CN1051356C - 8 shape rail rod series connection crankshaft reciprocating piston engine - Google Patents
8 shape rail rod series connection crankshaft reciprocating piston engine Download PDFInfo
- Publication number
- CN1051356C CN1051356C CN94106113A CN94106113A CN1051356C CN 1051356 C CN1051356 C CN 1051356C CN 94106113 A CN94106113 A CN 94106113A CN 94106113 A CN94106113 A CN 94106113A CN 1051356 C CN1051356 C CN 1051356C
- Authority
- CN
- China
- Prior art keywords
- crank
- bent axle
- speed change
- piston
- series connection
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Images
Landscapes
- Transmission Devices (AREA)
Abstract
The present invention relates to a reciprocating piston engine of a series crank shaft for a rail rod in a transverse 8 shape, which belongs to the field of an engine. The present invention comprises a cylinder body, a piston, a connection rod, an inertia wheel, a speed change crank shaft and a constant speed crank shaft, wherein the two crank shafts are connected in series through the rail connection rod in a transverse 8 shape; the wheel lines of the two crank shafts are identical, the turning directions are opposite, the rotary speed is identical, and the speeds of the rotation angles in every circle are different; the speed change crank shaft is provided with an end crank which forms a fixed included angle with the crank of the speed change crank shaft; the constant speed crank shaft is provided with the inertia wheel; the large head of the connection rod of the piston is hinged with the outer end of the crank on the speed change crank shaft; one end of the rail connection rod in a transverse 8 shape is hinged with the end crank, and the other end is hinged with the outer end of the crank of the constant speed crank shaft; the two crank shafts are also provided with stylus pin devices.
Description
The present invention relates to the reciprocating-piston engine field, particularly relate to the crank of motor, the improvement design of linkage mechanism.
Traditional conventional engine, possessed piston near last lower dead center, the advantage that movement velocity is slower, this advantage can produce bigger maximum pressure when making burning, and this also is similar in appearance to one of great advantage of the conventional engine of adiabatic reversible process.Also exist simultaneously disadvantage: leave top dead center at piston and be equivalent in later descending of 10 °～15 ° of crank angles, just significantly produced bigger acceleration, the burning that maximum pressure is occurred in one section of the quasi-adiabatic point (maximum temperature) is all carried out in being equivalent to less compression ratio.Because working medium density at this moment is little and continuation reduces in acceleration, and the pressure build-up speed of burning is more and more slower, so the heat energy of a large amount of fuel combustions can not be converted to kinetic energy, appearing at (about 20-55%) this section burning in the exhaust with the form of enthalpy is not only carrying out in big and the swept volume of a single chamber that enlarging, add the burning later of a large amount of unburned mixtures, also make casing wall pass to heat-eliminating medium and the heat that loses up to 10-35%.The heat-energy losses of the maximum in these two available engines accounts for the 50-90% (the comprehensive number of addition) that brings the engine thermal amount into fuel altogether and account for 45-75% in diesel engine in petrol engine (positive ignition), account for 30-58% in the high pressure-charging complex machine.
In the prior art, as application number be: 90103837.7, name is called " novel crank one linkage mechanism of reciprocating engine ", employing adds intermediate connecting rod further slows down near the movement velocity of piston top dead center by a small margin, can partly solve the problem of deficiency period of combustion, but the unallowed mistake of growth rate that must be under pressure limits (mechanical shock and pinking) suddenly.Thisly make piston speed motion with slow excessively (or be similar to do not move) in the scope of too small lever ratio, be impossible have bigger transfer capability, more crucial is that piston quickens to exercise down the problem that working medium density reduces significantly when can't resolve the fuel combustion maximum pressure and occurring.(before the quasi-adiabatic point) has a large amount of heat energy in the same old way and can not be converted to kinetic energy before fuel combustion finishes substantially.Its main cause is: the rule that the variable motion rule of piston and firing pressure increase does not match.This situation (be among Fig. 1 between the Pm-Tm) in the conventional engines indicator diagram between pressure and temperature curve and two the peak maximum values all obviously presents at a distance of (see figure 1) too far away.
In tradition and available engine, pistons reciprocating is limiting the optimization of gas exchange process with respect to the symplex structure of crank angle in addition, the fluid properties reduction when making high rotating speed, and the loss of compression stroke (unwanted overlong time) is also bigger.
