JP2002021956A - Belt driving system - Google Patents
Belt driving systemInfo
- Publication number
- JP2002021956A JP2002021956A JP2000200008A JP2000200008A JP2002021956A JP 2002021956 A JP2002021956 A JP 2002021956A JP 2000200008 A JP2000200008 A JP 2000200008A JP 2000200008 A JP2000200008 A JP 2000200008A JP 2002021956 A JP2002021956 A JP 2002021956A
- Authority
- JP
- Japan
- Prior art keywords
- belt
- pulley
- block
- surface roughness
- driven pulley
- 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
Links
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
- F16G—BELTS, CABLES, OR ROPES, PREDOMINANTLY USED FOR DRIVING PURPOSES; CHAINS; FITTINGS PREDOMINANTLY USED THEREFOR
- F16G5/00—V-belts, i.e. belts of tapered cross-section
- F16G5/16—V-belts, i.e. belts of tapered cross-section consisting of several parts
- F16G5/166—V-belts, i.e. belts of tapered cross-section consisting of several parts with non-metallic rings
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Pulleys (AREA)
- Transmissions By Endless Flexible Members (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明は、一対のプーリ間に高
負荷伝動用のブロックベルトを掛け渡してなるベルト駆
動システムに関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a belt drive system in which a block belt for transmitting a high load is stretched between a pair of pulleys.
【０００２】[0002]
【従来の技術及びその課題】従来より、ＣＶＴと呼ばれ
る自動車等用の無段変速機に使用されるベルトは、極め
て高いトルクの伝動能力を必要とするため、各種の高負
荷ベルトが知られている（例えば特開昭５５−２７５９
５号、特開昭５６−７６７４５号、特開昭５９−７７１
４７号の各公報参照）。また、エンドレスの一対の張力
帯と、多数のブロックとで構成され、ブロックを張力帯
に対しベルト長手方向に係止固定してなるブロックベル
トと呼ばれる高負荷伝動用ベルトについても提案がなさ
れている（特開昭６０−４９１５１号、特開昭６１−２
０６８４７号、特開昭６２−５４３４８号の各公報参
照）。2. Description of the Related Art Various types of high-load belts have been known since belts used in continuously variable transmissions for automobiles and the like called CVT require extremely high torque transmission capacity. (For example, Japanese Patent Laid-Open No. 55-2759)
5, JP-A-56-76745, JP-A-59-771.
No. 47). Further, there has been proposed a high-load transmission belt called a block belt which is constituted by a pair of endless tension bands and a large number of blocks, and the blocks are locked and fixed to the tension bands in the belt longitudinal direction. (JP-A-60-49151, JP-A-61-2)
No. 06847, JP-A-62-54348).
【０００３】この種のブロックベルトにおいては、伝動
可能な負荷に関連するプーリ推力を各ブロックで受ける
構造であり、各ブロック左右両側の当接部とプーリのベ
ルト溝面との間の動摩擦係数（以下、単に摩擦係数μと
いう）は、摩擦伝動能力を高める観点から、通常０．３
以上の値に設定されている。すなわち、自動車用のＣＶ
Ｔシステムでは、エンジンルーム内に配置される関係か
らコンパクト化及び軽量化が要求されるが、同じ変速比
を得るためにベルトの軸方向の移動量が小さく、従って
システム全体の軸方向に沿った大きさが小さくて済むこ
とから、プーリの楔角は小さく設定され、望ましくは３
０°以下とされている。そして、一般的に、上記摩擦係
数μには、この楔角により決まる最適範囲があるが、こ
れまでのＣＶＴシステムでは、高馬力のトルク伝動を優
先する観点から、摩擦係数μが０．３以上の領域で使用
しているのが現状である。This type of block belt has a structure in which each block receives a pulley thrust related to a load that can be transmitted, and a coefficient of kinetic friction between contact portions on both left and right sides of each block and a belt groove surface of the pulley. Hereinafter, simply referred to as a friction coefficient μ) is usually 0.3
It is set to the above value. That is, CV for automobile
In the T system, compactness and weight reduction are required due to the arrangement in the engine room, but the amount of movement of the belt in the axial direction is small in order to obtain the same gear ratio, and therefore, the T Since the size can be small, the wedge angle of the pulley is set to be small, preferably 3
0 ° or less. In general, the friction coefficient μ has an optimum range determined by the wedge angle. However, in the conventional CVT system, the friction coefficient μ is 0.3 or more from the viewpoint of giving priority to high horsepower torque transmission. It is currently used in the area.
