JPS635620B2 - - Google Patents
Info
- Publication number
- JPS635620B2 JPS635620B2 JP27513584A JP27513584A JPS635620B2 JP S635620 B2 JPS635620 B2 JP S635620B2 JP 27513584 A JP27513584 A JP 27513584A JP 27513584 A JP27513584 A JP 27513584A JP S635620 B2 JPS635620 B2 JP S635620B2
- Authority
- JP
- Japan
- Prior art keywords
- timing belt
- string
- vibration resonance
- engine
- timing
- 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
Links
- 238000004804 winding Methods 0.000 claims description 7
- 230000000694 effects Effects 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 1
- 230000001747 exhibiting effect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 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
- F16H7/00—Gearings for conveying rotary motion by endless flexible members
- F16H7/02—Gearings for conveying rotary motion by endless flexible members with belts; with V-belts
- F16H7/023—Gearings for conveying rotary motion by endless flexible members with belts; with V-belts with belts having a toothed contact surface or regularly spaced bosses or hollows for slipless or nearly slipless meshing with complementary profiled contact surface of a pulley
-
- 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
- F16H7/08—Means for varying tension of belts, ropes or chains
- F16H7/10—Means for varying tension of belts, ropes or chains by adjusting the axis of a pulley
- F16H7/12—Means for varying tension of belts, ropes or chains by adjusting the axis of a pulley of an idle pulley
- F16H7/1254—Means for varying tension of belts, ropes or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
Description
【発明の詳細な説明】
Ａ 発明の目的
(1) 産業上の利用分野
本発明は、クランク軸に固定される駆動プーリ
と、カム軸に固定されるカムプーリとに無端状タ
イミングベルトが卷回されるとともに、前記両プ
ーリ間でタイミングベルトが被駆動輪に巻掛けら
れる車両用エンジンのタイミングベルト巻掛装置
に関する。[Detailed Description of the Invention] A. Purpose of the Invention (1) Field of Industrial Application The present invention provides a method in which an endless timing belt is wound around a drive pulley fixed to a crankshaft and a cam pulley fixed to a camshaft. The present invention also relates to a timing belt winding device for a vehicle engine, in which a timing belt is wound around a driven wheel between both pulleys.
(2) 従来の技術
従来、かかるタイミングベルト巻掛装置では、
被駆動輪として、タイミングベルトの張力を調節
するためのテンシヨナを駆動プーリおよびカムプ
ーリ間に設けている。 (2) Conventional technology Conventionally, in such a timing belt winding device,
As a driven wheel, a tensioner for adjusting the tension of the timing belt is provided between the drive pulley and the cam pulley.
(3) 発明が解決しようとする問題点
上記タイミングベルト巻掛装置では、エンジン
の高速回転化およびDOHC化に伴うカム軸の駆
動力の増大化等により、タイミングベルトの張力
が増大化している。ところが、このタイミングベ
ルトの張力の増大に伴つて、テンシヨナ前後での
タイミングベルトの弦振動による騒音が大きくな
つており、従来これに有効に対処する手段は実現
されていない。 (3) Problems to be Solved by the Invention In the above-mentioned timing belt winding device, the tension of the timing belt is increasing due to an increase in the driving force of the camshaft due to higher rotational speed of the engine and the use of DOHC. However, as the tension of the timing belt increases, the noise caused by string vibration of the timing belt before and after the tensioner increases, and no means to effectively deal with this problem has been realized so far.
本発明は、かかる事情に鑑みてなされたもので
あり、被駆動輪の前後でのタイミングベルトの弦
振動に起因した騒音の低減を図つた車両用エンジ
ンのタイミングベルト巻掛装置を提供することを
目的とする。 The present invention has been made in view of the above circumstances, and it is an object of the present invention to provide a timing belt winding device for a vehicle engine that is capable of reducing noise caused by string vibration of a timing belt before and after a driven wheel. purpose.