The object of the invention provides a kind of 8 shape rail rod series connection crankshaft reciprocating piston engine, by improvement design to the connecting rod of known engine, to change piston motion rule in the known technology, produce bigger pressure when making fuel combustion and make cylinder interior pressure Changing Pattern and temperature changing regularity relative as much as possible identical, the object of the invention essence is to make every effort to change the piston of conventional engines with the antitropic Changing Pattern of crank angle displacement diagram from the connecting rod utilization furtherly, and realize that weekly phase inner carrier motion is descending slow, up fast asymmetrical Changing Pattern, and when descent of piston, be equivalent to the most favourable interval behind 10 ° of the crank angles apart from top dead center, piston has the downstream rate that is reducing, to prolong the fuel combustion time significantly, when making full combustion of fuel, guarantee that piston is long-time relatively, big pressure, big density working medium, finish the burning expansion working procedure under the operating mode of big compression ratio, under favourable situation, realize as much as possible changing fuel chemical energy into mechanical kinetic energy, to improve the useful horsepower of motor.
The technological scheme that adopts that achieves the above object is: this 8 shape rail rod series connection crankshaft reciprocating piston engine, include cylinder body, piston, connecting rod, bent axle, flying wheel, its spy is characterised in that: the wheel line that this motor has by the 8 rail link serial connection equates, switched in opposite, rotating speed equate, the unequal speed change bent axle of inside lock speed and at the uniform velocity two bent axles of bent axle weekly, wherein have with the coaxial setting of speed change crankshaft crank on the speed change bent axle and be formed with the end crank structure of fixed angle with it, at the uniform velocity bent axle is provided with flying wheel; The crank throw outer end is hinged on said piston rod major part and the speed change bent axle, and the end crank of 8 rail link one end and speed change bent axle is hinged, other holds and at the uniform velocity the crankshaft crank outer end is hinged; Also be provided with the stylus pin device on two bent axles.
Fig. 1 is under the normal combustion situation, the indicator diagram of pressure and temperature in the traditional and existing controlled-ignition engine cylinder.
Fig. 2 is the crank of 8 shape rail rod series connection crankshaft reciprocating piston engine of the present invention, the aufbauprinciple floor map of linkage mechanism.
Fig. 3 is the aufbauprinciple schematic representation of straight arrangement double-cylinder formula crank-connecting rod mechanism for engine of the present invention.
Fig. 4 is the aufbauprinciple schematic representation of in-line four cylinder formula crank-connecting rod mechanism for engine of the present invention.
Fig. 5 is the aufbauprinciple schematic representation of parallel four cylinder type engine connecting rods arranged side by side of the present invention.
Fig. 6 is dovetail type piston rod of the present invention and the crank-connecting rod mechanism for engine aufbauprinciple schematic representation of 8 rail link in same plane.
Fig. 7 is a piston displacement curve synoptic diagram of the present invention.
Fig. 8 is equivalent to the at the uniform velocity valve timing diagram of crank angle among the present invention.
Fig. 9 be in piston displacement curve of the present invention and the prior art piston displacement curve ratio than schematic representation.
The embodiment who provides below in conjunction with accompanying drawing further describes the present invention.As Fig. 2, shown in Figure 3, crank-connecting rod mechanism for engine of the present invention includes cylinder body (1), piston (2), connecting rod (3), speed change bent axle (4), speed change crankshaft crank (5), end crank (6), at the uniform velocity bent axle (7), at the uniform velocity crankshaft crank (8), 8 rail link (9), flying wheel (10), stylus pin device (11), (12).Wherein connecting rod (3) major part and crank throw (5) outer end are hinged; 8 rail link (9) one ends and end crank (6) are hinged, and other holds, and at the uniform velocity crankshaft crank (8) is hinged.And end crank (6) is with the coaxial setting of speed change crankshaft crank (5) and be formed with several angle (α), and this angle can be selected promptly in 0 °≤α≤360 ° selected in circumference.Present embodiment is selected 45 for use.At the uniform velocity on the bent axle (7) flying wheel (10) is being set.As shown in Figure 1 and Figure 2, because 8 rail link (9) is connected in series two bent axles, 8 rail link (9), end crank (6) at the uniform velocity crankshaft crank (8) constitutes quadratic crank mechanism, and the length of the 8 rail link in the quadratic crank mechanism of the present invention (9) must be greater than the length of end crank, and with two bent axles between distance equate that and when two crankshaft crank radiuses were equal, the motion of center of mass track of 8 rail link (9) was a ∞ shape track.Because of at the uniform velocity being provided with flying wheel (10) on the bent axle (7), pretend the at the uniform velocity bent axle (7) for power output shaft, be uniform rotation when engine operation, speed change bent axle (4) is that speed change is rotated relative to bent axle at the uniform velocity then, formed two and equated wheel line bent axle switched in opposite, rotating speed equates.But the different kinetic characteristic of Nei tarnsition velocity weekly, thereby cause the speed change of speed change bent axle to rotate and make hinged with it piston (2) produce descending slow, up fast speed change straight reciprocating motion, realize purpose of the present invention.Above said stylus pin device mean and on two bent axles, install stylus pin (11) (12) respectively that being that the quadratic crank mechanism general construction is no longer superfluous states.