【０００４】しかし、このように摩擦係数μを高く設定
すると、ベルト走行時の騒音レベルが高くなるととも
に、プーリからのベルトの抜け性が悪くなり、ブロック
に異常な力が発生してその早期破壊や張力帯の切断等を
招くという不具合がある。そのため、プーリとベルトと
の間の摩擦係数μを、伝動能力からと騒音レベルからの
中間点に設定するため、騒音レベルが十分低い点に摩擦
係数μを設定できないという問題点がある。However, when the friction coefficient μ is set to a high value as described above, the noise level during running of the belt becomes high, and the pull-out property of the belt from the pulley is deteriorated. Or the cutting of the tension band. Therefore, since the friction coefficient μ between the pulley and the belt is set at an intermediate point between the transmission capacity and the noise level, there is a problem that the friction coefficient μ cannot be set at a point where the noise level is sufficiently low.
【０００５】[0005]
【課題を解決するための手段】本発明は上記従来の問題
点に鑑み案出したものであって、請求項１の発明では、
多数のブロックが張力帯に対しベルト長手方向に係止固
定されてなる高負荷伝動用ブロックベルトを、駆動プー
リ及び従動プーリの各ベルト溝面に当接状に巻きかけて
なるベルト駆動システムにおいて、上記ブロックベルト
のブロックのベルト溝面に対する当接面は樹脂材で構成
され、上記プーリのうち、少なくとも一方のプーリのベ
ルト溝面の面粗度を、円周方向の面粗度がＲａ０．２５
以下になるように設定し、半径方向の面粗度がＲａ０．
３５以上になるように設定した構成としている。SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned conventional problems.
In a belt driving system in which a high load transmission block belt in which a number of blocks are locked and fixed in a belt longitudinal direction with respect to a tension band is wound around each belt groove surface of a driving pulley and a driven pulley in an abutting manner, The contact surface of the block of the block belt with respect to the belt groove surface is made of a resin material, and the surface roughness of the belt groove surface of at least one of the pulleys is defined as Ra0.25 in the circumferential direction.
The surface roughness in the radial direction is Ra0.
The configuration is set so as to be 35 or more.
【０００６】請求項２の発明では、多数のブロックが張
力帯に対しベルト長手方向に係止固定されてなる高負荷
伝動用ブロックベルトを、駆動プーリ及び従動プーリの
各ベルト溝面に当接状に巻きかけてなるベルト駆動シス
テムにおいて、上記ブロックベルトのブロックのベルト
溝面に対する当接面は樹脂材で構成され、上記プーリの
うち、少なくとも一方のプーリのベルト溝面に、円周方
向に微少な溝を形成した構成としている。According to the second aspect of the present invention, a high-load transmission block belt in which a number of blocks are locked and fixed in a belt longitudinal direction with respect to a tension band is formed in abutment with respective belt groove surfaces of a driving pulley and a driven pulley. In the belt driving system, the contact surface of the block belt with respect to the belt groove surface of the block is formed of a resin material, and the belt groove surface of at least one of the pulleys is minutely circumferentially formed. It has a configuration in which a simple groove is formed.
【０００７】[0007]
【実施例】以下、本発明の実施例を図面に基づいて説明
する。図１は、この発明の一実施例に係る高負荷伝動用
のベルト駆動システムＡを模式的に示し、このベルト駆
動システムは例えば自動車の変速機（ＣＶＴ）として使
用される。１，２はそれぞれ互いに並行に配置支持され
た駆動軸及び従動軸であって、上記駆動軸１には可変プ
ーリからなる駆動プーリ３が、また従動軸２には同様の
従動プーリ７がそれぞれ設けられている。上記駆動プー
リ３は、駆動軸１に回転一体にかつ摺動不能に固定され
たフランジ状の固定シーブ４と、該固定シーブ４に対向
するように駆動軸１に摺動可能にかつ回転一体にスプラ
イン等により結合されたフランジ状の可動シーブ５とか
らなり、これら両シーブ４，５間には所定の楔角（例え
ば２６°）を有する断面Ｖ字状のベルト溝面６が形成さ
れている。Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 schematically shows a belt drive system A for high-load transmission according to an embodiment of the present invention, and this belt drive system is used, for example, as a transmission (CVT) of an automobile. Reference numerals 1 and 2 denote a driving shaft and a driven shaft arranged and supported in parallel with each other. The driving shaft 1 is provided with a driving pulley 3 composed of a variable pulley, and the driven shaft 2 is provided with a similar driven pulley 7. Have been. The drive pulley 3 includes a flange-shaped fixed sheave 4 fixed to the drive shaft 1 so as to be rotatable and non-slidable, and slidably and rotatable integrally with the drive shaft 1 so as to face the fixed sheave 4. It comprises a flange-shaped movable sheave 5 connected by a spline or the like, and a belt groove surface 6 having a V-shaped cross section having a predetermined wedge angle (for example, 26 °) is formed between the sheaves 4 and 5. .
【０００８】一方、従動プーリ７は、上記駆動プーリ３
と同様の構成であり、従動軸２に回転一体にかつ摺動不
能に固定された固定シーブ８と、該固定シーブ８に、上
記駆動プーリ３における固定シーブ４に対する可動シー
ブ５の対向方向と逆方向でもって対向するように従動軸
２に摺動可能にかつ回転一体に結合された可動シーブ９
とからなり、これらの両シーブ８，９間には、上記駆動
プーリ３と同じ楔角を有するベルト溝面１０が形成され
ている。On the other hand, the driven pulley 7 is
And a fixed sheave 8 fixed to the driven shaft 2 so as to be rotatable integrally and non-slidably, and the fixed sheave 8 is provided with a movable sheave 5 opposite to the fixed sheave 4 of the drive pulley 3 in the opposite direction. Movable sheave 9 slidably and integrally rotatably coupled to the driven shaft 2 so as to face each other
A belt groove surface 10 having the same wedge angle as the drive pulley 3 is formed between the sheaves 8 and 9.
【０００９】そして、上記駆動プーリ３及び従動プーリ
７のベルト溝面６，１０間には、図２および図３に示す
ようなブロックベルトＢが巻き掛けられている。ブロッ
クベルトＢは、上下面にそれぞれ長手方向に並んで形成
された多数の契合部を有し、かつ内部に心線が埋設され
たエンドレスの平ベルトからなる一対の張力帯１１，１
１と、左右側面に上記張力帯１１，１１を嵌合する切欠
状の嵌合溝と、左右側面にプーリのベルト溝面６，１０
に当接する当接面１２ｂ，１２ｂとを有する多数のブロ
ック１２，１２で構成されている。尚、各ブロック１２
の当接面１２ｂ，１２ｂは樹脂材１２ａで構成されてい
る。A block belt B as shown in FIGS. 2 and 3 is wound between the belt groove surfaces 6 and 10 of the driving pulley 3 and the driven pulley 7. The block belt B has a large number of engagement portions formed on the upper and lower surfaces thereof in a longitudinal direction, and a pair of tension belts 11, 1 each composed of an endless flat belt having a core wire embedded therein.
1, a notch-shaped fitting groove on the left and right sides for fitting the tension bands 11, 11, and a belt groove surface 6, 10 of the pulley on the left and right sides.
And a large number of blocks 12 having contact surfaces 12b. Each block 12
The contact surfaces 12b, 12b are made of a resin material 12a.
【００１０】図示しないモーター等からなる変速機構に
より駆動及び従動プーリ３，７の各可動シーブ５，９を
それぞれ固定シーブ４，８に対して接離させて各プーリ
３，７のプーリ径（ベルトＢに対する有効半径）を変更
する。例えば駆動プーリ３の可動シーブ５を固定シーブ
４に接近させ、かつ従動プーリ７の可動シーブ９を固定
シーブ８から離隔させた時には、駆動プーリ３のプーリ
径を従動プーリ７よりも大きくすることにより、駆動軸
１の回転を従動軸２に増速して伝動することができる。
一方、逆に、図示のように、駆動プーリ３の可動シーブ
５を固定シーブ４から離隔させ、かつ従動プーリ７の可
動シーブ９を固定シーブ８に接近させたときには、駆動
プーリ３のプーリ径を小にし、従動プーリ７のプーリ径
を大きくすることにより、駆動軸１の回転を減速して従
動軸２に伝えることができるものである。The movable sheaves 5 and 9 of the drive and driven pulleys 3 and 7 are moved toward and away from the fixed sheaves 4 and 8 by a speed change mechanism including a motor or the like (not shown) so that the pulley diameter (belt) of each pulley 3 and 7 is changed. (Effective radius for B) is changed. For example, when the movable sheave 5 of the driving pulley 3 approaches the fixed sheave 4 and the movable sheave 9 of the driven pulley 7 is separated from the fixed sheave 8, the diameter of the driving pulley 3 is made larger than that of the driven pulley 7. The rotation of the drive shaft 1 can be transmitted to the driven shaft 2 at an increased speed.
On the other hand, when the movable sheave 5 of the driving pulley 3 is separated from the fixed sheave 4 and the movable sheave 9 of the driven pulley 7 approaches the fixed sheave 8 as shown in the drawing, the diameter of the driving pulley 3 is reduced. By reducing the diameter of the driven pulley 7 and increasing the diameter of the driven pulley 7, the rotation of the drive shaft 1 can be reduced and transmitted to the driven shaft 2.
【００１１】なお、発明者らは、ベルト溝面６，１０の
面粗度Ｒａを変えたプーリを作成して、摩擦係数μを測
定したところ、図４のような結果が得られ、この結果か
ら、面粗度Ｒａが粗くなると摩擦係数μが低くなること
が判明した。The inventors made pulleys having different surface roughnesses Ra of the belt groove surfaces 6 and 10 and measured the friction coefficient μ. As a result, the results shown in FIG. 4 were obtained. From this, it was found that when the surface roughness Ra became rough, the friction coefficient μ became low.
【００１２】次に、発明者らは、駆動プーリ３と従動プ
ーリ７とを図１に示すようなレイアウトに配置し、これ
らプーリ間にブロックベルトＢを巻き掛けてベルト走行
させ、騒音テストを行った。Next, the inventors arranged the driving pulley 3 and the driven pulley 7 in a layout as shown in FIG. 1, wrapped the block belt B between these pulleys and caused the belt to run, and performed a noise test. Was.
【００１３】騒音テストにおいて、例１では、駆動プー
リ３及び従動プーリ７とも、ベルト溝面６，１０の、半
径方向の面粗度Ｒａを３．０、円周方向の面粗度Ｒａを
０．２に設定したところ、ベルト騒音は６７ｄＢであっ
た。また、この条件でのブロックベルトＢの伝達能力は
十分であった。（図５のスリップテストのａ線で示
す。）In the noise test, in Example 1, both the drive pulley 3 and the driven pulley 7 have a surface roughness Ra of 3.0 on the belt groove surfaces 6 and 10 and a surface roughness Ra of 0 on the circumferential direction. .2, the belt noise was 67 dB. The transmission capacity of the block belt B under these conditions was sufficient. (Indicated by line a of the slip test in FIG. 5)
【００１４】次に、例２では、駆動プーリ３及び従動プ
ーリ７とも、ベルト溝面６，１０の、半径方向の面粗度
Ｒａを１．０、円周方向の面粗度Ｒａを０．２に設定し
たところ、ベルト騒音は７３ｄＢであった。また、この
条件でのブロックベルトＢの伝達能力は十分であった。
（図５のスリップテストのａ線で示す。）Next, in Example 2, both the drive pulley 3 and the driven pulley 7 have a surface roughness Ra of 1.0 in the radial direction and a surface roughness Ra of 0.1 in the circumferential direction of the belt groove surfaces 6 and 10. When set to 2, the belt noise was 73 dB. The transmission capacity of the block belt B under these conditions was sufficient.
(Indicated by line a of the slip test in FIG. 5)
【００１５】また、例３では、駆動プーリ３のベルト溝
面６の半径方向の面粗度Ｒａを１．０、従動プーリ７の
ベルト溝面１０の半径方向の面粗度Ｒａを０．２とし、
駆動プーリ３及び従動プーリ７ともベルト溝面６，１０
の円周方向の面粗度Ｒａは０．４に設定したところ、ベ
ルト騒音は７５ｄＢであった。また、この条件でのブロ
ックベルトＢの伝達能力は十分であった。（図５のスリ
ップテストのａ線で示す。）In Example 3, the surface roughness Ra of the belt groove surface 6 of the driving pulley 3 in the radial direction is 1.0, and the surface roughness Ra of the belt groove surface 10 of the driven pulley 7 in the radial direction is 0.2. age,
Both the drive pulley 3 and the driven pulley 7 have belt groove surfaces 6,10.
When the surface roughness Ra in the circumferential direction was set to 0.4, the belt noise was 75 dB. The transmission capacity of the block belt B under these conditions was sufficient. (Indicated by line a of the slip test in FIG. 5)
【００１６】また、例４では、駆動プーリ３及び従動プ
ーリ７とも、ベルト溝面６，１０の、半径方向の面粗度
Ｒａを０．２、円周方向の面粗度Ｒａを０．２に設定し
たところ、ベルト騒音は８０ｄＢであった。また、この
条件でのブロックベルトＢの伝達能力は十分であった。
（図５のスリップテストのａ線で示す。）即ち例４で
は、半径方向の面粗度Ｒａと円周方向の面粗度Ｒａを同
じにした従来例の設定であり、騒音レベルが高いことが
わかる。In Example 4, both the driving pulley 3 and the driven pulley 7 have a surface roughness Ra of 0.2 in the radial direction and a surface roughness Ra in the circumferential direction of the belt groove surfaces 6 and 10 of 0.2. , The belt noise was 80 dB. The transmission capacity of the block belt B under these conditions was sufficient.
(Indicated by the line a of the slip test in FIG. 5.) That is, Example 4 is a setting of the conventional example in which the surface roughness Ra in the radial direction and the surface roughness Ra in the circumferential direction are the same, and the noise level is high. I understand.
【００１７】また、例５では、駆動プーリ３及び従動プ
ーリ７とも、ベルト溝面６，１０の、半径方向の面粗度
Ｒａを１．０、円周方向の面粗度Ｒａを１．０に設定し
たところ、ベルト騒音は７３ｄＢであった。また、この
条件でのブロックベルトＢの伝達能力は不十分であっ
た。（図５のスリップテストのｂ線で示す。）即ち例５
では、騒音レベルは低いが、スリップが発生することが
確認された。In Example 5, both the driving pulley 3 and the driven pulley 7 have the belt groove surfaces 6 and 10 with a radial surface roughness Ra of 1.0 and a circumferential surface roughness Ra of 1.0. , The belt noise was 73 dB. Further, the transmission capacity of the block belt B under these conditions was insufficient. (Indicated by the b line in the slip test in FIG. 5) That is, Example 5
It was confirmed that the noise level was low, but slip occurred.
【００１８】上記の結果を参考にして、伝動能力を高く
維持でき、かつ騒音レベルを十分低くするため、発明者
らは、駆動プーリ３と従動プーリ７のうち、少なくとも
一方のプーリのベルト溝面６，１０の面粗度Ｒａを、円
周方向はＲａ０．２５以下となるように設定し、半径方
向はＲａ０．３５以上となるように設定した。なお、上
記駆動プーリ３と従動プーリ７のベルト溝面６，１０に
は、摩擦係数安定化のため、無電解Ｎｉ−Ｐメッキ等の
コーティングを施すことが望ましい。Referring to the above results, in order to maintain a high transmission capacity and sufficiently reduce the noise level, the inventors have determined that the belt groove surface of at least one of the driving pulley 3 and the driven pulley 7 is not limited. The surface roughness Ra of 6, 10 was set to be Ra 0.25 or less in the circumferential direction, and was set to be Ra 0.35 or more in the radial direction. It is desirable that the belt groove surfaces 6, 10 of the driving pulley 3 and the driven pulley 7 be coated with electroless Ni-P plating or the like in order to stabilize the friction coefficient.
【００１９】なお、図示していないが、プーリ３，７の
うち、少なくとも一方のプーリのベルト溝面６，１０に
円周方向のみに微少な溝を形成しても、従来例よりもベ
ルトの騒音を低減できることを確認した。Although not shown, even if minute grooves are formed only in the circumferential direction on the belt groove surfaces 6 and 10 of at least one of the pulleys 3 and 7, it is possible to make the It was confirmed that noise could be reduced.
【００２０】[0020]
【発明の効果】本発明は、多数のブロックが張力帯に対
しベルト長手方向に係止固定されてなる高負荷伝動用ブ
ロックベルトを、駆動プーリ及び従動プーリの各ベルト
溝面に当接状に巻きかけてなるベルト駆動システムにお
いて、ブロックベルトのブロックのベルト溝面に対する
当接面は樹脂材で構成され、プーリのうち、少なくとも
一方のプーリのベルト溝面の面粗度を、円周方向の面粗
度がＲａ０．２５以下になるように設定し、半径方向の
面粗度がＲａ０．３５以上になるように設定したことに
より、プーリのベルト溝面の面粗度を円周方向と半径方
向で設定を変えて、ベルト走行時の騒音レベルを低くす
ることができ、また、スリップの発生を低減させて満足
いく伝動能力を確保することができ、自動車用の無段変
速機におけるベルト駆動システムにおいて有効に用いる
ことができる効果がある。According to the present invention, a high load transmission block belt in which a number of blocks are locked and fixed in a belt longitudinal direction with respect to a tension band is provided so as to abut on belt groove surfaces of a driving pulley and a driven pulley. In the wound belt drive system, the contact surface of the block belt with respect to the belt groove surface of the block is formed of a resin material, and of the pulleys, the surface roughness of the belt groove surface of at least one of the pulleys is determined in the circumferential direction. By setting the surface roughness to be not more than Ra 0.25 and the surface roughness in the radial direction to be not less than Ra 0.35, the surface roughness of the belt groove surface of the pulley can be changed in the circumferential direction and the radius. By changing the setting in the direction, the noise level during belt running can be reduced, and the occurrence of slip can be reduced to ensure satisfactory transmission performance. There is an effect that can be effectively used in the drive system.
【００２１】また、多数のブロックが張力帯に対しベル
ト長手方向に係止固定されてなる高負荷伝動用ブロック
ベルトを、駆動プーリ及び従動プーリの各ベルト溝面に
当接状に巻きかけてなるベルト駆動システムにおいて、
ブロックベルトのブロックのベルト溝面に対する当接面
は樹脂材で構成され、プーリのうち、少なくとも一方の
プーリのベルト溝面に、円周方向に微少な溝を形成した
ことにより、ベルト騒音を従来より低減できるという効
果がある。Further, a high load transmission block belt, in which a number of blocks are locked and fixed in the belt longitudinal direction with respect to the tension band, is wound around the belt groove surfaces of the driving pulley and the driven pulley in an abutting manner. In the belt drive system,
The contact surface of the block belt against the belt groove surface of the block is made of a resin material. At least one of the pulleys has a small circumferential groove on the belt groove surface of the pulley. There is an effect that it can be further reduced.
【図１】ベルト駆動システムを模式的に示す概略図であ
る。FIG. 1 is a schematic diagram schematically showing a belt drive system.
【図２】ブロックベルトの斜視図である。FIG. 2 is a perspective view of a block belt.
【図３】ブロックの断面図である。FIG. 3 is a sectional view of a block.
【図４】摩擦係数とプーリの面粗度との関係を示す特性
図である。FIG. 4 is a characteristic diagram showing a relationship between a friction coefficient and a surface roughness of a pulley.
【図５】スリップテストの結果を示す特性図である。FIG. 5 is a characteristic diagram showing a result of a slip test.
Ａ 無段変速システム Ｂ ブロックベルト ３ 駆動プーリ ６，１０ ベルト溝面 ７ 従動プーリ １２ ブロック １２ｂ 当接面 A continuously variable transmission system B block belt 3 drive pulley 6, 10 belt groove surface 7 driven pulley 12 block 12b abutment surface
フロントページの続き (72)発明者 宮崎 隆司 名古屋市熱田区川並町２番12号 愛知機械 工業株式会社内 Ｆターム(参考） 3J031 AA01 AB01 AB03 BA04 BB02 BC08 CA02 3J050 AA03 BA03 CD06 CE01 DA02Continued on the front page (72) Inventor Takashi Miyazaki 2-12 Kawanamicho, Atsuta-ku, Nagoya-shi F-term (reference) in Aichi Machine Industry Co., Ltd. 3J031 AA01 AB01 AB03 BA04 BB02 BC08 CA02 3J050 AA03 BA03 CD06 CE01 DA02
Claims (2)
手方向に係止固定されてなる高負荷伝動用ブロックベル
トを、駆動プーリ及び従動プーリの各ベルト溝面に当接
状に巻きかけてなるベルト駆動システムにおいて、上記
ブロックベルトのブロックのベルト溝面に対する当接面
は樹脂材で構成され、上記プーリのうち、少なくとも一
方のプーリのベルト溝面の面粗度を、円周方向の面粗度
がＲａ０．２５以下になるように設定し、半径方向の面
粗度がＲａ０．３５以上になるように設定したことを特
徴とするベルト駆動システム。1. A high load transmission block belt in which a number of blocks are locked and fixed in a belt longitudinal direction with respect to a tension band, is wound around each belt groove surface of a driving pulley and a driven pulley in an abutting manner. In the belt drive system, the contact surface of the block belt with respect to the belt groove surface of the block is formed of a resin material, and the surface roughness of the belt groove surface of at least one of the pulleys is determined by measuring the surface roughness in the circumferential direction. A belt drive system wherein the degree is set so as to be Ra 0.25 or less and the surface roughness in the radial direction is set to Ra 0.35 or more.
手方向に係止固定されてなる高負荷伝動用ブロックベル
トを、駆動プーリ及び従動プーリの各ベルト溝面に当接
状に巻きかけてなるベルト駆動システムにおいて、上記
ブロックベルトのブロックのベルト溝面に対する当接面
は樹脂材で構成され、上記プーリのうち、少なくとも一
方のプーリのベルト溝面に、円周方向に微少な溝を形成
したことを特徴とするベルト駆動システム。2. A high load transmission block belt in which a number of blocks are locked and fixed in a belt longitudinal direction with respect to a tension band, and are wound around the belt groove surfaces of a driving pulley and a driven pulley in an abutting manner. In the belt drive system, the contact surface of the block belt with respect to the belt groove surface of the block is formed of a resin material, and a small groove is formed in the circumferential direction on the belt groove surface of at least one of the pulleys. A belt drive system, characterized in that:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000200008A JP3743902B2 (en) | 2000-06-30 | 2000-06-30 | Belt drive system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000200008A JP3743902B2 (en) | 2000-06-30 | 2000-06-30 | Belt drive system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2002021956A true JP2002021956A (en) | 2002-01-23 |
| JP3743902B2 JP3743902B2 (en) | 2006-02-08 |
Family
ID=18697944
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2000200008A Expired - Fee Related JP3743902B2 (en) | 2000-06-30 | 2000-06-30 | Belt drive system |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3743902B2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7276002B2 (en) * | 2003-10-23 | 2007-10-02 | General Motors Corporation | Surface texture configuration for CVT pulley |
| JP2011122700A (en) * | 2009-12-14 | 2011-06-23 | Toyota Motor Corp | Belt-type continuously variable transmission |
| JP2021038845A (en) * | 2019-08-28 | 2021-03-11 | 三ツ星ベルト株式会社 | Pulley for belt type continuous speed variation device and belt type continuous speed variation device |
-
2000
- 2000-06-30 JP JP2000200008A patent/JP3743902B2/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7276002B2 (en) * | 2003-10-23 | 2007-10-02 | General Motors Corporation | Surface texture configuration for CVT pulley |
| JP2011122700A (en) * | 2009-12-14 | 2011-06-23 | Toyota Motor Corp | Belt-type continuously variable transmission |
| JP2021038845A (en) * | 2019-08-28 | 2021-03-11 | 三ツ星ベルト株式会社 | Pulley for belt type continuous speed variation device and belt type continuous speed variation device |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3743902B2 (en) | 2006-02-08 |
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