JP2004183764A - Wrapped v belt with notch - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a wrapped V belt with notch having remarkably low bending resistance, high power transmission efficiency and proper bending rigidity. <P>SOLUTION: A compression part 5, a neutral part 6 and a tension part 7 are wrapped by canvas 3, and a plurality of notches 2 are formed on the compression part 5 while keeping a specific interval between the notches 2 in the longitudinal direction of the belt. The notch 2 has two side faces 2a, 2b extended from a circular arc-shaped apex 10 toward a bottom face of the compression part. Conditions that hc×0.35≤H≤hc×0.69, hc×0.85≤P≤hc×1.73, and H×0.70≤W≤H×1.13 are satisfied, when a thickness of the compression part 5 is hc, a height of the notch 2 from the circular arc apex to the bottom face of the compression part 5 is H, and an interval at a corresponding part of the notches 2 adjacent to each other in the longitudinal direction of the belt is P. <P>COPYRIGHT: (C)2004,JPO&NCIPI

Description

【００２７】
【表２】

【００２８】
（２）試験方法
試験装置の概略配置は、図５に示すとおりである。図５において、２１はモータ、２２、２３はトルク検出器、２４、２５はプーリ、２６はベルト、２７は負荷機である。
（３）試験結果
ａ．Ａ形ベルト
図５に示す試験装置において、負荷機２７の重量を５０ｋｇとし、プーリ２４と２５の外径は６７ｍｍとし、これらのプーリにＡ形ベルトを２本掛けた場合における伝動効率、スリップ率およびベルト曲げ剛性の測定試験結果を、それぞれ図６（ａ）、図６（ｂ）、図６（ｃ）に示す。
【００２９】
図６および後記する図７〜９において、実線は実施例（本発明）のベルト、破線は比較例１のベルト、一点鎖線は比較例２のベルトを示す。
【００３０】
なお、伝動効率、スリップ率およびベルト曲げ剛性は、それぞれ以下のような式にて算出した。
【００３１】
伝動効率＝（負荷機側動力／モータ側動力）×１００（％）
スリップ率＝（（Ｉ_０−Ｉ_ｔ）／Ｉ_ｔ）×１００（％）
Ｉ_０＝Ｎ_ｎ０／Ｎ_ｒ０、Ｉ_ｔ＝Ｎ_ｎｔ／Ｎ_ｒｔ
Ｎ_ｒ０：無負荷時のモータ側軸回転数
Ｎ_ｒｔ：負荷時のモータ側軸回転数
Ｎ_ｎ０：無負荷時の負荷機側軸回転数
Ｎ_ｎｔ：負荷時の負荷機側軸回転数
ベルト曲げ剛性については、図１０に示すように、パンタグラフ形状の部材３１の内側にベルト３２を挿入して、部材３１を介してベルト３２に負荷する荷重（Ｗ）３３を変化させたときの変位量ｂ_０ を測定し、このｂ_０ に基づいて上下のベルトの曲げ中心（中立位置）間の距離ｂを算出し、次式よりベルト曲げ剛性ＥＩを求めた。
【００３２】
ＥＩ＝０．１７４１５×Ｗ×ｂ^２（ｋｇｆ ｃｍ^２）
以下、Ｂ形ベルト、Ｃ形ベルト、Ｄ形ベルトにおいても同様の方法により伝動効率とスリップ率とベルト曲げ剛性を求めた。
【００３３】
図６（ａ）に示されているように、実施例のベルトは最も伝動効率が高く、図６（ｂ）に示されているように、実施例のベルトは最もスリップしにくく、図６（ｃ）に示されているように、実施例のベルトは最もベルト曲げ剛性が低い（曲げ抵抗が小さい）。
ｂ．Ｂ形ベルト
図５に示す試験装置において、負荷機２７の重量を１００ｋｇとし、プーリ２４と２５の外径は１１８ｍｍとし、これらのプーリにＢ形ベルトを３本掛けた場合における伝動効率、スリップ率およびベルト曲げ剛性の測定試験結果を、それぞれ図７（ａ）、図７（ｂ）、図７（ｃ）に示す。
【００３４】
図７（ａ）に示されているように、実施例のベルトは最も伝動効率が高く、図７（ｂ）に示されているように、実施例のベルトは最もスリップしにくく、図７（ｃ）に示されているように、実施例のベルトは最もベルト曲げ剛性が低い（曲げ抵抗が小さい）。
ｃ．Ｃ形ベルト
図５に示す試験装置において、負荷機２７の重量を９０ｋｇ（伝動効率測定時）または５０ｋｇ（スリップ率測定時）とし、プーリ２４と２５の外径は１８０ｍｍとし、これらのプーリにＣ形ベルトを１本掛けた場合における伝動効率、スリップ率およびベルト曲げ剛性の測定試験結果を、それぞれ図８（ａ）、図８（ｂ）、図８（ｃ）に示す。
【００３５】