Similar no longer superfluous the stating of in-line four cylinder 8 shape rail rod series connection crankshaft reciprocating piston engine shown in Figure 4 and two cylinder working principle shown in Figure 3.Four cylinder type engine connecting rods parallel arranged side by side that Fig. 5 provides and similar no longer superfluous the stating of two cylinder working principle shown in Figure 3.The four cylinder type engine connecting rods and shown in Figure 3 parallel arranged side by side that Fig. 5 provides, working principle roughly the same, no longer superfluous stating.
Dovetail type piston rod shown in Figure 6 and 8 rail link are at conplane motor, and its structural feature is: speed change crankshaft crank and the bent end of end fixed angle α=0, in fact the two is combined into a crank throw, is applicable to single cylinder, the usefulness of little stroke engine.
By technique scheme and embodiment as seen, motor of the present invention is owing to adopted 8 shape rail rod series connection crankshaft structural type, utilize ∞ rail connecting rod the quadratic crank mechanism characteristic changing conventional piston to-and-fro motion rule and produce following technical characterstic, at the 8 rail link between two bent axles with at the uniform velocity on the bent axle under the acting in conjunction of flying wheel, make the rotational velocity of speed change bent axle that cyclically-varying take place, under the acting in conjunction of fixed angle between the end crank of the crank throw on the speed change bent axle and coaxial setting, piston has been produced with respect to every stroke is needed along the straight reciprocating motion of casing wall more is tending towards the desirable speed that is changing, be in particular in:
1, up fast, descending slow (speed ratio of quickreturn characteristics can be adjusted selection);
2, leaving about 10 ° of angles of top dead center, the downstream rate of piston reduces; Particularly reduce to LAP inner carrier downstream rate between the quasi-adiabatic point in the maximal pressure force.
3, the distance of leaving top dead center at whole combustion duration (about 80 ° of crank angles) piston only accounts for whole stroke 10%, and working medium is keeping greater density always around here.
From Fig. 7 provide when two crank wheel lines are tangent, be equivalent at the uniform velocity the relative crank angle of piston (Φ) displacement diagram of bent axle and can clearly find out above three technical characterstics of the present invention.The descent of piston process is finished in 0-257 ° of angle greatly at crank angle at the uniform velocity as seen from Figure 7, and is promptly so-called descending slow; Uply then in about 257 ° of-360 ° of corners, finish, promptly so-called up fast, have quickreturn characteristics.As seen from Figure 7, the piston displacement curve is an asymmetrical curve, and descent of piston has in the best interval concerning work done and reduces the downstream rate characteristic, and this point is crank-connecting rod mechanism for engine of the present invention and traditional difference the most essential with known mechanism.
Because crank-connecting rod mechanism for engine of the present invention has 3 technical characterstics as mentioned above, motor of the present invention in view of the above has good effect as described below:
1, under the situation of pressure build-up rate normal (filling the ignition advance angle θ in the scope of being permitted), can produce higher pressure maximum, the endurance also prolongs significantly.
2, because given enough period of combustion and bigger working medium density, most of heat energy of fuel all changes pressure into and acts on piston-top surface, moves behind the falloff curve and near temperature curve, makes it identical relatively, and the enthalpy in the exhaust is reduced significantly.
3, since all burning all finish during apart from the position of top dead center at piston, therefore reduced the heat of passing to heat-eliminating medium effectively.
4, because the quickreturn characteristics of reciprocating motion of the pistons: descending slow, period of intake is prolonged, improve effective charge of motor and charging efficiency; Up fast, just strengthened the flow-disturbing effect in the gas exchange process, the time of compression stroke is shortened, rush down to leak and reduce, compress at the end that the loss of gas parameter reduces, starting is more prone to.And can use the bigger weak mixture of excess air coefficient.Referring to Fig. 8, among Fig. 8
-air inlet,
-compression,
-work,
-exhaust, as seen from Figure 8, piston is a non-symmetry structure with respect to crank angle among the present invention, does not reduce fluid properties in the time of can being implemented in high rotating speed, the loss of compression stroke (unwanted overlong time) is also less.
