JP2006282363A - Power transmission device of chain conveyer and sprocket used for it - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a chain conveyer with structure reducing change in speed of a carrier table moving on an outward passage side not changed in a vertical direction. <P>SOLUTION: The chain conveyer comprises: a drive sprocket 3; a drive chain 4 wound on the drive sprocket; a main shaft drive sprocket 5 attached to a main shaft 6 and wound around a drive chain; a chain bending device 38 disposed between the drive sprocket and the main shaft drive sprocket to bend the drive chain; a carrying table drive sprocket 7 attached to a main shaft and rotated at the same angular speed as the main shaft sprocket; a driven sprocket 9; and a carrying table drive chain 10 to which the carrying table 15, which is wound around a carrying table drive sprocket and the driven sprocket, is attached. The chain bending device 38 changes a bent amount of the drive chain 4 depending on position of the carrying table. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a chain conveyor that drives a carrier using a chain and a sprocket, and more particularly to a sprocket used therefor.

  A chain conveyor has an endlessly circulating carrier between the loading port near one end of the conveyor and the cargo outlet on the other end. Loaded and transported. In addition to goods, there are also chain conveyors for carrying people as well as goods, and these are called man conveyors. A moving walkway with the same height between the entrance of the person near one end of the man conveyor and the exit of the other end is called a “moving sidewalk”, and a thing with different heights is called an “escalator”. In recent years, there has been a growing need for reducing the installation space of these chain conveyors.

The structure of a conventional chain conveyor will be described with reference to FIGS. FIG. 10 is a side view showing a schematic configuration of a conventional chain conveyor, and FIG. 11 is a cross-sectional view taken along the line ZZ of FIG.
A rotatable driven shaft 8 is attached to a chain conveyor frame (not shown) near one end in the longitudinal direction of the chain conveyor, and a pair of driven sprockets 9 are attached near both ends of the driven shaft 8. ing. A rotatable main shaft 6 is attached to a chain conveyor frame (not shown) near the other end in the longitudinal direction of the chain conveyor, and a pair of transport platform drive sprockets 7 are located near both ends of the main shaft 6. It is attached. The carriage drive chain 10 is composed of two endless bodies that can be bent, one of which is attached to the driven sprocket 9 attached near the end of the driven shaft 8 and the end of the main shaft 6. It is wound around the carriage drive sprocket 7. The other is wound around the driven sprocket 9 attached in the vicinity of the other end of the driven shaft 8 and the carriage drive sprocket 7 attached in the vicinity of the other end of the main shaft 6.
These two transport table drive chains 10 are respectively attached to the vicinity of both ends of a plurality of drive roller shafts 12 arranged at substantially the same distance P as the transport table length P ′, and integrated with the drive roller shaft 12. Yes. The drive roller shaft 12 is formed so as to penetrate the transport table drive chain 10, and drive rollers 11 are rotatably provided near both ends thereof.
The transport table 15 is attached to the drive roller shaft 12 via a drive roller shaft bracket 13 provided integrally with the transport table.
Since the linear drive roller guide 14 is provided below the drive roller 11 on the forward path side I of the chain conveyor, the upper surface of the transport table 15 continuously moved is the upper surface of the adjacent transport table 15. The height is the same as that of the step.
A main shaft drive sprocket 5 is attached to one end side of the main shaft 6 to which the carriage drive sprocket 7 is attached. Further, the drive unit 1 is placed at a position away from the main shaft 6, and the drive unit shaft 2 is rotated by power. In the vicinity of the end of the drive unit shaft 2, a drive sprocket 3 is attached integrally with the drive unit shaft 2. One endlessly formed drive chain 4 is wound around the drive sprocket 3 and the main shaft drive sprocket 5 so that the rotation of the drive unit shaft 2 can be transmitted to the main shaft 6.

