CN109854370A - A kind of variable compression ratio internal combustion engine - Google Patents
A kind of variable compression ratio internal combustion engine Download PDFInfo
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- CN109854370A CN109854370A CN201910179408.2A CN201910179408A CN109854370A CN 109854370 A CN109854370 A CN 109854370A CN 201910179408 A CN201910179408 A CN 201910179408A CN 109854370 A CN109854370 A CN 109854370A
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Abstract
The present invention provides a kind of variable compression ratio internal combustion engines, it changes compression ratio of internal-combustion engine by changing combustion chamber volume, has inlet valve, exhaust valve, auxiliary piston, auxiliary connecting rod, assistant cylinder, auxiliary crankshaft, the operation of auxiliary crankshaft and regulating mechanism and the other components of internal combustion engine；It assists crankshaft operation and regulating mechanism to have control motor, sprocket wheel, ring gear, capacity eccentric bearing, planetary gear and auxiliary crankshaft toothed wheel；The crankshaft and auxiliary crankshaft of the internal combustion engine are rotated with the speed ratio of 2:1 or 1:1.When assisting crankshaft operation not generate adjusting movement with regulating mechanism, compression ratio of internal-combustion engine keeps former compression ratio constant.While piston expansion work, auxiliary piston also expansion work, therefore, the internal combustion engine also can change expansion ratio.
Description
Technical field
The present invention relates to a kind of internal-combustion engine technologys more particularly to a kind of variable compression ratio and variable expansion to compare internal combustion engine.
Background technique
Variable compression ratio internal combustion engine patent is more, and practical commercial variable compression ratio internal combustion engine only has multi-connecting-rod mechanism at present
(multi-link) a kind of.
One United States Patent (USP) (patent No. 4,516,537) discloses by increasing a moveable auxiliary in a combustion chamber
Piston changes combustion chamber volume, further changes the device of compression ratio of internal-combustion engine.
Other United States Patent (USP)s 4987863,5195469,6427643,6708655,8418663,7387103 and 7856952
Deng there is similar idea.
There are many advantages of this mechanism, such as at low cost, compact-sized etc., but the disadvantage is that: no matter auxiliary piston uses
Mechanically or hydraulically it is driven to move in assistant cylinder, is all in assistant cylinder without its auxiliary piston when changing in compression ratio
Fixed, in this way when auxiliary piston and assistant cylinder periphery generate carbon distribution, which can not be removed, and carbon distribution is serious
When, auxiliary piston can also be stuck, meanwhile, auxiliary piston can not be carried out effectively cooling and lubricated, to lose compression
Than variable function.These disadvantages cause this structure to can not achieve commercialization.
Summary of the invention
What the present invention formulated regarding to the issue above, the object of the invention is to overcome the deficiencies of existing technologies, by variable
The crankshaft and auxiliary crankshaft of compression ratio internal combustion engine are with the rotation of 2:1 or 1:1 speed ratio, so that piston and auxiliary piston carry out back and forth always
Movement, and the phase change by auxiliary crankshaft relative to crankshaft are held to change the combustion chamber in internal combustion engine compression top center
Product, thus compression ratio when changing compression top center.
The technical solution of the present invention is to provide a kind of variable compression ratio internal combustion engines, including at least one inlet valve, at least
One exhaust valve, at least one piston, cylinder cap, crankshaft, it is characterised in that: further include each cylinder at least one auxiliary piston,
Assistant cylinder, auxiliary crankshaft, auxiliary Crankshaft motion and regulating mechanism, the crankshaft and the auxiliary crankshaft are always with 2:1 or 1:1
Speed ratio rotation, the piston moves back and forth in the cylinder and assistant cylinder always with the auxiliary piston；
The auxiliary Crankshaft motion and regulating mechanism are for driving the auxiliary crankshaft or being driven by the auxiliary crankshaft, institute
Rotatable phase α of the auxiliary crankshaft relative to the crankshaft can be changed by stating auxiliary Crankshaft motion and regulating mechanism, and phase α determines
Determine when the piston reaches compression top center, the position that the corresponding auxiliary piston is stopped in the assistant cylinder
It sets, the stop place of the auxiliary piston determines combustion chamber total measurement (volume) of the internal combustion engine in compression top center, thus certainly
The compression ratio of internal-combustion engine at corresponding moment is determined.
Further, the auxiliary crankshaft relative to crankshaft rotatable phase α can consecutive variations, therefore the internal combustion engine
Compression ratio also being capable of consecutive variations.
Further, when the auxiliary Crankshaft motion and regulating mechanism do not generate adjusting movement, the internal combustion engine compression
Than keeping former compression ratio constant.
Further, in the expansion stroke of internal combustion engine, while the piston expansion work, the auxiliary piston also exists
Expansion work, therefore the variable compression ratio internal combustion engine can change the expansion ratio of internal combustion engine.
Further, the internal combustion engine is 4 stroke IC engines or 2 stroke IC engines.
Further, auxiliary Crankshaft motion and regulating mechanism include a control motor and a 2K-H Planetary Gear Transmission
Mechanism, auxiliary crankshaft operation are mounted on one end of auxiliary crankshaft with regulating mechanism, drive the rotation of auxiliary crankshaft or by auxiliary crankshaft
Driving, phase α of the adjustable auxiliary crankshaft relative to crankshaft when controlling motor and being rotated with a certain speed；Assist crankshaft installed
On cylinder cap, auxiliary crankshaft rotates and auxiliary piston 7 is driven to generate reciprocating motion, and the reciprocating stroke of auxiliary piston 7 is S.
