CN101629515A - Automatically varied crank-link mechanism of four-stroke internal combustion engine - Google Patents
Automatically varied crank-link mechanism of four-stroke internal combustion engine Download PDFInfo
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- CN101629515A CN101629515A CN200910023621A CN200910023621A CN101629515A CN 101629515 A CN101629515 A CN 101629515A CN 200910023621 A CN200910023621 A CN 200910023621A CN 200910023621 A CN200910023621 A CN 200910023621A CN 101629515 A CN101629515 A CN 101629515A
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- crank pin
- crank
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- connecting rod
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Abstract
The invention relates to an automatically varied crank-link mechanism of a four-stroke internal combustion engine, comprising a piston (1), a piston pin (2), a connecting rod (3), a crank arm (4), a bent axle (5) and a crank pin (6); one end of the crank arm (4) which is far away from the bent axle (5) is provided with a crank pin hole (7), the crank pin (6) is inserted into the crank pin hole (7); in operation, according to different action relationship between the connecting rod (3), a crank arm (4) and the crank pin (6), the crank pin (6) can slide freely in the crank pin hole (7) along the hole wall or rolls to different positions which are close to or far away from the center of a bent axle (6); in air suction and compression stroke, shorter crank radius is used for operation, while in expansion and air exhaust stroke, longer crank radius is used for operation, so that the actual stroke of the piston in the air suction and compression stroke is less than that of in the expansion and air exhaust stroke, and the expansion ratio is greater than the compression ratio, thus automatically realizing efficient and energy-saving operating cycle of the internal combustion engine.
Description
(1) technical field
The present invention relates to the connecting rod of two-stroke piston internal-combustion engine.
(2) background technique
Two-stroke piston internal-combustion engine of the prior art is normally worked by Otto cycle (petrol engine) or diesel cycle (diesel engine), because the traveled distance of piston is identical in four strokes, promptly from top dead center move to lower dead center or move to top dead center from lower dead center, the air inlet maximum volume of cylinder is identical with the acting maximum volume that expands, and the compression ratio of internal-combustion engine equals expansion ratio.Because the fuel gas temperature when piston expand to finish in the cylinder is higher than the air temperature of compression stroke when initial, combustion gas when make to expand finishing still has pressure and dump energy higher when more initial than compression, and this part energy is discharged with waste gas and caused the efficient of internal-combustion engine lower.
In order to improve the combustion gas energy utilization ratio, thereby improve the efficient of internal-combustion engine, the quartastroke engine of prior art utilizes intake valve in advance or postpone and cutting out, and actual compression ratio is reduced, and realizes the energy-efficient duty cycle mode of expansion ratio greater than compression ratio.
In the quartastroke engine of prior art, the composition structure of its connecting rod all is the same, and working principle is also identical, and the traveled distance of piston is duplicate in four strokes of internal-combustion engine.In Otto or diesel-cycle internal combustion machine, the crank radius in the connecting rod is changeless, and compression ratio equals expansion ratio, and a part of available energy has been taken away in exhaust, and its thermal efficiency is lower.For Miller cycle engine of the prior art, though its compression ratio is less than expansion ratio, but the crank radius in the used connecting rod remains changeless, piston real work stroke in air inlet and compression stroke does not reduce, with respect to its lower compression ratio, exist one section unnecessary piston stroke respectively in these two strokes, produced extra frictional loss between piston and the cylinder, and consumed certain power, reduced its output power and thermal efficiency of cycle.
(3) summary of the invention
The deficiency that immobilizes and produced for the crank radius that overcomes quartastroke engine connecting rod in the prior art, the present invention proposes the connecting rod that a kind of crank radius can change automatically in four strokes, make quartastroke engine not need extra control gear just can realize that compression ratio is lower than the energy-efficient duty cycle mode of expansion ratio.
