CN114001145A - Engine timing tooth chain system tooth form matching method based on cooperative algorithm - Google Patents

Engine timing tooth chain system tooth form matching method based on cooperative algorithm Download PDF

Info

Publication number
CN114001145A
CN114001145A CN202111382838.8A CN202111382838A CN114001145A CN 114001145 A CN114001145 A CN 114001145A CN 202111382838 A CN202111382838 A CN 202111382838A CN 114001145 A CN114001145 A CN 114001145A
Authority
CN
China
Prior art keywords
chain
tooth
chain plate
tooth form
plate
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.)
Granted
Application number
CN202111382838.8A
Other languages
Chinese (zh)
Other versions
CN114001145B (en
Inventor
程亚兵
安立持
李家宝
朱凯宏
刘雨
高俊珂
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Jilin University
Original Assignee
Jilin University
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Jilin University filed Critical Jilin University
Priority to CN202111382838.8A priority Critical patent/CN114001145B/en
Publication of CN114001145A publication Critical patent/CN114001145A/en
Application granted granted Critical
Publication of CN114001145B publication Critical patent/CN114001145B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/30—Chain-wheels
    • F16H55/303—Chain-wheels for round linked chains, i.e. hoisting chains with identical links
    • 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
    • F16G—BELTS, CABLES, OR ROPES, PREDOMINANTLY USED FOR DRIVING PURPOSES; CHAINS; FITTINGS PREDOMINANTLY USED THEREFOR
    • F16G13/00—Chains
    • F16G13/02—Driving-chains
    • F16G13/06—Driving-chains with links connected by parallel driving-pins with or without rollers so called open links
    • 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
    • F16G—BELTS, CABLES, OR ROPES, PREDOMINANTLY USED FOR DRIVING PURPOSES; CHAINS; FITTINGS PREDOMINANTLY USED THEREFOR
    • F16G15/00—Chain couplings, Shackles; Chain joints; Chain links; Chain bushes
    • F16G15/12—Chain links
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/08—Profiling
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/08—Profiling
    • F16H55/0833—Flexible toothed member, e.g. harmonic drive
    • 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
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/06—Gearings for conveying rotary motion by endless flexible members with chains
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F17/00—Digital computing or data processing equipment or methods, specially adapted for specific functions
    • G06F17/10—Complex mathematical operations
    • G06F17/15—Correlation function computation including computation of convolution operations

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Mathematical Optimization (AREA)
  • Mathematical Analysis (AREA)
  • Computational Mathematics (AREA)
  • Pure & Applied Mathematics (AREA)
  • Data Mining & Analysis (AREA)
  • Mathematical Physics (AREA)
  • Theoretical Computer Science (AREA)
  • Computing Systems (AREA)
  • Algebra (AREA)
  • Databases & Information Systems (AREA)
  • Software Systems (AREA)
  • Gears, Cams (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)

Abstract

The invention discloses an engine timing tooth-shaped chain system tooth-shaped matching method based on a collaborative algorithm, and belongs to the technical field of automobile engines. The matching method comprises the following steps: determining a comparison coefficient k based on the tooth width ratio and the positioning relation of the driven sprocket under the tooth form of the set link plate1(ii) a Determining a comparison coefficient k based on the limit of the tooth form of the driving sprocket under the tooth form of the set chain plate2(ii) a Based on cooperative algorithm, by controlling the proportionality coefficient k1And k is2And (4) carrying out secondary adjustment to output the tooth shape parameters. The invention is suitable for timing toothed chain transmission systems in any forms, and can reasonably avoid a series of problems of unreasonable tooth profile caused by the over-poor matching degree of the tooth profile of the system, chain scrapping in advance, chain wheel abrasion in advance, chain elongation too large and pre-tightening failure and the like caused by the fact that the tooth profile of the system cannot be secondarily matched. On the other hand, the method does not need to rely on the experience of designers, thereby reducing the design difficulty and improving the design efficiency.

Description

Engine timing tooth chain system tooth form matching method based on cooperative algorithm
Technical Field
The invention relates to an engine timing tooth-shaped chain system tooth-shaped matching method based on a collaborative algorithm, and belongs to the technical field of automobile engines.
Background
The tooth-shaped chain has been widely applied to the field of engine timing systems of middle and high-end vehicle types at present due to the advantages of light weight under medium and long distance transmission and the advantages of low noise, long service life, high durability and the like under high-speed and heavy-load working conditions.
For timing toothed chain systems of automobile engines, tooth form matching between a chain plate and a driving/driven sprocket is a great technical difficulty. This is because: firstly, the tooth form chain has a multivariate variation characteristic, the parameters involved in the tooth form are numerous, and the parameters show a nonlinear trend, so that the matching relationship between the tooth forms is difficult to describe through a linear equation. Secondly, the matching relationship between the tooth profiles of the chain plate and the sprocket is extremely complex, not only the matching between the chain plate and the driving sprocket, the matching between the chain plate and the driven sprocket, and the matching between the driving sprocket and the driven sprocket, but also the re-matching of the matching relationship.
The traditional tooth form matching method of the timing tooth form chain system of the engine extremely depends on the experience of a designer, and no formula or algorithm is used for effectively ensuring the matching effect. When the tooth form of the chain plate is selected to be too large, the tooth root strength of the driving chain wheel with less tooth number is lower, the driving chain wheel is easy to fatigue and break to cause system failure, and the chain plate shows an undercut phenomenon in appearance; when the tooth form of the link plate is selected to be too small, on one hand, the strength and the wear resistance of the link plate are reduced, so that the chain is lengthened and failed in advance, and on the other hand, the tooth form of the driven sprocket with more teeth is too thick, so that the transmission efficiency is reduced and the material is wasted. When the link joint and the tooth form matching relationship of the driving sprocket and the link joint and the tooth form matching relationship of the driven sprocket cannot be matched for the second time, the quality defects of the whole batch of products can be caused, such as: the chain is scrapped in advance, the chain wheel is worn in advance, and the pre-tightening is failed due to overlarge chain elongation.
The invention discloses a method for designing the tooth form matching of an engine timing sprocket and a timing chain, which only explains the geometrical position relation of the tooth form of a tooth form chain plate and a sprocket based on a 'chain enclosing' and provides a method for drawing the tooth form of the sprocket based on a known chain plate.
Disclosure of Invention
The invention aims to provide a timing toothed chain system tooth form matching method of an engine based on a cooperative algorithm, which is characterized in that the timing toothed chain cooperative algorithm is determined based on the cooperative fit relationship among a chain plate tooth form, a driving chain wheel tooth form and a driven chain wheel tooth form, the problems of too low tooth root strength of a driving chain wheel and unreasonable tooth form of a driven chain wheel in the traditional design method are solved, and the problems of chain early scrapping, chain early abrasion, chain elongation overlarge pre-tightening failure and the like caused by the fact that the chain plate and driving chain wheel tooth form matching relationship and the chain plate and driven chain wheel tooth form matching relationship cannot be secondarily matched are solved.
The technical scheme of the invention is described as follows by combining the attached drawings:
a tooth form matching method of an engine timing tooth form chain system based on a cooperative algorithm comprises the following steps:
step one, determining basic parameters of a system;
specifically, the pitch p of the chain plate is included; the distance f between the edges of the chain plate; number of teeth of driving sprocket z1(ii) a Number of teeth z of driven sprocket2(ii) a Initial value H of half height of chain plate tooth0(ii) a Initial value h of chain plate span height0；
Step twoCalculating a comparison coefficient k according to the positioning relation between the chain plate and the driven chain wheel and by taking the width and the tooth form of the driven chain wheel as a reference2；
The specific positioning relationship between the link plates and the driven sprocket includes: distance h between driven chain wheel relative dividing line and chain pitch linesAnd the width s of the driven sprocket tooth2，
Step three, calculating the radius r of the root circle according to the limit condition of the tooth form of the driving sprocketf1Radius of base circle rb1And the involute has a limit included angle theta1', and calculating a comparison coefficient k based thereon1；
Step four, based on the tooth shape and chain tooth shape cooperation algorithm, the comparison coefficient k is controlled2And k is1Calculating the optimal solution of the half height H of the chain plate teeth and the span height H of the chain plate, thereby completely determining the tooth form of the timing tooth form chain system;
the specific method of the first step is as follows:
firstly, determining a basic pitch p, and then determining a side center distance f according to the following formula:
f＝c·p；
in the formula, p is a chain plate pitch; f is the edge center distance of the chain plate; c is an edge-center distance relation coefficient, and when the span height h of the chain plate is greater than 0, c is 0.4; when the span height h of the chain plate is less than 0, c is 0.355;
the specific method of the second step is as follows:
distance h between driven chain wheel relative dividing line and chain pitch linesThis can be calculated by the following equation:
Figure BDA0003366249760000031
in the formula, p is a chain plate pitch; f is the edge center distance of the chain plate; z is a radical of2The number of teeth of the driven sprocket; alpha is the chain plate tooth form half angle, generally pi/6;
driven sprocket tooth width s2This can be calculated by the following equation:
Figure BDA0003366249760000032
in the formula, p is a chain plate pitch; f is the edge center distance of the chain plate; z is a radical of2The number of teeth of the driven sprocket; alpha is the chain plate tooth form half angle, generally pi/6; h issThe distance between the chain wheel and the pitch line of the chain relative to the dividing line;
comparison coefficient k2The calculation can be made from the following equation:
Figure BDA0003366249760000041
in the formula, H is the half height of the chain plate tooth; h is the span height of the chain plate; s2The tooth width of the driven chain wheel is wide;
the concrete method of the third step is as follows:
root radius r of driving sprocketf1The calculation can be made from the following equation:
Figure BDA0003366249760000042
in the formula, p is a chain plate pitch; z is a radical of1The number of teeth of the driving sprocket; h is half height of the chain plate tooth;
radius r of base circle of driving sprocketb1Can be calculated by the following formula;
Figure BDA0003366249760000043
in the formula, p is a chain plate pitch; z is a radical of1The number of teeth of the driving sprocket; alpha is the chain plate tooth form half angle, generally pi/6;
involute of driving sprocket with limited included angle theta1' can be calculated from the following equation:
Figure BDA0003366249760000044
in the formula, alpha is a chain plate tooth form half angle and is generally pi/6;z1the number of teeth of the driving sprocket; p is the pitch of the chain plate; r isb1The base radius of the driving chain wheel; f is the edge center distance of the chain plate;
comparison coefficient k1The calculation can be made from the following equation:
Figure BDA0003366249760000045
in the formula, rf1The radius of the tooth root of the driving sprocket is the radius; r isb1The base radius of the driving chain wheel; theta1' the involute of the driving sprocket has a limit included angle;
the concrete method of the fourth step is as follows:
for the comparison coefficient k1And k2The following formula should be satisfied:
Figure BDA0003366249760000051
when comparing the coefficient k2>When 0, increasing the span height H of the chain plate, and reducing the half height H of the tooth of the chain plate; when comparing the coefficient k2<When 0, reducing the chain plate span height H, increasing the chain plate tooth half height H, and comparing the coefficient k1<When 0, reducing the half height H of the chain plate teeth;
and outputting the adjusted tooth profile parameters through secondary adjustment based on the cooperation algorithm shown in the figure 3.
The invention has the beneficial effects that:
the invention is suitable for a series of tooth-shaped chain systems with large transmission ratio such as timing tooth-shaped chain transmission systems in any forms, and can reasonably avoid the phenomenon of 'undercut' of the driving sprocket shown in figure 5 and the phenomenon of too thick and unreasonable tooth shape of the driven sprocket shown in figure 6 caused by the over-poor tooth shape matching degree of the timing tooth-shaped chain system; the problems that a chain is scrapped in advance, the chain wheel is worn in advance, the chain is extended too much and pre-tightening fails and the like caused by the fact that the matching relationship of the tooth forms of the chain plate and the driving chain wheel and the matching relationship of the tooth forms of the chain plate and the driven chain wheel cannot be matched for the second time are solved, and therefore the reliability and the wear resistance of a timing tooth-shaped chain system are improved remarkably. Meanwhile, the method does not need design experience, and common engineering technicians can use the method to carry out matching design on the tooth form of the chain plate and chain wheel of the timing system, so that the design difficulty is reduced, and the design efficiency is improved.
Drawings
FIG. 1 shows the tooth form relationship of a link plate and a driven sprocket
FIG. 2 shows the tooth form relationship between the link plate and the driving sprocket
FIG. 3 is a block diagram of a collaborative optimization algorithm
FIG. 4 is a schematic view of a master driven sprocket with a reasonable tooth form
FIG. 5 is a schematic view of the absence of a drive sprocket tooth form
FIG. 6 is a schematic view showing an irrational tooth form of a driven sprocket
Detailed Description
The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
The invention relates to an engine timing tooth form chain system tooth form matching method based on a collaborative algorithm, which specifically comprises the following steps:
step one, determining basic parameters of a system;
specifically, the pitch p of the chain plate is included; the distance f between the edges of the chain plate; number of teeth of driving sprocket z1(ii) a Number of teeth z of driven sprocket2(ii) a Initial value H of half height of chain plate tooth0(ii) a Initial value h of chain plate span height0；
For example, a link plate pitch p of 6.35mm is selected, and a link plate span height h is satisfied00.744mm, the half height of the link plate tooth satisfies H ═ H04.4mm, number of teeth of driving sprocket z123, the number of teeth of the driven sprocket is z2For 46, the edge distance f can be calculated by:
f＝c·p；
in the formula, p is a chain plate pitch; f is the edge center distance of the chain plate; c is an edge-center distance relation coefficient, and when the span height h of the chain plate is greater than 0, c is 0.4; when the span height h of the chain plate is less than 0, c is 0.355;
therefore, the edge center distance f of the chain plate is 2.54 mm;
step two, calculating a comparison coefficient k according to the positioning relation between the chain plate and the driven chain wheel and by taking the width and the tooth form of the driven chain wheel as a reference2；
The specific positioning relationship between the link plates and the driven sprocket includes: distance h between driven chain wheel relative dividing line and chain pitch linesAnd the width s of the driven sprocket tooth2，
Distance h between driven chain wheel relative dividing line and chain pitch linesThis can be calculated by the following equation:
Figure BDA0003366249760000071
in the formula, p is a chain plate pitch; f is the edge center distance of the chain plate; z is a radical of2The number of teeth of the driven sprocket; alpha is the chain plate tooth form half angle, generally pi/6;
according to the result obtained in the step one, the distance h between the relative graduation line of the chain wheel and the pitch line of the chain can be obtaineds＝2.6730mm；
Driven sprocket tooth width s2This can be calculated by the following equation:
Figure BDA0003366249760000072
in the formula, p is a chain plate pitch; f is the edge center distance of the chain plate; z is a radical of2The number of teeth of the driven sprocket; alpha is the chain plate tooth form half angle, generally pi/6; h issThe distance between the chain wheel and the pitch line of the chain relative to the dividing line;
from this, the tooth width s of the driven sprocket can be obtained2＝3.04312mm。
Comparison coefficient k2The calculation can be made from the following equation:
Figure BDA0003366249760000073
in the formula, H is the half height of the chain plate tooth; h is the span height of the chain plate; s2The tooth width of the driven chain wheel is wide;
thus, the coefficient k is compared2＝0.0818；
Step three, calculating the radius r of the root circle according to the limit condition of the tooth form of the driving sprocketf1Radius of base circle rb1And the involute has a limit included angle theta1', and calculating a comparison coefficient k based thereon1；
Root radius r of driving sprocketf1The calculation can be made from the following equation:
Figure BDA0003366249760000074
in the formula, p is a chain plate pitch; z is a radical of1The number of teeth of the driving sprocket; h is half height of the chain plate tooth;
based on the calculation result of the step one, r can be obtained by the formulaf1＝18.4526mm；
Radius r of base circle of driving sprocketb1Can be calculated by the following formula;
Figure BDA0003366249760000081
in the formula, p is a chain plate pitch; z is a radical of1The number of teeth of the driving sprocket; alpha is the chain plate tooth form half angle, generally pi/6;
from this, the base radius r of the drive sprocketb1＝20.1303mm；
Involute of driving sprocket with limited included angle theta1' can be calculated from the following equation:
Figure BDA0003366249760000082
in the formula, alpha is a chain plate tooth form half angle and is generally pi/6; z is a radical of1The number of teeth of the driving sprocket; p is the pitch of the chain plate; r isb1The base radius of the driving chain wheel; f is the edge center distance of the chain plate;
therefore, the involute of the driving sprocket has a limit included angle theta1’＝4.356°；
Comparison coefficient k1The calculation can be made from the following equation:
Figure BDA0003366249760000083
in the formula, rf1The radius of the tooth root of the driving sprocket is the radius; r isb1The base radius of the driving chain wheel; theta1' the involute of the driving sprocket has a limit included angle;
this gives: comparison coefficient k1＝-0.2027；
The concrete method of the fourth step is as follows:
for the comparison coefficient k1And k2The following formula should be satisfied:
Figure BDA0003366249760000084
when comparing the coefficient k2>When 0, increasing the span height H of the chain plate, and reducing the half height H of the tooth of the chain plate; when comparing the coefficient k2<And when 0, reducing the height H of the chain plate span and increasing the half height H of the chain plate tooth. When comparing the coefficient k1<When 0, reducing the half height H of the chain plate teeth;
since at this time k1<0 and k2>0, based on the synergy algorithm as shown in fig. 3, we can obtain:
when the half height H of the chain plate tooth is 3.9mm and the span height H of the chain plate tooth is 0.22mm, k is always present20 and k1＝0.29260；
When the half height H of the chain plate tooth is 4mm and the span height H of the chain plate tooth is 0.32mm, k is always present20 and k1＝0.19353；
When the half height H of the chain plate tooth is 4.1mm and the span height H of the chain plate tooth is 0.42mm, k is always present20 and k1＝0.09446；
The output results all meet the tooth form matching requirements of the timing system;
during the second adjustment, since the computer algorithm and the drawing software have errors, k should be adjusted1The half height H of the chain plate tooth is 3.9mm, and the group of data of the span height H of the chain plate tooth is 0.22mm is reasonable.
The invention has the beneficial effects that:
the invention is suitable for a series of tooth-shaped chain systems with large transmission ratio such as timing tooth-shaped chain transmission systems in any forms, and can reasonably avoid the phenomenon of 'undercut' of the driving sprocket shown in figure 5 and the phenomenon of too thick and unreasonable tooth shape of the driven sprocket shown in figure 6 caused by the over-poor tooth shape matching degree of the timing tooth-shaped chain system; the problems that a chain is scrapped in advance, the chain wheel is worn in advance, the chain is extended too much and pre-tightening fails and the like caused by the fact that the matching relationship of the tooth forms of the chain plate and the driving chain wheel and the matching relationship of the tooth forms of the chain plate and the driven chain wheel cannot be matched for the second time are solved, and therefore the reliability and the wear resistance of a timing tooth-shaped chain system are improved remarkably. Meanwhile, the method does not need design experience, and common engineering technicians can use the method to carry out matching design on the tooth form of the chain plate and chain wheel of the timing system, so that the design difficulty is reduced, and the design efficiency is improved.
Although embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that changes, modifications, substitutions and alterations can be made in these embodiments without departing from the principles and spirit of the invention, the scope of which is defined in the appended claims and their equivalents.

Claims (4)

1. A tooth form matching method of an engine timing tooth form chain system based on a cooperative algorithm is characterized by comprising the following steps:
step one, determining basic parameters of a system;
specifically, the pitch p of the chain plate is included; the distance f between the edges of the chain plate; number of teeth of driving sprocket z1(ii) a Number of teeth z of driven sprocket2(ii) a Initial value H of half height of chain plate tooth0(ii) a Link jointSpan height initial value h0；
Step two, calculating a comparison coefficient k according to the positioning relation between the chain plate and the driven chain wheel and by taking the width and the tooth form of the driven chain wheel as a reference2；
The specific positioning relationship between the link plates and the driven sprocket includes: distance h between driven chain wheel relative dividing line and chain pitch linesAnd the width s of the driven sprocket tooth2；
Step three, calculating the radius r of the root circle according to the limit condition of the tooth form of the driving sprocketf1Radius of base circle rb1And the involute has a limit included angle theta1', and calculating a comparison coefficient k based thereon1；
Step four, based on the tooth shape and chain tooth shape cooperation algorithm, the comparison coefficient k is controlled2And k is1And (3) calculating the optimal solution of the half height H of the chain plate tooth and the span height H of the chain plate, so that the tooth form of the timing tooth form chain system can be completely determined.
2. The engine timing toothed chain system tooth form matching method based on the cooperative algorithm as claimed in claim 1, characterized in that: in the second step, the distance h between the driven chain wheel and the pitch line of the chain relative to the index linesThis can be calculated by the following equation:
Figure FDA0003366249750000011
in the formula, p is a chain plate pitch; f is the edge center distance of the chain plate; z is a radical of2The number of teeth of the driven sprocket; alpha is the chain plate tooth form half angle, generally pi/6;
driven sprocket tooth width s2This can be calculated by the following equation:
Figure FDA0003366249750000021
in the formula, p is a chain plate pitch; f is the edge center distance of the chain plate; z is a radical of2For driven sprocket teethCounting; alpha is the chain plate tooth form half angle, generally pi/6; h issThe distance between the chain wheel and the pitch line of the chain relative to the dividing line;
comparison coefficient k2The calculation can be made from the following equation:
Figure FDA0003366249750000022
in the formula, H is the half height of the chain plate tooth; h is the span height of the chain plate; s2The width of the driven sprocket teeth.
3. The engine timing toothed chain system tooth form matching method based on the cooperative algorithm as claimed in claim 1, characterized in that: in the third step, the radius r of the root circle of the driving sprocketf1The calculation can be made from the following equation:
Figure FDA0003366249750000023
in the formula, p is a chain plate pitch; z is a radical of1The number of teeth of the driving sprocket; h is half height of the chain plate tooth;
involute of driving sprocket with limited included angle theta1' can be calculated from the following equation:
Figure FDA0003366249750000024
in the formula, alpha is a chain plate tooth form half angle and is generally pi/6; z is a radical of1The number of teeth of the driving sprocket; p is the pitch of the chain plate; r isb1The base radius of the driving chain wheel; f is the edge center distance of the chain plate;
comparison coefficient k1The calculation can be made from the following equation:
Figure FDA0003366249750000025
in the formula, rf1The radius of the tooth root of the driving sprocket is the radius; r isb1The base radius of the driving chain wheel; theta1' A limit included angle exists for the involute of the driving chain wheel.
4. The engine timing toothed chain system tooth form matching method based on the cooperative algorithm as claimed in claim 1, characterized in that: in the fourth step, for the comparison coefficient k1And k2The following formula should be satisfied:
Figure FDA0003366249750000031
when comparing the coefficient k2>When 0, increasing the span height H of the chain plate, and reducing the half height H of the tooth of the chain plate; when comparing the coefficient k2<When 0, reducing the chain plate span height H, increasing the chain plate tooth half height H, and comparing the coefficient k1<And when 0, reducing the half height H of the chain plate teeth.
CN202111382838.8A 2021-11-22 2021-11-22 Tooth form matching method of engine timing tooth form chain system based on cooperative algorithm Active CN114001145B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202111382838.8A CN114001145B (en) 2021-11-22 2021-11-22 Tooth form matching method of engine timing tooth form chain system based on cooperative algorithm