図８（ａ）に示されているように、実施例のベルトは最も伝動効率が高く、図８（ｂ）に示されているように、実施例のベルトは最もスリップしにくく、図８（ｃ）に示されているように、実施例のベルトは最もベルト曲げ剛性が低い（曲げ抵抗が小さい）。
【００３６】
ｄ．Ｄ形ベルト
図５に示す試験装置において、負荷機２７の重量を１８０ｋｇ（伝動効率測定時）または２３０ｋｇ（スリップ率測定時）とし、プーリ２４と２５の外径は２８５ｍｍとし、これらのプーリにＤ形ベルトを１本掛けた場合における伝動効率、スリップ率およびベルト曲げ剛性の測定試験結果を、それぞれ図９（ａ）、図９（ｂ）、図９（ｃ）に示す。
【００３７】
図９（ａ）に示されているように、実施例のベルトは最も伝動効率が高く、図９（ｂ）に示されているように、実施例のベルトは標準品である比較例２に対して比較例１と同じようにスリップしにくく、図９（ｃ）に示されているように、実施例のベルトは最もベルト曲げ剛性が低い（曲げ抵抗が小さい）。
【００３８】
さらに、本発明のノッチ付きラップドＶベルトを送風機の動力伝達用ベルトとして用いた場合の省エネルギー効果と、無負荷耐久性能について、具体的なデータに基づいて説明する。
（１）省エネルギー効果
ａ．試験その１
図１１に示すように、直径１４４ｍｍの駆動プーリ４１と直径１６７．５ｍｍの従動プーリ４２との間にＢ形ベルト４３を３本懸回して、２００１年５月２２日から２００１年６月５日にかけて高温（１２０℃）の空気を給気する送風機の動力伝達用ベルトとして用いた場合（２４時間連続稼働）、本発明のベルトの平均消費電力は、３．４０４ｋｗであり、比較例２のベルト（現標準品）の平均消費電力は３．５１３ｋｗであった。すなわち、本発明のベルトによれば、標準品のベルトに対して３．１０％の省エネルギー効果がある。なお、駆動ベルト４１のモータの規格は、５．５ｋｗ、１７４０ｒｐｍ である。
ｂ．試験その２
図１２に示すように、直径１８０ｍｍの駆動プーリ５１と直径３０５ｍｍの従動プーリ５２との間にＣ形ベルト５３を５本懸回して、２００１年１月１３日から２００１年２月２６日にかけて標準大気を排気する送風機の動力伝達用ベルトとして用いた場合（２４時間連続稼働）、本発明のベルトの平均消費電力は、９．５５ｋｗであり、比較例２のベルト（現標準品）の平均消費電力は９．８９ｋｗであった。すなわち、本発明のベルトによれば、標準品のベルトに対して３．４４％の省エネルギー効果がある。なお、駆動ベルト５１のモータの規格は、２．２ｋｗ、１４５０ｒｐｍ である。
ｃ．試験その３
図１３に示すように、直径１７０ｍｍの駆動プーリ６１と直径１２７ｍｍの従動プーリ６２との間にＢ形ベルト６３を３本懸回して、２００１年５月２９日から２００１年６月２４日にかけて標準大気を排気する送風機の動力伝達用ベルトとして用いた場合（２４時間連続稼働）、本発明のベルトの平均消費電力量は、４．５１６ｋｗｈであり、比較例２のベルト（現標準品）の平均消費電力量は、４．６４２ｋｗであった。すなわち、本発明のベルトによれば、標準品のベルトに対して２．７１％の省エネルギー効果がある。なお、駆動ベルト６２のモータの規格は、５．５ｋｗ、１７３５ｒｐｍ である。
（２）無負荷耐久性能
一般に、動力伝達用ベルトに使用されるゴムは、使用時の摩擦による発熱に伴って徐々に硬化し、硬化が進行すると、やがて屈曲疲労によりベルト底部に亀裂が入り、破損に至るという経過をたどることが多い。そこで、ベルト形態の違いによる耐久性能を比較するために、以下のような試験を行った。
【００３９】
図１４（ａ）に示すように、同一径のプーリ７１と７２の間にＢ形ベルト７３を１本懸回して、従動側プーリ７２の軸荷重を８０ｋｇｆ とし、駆動側プーリ７１を４８００ｒｐｍ で回転させたとき、プーリ径が８０ｍｍ、１００ｍｍ、１１８ｍｍのそれぞれの場合におけるベルトの破損に至るまでの時間を図１４（ｂ）に示す。図１４（ｂ）および後記する図１５において、実線は実施例（本発明）のベルト、破線は比較例１のベルト、一点鎖線は比較例２のベルトを示す。
【００４０】
図１４（ｂ）に示すように、実施例のベルトは適性な形状のノッチが付与されているので、屈曲性が良好で、曲げ抵抗が小さいのでベルトの発熱が低く、ゴムの硬化が進みにくい。その結果、図１４（ｂ）に示すように、実施例のベルトは、最も耐久性能が優れている。図１５は、上記無負荷耐久性能試験中におけるベルト底面の平均温度を比較する図であり、いずれのプーリ径においても実施例のベルトの温度が最も低く、本発明に係る実施例のベルトの耐久性能が優れていることの証左である。
【００４１】
【発明の効果】
本発明は上記のように構成されているので、曲げ抵抗が極めて小さく、しかも、伝動効率が高くて、適度の曲げ剛性を有するノッチ付きラップドＶベルトを提供することができる。特に、ラップドＶベルトであるから、動力伝達時の騒音が小さく、送風機のように連続使用される機器の動力伝達用ベルトとして用いた場合、伝動効率が向上することによる省エネルギー効果は極めて大きい。
【図面の簡単な説明】
【図１】図１（ａ）はラップドＶベルトの斜視図、図１（ｂ）はノッチ付きラップドＶベルトの斜視図である。
【図２】図２（ａ）はローエッジベルトの斜視図、図２（ｂ）はノッチ付きローエッジベルトの斜視図である。
【図３】入力側プーリと出力側プーリにノッチ付きＶベルトを巻き付けた状態を示す図である。
【図４】図４（ａ）は本発明のノッチ付きラップドＶベルトの側面図、図４（ｂ）は図４（ａ）のＩＶ−ＩＶ矢視断面図、図４（ｃ）は図４（ａ）とは異なる形状のノッチを有するノッチ付きラップドＶベルトの側面図である。
【図５】伝動効率、スリップ率およびベルト剛性の測定装置の概略配置図である。
【図６】図６（ａ）（ｂ）（ｃ）は、それぞれ表１に示す仕様のＡ形ベルトの伝動効率、スリップ率およびベルト剛性を示す図である。
【図７】図７（ａ）（ｂ）（ｃ）は、それぞれ表１に示す仕様のＢ形ベルトの伝動効率、スリップ率およびベルト剛性を示す図である。
【図８】図８（ａ）（ｂ）（ｃ）は、それぞれ表１に示す仕様のＣ形ベルトの伝動効率、スリップ率およびベルト剛性を示す図である。
【図９】図９（ａ）（ｂ）（ｃ）は、それぞれ表１に示す仕様のＤ形ベルトの伝動効率、スリップ率およびベルト剛性を示す図である。
【図１０】ベルト曲げ剛性を測定する試験方法を説明する図である。
【図１１】本発明のノッチ付きラップドＶベルトの省エネルギー効果を求めるためのベルト走行試験方法を示す概略図である。
【図１２】本発明のノッチ付きラップドＶベルトの省エネルギー効果を求めるためのベルト走行試験方法を示す概略図である。
【図１３】本発明のノッチ付きラップドＶベルトの省エネルギー効果を求めるためのベルト走行試験方法を示す概略図である。
【図１４】図１４（ａ）は、ベルトの無負荷耐久性能を測定する試験方法を示す概略図であり、図１４（ｂ）その試験結果を示す図である。
【図１５】図１４（ａ）に示すベルトの無負荷耐久性能を測定する試験中のベルト底面の平均温度を示す図である。
【符号の説明】
１…ノッチ付きラップドＶベルト
２、２ａ、１２…ノッチ
３…帆布
５…圧縮部
６…中立部
６ａ…接着ゴム層
７…引っ張り部
８…張力帯
９…コグ
１０…円弧状の頂部
１１…ローエッジベルト
１４、１５…プーリ
ｈｃ…圧縮部の厚さ
Ｈ…ノッチの高さ
Ｐ…ノッチの間隔
Ｗ…ノッチの開口幅[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a notched wrapped V-belt, and more particularly, to a notched wrapped V-belt suitable for a power transmission belt of a blower, which is characterized by the shape, size and arrangement of a notch provided in a compression portion of the V-belt. .
[0002]
[Prior art]
2. Description of the Related Art Conventionally, notching a compression portion of a V-belt for the purpose of relieving stress concentration on the V-belt caused by dynamic bending when the V-belt for power transmission is wound around a pulley and rotated has been widely practiced. Has been done. Due to the effect of reducing the stress concentration of the notch, the crack in the V-belt compression part is minimized, and the V-belt can be wound around a small pulley (for example, see Patent Documents 1 and 2).
[0003]
Patent Literature 1 discloses a V-belt having a notch in which the curvature at the center of the notch is larger than the curvature at the end of the notch. Further, Patent Literature 2 discloses a V-belt in which parameters of the notch depth, the radius of the arc-shaped top of the notch, the interval between the notches, and the angle formed by the two side surfaces forming the notch are indicated by parameters.
[0004]
According to the V-belt with a notch described in Patent Documents 1 and 2, the following effects can be expected.
[0005]
Stress concentration in the compression portion of the V-belt is reduced, cracks in the compression portion of the V-belt are minimized, and the V-belt can be wound around a small-diameter pulley.