Further, adjustable range of the auxiliary crankshaft relative to crank phase α: 0 °≤α < α max, in which: α max <
180°。
Further, the auxiliary crankshaft is 0 degree relative to the phase α of the crankshaft, refers to internal combustion engine in maximum compression
Than under working condition, when the piston reaches compression top center, the auxiliary piston is also reached exactly in the compression of its own
Stop, while the piston expansion work, the auxiliary piston also expansion work.
Further, the auxiliary crankshaft is α max degree relative to the phase α of the crankshaft, refers to that internal combustion engine is pressed in minimum
Contracting is than under working condition, when the piston reaches compression top center, the auxiliary piston reaches exactly to compress with its own
Stop towards the position of direction α max degree is rotationally advancing, in the position under, while the piston expansion work, the auxiliary piston
Also expansion work.
Further, the variable compression ratio internal combustion engine includes in-line internal combustion engine, V-type internal combustion engine and W type internal combustion engine.
Further, signal panels are installed on the auxiliary crankshaft, for judging the auxiliary crankshaft relative to the song
The phase α of axis, and position of the auxiliary piston in the assistant cylinder is judged with this.
Beneficial outcomes of the invention are:
(1) auxiliary piston continuously moves back and forth the carbon distribution generation that can effectively prevent auxiliary piston and assistant cylinder periphery,
It can be removed in time by it occurring, and auxiliary piston can also be carried out effectively cooling and lubricated；Due to auxiliary piston
The expansion work in assistant cylinder, therefore, internal combustion engine actually also changes expansion ratio, increases expansion stroke, to increase
The efficiency of internal combustion engine.
(2) in the medium and small load setting operation of internal combustion engine, the raising of compression ratio can greatly improve the efficiency of internal combustion engine
(15% being usually no less than, at most up to 30% or more)；It is different from general variable compression ratio internal combustion engine, it is of the present invention variable
Compression ratio can also change expansion ratio, this has higher efficiency than the variable compression ratio internal combustion engine of immutable expansion ratio；
(3) the small load setting in middle low speed, can greatly improve the output torque of internal combustion engine, for improving vehicle
Power performance and reduction CO2 emission all have highly important meaning.
Detailed description of the invention
Fig. 1 is the axonometric drawing of the preferred embodiment of the invention；
Fig. 2 is the assistant cylinder layout drawing of the preferred embodiment of the invention；
Fig. 3 is the sectional view of the preferred embodiment of the invention；
When Fig. 4 is crankshaft and auxiliary crankshaft speed ratio is 2:1, the operation figure of piston and auxiliary piston in maximum compression ratio；
When Fig. 5 is crankshaft and auxiliary crankshaft speed ratio is 2:1, the operation figure of piston and auxiliary piston in minimum compression ratio；
Fig. 6 is auxiliary crankshaft, auxiliary piston, movement and regulating mechanism layout drawing；
Fig. 7 is the operation of auxiliary crankshaft and regulating mechanism axonometric drawing；
Fig. 8 is 2K-H planetary gear transmission mechanism sectional view；
When Fig. 9 is crankshaft and auxiliary crankshaft speed ratio is 1:1, the operation figure of piston and auxiliary piston in maximum compression ratio；
When Figure 10 is crankshaft and auxiliary crankshaft speed ratio is 1:1, the operation figure of piston and auxiliary piston in minimum compression ratio；
Figure 11 is different number auxiliary piston and different number valve plane layout drawing；
Specific embodiment
Technical solution of the present invention is described in detail below with reference to attached drawing 1-11.
As shown in Fig. 1-3 and Fig. 6, this embodiment offers a kind of variable compression ratio internal combustion engines comprising exhaust cam shaft
1, exhaust valve 2, admission cam shaft 3, inlet valve 4, auxiliary crankshaft 5, auxiliary connecting rod 6, auxiliary piston 7, assistant cylinder 11, auxiliary are bent
Axis operation and regulating mechanism 28, crankshaft 8, piston 9, cylinder 10, cylinder cap 12；
Internal combustion engine drives exhaust valve 2 and admission cam shaft 3 that inlet valve 4 is driven to take a breath by exhaust cam shaft 1, assists
Crankshaft 5 drives auxiliary connecting rod 6 that auxiliary piston 7 is driven to move back and forth, while crankshaft 8 drives piston 9 to move back and forth.
As shown in Fig. 2, exhaust valve 2 is two, inlet valve 4 is 3, and assistant cylinder 11 is 1, and wherein assistant cylinder 11 is pressed
Diagram is arranged in the middle part of cylinder 10, and exhaust valve 2 and inlet valve 4 are arranged in around assistant cylinder 11, piston 9 it is reciprocal
Movement carries out in the cylinder 10, and the reciprocating motion of auxiliary piston 7 carries out in assistant cylinder 11.
Position institute when Fig. 3 is compression ratio maximum and compression ratio minimum, between 7 two pistons of piston 9 and auxiliary piston
The case where combustion chamber volume variation of formation.