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202111382838.8A CN114001145B (en) 2021-11-22 2021-11-22 Tooth form matching method of engine timing tooth form chain system based on cooperative algorithm

Publications (2)

Publication Number Publication Date
CN114001145A true CN114001145A (en) 2022-02-01
CN114001145B CN114001145B (en) 2024-03-19

Family

ID=79929608

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202111382838.8A Active CN114001145B (en) 2021-11-22 2021-11-22 Tooth form matching method of engine timing tooth form chain system based on cooperative algorithm

Country Status (1)

Country Link
CN (1) CN114001145B (en)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0886085A1 (en) * 1997-06-18 1998-12-23 Morse Tec Europe S.p.A. Sprocket wheel with improved tooth profile for greater silentness
CN104019198A (en) * 2014-06-17 2014-09-03 吉林大学 Asymmetrical tooth profile chain two-phase transmission system
CN107747614A (en) * 2017-11-22 2018-03-02 吉林大学 A kind of complex phase chain drive system of single helical teeth
US20200166105A1 (en) * 2018-11-28 2020-05-28 Tsubakimoto Chain Co. Chain drive mechanism
CN112610664A (en) * 2020-11-25 2021-04-06 青岛征和工业股份有限公司 Motorcycle rear drive transmission is with silence drive chain system and motorcycle

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0886085A1 (en) * 1997-06-18 1998-12-23 Morse Tec Europe S.p.A. Sprocket wheel with improved tooth profile for greater silentness
CN104019198A (en) * 2014-06-17 2014-09-03 吉林大学 Asymmetrical tooth profile chain two-phase transmission system
CN107747614A (en) * 2017-11-22 2018-03-02 吉林大学 A kind of complex phase chain drive system of single helical teeth
US20200166105A1 (en) * 2018-11-28 2020-05-28 Tsubakimoto Chain Co. Chain drive mechanism
CN112610664A (en) * 2020-11-25 2021-04-06 青岛征和工业股份有限公司 Motorcycle rear drive transmission is with silence drive chain system and motorcycle

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
庞景元: "某V12汽油发动机正时齿形链传动系统的设计及动力学分析", 全国优秀硕士论文全文数据库 工程科技II辑, no. 2016, 15 September 2016 (2016-09-15) *
杨金兴: "汽油发动机正时齿形链传动系统的设计与动力学分析", 全国优秀硕士论文全文数据库 工程科技II辑, no. 2019, 15 November 2019 (2019-11-15) *

Also Published As

Publication number Publication date
CN114001145B (en) 2024-03-19

Similar Documents

Publication Publication Date Title
US7442139B2 (en) Conveyance system
US9802352B2 (en) Extruder screw, extruder, and method for producing an extruder screw
JP5160444B2 (en) Silent chain with high strength and rigidity with improved noise
US20060068959A1 (en) Inverted tooth chain system with inside flank engagement
JP5027825B2 (en) Toothed chain with optimized chain joint and enlarged external flank angle
CN102144111B (en) Inverted tooth chain and chain sprocket drive system with reduced meshing impact
US20080096709A1 (en) Chain transmission device
CN108662115B (en) Multi-objective optimization design method for profile modification of cycloidal gear tooth profile
US9003758B2 (en) Low-waste method for producing high-performance chain link plates
WO2016197905A1 (en) Gear-cutting hob and designing method therefor, and non-fully-symmetric involute gear and machining method therefor
CN102753857B (en) Inverted tooth chain and sprocket drive system with reduced meshing impact
US20010045773A1 (en) Drive sprocket wheel for a track vehicle
CA2259391A1 (en) Random engagement roller chain sprocket having improved noise characteristics
US20110287883A1 (en) Non-Circular Joint Openings in Toothed Plates of Silent Chains
US4147069A (en) Geared belt for positive drive transmission
US20070087878A1 (en) Standard sprocket for chain
CN109376456A (en) Contact force contact performance numerical computation method of the spiral bevel gear containing installation error
CN110704968A (en) RV reducer multi-target optimization method based on cycloidal gear tooth profile modification
CN114001145A (en) Engine timing tooth chain system tooth form matching method based on cooperative algorithm
CN110083939B (en) Pure electric vehicle differential gear modification optimization method
JP3786982B2 (en) Gear tooth surface modification method
CN101334089B (en) Silent chain with asymmetric involute profile
JP2004013797A (en) Curve interpolation method by circular arc, numerical value control device using the same, design supporting device and analysis supporting device
JPH05340463A (en) Tooth shape correction method for spur gear and tooth shape correction spur gear pair
CN108757438B (en) Full-smooth screw rotor with small enclosed volume and design method thereof

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant