CN109282001A - A kind of design method of double balance shaft system - Google Patents
A kind of design method of double balance shaft system Download PDFInfo
- Publication number
- CN109282001A CN109282001A CN201811496327.7A CN201811496327A CN109282001A CN 109282001 A CN109282001 A CN 109282001A CN 201811496327 A CN201811496327 A CN 201811496327A CN 109282001 A CN109282001 A CN 109282001A
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- China
- Prior art keywords
- balance shaft
- maximum
- shaft system
- inertia force
- crankshaft
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H33/00—Gearings based on repeated accumulation and delivery of energy
- F16H33/02—Rotary transmissions with mechanical accumulators, e.g. weights, springs, intermittently-connected flywheels
- F16H33/04—Gearings for conveying rotary motion with variable velocity ratio, in which self-regulation is sought
- F16H33/08—Gearings for conveying rotary motion with variable velocity ratio, in which self-regulation is sought based essentially on inertia
- F16H33/10—Gearings for conveying rotary motion with variable velocity ratio, in which self-regulation is sought based essentially on inertia with gyroscopic action, e.g. comprising wobble-plates, oblique cranks
Abstract
The invention discloses a kind of design methods of double balance shaft system, comprising the following steps: step A: obtaining the reciprocating mass m acted on piston pinj；Step B: throw of crankshaft R and crank to connecting rod length ratio λ is obtained；Step C: angular velocity of crankshaft ω is obtained；Step D: the maximum two-stage reciprocating inertia force F of engine is obtainedjmax；Step E: the eccentric mass M of balance weight to be set is obtainedBAnd eccentricity RB；Step F: the maximum two-stage reciprocating inertia force F of double balance shaft system is obtainedBmax；Step G: according to maximum two-stage reciprocating inertia force FjmaxWith maximum two-stage reciprocating inertia force FBmaxRelationship, be balanced rate η.Compared with prior art, design method provided by the invention is simple, effective, is balanced rate by set procedures, if balanced ratio is lower than given requirements, by adjusting the size of the parameters such as balance weight eccentric mass and eccentricity, until meeting design requirement.
Description
Technical field
The present invention relates to engine component technical field, especially a kind of design method of double balance shaft system.
Background technique
In the working cycles of engine, the movement velocity of piston is very fast, and speed is uneven.Since piston is in gas
High-speed straight-line movement repeatedly is done in cylinder, it is inevitable that very big inertia force is generated on piston, piston pin and connecting rod, produce engine
Raw vibration.It is single order vibration that wherein vibration frequency domain engine speed is identical, and frequency is to be second order twice of engine speed
Vibration, and so on there is also the vibration of three ranks, quadravalence vibration, it is smaller that frequency gets over high amplitude, more than two ranks can be ignored.
With the raising of engine power performance, the reciprocating speed of piston is improved, and the vibration of engine increases, and passes through design
Balance shaft can offset the second order vibration of a part, promote the NVH performance of engine.By studying engine double balance shaft system
Design method, can effectively design balance shaft.
Summary of the invention
The object of the present invention is to provide a kind of design methods of double balance shaft system, are asked with solving technology in the prior art
Topic, it can design effectively go out the balance shaft of high balanced ratio.
The present invention provides a kind of design methods of double balance shaft system, comprising the following steps:
Step A: the reciprocating mass m acted on piston pin is obtainedj；
Step B: throw of crankshaft R and crank to connecting rod length ratio λ is obtained；
Step C: angular velocity of crankshaft ω is obtained；
Step D: according to the reciprocating mass m in abovementioned stepsj, throw of crankshaft R, crank to connecting rod length ratio λ and crank shaft angle
The relationship of speed omega obtains the maximum two-stage reciprocating inertia force F of enginejmax；
Step E: the eccentric mass M of balance weight to be set is obtainedBAnd eccentricity RB；
Step F: according to throw of crankshaft R, the eccentric mass M in abovementioned stepsBAnd eccentricity RBRelationship, obtain double flat
The maximum two-stage reciprocating inertia force F of weighing apparatus axle systemBmax；
Step G: according to maximum two-stage reciprocating inertia force FjmaxWith maximum two-stage reciprocating inertia force FBmaxRelationship, put down
Weighing apparatus rate η.