Ｂ 発明の構成
(1) 問題点を解決するための手段
本発明によれば、タイミングベルトの弦長を
ｌ、タイミングベルトの幅および張力によつて定
まる定数をＫ、タイミングベルトの弦振動共振周
を、fr＝Ｋ／2lとしたときに、被駆動輪の前後の
タイミングベルトの弦振動共振周波数fr1，fr2が
｜fr1−fr2｜≠０なる関係を有する。B. Structure of the Invention (1) Means for Solving Problems According to the present invention, the string length of the timing belt is l, the constant determined by the width and tension of the timing belt is K, and the string vibration resonance frequency of the timing belt is When fr=K/2l, the string vibration resonance frequencies fr 1 and fr 2 of the timing belts before and after the driven wheels have a relationship of |fr 1 −fr 2 |≠0.
(2) 作用
｜fr1−fr2｜≠０とすることにより、被駆動輪
の前後でのタイミングベルトの振動の抑制および
騒音増大側への相互の影響排除を図り、もつて騒
音の低減化が可能となる。 (2) Effect By setting ｜fr 1 −fr 2 ｜≠0, it is possible to suppress the vibration of the timing belt before and after the driven wheels and eliminate their mutual influence on the noise increase side, thereby reducing noise. becomes possible.
(3) 実施例
以下、図面により本発明の一実施例について説
明すると、先ず第１図において、エンジン本体１
の一側には、ベルトカバー２が取付けられてお
り、このベルトカバー２内で、クランク軸３に固
定された駆動プーリ４と、一対のカム軸５，６に
それぞれ固定されたカムプーリ７，８とに無端状
タイミングベルト９が卷回される。また駆動プー
リ４およびカムプーリ７間には、駆動プーリ４側
から順に、被駆動輪としてのテンシヨナ１０と、
ウオータポンプ１１の駆動軸１２に固定された補
機駆動用プーリ１３とが配設されており、タイミ
ングベルト９はテンシヨナ１０および補機駆動用
プーリ１３にも巻掛けられる。 (3) Embodiment An embodiment of the present invention will be explained below with reference to the drawings. First, in FIG.
A belt cover 2 is attached to one side, and within this belt cover 2, a drive pulley 4 fixed to a crankshaft 3 and cam pulleys 7 and 8 fixed to a pair of camshafts 5 and 6, respectively, are installed. The endless timing belt 9 is wound. Further, between the drive pulley 4 and the cam pulley 7, in order from the drive pulley 4 side, there is a tensioner 10 as a driven wheel;
An auxiliary drive pulley 13 fixed to the drive shaft 12 of the water pump 11 is provided, and the timing belt 9 is also wound around the tensioner 10 and the auxiliary drive pulley 13.
タイミングベルト９は歯付ベルトであり、前記
駆動プーリ４、カムプーリ７，８、テンシヨナ１
０および補機駆動用プーリ１３の外周面にはタイ
ミングベルト９に噛合する歯がそれぞれ設けられ
る。 The timing belt 9 is a toothed belt, and includes the drive pulley 4, cam pulleys 7 and 8, and the tensioner 1.
Teeth that mesh with the timing belt 9 are provided on the outer peripheral surfaces of the pulley 0 and the auxiliary drive pulley 13, respectively.
本発明に従えば、テンシヨナ１０の前後におけ
るタイミングベルト９の弦部Ｓ１，Ｓ２の弦振動
共振周波数fr1，fr2は｜fr1−fr2｜≠０、好ましく
は｜fr1−fr2｜≧100となるように定められる。こ
こで、弦振動共振周波数frは次の第(1)式で表され
るものである。 According to the present invention, the string vibration resonance frequencies fr 1 , fr 2 of the string portions S1, S2 of the timing belt 9 before and after the tensioner 10 are |fr 1 −fr 2 |≠0, preferably |fr 1 −fr 2 | It is determined to be ≧100. Here, the string vibration resonance frequency fr is expressed by the following equation (1).
fr＝Ｋ／2l ……(1)
第(1)式において、符号Ｋはタイミングベルト９
の幅および張力によつて定まる定数であり、符号
ｌは弦長である。 fr=K/2l...(1) In equation (1), the symbol K is the timing belt 9
is a constant determined by the width and tension of , and the symbol l is the chord length.
次にこの実施例の作用について説明すると、先
ず弦部Ｓ１の弦長ｌ１を75mm、弦部Ｓ２の弦長ｌ
２を67mmと設定していた従来のものの騒音レベル
について検討する。これらの弦部Ｓ１，Ｓ２の騒
音レベルは第２図で示すようになり、弦部Ｓ１の
騒音レベルピーク値は第２図ａで示すようにエン
ジン回転数1200rpm、弦部Ｓ２の騒音レベルピー
ク値は第２図ｂで示すようにエンジン回転数
1300rpmで示され、それらのエンジン回転数は近
接している。 Next, to explain the operation of this embodiment, first, the chord length l1 of the string section S1 is 75 mm, and the chord length l of the string section S2 is 75 mm.
Let's consider the noise level of the conventional model, which was set at 67mm. The noise levels of these string sections S1 and S2 are as shown in Fig. 2, and the noise level peak value of the string section S1 is as shown in Fig. 2 a when the engine rotation speed is 1200 rpm and the noise level peak value of the string section S2. is the engine speed as shown in Figure 2b.
Shown at 1300rpm, their engine speeds are close.
一方、前述の第(1)式に基づいて第３図で示され
るグラフによれば、弦部Ｓ１，Ｓ２の弦振動共振
周波数はfr1，fr2はそれぞれ380Hz、430Hzである。
ここで、このような周波数を示すエンジン回転数
を求めてみると、カムプーリ７，８のピツチ周波
数fpは、第(2)式で示される。 On the other hand, according to the graph shown in FIG. 3 based on the above-mentioned equation (1), the string vibration resonance frequencies fr 1 and fr 2 of the string sections S1 and S2 are 380 Hz and 430 Hz, respectively.
Now, when the engine rotational speed exhibiting such a frequency is determined, the pitch frequency fp of the cam pulleys 7 and 8 is expressed by the equation (2).
fp＝Ｔ×Ne／60 ……(2)
第(2)式において符号Ｔはカムプーリ７，８の歯
数であり、符号Neはエンジン回転数であり、Ｔ
＝20とし、fp＝380、430としたときのエンジン回
転数Neは1140rpm、1290rpmである。すなわち、
第２図で示されたような騒音レベルのピーク値を
示すときのエンジン回転数1200rpm、1300rpmと
ほぼ一致する。 fp=T×Ne/60...(2) In equation (2), the symbol T is the number of teeth of the cam pulleys 7 and 8, the symbol Ne is the engine rotation speed, and the symbol T
= 20, and when fp = 380 and 430, the engine rotation speed Ne is 1140 rpm and 1290 rpm. That is,
This almost coincides with the engine rotation speeds of 1200 rpm and 1300 rpm when the noise level peaks as shown in FIG.
このことは、両弦部Ｓ１，Ｓ２の騒音が相互に
影響し合つて騒音レベルを増大させる要因とな
る。また、ほぼ同一のエンジン回転数で弦振動共
振周波数とピツチ周波数とが一致することは、弦
部Ｓ１，Ｓ２の振幅の増大につながり、それによ
つても騒音レベルが大となる。 This causes the noises of both string sections S1 and S2 to influence each other and increase the noise level. Furthermore, matching the string vibration resonance frequency and the pitch frequency at substantially the same engine speed leads to an increase in the amplitude of the string sections S1 and S2, which also increases the noise level.
このような従来のものに対し、本発明に従つて
｜fr1−fr2｜≠０、好ましくは｜fr1−fr2｜≧100
とすべく、弦長ｌ１を81mm、弦長ｌ２を61mmとし
たときの騒音レベルについて検討すると、弦部Ｓ
１，Ｓ２の弦振動共振周波数fr1，fr2は、第３図
で示されるように、350Hz、470Hzとなる。またこ
のときの第(2)式に基づくエンジン周波数は、
1050rpm、1410rpmとなる。 In contrast to such conventional ones, according to the present invention |fr 1 −fr 2 |≠0, preferably |fr 1 −fr 2 |≧100
In order to achieve this, when considering the noise level when the string length l1 is 81 mm and the string length l2 is 61 mm, it is found that the string section S
The string vibration resonance frequencies fr 1 and fr 2 of the strings 1 and S2 are 350 Hz and 470 Hz, as shown in FIG. Also, the engine frequency based on equation (2) at this time is:
1050rpm, 1410rpm.