[0006]
By forming the notch in the compression portion of the V-belt as described above, the bending resistance when the V-belt is wound around the pulley is reduced, and the above-described effect can be expected.
[0007]
However, the area of the side of the belt decreases with the notch, and the rigidity of the side surface of the belt, which is the power transmission unit, decreases, so that the efficiency of power actually transmitted to the input power (transmission efficiency) decreases. Sometimes. Further, depending on the size of the opening of the notch, it is not possible to withstand bending fatigue, and the notch may rather shorten the life of the belt. Thus, the optimum notch shape of the notched V-belt for power transmission has not been proposed so far.
[0008]
[Patent Document 1] US Pat. No. 2,625,828 [Patent Document 2]
US Pat. No. 3,626,775.
[Problems to be solved by the invention]
In other words, the notch on the V-belt has the effect of making it easy to wind around the pulley, but on the other hand, the notch is a portion that does not contribute to the transmission of power, and the presence of the notch increases the power loss. There are disadvantages. Further, the bending strength may be reduced due to the notch, and the durability of the belt may be reduced.
[0010]
Further, a canvas is attached only to the lower surface of the compression portion and the upper surface of the tension portion of the V-belt including the compression portion, the neutral portion, and the tension portion, and the belt side which is the power transmission surface is not covered with the canvas. "Low edge belt") has high transmission efficiency and low power loss. However, the low-edge belt has a drawback that noise is loud because the belt side which is a power transmission surface is made of rubber, and using a low-edge belt as a power transmission belt for continuously used equipment, for example, a blower, is disadvantageous in terms of noise. There's a problem.
[0011]
On the other hand, a belt in which the entire outer peripheral surface of a V-belt including a compression portion, a neutral portion, and a tension portion is covered with canvas (this belt is referred to as a “wrapped V-belt” in this specification) has an advantage of extremely low noise. It is suitable as a power transmission belt for equipment used continuously such as a blower. However, the wrapped V-belt has a disadvantage that the transmission efficiency is slightly lower than that of the low-edge belt.
[0012]
SUMMARY OF THE INVENTION The present invention has been made in view of such problems of the prior art, and has as its object the purpose of extremely low bending resistance, high transmission efficiency (low energy loss), and moderate An object of the present invention is to provide a notched wrapped V-belt having bending rigidity and suitable as a power transmission belt for a blower.
[0013]
[Means for Solving the Problems]
In order to achieve the above object, the present invention provides a notch in a compression portion of a wrapped V-belt having a compression portion, a neutral portion, and a tension portion, a thickness of the compression portion being hc, a height of the notch being H, In the case where the interval between the corresponding portions of the notches adjacent in the longitudinal direction of the belt is P and the opening width of the notch is W, the notch height H, the interval P between the notches, and the opening width W of the notch are respectively within appropriate ranges. By setting, it is possible to provide an energy-saving notched wrapped V-belt having low bending resistance, appropriate bending rigidity, and high transmission efficiency.
[0014]
BEST MODE FOR CARRYING OUT THE INVENTION
That is, the notched wrapped V-belt of the present invention is a V-shaped V-shaped belt having a compression portion, a tension portion, and a neutral portion between the compression portion and the tension portion, wherein the compression portion, the neutral portion, and the tension portion In a notched wrapped V-belt in which a plurality of notches are formed in the compression section with a predetermined interval provided between the notches in the longitudinal direction of the belt, the notches face from the top to the bottom of the compression section. Hc, the height of the notch from the top of the notch to the bottom of the compression portion is H, and the interval between corresponding portions of adjacent notches in the longitudinal direction of the belt is P. When the opening width of the notch at the bottom of the compression portion is W, the height H of the notch, the interval P between the notches, and the opening width W of the notch are respectively in the following ranges.
[0015]
As for the height H of the notch, hc × 0.35 ≦ H ≦ hc × 0.69,
The notch interval P is hc × 0.85 ≦ P ≦ hc × 1.73,
The opening width W of the notch is H × 0.70 ≦ W ≦ H × 1.13.
[0016]
The V belts 1 and 11 having a V-shaped cross section as shown in FIGS. 1A and 2A have a large bending resistance. The V belt is wound around pulleys 14 and 15 shown in FIG. When transmitting power to the output side pulley 15, constant power is consumed due to bending resistance. Therefore, it is preferable to suppress this useless power consumption as much as possible in order to increase energy efficiency. That is, as shown in FIGS. 1 (b) and 2 (b), by attaching notches 2 and 12 to V-shaped belts 1 and 11, respectively, having a V-shaped cross section, bending resistance is reduced, and wasteful resistance is reduced. The power consumption (loss power) can be reduced, the power (actual power) consumed by the load on the output side can be increased, and the ratio of the loss power can be reduced. In this case, the V-belt (the belt attached to only the upper surface and the lower surface of the belt, and the side not covered with the canvas, that is, the low-edge belt) 11 shown in FIG. 2 and the wrapped V-belt 1 (the belt) shown in FIG. Comparing the belt whose entire outer peripheral surface is covered with the canvas 3), the actual power of the low-edge belt 11 whose power transmission surface is a rubber side surface is rubber is larger than that of the wrapped V-belt 1, and conversely, the loss of the wrapped V-belt 1 The power is greater than the low edge belt 11.
[0017]
On the other hand, both the low-edge belt 11 and the wrapped V-belt 1 have a power transmission surface, the side surface 13 of the low-edge belt 11 is made of rubber, and the side surface 4 of the wrapped V-belt 1 is canvas. Is larger than the wrapped V-belt 1, and the noise of the low edge belt 11 is larger than that of the wrapped V-belt 1 due to the large friction coefficient, and this noise is large in continuously used equipment (for example, a blower). It becomes a problem. Therefore, there is a problem in using the low edge belt as the power transmission belt of the blower.
[0018]
Therefore, as shown in FIG. 1 (b), by providing a notch 2 on the wrapped V-belt 1, it is possible to provide a wrapped V-belt in which power loss due to belt bending is small and noise during power transmission is low. In particular, the notched wrapped V-belt of the present invention is characterized by notch height, notch spacing, and notch opening width, and is used as a power transmission belt for equipment used continuously such as a blower. When a wrapped V-belt with a notch is used, the energy saving effect becomes extremely large. Hereinafter, the reason for limiting the notch shape of the notched wrapped V-belt of the present invention will be specifically described.
(1) Notch height H As shown in FIG. 4A, when the height of the notch 2 from the vertex of the arc to the bottom of the compressed portion is H, if the height of the notch 2 is low, it is sufficient. The bending resistance cannot be reduced. Therefore, as shown in FIG. 4B, when the thickness of the compressed portion is hc, it is preferable to determine the height H of the notch 2 such that hc × 0.35 ≦ H. On the other hand, if the height H of the notch 2 is too large, the bending strength decreases, and the bending fatigue property decreases. Therefore, it is preferable to determine the height H of the notch 2 so that H ≦ hc × 0.69. .
[0019]
In FIG. 4A, the top of the notch 2 has an arc shape, but the shape of the notch top is not necessarily limited to the arc shape. As shown in FIG. The shape may be sharp. However, the notch 2a having a sharp tip has an inconvenience that stress concentration tends to occur in the notch itself as compared with the notch 2 having an arc-shaped tip. Therefore, the notch 2 shown in FIG. Is more preferred.
(2) Notch Interval P As shown in FIG. 4A, when the interval between corresponding portions (vertices) of adjacent notches in the longitudinal direction of the belt is P, if the interval P between the notches 2 is too short ( In other words, if the number of notches is too large, the area required for power transmission cannot be sufficiently secured, and the transmission efficiency may be reduced. The durability is reduced. Therefore, it is preferable to determine the interval P between the notches 2 so that hc × 0.85 ≦ P. On the other hand, if the interval P between the notches 2 is too long (that is, if the number of notches is too small), the bending resistance cannot be sufficiently reduced. Therefore, it is preferable to determine the interval P between the notches 2 so that P ≦ hc × 1.73.
(3) Regarding the opening width W of the notch As shown in FIG. 4A, when the opening width of the notch 2 at the bottom of the compression portion is W, if the W is too short, both ends forming the notch 2 when wound around the pulley. Since the portions contact each other and the notch forming surfaces 2a and 2b may be damaged, it is preferable to determine the opening width W of the notch 2 such that H × 0.70 ≦ W. On the other hand, if the opening width W of the notch 2 is too large, the area required for power transmission cannot be sufficiently secured, so that the transmission efficiency may decrease. In addition, since the required rigidity cannot be secured on the side surface of the belt, the durability of the belt decreases. Therefore, it is preferable to determine the opening width W of the notch 2 such that W ≦ H × 1.13.
[0020]
As described above, according to the present invention, by setting the notch height, the notch interval, and the notch opening width in appropriate ranges, the bending resistance is small, the transmission efficiency is high, and the bending rigidity is appropriate. A notched wrapped V-belt can be provided.
[0021]
【Example】
Hereinafter, embodiments of the present invention will be described with reference to the drawings. However, appropriate modifications and changes can be made without departing from the technical scope of the present invention.
[0022]
In FIG. 4B, the notched wrapped V-belt 1 includes a compression part 5, a neutral part 6, and a tension part 7. The entire outer peripheral surface of the compression part 5, the neutral part 6, and the tension part 7 is covered with the canvas 3. The compression part 5 forming the lower part of the belt is made of chloroprene rubber, but other materials having a high elastic modulus may be used. A neutral portion 6 is provided immediately above the compression portion 5, and the neutral portion 6 has a number of tension bands (SUS steel wires) 8 as a support embedded in an adhesive rubber layer (chloroprene rubber) 6a. The tension band 8 is buried along the longitudinal direction of the belt at a distance in the width direction of the belt. The adhesive rubber layer 6a may be a rubber composition containing a reinforcing material sufficient to support the tension band 8 and having sufficient tackiness to bind the tension band 8. Immediately above the neutral part 6, there is a tension part 7 made of chloroprene rubber forming the upper part of the belt.