The design method of double balance shaft system as described above, wherein preferably, in the step A, according to following public affairs
Formula obtains reciprocating mass mj:
mj=mh+m1
Wherein mhRepresent the equivalent reciprocating mass that piston assembly is converted to piston pin center, m1Connecting rod ASSY is represented to be converted to
The equivalent reciprocating mass at small end of connecting rod center.
The design method of double balance shaft system as described above, wherein preferably, in the step B, according to following public affairs
Formula obtains crank to connecting rod length ratio λ:
λ=R/L
Wherein L represents length of connecting rod.
The design method of double balance shaft system as described above, wherein preferably, in the step C, according to following public affairs
Formula obtains angular velocity of crankshaft ω:
π/30 ω=n
Wherein n represents rated engine speed.
The design method of double balance shaft system as described above, wherein preferably, in the step D, according to following public affairs
Formula obtains the maximum two-stage reciprocating inertia force F of enginejmax:
Fjmax=4 λ mjRω2。
The design method of double balance shaft system as described above, wherein preferably, in the step F, according to following public affairs
Formula obtains the maximum two-stage reciprocating inertia force F of double balance shaft systemBmax:
FBmax=16MBRBω2。
The design method of double balance shaft system as described above, wherein preferably, in the step G, according to following public affairs
Formula is balanced rate η:
η=FBmax/Fjmax。
Compared with prior art, design method provided by the invention is simple, effective, is balanced rate by set procedures,
If balanced ratio is lower than given requirements, by adjusting the size of the parameters such as balance weight eccentric mass and eccentricity, until meeting
Design requirement.
Detailed description of the invention
Fig. 1 is the structural schematic diagram of double balance shaft system.
Description of symbols: 1- balance shaft, 2- drive shaft, 3- crankshaft toothed wheel, 4- balance weight, the first balance shaft gear of 5-,
6- drives gear, 7- secondary balance shaft gear.
Specific embodiment
The embodiments described below with reference to the accompanying drawings are exemplary, for explaining only the invention, and cannot be construed to
Limitation of the present invention.
As shown in Figure 1, the double balance shaft system of the targeted design of the embodiment of the present invention include balance shaft 1, drive shaft 2 with
And crankshaft (not shown), the angular speed of balance shaft 1 are twice of crankshaft 3, the both ends of balance shaft 1 and drive shaft 2 are mounted on flat
Weigh block 4, and the balance weight 4 at both ends is arranged in 180 degree relative direction, is equipped with 1 gear 5 of the first balance shaft, drive shaft in balance shaft 1
Driving gear 6 and secondary balance shaft gear 7 are installed, 1 gear 5 of the first balance shaft and secondary balance shaft gear 7 are engaged, driven on 2
Crankshaft toothed wheel 3 on moving gear 6 and crankshaft engages.
The embodiment of the present invention is directed to the design method of above-mentioned double balance shaft system, comprising the following steps:
Step A: the reciprocating mass m acted on piston pin is obtainedj, in the present embodiment, preferably according to the following formula,
Obtain reciprocating mass mj:
mj=mh+m1
Wherein mhRepresent the equivalent reciprocating mass that piston assembly is converted to piston pin center, m1Connecting rod ASSY is represented to be converted to
The equivalent reciprocating mass at small end of connecting rod center.
Step B: obtaining throw of crankshaft R and crank to connecting rod length ratio λ, in the present embodiment, preferably according to the following formula, obtains song
Handle connecting rod ratio λ:
λ=R/L
Wherein L represents length of connecting rod.
Step C: obtaining angular velocity of crankshaft ω, in the present embodiment, preferably according to the following formula, obtains angular velocity of crankshaft ω:
π/30 ω=n
Wherein n represents rated engine speed.