As shown in Figure 3a, auxiliary crankshaft 5 is rotated around auxiliary crankshaft center 20, and auxiliary connecting rod major part center 21 is made to reach diagram
Position, the position are that auxiliary piston 7 is back and forth run in assistant cylinder 11 to bottom and the operation of auxiliary piston 7 to it certainly
The compression top center position of body；Crankshaft 8 makes big end center 23 reach diagram position around 22 rotating Vortex of crankshaft center simultaneously
It sets, which is that piston 9 moves back and forth in the cylinder 10 to the top and piston 9 and is in compression top center position；Due to work
Plug 9 and auxiliary piston 7 are in the compression top center of their own, and the phase difference between them is 0 °, so auxiliary by this time
Crankshaft 5 is helped to be defined as 0 degree relative to the phase α of crankshaft 8.In order to describe conveniently, piston shown in Fig. 3 a is in compression only
Point, while position when auxiliary piston 7 is also at compression top center is defined as first position.I.e. at piston 9 and auxiliary piston 7
When first position, auxiliary crankshaft 5 is 0 ° relative to the phase α of crankshaft 8, at this point, by auxiliary piston 7, piston 9 and cylinder cap 12 etc.
The space of formation constitutes fixed combustion room 24, and volume is indicated with Vb.
Such as Fig. 3 b, crankshaft 5 is assisted to rotate around auxiliary crankshaft center 20, auxiliary connecting rod major part center 21 is made to reach diagram position
It sets and auxiliary piston 7 back and forth runs to the top and auxiliary piston 7 in assistant cylinder 11 and runs under its own
Dead-centre position；Crankshaft 8 makes big end center 23 reach shown position, which is around 22 rotating Vortex of crankshaft center simultaneously
Piston 9 moves back and forth in the cylinder 10 to the top and piston 9 and is in compression top center position；At this point, at due to piston 9
In compression top center, and auxiliary piston 7 is in lower dead center, and the phase difference between them is 180 °, so auxiliary crankshaft 5 at this time
Phase α relative to crankshaft 8 is 180 degree.Equally, also as shown in Figure 3b, piston 9 is in compression top center, while auxiliary piston 7
Position when in lower dead center is defined as " second position ".I.e. when piston 9 and auxiliary piston 7 are in the second position, auxiliary is bent
Axis 5 is 180 ° relative to the phase α of crankshaft 8.Movement when auxiliary piston 7 is run from the first position Fig. 3 a to the second position b Fig. 3
Stroke S is formed by space and constitutes variable combustion 25, and volume is indicated with Vv.
It can be seen from the above, Vb combustion chamber volume be forever it is immovable, after the completion of Combustion chamber design just it has been determined that
And variable combustion volume Vv can then change.
Combustion chambers of internal combustion engines total measurement (volume) Vc=Vb+Vv is defined by compression ratio of internal-combustion engine it is found that its compression ratio:
ε=(Vd+Vb+Vv)/(Vb+Vv)=Vd/ (Vb+Vv)+1,
In formula: Vd is the discharge capacity of internal combustion engine 9；Vv is variable combustion volume；Vb is fixed combustion room volume.
By above formula it is known that the change of compression ratio depends on the change of combustion chamber total measurement (volume), and combustion chamber total measurement (volume)
Change the variation for uniquely depending on variable combustion volume, the variation of variable combustion volume is again unique to depend on auxiliary crankshaft 5
The variation of phase α relative to crankshaft 8.
When to assist crankshaft 5 relative to the phase α of crankshaft 8 be 0 degree, variable combustion volume Vv is 0, and auxiliary crankshaft 5 is opposite
When the phase α of crankshaft 8 is that α max is spent, variable combustion volume Vv is Vvmax.
With auxiliary crankshaft 5 relative to crankshaft 8 phase α from 0 change to α max when, variable combustion volume Vv is then from 0
Vvmax is changed to, compression ratio is then changed to ε=Vd/ (Vb+Vvmax)+1 from ε=Vd/Vb+1.It is opposite to change auxiliary crankshaft 5
In the phase α of crankshaft 8, so that it may stop place of the auxiliary piston 7 in assistant cylinder 11 when changing compression top center, it is described to stop
It stays position to determine the size of variable combustion volume Vv, and then changes compression ratio of the internal combustion engine in compression top center.
It can be seen that it changes compression ratio of internal-combustion engine by changing combustion chamber volume, the crankshaft 8 and auxiliary of internal combustion engine are bent
Axis 5 is rotated with the speed ratio of 2:1, and piston 9 moves back and forth always with auxiliary piston 7.
When Fig. 4 shows crankshaft 8 and the speed ratio of crankshaft 5 is assisted to be 2:1, under maximum compression ratio operating condition, piston 9 and auxiliary
For piston 7 in the complete cycle of quartastroke engine, the positional relationship that they run assists crankshaft 5 relative to crankshaft at this time
Phase α be consistently equal to 0 degree it is constant.
When Fig. 4 a is that piston 9 reaches compression top center, auxiliary piston 7 also reaches its top dead centre, auxiliary connecting rod major part center
21 along the operation of its circus movement track 26 to the bottom for assisting crankshaft center 20, this position is exactly above-mentioned " first
It sets ".
Fig. 4 b is that crankshaft 8 is rotated to 180 degree, assists the position of 5 rotating Vortex of crankshaft to 90 degree, the position be piston 9 and
The position of 7 expansion work stroke of auxiliary piston finally.From the first position of Fig. 4 a, the work that internal combustion engine has started it is followed
Ring.As crankshaft 8 rotates, piston 9 starts expansion work stroke, until crankshaft 8 rotates 180 degree, completes expansion work；Meanwhile
It assists crankshaft 5 due to also starting to rotate with 8 interaction relation of crankshaft, the expansion work stroke of auxiliary piston 7 is opened, according to crankshaft
8 assist 5 expansion work of crankshaft, 90 degree of corners with the speed ratio of crankshaft 5 is assisted for the relationship of 2:1, when 9 expansion work of piston,
The also expansion work of auxiliary piston 7, expansion stroke S1.After 9 expansion work of piston to crankshaft 8 rotates 180 °, exhaust valve 2 is beaten
It opens, is prepared to enter into exhaust stroke, after the gas pressure in cylinder 10 and cylinder 11 drops to atmospheric pressure, gas cannot be after
Continuous acting.Although auxiliary piston 7 is in 90 degree of positions, as it still can continue to move towards lower dead center, this has no longer been swollen
Swollen stroke.
Fig. 4 c is that crankshaft 8 is rotated to 360 degree, according to the speed ratio relationship of 2:1 between crankshaft 8 and auxiliary crankshaft 5, assists crankshaft
5 rotating Vortexes are to 180 degree.Piston 9 reaches exhaust top dead center position at this time, and auxiliary piston 7 reaches its bottom dead center position, should
Position is the position of exhaust stroke finally.
Fig. 4 d is that crankshaft 8 is further rotated to 540 degree of positions, is closed according to the speed ratio of 2:1 between crankshaft 8 and auxiliary crankshaft 5
System, auxiliary crankshaft 5 then rotating Vortex to 270 degree of positions.Piston 9 reaches air inlet bottom dead center position at this time, and auxiliary piston 7 reaches
Its auxiliary connecting rod major part center 21 is run to 270 degree of positions, which is the position of induction stroke finally.
It is then to be compressed to the gas for entering cylinder 10 and cylinder 11 in next step, when compressing finally, that is, reaches diagram 4a
Position, so in cycles, continue engine cycle.
In figure 4 above a, 4b, 4c and 4d, working cycles situation of the internal combustion engine under maximum compression ratio operating condition, especially by force
It adjusts, at runtime, auxiliary crankshaft 5 never changes internal combustion engine relative to the phase α of crankshaft 8, and consistently equal to 0 degree.
When Fig. 5 shows crankshaft 8 and the speed ratio of crankshaft 5 is assisted to be 2:1, under minimum compression ratio operating condition, in quartastroke engine
Complete cycle in, the positional relationship that piston 9 and auxiliary piston 7 are run assists phase α of the crankshaft 5 relative to crankshaft 8 at this time
Consistently equal to α max is constant.
When Fig. 5 a is that piston 9 reaches compression top center, auxiliary piston 7 reaches auxiliary connecting rod major part center 21 along its circle
Motion profile 26 is run to the position of α max.
The α is in the position α max, is not above-mentioned " second position ".In fact, if minimum is pressed in the design
Contracting is than being set to α equal to 180 degree, and piston 9 is in compression top center position at this time, it is meant that immediately enters expansion work punching in next step
Journey, and auxiliary piston 7 is in its lower dead center at this time, next step auxiliary piston 7 will immediately enter backstroke and to its top dead centres
Direction operation, the top for making auxiliary piston 7 is encountered cylinder 10 and cylinder 11 (the two cylinders are in a communal space) by this
The huge air resistance generated when expansion work, leads to the consumption of power, and therefore, this design is worthless.
In order to avoid the generation of above situation, under minimum compression ratio operating condition, it should so that piston 9 is reached compression top center,
And be immediately ready for igniting explosion enter expansion work stroke when, auxiliary piston 7 be still within to lower dead center direction run, reserve
Auxiliary piston 7 can continue the space of expansion work.In general, inner pressure of air cylinder can steeply rise after internal-combustion engine ignition, and
And gas high pressure will maintain a period of time, this is also internal combustion engine mechanical efficiency highest a period of time.With the rotation angle of crankshaft
Measurement can generally continue 40 ° of -60 ° of crank angles after internal combustion engine compression top center, the case where for preferred embodiments, crankshaft 8
With auxiliary crankshaft 5 be 2:1 speed ratio relationship, that is to say, that auxiliary crankshaft 5 continue 20 ° -30 ° after compression top center, in order to
In this period of time, make auxiliary piston 7 continue expansion work, α max is drafted to be advisable at 135 ° or so, in this way from auxiliary piston 7 to
180 ° of the maximum position in lower dead center direction, the also space there are 45 ° or so of expansion work, that is, piston 9 have 90 ° or so
Working application time, and make auxiliary piston 7 in the acting as much as possible of highest gas pressure and the highest section of mechanical efficiency.
Certainly, will continue to do work in 9 remaining 90 ° of crank angles of piston, meanwhile, auxiliary piston 7 starts inverse gas pressure direction and consumes
Very small part function.Since in this section, gas pressure sharply declines, function and the expansion of auxiliary piston 7 of consumption are done
Function compare, mistake must be far longer than.
Fig. 5 b is 8 rotation β degree of crankshaft, and according to the speed ratio relationship of 2:1 between crankshaft 8 and auxiliary crankshaft 5, auxiliary crankshaft 5 is then
0.5 β degree of rotating Vortex, and auxiliary piston 7 is made to reach its lower dead center, which is numerically equal to 180 ° of-α max, works as piston
9 expansions, when crankshaft 8 runs the acting of the angle β, the also expansion work of auxiliary piston 7, expansion stroke S2, until its operation stops to lower
Point position.At this point, the acting of piston 9 is not yet completed, and the acting of auxiliary piston 7 is over.
Fig. 5 c is that crankshaft 8 is rotated to 180 degree, and according to the speed ratio relationship of the 2:1 between crankshaft 8 and auxiliary crankshaft 5, auxiliary is bent
Then 90 degree of rotating Vortex of axis 5, piston 9 reaches bottom dead center position at this time, and auxiliary piston 7 reaches auxiliary connecting rod major part center 21 and revolves
Go to the position of (90+ α max).The piston 9 reaches bottom dead center position, and expansion work has been completed, and auxiliary piston 7 then disappears
Very small part function is consumed.
Fig. 5 d is that crankshaft 8 is rotated to 360 degree, and according to the speed ratio relationship of the 2:1 between crankshaft 8 and auxiliary crankshaft 5, auxiliary is bent
The then rotating Vortex 180 degree of axis 5.Piston 9 reaches exhaust top dead center position at this time, and auxiliary piston 7 reaches in auxiliary connecting rod major part
The heart 21 is rotated to the position of (180+ α max).The position is the position of exhaust stroke finally.
Fig. 5 e is that crankshaft 8 is rotated to 540 degree, and according to the speed ratio relationship of the 2:1 between crankshaft 8 and auxiliary crankshaft 5, auxiliary is bent
Then 270 degree of rotating Vortex of axis 5.Piston 9 reaches air inlet bottom dead center position at this time, and auxiliary piston 7 reaches in auxiliary connecting rod major part
The rotation of the heart 21 spends position to (270+ α max).The position is the position of induction stroke finally.
It is then to be compressed to the gas for entering cylinder 10 and cylinder 11 in next step, when compressing finally, that is, reaches diagram 5a
Position, so in cycles, continue engine cycle.
In figure 5 above a, 5b, 5c, 5d and 5e, working cycles situation of the internal combustion engine under minimum compression ratio operating condition, especially
, it is emphasized that internal combustion engine is at runtime, auxiliary crankshaft 5 never changes relative to the phase α of crankshaft 8, consistently equal to α
Max degree.
As shown in fig. 6, variable compression ratio internal combustion engine includes an auxiliary crankshaft operation and regulating mechanism 28, controlled by one
Motor 27 processed and a 2K-H planetary gear transmission mechanism 30 form.The operation of auxiliary crankshaft is mounted on auxiliary song with regulating mechanism 28
One end of axis 5 drives or is rotated by driving auxiliary crankshaft 5, and adjusts phase α of the auxiliary crankshaft 5 relative to crankshaft 8；Auxiliary is bent
Axis 5 is mounted on cylinder cap 12, and the auxiliary rotation of crankshaft 5 drives auxiliary connecting rod major part 21 to rotate, and auxiliary piston 7 is made to generate reciprocal fortune
Dynamic, the reciprocating stroke of auxiliary piston 7 is S, while installing a signal panels 29 on auxiliary crankshaft 5, to confirm auxiliary
Phase of the crankshaft 5 relative to crankshaft 8.
Special emphasis is that the operation of auxiliary crankshaft and regulating mechanism 28 are not always that its operation is driven by crankshaft 8.Due to
There is no as crankshaft 8 there is huge flywheel crankshaft 8 can be needed once in a while to drive with energy reserve, therefore for auxiliary crankshaft 7
Crankshaft 7 is assisted to run.More often, due to auxiliary piston 7 in assistant cylinder 11 expansion work, at this point, auxiliary piston 7 drive
Crankshaft operation and regulating mechanism 28 are assisted, by power output to crankshaft 8.
Such as Fig. 7,2K-H planetary gear mechanism 30 include a sprocket wheel 31, ring gear 32, planetary gear 33, capacity eccentric bearing 34,
Connector 35 and auxiliary crankshaft toothed wheel 37；
When crankshaft 8 rotates, sprocket wheel 31 connected to it is driven by crankshaft sprocket and chain (not shown), and then drive
Ring gear 32 is intermeshed with the gear teeth 39 on planetary gear 33 due to the gear teeth 38 on ring gear 32, is further driven planetary gear
33 rotate, and another gear teeth 41 on planetary gear 33 intermesh with the gear teeth 40 on auxiliary crankshaft toothed wheel 37, therefore, planetary gear 33
Rotation driving auxiliary crankshaft toothed wheel 37, and drive and rotated with the auxiliary crankshaft 5 that is coaxially fixed as one of auxiliary crankshaft toothed wheel 37, it is complete
At the driving campaign of auxiliary crankshaft 5.In contrast, when assisting crankshaft 5 to rotate, crankshaft is assisted along opposite path drives
Operation and regulating mechanism 28, and by power output to crankshaft 8, auxiliary piston 7 externally does work at this time, and increases the effect of internal combustion engine
Rate.This is auxiliary crankshaft 5 and the driving of crankshaft 8 and driven movement transmittance process.
See Fig. 8, when controlling motor 27 and auxiliary crankshaft 5 is rotated with a certain speed ratio and generates adjusting movement, motor master
Axis 36 drives capacity eccentric bearing 34 to rotate, and capacity eccentric bearing 34 has the inner periphery 45 coaxial with central axis 42, the bias
Bearing 34 also has the outer cylinder surface 44 coaxial with eccentric axis 43；When capacity eccentric bearing 34 rotates, according to 2K-H planet tooth
The working principle for taking turns mechanism 30, generates two kinds of rotary motions, first is that the inner periphery 45 of capacity eccentric bearing 34 is around central axis 42
Rotary motion, the other is the outer cylinder surface 44 of capacity eccentric bearing 34 is using eccentricity E as radius, around the revolution of central axis 42
Movement；The revolution motion drives the planetary gear 33 fixed with the outer cylinder surface 44 of capacity eccentric bearing 34, revolution is also generated, due to row
The gear teeth 39 on star-wheel 33 and the gear teeth 38 on ring gear 32 are intermeshed, this kind engagement constraint make simultaneously the generation of planetary gear 33 around
The spinning motion of eccentric axis 43, the spinning motion change the rotation angle of planetary gear 33 Yu ring gear 32, this changes
The angle of change is intermeshed relationship also by the gear teeth 40 on another gear teeth 41 and auxiliary crankshaft toothed wheel 37 on planetary gear 33, band
Dynamic auxiliary crankshaft toothed wheel 37 changes rotation angle, further changes the auxiliary crankshaft 5 being fixedly connected with auxiliary crankshaft toothed wheel 37 and changes
Varied angle；Since the rotation angle of ring gear 32 is synchronous with crankshaft 8, the angle of the auxiliary crankshaft 5 is relative to ring gear 32
Change it can be appreciated that change of the auxiliary crankshaft 5 relative to the phase α of crankshaft 8, the rotation of electric machine main shaft 36 is changed into as a result,
Variation of the crankshaft 5 relative to the rotatable phase α of crankshaft 8 is assisted, and the variation of α is determined when piston 9 reaches compression top center,
Its stop place of auxiliary piston 7 in assistant cylinder 11, and the stop place of auxiliary piston 7 determines variable combustion volume
The volume size and internal combustion engine of Vv further determines internal combustion engine pressure at this very moment in the combustion chamber total measurement (volume) of compression top center
Contracting ratio.
When controlling motor 27 and auxiliary crankshaft 5 with the rotation of a certain speed ratio but not generating adjusting movement, auxiliary crankshaft 5 is opposite
Do not change in the phase of crankshaft 8, the compression ratio of variable compression ratio internal combustion engine does not also change.
Another embodiment of the invention:
Embodiment is essentially identical with preferred embodiments, and only the speed ratio relationship of crankshaft 8 and auxiliary crankshaft 5 is 1:1, in detail as schemed
The explanation of 9 and Figure 10:
When Fig. 9 shows crankshaft 8 and the speed ratio of crankshaft 5 is assisted to be 1:1, under maximum compression ratio operating condition, piston 9 and auxiliary
Running position relationship of the piston 7 in the complete cycle of quartastroke engine assists phase α of the crankshaft 5 relative to crankshaft at this time
Consistently equal to 0 is constant.
When Fig. 9 a is that piston 9 reaches compression top center, auxiliary piston 7 also reaches its top dead centre, auxiliary connecting rod major part center
21 along the operation of its circus movement track 26 to the bottom for assisting crankshaft center 20, this position is exactly above-mentioned " first
It sets ".
Fig. 9 b rotates the position to 180 degree, after assisting 5 rotating Vortex 180 degree of crankshaft for crankshaft 8, when 9 expansion work of piston
When 180 degree crank angle, the also expansion work 180 degree crank angle of auxiliary piston 7, expansion stroke S3.The position is piston 9
With the position of 7 expansion work stroke of auxiliary piston finally.
Fig. 9 c is that crankshaft 8 is rotated to 360 degree, according to the speed ratio relationship of 1:1 between crankshaft 8 and auxiliary crankshaft 5, assists crankshaft
5 360 degree of rotating Vortex.Piston 9 reaches exhaust top dead center position at this time, and auxiliary piston 7 also reaches its exhaust top dead center position
It sets.The position is the position of exhaust stroke finally.
Fig. 9 d is that crankshaft 8 is rotated to 540 degree, according to the speed ratio relationship of 1:1 between crankshaft 8 and auxiliary crankshaft 5, assists crankshaft
5 540 degree of rotating Vortex.Piston 9 reaches air inlet bottom dead center position at this time, and auxiliary piston 7 also reaches its air inlet lower dead center position
It sets.The position is the position of induction stroke finally.
It is then to be compressed to the gas for entering cylinder 11 and cylinder 10 in next step, when compressing finally, that is, reaches diagram 9a
Position, so in cycles, continue engine cycle.
