JP2502115Y2 - Toothed belt drive - Google Patents
Toothed belt driveInfo
- Publication number
- JP2502115Y2 JP2502115Y2 JP1991008048U JP804891U JP2502115Y2 JP 2502115 Y2 JP2502115 Y2 JP 2502115Y2 JP 1991008048 U JP1991008048 U JP 1991008048U JP 804891 U JP804891 U JP 804891U JP 2502115 Y2 JP2502115 Y2 JP 2502115Y2
- Authority
- JP
- Japan
- Prior art keywords
- belt
- pulley
- tooth
- pressure
- pressure surface
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Landscapes
- Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本考案は、歯付ベルトの駆動装置
に係り、詳しくは歯付ベルトとプーリとの噛み合い時に
おいて発生する騒音を減少させた歯付ベルトの駆動装置
に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a drive device for a toothed belt, and more particularly to a drive device for a toothed belt that reduces noise generated when the toothed belt and a pulley are meshed with each other. br />.
【０００２】[0002]
【従来の技術】今日、一般に使用されている歯付ベルト
とプーリの組合せ体からなる駆動装置としては、ＲＭＡ
（Ｒｕｂｂｅｒ Ｍａｎｕｆａｃｔｕｒｅｓ Ａｓｓｏ
ｃｉａｔｉｏｎ）ＩＰ−２４（１９７８年）に定められ
ているように、断面台形のベルト歯部とその歯部と相似
形のプーリとの噛み合いによる伝動システムがある。と
ころが、この種のベルトはプーリと噛み合う場合、歪が
ベルト歯部の歯元に集中し、ベルト歯部の歯先はプーリ
と完全に係合した時でも歪むことが無く、ベルト歯部は
大部分不必要で本質的にほとんど荷重を受けていない。
また、荷重はベルト歯部から抗張体へ不均等に伝達さ
れ、かつベルト歯部の歯先がプーリ歯側面と係合中に干
渉が起こる欠点が見られた。この台形状のベルト歯部は
このような歪み集中、荷重のベルト歯部から抗張体への
不均等な伝達及び歯の干渉を生じるため、改善が望まれ
ていた。2. Description of the Related Art RMA is a driving device which is a combination of a toothed belt and a pulley that is generally used today.
(Rubber Manufactures Asso
(ciation) IP-24 (1978), there is a transmission system by a belt tooth portion having a trapezoidal cross section and meshing between the tooth portion and a pulley having a similar shape. However, when this kind of belt meshes with the pulley, the strain concentrates on the root of the belt tooth portion, and the tooth tip of the belt tooth portion does not distort even when it is completely engaged with the pulley, and the belt tooth portion is large. Partly unnecessary and essentially unloaded.
In addition, the load was unevenly transmitted from the belt tooth portion to the tensile body, and there was a drawback that the tooth tip of the belt tooth portion interfered with the tooth flank of the pulley during engagement. This trapezoidal belt tooth portion causes such strain concentration, uneven transmission of load from the belt tooth portion to the tensile body, and tooth interference. Therefore, improvement has been desired.
【０００３】そこで、これに対応して叙上の点を改善し
た装置としてベルト歯部が互いに交差すると共にそれぞ
れ等しい半径を有する２つの円弧からなり、所定荷重下
で１／２次の等色しまの輪郭とほぼ等しい輪郭をもつ歯
付ベルトと、このベルト歯部とコンジユゲートである円
弧状の溝を有するプーリとを組合せたものが提供され
た。（米国特許第３７５６０８１号明細書参照）Therefore, as a device corresponding to the above, the belt tooth portions are crossed with each other and two arcs having equal radii are formed, and a half-order color matching is performed under a predetermined load. There is provided a combination of a toothed belt having a contour approximately equal to that of the above and a pulley having a belt tooth portion and a circular arc groove which is a conduit. (See US Pat. No. 3,756,081)
【０００４】[0004]
【考案が解決しようとする課題】しかし、従来の歯付ベ
ルトは、歯元の圧力角がほぼゼロになって直立している
ため、ベルトがプーリから離れる時にベルト圧力面及び
歯先部がスムーズに離れずにプーリとの干渉によってこ
すれてしまうことがあって噛合１次振動、つまり１秒当
りにベルトに噛み合うプーリ歯数と同一の周波数を発生
する。一方、固有振動数はベルトのプーリ間のスパン長
とベルト単位重量及びベルト張力により決定される。こ
の噛合１次振動数がそのスパンでの固有振動数と倍数関
係にあるとき、ベルトは共振して大きな騒音を発してい
た。本考案は、このような問題点を改善し、前記共振音
の発生を軽減してなる歯付ベルトの駆動装置を提供する
ことを目的とする。However, in the conventional toothed belt, since the pressure angle at the root of the tooth is almost zero and the belt is upright, the belt pressure surface and the tip of the tooth are smooth when the belt is separated from the pulley. It may be rubbed due to interference with the pulley without being separated, and primary meshing vibration, that is, the same frequency as the number of pulley teeth meshing with the belt per second is generated. On the other hand, the natural frequency is determined by the span length between belt pulleys, the belt unit weight, and the belt tension. When this meshing primary frequency was in a multiple relationship with the natural frequency in the span, the belt resonated and made a lot of noise. SUMMARY OF THE INVENTION It is an object of the present invention to provide a drive device for a toothed belt which solves the above problems and reduces the occurrence of the resonance noise.
【０００５】[0005]
【課題を解決するための手段】即ち、本考案の特徴とす
るところは、ベルト長手方向に一定ピッチでベルト歯部
とベルト溝部とを交互に有する歯付ベルトと、該ベルト
と噛み合うプーリとからなり、前記ベルト歯部は円弧の
ベルト歯元部と、直線からなるベルト圧力面そして円弧
からなるベルト歯元部をそれぞれ連結した３つの領域か
らなり、一方これに噛み合うプーリ溝部は円弧のプーリ
歯先部と、直線からなるプーリ圧力面そして１つの円弧
からなるプーリ溝底部から形成され、ベルト歯部の該圧
力面がベルト歯部中心線に対して５〜１０°傾斜した圧
力角を有し、しかもそれがプーリ溝部の圧力角より小さ
くて、その差は最大１５°にある。 Means for Solving the Problems That is, the features of the present invention
The belt teeth at a constant pitch in the longitudinal direction of the belt.
Belt having teeth and belt groove portions alternately, and the belt
The belt tooth part is a circular arc.
Belt root, straight belt pressure surface and arc
3 areas that connect the root parts of
On the other hand, the pulley groove that meshes with this is a circular pulley
Tooth tip, straight pulley pressure surface and one arc
It is formed from the bottom of the pulley groove that consists of
Pressure with the force surface inclined 5 to 10 ° with respect to the belt center line.
It has a force angle and it is smaller than the pressure angle of the pulley groove.
The maximum difference is 15 °.
【０００６】[0006]
【０００７】[0007]
【作用】本考案の歯付ベルトの駆動装置では、特にベル
ト圧力面とプーリ圧力面をともに直線にして、ベルト圧
力面の角度をプーリ溝部の圧力角より小さくし、その差
を最大１５°に設定したことにより、ベルト歯部がプー
リ溝部に嵌入しやすく、またプーリ溝部から離れやすく
なるために、ベルトがプーリから離れる時にベルト歯部
の圧力面とプーリ溝部とのこすれによる干渉がなくな
り、ベルト歯部はプーリ溝部からスムーズに離れていく
ため、この時生じる噛合１次振動を小さくでき、これに
よりベルトの共振音を軽減する作用がある。In the drive device for the toothed belt of the present invention, especially the bell
Both the belt pressure surface and the pulley pressure surface are straight, and the belt pressure
Make the angle of the force surface smaller than the pressure angle of the pulley groove, and
By setting the maximum to 15 °, the belt teeth
Easy to fit in the groove and easily separate from the pulley groove
To become, belt eliminates interference due to rubbing between the pressure surface and the pulley groove of the belt tooth portion when away from the pulley, since the belt tooth portion moves away smoothly from the pulley groove, it is possible to reduce the meshing primary vibration caused when the This has the effect of reducing the resonance noise of the belt.
【０００８】[0008]
【実施例】以下、添付図面を参照し、本考案の１つの実
施例を説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT An embodiment of the present invention will be described below with reference to the accompanying drawings.
【０００９】 図１は本考案の歯付ベルトの駆動装置に
使用する歯付ベルトの１例であり、該ベルト１はベルト
長手方向に一定ピッチで設けたベルト歯部２、ベルト溝
部３そしてピッチライン４上に心線５を埋設している。
ベルト歯部２は曲率半径ｒｂ円弧からなるベルト歯元部
７と、プーリ溝部と実質的に係合して動力伝達を担う傾
斜したベルト圧力面８と、プーリ溝部によって支持され
るベルト歯先部９から構成されている。FIG. 1 shows a drive device for a toothed belt according to the present invention.
This is an example of a toothed belt to be used , and the belt 1 has a belt tooth portion 2, a belt groove portion 3, and a core wire 5 embedded on a pitch line 4 provided at a constant pitch in the belt longitudinal direction.
The belt tooth portion 2 includes a belt tooth root portion 7 having a radius of curvature rb, an inclined belt pressure surface 8 that substantially engages with the pulley groove portion to transmit power, and a belt tooth tip portion supported by the pulley groove portion. It is composed of nine.
【００１０】上記圧力面８は直線からなり、実質的にベ
ルト歯部高さＨＢの１５〜４５％分に相当し、しかもベ
ルト歯部中心線１０に対して５〜１０°傾斜した圧力角
ΘＢを有している。従って、この圧力面８の領域ではベ
ルト歯幅Ｗがベルト歯先部９の先端に向かって徐々に小
さくなり、このためベルト歯部２はプーリ溝部に干渉せ
ずスムーズに離れる。The pressure surface 8 is a straight line and substantially corresponds to 15 to 45% of the belt tooth height HB, and the pressure angle ΘB is 5 to 10 ° with respect to the belt tooth center line 10. have. Therefore, in the area of the pressure surface 8, the belt tooth width W gradually becomes smaller toward the tip of the belt tooth tip 9, so that the belt tooth 2 smoothly separates without interfering with the pulley groove.
【００１１】前記圧力角ΘＢが５°未満の場合には、ベ
ルト圧力面８がプーリから受ける荷重Ｐにおいて圧力面
８に対して直角方向の分力ＰｃｏｓΘＢ（ΘＢは圧力
角）が大きくなり、逆に平行方向の分力ＰｓｉｎΘＢが
小さくなる。この結果、ベルト歯元部７は応力集中を受
けやすく大きな歪みをうけ、ベルト歯部２が心線５から
剥離しやすくなる。また、ベルト歯部２のグリップ力は
大きくなり、ベルト歯部２はプーリ溝部から抜けにくく
なる問題も生じる。When the pressure angle ΘB is less than 5 °, the component force Pcos ΘB (ΘB is the pressure angle) in the direction perpendicular to the pressure surface 8 becomes large under the load P received by the belt pressure surface 8 from the pulley, and vice versa. The component force Psin ΘB in the parallel direction becomes smaller. As a result, the belt root portion 7 is easily subjected to stress concentration and is subjected to a large strain, and the belt tooth portion 2 is easily separated from the core wire 5. Further, the grip force of the belt tooth portion 2 becomes large, and the belt tooth portion 2 becomes difficult to come off from the pulley groove portion.
【００１２】一方、圧力角ΘＢが１０°を越えると、ベ
ルト圧力面８に対して直角方向の分力ＰｃｏｓΘＢは小
さくなり、逆に平行方向の分力ＰｓｉｎΘＢが大きくな
る傾向になるため、ベルト歯部２のグリップ力は小さく
なって、ベルト歯部２はプーリ溝部から抜けやすくなる
反面、ベルトの動力伝達効率は小さくなる。On the other hand, if the pressure angle ΘB exceeds 10 °, the component force Pcos ΘB in the direction perpendicular to the belt pressure surface 8 becomes smaller, and conversely the component force Psin ΘB in the parallel direction tends to become larger, so that the belt teeth The gripping force of the portion 2 becomes small and the belt tooth portion 2 easily comes out of the pulley groove portion, but the power transmission efficiency of the belt becomes small.
【００１３】また、前記ベルト圧力面８はベルト歯元部
７との接続点である第１境界点１１とベルト歯先部９と
の接続点である第２境界点１２との間にあり、この領域
の高さｈｂはベルト歯部高さＨＢの１５〜４５％分に相
当している。もし、１５％未満であると動力伝達領域が
小さくて伝達効力が悪くなり、一方４５％を越えると、
ベルト圧力面８とベルト歯先部９との接続点である第２
境界点１２がベルト歯部２がプーリと噛み合う時、また
プーリから離れる時に干渉する確率が高くなる。The belt pressure surface 8 is located between a first boundary point 11 which is a connection point with the belt root portion 7 and a second boundary point 12 which is a connection point with the belt tip portion 9. The height hb of this region corresponds to 15 to 45% of the belt tooth height HB. If it is less than 15%, the power transmission region is small and the transmission efficiency becomes poor, while if it exceeds 45%,
The second connecting point between the belt pressure surface 8 and the belt tooth top 9
There is a high probability that the boundary point 12 interferes when the belt tooth portion 2 meshes with the pulley and when it separates from the pulley.
【００１４】また、前記歯先部９はベルト歯部中心線１
０に対して反対側に起点１３、１４を有し、互いに交差
する等しい曲率半径ＲＢ、ＲＢの円弧からなり、２つの
円弧はベルト歯先部の先端部１５で交差している。Further, the tooth top portion 9 is the belt tooth center line 1
It has starting points 13 and 14 on the opposite side to 0, and is composed of arcs of the same radius of curvature RB, RB intersecting each other, and the two arcs intersect at the tip portion 15 of the tooth tip of the belt.
【００１５】前記歯付ベルト１と噛み合うプーリ２０
は、図２に示すように一定ピッチでプーリ溝部２１とプ
ーリ歯部２２とを交互に有し、プーリ溝部２１は曲率半
径ｒｐからなる円弧のプーリ歯先部２３と、直線部分の
プーリ圧力面２４、そしてプーリ溝部中心部２５上に起
点２６を有する曲率半径ＲＰを有する１つの円弧からプ
ーリ溝底部２７から形成される。前記圧力面２４はプー
リ歯先部２３との接続点である第１境界点２８とプーリ
溝底部２７との接続点である第２境界点２９との間にあ
り、この領域はプーリ溝部深さＨＰの１５〜６０％の長
さに相当している。そして、前記圧力面２４の圧力角Θ
はＰ１５〜２５°である。A pulley 20 meshing with the toothed belt 1
2, the pulley groove portions 21 and the pulley tooth portions 22 are alternately arranged at a constant pitch as shown in FIG. 2, and the pulley groove portions 21 have an arcuate pulley tooth tip portion 23 having a radius of curvature rp and a straight portion of the pulley pressure surface. 24, and the pulley groove bottom portion 27 is formed from one circular arc having a radius of curvature RP and having a starting point 26 on the pulley groove central portion 25. The pressure surface 24 is located between a first boundary point 28, which is a connection point with the pulley tooth tip 23, and a second boundary point 29, which is a connection point with the pulley groove bottom portion 27. This corresponds to a length of 15 to 60% of HP. Then, the pressure angle Θ of the pressure surface 24
Is P15 to 25 °.
【００１６】前記歯付ベルト１がプーリ２０に噛み合っ
たとき、ベルト歯部の圧力角ΘＢはプーリ溝部の圧力角
ΘＰより小さくてその差は最大１５°である。このよう
にすれば、ベルト歯部２はプーリ溝部２１と干渉せずに
スムーズに抜けることで、噛合１次振動を小さくし、こ
れに伴う共振音を軽減することになる。もし、この差が
１５°を越えるとベルト歯部２がプーリ溝部２１から離
れるときに、ベルト歯部２とプーリ歯部２２との干渉は
避けられず、またベルト圧力面８はプーリから充分な荷
重を受けず、むしろ荷重を受ける位置がベルト歯先部９
に移る。こうなるとベルトの伝達効力が悪くなり、しか
もベルト歯先部９はモーメントの関係から大きな応力集
中を受けて、ベルト歯部２が心線５から剥離しやすくな
る。When the toothed belt 1 meshes with the pulley 20, the pressure angle ΘB of the belt tooth portion is smaller than the pressure angle ΘP of the pulley groove portion, and the difference is 15 ° at the maximum. By doing so, the belt tooth portion 2 smoothly comes out without interfering with the pulley groove portion 21, so that the meshing primary vibration is reduced and the resonance sound accompanying this is reduced. If this difference exceeds 15 °, when the belt tooth portion 2 separates from the pulley groove portion 21, the interference between the belt tooth portion 2 and the pulley tooth portion 22 is unavoidable, and the belt pressure surface 8 is sufficiently separated from the pulley. The position where the load is not applied, but rather the load is applied, is the tooth tip 9 of the belt.
Move on to. In this case, the transmission efficiency of the belt is deteriorated, and moreover, the belt tooth top portion 9 receives a large stress concentration due to the relation of the moment, and the belt tooth portion 2 is easily separated from the core wire 5.
【００１７】また、ベルト歯部高さＨＢはプーリ溝部深
さＨＰより２〜５％大きくなり、ベルト歯部２はプーリ
溝部２１と圧縮係合する。Further, the belt tooth portion height HB is larger than the pulley groove portion depth HP by 2 to 5%, and the belt tooth portion 2 is in compression engagement with the pulley groove portion 21.
【００１８】 以下に本考案の歯付ベルトの駆動装置の
走行試験を行ない、ベルト走行中の音圧を測定した結果
を示す。ここで用いた歯付ベルトは、ＰＬＤ（ピッチラ
インとベルト溝部表面間の距離）０．６８６ｍｍ、歯部
ピッチ８ｍｍ、ベルト幅２１．１ｍｍであり、ベルト歯
部は図１と同一形状で、ベルト歯元部の曲率半径ｒｂが
０．６３ｍｍ、歯幅Ｗが４．４０ｍｍ、圧力角ΘＢが８
°、ベルト歯先部の曲率半径ＲＢが２．２０ｍｍ、ベル
ト歯部高さＨＢが３．０５ｍｍである。The running test of the drive device for a toothed belt of the present invention was conducted below, and the results of measuring the sound pressure during running of the belt are shown below. The toothed belt used here had a PLD (distance between the pitch line and the surface of the belt groove) of 0.686 mm, a tooth pitch of 8 mm, and a belt width of 21.1 mm. The belt tooth had the same shape as in FIG. The radius of curvature rb of the tooth root is 0.63 mm, the tooth width W is 4.40 mm, and the pressure angle ΘB is 8.
The radius of curvature RB of the tip of the belt tooth portion is 2.20 mm, and the height HB of the tooth portion of the belt is 3.05 mm.
【００１９】それに対して、比較例として用いる歯付ベ
ルトは、ＰＬＤ０．６８６mm、歯数１１７、歯部ピッチ
８mm、ベルト幅２１．１mmであり、ベルト歯部はｒｂが
０．６３mm、歯幅Ｗが４．４０mm、圧力角ΘＢが０°、
ベルト歯先部の曲率半径ＲＢが２．２７mm、ベルト歯部
高さ３．０１mmである。On the other hand, the toothed belt used as a comparative example has a PLD of 0.686 mm, a number of teeth of 117, a tooth pitch of 8 mm, and a belt width of 21.1 mm. The belt tooth portion has rb of 0.63 mm and tooth width W. Is 4.40 mm, pressure angle ΘB is 0 °,
The radius of curvature RB of the tip of the belt tooth is 2.27 mm, and the height of the tooth of the belt is 3.01 mm.
【００２０】一方、前記本考案及び比較例の歯付ベルト
に用いるプーリは図２に示す形状と同一であり、プーリ
歯先部の曲率半径ｒｐが０．７４mm、圧力角ΘＰが２０
°、プーリ溝底部がプーリ溝部中心線上に中心点を有す
る曲率半径ＲＰが２．２９mm、プーリ溝部深さ３mmから
なっている。On the other hand, the pulleys used in the toothed belts of the present invention and the comparative example have the same shape as shown in FIG. 2, and the radius of curvature rp of the tooth tip of the pulley is 0.74 mm and the pressure angle ΘP is 20.
The radius of curvature RP having the center of the pulley groove bottom on the center line of the pulley groove is 2.29 mm and the depth of the pulley groove is 3 mm.
【００２１】前記ベルトをカムシャフトに装着した従動
プーリ（歯数４８）及びクランク軸に装着した駆動プー
リ（歯数２４）からなる１５００ｃｃ４気筒エンジン実
機モータリング試験機に取り付け、更にテンションプー
リによってそれぞれ２０、３０、４０ｋｇｆの張力を付
与し、カムシャフトを８２０ｒｐｍで回転させた。そし
て、ベルト背面から約３ｃｍ離してマイクを設置してベ
ルト走行中の音圧を測定した。The driven <br/> pulley (the number of teeth 48) and 1500cc4 cylinder engine actual motoring testing machine comprising a crankshaft mounted the driving pulley <br/> Li (24 teeth number) equipped with the belt to the camshaft And tensions of 20, 30, and 40 kgf were applied by a tension pulley, and the cam shaft was rotated at 820 rpm. Then, a microphone was installed at a distance of about 3 cm from the back surface of the belt, and the sound pressure during running of the belt was measured.
【００２２】測定項目は、マイクでひろった全音圧のオ
ーバーオール、１秒当りにベルトに噛み合うプーリ歯数
と同一の周波数である噛合１次音圧、そして１／３オク
ターブ音圧である。The items to be measured are overall sound pressure picked up by a microphone, meshing primary sound pressure having the same frequency as the number of pulley teeth meshing with the belt per second, and 1/3 octave sound pressure.
【００２３】この１／３オクターブとは周波数を分割し
てブロックに分け、そのブロックごとに評価する方法の
１つで、任意の区分する周波数上限をＦとすると、その
上限Ｆは２の１／３乗と下限ｆを掛け合わせて計算され
る。このようにして測定最大周波数より０までをブロッ
クごとに区分してそれぞれのブロック音圧を評価した。
本測定では、３３２Hzを含むブロックの音圧をここでは
１／３オクターブ音圧とした。このようにして得られた
音圧の結果を表１に示す。The 1/3 octave is one of the methods of dividing a frequency into blocks and evaluating each block. When the frequency upper limit for arbitrary division is F, the upper limit F is 1/2. It is calculated by multiplying the third power and the lower limit f. In this way, from the measured maximum frequency to 0, the blocks were divided into blocks and the block sound pressures were evaluated.
In this measurement, the sound pressure of the block including 332 Hz was set to 1/3 octave sound pressure here. The results of the sound pressure thus obtained are shown in Table 1.
【００２４】[0024]
【表１】[Table 1]
【００２５】 このように、本考案の歯付ベルトの駆動
装置では、オーバーオール、噛合１次及び１／３オクタ
ーブの音圧がいずれも比較例に比べて小さくなり、音圧
について充分に改善されていることが判る。Thus, the drive of the toothed belt of the present invention
In the device , the sound pressures of overall, primary meshing, and 1/3 octave are all smaller than that of the comparative example, and it is understood that the sound pressure is sufficiently improved.
【００２６】[0026]
【考案の効果】以上のように、本考案の歯付ベルトの駆
動装置では、ベルト歯部の圧力面が直線で、またこの領
域がベルト歯部高さの１５〜４５％に相当し、そして圧
力面とベルト歯部中心とのなす角度である圧力角が５〜
１０゜であるために、ベルト歯部はプーリ溝部に干渉せ
ずにスムーズに離れ、この時の噛合１次振動を小さくし
て、ベルトの共振音を軽減することができる効果を有す
る。[Effects of the Invention] As described above, the drive of the toothed belt of the present invention
In the moving device , the pressure surface of the belt tooth portion is a straight line, and this region corresponds to 15 to 45% of the belt tooth portion height, and the pressure angle which is an angle formed by the pressure surface and the belt tooth portion is 5 ~
Since the angle is 10 °, the belt teeth are smoothly separated without interfering with the pulley groove, and the primary vibration of meshing at this time is reduced, so that the resonance noise of the belt can be reduced.
【図１】本考案の歯付ベルトの駆動装置に使用する歯付
ベルトの側面図である。FIG. 1 Tooth used in a drive device for a toothed belt of the present invention
It is a side view of a belt .
【図２】図１に示す歯付ベルトに噛み合うプーリの側面
図である。2 is a side view of a pulley meshing with the toothed belt shown in FIG.
１ 歯付ベルト ２ ベルト歯部 ３ ベルト溝部 ４ ピッチライン ５ 心線 ７ ベルト歯元部 ８ ベルト圧力面 ９ ベルト歯先部 ２０ プーリ ２１ プーリ溝部 ２２ プーリ歯部 ２３ プーリ歯先部 ２４ プーリ圧力面 ２５ プーリ溝底部 1 Toothed Belt 2 Belt Tooth Part 3 Belt Groove Part 4 Pitch Line 5 Core Wire 7 Belt Tooth Root Part 8 Belt Pressure Surface 9 Belt Tooth Tip Part 20 Pulley 21 Pulley Groove Part 22 Pulley Tooth Part 23 Pulley Tooth Part 24 Pulley Pressure Surface 25 Pulley groove bottom
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 平１−316543（ＪＰ，Ａ) 特開 平２−221734（ＪＰ，Ａ) 実公 昭61−32186（ＪＰ，Ｙ２) ─────────────────────────────────────────────────── ─── Continuation of the front page (56) References JP-A-1-316543 (JP, A) JP-A-2-221734 (JP, A) Jikken 61-32186 (JP, Y2)
Claims (1)
とベルト溝部とを交互に有する歯付ベルトと、該ベルト
と噛み合うプーリとからなり、前記ベルト歯部は円弧の
ベルト歯元部と、直線からなるベルト圧力面そして円弧
からなるベルト歯先部をそれぞれ連結した３つの領域か
らなり、一方これに噛み合うプーリ溝部は円弧のプーリ
歯先部と、直線からなるプーリ圧力面そして１つの円弧
からなるプーリ溝底部から形成され、ベルト歯部の該圧
力面がベルト歯部中心線に対して５〜１０°傾斜した圧
力角を有し、しかもそれがプーリ溝部の圧力角より小さ
くて、その差は最大１５°であることを特徴とする歯付
ベルトの駆動装置。1. A toothed belt having belt tooth portions and belt groove portions alternately arranged at a constant pitch in a longitudinal direction of the belt, and a pulley meshing with the belt, wherein the belt tooth portion is an arc belt root portion. The belt pressure surface consisting of a straight line and the belt tooth tip consisting of an arc are composed of three areas , respectively, while the pulley groove part that meshes with this is an arcuate pulley tooth tip, a straight pulley pressure surface and one arc. Is formed from the bottom of the pulley groove, the pressure surface of the belt tooth portion has a pressure angle inclined by 5 to 10 ° with respect to the center line of the belt tooth portion, and it is smaller than the pressure angle of the pulley groove portion. Is a drive device for a toothed belt, which is up to 15 °.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1991008048U JP2502115Y2 (en) | 1991-01-28 | 1991-01-28 | Toothed belt drive |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1991008048U JP2502115Y2 (en) | 1991-01-28 | 1991-01-28 | Toothed belt drive |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0496646U JPH0496646U (en) | 1992-08-21 |
| JP2502115Y2 true JP2502115Y2 (en) | 1996-06-19 |
Family
ID=31740236
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1991008048U Expired - Lifetime JP2502115Y2 (en) | 1991-01-28 | 1991-01-28 | Toothed belt drive |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2502115Y2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2011520071A (en) * | 2008-05-02 | 2011-07-14 | ザ ゲイツ コーポレイション | Synchronous belt / sprocket |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002098201A (en) * | 2000-09-25 | 2002-04-05 | Bando Chem Ind Ltd | Toothed belt transmission device and business equipment |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6132186U (en) * | 1984-07-30 | 1986-02-26 | 丸井産業株式会社 | Construction reinforcing bar hanging hardware |
| JP2875274B2 (en) * | 1989-02-21 | 1999-03-31 | 三ツ星ベルト株式会社 | Toothed belt |
-
1991
- 1991-01-28 JP JP1991008048U patent/JP2502115Y2/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2011520071A (en) * | 2008-05-02 | 2011-07-14 | ザ ゲイツ コーポレイション | Synchronous belt / sprocket |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0496646U (en) | 1992-08-21 |
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| Date | Code | Title | Description |
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| EXPY | Cancellation because of completion of term |