5, because above-mentioned composite factor improves the adaptive coefficient of this motor, can under unstable operating mode, have the speed range and the comparatively ideal acceleration of broad.
6, because the raising of above-mentioned composite factor makes this motor on the basis with low speed large torque, Max. torque occurs in the time of can being extended to higher revolution.Thereby can improve useful horsepower greatly.
7, owing to prolong the raising of degree fully that makes burning period of combustion, the noise of exhaust can reduce, and temperature and toxic component all can obviously reduce.
8, since the average gas density of burning overall process than big 4 times (5: 1) of existing vaporizer positive ignition formula big 2 times (3: 1) than existing turbosupercharging complex machine, by calculating, the thermal efficiency can reach 85%, deduction is because after mechanical efficiency reduced the enthalpy increase rub negative work and exhaust and the heat that heat-eliminating medium spreads out of, useful horsepower can be brought up to fuel and bring about 65% of motor total amount of heat into.Though complete machine need increase a ∞ rail connecting rod of a bent axle and per two cylinders, for the specific power that increases substantially, the oeverall quality of motor reduces about 1/3 than original; Fuel consumption rate reduces about 3/5 than original motor.
Referring to piston displacement curve of the present invention and tradition, existing crank-connecting rod mechanism for engine piston displacement curve that Fig. 8 provides, comparison diagram more can be known statement structural feature of the present invention and technique effect.Curve 1 is a conventional engines piston displacement curve among Fig. 8, by curve 1 as can be seen, and near to the very important top dead center that burns, piston has bigger movement velocity, corresponding crank angle Φ, it has big displacement, and near lower dead center, piston has lower movement velocity, corresponding identical crank angle Φ, it has less displacement, its defective is that near top dead center, the active combustion time is short, burning has little time fully to carry out, thereby output work is less in each circulation.For defective 90103837.7 Chinese invention patents that overcome curve 1 improve the traditional crank linkage mechanism, promptly between former piston rod and bent axle, set up intermediate connecting rod, piston displacement curve after the improvement is shown in curve 2, this structure curve is to have reduced the movement velocity of descent of piston near top dead center than the conventional construction difference, prolonged the fuel combustion time, but the problem that this structure exists is:
1, because of descent of piston is to carry out between 0-180 ° at crank angle still, because symplex structure limits, still prolongation period of combustion that can not be fully effective and favourable;
2, as can be seen by curve 2, descent of piston is after being equivalent to about 15 ° of crank angle, promptly descending with bigger acceleration, thereby do not solve piston and cross atdc, the problem that do not match to pressure rate of rise that is reducing between standard is filled up a little extremely and the descent of piston speed that is strengthening appears in maximum pressure.
3, because the piston displacement curve is symmetrical, scavenging efficiency still reduces when high rotating speed significantly.
In Fig. 9, curve 3 of the present invention can fundamentally solve tradition and problems of the prior art because of its non-symmetry structure.
Technological scheme of the present invention is applicable to stroke piston combustion engine (containing petrol engine, diesel engine), the external-combustion engine of various different cylinder numbers, different stroke, different fuel, fields such as steam engine, press machine, pump.
Claims (4)
1,8 shape rail rod series connection crankshaft reciprocating piston engine, include cylinder body, piston, connecting rod, bent axle, flying wheel, it is characterized in that: this motor has that wheel line by 8 rail link serial connection equates, switched in opposite, rotating speed equate, the unequal speed change bent axle of inside lock speed and two bent axles of bent axle at the uniform velocity weekly, wherein have with the coaxial setting of speed change crankshaft crank on the speed change bent axle and be formed with the end crank structure of fixed angle with it, at the uniform velocity bent axle is provided with flying wheel; The crank throw outer end is hinged on said piston rod major part and the speed change bent axle, and it is hinged that the end crank of 8 rail link one end and speed change bent axle is hinged, end and bent axle at the uniform velocity turn the outer end in addition; Also be provided with the stylus pin device on two bent axles.
2,8 shape rail rod series connection crankshaft reciprocating piston engine according to claim 1 is characterized in that: at the fixed angle that forms between crank throw on the speed change bent axle and the end crank in ° scope of 0 °≤α≤360.