In figure 9 above a, 9b, 9c and 9d, working cycles situation of the internal combustion engine under maximum compression ratio operating condition, especially by force
It adjusts, at runtime, auxiliary crankshaft 5 never changes internal combustion engine relative to the phase α of crankshaft 8, and consistently equal to 0 degree.
When Figure 10 shows crankshaft 8 and the speed ratio of crankshaft 5 is assisted to be 1:1, under minimum compression ratio operating condition, in quartastroke engine
Complete cycle in, the running position relationship of piston 9 and auxiliary piston 7 assists phase α of the crankshaft 5 relative to crankshaft 8 at this time
Consistently equal to α max is constant.
When Figure 10 a is that piston 9 reaches compression top center, auxiliary piston 7 reaches auxiliary connecting rod major part center 21 along its circle
Shape motion profile 26 is run to the position of α max.
Numerical value about α max is similar to described in Fig. 5 a.
Figure 10 b is that crankshaft 8 rotates γ degree, according to the speed ratio relationship of 1:1 between crankshaft 8 and auxiliary crankshaft 5, assists crankshaft 5
Then rotating Vortex γ degree and reach its lower dead center, when 9 expansion work of piston, the also expansion work of auxiliary piston 7, expansion stroke
For S4, until it runs to bottom dead center position.At this point, the acting of piston 9 is not yet completed, and the acting of auxiliary piston 7 is over.
Figure 10 c is that crankshaft 8 is rotated to 180 degree, and according to the speed ratio relationship of 1:1 between crankshaft 8 and auxiliary crankshaft 5, auxiliary is bent
The then rotating Vortex 180 degree of axis 5, piston 9 reaches bottom dead center position at this time, and auxiliary piston 7 reaches auxiliary connecting rod major part center 21
It rotates to the position of (180+ α max).The piston 9 reaches bottom dead center position, and expansion work has been completed, and auxiliary piston 7 is then
Consume a part of function.
Figure 10 d is that crankshaft 8 is rotated to 360 degree, and according to the speed ratio relationship of 1:1 between crankshaft 8 and auxiliary crankshaft 5, auxiliary is bent
Then 360 degree of rotating Vortex of axis 5.Piston 9 reaches exhaust top dead center position at this time, and auxiliary piston 7 reaches in auxiliary connecting rod major part
The heart 21 is rotated to the position of (360+ α max).The position is the position of exhaust stroke finally.
Figure 10 e is that crankshaft 8 is rotated to 540 degree, and according to the speed ratio relationship of 1:1 between crankshaft 8 and auxiliary crankshaft 5, auxiliary is bent
Then 540 degree of rotating Vortex of axis 5.Piston 9 reaches air inlet bottom dead center position at this time, and auxiliary piston 7 reaches in auxiliary connecting rod major part
The position that the rotation of the heart 21 is spent to (540+ α max).The position is the position of induction stroke finally.
It is then to be compressed to the gas for entering cylinder 10 and cylinder 11 in next step, when compressing finally, that is, reaches diagram 10a
Position, so in cycles, continue engine cycle.
In figure 10 above a, 10b, 10c, 10d and 10e, working cycles feelings of the internal combustion engine under minimum compression ratio operating condition
Condition, special emphasis are that at runtime, auxiliary crankshaft 5 never changes internal combustion engine relative to the phase α of crankshaft 8, always
Equal to αmaxDegree.
In Fig. 4, Fig. 5, Fig. 9 and Figure 10, the phase α for only showing auxiliary crankshaft 5 relative to crankshaft 8 is equal to 0 and α
Under the conditions of α max, running position situation of the auxiliary piston 7 in assistant cylinder 11.Since α can assist living with consecutive variations
Stop place of the plug 7 in assistant cylinder 11 is also consecutive variations, and other position situations can be by crankshaft 8 and auxiliary crankshaft
5 speed ratio relationship and the size of α, which are reasoned out, to be come, and is repeated no more.
Other embodiments of the invention are the different arrangement shapes of the auxiliary piston 7 of different number, inlet valve 4 and exhaust valve 2
Formula.
Figure 11 a is the arrangement of an exhaust valve 4, an inlet valves 2 and two auxiliary pistons 7；
Figure 11 b is the arrangement of two exhaust valves 4, two inlet valves 2 and two auxiliary pistons 7；
Figure 11 c is the arrangement of two exhaust valves 4,4 inlet valves 2 and an auxiliary piston 7；
Figure 11 d is the arrangement of two exhaust valves 4, two inlet valves 2 and an auxiliary piston 7.
Claims (11)
1. a kind of variable compression ratio internal combustion engine, including at least one inlet valve, at least one exhaust valve, at least one piston, cylinder
Lid, crankshaft, it is characterised in that: further include each cylinder at least one auxiliary piston, assistant cylinder, auxiliary crankshaft, auxiliary crankshaft
Driving and regulating mechanism, the crankshaft and the auxiliary crankshaft are rotated always with the speed ratio of 2:1 or 1:1, the piston with it is described
Auxiliary piston moves back and forth in the cylinder and assistant cylinder always；
The auxiliary Crankshaft motion and regulating mechanism are described auxiliary for driving the auxiliary crankshaft or being driven by the auxiliary crankshaft
Help Crankshaft motion and regulating mechanism that can change rotatable phase α of the auxiliary crankshaft relative to the crankshaft, phase α is determined
When the piston reaches compression top center, the position that the corresponding auxiliary piston is stopped in the assistant cylinder,
The stop place of the auxiliary piston determines combustion chamber total measurement (volume) of the internal combustion engine in compression top center, to determine
The compression ratio of internal-combustion engine at corresponding moment.
2. variable compression ratio internal combustion engine according to claim 1, it is characterised in that: the auxiliary crankshaft is relative to crankshaft
Rotatable phase α can consecutive variations, therefore the compression ratio of the internal combustion engine also being capable of consecutive variations.
3. variable compression ratio internal combustion engine according to claim 1, it is characterised in that: when the auxiliary Crankshaft motion and adjust
When mechanism does not generate adjusting movement, the compression ratio of internal-combustion engine keeps former compression ratio constant.
4. variable compression ratio internal combustion engine according to claim 1, it is characterised in that: in the expansion stroke of internal combustion engine, in institute
While stating piston expansion work, the auxiliary piston is also in expansion work, therefore the variable compression ratio internal combustion engine can change
The expansion ratio of internal combustion engine.
5. variable compression ratio internal combustion engine described in any one of -4 claims according to claim 1, it is characterised in that: described
Internal combustion engine is 4 stroke IC engines or 2 stroke IC engines.
6. variable compression ratio internal combustion engine described in any one of -4 claims according to claim 1, it is characterised in that: auxiliary
Crankshaft motion and regulating mechanism include control motor and a 2K-H planetary gear transmission mechanism, and auxiliary crankshaft is run and the machine of adjusting
Structure is mounted on one end of auxiliary crankshaft, and driving assists Qu Xuanzhuan or driven by auxiliary crankshaft, when control motor is revolved with a certain speed
When turning, phase α of the adjustable auxiliary crankshaft relative to crankshaft；Assist crankshaft installed on cylinder cap, the rotation of auxiliary crankshaft and band
Dynamic auxiliary piston 7 generates reciprocating motion, and the reciprocating stroke of auxiliary piston 7 is S.
7. variable compression ratio internal combustion engine described in any one of -4 claims according to claim 1, it is characterised in that: described
Assist adjustable range of the crankshaft relative to crank phase α: 0 °≤α < α max, in which: max < 180 ° α.
8. claim according to claim 7, it is characterised in that: phase of the auxiliary crankshaft relative to the crankshaft
α is 0 degree, refers to internal combustion engine under maximum compression ratio working condition, when the piston reaches compression top center, the auxiliary is lived
Plug also reaches exactly to the compression top center of its own, and while the piston expansion work, the auxiliary piston, which also expands, to be done
Function.
9. claim according to claim 7, it is characterised in that: phase of the auxiliary crankshaft relative to the crankshaft
α be α max degree, refer to internal combustion engine under minimum compression ratio working condition, when the piston reach compression top center when, it is described auxiliary
Help piston to reach exactly to its own compression top center towards the position of direction α max degree is rotationally advancing, in the position under, the work
While filling in expansion work, the auxiliary piston also expansion work.
10. variable compression ratio internal combustion engine described in any one of -4 claims according to claim 1, it is characterised in that: institute
Stating variable compression ratio internal combustion engine includes in-line internal combustion engine, V-type internal combustion engine and W type internal combustion engine.
11. variable compression ratio internal combustion engine described in any one of -4 claims according to claim 1, it is characterised in that: institute
It states and signal panels is installed on auxiliary crankshaft, for judging phase α of the auxiliary crankshaft relative to the crankshaft, and judged with this
Position of the auxiliary piston in the assistant cylinder.
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| CN201910179408.2A CN109854370A (en) | 2019-03-11 | 2019-03-11 | A kind of variable compression ratio internal combustion engine |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN110273749A (en) * | 2019-07-11 | 2019-09-24 | 襄阳康捷飞龙机械制造有限公司 | The engine and its mobile device and operating method of variable combustion building volume |
| CN110469379A (en) * | 2019-08-07 | 2019-11-19 | 中国北方发动机研究所(天津) | A kind of variable-geometry compression ratio device based on multistage actuated by cams |
| CN110925086A (en) * | 2019-07-11 | 2020-03-27 | 襄阳康捷飞龙机械制造有限公司 | Engine and mechanical equipment and application |
| CN111811447A (en) * | 2020-06-11 | 2020-10-23 | 广汽本田汽车有限公司 | Engine piston top dead center measuring system and method |
| CN112112733A (en) * | 2020-09-22 | 2020-12-22 | 东风汽车集团有限公司 | Valve driving structure of engine and using method thereof |
| CN113530674A (en) * | 2020-04-16 | 2021-10-22 | 通用汽车环球科技运作有限责任公司 | Engine assembly including a gearbox for varying a compression ratio of the engine assembly using a stationary actuator |
| CN114198213A (en) * | 2021-07-02 | 2022-03-18 | 卢辉 | Variable displacement and variable compression ratio engine integrated with continuously variable transmission |
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| CN112112733A (en) * | 2020-09-22 | 2020-12-22 | 东风汽车集团有限公司 | Valve driving structure of engine and using method thereof |
| CN114198213A (en) * | 2021-07-02 | 2022-03-18 | 卢辉 | Variable displacement and variable compression ratio engine integrated with continuously variable transmission |
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Application publication date: 20190607 |