Comprise piston in the connecting rod of the present invention, wrist pin, connecting rod, crankweb, crank pin, bent axle, the piston skirt is connected with wrist pin, the connecting rod small end end is installed in rotation on the wrist pin, one end of crankweb is fixedlyed connected with bent axle, the connnecting rod big end end is installed in rotation on the crank pin, it is characterized in that: be provided with crank pin hole away from an end of bent axle at crankweb, the two ends of crank pin are respectively charged in the crank pin hole of a pair of crankweb, the cylindrical outer circumferential profile of the part of crank pin in crank pin hole should be completely contained in the profile line of crank pin hole, makes crank pin freely slide or freely to roll along crank pin hole wall any point; Greater than zero, this difference should be corresponding in the progressive error of expansion stroke and compression stroke with the piston (1) of designing requirement apart from the difference of the distance between crankshaft center solstics and the closest approach and the cylinder diameter of the part of crank pin (6) in crank pin hole (7) for the hole wall of described crank pin hole (7); Crank pin hole be shaped as the closed curve that closed curve that closed curve that circle a plurality of straightways oval or tangent to each other and a plurality of arc section combine or a plurality of straightways tangent to each other and a plurality of oval segmental arc combine or a plurality of curved sections tangent to each other combine.
Following brief description working principle of the present invention.Suppose that cylinder center and crankshaft rotating center line intersect, the distance in definition crank pin axle center to bent axle axle center is a crank radius.
The two-stroke piston internal-combustion engine crankshaft rotating is finished a work cycle for 720 °, comprises air inlet, compression, expansion and four strokes of exhaust.
Aspirating stroke: crankshaft rotating drives piston and is moved to the lower dead center direction by top dead center, and the crankshaft rotating angular range is 0 °～180 °, and what connecting rod was subjected to is that crank rotates the pulling force to it produced.When bent axle was in 0 °, crank pin was arranged in close bent axle one side of crank pin hole on the crankweb.When bent axle since 0 ° of first section of rotating, because the crank rotation is to the effect of connecting rod, make crank pin move along the crank pin hole wall, identical when keeping the distance of crank pin between wrist pin with 0 °, begin up to certain angle between the crankshaft rotating to 0 °～180 °, crank pin makes this distance begin to increase under the promotion of crank pin hole wall, and piston just really begins to move downward.When the position of crankshaft rotating to 180 °, crank pin moves in the crank pin hole near a side of bent axle, and piston also moves to the position of compression starting point from top dead center.
Compression stroke: crankshaft rotating promotes piston and is moved to the top dead center direction by compression beginnning, and the crankshaft rotating angular range is 180 °～360 °, and what connecting rod was subjected to is that crank rotates the thrust to it produced.At bent axle since 270 ° of first sections of rotating, because the crank rotation is to the effect of connecting rod, make crank pin move along the crank pin hole wall, and identical when keeping the distance of crank pin between wrist pin with 180 °, piston does not have real setting in motion during this period of time, up to crankshaft rotating to greater than certain angle of 180 ° the time, crank pin makes this distance begin to reduce under the promotion of crank pin hole wall, at this moment, piston begins to move upward, and compression process begins.When the corner of bent axle reached 360 °, crank pin moved to a side of close bent axle in the crank pin hole, and piston also moves to top dead center from the compression beginnning position.
Expansion stroke: piston promotes crankshaft rotating, and the angle range of bent axle is 360 °～540 °, and piston is moved to lower dead center by top dead center under the effect of high temperature, pressurized gas, and connecting rod is subjected to piston and moves downward the thrust that it is produced.When piston began to move downward, crank pin throw crank pin-and-hole wall made the crank rotation, and simultaneously, crank pin moves along the crank pin hole wall.When bent axle during from the position of 360 ° of rotated position to 540 °, crank pin moves in the crank pin hole away from a side of bent axle, and piston has also moved to bottom dead center position from top dead center.
Exhaust stroke: crankshaft rotating promotes piston and is moved to top dead center by lower dead center, and the angle range of bent axle is 540 °～720 °, and connecting rod is subjected to the thrust that the crankshaft rotating motion is produced.Because when bent axle was in 540 ° position, the distance between crank pin and the wrist pin was maximum, therefore, bent axle is since 540 ° of rotations, and crank pin is under the effect of crank pin hole wall, and the distance between crank pin and the wrist pin reduces, and piston also moves upward simultaneously.When bent axle when 540 ° turn to 720 ° of positions, crank pin moves in the crank pin hole near a side of bent axle, piston also moves to top dead center position from bottom dead center position, finishes waste gas and discharges.
Connecting rod of the present invention is when four stroke work, crank pin is except together rotating with crankweb, crank pin also will move in the crank pin hole of crankweb, automatically changed the size of crank radius, make air inlet and two strokes of compression the piston traveled distance less than expand and two strokes of exhaust in the actual motion distance of piston, the difference of the piston displacement distance of expansion stroke and compression stroke just equals the crank pin hole wall in the distance of crank radius direction and the difference of crank pin diameter, and the difference of this piston stroke has realized the energy conservation circulation of compression ratio less than expansion ratio just.
Compared with prior art, the present invention has following tangible advantage:
1, owing to the change of crank radius, the compression stroke of piston is less than expansion stroke, and promptly compression ratio has increased the degree of utilizing of work cycle energy less than expansion ratio, and the thermal efficiency improves, and reaches energy-conservation effect;
2, piston at the real motion of aspirating stroke and compression stroke apart from shortening, not only reduced the mechanical friction loss of piston motion, improved the working life of part, but also reduced the actual wasted work of air inlet and compression process, the internal-combustion engine output power and the thermal efficiency are improved;
3, the motion of crank pin in crank pin hole is different and finish automatically according to crank pin stressing conditions at work fully, do not need extra control gear;
4, first section of aspirating stroke, piston will postpone a period of time to the motion of lower dead center direction with respect to the rotatablely moving of crank, actual intake process also will be postponed the regular hour, like this, exhaust valve can late release, and intake valve postpones to open simultaneously, has reduced the phase mutual interference between the inlet and outlet, help the discharge of waste gas, improved the operating conditions of inlet and outlet effectively;
5, first section of compression stroke, piston also will postpone a period of time to the zero-time of top dead center direction motion with respect to the rotatablely moving of crank, the time of compression beginning is delayed simultaneously, can utilize piston motion to close intake valve during this period of time to what begin to compress behind the compression beginnning, so not only a small amount of fresh momentum of inspiration can not discharged, also can be lower than extra some live gass of many inspirations of pressure of suction tude because of cylinder pressure, help improving the momentum of air inlet, thereby improve the output power of internal-combustion engine;
6, since expansion ratio greater than compression ratio, the gas in the jar temperature descends in the exhaust stroke, reduced the temperature of cylinder and piston when air-breathing, the density of gas in the jar and air inflow in the time of can improving air inlet, and the reduction of delivery temperature and pressure also makes the corresponding decline of exhaust velocity, helps reducing exhaust sound and harmful substance content.
7, for four-stroke gasoline engine, under the certain condition of output power,, can use more low-grade gasoline because compression ratio reduces, reduced user's user cost.
(4) description of drawings:
Fig. 1 is that connecting rod of the present invention is formed schematic representation.
Fig. 2 is a connecting rod crank pin hole shape schematic representation one of the present invention.
Fig. 3 is a connecting rod crank pin hole shape schematic representation two of the present invention.
Fig. 4 is a connecting rod crank pin hole shape schematic representation three of the present invention.
Fig. 5 is a connecting rod crank pin hole shape schematic representation four of the present invention.
Fig. 6 is connecting rod crankweb of the present invention and crank pin position structure and scheme of installation one.
Fig. 7 is connecting rod crankweb of the present invention and crank pin position structure and scheme of installation two.
Fig. 8 is connecting rod crankweb of the present invention and crank pin position structure and scheme of installation three.
Fig. 9 is connecting rod crankweb of the present invention and crank pin position structure and scheme of installation four.
Among the figure: 1-piston 2-wrist pin 3-connecting rod 4-crankweb 5-bent axle
6-crank pin 7-crank pin hole 8-gulde edge
9-positioning end 10-positioning ring 11-locating slot
(5) embodiment
Embodiment
Fig. 1 is seen in the connecting rod signal of present embodiment, comprise piston 1, wrist pin 2, connecting rod 3, crankweb 4, bent axle 5, crank pin 6, the skirt section of piston 1 is connected with wrist pin 2, connecting rod 3 little head ends are installed in rotation on the wrist pin 2, one end of crankweb 4 is fixedlyed connected with bent axle 5, connecting rod 3 stub ends are installed in rotation on the crank pin 6, and the method for installation and prior art are roughly the same; Crankweb 4 is provided with crank pin hole 7 away from an end of bent axle, and the two ends of crank pin 6 are respectively charged in the crank pin hole 7 of a pair of crankweb 4.The hole wall of crank pin hole 7 apart from the difference of the distance between crankshaft center solstics and the closest approach and the cylinder diameter of the part of crank pin 6 in crank pin hole 7 greater than zero, and the size of this difference should satisfy the designing requirement of piston 1 in the progressive error of expansion stroke and compression stroke, for central located connecting rod, this difference just equals the progressive error of the piston 1 of designing requirement in expansion stroke and compression stroke; For offset connecting rod, this difference should be consistent in the progressive error of expansion stroke and compression stroke with the piston 1 of designing requirement according to the size of offset.
The shape of crank pin hole 7 adopts any in following four kinds: first kind as shown in Figure 2, crank pin hole 7 is a circular port, the difference of the diameter of circular crank pin hole 7 and the cylinder diameter of the part of crank pin 6 in crank pin hole 7 is greater than zero, and equal the difference of the stroke of piston 1 in expansion stroke and compression stroke of designing requirement, and the center of circle of circular crank pin hole 7 hole wall that is positioned at crank pin hole 7 is on the line of the solstics at bent axle 5 centers and closest approach; Second kind as shown in Figure 3, crank pin hole 7 is a slotted eye, the two-end-point of the major axis of oval crank pin hole 7 overlaps with the solstics and the closest approach of the hole wall of crank pin hole 7 apart from bent axle 5 centers, the difference of transverse length and focal length is greater than the cylinder diameter of the part of crank pin 6 in crank pin hole 7, and the difference of the cylinder diameter of the length of long axis of ellipse and the part of crank pin 6 in crank pin hole 7 equals the difference of piston 1 stroke in expansion stroke and compression stroke of designing requirement; The third as shown in Figure 4, the contour shape of crank pin hole 7 is two curved sections and two straightway closed curves that constituted that are connected tangent to each other, arbitrary curved section is arc section or oval segmental arc, two curved sections must pass through solstics and the closest approach of the hole wall of crank pin hole 7 apart from bent axle 5 centers respectively, the difference of the diameter of arc section or the major axis of oval segmental arc and focal length is greater than the cylinder diameter of crank pin 6 part in crank pin hole 7, between two curved sections by two straightways formation closed curve that links together; The 4th kind as shown in Figure 5, the contour shape of crank pin hole 7 is the closed curve that adjacent a plurality of curved sections connection tangent to each other is constituted, and described curved section is a diameter greater than the difference of the arc section of crank pin 6 cylinder diameter of part in crank pin hole 7 or major axis and focal length greater than crank pin 6 partly oval segmental arc of cylinder diameter in crank pin hole 7.
Crank pin 6 adopts a kind of in following four kinds of modes along the location of its axial direction: first kind as shown in Figure 6, crank pin 6 is isodiametric cylindrical body, crank pin hole 7 has the gulde edge 8 that is projected into crank pin hole 7 inside in a side of crankweb 4 connections and bent axle 5, the contour shape of this gulde edge 8 is similar to the contour shape of crank pin hole 7, the inner side surface of gulde edge 8 is contacted with the circular end surface of crank pin 6, be used for the axially locating of crank pin 6; Second kind as shown in Figure 7, the cylindrical crank pin of equal diameter 6 two ends have positioning end 9, positioning end 9 be with crank pin 6 coaxial and diameter greater than the cylindrical body of the diameter of crank pin 6, the outstanding annular end face in positioning end 9 and crank pin 6 outer round surface intersections is connected the contacts side surfaces of bent axle 5 with crankweb 4, be used for the axially locating of crank pin 6; The third as shown in Figure 8, crank pin 6 is isodiametric cylindrical structure, at the bossed positioning ring 10 of band of position near crank pin 6 two ends, positioning ring 10 be with crank pin 6 coaxial and diameter greater than the cylindrical body of the diameter of crank pin 6, positioning ring 10 along the axial width of crank pin 6 less than crankweb 4 half along the axial thickness of crank pin 6, axial direction along crank pin 6 in the crank pin hole 7 is provided with a locating slot 11, the degree of depth of locating slot 11 is greater than the difference of the radius of the radius of positioning ring 10 and crank pin 6, the width of locating slot 11 is greater than the width of positioning ring 10, and crank pin 6 makes positioning ring 10 be installed to the axially locating that is used for crank pin 6 in the locating slot 11 when packing in the crank pin hole 7; The 4th kind as shown in Figure 9, crank pin 6 adopts stepped cylindrical structure, near the two ends of crank pin 6 cylinder diameter is less than the cylinder diameter of intermediate portion, and the cylindrical length of the intermediate portion that diameter is bigger should guarantee that crank pin 6 packs into behind the crank pin hole 7, the outstanding annular end face in crank pin 6 intermediate portion cylindrical body two ends and a pair of crankweb 4 relative side surfaces contact, and are used for crank pin 6 in axial location.
Claims (9)
1. the connecting rod that automatically changes of quartastroke engine crank radius, comprise piston (1), wrist pin (2), connecting rod (3), crankweb (4), bent axle (5), crank pin (6), it is characterized in that: an end that leaves bent axle (5) at crankweb (4) is provided with crank pin hole (7), the two ends of crank pin (6) are respectively charged in the crank pin hole (7) of a pair of crankweb (4), the cylindrical outer circumferential profile of the part of crank pin (6) in crank pin hole (7) should be completely contained in the profile line of crank pin hole (7), makes crank pin (6) freely slide or freely to roll along crank pin hole (7) wall any point; Greater than zero, this difference should satisfy the designing requirement of piston (1) in the progressive error of expansion stroke and compression stroke to the hole wall of described crank pin hole (7) apart from the difference of the distance between crankshaft center solstics and the closest approach and the cylinder diameter of the part of crank pin (6) in crank pin hole (7); Crank pin hole (7) be shaped as the closed curve that closed curve that circle a plurality of straightways oval or tangent to each other and a plurality of curved section combine or a plurality of curved sections tangent to each other combine.
2. the connecting rod that quartastroke engine crank radius as claimed in claim 1 changes automatically, the diameter of circular crank pin hole (7) is greater than the cylinder diameter of the part of crank pin (6) in crank pin hole (7), and the center of circle of circular crank pin hole (7) hole wall that is positioned at crank pin hole (7) is on the line of the solstics at bent axle (5) center and closest approach.
3. the connecting rod that quartastroke engine crank radius as claimed in claim 1 changes automatically, the two-end-point of the major axis of oval crank pin hole (7) overlaps with the solstics and the closest approach of the hole wall of crank pin hole (7) apart from bent axle (5) center, and the difference of transverse length and focal length is greater than the cylinder diameter of the part of crank pin (6) in crank pin hole (7).
4. the connecting rod that quartastroke engine crank radius as claimed in claim 1 changes automatically, arbitrary curved section of the crank pin hole (7) that is constituted by two curved sections tangent to each other and two straightways is arc section or oval segmental arc, two curved sections must pass through closest approach and the solstics of the hole wall of crank pin hole (7) apart from bent axle (5) respectively, the difference of the diameter of arc section or the major axis of oval segmental arc and focal length is greater than the cylinder diameter of crank pin (6) part in crank pin hole (7), between two sections curves by two straightways formation closed curve that links together.
5. the connecting rod that quartastroke engine crank radius as claimed in claim 1 changes automatically, arbitrary curved section of the crank pin hole (7) that is made of adjacent a plurality of curved sections connection tangent to each other is arc section or oval segmental arc, and the difference of the diameter of arc section or the major axis of oval segmental arc and focal length is greater than the cylinder diameter of crank pin (6) part in crank pin hole (7).
6. the connecting rod that quartastroke engine crank radius as claimed in claim 1 changes automatically, crank pin (6) is isodiametric cylindrical body, crank pin hole (7) has the gulde edge (8) that is projected into crank pin hole (7) inside in the side that crankweb (4) connects bent axle (5), the contour shape of gulde edge (8) is the similar figures of the contour shape of crank pin hole (7), the inner side surface of gulde edge (8) is contacted with the circular end surface of crank pin (6), be used for the axially locating of crank pin (6).
7. the connecting rod that quartastroke engine crank radius as claimed in claim 1 changes automatically, the cylindrical crank pin of equal diameter (6) two ends have positioning end (9), positioning end (9) be with crank pin (6) coaxial and diameter greater than the cylindrical body of the diameter of crank pin (6), the outstanding annular end face in positioning end (9) and crank pin (6) outer round surface intersection is connected the contacts side surfaces of bent axle (5) with crankweb (4), be used for the axially locating of crank pin (6).
8. the connecting rod that quartastroke engine crank radius as claimed in claim 1 changes automatically, at the band of position bossed positioning ring (10) of equal diameter cylindrical body crank pin (6) near two ends, positioning ring (10) be with crank pin (6) coaxial and diameter greater than the cylindrical body of the diameter of crank pin (6), positioning ring (10) along the axial width of crank pin (6) less than crankweb (4) half along the axial thickness of crank pin (6), axial direction along crank pin (6) in the crank pin hole (7) is provided with a locating slot (11), the degree of depth of locating slot (11) is greater than the difference of the radius of the radius of positioning ring (10) and crank pin (6), the width of locating slot (11) is greater than the width of positioning ring (10), and crank pin (6) crank pin hole (7) of packing into makes positioning ring (10) be installed to the axially locating that is used for crank pin (6) in the locating slot (11) when interior.
9. the connecting rod that quartastroke engine crank radius as claimed in claim 1 changes automatically, crank pin (6) adopts stepped cylindrical structure, near crank pin (6) two ends cylinder diameter is less than the cylinder diameter of intermediate portion, and the cylindrical length of the intermediate portion that diameter is bigger should guarantee that crank pin (6) packs into behind the crank pin hole (7), the outstanding annular end face side surface relative with a pair of crankweb (4) in crank pin (6) intermediate portion cylindrical body two ends contacts, and is used for crank pin (6) in axial location.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910023621A CN101629515A (en) | 2009-08-18 | 2009-08-18 | Automatically varied crank-link mechanism of four-stroke internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910023621A CN101629515A (en) | 2009-08-18 | 2009-08-18 | Automatically varied crank-link mechanism of four-stroke internal combustion engine |
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| Publication Number | Publication Date |
|---|---|
| CN101629515A true CN101629515A (en) | 2010-01-20 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200910023621A Pending CN101629515A (en) | 2009-08-18 | 2009-08-18 | Automatically varied crank-link mechanism of four-stroke internal combustion engine |
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| CN (1) | CN101629515A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105221259A (en) * | 2015-07-08 | 2016-01-06 | 刘丕财 | Centrifugal vuilt-up crankshaft energy-saving engine |
| CN112412748A (en) * | 2020-11-09 | 2021-02-26 | 珠海格力节能环保制冷技术研究中心有限公司 | Piston assembly, crankshaft assembly, compressor and refrigeration equipment |
-
2009
- 2009-08-18 CN CN200910023621A patent/CN101629515A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105221259A (en) * | 2015-07-08 | 2016-01-06 | 刘丕财 | Centrifugal vuilt-up crankshaft energy-saving engine |
| CN112412748A (en) * | 2020-11-09 | 2021-02-26 | 珠海格力节能环保制冷技术研究中心有限公司 | Piston assembly, crankshaft assembly, compressor and refrigeration equipment |
| CN112412748B (en) * | 2020-11-09 | 2022-05-31 | 珠海格力节能环保制冷技术研究中心有限公司 | Piston assembly, crankshaft assembly, compressor and refrigeration equipment |
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Application publication date: 20100120 |