3,8 shape rail rod series connection crankshaft reciprocating piston engine according to claim 1 is characterized in that: the length of said 8 rail link must greater than the length of end crank and with two bent axles between distance equate.
4,8 shape rail rod series connection crankshaft reciprocating piston engine according to claim 1 is characterized in that: said on the speed change bent axle crank throw and coaxial end crank setting at grade.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN94106113A CN1051356C (en) | 1994-05-25 | 1994-05-25 | 8 shape rail rod series connection crankshaft reciprocating piston engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN94106113A CN1051356C (en) | 1994-05-25 | 1994-05-25 | 8 shape rail rod series connection crankshaft reciprocating piston engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1113999A CN1113999A (en) | 1995-12-27 |
| CN1051356C true CN1051356C (en) | 2000-04-12 |
Family
ID=5032399
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN94106113A Expired - Fee Related CN1051356C (en) | 1994-05-25 | 1994-05-25 | 8 shape rail rod series connection crankshaft reciprocating piston engine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1051356C (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100445532C (en) * | 2006-05-18 | 2008-12-24 | 刘清昌 | Combined crankshaft internal combustion engine |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2315114A (en) * | 1936-06-01 | 1943-03-30 | F S K Mfg Company Inc | Diesel engine |
| US2380778A (en) * | 1944-03-13 | 1945-07-31 | Jesse M Murdock | Internal-combustion engine |
| US4437438A (en) * | 1980-08-13 | 1984-03-20 | Gerhard Mederer | Reciprocating piston engine |
| CN1046785A (en) * | 1990-05-31 | 1990-11-07 | 毛羽 | The novel crank-link mechanism of reciprocating engine |
-
1994
- 1994-05-25 CN CN94106113A patent/CN1051356C/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2315114A (en) * | 1936-06-01 | 1943-03-30 | F S K Mfg Company Inc | Diesel engine |
| US2380778A (en) * | 1944-03-13 | 1945-07-31 | Jesse M Murdock | Internal-combustion engine |
| US4437438A (en) * | 1980-08-13 | 1984-03-20 | Gerhard Mederer | Reciprocating piston engine |
| CN1046785A (en) * | 1990-05-31 | 1990-11-07 | 毛羽 | The novel crank-link mechanism of reciprocating engine |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100445532C (en) * | 2006-05-18 | 2008-12-24 | 刘清昌 | Combined crankshaft internal combustion engine |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1113999A (en) | 1995-12-27 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN106224093B (en) | A kind of hydraulic speed control formula variable compression ratio engine | |
| CN106812603A (en) | A kind of pancake engine | |
| CN2313052Y (en) | Dual-rotating non-linear drive piston-type internal combustion engine | |
| CN1873197A (en) | Revolving internal-combustion engine | |
| CN206111338U (en) | Vary voltage scaling's wankel engine | |
| CN101666267A (en) | Combustion engine | |
| CN1051356C (en) | 8 shape rail rod series connection crankshaft reciprocating piston engine | |
| CN1054292A (en) | Rotary-piston internal combustion engine with compressed-air burning in different cylinders | |
| CA2294375C (en) | Engine | |
| EP2449223A1 (en) | Internal combustion engine with separate combustion chamber and a method to achieve modified and controlled autoignition in said chamber | |
| US11274552B2 (en) | Engine crank and connecting rod mechanism | |
| CN201531309U (en) | Internal combustion engine | |
| CN209228457U (en) | A kind of opposed single direction rotation engine of four strokes, four cylinder | |
| CN1103403C (en) | Rolling-rotor engine with unequal volume ratio | |
| CN1038355C (en) | Internal combustion engine with axial rotating intake and exhaust valves | |
| CN1093143A (en) | Straight shaft engine | |
| CN2198392Y (en) | Multiple crankshaft in the same cavity engine | |
| CN2181572Y (en) | Straight shaft engine | |
| CN2050078U (en) | Cam mechanism transmission internal-combustion engine | |
| CN2336097Y (en) | oscillating piston engine | |
| CN2316465Y (en) | Gasoline engine for minicar | |
| CN1047364A (en) | Reciprocating internal combustion engine with dual pistons | |
| JPS6232331B2 (en) | ||
| CN2665375Y (en) | Engine | |
| RU2126091C1 (en) | Four-stroke internal combustion engine with auxiliary cylinder |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |