CN114001145B - Tooth form matching method of engine timing tooth form chain system based on cooperative algorithm - Google Patents
Tooth form matching method of engine timing tooth form chain system based on cooperative algorithm Download PDFInfo
- Publication number
- CN114001145B CN114001145B CN202111382838.8A CN202111382838A CN114001145B CN 114001145 B CN114001145 B CN 114001145B CN 202111382838 A CN202111382838 A CN 202111382838A CN 114001145 B CN114001145 B CN 114001145B
- Authority
- CN
- China
- Prior art keywords
- chain
- tooth
- teeth
- chain plate
- 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.)
- Active
Links
- 238000000034 method Methods 0.000 title claims abstract description 35
- 238000004364 calculation method Methods 0.000 claims description 18
- 230000005540 biological transmission Effects 0.000 abstract description 7
- 238000005299 abrasion Methods 0.000 abstract description 4
- 230000002028 premature Effects 0.000 abstract 2
- 208000035874 Excoriation Diseases 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000004075 alteration Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
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
Abstract
The invention discloses a tooth form matching method of an engine timing tooth form chain system based on a cooperative 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 ratio of the tooth widths of the driven sprockets and the positioning relationship under the tooth shape of a given chain plate 1 The method comprises the steps of carrying out a first treatment on the surface of the Determining a comparison coefficient k based on the limit of the tooth shape of the driving sprocket under the given tooth shape of the chain plate 2 The method comprises the steps of carrying out a first treatment on the surface of the Based on a collaborative algorithm, by controlling the proportionality coefficient k 1 And k is equal to 2 And through secondary adjustment, the tooth profile parameters are output. The invention is suitable for any form of timing toothed chain transmission system, and can reasonably avoid a series of problems of unreasonable tooth profile caused by too poor matching degree of the tooth profile of the system, premature scrapping of the chain, premature abrasion of a chain wheel, excessive pre-tightening failure of chain elongation and the like caused by the fact that the tooth profile of the system cannot be matched secondarily. On the other hand, the method does not depend on experience of a designer, so that design difficulty is reduced and design efficiency is improved.
Description
Technical Field
The invention relates to a tooth form matching method of an engine timing tooth form chain system based on a cooperative algorithm, and belongs to the technical field of automobile engines.
Background
The toothed chain has been widely used in the field of engine timing systems of medium-high-end vehicles because of the light weight advantage of the toothed chain under medium-long distance transmission, low noise, long service life, high durability and the like under high-speed heavy-load working conditions.
For automotive engine timing toothed chain systems, the tooth matching between the link plates and the driving/driven sprocket is a great technical difficulty. This is because: firstly, a tooth-shaped chain has a multiple variation characteristic, the parameters related to tooth shapes are numerous, the parameters show a nonlinear trend, and the matching relation between the tooth shapes is difficult to describe through a linear equation. Secondly, the matching relationship between the chain plate and the tooth form of the chain wheel is extremely complex, and the matching relationship is not only the matching between the chain plate and the driving chain wheel, the matching between the chain plate and the driven chain wheel and the matching between the driving chain wheel and the driven chain wheel, but also the re-matching of the matching relationship.
The traditional tooth profile matching method of the engine timing tooth profile chain system is extremely dependent on experience of a designer, and no formula or algorithm is used for effectively guaranteeing the matching effect. When the tooth shape of the chain plate is excessively large, the tooth strength of the tooth root of the driving chain wheel with fewer teeth is lower, the system is easy to fail due to fatigue fracture, and the root cutting phenomenon is shown on the appearance; when the tooth form of the chain plate is too small, on one hand, the strength and the wear resistance of the chain plate are reduced, so that the chain is lengthened and disabled in advance, and on the other hand, the tooth form of the driven chain wheel with more tooth numbers is too thick, so that the transmission efficiency is reduced and the material is wasted. When the matching relationship between the chain plate and the tooth form of the driving chain wheel and the matching relationship between the chain plate and the tooth form of the driven chain wheel can not be matched secondarily, 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 failure is caused by excessive elongation of the chain.
The present Chinese patent CN106446457A relates to a design method for matching the tooth form of a timing chain wheel and a timing chain of an engine, and the invention only explains the geometric position relation of the tooth form of a chain wheel tooth form of a tooth-shaped chain plate of a 'surrounding chain' based on the invention, and provides a method for drawing the tooth form of the chain wheel based on the known chain plate, but the method is not based on the tooth form chain meshing principle, does not consider the proportion problem of the tooth form of a driving chain wheel and a driven chain wheel, and does not consider the tooth form strength and tooth form parameter coordination problem, so the actual engineering problem cannot be solved.
Disclosure of Invention
The invention aims to provide a tooth profile matching method of an engine timing toothed chain system based on a cooperative algorithm, which is used for determining the cooperative algorithm of the timing toothed chain based on the cooperative cooperation relationship among the tooth profile of a chain plate, the tooth profile of a driving sprocket and the tooth profile of a driven sprocket, solving the problems of excessively low tooth root strength of the driving sprocket and unreasonable tooth profile of the driven sprocket which occur under the traditional design method, and solving the problems of early rejection, early abrasion of the sprocket, excessively large chain elongation, failure of pre-tightening and the like of a chain caused by the fact that the tooth profile matching relationship between the chain plate and the driving sprocket cannot be matched secondarily with the tooth profile matching relationship between the chain plate and the driven sprocket.
The technical scheme of the invention is as follows in combination with the accompanying 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 comprises a chain plate pitch p; the edge center distance f of the chain plate; tooth number z of driving sprocket 1 The method comprises the steps of carrying out a first treatment on the surface of the Driven sprocket tooth number z 2 The method comprises the steps of carrying out a first treatment on the surface of the Half-height initial value H of chain plate tooth 0 The method comprises the steps of carrying out a first treatment on the surface of the Initial value h of chain plate crossing height 0 ；
Step two, calculating a comparison coefficient k according to the positioning relation between the chain plate and the driven sprocket and taking the wide tooth form of the driven sprocket as a reference 2 ；
The specific positioning relationship between the link plate and the driven sprocket includes: distance h between driven sprocket relative to index line and chain pitch line s And the tooth width s of the driven sprocket 2 ，
Step three, calculating the radius r of the root circle according to the limit condition of the tooth form of the driving sprocket f1 Radius of base circle r b1 And the involute has a limit included angle theta 1 ' and calculate the comparison coefficient k based thereon 1 ；
Step four, based on tooth-shaped chain tooth cooperative algorithm, comparing coefficient k by controlling 2 And k is equal to 1 Calculating the optimal solution of half height H of the chain plate teeth and the span height H of the chain plate, so that the tooth shape of the timing tooth-shaped chain system can be completely determined;
the specific method of the first step is as follows:
the basic pitch p is determined first, and then the edge center distance f is determined according to the following formula:
f＝c·p；
wherein p is the pitch of the link plate; f is the edge center distance of the chain plate; c is an edge-center distance relationship coefficient, and c=0.4 when the span height h of the chain plate is greater than 0; c=0.355 when the link plate span height h < 0;
the specific method of the second step is as follows:
distance h between driven sprocket relative to index line and chain pitch line s The calculation can be made by the following formula:
wherein p is the pitch of the link plate; f is the edge center distance of the chain plate; z 2 The number of teeth of the driven sprocket wheel is the number of teeth; alpha is the half angle of the tooth form of the chain plate, and pi/6 is generally taken;
driven sprocket tooth width s 2 The calculation can be made by the following formula:
wherein p is the pitch of the link plate; f is the edge center distance of the chain plate; z 2 The number of teeth of the driven sprocket wheel is the number of teeth; alpha is the half angle of the tooth form of the chain plate, and pi/6 is generally taken; h is a s Is the distance between the chain wheel relative to the index line and the chain pitch line;
comparing coefficient k 2 The calculation can be performed by the following formula:
in the middle ofH is half height of the chain plate teeth; h is the span height of the chain plate; s is(s) 2 Is the tooth width of the driven sprocket;
the specific method of the third step is as follows:
radius r of tooth root of driving sprocket f1 The calculation can be performed by the following formula:
wherein p is the pitch of the link plate; z 1 The number of teeth of the driving chain wheel is the number of teeth; h is half height of the chain plate teeth;
base radius r of drive sprocket b1 The calculation can be performed by the following formula;
wherein p is the pitch of the link plate; z 1 The number of teeth of the driving chain wheel is the number of teeth; alpha is the half angle of the tooth form of the chain plate, and pi/6 is generally taken;
limit included angle theta exists on involute of driving sprocket 1 ' may be calculated by the following formula:
wherein alpha is the half angle of the tooth form of the chain plate, and pi/6 is generally taken; z 1 The number of teeth of the driving chain wheel is the number of teeth; p is the pitch of the link plate; r is (r) b1 The radius of the base circle of the driving sprocket; f is the edge center distance of the chain plate;
comparing coefficient k 1 The calculation can be performed by the following formula:
wherein r is f1 Is the root radius of the active sprocket teeth; r is (r) b1 The radius of the base circle of the driving sprocket; θ 1 ' is that the involute of the driving sprocket has a limit included angle;
the specific method of the fourth step is as follows:
for comparison coefficient k 1 And k 2 The following formula should be satisfied:
when comparing coefficient k 2 >When 0, increasing the span height H of the chain plate and reducing the half height H of the teeth of the chain plate; when comparing coefficient k 2 <When 0, the span height H of the chain plate is reduced, the half height H of the chain plate teeth is increased, and when the coefficient k is compared 1 <When 0, reducing half height H of the chain plate teeth;
based on the collaborative algorithm shown in fig. 3, the tooth profile parameters after adjustment are output after secondary adjustment.
The beneficial effects of the invention are as follows:
the invention is suitable for a series of large transmission ratio toothed chain systems such as any form of timing toothed chain transmission system, and can reasonably avoid the phenomenon of 'undercut' of a driving sprocket shown in figure 5 and the phenomenon of unreasonable tooth profile of a driven sprocket shown in figure 6 caused by too poor tooth profile matching degree of the timing toothed chain system; the problems of advanced scrapping of the chain, advanced abrasion of the chain wheel, excessive chain elongation, pre-tightening failure and the like caused by the fact that the matching relationship between the chain plate and the tooth form of the driving chain wheel is not matched with the matching relationship between the chain plate and the tooth form of the driven chain wheel can be solved effectively, and therefore reliability and wear resistance of the timing tooth-shaped chain system are improved remarkably. Meanwhile, the method does not need to help design experience, and common engineering technicians can use the method to carry out matched design on the tooth shape of the chain plate chain wheel of the timing system, so that the design difficulty is reduced and the design efficiency is improved.
Drawings
FIG. 1 is a tooth form relationship of a link plate to a driven sprocket
FIG. 2 is a tooth form relationship of a link plate to a drive sprocket
FIG. 3 is a block diagram of a collaborative optimization algorithm
FIG. 4 is a schematic diagram of a reasonably toothed master-slave sprocket
FIG. 5 is a schematic view of the absence of a drive sprocket tooth form
FIG. 6 is a schematic view of unreasonable tooth form of driven sprocket
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
The invention relates to a tooth profile matching method of an engine timing tooth profile chain system based on a cooperative algorithm, which specifically comprises the following steps:
step one, determining basic parameters of a system;
specifically comprises a chain plate pitch p; the edge center distance f of the chain plate; tooth number z of driving sprocket 1 The method comprises the steps of carrying out a first treatment on the surface of the Driven sprocket tooth number z 2 The method comprises the steps of carrying out a first treatment on the surface of the Half-height initial value H of chain plate tooth 0 The method comprises the steps of carrying out a first treatment on the surface of the Initial value h of chain plate crossing height 0 ；
For example, the pitch p of the link plate is selected to be 6.35mm, and the link plate span height satisfies h=h 0 =0.744 mm, the half height of the link plate teeth satisfying h=h 0 =4.4mm, drive sprocket tooth number z 1 =23, the number of teeth of the driven sprocket is z 2 =46, the edge-center distance f is calculated by:
f＝c·p；
wherein p is the pitch of the link plate; f is the edge center distance of the chain plate; c is an edge-center distance relationship coefficient, and c=0.4 when the span height h of the chain plate is greater than 0; c=0.355 when the link plate span height h < 0;
as a result, the pitch f=2.54 mm of the link plate edge;
step two, calculating a comparison coefficient k according to the positioning relation between the chain plate and the driven sprocket and taking the wide tooth form of the driven sprocket as a reference 2 ；
The specific positioning relationship between the link plate and the driven sprocket includes: distance h between driven sprocket relative to index line and chain pitch line s And the tooth width s of the driven sprocket 2 ，
Driven sprocket relative toDistance h between index line and chain pitch line s The calculation can be made by the following formula:
wherein p is the pitch of the link plate; f is the edge center distance of the chain plate; z 2 The number of teeth of the driven sprocket wheel is the number of teeth; alpha is the half angle of the tooth form of the chain plate, and pi/6 is generally taken;
from the result of the first step, the distance h between the chain wheel relative to the index line and the chain pitch line can be obtained s ＝2.6730mm；
Driven sprocket tooth width s 2 The calculation can be made by the following formula:
wherein p is the pitch of the link plate; f is the edge center distance of the chain plate; z 2 The number of teeth of the driven sprocket wheel is the number of teeth; alpha is the half angle of the tooth form of the chain plate, and pi/6 is generally taken; h is a s Is the distance between the chain wheel relative to the index line and the chain pitch line;
from this, the tooth width s of the driven sprocket 2 ＝3.04312mm。
Comparing coefficient k 2 The calculation can be performed by the following formula:
wherein H is half height of the chain plate teeth; h is the span height of the chain plate; s is(s) 2 Is the tooth width of the driven sprocket;
from this, the comparison coefficient k 2 ＝0.0818；
Step three, calculating the radius r of the root circle according to the limit condition of the tooth form of the driving sprocket f1 Radius of base circle r b1 And the involute has a limit included angle theta 1 ' and calculate the comparison coefficient k based thereon 1 ；
Radius r of tooth root of driving sprocket f1 The calculation can be performed by the following formula:
wherein p is the pitch of the link plate; z 1 The number of teeth of the driving chain wheel is the number of teeth; h is half height of the chain plate teeth;
based on the calculation result of the step one, r is obtained by the above formula f1 ＝18.4526mm；
Base radius r of drive sprocket b1 The calculation can be performed by the following formula;
wherein p is the pitch of the link plate; z 1 The number of teeth of the driving chain wheel is the number of teeth; alpha is the half angle of the tooth form of the chain plate, and pi/6 is generally taken;
from this, the base radius r of the drive sprocket b1 ＝20.1303mm；
Limit included angle theta exists on involute of driving sprocket 1 ' may be calculated by the following formula:
wherein alpha is the half angle of the tooth form of the chain plate, and pi/6 is generally taken; z 1 The number of teeth of the driving chain wheel is the number of teeth; p is the pitch of the link plate; r is (r) b1 The radius of the base circle of the driving sprocket; f is the edge center distance of the chain plate;
it can be obtained that the involute of the driving sprocket has a limit included angle theta 1 ’＝4.356°；
Comparing coefficient k 1 The calculation can be performed by the following formula:
wherein r is f1 Is the root radius of the active sprocket teeth; r is (r) b1 The radius of the base circle of the driving sprocket; θ 1 ' is that the involute of the driving sprocket has a limit included angle;
this can be achieved by: comparing coefficient k 1 ＝-0.2027；
The specific method of the fourth step is as follows:
for comparison coefficient k 1 And k 2 The following formula should be satisfied:
when comparing coefficient k 2 >When 0, increasing the span height H of the chain plate and reducing the half height H of the teeth of the chain plate; when comparing coefficient k 2 <And when 0, the span height H of the chain plate is reduced, and the half height H of the chain plate teeth is increased. When comparing coefficient k 1 <When 0, reducing half height H of the chain plate teeth;
due to the fact that at this time k 1 <0 and k 2 >0, based on the collaborative algorithm as shown in fig. 3, can be obtained:
when the half height h=3.9 mm of the link plate teeth and the span height h=0.22 mm of the link plate teeth, k is always present 2 =0 and k 1 ＝0.29260；
When the half height H=4mm of the link plate teeth and the span height h=0.32 mm of the link plate teeth, there is always k 2 =0 and k 1 ＝0.19353；
When the half height h=4.1 mm of the link plate teeth and the span height h=0.42 mm of the link plate teeth, k is always present 2 =0 and k 1 ＝0.09446；
The output results meet the tooth form matching requirement of the timing system;
during secondary adjustment, since errors occur in the computer algorithm and the drawing software, k should be made 1 The data of the half height H=3.9 mm of the chain plate teeth and the span height h=0.22 mm of the chain plate teeth are reasonable.