Next, the operation of the conventional chain conveyor will be described.
When the drive unit shaft 2 is rotated by the drive unit 1 and the drive sprocket 3 attached thereto is rotated, the power is transmitted to the main shaft drive sprocket 5 by the tension of the drive chain 4, and the main shaft 6 rotates.
Along with the rotation of the main shaft 6, the transport table drive sprocket 7 attached to the main shaft 6 rotates and hangs around the transport table drive chain 10, whereby the drive roller shaft 12 and the drive roller shaft bracket 13 are moved around the transport table drive chain 10. The transfer table 15 attached via is moved.
In the case where the transport platform 15 on the forward path side I moves from the driven sprocket 9 side toward the transport platform drive sprocket 7, the transport platform drive chain 10 that moves along the straight drive roller guide 14 on the forward path side I is as follows. The direction is changed in the vicinity of the main shaft 6, that is, the main shaft side reversing section II while being wound around the transport table drive sprocket 7. At this time, the transport table 15 also changes the direction together with the transport table drive chain 10 and performs the reversing operation.
Thereafter, the transport table 15 moves the transport surface downward, the drive roller 11 upward, and the return path III from the transport table drive sprocket 7 to the driven sprocket 9.
In the driven shaft side reversing part IV, the driven sprocket 9 is wound around the carrier drive chain 10 driven by the carrier drive sprocket 7, so that the direction is changed. At this time, the carrier 15 is also used as the carrier drive chain. The direction is changed together with 10 and the reversing operation is performed, and it returns to the forward path I again. By continuously performing such operations, articles and people can be continuously conveyed.

Here, the chain used for the conventional chain conveyor will be described.
Since the drive chain 4 has a shorter chain length than the transport table drive chain 10, the total number of rotations of the chain within the operation time is larger than that of the transport table drive chain 10, and wear and tear are significant. For this reason, since the frequency of replacement becomes high, a standard product with a relatively short chain pitch shown in Japanese Industrial Standards (JIS), which is generally inexpensive and easily available, is often used. 3 and the main shaft drive sprocket 5 are also used as standard products.
FIG. 16 is an explanatory view showing an aspect of a standard sprocket. These sprockets are obtained by processing the outer periphery of a disk-shaped material so as to form a recess using a tool. The outer shape of the finished product is a shape in which irregularities are continuous as shown in FIG. This concave portion is called a tooth profile 31 so that when the drive chain 4 is wound, the chain roller 22 of the drive chain 4 fits smoothly. This tooth profile 31 has a shape in which a plurality of arcs obtained by a Japanese Industrial Standard procedure based on the tooth profile reference point 32 are continuous, and the distance between adjacent tooth profile reference points 32 is the chain pitch P _{K of the} drive chain 4. Almost matches. Although these tooth profile reference points 32 are arranged on a single arc, as described above, the chain pitch P _K of the drive chain 4 is relatively short, so that the number of teeth is relatively large, and the chain is connected to the drive sprocket 3. When it is wound around the main shaft drive sprocket 5, it becomes a polygonal shape with a large apex angle, that is, a substantially arc shape.
On the other hand, for the carriage drive chain 10, a chain having a long chain pitch is often used because the number of chain joints is reduced, the number of parts of the chain is reduced, and the cost is reduced. The chain conveyor has a thin frame to keep the installation space small, so the sprocket used for this must also have a small outer diameter, and for this reason, the number of teeth must be reduced. . Therefore, when the carriage drive chain 10 is wound around the carriage drive sprocket 7 and the driven sprocket 9, a regular polygonal shape having a relatively small apex angle is obtained.

である。チェーンローラ１７ｂの軸心の水平方向の位置Ｘ_３ は（１）式と（２）式との差であるから、

となる。
また、搬送台駆動スプロケット７の回転角速度を ω_Ｈ、時間を ｔ と置いた場合、角度θ_Ｈは、
θ_Ｈ＝ω_Ｈ ・ ｔ …… （４）
である。ここで（４）式を（３）式に代入し、Ｘ_３を 時間ｔについて微分してチェーンローラ１７ｂの水平方向の速度ｖ_Ｘ３を求めると、

