CN2035817U - Multicylinder diesel engine balanced means - Google Patents
Multicylinder diesel engine balanced means Download PDFInfo
- Publication number
- CN2035817U CN2035817U CN 88207405 CN88207405U CN2035817U CN 2035817 U CN2035817 U CN 2035817U CN 88207405 CN88207405 CN 88207405 CN 88207405 U CN88207405 U CN 88207405U CN 2035817 U CN2035817 U CN 2035817U
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- CN
- China
- Prior art keywords
- couple
- force couple
- crankshaft
- additional
- balance
- 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 - Lifetime
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- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
The utility model discloses a multicylinder diesel engine balancing device. The multicylinder diesel engine balancing device is suitable for balancing the reciprocating force couple of double cylinder and triple cylinder four-stroke diesel engines and modifying unbalanced two-stroke diesel engines. The principle is that both ends of a crankshaft are provided with an additional proper eccentric mass. Thus, the crankshaft is formed with an additional force couple. The moment of the additional force couple is sufficient for balancing 50% of the reciprocating force couple. Moreover, a balance shaft is arranged parallel to a cam shaft and has same rotating speed and opposite rotating direction with the crankshaft. Balance blocks of both ends of the balance shaft form a force couple which is also sufficient for balancing 50% of the reciprocating force couple. At the same time, the horizontal force couple of the balance shaft and the additional horizontal force couple of the crankshaft are directed to opposite directions, but the moments are equal. Therefore, the lateral balance of the diesel engines is ensured.
Description
The design is that the better simply mechanism of a kind of usefulness comes the device of the reciprocal couple of balance multi-cylinder diesel engine, is best suited for the balance of twin-tub and three cylinder four-stroke diesel engines, adapts to the requirement of power train in vehicle application and mobile operating to alleviate vibration.
The domestic production agricultural transportation vehicle is very in vogue in recent years, and selected power is roughly diesel engines such as 290,295 and 2100, and what is heard is arranged when therefore two cylinder diesel engine being required the cry of vibration damping.About the vibration damping problem of four-cycle diesel, at present except that single cylinder engine adopts double-shaft balance (S195 type), for twin-tub and three cylinder machines as yet not information what measure is arranged.In general, twin-tub and three-cylinder diesel also adopt double-shaft balance, and its structure is a more complicated.As desire existing type is installed additional double-shaft balance, then original structure must be done a large amount of the change, it seems also uneconomical.
This apparatus structure is simple, when existing twin-tub three cylinder four-stroke diesel engines are transformed, as long as install a trunnion shaft parallel with camshaft additional on prototype, just can receive the effectiveness in vibration suppression same with double-shaft balance.(please read hereinafter vibration attenuation mechanism.) simultaneously, with the diesel engine that the design transforms, its boundary dimension is constant fully, never hinders supporting to first wife's vehicle.Aspect processing, except that balance shaft bearing hole operation was warded off in increase, former organism process unit was also constant fully.In transformation, estimated weight will increase by 3%, and cost also will increase by 3%, and improved diesel engine is as power train in vehicle application, and short-time rating can increase by 20%.(, can suitably improve rotating speed in case of necessity because of vibration alleviates.）
This device is realized according to following principle:
1. in the additional proper eccentric quality of crankshaft two end, make former Balanced bent axle form one group of additional couple when rotated, the sensing of this additional couple is with back and forth couple is opposite, and its moment is enough to the reciprocal couple of balance 50%.
2. install the trunnion shaft of (avoiding valve actuating push rod) in parallel above camshaft additional, the rotating speed of this trunnion shaft is identical with bent axle, and turns to opposite with bent axle.When trunnion shaft rotated, the couple that its two ends equilibrium block forms was pointed to also on the contrary with reciprocal couple, and moment also is 50% of reciprocal couple.
3. because the sensing of the additional couple of trunnion shaft couple and bent axle is identical, itself and equate with the reciprocal couple of directed in opposite, thereby reciprocal couple acquisition balance.Simultaneously, two groups of horizontal couple of force (accompanying drawing 3) that the equilibrium block horizontal component forms, because of directed in opposite each other, also mutual balance.
This device construction is illustrated in down:
(1) twin-tub four-cycle diesel balanced controls please be read accompanying drawing 1.Fig. 1 (a) is tumbrel several diesel engine gear chamber train figure commonly used, and numeral 1 is a crankshaft gear, and 2 is idle pulley, and 3 is camshaft gear wheel, and 4 is the balance shaft gear that preparation is installed additional, and 5 is flywheel external diameter garden arc, and this arc is represented relative position between equilibrium block and the flywheel.D among the figure
1, d
2Be respectively camshaft and trunnion shaft distance to cylinder centerline.
Accompanying drawing 1(b) equilibrium block and bent axle positioning relation being described, also is the peaked position of reciprocal couple.First crank is represented piston at upper dead center among the figure, two balancing mass m on the right
1And m
1' under all pointing to; Second crank is represented piston at lower dead centre, two balancing mass m on the left side
2And m
2' directly over all pointing to.Because it is asymmetric that four balancing mass Fabric of this device put, must be between two cylinders during EQUILIBRIUM CALCULATION FOR PROCESS an illusory relation line, in the hope of the moment on both sides; Therefore to be divided equally by relation line be two 1/2 a to two cylinder centre distance a.B among the figure
1, b
1' and b
2, b
2' be respectively balancing mass m
1, m
1' and m
2, m
2' to the distance of relation line.In accompanying drawing 2, D is garden in the flywheel, in order to balancing mass m
2The location, R is that Qu Bing Xiao rotation changes radius, m is piston and connecting rod small end quality.All the other symbols are respectively turning radius, the centrifugal force of four balancing masses, the vertical stress component and the horizontal component of centrifugal force.And with amR ω
2Cos θ is the foundation of EQUILIBRIUM CALCULATION FOR PROCESS.ω is crank angular velocity (radian per second) in the formula.
(Fig. 2 a), the one-level reciprocal inertia force of quality m such as piston is mR ω as the first crank angle θ during less than 90 °
2Cos θ, points upwards forms anticlockwise moment 1/2 an amR ω to relation line
2Cos θ.At this moment associated mass m on the bent axle
1Centrifugal force be F
1, its vertical stress component F
1V is m
1R
1ω
2Cos θ; Upper right equilibrium block m
1' centrifugal force be F
1', its vertical stress component F
1' v is m
1' R
1' ω
2Cos θ; These two vertical stress components are directed downwards all, and relation line (Fig. 1 b) is formed two clockwise moment b
1M
1R
1ω
2Cos θ and b
1' m
1' R
1' ω
2Cos θ.Express the relation of reciprocal moment and trimming moment with mathematical expression, then the right moment sum is
1/2 × 1/2 a·mRω
2COSθ－b
1·m
1R
1ω
2COSθ＝0……（1）
1/2 × 1/2 a·mRω
2COSθ－b
1′·m
1′R
1′ω
2COSθ＝0……（2）
Equally, the moment sum on the relation line left side is
1/2 × 1/2 a·mRω
2COSθ－b
2·m
2R
2ω
2COSθ＝0……（3）
1/2 × 1/2 a·mRω
2COSθ－b
2′·m
2′R
2′ω
2COSθ＝0……（4）
Equilibrium relation from formula (1) to formula (4) as can be known, four trimming moments all equal 1/4 amR ω
2COS θ.So
b
1m
1R
1＝b
1′m
1′R
1′＝b
2m
2R
2＝b
2′m
2′R
2′……（5）
Therefore, formula (1) formula (3) addition is the relation that bent axle adds couple and reciprocal couple
1/2 amRω
2COSθ＝（b
1m
1R
1＋b
2m
2R
2）ω
2COSθ……（6）
Equally, formula (2) formula (4) addition is the trunnion shaft couple and the reciprocal relation of couple
1/2 amRω
2COSθ＝（b
1′m
1′R
1′＋b
2′m
2′R
2′）ω
2COSθ……（7）
Formula (6) and formula (7) have reflected first and second of aforementioned principles, and promptly the additional couple of bent axle equals 50% of reciprocal couple, and the trunnion shaft couple also equals 50% of reciprocal couple.
Formula (6) formula (7) addition then is a complete machine equilibrium of couples equation
amRω
2COSθ＝（b
1m
1R
1＋b
2m
2R
2）ω
2COSθ＋
（b
1′m
1′R
1′＋b
2′m
2′R
2′）ω
2COSθ……（8）
Formula (8) shows that this device is to realize to the balance of the reciprocal couple of one-level.
About the balance of equilibrium block horizontal component, please read accompanying drawing 2.The balancing mass m of crankshaft free-end
1(Fig. 2 is horizontal component F a)
1H is m
1R
1ω
2Sin θ is with the distance b on relation line (Fig. 1 b) the right
1Form a clockwise moment b
1m
1R
1ω
2Sin θ; The balancing mass m of flywheel end
2(Fig. 2 b) horizontal component F
2H is m
2R
2ω
2Sin θ is with the distance b on the relation line left side
2Also form a clockwise moment b
2m
2R
2ω
2Sin θ.According to the relation that each trimming moment of formula (5) equates, act on the horizontal moment of crankshaft two end, just become one group of horizontal couple of force (accompanying drawing 3).Its formula is
M
c＝（b
1m
1R
1＋b
2m
2R
2）ω
2sinθ……（9）
At the top-right equilibrium block of piston (accompanying drawing 2), i.e. the equilibrium block at trunnion shaft two ends, because of its turn to opposite with bent axle, so horizontal component F
1' H is m
1' R
1' ω
2Sin(-θ), the other end horizontal component F
2' H is m
2' R
2' ω
2Sin(-θ); Its moment is respectively-b
1' m
1' R
1' ω
2Sin θ and-b
2' m
2' R
2' ω
2Sin θ.Therefore, the couple of trunnion shaft is negative sense (accompanying drawing 3), and is just counterclockwise.Its formula is
M
b＝－（b
1′m
1′R
1′＋b
2′m
2′R
2′）ω
2sinθ……（10）
Formula (9) and (10) though two groups of horizontal couple of force not on same plane, itself and equal zero all the time.According to couple theorem " couple can move to arbitrary parallel plane by a plane, and its external effect is constant ".Argumentation, these two groups of horizontal couple of force can reach external balance; Do not cause the diesel engine transverse vibration.
The moment of each equilibrium block itself (product of weight and distance of centre of gravity) gets from formula (1) to (4)
m
1R
1＝amR／4b
1m
2R
2＝amR／4b
2
m
1′R
1′＝amR／4b
1′ m
2′R
2′＝amR／4b
2′
(2) three cylinder four-stroke diesel oil balanced controls please be read accompanying drawing 4.Associated mass m on Fig. 4 (a) expression bent axle
1And m
2The position and the relation of crankangle, at this moment first crank is 30 ° of after top dead center.D is garden in the flywheel among the figure, and d is that trunnion shaft is to cylinder pintch; Letter A, B, C are respectively first, second and the 3rd crank; The m in the upper left corner
1' and m
2' be the equilibrium block on the trunnion shaft.
Fig. 4 (b) expression bent axle and the vertical Fabric of trunnion shaft put.When first crank when upper dead center forwards 30 ° to, back and forth couple be a maximum.At this moment the reciprocal inertia force in first cylinder makes progress, so the balancing mass m on the right
1And m
1' under all pointing to; Reciprocal inertia force in the 3rd cylinder is downward, so the balancing mass m of flywheel end
2And m
2' directly over all pointing to; Instantaneous at this, the one-level reciprocal inertia force in second cylinder equals zero.B among the figure
1, b
1' and b
2, b
2' being respectively the distance of four balancing masses to relation line, a is the centre distance of two adjacent cylinder, digital I, II, III are respectively the center line of first cylinder, second cylinder and the 3rd cylinder.
Because it is asymmetric that the equilibrium block Fabric of this device puts, thus with the second cylinder center line as relation line, in order to the equalising torque on calculating both sides.Because of the reciprocal couple maximum value of three cylinder machines be again
MR ω
2A, (m is piston and connecting rod small end quality in the formula.R is that Qu Bing Xiao rotation changes radius, and a is the central moment of two adjacent cylinder.) when making equalising torque and calculate, couple should be become the form of moment, so be 1/2 to the reciprocal moment of relation line
MR ω
2A.According to Fig. 4 (b) the piece that balances to the distance of relation line, its trimming moment with the reciprocal pass of moment is:
The right moment sum 1/2 * 1/2
MR ω
2A-m
1R
1ω
2b
1=0 ... (11)
1/2 × 1/2
mRω
2a－m
1′R
1′ω
2b
1′＝0……（12）
Left side moment sum 1/2 * 1/2
MR ω
2A-m
2R
2ω
2b
2=0 ... (13)
1/2 × 1/2
mRω
2a－m
2′R
2′ω
2b
2′＝0……（14）
Separate above-listed four formulas, the own moment of equilibrium block (product of weight and center of gravity square) is followed successively by
m
1R
1＝0.433mRa／b
1m
1′R
1′＝0.433mRa／b
1′
m
2R
2＝0.433mRa／b
2m
2′R
2′＝0.433mRa／b
2′
Formula (11) then is the assembled machine balance equation to formula (14) four formula additions
（m
1′R
1′b
1′＋m
2′R
2′b
2′）ω
2……（15）
(m in the formula
1R
1b
1+ m
2R
2b
2) ω
2Be the additional couple of bent axle, (m
1' R
1' b
1'+m
2' R
2' b
2') ω
2Couple for trunnion shaft.Formula (15) and formula (8) difference be not represent with vertical stress component, and this is because selected the peaked position of reciprocal couple during calculated equilibrium moment; In this moment, under two equilibrium blocks on relation line the right all pointed to, directly over all sensings on the left side, there was not horizontal component in they, so equilibrant at this moment is pure centrifugal force.
About the balance of horizontal couple of force, in twin-tub machine horizontal couple of force is analyzed, proved that diesel engine can not produce transverse vibration; The balanced controls of three cylinder machines and twin-tub machine are identical, and its counterbalance effect also is identical naturally.
When (three) the design is used for the two stroke diesel engine transformation of lack of equilibrium, just do not need to add in addition trunnion shaft, it is opposite with bent axle to only require that camshaft turns to, and equilibrium block has been mixed just in its two ends.