The beneficial effects of the invention are as follows:
the invention is suitable for a series of large transmission ratio toothed chain systems such as any form of timing toothed chain transmission system, and can reasonably avoid the phenomenon of 'undercut' of a driving sprocket shown in figure 5 and the phenomenon of unreasonable tooth profile of a driven sprocket shown in figure 6 caused by too poor tooth profile matching degree of the timing toothed chain system; the problems of advanced scrapping of the chain, advanced abrasion of the chain wheel, excessive chain elongation, pre-tightening failure and the like caused by the fact that the matching relationship between the chain plate and the tooth form of the driving chain wheel is not matched with the matching relationship between the chain plate and the tooth form of the driven chain wheel can be solved effectively, and therefore reliability and wear resistance of the timing tooth-shaped chain system are improved remarkably. Meanwhile, the method does not need to help design experience, and common engineering technicians can use the method to carry out matched design on the tooth shape of the chain plate 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 understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made therein without departing from the principles and spirit of the invention, the scope of which is defined in the appended claims and their equivalents.
Claims (1)
1. The tooth profile matching method of the engine timing tooth profile chain system based on the cooperative algorithm is characterized by comprising the following steps of:
step one, determining basic parameters of a system;
specifically comprises a chain plate pitch p; the edge center distance f of the chain plate; tooth number z of driving sprocket 1 The method comprises the steps of carrying out a first treatment on the surface of the Driven sprocket tooth number z 2 The method comprises the steps of carrying out a first treatment on the surface of the Half-height initial value H of chain plate tooth 0 The method comprises the steps of carrying out a first treatment on the surface of the Initial value h of chain plate crossing height 0 ；
Step two, calculating a comparison coefficient k according to the positioning relation between the chain plate and the driven sprocket and taking the wide tooth form of the driven sprocket as a reference 2 ；
The specific positioning relationship between the link plate and the driven sprocket includes: distance h between driven sprocket relative to index line and chain pitch line s And the tooth width s of the driven sprocket 2 ；
Step three, calculating the radius r of the root circle according to the limit condition of the tooth form of the driving sprocket f1 Radius of base circle r b1 And the involute has a limit included angle theta 1 ' and calculate therefromComparing coefficient k 1 ；
Step four, based on tooth-shaped chain tooth cooperative algorithm, comparing coefficient k by controlling 2 And k is equal to 1 Calculating the optimal solution of half height H of the chain plate teeth and the span height H of the chain plate, so that the tooth shape of the timing tooth-shaped chain system can be completely determined;
in the second step, the driven sprocket is positioned at a distance h from the index line to the chain pitch line s The calculation can be made by the following formula:
wherein p is the pitch of the link plate; f is the edge center distance of the chain plate; z 2 The number of teeth of the driven sprocket wheel is the number of teeth; alpha is the half angle of the tooth form of the chain plate, and pi/6 is generally taken;
driven sprocket tooth width s 2 The calculation can be made by the following formula:
wherein p is the pitch of the link plate; f is the edge center distance of the chain plate; z 2 The number of teeth of the driven sprocket wheel is the number of teeth; alpha is the half angle of the tooth form of the chain plate, and pi/6 is generally taken; h is a s Is the distance between the chain wheel relative to the index line and the chain pitch line;
comparing coefficient k 2 The calculation can be performed by the following formula:
wherein H is half height of the chain plate teeth; h is the span height of the chain plate; s is(s) 2 Is the tooth width of the driven sprocket;
in the third step, the radius r of the root circle of the driving sprocket f1 The calculation can be performed by the following formula:
wherein p is the pitch of the link plate; z 1 The number of teeth of the driving chain wheel is the number of teeth; h is half height of the chain plate teeth;
limit included angle theta exists on involute of driving sprocket 1 ' may be calculated by the following formula:
wherein alpha is the half angle of the tooth form of the chain plate, and pi/6 is generally taken; z 1 The number of teeth of the driving chain wheel is the number of teeth; p is the pitch of the link plate; r is (r) b1 The radius of the base circle of the driving sprocket; f is the edge center distance of the chain plate;
comparing coefficient k 1 The calculation can be performed by the following formula:
wherein r is f1 Is the root radius of the active sprocket teeth; r is (r) b1 The radius of the base circle of the driving sprocket; θ 1 ' is that the involute of the driving sprocket has a limit included angle;
in the fourth step, for the comparison coefficient k 1 And k 2 The following formula should be satisfied:
when comparing coefficient k 2 >When 0, increasing the span height H of the chain plate and reducing the half height H of the teeth of the chain plate; when comparing coefficient k 2 <When 0, the span height H of the chain plate is reduced, the half height H of the chain plate teeth is increased, and when the coefficient k is compared 1 <And 0, reducing the half height H of the chain plate teeth.
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 CN114001145A (en) | 2022-02-01 |
| CN114001145B true 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 (4)
| 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 |
| 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 |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP7260738B2 (en) * | 2018-11-28 | 2023-04-19 | 株式会社椿本チエイン | chain transmission mechanism |
-
2021
- 2021-11-22 CN CN202111382838.8A patent/CN114001145B/en active Active
Patent Citations (4)
| 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 |
| 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)
| Title |
|---|
| 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;庞景元;全国优秀硕士论文全文数据库 工程科技II辑;20160915(2016年第09期);全文 * |
| 汽油发动机正时齿形链传动系统的设计与动力学分析;杨金兴;全国优秀硕士论文全文数据库 工程科技II辑;20191115(2019年第11期);全文 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN114001145A (en) | 2022-02-01 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP3552234B2 (en) | Gear designing method, gear manufacturing method, and gear manufactured by the manufacturing method | |
| EP1873420B1 (en) | Gear with cornu's spiral tooth profile | |
| JP4201784B2 (en) | Silent chain for direct injection engine | |
| US9003758B2 (en) | Low-waste method for producing high-performance chain link plates | |
| JP2009519426A (en) | Silent chain with high strength and rigidity with improved noise | |
| US8550946B2 (en) | Non-circular joint openings in toothed plates of silent chains | |
| US6796920B2 (en) | Silent chain power transmission apparatus | |
| US6461263B2 (en) | Silent chain drive mechanism | |
| CN106369139A (en) | Method for obtaining machining parameters of hypoid gear meeting high-order transmission error | |
| US6533107B2 (en) | Silent chain power transmitting apparatus | |
| CN101010525A (en) | Inverted tooth chain sprocket with frequency modulated meshing | |
| US6595603B2 (en) | Drive sprocket wheel for a track vehicle | |
| CN104889505B (en) | Asymmetric hobboing cutter and its design method | |
| WO2016197905A1 (en) | Gear-cutting hob and designing method therefor, and non-fully-symmetric involute gear and machining method therefor | |
| CN114001145B (en) | Tooth form matching method of engine timing tooth form chain system based on cooperative algorithm | |
| EP1803974A2 (en) | Gear wheel with chamfered portions | |
| US4147069A (en) | Geared belt for positive drive transmission | |
| CN109084006B (en) | Trigonometric function shape modifying method for cycloid gear and cycloid pin gear speed reducer | |
| CN111322373B (en) | Gear pair design method based on claw helix rack knife | |
| CN111299982B (en) | Shape-modifying machining process for gear of agricultural machine | |
| JP3914799B2 (en) | Power transmission chain and sprocket assembly | |
| EP1426655A2 (en) | A silent chain for restraining chordal action | |
| CN108775376A (en) | A kind of straight bevel gear is secondary and its axial modification method | |
| JP3786982B2 (en) | Gear tooth surface modification method | |
| GB2445645A (en) | Silent chain link plate having a protruding surface and a retracted surface |
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 |