CN102400785A - Linear motion guide rail engine - Google Patents
Linear motion guide rail engine Download PDFInfo
- Publication number
- CN102400785A CN102400785A CN2010102900942A CN201010290094A CN102400785A CN 102400785 A CN102400785 A CN 102400785A CN 2010102900942 A CN2010102900942 A CN 2010102900942A CN 201010290094 A CN201010290094 A CN 201010290094A CN 102400785 A CN102400785 A CN 102400785A
- Authority
- CN
- China
- Prior art keywords
- guide rail
- piston
- engine
- linear motion
- motion guide
- 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.)
- Pending
Links
Images
Landscapes
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
The invention relates to a linear motion guide rail engine; a piston is fixed by a linear motion guide rail device and makes reciprocating linear motion on the basis of reserving the whole structural form of the original engine, the structure of the piston is improved, the height of a cylinder is reduced, and the stroke of the piston is increased, so that the output power of the engine is improved, and the power performance, the economic performance and the emission performance of the engine can be improved; and therefore, the linear motion guide rail engine which is low in consumption and high in power can be provided for the technical field of the engine.
Description
Technical field
The present invention relates to a kind of reciprocating-piston engine, especially linear motion guide rail is applied among the motor, the fixed piston linear reciprocating motion increases piston stroke, increases the linear motion guide rail engine that moment increases power.
Background technique
Original vapour, DENG generally are made up of a body (body group), two mechanisms (connecting rod, distribution device), five big systems (fuel oil supply system, ignition system, cooling system, lubrication system and start-up system).Connecting rod is made up of piston rod group, crankshaft-flywheel group, is that reciprocating-piston engine is the principal organ of mechanical energy with thermal power transfer.In the course of the work, combustion-gas pressure acts directly on the piston, promotes piston linear reciprocating motion, through wrist pin, connecting rod and bent axle, changes the linear reciprocating motion of piston into bent axle rotatablely move.Select from Chemical Industry Press and publish, Wu Wenlin chief editor's " diagram automobile engine construction handbook.Can know from
formula; The size of engine power (P) depends on the size of torque (Me) and rotating speed (n); According to torque, moment of torsion, moment definition; The moment of increase by 10% is exactly to increase by 10% power, increases by 20% moment, increases by 20% power exactly.Can know to the resultant moment of force theorem of axle to square M (the F)=Fxyxd formula and the power of axle that from power the size of engine moment depends on the length dimension and the size that acts on (Fxy) on the crank arm of crank arm.Keep (Fxy) constant, the crank arm length dimension increases by 20% on the basis of former engine crankshaft arm, increase by 20% moment exactly, increases by 20% power.The emphasis of original engine technology research all is placed on and how has improved on the combustion-gas pressure.But unilaterally only do not increase the crank arm length dimension, increase the achievement in research that piston stroke increases moment, increases power.And this is to make full use of the optimal path that original engine technology achievement is improved engine power performance, economic performance, emission performance the most directly, most effectively on the one hand.In case breaking through is exactly the great innovation of technical field of engines.Yet original engine technology is from ceiling structure system and restricted only one-sided research and development that increase crank arm length dimension, increase moment, increase power, mainly has following problem:
1, the restriction of cylinder diameter: original engine structure increases piston stroke just must increase cylinder diameter simultaneously.Increase piston stroke exactly because increase the crank arm length dimension.Increased piston stroke, cylinder height increases thereupon, does not come broadening connecting rod amplitude of oscillation space if do not increase cylinder diameter simultaneously, and connecting rod one motion will block cylinder.
2, piston, piston ring are because of the restriction of frictional loss between side pressure and the cylinder wall.Publish by National Defense Industry Press; " motor car engine principle and automobile theory " book of Yan Dajian chief editor is pointed out: " frictional loss accounts for the 60%-75% of all mechanical losses, and the frictional loss between piston, piston ring and the cylinder wall accounts for the 70%-80% of total friction head, therefore; when coming the reinforcing stimulus power character through the raising rotating speed; reduce the moving TAS true airspeed of piston as far as possible, and is to reduce the frictional loss between piston, piston ring and the cylinder, significant to improving mechanical efficiency.Improve engine speed, do not make the piston motion speed too high again, then should reduce piston stroke as far as possible." this explains that the frictional loss between original engine piston, piston ring and the cylinder wall has restricted the only one-sided research and development that increase crank arm length dimension, increase piston stroke, increase moment, increase power.And the reason that frictional loss produces is: former piston skirt play the guiding role in cylinder; Piston ring plays sealing and knife-type oil stripping action in cylinder; Must contact with cylinder wall in the work and produce sliding friction,, can not account for the 70-80% of total friction head if be this sliding friction loss.Main cause is that piston diameter is less than cylinder diameter; Piston pin boss hole center-biased centre line; And become revolute pair with the connecting rod small end hinge; So must produce side pressure when bearing combustion-gas pressure, the same side pressure that produces of the amplitude of oscillation motion of connecting rod is exactly that these side pressure have increased the frictional loss between piston, piston ring and the cylinder wall.
Summary of the invention
It is little to the purpose of this invention is to provide a kind of cylinder diameter, and the fixed piston linear reciprocating motion can increase the crank arm length dimension by a relatively large margin, increases piston stroke, increases the linear motion guide rail engine that moment increases engine power.
Be on the basis that keeps former engine body group, connecting rod, distribution device, fuel oil supply system, lubrication system, cooling system, ignition system, start-up system overall structure form; The technical solution adopted for the present invention to solve the technical problems is: on cylinder block crankcase one side inwall, be equipped with guide rail; Slide block cooperates with guide rail and does straight line motion along guide rail; One end and the slide block of piston groove timbering are fixed, and the other end of piston groove timbering is a piston crown, have fixed piston crown thus and in cylinder, have done linear reciprocating motion; Cancel former piston skirt structure; Thereby reduce former piston skirt shared cylinder height in cylinder, correspondingly increase the crank arm length dimension, increase piston stroke and realize above-mentioned purpose.
Cylinder height physical dimension of the present invention is by piston crown structure height size and piston stroke size composition, reduced cylinder height, increased the height space dimensional structure of connecting rod amplitude of oscillation width and cylinder block crankcase.
Linear motion guide rail assembling of the present invention connects and working principle is: the rail pair cylinder center in the linear motion guide rail; Vertical mount is on cylinder block crankcase one side inwall; Slide block in the linear motion guide rail is connected with an end of piston groove timbering, and the other end is a piston crown.In the working procedure; Combustion-gas pressure acts on the piston head; Promote the piston groove timbering on the one hand and on guide rail, move, at the linear reciprocating motion of linear reciprocating motion fixed piston head in cylinder on the guide rail, eliminate the side pressure of piston crown countercylinder with slide block at motion drive slide block between the crankshaft counter balance; On the other hand; Combustion-gas pressure acts on the piston head, promotes through piston pin boss that motion promotes bent axle between the groove crack of connecting rod at the piston groove timbering, changes the linear reciprocating motion of piston into bent axle rotatablely move.
Design of structural size of the present invention is confirmed mode:
1, the physical dimension of the linear motion guide rail among the present invention, body group, connecting rod, distribution device, the technical parameter that designs with linear motion guide rail engine of the present invention designs and makes.
2, the physical dimension of the fuel oil supply system among the present invention, lubrication system, cooling system, ignition system, start-up system and assembling layout are adjusted, design, are made and assemble with technical parameter, the physical dimension of linear motion guide rail engine of the present invention.
Compared with present technology, the present invention has advantage:
1, can reduce frictional loss significantly.Assembling applicable line motion guide rail is transferred to the sliding friction of former piston in cylinder on the linear motion guide rail of cylinder block crankcase, and lubrication effect is superior to the rugged environment in the cylinder; Main is to have eliminated the frictional loss of former piston skirt in cylinder; Eliminated the frictional loss that former piston, piston ring increase because of side pressure countercylinder wall.If the use rolling linear guide, the frictional loss meeting is lower.Because the rolling linear guide friction factor has only 0.003-0.005, be the 1/20-1/50 of sliding friction.
2, structure innovation.The present invention assembles the applicable line motion guide rail and has fixed the linear reciprocating motion of piston in cylinder, cancelled former piston skirt structure after, reduced cylinder height, broadening connecting rod amplitude of oscillation space, increased cylinder block crankcase height space.The technical characteristics of this structure innovation, having broken through former motor can not unilaterally increase the crank arm length dimension, increases piston stroke, increases the structural limitations of moment.And crank arm length dimension value added can increase by 10%, 20%, 30% on former engine crankshaft arm basis ... As long as not blocking cylinder, crankshaft counter balance during the maximum amplitude of oscillation of connecting rod, not bump cylinder just passable.Reach and increase considerably moment, increase power, the purpose of realization energy-saving and emission-reduction.
3, have more practicability.Structure innovation of the present invention.Can unilaterally only increase the crank arm length dimension, just can be according to the different usage requirements of motor, production is researched and developed in use occasion, makes engine application have more practicability:
(1) reduce cylinder diameter, keep former engine displacement, compression ratio is constant; It is constant to make every effort to combustion-gas pressure; Between the maximum amplitude of oscillation of former engine crankshaft arm to connecting rod, select crank arm length dimension value added, increase moment; Increase power, and each different crank arm length value added is exactly the motor of different moments, power, height.Reach with little cylinder diameter, little discharge capacity, big stroke, powerful structure and technical parameter research and development production energy-saving and emission-reduction h type engine h.
(2) it is constant to keep former engine cylinder diameter, only unilaterally on the basis of former engine crankshaft arm, increases length dimension, the maximum value when being increased to connecting rod always and not blocking cylinder.Like this, the crank arm length dimension increases, and piston stroke, cylinder volume, discharge capacity all increase thereupon; The arm of force and combustion-gas pressure are increased simultaneously; Just can research and develop and produce two kinds of different fuels, and moment, all maximized new work engine of power: petrol engine, compression ratio is between 6-12; When the crank arm length dimension increases; Piston stroke increases, and cylinder volume increases, and just can produce the petrol engine of moment, maximizes power when the adjustment combustion chamber volume makes compression ratio reach between the 10-12; The DENG compression ratio is increased to maximum value, adjustment combustion chamber volume to the crank arm length dimension between 14-22, make compression ratio be controlled at the novel diesel motor that just can produce moment, maximizes power between the 20-22.Increasing the just necessary structure that increases cylinder diameter of piston stroke with former motor compares; Cylinder diameter of the present invention does not change; Discharge capacity is lower than former motor, and the crank arm size then has been increased to maximum value, is still little cylinder diameter, little discharge capacity, big stroke, powerful energy-saving and emission-reduction h type engine h.
Description of drawings
Below in conjunction with accompanying drawing and embodiment the present invention is further specified.
Fig. 1 is a linear motion guide rail engine cylinder block connecting rod structural representation of the present invention.
Fig. 2 is a linear motion guide rail engine piston structure schematic representation of the present invention.
Fig. 3 is the A-A sectional view of linear motion guide rail engine piston of the present invention.
Among the figure: 1, guide rail; 2, slide block; 3, piston groove timbering; 4, piston crown; 5, piston head; 6, piston pin boss; 7, connecting rod; 8, crank arm; 9, bent axle; 10, crankshaft counter balance.
The practical implementation method
Like Fig. 1, Fig. 2, shown in Figure 3; On cylinder block crankcase one side inwall, be equipped with guide rail (1), slide block (2) cooperates with guide rail (1) and along doing straight line motion on the guide rail, an end of piston groove timbering (3) and slide block (2) are fixing; The other end of piston groove timbering (3) is piston crown (4); Fix piston crown (4) thus and in cylinder, done linear reciprocating motion, cancelled former piston skirt structure, thereby reduced former piston skirt shared cylinder height in cylinder; Correspondingly increase the crank arm length dimension, increase piston stroke.
Linear motion guide rail assembling of the present invention connects and working principle is: the guide rail in the linear motion guide rail (1) centering cylinder center; Vertical mount is on cylinder block crankcase one side inwall; Slide block in the linear motion guide rail (2) is connected with an end of piston groove timbering (3), and the other end is a piston.In the working procedure; Combustion-gas pressure acts on the piston head (5); Promote piston groove timbering (3) on the one hand and between crankshaft counter balance (10), move drive slide block (2),, eliminate the side pressure of piston crown (4) countercylinder with the linear reciprocating motion of linear reciprocating motion fixed piston head (4) in cylinder of slide block (2) on guide rail (1) in upward motion of guide rail (1); On the other hand; Combustion-gas pressure acts on the piston head (5), promotes connecting rod (7) the promotion crank arm (8) that between the groove crack of piston groove timbering (3), move through piston pin boss (6), changes the linear reciprocating motion of piston into bent axle (9) rotatablely move.
Embodiment one
Structure, Placement, design of structural size are confirmed described in mode such as the summary of the invention.Just cylinder block is in-line arrangement 4 cylinders, cylinder diameter 74mm, and linear motion guide rail is that linear rolling guide, the crank arm length dimension piston stroke in the rolling linear guide increases by 10% on former engine crankshaft arm lengths size, piston stroke basis.
Embodiment two
Structure, Placement, design of structural size confirm that mode is identical with example one; Difference is that cylinder block is V-type 6 cylinders; Cylinder diameter 74mm; Linear motion guide rail is the rolling spline pair in the rolling linear guide, and crank arm length dimension, piston stroke increase by 20% on the basis of former engine crankshaft arm lengths size, piston stroke.
Embodiment three
Structure, Placement, design of structural size confirm that mode is identical with embodiment one, and difference is that linear motion guide rail is the linear rail in the slide guide.Crank arm length dimension, piston stroke increase by 30% on former engine crankshaft arm lengths size, piston stroke basis, compression ratio adjustment design, and the petrol engine compression ratio is between 6-12, and the diesel engine compression ratio is between 14-22.
Claims (2)
1. a linear motion guide rail engine; It comprises body group, connecting rod, distribution device, fuel oil supply system, lubrication system, cooling system, ignition system, start-up system; Piston crown in connecting rod (4) connects connecting rod (7) and bent axle (9), crank arm (8) and crankshaft counter balance (10) through piston pin boss (6); It is characterized in that: on cylinder block crankcase one side inwall, be equipped with guide rail (1); Slide block (2) cooperates with guide rail (1) and along doing straight line motion on the guide rail, an end of piston groove timbering (3) and slide block (2) are fixing, and the other end of piston groove timbering (3) is piston crown (4).
2. according to claim 1 described linear motion guide rail engine, it is characterized in that: design of structural size confirms that mode is:
The physical dimension of the linear motion guide rail among a, the present invention, body group, connecting rod, distribution device, the technical parameter that designs with linear motion guide rail engine of the present invention designs and makes.
The physical dimension of the fuel oil supply system among b, the present invention, lubrication system, cooling system, ignition system, start-up system and assembling layout are adjusted, design, are made and assemble with technical parameter, the physical dimension of linear motion guide rail engine of the present invention.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010102900942A CN102400785A (en) | 2010-09-14 | 2010-09-14 | Linear motion guide rail engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010102900942A CN102400785A (en) | 2010-09-14 | 2010-09-14 | Linear motion guide rail engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102400785A true CN102400785A (en) | 2012-04-04 |
Family
ID=45883360
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010102900942A Pending CN102400785A (en) | 2010-09-14 | 2010-09-14 | Linear motion guide rail engine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN102400785A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103195562A (en) * | 2013-04-11 | 2013-07-10 | 北京理工大学 | Piston assembly phase position locking device of free piston internal combustion generating power system |
| CN105201644A (en) * | 2015-08-01 | 2015-12-30 | 李长松 | Engine transmission mechanism |
| CN105202137A (en) * | 2015-08-01 | 2015-12-30 | 李长松 | Device for changing structure and motion mode of slider-crank mechanism |
| CN113103229A (en) * | 2021-03-30 | 2021-07-13 | 鲁东大学 | Method for realizing moment of force-to-shaft on robot connecting rod |
-
2010
- 2010-09-14 CN CN2010102900942A patent/CN102400785A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103195562A (en) * | 2013-04-11 | 2013-07-10 | 北京理工大学 | Piston assembly phase position locking device of free piston internal combustion generating power system |
| CN105201644A (en) * | 2015-08-01 | 2015-12-30 | 李长松 | Engine transmission mechanism |
| CN105202137A (en) * | 2015-08-01 | 2015-12-30 | 李长松 | Device for changing structure and motion mode of slider-crank mechanism |
| CN105201644B (en) * | 2015-08-01 | 2018-05-08 | 李长松 | A kind of engine drive mechanism device |
| CN113103229A (en) * | 2021-03-30 | 2021-07-13 | 鲁东大学 | Method for realizing moment of force-to-shaft on robot connecting rod |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US10502129B2 (en) | Double-crankshaft engine | |
| CN106224093A (en) | A kind of hydraulic speed control formula variable compression ratio engine | |
| US20110192370A1 (en) | Positive-Displacement Engine | |
| US10267225B2 (en) | Internal combustion engine | |
| CN102400785A (en) | Linear motion guide rail engine | |
| US20100300410A1 (en) | Variable stroke and compression ratio engine | |
| CN103821612A (en) | Magnetic drive engine energy transmission system | |
| CN201401230Y (en) | High-speed vibration-reducing engine | |
| US8281764B2 (en) | Half cycle eccentric crank-shafted engine | |
| CN1831310A (en) | Paired pendulum piston engine | |
| CN2900811Y (en) | Double crank shaft link rod mechanism engine | |
| CN101158316A (en) | Non-round annular wheel crankless engines | |
| CN101526028B (en) | Vertical cylinder piston type internal combustion engine | |
| CN100504052C (en) | Rotating straight axle four-stroke piston engine device | |
| CN205744144U (en) | Twin crankshaft engine | |
| CN213953746U (en) | Countershaft output type variable compression ratio engine | |
| CN210264917U (en) | Double-spring connecting rod opposed two-stroke engine | |
| CN103742263A (en) | Connecting rod piston type combustion chamber combined dead-center-free reciprocating internal combustion engine | |
| KR20120081400A (en) | Balance shaft for engine | |
| CN1032057A (en) | Multi-cylinder integral assembly four strokes oscillating piston internal combustion engine | |
| CN1280530C (en) | Single-crankshaft opposite vertex piston internal combustion engine with double-barrel working simultaneously | |
| CN102192008B (en) | Gear-driven internal combustion engine | |
| CN105804869A (en) | Double-shaft piston engine | |
| CN101408130A (en) | Internal combustion engine with four cylinders, four strokes, reciprocating piston and double-peak convex disk | |
| CN201306211Y (en) | Reciprocating internal combustion engine with double-sided piston and arc cylinder body |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20120404 |