Claims (1)
- A kind of balancer for multi-cylindered diesel engine of forming by a trunnion shaft and the additional couple of bent axle; It is characterized in that at additional two the eccentric mass m of crankshaft two end 1And m 2, the reciprocal couple that the couple that this associated mass forms equals 50%; In body one side a trunnion shaft is arranged, its two ends equilibrium block m 1' and m 2The couple of ' formation also equals 50% reciprocal couple; Transmission between trunnion shaft and the bent axle reaches balance shaft gear 4 by crankshaft gear 1 through gear 2,3, and gear 1 equates with the rotating speed of gear 4.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 88207405 CN2035817U (en) | 1988-06-18 | 1988-06-18 | Multicylinder diesel engine balanced means |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 88207405 CN2035817U (en) | 1988-06-18 | 1988-06-18 | Multicylinder diesel engine balanced means |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2035817U true CN2035817U (en) | 1989-04-12 |
Family
ID=4841431
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 88207405 Expired - Lifetime CN2035817U (en) | 1988-06-18 | 1988-06-18 | Multicylinder diesel engine balanced means |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2035817U (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1041549C (en) * | 1993-07-09 | 1999-01-06 | F·L·史密斯公司 | A vibration-compensating apparatus for counteracting vibrations |
| CN1075609C (en) * | 1996-05-20 | 2001-11-28 | 奥迪股份公司 | Device for balancing inertia moment of reciprocative piston in internal combustion engine |
| CN100432479C (en) * | 2005-08-29 | 2008-11-12 | 奇瑞汽车股份有限公司 | Engine crankshaft balance shaft mechanism |
| CN101660586A (en) * | 2008-08-25 | 2010-03-03 | 现代自动车株式会社 | Balance weight system of crankshaft |
| CN1955500B (en) * | 2005-10-13 | 2010-06-23 | 依纳-谢夫勒两合公司 | Radial bearing device |
| CN102853026A (en) * | 2011-06-29 | 2013-01-02 | 福特环球技术公司 | Multicylinder in-line internal combustion engine for a motor vehicle and method for operating the engine |
| CN103185062A (en) * | 2011-12-31 | 2013-07-03 | 上海汽车集团股份有限公司 | Crank shaft balanced system of inline three-cylinder engine |
| CN104047993A (en) * | 2013-03-14 | 2014-09-17 | 通用汽车环球科技运作有限责任公司 | Dry Sump Scavenge Pump System With Balance Shaft Capability For Application To Flat Plane V8 Engines |
| CN108884905A (en) * | 2016-03-31 | 2018-11-23 | 本田技研工业株式会社 | The balancing device of internal combustion engine |
| CN109611512A (en) * | 2019-02-15 | 2019-04-12 | 广西玉柴机器股份有限公司 | The balanced structure of engine crankshaft |
-
1988
- 1988-06-18 CN CN 88207405 patent/CN2035817U/en not_active Expired - Lifetime
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1041549C (en) * | 1993-07-09 | 1999-01-06 | F·L·史密斯公司 | A vibration-compensating apparatus for counteracting vibrations |
| CN1075609C (en) * | 1996-05-20 | 2001-11-28 | 奥迪股份公司 | Device for balancing inertia moment of reciprocative piston in internal combustion engine |
| CN100432479C (en) * | 2005-08-29 | 2008-11-12 | 奇瑞汽车股份有限公司 | Engine crankshaft balance shaft mechanism |
| CN101469645B (en) * | 2005-10-13 | 2013-02-13 | 谢夫勒科技股份两合公司 | Radial bearing |
| CN1955500B (en) * | 2005-10-13 | 2010-06-23 | 依纳-谢夫勒两合公司 | Radial bearing device |
| CN101457708B (en) * | 2005-10-13 | 2011-02-16 | 谢夫勒科技有限两合公司 | Radial bearing |
| CN101660586A (en) * | 2008-08-25 | 2010-03-03 | 现代自动车株式会社 | Balance weight system of crankshaft |
| CN102853026A (en) * | 2011-06-29 | 2013-01-02 | 福特环球技术公司 | Multicylinder in-line internal combustion engine for a motor vehicle and method for operating the engine |
| CN103185062A (en) * | 2011-12-31 | 2013-07-03 | 上海汽车集团股份有限公司 | Crank shaft balanced system of inline three-cylinder engine |
| CN104047993A (en) * | 2013-03-14 | 2014-09-17 | 通用汽车环球科技运作有限责任公司 | Dry Sump Scavenge Pump System With Balance Shaft Capability For Application To Flat Plane V8 Engines |
| CN108884905A (en) * | 2016-03-31 | 2018-11-23 | 本田技研工业株式会社 | The balancing device of internal combustion engine |
| CN109611512A (en) * | 2019-02-15 | 2019-04-12 | 广西玉柴机器股份有限公司 | The balanced structure of engine crankshaft |
| CN109611512B (en) * | 2019-02-15 | 2023-08-01 | 广西玉柴机器股份有限公司 | Balance structure of engine crankshaft |
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| PB01 | Publication | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CX01 | Expiry of patent term |