となり、ｖ_Ｘ３はθ_Ｈの関数で表される。これは、搬送台駆動スプロケット７の回転角速度ω_Ｈを一定として回転させても、搬送台駆動スプロケット７に巻き掛ったチェーンローラ１７ａの主軸６の軸心を原点としたときの極座標によって、往路側Ｉの軌道上を移動しているチェーンローラ１７ｂの移動速度が変わり、搬送台駆動チェーン１０や搬送台駆動チェーン１０に取り付けられている搬送台１５の移動速度が変化してしまうことを表している。なお以降、このθ_Ｈを、搬送台駆動スプロケット７の変位角度と称することにする。
今、搬送台駆動スプロケット７に巻き掛った搬送台駆動チェーン１０のチェーンローラ１７ａが、主軸６の軸心を通る垂直線の上にあるとすると、搬送台駆動スプロケット７の
変位角度θ_Ｈ０は、
θ_Ｈ０ ＝ ０° …… （６）
であり、このときの隣接するチェーンローラ１７ｂの移動速度ｖｘ_３０ は、（５）式に（６）式を代入して、
ｖ_Ｘ３０ ＝ Ｒ_Ｈ・ω_Ｈ
となる。
そして、搬送台駆動スプロケット７が時計方向に回転すると、搬送台駆動スプロケット７の変位角度θ_Ｈ が大きくなるにつれ、往路側Ｉの軌道上を移動しているチェーンローラ１７ｂの速度は（６）式の計算結果のように変化していく。
さらに、搬送台駆動スプロケット７が時計方向に回転し、チェーンローラ１７ｂが搬送台駆動チェーン１０のチェーンピッチＰの距離を移動すると、その軸心は、主軸６の軸心を通る垂直線の上に位置することになり、チェーンローラ１７ａの軸心が主軸６の軸心を通る垂直線の上に位置していた（６）式の条件と一致し、往路側Ｉを移動するチェーンローラの速度が再び ｖ_Ｘ３０ と等しくなる。
また、このとき搬送台駆動スプロケット７に巻き掛っていたチェーンローラ１７ａは、（６）式の時の状態から主軸６の軸心を中心にθ_ＨＥの角度を回転移動することになるが、この角度θ_ＨＥは搬送台駆動スプロケット７の割出し角度と称し、その大きさは搬送台駆動スプロケット７の歯数をＮ_Ｈとおくと、

である。
図１４は（５）式をもとに、搬送台駆動スプロケット７の変位角度θ_Ｈを θ_Ｈ０からθ_ＨＥまでの範囲で変化させたとき、のチェーンローラ１７ｂの水平方向の速度ｖ_Ｘ３の変化を線図に表したものであり、横軸は搬送台駆動スプロケット７の変位角度θ_Ｈ、縦軸はチェーンローラ１７ｂの水平方向の移動速度ｖ_ｘ３としている。
前述したように、搬送台駆動スプロケット７の変位角度θ_Ｈが θ_Ｈ０からθ_ＨＥ まで変化すると、チェーンローラ１７ｂの配置はθ_Ｈ０のときの配置に一致するので、それ以降の往路側Ｉを移動するチェーンローラ１７ｂも同様の速度変化を繰り返し、往路側Ｉを移動する搬送台駆動チェーン１０は連続的に規則的な速度変化を繰り返す、つまり脈動が発生することになる。
搬送台１５は、駆動ローラ軸１２と駆動ローラ軸ブラケット１３とを介して搬送台駆動チェーン１０に取り付けられているので、搬送台１５の速度も搬送台駆動チェーン１０の速度に一致した脈動を起こす。横軸を時間ｔ、縦軸を搬送台１５の速度ｖ_ｘ３として線図に示すと、図１５のようになる。
このように搬送台１５の移動速度が脈動すると、その度合いが顕著な場合、搬送物が揺れたり、倒れたりして不具合が生じる場合が考えられる。またそのチェーンコンベヤが人を搬送する動く歩道やエスカレーターの場合だと乗り心地が悪く、乗客に対して不快感を与えたり、場合によっては転倒事故を引き起こすなどの不具合が考えられる。 FIG. 12 is an explanatory diagram showing a configuration in the vicinity of a drive unit of a conventional chain conveyor. Problems of the conventional chain conveyor will be described with reference to FIG.
The chain roller 17a of the carriage drive chain 10 is wound around the carriage drive sprocket 7. The distance from the rotation center of the carriage drive sprocket 7, that is, the axis of the main shaft 6, is the pitch circle of the carriage drive sprocket 7. Equal to a distance _RH that is half the diameter. Further, the adjacent chain roller 17b is located on the path on the forward path side, and the distance between the axis of the main shaft 6 and the path on the forward path side of the chain roller 17b is half the pitch circle diameter of the carriage drive sprocket 7. Equal to the distance _RH .
The two chain rollers 17a and 17b are connected by a chain link 16, and the distance is a fixed distance P.
Now, the coordinate of the axis O _S of the main shaft 6 is defined as O _S (0, 0), and the angle formed between the straight line connecting the axis of the main shaft 6 and the chain roller 17a and the vertical line passing through the axis O _S of the main shaft 6 Is θ _H , the horizontal position X ₁ of the axial center of the chain roller 17a is
X ₁ = R _H · sin θ _H (1)
It is. The horizontal distance X ₂ between the chain rollers 17b which are positioned in orbit of the chain rollers 17a and forward path I is

It is. Since horizontal position X ₃ of the axis of the chain rollers 17b is the difference between (1) and (2),