このように弦振動共振周波数と、それに相当す
るエンジン回転数とが相互に離隔した値を示すこ
とにより、弦部Ｓ１，Ｓ２での騒音レベルの低減
を図ることができる。 In this way, by making the string vibration resonance frequency and the engine rotational speed corresponding thereto exhibit values that are separated from each other, it is possible to reduce the noise level in the string sections S1 and S2.
第４図は、実験結果を示すものであり、実線で
示す曲線が弦長ｌ１，ｌ２を75mm、67mmとしたと
きの従来のものを示し、破線で示す曲線が本発明
に従つて弦長ｌ１，ｌ２を81mm、61mmとしたとき
のものを示す。また、第４図の上方はＡ特性補正
音圧レベルを示すものである。 FIG. 4 shows the experimental results, where the curve shown by a solid line shows the conventional one when the chord lengths l1 and l2 are 75 mm and 67 mm, and the curve shown by a broken line shows the result when the chord length l1 and l2 are set according to the present invention. , l2 are 81 mm and 61 mm. Moreover, the upper part of FIG. 4 shows the A-weighting corrected sound pressure level.
この第４図から明らかなように、本発明に従つ
て弦振動共振周波数fr1，fr2を定めることにより
騒音レベルが低減される。 As is clear from FIG. 4, the noise level is reduced by determining the string vibration resonance frequencies fr 1 and fr 2 according to the present invention.
なお、弦部Ｓ１，Ｓ２の弦長ｌ１，ｌ２を変え
ることに代えて、プーリの歯数を変更することに
より、ピツチ周波数と弦振動共振周波数とを一致
させないようにすることも可能であり、これによ
つても前述と同様の効果を奏することができる。 Note that instead of changing the string lengths l1 and l2 of the string parts S1 and S2, it is also possible to make the pitch frequency and the string vibration resonance frequency not match by changing the number of teeth of the pulley. This also provides the same effects as described above.
Ｃ 発明の効果
以上のように本発明によれば、被駆動輪の前後
のタイミングベルトの弦振動共振周波数fr1，fr2
を｜fr1−fr2｜≠０とするようにしたので、被駆
動輪の前後でのタイミングベルトの弦振動が相互
に影響し合つて騒音レベルを大とすることを防止
し、弦振幅の増大をも抑えて騒音レベルの抑制を
図ることができる。C. Effects of the Invention As described above, according to the present invention, the string vibration resonance frequencies fr 1 , fr 2 of the timing belts before and after the driven wheels are
By setting |fr 1 −fr 2 |≠0, it is possible to prevent the string vibrations of the timing belt before and after the driven wheels from influencing each other and increasing the noise level, and to reduce the string amplitude. It is possible to suppress the noise level by suppressing the increase.
図面は本発明の一実施例を示すものであり、第
１図は縦断面図、第２図は従来のものの騒音レベ
ルを示すグラフ、第３図は弦振動共振周波数を示
すグラフ、第４図は実験結果を示すグラフであ
る。
３……クランク軸、４……駆動プーリ、５，６
……カム軸、７，８……カムプーリ、１０……被
駆動輪としてのテンシヨナ、１３……補機駆動用
プーリ。
The drawings show one embodiment of the present invention, and FIG. 1 is a longitudinal cross-sectional view, FIG. 2 is a graph showing the noise level of the conventional one, FIG. 3 is a graph showing string vibration resonance frequency, and FIG. 4 is a graph showing the string vibration resonance frequency. is a graph showing the experimental results. 3... Crankshaft, 4... Drive pulley, 5, 6
...Cam shaft, 7, 8 ... Cam pulley, 10 ... Tensioner as a driven wheel, 13 ... Pulley for driving auxiliary equipment.
Claims (1)
軸に固定されるカムプーリとに無端状タイミング
ベルトが巻回されるとともに、前記両プーリ間で
タイミングベルトが被駆動輪に巻掛けられる車両
用エンジンのタイミングベルト巻掛装置におい
て、前記タイミングベルトの弦長をｌ、タイミン
グベルトの幅および張力によつて定まる定数を
Ｋ、タイミングベルトの弦振動共振周波数frを、
fr＝Ｋ／2lとしたときに、前記被駆動輪の前後の
タイミングベルトの弦振動共振周波数fr1，fr2が
｜fr1−fr2｜≠０なる関係を有することを特徴と
する車両用エンジンのタイミングベルト巻掛装
置。 ２ 前記被駆動輪の前後のタイミングベルトの振
動共振周波数fr1，fr2が、｜fr1−fr2｜≧100なる関
係を有することを特徴とする特許請求の範囲第１
項記載の車両用エンジンのタイミングベルト巻掛
装置。[Claims] 1. An endless timing belt is wound around a drive pulley fixed to a crankshaft and a cam pulley fixed to a camshaft, and the timing belt is wound around a driven wheel between the two pulleys. In the timing belt winding device for a vehicle engine to be hung, the chord length of the timing belt is l, the constant determined by the width and tension of the timing belt is K, and the string vibration resonance frequency fr of the timing belt is,
A vehicle characterized in that, when fr=K/2l, the string vibration resonance frequencies fr 1 and fr 2 of the timing belts before and after the driven wheels have a relationship of |fr 1 −fr 2 |≠0. Engine timing belt winding device. 2. Claim 1, wherein the vibration resonance frequencies fr 1 and fr 2 of the timing belts before and after the driven wheels have a relationship of |fr 1 −fr 2 |≧100.
A timing belt winding device for a vehicle engine as described in 2.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP27513584A JPS61153047A (en) | 1984-12-25 | 1984-12-25 | Timing-belt laying device for engine for car |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP27513584A JPS61153047A (en) | 1984-12-25 | 1984-12-25 | Timing-belt laying device for engine for car |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61153047A JPS61153047A (en) | 1986-07-11 |
| JPS635620B2 true JPS635620B2 (en) | 1988-02-04 |
Family
ID=17551179
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP27513584A Granted JPS61153047A (en) | 1984-12-25 | 1984-12-25 | Timing-belt laying device for engine for car |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS61153047A (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6572501B2 (en) * | 1999-04-29 | 2003-06-03 | Gerhard Winklhofer | Method and device for reducing vibrations of a control chain in a camshaft drive of an internal combustion engine |
| CN110987454A (en) * | 2019-12-23 | 2020-04-10 | 奇瑞汽车股份有限公司 | Test method and device for reducing vehicle noise, test equipment and storage medium |
-
1984
- 1984-12-25 JP JP27513584A patent/JPS61153047A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS61153047A (en) | 1986-07-11 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US8303444B2 (en) | Synchronous drive apparatus and methods | |
| US7493880B2 (en) | Non-circular rotary component | |
| JPH10266868A (en) | Camshaft drive | |
| US4981462A (en) | Belt construction, rotatable pulley and combination thereof and methods making the same | |
| US5026327A (en) | Belt construction, rotatable pulley and combination thereof and methods of making the same | |
| JPS635620B2 (en) | ||
| JPS6388368A (en) | Constant speed drive device | |
| EP0460108A4 (en) | Belt construction, rotatable pulley and combination thereof and methods of making the same | |
| KR20070026527A (en) | Belt drive unit for internal combustion engine | |
| US4940450A (en) | Power transmission system using toothed belt of engine for vehicle | |
| GB2094439A (en) | Toothed belt and valve gear for an internal combustion engine | |
| US4758206A (en) | Cam shaft drive structure for OHC V-type engine | |
| JPS5922255Y2 (en) | Internal combustion engine power transmission device | |
| JP2512768B2 (en) | Camshaft drive for V-type DOHC engine | |
| JPS58220925A (en) | Belt transmission device | |
| JPS58214052A (en) | Power transmission mechanism for time-regulation | |
| JPS60172749A (en) | toothed power transmission belt | |
| EP0580646A1 (en) | An arrangement in internal combustion engines | |
| JPS58214053A (en) | Toothed belt driving gear | |
| KR19980017711U (en) | Timing belt and pulley structure of automobile engine | |
| KR100401878B1 (en) | Noise decreasing structure of timing chain in vehicle | |
| JPH022910Y2 (en) | ||
| JPS58203264A (en) | Tooth shape of sprocket | |
| KR200174854Y1 (en) | Generator mounting structure of internal combustion engine | |
| JPH0515544Y2 (en) |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EXPY | Cancellation because of completion of term |