[0023]
As shown in FIG. 4A, a number of notches 2 are formed in the compression section 5 so as to have a predetermined interval in the longitudinal direction of the belt. A cog (teeth) 9 is formed between the notches 2. The notch 2 has two side surfaces 2 a and 2 b extending from the arc-shaped top 10 to the opening on the bottom surface of the compression unit 5 so as to increase in diameter.
[0024]
The presence of the notch 2 reduces bending resistance, so that the notched lap V-belt 1 can be wound along the small-diameter pulley 15 in FIG. On the small-diameter pulley 15, it is generally known that severe stress concentration occurs on the V-belt 1. However, the presence of the notch 2 alleviates the stress concentration, and the V-belt 1 does not crack. 1 can be wound around the small-diameter pulley 15 and rotated. However, when the V-belt is wound around the small-diameter pulley 15 and rotated, the stress concentration of the notch 2 itself may increase, and as a result, the notch 2 may crack. If such cracks occur, the belt will break prematurely, leading to a short life of the belt.
[0025]
However, according to the notched wrapped V-belt of the present invention, stress concentration can be reduced and the belt life can be extended. Next, a description will be given of a test for measuring the transmission efficiency, the slip ratio, and the belt bending stiffness of the notched wrapped V-belt of the present invention and the wrapped V-belts of Comparative Examples 1 and 2 having no notch.
(1) The shape of the belt used for the shape test of the belt and the notch is the same as the example of the present invention (the rubber of the compression part and the tension part is chloroprene rubber) and the comparative example 1 (the rubber of the compression part and the tension part is chloroprene rubber). 4 (b), the upper width b _t , the total thickness h, the thickness hc of the compression portion, and the taper angle αc of the belt of Comparative Example 2 (the rubber of the compression portion and the tension portion is natural rubber). Is as shown in Table 1 below for each type of belt. In FIG. 4A, the interval P between the vertices of adjacent notches in the longitudinal direction of the belt, the opening width W of the notch in the bottom surface of the compression portion, the height H of the notch from the apex of the arc to the bottom surface of the compression portion. , The notch angle θ and the arc radius R at the top of the notch are as shown in Table 2 below (the center value was adopted in this test).
[0026]
[Table 1]

[0027]
[Table 2]

[0028]
(2) Test Method The schematic arrangement of the test apparatus is as shown in FIG. In FIG. 5, 21 is a motor, 22 and 23 are torque detectors, 24 and 25 are pulleys, 26 is a belt, and 27 is a load machine.
(3) Test results a. A-Type Belt In the test apparatus shown in FIG. 5, the weight of the loader 27 is set to 50 kg, the outer diameters of the pulleys 24 and 25 are set to 67 mm, and the transmission efficiency and the slip ratio when two A-type belts are wound on these pulleys. 6 (a), 6 (b) and 6 (c) show the measurement test results of the belt bending rigidity.
[0029]
In FIG. 6 and FIGS. 7 to 9 described later, a solid line indicates the belt of the example (the present invention), a broken line indicates the belt of Comparative Example 1, and a dashed line indicates the belt of Comparative Example 2.
[0030]
In addition, the transmission efficiency, the slip ratio, and the belt bending rigidity were calculated by the following equations, respectively.
[0031]
Transmission efficiency = (load machine side power / motor side power) x 100 (%)
Slip ratio = ((I ₀ −I _t ) / I _t ) × 100 (%)
_{I 0 = N n0 / N r0} , I t = N nt / N rt
N _r0: no-load motor side shaft rotational speed N _rt: load motor side shaft speed during N _n0: no load of the load-side shaft speed N _nt: Bending load-side shaft speed belt under load Regarding the rigidity, as shown in FIG. 10, as shown in FIG. 10, the amount of displacement b when the belt 32 is inserted inside the pantograph-shaped member 31 and the load (W) 33 applied to the belt 32 via the member 31 is changed. ₀ , the distance b between the bending centers (neutral positions) of the upper and lower belts was calculated based on this b ₀ , and the belt bending rigidity EI was obtained from the following equation.
[0032]
EI = 0.17415 × W × b ² (kgf cm ² )
Hereinafter, the transmission efficiency, the slip ratio, and the belt bending rigidity of the B-type belt, the C-type belt, and the D-type belt were determined in the same manner.
[0033]
As shown in FIG. 6 (a), the belt of the embodiment has the highest transmission efficiency, and as shown in FIG. 6 (b), the belt of the embodiment is least likely to slip. As shown in c), the belt of the example has the lowest belt bending stiffness (lowest bending resistance).
b. B-type Belt In the test apparatus shown in FIG. 5, the weight of the loader 27 is set to 100 kg, the outer diameters of the pulleys 24 and 25 are set to 118 mm, and the transmission efficiency and the slip ratio when three B-type belts are hung on these pulleys. 7 (a), 7 (b), and 7 (c) show the measurement test results of the belt bending rigidity.
[0034]
As shown in FIG. 7 (a), the belt of the embodiment has the highest transmission efficiency, and as shown in FIG. 7 (b), the belt of the embodiment is least likely to slip, and FIG. As shown in c), the belt of the example has the lowest belt bending stiffness (lowest bending resistance).
c. C-type belt In the test device shown in FIG. 5, the weight of the loader 27 is set to 90 kg (when measuring the transmission efficiency) or 50 kg (when measuring the slip ratio), and the outer diameters of the pulleys 24 and 25 are set to 180 mm. FIGS. 8 (a), 8 (b) and 8 (c) show the measurement test results of the transmission efficiency, the slip ratio and the belt bending stiffness when a single shaped belt is hung.
[0035]
As shown in FIG. 8 (a), the belt of the embodiment has the highest transmission efficiency, and as shown in FIG. 8 (b), the belt of the embodiment is most difficult to slip, and FIG. As shown in c), the belt of the example has the lowest belt bending stiffness (lowest bending resistance).
[0036]
d. D-type belt In the test device shown in FIG. 5, the weight of the loader 27 is set to 180 kg (when measuring transmission efficiency) or 230 kg (when measuring the slip ratio), and the outer diameters of the pulleys 24 and 25 are set to 285 mm. 9 (a), 9 (b) and 9 (c) show the results of measurement tests of the transmission efficiency, the slip ratio and the belt bending stiffness when a single shaped belt is hung.
[0037]
As shown in FIG. 9 (a), the belt of the example has the highest transmission efficiency, and as shown in FIG. 9 (b), the belt of the example is different from the comparative example 2 which is a standard product. On the other hand, as in Comparative Example 1, slip is unlikely to occur, and as shown in FIG. 9C, the belt of the example has the lowest belt bending rigidity (lowest bending resistance).
[0038]
Further, the energy saving effect and the no-load durability performance when the notched wrapped V-belt of the present invention is used as a power transmission belt of a blower will be described based on specific data.
(1) Energy saving effect a. Test 1
As shown in FIG. 11, three B-shaped belts 43 were suspended between a driving pulley 41 having a diameter of 144 mm and a driven pulley 42 having a diameter of 167.5 mm, and from May 22, 2001 to June 5, 2001. When used as a power transmission belt for a blower that supplies high-temperature (120 ° C.) air over 24 hours (continuous operation for 24 hours), the average power consumption of the belt of the present invention is 3.404 kW, and the belt of Comparative Example 2 The average power consumption of the (current standard product) was 3.513 kw. That is, according to the belt of the present invention, there is an energy saving effect of 3.10% with respect to the standard belt. The standard of the motor of the drive belt 41 is 5.5 kw and 1740 rpm.
b. Test 2
As shown in FIG. 12, five C-shaped belts 53 are suspended between a driving pulley 51 having a diameter of 180 mm and a driven pulley 52 having a diameter of 305 mm, and are standardized from January 13, 2001 to February 26, 2001. When used as a power transmission belt for a blower that exhausts air (24-hour continuous operation), the average power consumption of the belt of the present invention is 9.55 kW, and the average consumption of the belt of Comparative Example 2 (current standard product) The power was 9.89 kw. That is, according to the belt of the present invention, there is an energy saving effect of 3.44% with respect to the standard belt. The standard of the motor of the drive belt 51 is 2.2 kw and 1450 rpm.
c. Test 3
As shown in FIG. 13, three B-shaped belts 63 are suspended between a driving pulley 61 having a diameter of 170 mm and a driven pulley 62 having a diameter of 127 mm, and a standard B-shaped belt 63 is provided from May 29, 2001 to June 24, 2001. When used as a power transmission belt for a blower that exhausts air (24-hour continuous operation), the average power consumption of the belt of the present invention is 4.516 kwh, which is the average of the belt of Comparative Example 2 (current standard product). The power consumption was 4.642 kw. That is, according to the belt of the present invention, there is an energy saving effect of 2.71% with respect to the standard belt. The standard of the motor of the drive belt 62 is 5.5 kw and 1735 rpm.
(2) No-load endurance performance In general, rubber used for power transmission belts gradually cures due to heat generation due to friction during use, and as curing progresses, cracks are formed in the bottom of the belt due to bending fatigue. It often follows the course leading to damage. Therefore, the following test was conducted to compare the durability performance depending on the difference in the belt form.