It becomes.
When the rotation angular velocity of the carriage drive sprocket 7 is ω _H and the time is t, the angle θ _H is
θ _H = ω _H · t (4)
It is. Where (4) by substituting formula of equation (3), the by differentiating the _{X 3} for the time t determine the horizontal speed _{v X3} chain rollers 17b,

_{Next, v X3} is expressed by a function of theta _H. This is based on the polar coordinates when the axis of the main shaft 6 of the chain roller 17a wound around the carriage drive sprocket 7 is the origin even if the rotation angular velocity ω _H of the carriage drive sprocket 7 is kept constant. This indicates that the moving speed of the chain roller 17b moving on the I track changes, and the moving speed of the transport table drive chain 10 and the transport table 15 attached to the transport table drive chain 10 changes. . Note later, the theta _H, will be referred to as the displacement angle of the transport table driving sprocket 7.
Assuming that the chain roller 17a of the carriage drive chain 10 wound around the carriage drive sprocket 7 is on a vertical line passing through the axis of the main shaft 6, the displacement angle θ _H0 of the carriage drive sprocket 7 is
θ _H0 = 0 ° (6)
The moving speed vx ₃₀ of the adjacent chain roller 17b at this time is obtained by substituting the equation (6) into the equation (5).
v _X30 = R _H · ω _H
It becomes.
Then, when the conveyor table drive sprocket 7 rotates clockwise, as displacement angle theta _H of the transport table driving sprocket 7 is increased, the speed of the chain rollers 17b which is moving on a track of the forward path I is (6) It changes like the calculation result of.
Further, when the carriage drive sprocket 7 rotates in the clockwise direction and the chain roller 17b moves the distance of the chain pitch P of the carriage drive chain 10, its axis is on a vertical line passing through the axis of the main shaft 6. The speed of the chain roller moving on the forward path I is equal to the condition of the equation (6) in which the axis of the chain roller 17a is located on the vertical line passing through the axis of the main shaft 6. Again it becomes equal to v _X30 .
At this time, the chain roller 17a wound around the carriage drive sprocket 7 rotates and moves at an angle of θ _HE around the axis of the main shaft 6 from the state of the expression (6). angle theta _HE is called indexing angle of the transport table driving sprocket 7, when the magnitude of which put the number of teeth of the conveying table drive sprocket 7 and N _H,

It is.
FIG. 14 shows a change in the horizontal speed v _X3 of the chain roller 17b when the displacement angle θ _H of the carriage drive sprocket 7 is changed in the range from θ _H0 to θ _HE based on the equation (5). The horizontal axis represents the displacement angle θ _H of the carriage drive sprocket 7, and the vertical axis represents the horizontal moving speed v _x3 of the chain roller 17b.
As described above, when the displacement angle θ _H of the carriage drive sprocket 7 changes from θ _H0 to θ _HE , the arrangement of the chain roller 17b coincides with the arrangement at the time of θ _H0 , so that the subsequent forward path side I is moved. The chain roller 17b that repeats repeats the same speed change, and the carriage drive chain 10 that moves on the forward path side I continuously repeats a regular speed change, that is, pulsation occurs.
Since the transport table 15 is attached to the transport table drive chain 10 via the drive roller shaft 12 and the drive roller shaft bracket 13, the speed of the transport table 15 causes pulsation that matches the speed of the transport table drive chain 10. . FIG. 15 is a diagram showing the time t on the horizontal axis and the speed v _{× 3} of the carriage 15 on the vertical axis.
When the moving speed of the transport table 15 pulsates in this way, if the degree is remarkable, the transported object may be shaken or fall down, causing a problem. In addition, when the chain conveyor is a moving walkway or escalator that carries people, the ride comfort is poor, and there are problems such as giving passengers an uncomfortable feeling and possibly causing a fall accident.

であり、ω_Ｓは角度θ_Ｓ の関数となることから、主軸６の回転速度ω_Ｓは、駆動チェーン４の速度ｖ_Ｋを一定にしたとしても、角度θ_Ｓ の変化に伴って変化することがわかる。なお以降、このθ_Ｓを、主軸駆動スプロケット２０の変位角度と称することにする。
次にこの従来技術における搬送台駆動スプロケット２１と搬送台駆動チェーン１０との関係を説明する。
搬送台駆動スプロケット２１の歯数は、主軸駆動スプロケット２０の歯数と同じであり、歯数が少ないのでこれに搬送台駆動チェーン１０を巻き掛けると略円弧状とはならずに比較的頂角の小さい多角形状になり、回転中心、すなわち主軸６の軸心から、搬送台駆動チェーン１０のピッチラインまでの距離Ｈ_２が変化する。その距離Ｈ_２は、搬送台駆動スプロケット２１のピッチ円直径の半分の距離をＲ_Ｈ、搬送台駆動スプロケット２１の変位角度をθ_Ｈとすると、
Ｈ_２ ＝ Ｒ_Ｈ・ｃｏｓθ_Ｈ …… （１０）
である。
搬送台駆動チェーン１０の速度ｖ_Ｈと主軸６の回転速度ω_Ｓとの関係は、
ｖ_Ｈ ＝ Ｈ_２・ω_Ｓ …… （１１）
であるので、これに（９）（１０）式を代入すると、

となる。また、この従来技術では主軸駆動スプロケット２０の歯形基準点３２と搬送台駆動スプロケット２１の変位角度を同一としているので θ_Ｈ＝θ_Ｓ であり、（１２）式は

となる。駆動チェーン４の速度ｖ_Ｋは一定であり、主軸駆動スプロケット２０のピッチ円直径の半分の距離Ｒ_Ｓ、および搬送台駆動スプロケット２１のピッチ円直径の半分の距離Ｒ_Ｈは固定値であるので、（１３）式の計算結果は常に一定であることになる。
しかしこの従来技術のチェーンコンベヤの場合、主軸６の軸心から、搬送台駆動チェーン１０までの距離Ｈ_２を変化させなければ（１３）式に示す関係は成り立たない。
仮に搬送台駆動チェーン１０のチェーンピッチＰ＝４０６．４ｍｍ（１６インチ）とし、搬送台駆動スプロケット２１の歯数を６歯とすると、主軸６の軸心から、搬送台駆動チェーン１０のピッチラインまでの距離Ｈ_２は、搬送台駆動スプロケット２１の変位角度θ_Ｈを、θ_Ｈ０から割出し角度θ_ＨＥまで変化させて、（１０）式より計算すると、Ｈ_２は最大約５５ｍｍ変化するという計算結果となる。例えばこの従来技術のチェーンコンベヤが、人を搬送するマンコンベヤであって、搬送台駆動チェーン１０のピッチラインまでの距離Ｈ_２が最大となるときの搬送台１５の高さと乗降口の床の高さを一致させていたとすると、搬送台駆動チェーン１０のピッチラインまでの距離Ｈ_２が最小となるときの搬送台１５と乗降口の床との間に約５５ｍｍもの段差を生じさせてしまい、乗降の際に乗客が足をとられて転倒する危険がある。また、往路側を移動する過程でも搬送台１５が上下方向に変位するために乗り心地が良くないなどという、新たな問題が発生する。 As a countermeasure against this, the case of “moving sidewalk” as a chain conveyor is taken as an example, and a conventional technique having the following contents is known as a method for reducing the pulsation of the transport table 15 (see, for example, Patent Document 1). . Hereinafter, the conventional chain conveyor will be described.
FIG. 13 is an explanatory diagram showing the vicinity of the drive unit in an example of the prior art. Since the configuration of each part is the same as that of the conventional chain conveyor described above, description thereof will be omitted. This chain conveyor is different from the above-described conventional chain conveyor in that the tooth profile reference point 32 of the above-described conventional spindle driving sprocket 5 is arranged on a single arc, whereas the conventional conveyor shown in FIG. The main shaft drive sprocket 20 shown in the technology has the same number of teeth as that of the carriage drive sprocket 21 and the drive chain 4 is wound around the main shaft drive sprocket 20 in a polygonal shape. Further, the direction of the tooth profile reference point 32 when the vertex of the polygonal shape, that is, the axis of the main shaft 6 is the origin, is set to be the same as that of the carriage drive sprocket 21.
Further, in this conventional chain conveyor, the driving roller guide 14 for guiding the movement of the driving roller 11 on the forward path side I as in the conventional chain conveyor shown in FIG. 10 is not provided.
According to this prior art chain conveyor, the number of teeth of the spindle drive sprocket 20 is the same as that of the carriage drive sprocket 21 and the phase of the teeth is set to be the same as that of the carriage drive sprocket 21. The pulsation that can reduce the pulsation of the driving roller 11 that moves on the side can be applied to the main shaft 6, and the carriage drive chain 10 and the carriage 15 can be driven at a substantially constant speed.
This theory will be described with reference to FIG.
The drive sprocket 3 has a large number of teeth like a conventional chain conveyor, and the tooth profile reference point 32 is arranged on a single arc, so that the winding state of the drive chain 4 is substantially circular. is there. Drive sprocket 3, since is driven at a constant speed omega _K by the drive unit 1, the speed of the drive chain 4 is also substantially constant speed v _K that is wound around it.
On the other hand, the main shaft drive sprocket 20 to which the rotational force is applied by the drive chain 4 has a small number of teeth, so when the drive chain 4 is wound around this, the main shaft drive sprocket 20 does not have a substantially arc shape but a polygonal shape with a relatively small apex angle. The distance H ₁ from the rotation center, that is, the axis of the main shaft 6 to the drive chain 4 changes. The distance H ₁ is R _S , which is half the pitch circle diameter of the main shaft drive sprocket 20, and a straight line connecting the axis of the main shaft 6 and the axis of the chain roller 22 of the drive chain 4 meshing with the main shaft drive sprocket 20. And the angle between the vertical straight line passing through the axis of the main shaft 6 and θ _S ,
H ₁ = R _S · cos θ _S (7)
It is.
The relationship between the speed v _K of the drive chain 4 and the rotational speed ω _S of the main shaft 6 is
v _K = H ₁ · ω _S (8)
Therefore, the rotational speed ω of the spindle is

Since ω _S is a function of the angle θ _S , the rotational speed ω _S of the main shaft 6 changes with the change of the angle θ _S even if the speed v _K of the drive chain 4 is constant. I understand. Hereinafter, this θ _S will be referred to as a displacement angle of the main shaft drive sprocket 20.
Next, the relationship between the carriage drive sprocket 21 and the carriage drive chain 10 in this prior art will be described.
The number of teeth of the carriage drive sprocket 21 is the same as the number of teeth of the main shaft drive sprocket 20, and the number of teeth is small. The distance H ₂ from the center of rotation, that is, the axis of the main shaft 6 to the pitch line of the carriage drive chain 10 changes. The distance H ₂ is defined as R _H , which is half the pitch circle diameter of the carriage drive sprocket 21, and θ _{H as} the displacement angle of the carriage drive sprocket 21.
H ₂ = R _H · cos θ _H (10)
It is.
The relationship between the speed v _H of the carriage drive chain 10 and the rotational speed ω _S of the spindle 6 is
v _H = H ₂ · ω _S (11)
Therefore, substituting equations (9) and (10) for this,

It becomes. Further, in this prior art, since the displacement angle of the tooth profile reference point 32 of the main spindle drive sprocket 20 and the carriage drive sprocket 21 is the same, θ _H = θ _S , and equation (12) is

It becomes. The speed v _K of the drive chain 4 is constant, and the distance R _S that is half the pitch circle diameter of the spindle drive sprocket 20 and the distance R _{H that} is half the pitch circle diameter of the carriage drive sprocket 21 are fixed values. The calculation result of equation (13) is always constant.
However, in the case of the chain conveyor of the prior art, from the axis of the main shaft 6, unless (13) relationship shown in equation does not hold alter the distance of H ₂ to the transport table driving chain 10.
Assuming that the chain pitch P of the carriage drive chain 10 is 166.4 mm (16 inches) and the number of teeth of the carriage drive sprocket 21 is six, from the axis of the spindle 6 to the pitch line of the carriage drive chain 10. distance of _{H 2} is the displacement angle theta _H of the transport table driving sprocket 21, by changing from theta _H0 to index angle theta _HE, (10) is calculated from the formula, the calculation result of _{H 2} is up to about 55mm change It becomes. For example the chain conveyor of the prior art, a man conveyor for conveying the human, high floor height and entrance of the transfer platform 15 when the distance of H ₂ until the pitch line of the transport table driving chain 10 is maximum when were you match is, it would be causing about 55mm thing step between the carrier table 15 and the floor of the entrance when the distance of H ₂ until the pitch line of the transport table driving chain 10 is minimized, passenger There is a danger that passengers will fall on their feet when they fall. In addition, there is a new problem that the ride comfort is not good because the transport table 15 is displaced in the vertical direction even in the process of moving on the forward path side.

JP-A-3-297792

  As described above, the conventional chain conveyor is, for example, a man conveyor that conveys people, and the height of the carriage and the floor of the entrance / exit when the distance to the pitch line of the carriage drive chain becomes maximum. If the distance is the same, a step of about 55 mm will be generated between the transport platform and the floor of the entrance / exit when the distance to the pitch line of the transport platform drive chain is minimized, There is a risk of falling on the foot. In addition, there is a problem that even in the process of moving on the forward path side, the transport platform is displaced in the vertical direction, so that the ride comfort is not good.

  The present invention has been made to solve the above-described problems, and provides a chain conveyor that can reduce the speed change of the transport table and that does not change the transport table moving on the forward path side in the vertical direction. To do.

  In the chain conveyor according to the present invention, a drive sprocket rotated by the drive unit, a drive chain wound around the drive sprocket, a spindle drive sprocket attached to the spindle and wound around the drive chain, a drive sprocket, A chain bending device, which is provided between the main shaft drive sprocket and abuts the drive chain to bend the drive chain, is attached to the main shaft and is rotated at the same angular speed as the main shaft drive sprocket, and a driven shaft. A driven sprocket that is pivotally attached, a carrier drive sprocket, and a carrier drive chain to which a carrier that is hung around the driven sprocket is attached. The chain bending device conveys the amount of bending of the drive chain. It is changed according to the position of the table.

  According to the present invention, the amount of bending of the drive chain can be changed according to the position of the transport table, so that the speed change of the transport table can be reduced.

Embodiment 1.
1 is a side view showing a schematic configuration of a chain conveyor according to Embodiment 1 of the present invention, FIG. 2 is an enlarged view showing a configuration in the vicinity of a drive unit of the chain conveyor according to Embodiment 1 of the present invention, and FIG. FIG. 2 is a characteristic diagram showing the bending angle of the drive chain bent by the drive chain bending device with time, showing a state after a lapse of a minute time from the initial state.

First, the first embodiment of the present invention will be described. The general configuration and operation are the same as those shown in the above-described conventional chain conveyor (FIGS. 10 to 12) and the above-described conventional chain conveyor ( Since this is the same as FIG. 13), detailed description is omitted, and here, the points of the present invention that are different from them will be mainly described.
The present invention differs from the conventional chain conveyor in that a chain bending device 36 is disposed on the drive chain 4 between the drive sprocket 3 and the main shaft drive sprocket 5.
The chain bending device 36 is electrically connected to the displaceable chain guide device 38 that contacts the drive chain 4, the displacement device 41 that is connected to the chain guide device 38 and changes the position of the chain guide device 38, and the displacement device 41. The controller 42 is connected and controls the displacement operation of the displacement device 41 by an electrical signal.
Since the chain guide device 38 is disposed in advance so as to contact the drive chain 4, the drive chain 4 is bent with the portion in contact with the chain guide device 38 as a vertex, and the drive chain 4 is bent at this time. The angle is α (state shown in FIG. 2). When control is performed so that the displacement device 41 is extended by an electric signal from the control device 42 from this state, the chain guide device 38 attached to the displacement device 41 causes the drive chain 4 between the drive sprocket 3 and the main shaft drive sprocket 5 to move. , And the bending angle α ′ changes so as to decrease (the state of FIG. 3). At this time, the length of the drive chain 4 from the point D ′ where the drive chain 4 comes into contact with the main shaft drive sprocket 5 to the point E ′ where the drive chain 4 comes into contact with the drive sprocket 3 via the chain guide device 38 changes. To do. As shown in FIG. 2, if there is no operation of pushing down the drive chain 4 by the displacement device 41, the length of the drive chain 4 taken up by the drive sprocket 3 rotating at a constant angular velocity and the drive pulled from the main shaft drive sprocket 5 are taken. The lengths of the chains 4 are equal, and the rotational speed thereof is multiplied by the speed obtained by multiplying the rotational speed of the drive sprocket 3 by the ratio of the pitch circle diameter of the drive sprocket 3 and the pitch circle diameter of the main shaft drive sprocket 5, that is, the speed ratio. It is speed.
On the other hand, as shown in FIG. 3, if the operation of pushing down the drive chain 4 by the displacement device 41 is performed, the drive sprocket 3 passes from the point D ′ contacting the main shaft drive sprocket 5 of the drive chain 4 through the chain guide device 38. The main shaft drive sprocket 5 adds the length of the drive chain 4 increased by being pushed down by the displacement device 41 to the length of the drive chain 4 taken up by the drive sprocket 3. Therefore, the main shaft drive sprocket 5 can be rotated faster than the speed obtained by multiplying the angular speed of the drive sprocket 3 by the speed ratio.
Conversely, when the displacement device 41 of the chain bending device 36 is changed from the extended state in FIG. 3 to the contracting direction, the bending angle of the drive chain 4 that has been reduced by pushing down the chain guide device 38, as shown in FIG. α ′ is pulled back so as to increase to a bending angle α, and the length from the point D contacting the main shaft drive sprocket 5 of the drive chain 4 to the point E contacting the drive sprocket 3 via the chain guide device 38 is shortened. To change. Therefore, the main shaft drive sprocket 5 rotates by the amount obtained by subtracting the length of the drive chain 4 that is reduced by the displacement of the displacement device 41 from the length of the drive chain 4 that the drive sprocket 3 winds up. The sprocket 5 can be rotated slower than the speed obtained by multiplying the angular speed of the drive sprocket 3 by the speed ratio.
When the drive sprocket 3 is rotated at an equiangular speed, the rotational speed of the main shaft drive sprocket 5 can be varied by extending and contracting the displacement device 41 and pushing down / retracting the drive chain 4. If this operation is performed continuously and regularly, it becomes possible to give regular pulsation to the rotational speed of the main shaft drive sprocket 5. Therefore, in the present invention, the position of the axis of the chain roller 17 of the carriage drive chain 10 that moves in the forward path side I in advance and the amount of expansion / contraction of the displacement device 41 that can reduce the speed change of the carriage drive chain 10, that is, the drive chain 4 is determined, and the amount of pressing of the drive chain 4 is controlled based on the relationship, so that the carriage drive chain 10 moving on the forward path I and the carriage attached to the carriage drive chain 10 are controlled. A change in the moving speed of the table 15 is considered.