Step D: according to the reciprocating mass m in abovementioned stepsj, throw of crankshaft R, crank to connecting rod length ratio λ and crank shaft angle
The relationship of speed omega obtains the maximum two-stage reciprocating inertia force F of enginejmax, in the present embodiment, preferably according to the following formula,
Obtain the maximum two-stage reciprocating inertia force F of enginejmax:
Fjmax=4 λ mjRω2。
Step E: the eccentric mass M of balance weight to be set is obtainedBAnd eccentricity RB；
Step F: according to throw of crankshaft R, the eccentric mass M in abovementioned stepsBAnd eccentricity RBRelationship, obtain double flat
The maximum two-stage reciprocating inertia force F of weighing apparatus axle systemBmax, in the present embodiment, preferably according to the following formula, obtain double balance shaft system
Maximum two-stage reciprocating inertia force FBmax:
FBmax=16MBRBω2。
Step G: according to maximum two-stage reciprocating inertia force FjmaxWith maximum two-stage reciprocating inertia force FBmaxRelationship, put down
Weighing apparatus rate η in the present embodiment, preferably according to the following formula, is balanced rate η:
η=FBmax/Fjmax。
The practical application of above-described embodiment is illustrated below:
Piston assembly (components such as piston, piston pin, piston ring, piston pin clamping spring) is converted to the equivalent at piston pin center
Reciprocating mass: mh=1.1127kg；
Connecting rod ASSY gross weight: 1.04kg is converted to the equivalent reciprocating mass at small end of connecting rod center are as follows:
m1=0.3267kg；
Therefore, the reciprocating mass on piston pin is acted on
mj=mh+m1=1.1127+0.3267=1.4394kg；
Throw of crankshaft R=50mm；
Length of connecting rod L=158mm；
Crank to connecting rod length ratio λ=R/L=50/158=0.3165；
Rated engine speed: n=3600r/min；
Angular velocity of crankshaft ω=n π/30=3600 × π/30=376.99rad/s；
If the eccentric mass of each balance weight is MB, eccentricity RB；
First set the eccentric mass M of single balance weightB=0.4747kg, mass center offset distance RB=11.92mm.
Calculate the maximum two-stage reciprocating inertia force of engine are as follows:
Fjmax=4 λ mjRω2=4 × 0.3165 × 1.4394 × 0.05 × 376.992=12949.25N
Calculate the maximum two-stage reciprocating inertia force of double balance shaft system are as follows:
FBmax=16MBRBω2=16 × 0.4747 × 0.01192 × 376.992N=12866.94N
Balanced ratio are as follows:
η=FBmax/FjmaxThe balance shaft of=12866.94/12949.25=0.9936=99.36%, design meet balance
It is required that.
If balanced ratio is lower than 99%, the eccentric mass MB of adjustable balance weight, the size of the parameters such as eccentricity RB, weight
It is new to calculate, until meeting design requirement.
Structure, feature and effect of the invention, the above institute are described in detail based on the embodiments shown in the drawings
Only presently preferred embodiments of the present invention is stated, but the present invention does not limit the scope of implementation as shown in the drawings, it is all according to structure of the invention
Think made change or equivalent example modified to equivalent change, when not going beyond the spirit of the description and the drawings,
It should all be within the scope of the present invention.
Claims (7)
1. a kind of design method of double balance shaft system, which comprises the following steps:
Step A: the reciprocating mass m acted on piston pin is obtainedj；
Step B: throw of crankshaft R and crank to connecting rod length ratio λ is obtained；
Step C: angular velocity of crankshaft ω is obtained；
Step D: according to the reciprocating mass m in abovementioned stepsj, throw of crankshaft R, crank to connecting rod length ratio λ and angular velocity of crankshaft ω
Relationship, obtain the maximum two-stage reciprocating inertia force F of enginejmax；
Step E: the eccentric mass M of balance weight to be set is obtainedBAnd eccentricity RB；
Step F: according to throw of crankshaft R, the eccentric mass M in abovementioned stepsBAnd eccentricity RBRelationship, obtain double balance shaft
The maximum two-stage reciprocating inertia force F of systemBmax；
Step G: according to maximum two-stage reciprocating inertia force FjmaxWith maximum two-stage reciprocating inertia force FBmaxRelationship, be balanced rate
η。
2. the design method of double balance shaft system according to claim 1, it is characterised in that: in the step A, according to
Lower formula, obtains reciprocating mass mj:
mj=mh+m1
Wherein mhRepresent the equivalent reciprocating mass that piston assembly is converted to piston pin center, m1It represents connecting rod ASSY and is converted to connecting rod
The equivalent reciprocating mass at microcephaly center.
3. the design method of double balance shaft system according to claim 1, it is characterised in that: in the step B, according to
Lower formula, obtains crank to connecting rod length ratio λ:
λ=R/L
Wherein L represents length of connecting rod.
4. the design method of double balance shaft system according to claim 1, it is characterised in that: in the step C, according to
Lower formula, obtains angular velocity of crankshaft ω:
π/30 ω=n
Wherein n represents rated engine speed.
5. the design method of double balance shaft system according to claim 1, it is characterised in that: in the step D, according to
Lower formula obtains the maximum two-stage reciprocating inertia force F of enginejmax:
Fjmax=4 λ mjRω2。
6. the design method of double balance shaft system according to claim 1, it is characterised in that: in the step F, according to
Lower formula obtains the maximum two-stage reciprocating inertia force F of double balance shaft systemBmax:
FBmax=16MBRBω2。
7. the design method of double balance shaft system according to claim 1, it is characterised in that: in the step G, according to
Lower formula, is balanced rate η:
η=FBmax/Fjmax。
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811496327.7A CN109282001A (en) | 2018-12-07 | 2018-12-07 | A kind of design method of double balance shaft system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811496327.7A CN109282001A (en) | 2018-12-07 | 2018-12-07 | A kind of design method of double balance shaft system |
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| CN109282001A true CN109282001A (en) | 2019-01-29 |
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| CN201811496327.7A Pending CN109282001A (en) | 2018-12-07 | 2018-12-07 | A kind of design method of double balance shaft system |
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Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4628876A (en) * | 1984-05-16 | 1986-12-16 | Kawasaki Jukogyo Kabushiki Kaisha | Engine balancing system |
| CN201475241U (en) * | 2009-05-25 | 2010-05-19 | 浙江吉利汽车研究院有限公司 | Improved engine double-shaft balance device |
| CN102410339A (en) * | 2011-09-22 | 2012-04-11 | 重庆长安汽车股份有限公司 | Design method of balance shafts and balance weights of inline four-cylinder engine |
-
2018
- 2018-12-07 CN CN201811496327.7A patent/CN109282001A/en active Pending
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4628876A (en) * | 1984-05-16 | 1986-12-16 | Kawasaki Jukogyo Kabushiki Kaisha | Engine balancing system |
| CN201475241U (en) * | 2009-05-25 | 2010-05-19 | 浙江吉利汽车研究院有限公司 | Improved engine double-shaft balance device |
| CN102410339A (en) * | 2011-09-22 | 2012-04-11 | 重庆长安汽车股份有限公司 | Design method of balance shafts and balance weights of inline four-cylinder engine |
Non-Patent Citations (2)
| Title |
|---|
| 刘鹏飞、刘伟、梁海龙: "《发动机双轴平衡机构的设计方法研究》", 《机械研究与应用》 * |
| 钱志鹏: "《8V280柴油机双轴平衡机构方案设计及平衡性能研究》", 《中国优秀硕士学位论文全文数据库 工程科技Ⅱ辑》 * |
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| CB02 | Change of applicant information |
Address after: 230601 No. 99 Ziyun Road, Hefei Economic and Technological Development Zone, Anhui Province Applicant after: Anhui Jianghuai Automobile Group Limited by Share Ltd Address before: 230601 No. 669 Shixin Road, Taohua Industrial Park, Hefei City, Anhui Province Applicant before: Anhui Jianghuai Automobile Group Limited by Share Ltd |
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Application publication date: 20190129 |
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