 20%～30% left and right at full capacity under, leaf spring body 2 is in its pre-compressed state, compression ratio is maximum value ε
max, obtain leaf spring body pretightening force numerical value by pressure maximum in the corresponding cylinder of loading therewith.In theory, as long as pretightening force can realize and not occur under the prerequisite of phenomenon of detonation, its value is the bigger the better.
In Fig. 1, in the length range of piston pin boss 5, because leaf spring briquetting 3 has taken certain length, make the current conventional wrist pin of Length Ratio of described wrist pin 1 short, the bearing area of wrist pin 1 reduces.Can consider piston pin boss to be designed to form short under upper length, correspondingly the microcephaly of connecting rod 6 is made to up-narrow and down-wide form, reach the object of the bearing area that increases wrist pin, also can make microcephaly's unit pressure of piston pin boss 5 and connecting rod 6 be tending towards approaching at upper and lower surface simultaneously.
As shown in Figure 2, the outside of this wrist pin 1 is fixedly equiped with a connecting rod 6, promotes piston and moves in cylinder to facilitate by this connecting rod 6.In the compression stroke stage, connecting rod is by wrist pin and leaf spring body and leaf spring briquetting promotion piston stroking upward, and in the time that cylinder pressure is greater than the pretightening force of leaf spring body, leaf spring is known from experience generation effective deformation amount and compression ratio is reduced; In the expansion stroke stage, in the time acting on gas pressure on piston and leaf spring body is compressed into produce maximum effective deformation amount △ h, wrist pin will jointly bear the gas load of piston pin boss transmission and this power will be passed to connecting rod together with leaf spring body.
The supporting surface (with the surface of contact of leaf spring briquetting 3) of this leaf spring body 2 can be that plane can be also arc surface, and the longitudinal section of leaf spring body deformability section can be that prismatic shapes can be also variable cross section shape (as trapezoidal shape or parabolic shape).The lower shape of this leaf spring body 2 is arc surfaces that radius is slightly less than wrist pin internal diameter, so that wrist pin can slowly rotate in piston pin boss.The amount of deflection of leaf spring body 2 ends is directly proportional to end load, and each physical dimension of leaf spring body 2 cooperatively interacts definite, produces corresponding effective deformation amount to meeting when the different load, makes compression ratio at ε
min～ε
maxbetween change.This leaf spring body 2 spring steel used require high degree of purity, tensile strength, limit of elasticity, fatigue strength and fatigue life, can, by adopting the technological methodes such as surface stress shot peening or finish rolling hardening processing to improve fatigue strength and the fatigue life of leaf spring body 2, make leaf spring body there is high fatigue behaviour.
The geometrical shape of these leaf spring briquetting 3 bottoms requires to match with the end geometries of leaf spring body 2, with the end of confinement plate spring body 2 in the interior rotation of leaf spring briquetting 3; And the external shape of leaf spring briquetting 3 and external geometric overall dimension require to coordinate with geometrical shape and the physical dimension in piston pin boss hole 7, the length that makes leaf spring briquetting 3 and piston pin boss hole 7 is that the straightway of the △ h confinement plate spring lock block 3 that closely cooperates rotates in piston pin boss, guarantees that leaf spring body 2 can only move up and down.
As Figure 3-Figure 4, the supporting surface of this leaf spring body 2 in this embodiment of the invention (with leaf spring briquetting 3 phase-contact surfaces) is plane, the deformation section longitudinal section of this leaf spring body 2 is variable cross section shape (parabolic shapes), and the bottom of this leaf spring body 2 is the arc surface that radius is slightly less than wrist pin internal diameter.Correspondingly, as shown in Fig. 5-Fig. 6, in one embodiment of the invention, the top shape of this leaf spring briquetting 3 is radius Rs
2be slightly less than the arc surface of piston pin boss hole 7 radiuses, the hypomere of this leaf spring briquetting 3 is that length is the straightway of △ h, and the bottom of this leaf spring briquetting 3 is the grooves that match with the section of supporting of this plate body 2.
The first half geometrical shape energy while limited piston pin 1 of this inside and outside back-up ring 4,8 and the axial float of leaf spring briquetting 3, the Lower Half geometrical shape energy while limited piston pin 1 of this inside and outside back-up ring 4,8 and the axial float of leaf spring body 2.As shown in Fig. 7-Fig. 8, the external diameter of inside and outside back-up ring 4,8 and the internal diameter in piston pin boss hole 7 of this embodiment of the invention match, and its concrete structure is the ring-type circle body of a bottom opening, and the middle part of this circle body is provided with the straightway that a length is △ h.
As shown in Figure 9, in this embodiment of the invention, the sectional shape in piston pin boss hole 7 is: centre is that length is the straightway of △ h, and two ends are respectively radius R
1the semicircle of (piston pin boss circular hole part radius).The size of △ h value has determined the lower limit ε of variable compression ratio
minwith CLV ceiling limit value ε
max.
As shown in Figure 10-Figure 11, the wrist pin 1 of this embodiment of the invention is that a wall thickness meets the cylinder that requirement of strength and length are L.The length L of this wrist pin 1 is consistent with the bottom lengths of leaf spring body 2.
When the present invention uses, as shown in Figure 12-Figure 15, piston of the present invention is installed in cylinder liner 9, and establish by cylinder head 10 envelopes at the top of this cylinder liner 9, and this cylinder head 10 is provided with intake valve 11 and exhaust valve 12.
For piston of the present invention is in cylinder bottom dead center position schematic diagram, now, piston upper space volume is cylinder operation total measurement (volume) as shown in figure 12, and piston is in compression stroke initial position, and the atmospheric pressure in cylinder is less than the pretightening force of leaf spring body.
As shown in figure 13 for piston of the present invention in the time that engine operation load is less than precompression load in top dead center position schematic diagram, now, piston upper space volume is combustion chamber volume.When engine operation is in the time being less than precompression load condition, in compression at the end, gas pressure in cylinder is less than the pretightening force of leaf spring body, now, the effective deformation amount of leaf spring body is zero, gap width between wrist pin top and top, piston pin boss hole is still △ h, and now, compression ratio is maximum value ε
max.
As shown in figure 14 for piston of the present invention engine operation during in operating mode at full capacity in top dead center position schematic diagram, now, piston upper space volume is combustion chamber volume.When engine operation is during in operating mode at full capacity, to end and when compression stroke starts, piston is in bottom dead center position in aspirating stroke, inlet and outlet door 11,12 is all closed.Now, the gas pressure in cylinder is less than the pretightening force of leaf spring body, and the effective deformation amount of leaf spring body is zero, and the gap width between wrist pin top and top, piston pin boss hole is △ h.After compression stroke starts, connecting rod 6 promotes piston stroking upward by wrist pin 1 and leaf spring body 2 and leaf spring briquetting 3, and the gas pressure in cylinder progressively increases.In the time that the gas pressure in cylinder is greater than the pretightening force of leaf spring body 2, leaf spring body 2 starts to produce effective deformation amount, and in compression stroke at the end, the effective deformation amount of leaf spring body 2 reaches △ h.Now, the gap width between wrist pin top and top, piston pin boss hole is zero, and now, compression ratio is minimum value ε
min.
When engine operation is at precompression load during to other load condition between at full capacity, in compression stroke at the end, the gap width between wrist pin top and top, piston pin boss hole is greater than zero and be less than △ h, and now, compression ratio is greater than ε
minand be less than ε
max.
Piston of the present invention as shown in figure 15 engine operation in precompression load condition (left figure) and at full capacity when operating mode (right figure) in relatively schematic diagram of top dead center position, when engine operation is during in precompression load condition, piston is in the time of top dead center position, and leaf spring body effective deformation amount is zero; When engine operation is during in operating mode at full capacity, piston is in the time of top dead center position, and leaf spring body effective deformation amount is △ h.Therefore, piston-top surface shown in left figure exceeds △ h than the piston-top surface shown in right figure, combustion chamber volume shown in the right figure of volume ratio of combustion cahmber shown in left figure is little, thereby the compression ratio that left figure is corresponding is greater than the compression ratio that right figure is corresponding, reacted the little compression ratio of engine load large, engine load greatly compression ratio is little.
Calculate about compression ratio, taking the piston pin boss hole that processes shown in Fig. 9 as example, establishing piston diameter is D, and piston stroke is S, and the combustion chamber volume of engine operation in the time being less than precompression load condition is V
c, cylinder operation total measurement (volume) is V
h,
V
h=V
c+ π D
2s/4
Engine operation is in the time of precompression load condition, and compression ratio is ε
max.
ε
max＝V
h/V
c
Engine operation, in the time of operating mode at full capacity, ends in compression stroke, and because leaf spring body effective deformation amount is △ h, combustion chamber volume increases, and is made as V '
c, now compression ratio is ε
min.
V '
c=V
c+ π D
2Δ h/4
ε
min＝V
h/V
c
Example: taking 1.6 liters of motor EA111 of golf as example, this engine piston diameter is 76.5mm, and stroke is 86.9mm, establishing the maximum effective deformation amount of leaf spring body △ h is 4mm, engine operation, in the time of precompression load condition, is got compression ratio ε
max=18, can calculate ε by above-mentioned formula
min=10.1, during with engine operation load variations, compression ratio can change between 10.1～18.
As from the foregoing, the present invention is simple in structure, there will not be and realize up to now the complicated in mechanical structure, the variable compression ratio numerical control difficulty that occur in the motor of changeable compression ratio technique scheme both at home and abroad, be difficult to the problems such as the volume and weight increase that solves dynamic balancing and make motor, the present invention adapts to reciprocating engine, particularly vehicular petrol engine and aviation piston engine.
Claims (9)
1. realize a piston structure for variable compression ratio of engines, comprise piston pin boss (5), it is characterized in that, be provided with piston pin boss hole (7) in this piston pin boss, a cartridge type wrist pin (1) is arranged in this piston pin boss hole with wholly floating; One leaf spring body (2) is arranged in this wrist pin, the two ends of this wrist pin arrange respectively inner shield ring (4), the outside of two ends inner shield ring arranges respectively leaf spring briquetting (3), the two ends of described leaf spring body (2) are held in piston pin boss hole through described leaf spring briquetting (3) with the pretightening force of setting, and make there is a gap between the top of described wrist pin (1) and the top in described piston pin boss hole
△ h; The two end plates spring lock block outside of described leaf spring body (2) is provided with outer back-up ring (8); The outside of this wrist pin is fixedly equiped with connecting rod (6); When engine operation load is less than 20%～30% at full capacity time, in the time of cylinder compression stroke terminal, this leaf spring body is only in its pre-compressed state, and its effective deformation amount is zero, and compression ratio reaches maximum value
e max; When engine operation load is at full capacity time, in the time of compression stroke terminal, this leaf spring body is compressed into the maximum effective deformation amount of generation
△ h, this wrist pin top contacts with top, piston pin boss hole, and compression ratio reaches minimum value
e min; Be 20%～30% during at full capacity to operating mode between at full capacity at engine operation load, in the time of compression stroke terminal, this leaf spring body is compressed into and produces and the corresponding effective deformation amount of load, corresponding the reducing of gap width between this wrist pin top and this top, piston pin boss hole, this leaf spring body effective deformation amount is greater than zero and be less than
△ h, corresponding compression ratio does not coexist with load
e minwith
e maxbetween change.
2. a kind of piston structure of realizing variable compression ratio of engines according to claim 1, is characterized in that, the middle part of the radial cross section in this piston pin boss hole is that length is
△ hstraightway, upper and lower two ends are that radius is
r 1semicircle.
3. a kind of piston structure of realizing variable compression ratio of engines according to claim 1, it is characterized in that, this piston structure is in the time of free state, and this wrist pin contacts with the bottom in this piston pin boss hole, the gap between this wrist pin top and this top, piston pin boss hole
△ hsize determined CLV ceiling limit value and the lower limit of variable compression ratio.
4. a kind of piston structure of realizing variable compression ratio of engines according to claim 2, is characterized in that, the supporting surface of this leaf spring body is plane or arc surface, and the longitudinal section of leaf spring body deformability section is prismatic shapes or variable cross section shape.
5. a kind of piston structure of realizing variable compression ratio of engines according to claim 2, is characterized in that, this wrist pin is drum, and the lower shape of this leaf spring body is the arc surface that radius is slightly less than wrist pin internal diameter.
6. a kind of piston structure of realizing variable compression ratio of engines according to claim 1, it is characterized in that, the geometrical shape of this leaf spring briquetting bottom requires to match with the supporting surface geometrical shape of this leaf spring body, rotates in this leaf spring briquetting with the end of limiting this leaf spring body; The external shape of this leaf spring briquetting and external geometric overall dimension require to coordinate with geometrical shape and the physical dimension in this piston pin boss hole, make the length in this leaf spring briquetting and this piston pin boss hole be
△ hthe straightway confinement plate spring lock block that closely cooperates in piston pin boss, rotate, guarantee that this leaf spring body can only move up and down.
7. a kind of piston structure of realizing variable compression ratio of engines according to claim 2, it is characterized in that, the supporting surface of this leaf spring body is plane, and deformation section longitudinal section is variable cross section shape, and the bottom of this leaf spring body is the arc surface that radius is slightly less than this wrist pin internal diameter; The top shape of this leaf spring briquetting is the arc surface that radius is slightly less than this piston pin boss pore radius, and the hypomere of this leaf spring briquetting is that length is
△ hstraightway, the bottom of this leaf spring briquetting is the groove matching with the section of supporting of this plate body.
8. a kind of piston structure of realizing variable compression ratio of engines according to claim 1, is characterized in that, the radial cross section in this piston pin boss hole is shaped as: centre is that length is
△ hstraightway, two ends are respectively radius and equal the semicircle of piston pin boss pore radius.
9. a kind of piston structure of realizing variable compression ratio of engines according to claim 1, is characterized in that, the length of this wrist pin consistent with the bottom lengths of this leaf spring body
.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410394724.9A CN104179591B (en) | 2014-08-12 | 2014-08-12 | A kind of piston structure realizing variable compression ratio of engines |
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Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105508046A (en) * | 2016-01-20 | 2016-04-20 | 吉林大学 | Piston with variable compression ratio |
| CN106996346A (en) * | 2017-01-06 | 2017-08-01 | 中国第汽车股份有限公司 | A kind of automated variable compression ratio engine piston |
| CN107201943A (en) * | 2016-03-16 | 2017-09-26 | 现代自动车株式会社 | Variable Compression Ratio Device |
| CN107620636A (en) * | 2017-10-24 | 2018-01-23 | 青岛大学 | A kind of mechanical-electric binary power 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 |
| CN112282931A (en) * | 2020-10-20 | 2021-01-29 | 苗立志 | New energy automobile engine |
| CN113396275A (en) * | 2019-02-01 | 2021-09-14 | 海德曼爱立信专利公司 | Method for providing a variable compression ratio in an internal combustion engine and device for the method |
| CN115138233A (en) * | 2022-07-07 | 2022-10-04 | 侯树壮 | Sizing material mixing and stirring mechanism and method |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6424130A (en) * | 1987-07-16 | 1989-01-26 | Nissan Motor | Compression ratio variable device for internal combustion engine |
| JPH03108833U (en) * | 1990-02-22 | 1991-11-08 | ||
| CN1516780A (en) * | 2001-06-15 | 2004-07-28 | ���＼�й�ҵ��ʽ���� | Compression ratio variable device of internal combustion engine |
| US20060243240A1 (en) * | 2003-04-12 | 2006-11-02 | Galvin George F | Piston |
| US7273022B2 (en) * | 2005-05-09 | 2007-09-25 | Francisco Azocar Valdivia | Concentric piston for variable compression ratio directly based on the combustion chamber pressure |
| CN102032054A (en) * | 2009-10-06 | 2011-04-27 | 现代自动车株式会社 | Variable compression ratio device |
| DE102010041103A1 (en) * | 2010-09-21 | 2012-03-22 | Bayerische Motoren Werke Aktiengesellschaft | Piston for lifting cylinder combustion engine, has bistable spring board formed at large extent at round face portion of piston head, where bistable spring board deforms inward to concave shape towards piston |
-
2014
- 2014-08-12 CN CN201410394724.9A patent/CN104179591B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6424130A (en) * | 1987-07-16 | 1989-01-26 | Nissan Motor | Compression ratio variable device for internal combustion engine |
| JPH03108833U (en) * | 1990-02-22 | 1991-11-08 | ||
| CN1516780A (en) * | 2001-06-15 | 2004-07-28 | ���＼�й�ҵ��ʽ���� | Compression ratio variable device of internal combustion engine |
| US20060243240A1 (en) * | 2003-04-12 | 2006-11-02 | Galvin George F | Piston |
| US7273022B2 (en) * | 2005-05-09 | 2007-09-25 | Francisco Azocar Valdivia | Concentric piston for variable compression ratio directly based on the combustion chamber pressure |
| CN102032054A (en) * | 2009-10-06 | 2011-04-27 | 现代自动车株式会社 | Variable compression ratio device |
| DE102010041103A1 (en) * | 2010-09-21 | 2012-03-22 | Bayerische Motoren Werke Aktiengesellschaft | Piston for lifting cylinder combustion engine, has bistable spring board formed at large extent at round face portion of piston head, where bistable spring board deforms inward to concave shape towards piston |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105508046A (en) * | 2016-01-20 | 2016-04-20 | 吉林大学 | Piston with variable compression ratio |
| CN107201943A (en) * | 2016-03-16 | 2017-09-26 | 现代自动车株式会社 | Variable Compression Ratio Device |
| CN107201943B (en) * | 2016-03-16 | 2020-02-11 | 现代自动车株式会社 | Variable compression ratio apparatus |
| CN106996346A (en) * | 2017-01-06 | 2017-08-01 | 中国第汽车股份有限公司 | A kind of automated variable compression ratio engine piston |
| CN106996346B (en) * | 2017-01-06 | 2020-09-18 | 中国第一汽车股份有限公司 | Automatic variable compression ratio engine piston |
| CN107620636A (en) * | 2017-10-24 | 2018-01-23 | 青岛大学 | A kind of mechanical-electric binary power engine |
| CN113396275A (en) * | 2019-02-01 | 2021-09-14 | 海德曼爱立信专利公司 | Method for providing a variable compression ratio in an internal combustion engine and device for the method |
| CN113396275B (en) * | 2019-02-01 | 2023-08-25 | 海德曼爱立信专利公司 | Method for providing variable compression ratio in internal combustion engine and device therefor |
| 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 |
| CN112282931A (en) * | 2020-10-20 | 2021-01-29 | 苗立志 | New energy automobile engine |
| CN115138233A (en) * | 2022-07-07 | 2022-10-04 | 侯树壮 | Sizing material mixing and stirring mechanism and method |
| CN115138233B (en) * | 2022-07-07 | 2023-11-10 | 江西华琪合成橡胶有限公司 | Sizing material mixing and stirring mechanism and method |
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