[0039]
As shown in FIG. 14A, one B-shaped belt 73 is suspended between pulleys 71 and 72 having the same diameter, the axial load of the driven pulley 72 is set to 80 kgf, and the drive pulley 71 is rotated at 4800 rpm. FIG. 14B shows the time required until the belt is damaged when the pulley diameters are 80 mm, 100 mm, and 118 mm. In FIG. 14B and FIG. 15 to be described later, the solid line indicates the belt of the embodiment (the present invention), the broken line indicates the belt of Comparative Example 1, and the dashed line indicates the belt of Comparative Example 2.
[0040]
As shown in FIG. 14 (b), the belt of the example is provided with a notch of an appropriate shape, so that it has good flexibility and low bending resistance, so that the heat generation of the belt is low and the hardening of the rubber hardly proceeds. . As a result, as shown in FIG. 14B, the belt of the example has the highest durability performance. FIG. 15 is a diagram comparing the average temperatures of the belt bottom surface during the no-load durability test. The belt temperature of the example was the lowest at any pulley diameter, and the belt durability of the example according to the present invention was low. This is evidence that the performance is excellent.
[0041]
【The invention's effect】
Since the present invention is configured as described above, it is possible to provide a notched wrapped V-belt having extremely low bending resistance, high transmission efficiency, and appropriate bending rigidity. In particular, since the belt is a wrapped V-belt, noise during power transmission is small, and when the belt is used as a power transmission belt for a device that is continuously used such as a blower, the energy saving effect due to the improvement in transmission efficiency is extremely large.
[Brief description of the drawings]
FIG. 1A is a perspective view of a wrapped V-belt, and FIG. 1B is a perspective view of a notched wrapped V-belt.
FIG. 2A is a perspective view of a low edge belt, and FIG. 2B is a perspective view of a notched low edge belt.
FIG. 3 is a diagram illustrating a state in which a notched V-belt is wound around an input pulley and an output pulley.
4 (a) is a side view of a notched wrapped V-belt of the present invention, FIG. 4 (b) is a sectional view taken along the line IV-IV of FIG. 4 (a), and FIG. 4 (c) is FIG. It is a side view of the notched wrapped V belt which has a notch of a different shape from (a).
FIG. 5 is a schematic layout diagram of a measuring device for transmission efficiency, slip ratio and belt rigidity.
FIGS. 6A, 6B, and 6C are diagrams showing the transmission efficiency, the slip ratio, and the belt rigidity of the A-type belt having the specifications shown in Table 1, respectively.
FIGS. 7A, 7B, and 7C are diagrams showing the transmission efficiency, the slip ratio, and the belt rigidity of the B-type belt having the specifications shown in Table 1, respectively.
FIGS. 8A, 8B, and 8C are diagrams showing the transmission efficiency, slip ratio, and belt rigidity of a C-shaped belt having the specifications shown in Table 1, respectively.
9 (a), 9 (b) and 9 (c) are diagrams showing the transmission efficiency, slip ratio and belt rigidity of a D-shaped belt having the specifications shown in Table 1, respectively.
FIG. 10 is a diagram illustrating a test method for measuring a belt bending stiffness.
FIG. 11 is a schematic diagram showing a belt running test method for obtaining the energy saving effect of the notched wrapped V-belt of the present invention.
FIG. 12 is a schematic view showing a belt running test method for obtaining the energy saving effect of the notched wrapped V-belt of the present invention.
FIG. 13 is a schematic view showing a belt running test method for obtaining the energy saving effect of the notched wrapped V-belt of the present invention.
14A is a schematic view showing a test method for measuring the no-load durability of the belt, and FIG. 14B is a view showing the test results.
FIG. 15 is a diagram showing the average temperature of the belt bottom surface during a test for measuring the no-load durability of the belt shown in FIG. 14 (a).
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Notched wrapped V belt 2, 2a, 12 ... Notch 3 ... Canvas 5 ... Compression part 6 ... Neutral part 6a ... Adhesive rubber layer 7 ... Pulling part 8 ... Tension band 9 ... Cog 10 ... Arc-shaped top part 11 ... Low edge Belts 14 and 15 Pulley hc Thickness of compressed portion H Notch height P Notch interval W Notch opening width

Claims (1)

A V-shaped V-belt having a compression portion, a tension portion, and a neutral portion between the compression portion and the tension portion, wherein the compression portion, the neutral portion, and the tension portion are wrapped with canvas, and each of the V-shaped belts is disposed in a longitudinal direction of the belt. In a notched wrapped V-belt in which a plurality of notches are formed in the compression portion with a predetermined interval between the notches, the notch has two side surfaces extending from the top to the bottom surface of the compression portion, and has a thickness of the compression portion. Hc, the height of the notch from the top of the notch to the bottom of the compression portion is H, the interval between corresponding portions of adjacent notches in the longitudinal direction of the belt is P, and the opening width of the notch at the bottom of the compression portion is W. In this case, the notch height H, the notch interval P, and the notch opening width W are in the following ranges, respectively.
hc × 0.35 ≦ H ≦ hc × 0.69,
hc × 0.85 ≦ P ≦ hc × 1.73,
H × 0.70 ≦ W ≦ H × 1.13.

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