Ｙ_１ ＝ ｐ・Ｘ_１＋ｑ
ただし、

と計算できる。このとき、搬送台駆動スプロケット７の変位角度θ_Ｈ１は、

であり、搬送台駆動スプロケット７は主軸駆動スプロケット５とともに主軸６に一体に形成されているので、このときの主軸駆動スプロケット５の変位角度θ_Ｓ１は、搬送台駆動スプロケット７の変位角度θ_Ｈ１と等しい。そして、搬送台駆動スプロケット７のピッチ円直径の半分の距離をＲ_Ｓとおくと、微少時間Δｔの間に搬送台駆動スプロケット７から引っ張り取られる駆動チェーン４の長さＬ_Ｓ１は、
Ｌ_Ｓ１ ＝ Ｒ_Ｓ×θ_Ｈ１
と計算できる。
一方、駆動スプロケット３は、駆動ユニット１により等角速度ω_Ｈで駆動されるので、微少時間Δｔの間に駆動スプロケット３が巻取るチェーンの長さＬ_Ｋは、駆動スプロケットのピッチ円直径の半分の距離をＲ_Ｋとすると
Ｌ_Ｋ（一定） ＝ Ｒ_Ｋ・ω_Ｋ
である。
これにより、駆動チェーン４の主軸駆動スプロケット５と接する点Ｄ’から、チェーン案内装置３８を経て駆動スプロケット３と接する点Ｅ’までの駆動チェーン４の長さＬ_１は、図２のときの基準長さＬ_０と比べて次式のように変化する。
Ｌ_１ ＝ Ｌ_０−Ｌ_Ｋ＋Ｌ_Ｓ１
このとき、この区間の駆動チェーン４の長さは、Ｌ_０からＬ_１に変化するので、変位装置４１を延伸させて、この区間の駆動チェーン４の長がＬ_１になるようにチェーン案内装置３８の位置を決める。
さらに同様の手順で、さらに微少時間Δｔ経過した後の搬送台駆動チェーン１０のチェーンローラ１７の軸心位置より、そのときの主軸駆動スプロケット５の変位角度θ_Ｓ２を計算し、この微少時間Δｔの間に主軸駆動スプロケット５から引き離されるチェーンの長さＬ_Ｓ２を求める。そして、この時間でも駆動スプロケット３が巻取るチェーンの長さはＬ_Ｋであるので、駆動チェーン４の主軸駆動スプロケット５と接する点から、チェーン案内装置３８を経て駆動スプロケット３と接する点までの駆動チェーン４の長さＬ_２は、
Ｌ_２ ＝ Ｌ_１−Ｌ_Ｋ＋Ｌ_Ｓ２
である。このときのこの区間の駆動チェーン４の長さはＬ_１からＬ_２に変化するので、変位装置４１をさらに延伸させて、この区間の駆動チェーン４の長さがＬ_２になるようにチェーン案内装置３８の位置を決める。
またさらに微少時間Δｔを経過させたときの、駆動チェーン４の主軸駆動スプロケット５と接する点から、チェーン案内装置３８を経て駆動スプロケット３と接する点までの駆動チェーン４の長さを計算して、それよりチェーン案内装置３８の位置を求め、この手順を連続的に繰り返していくと各時刻または、往路側Ｉを移動する搬送台駆動チェーン１０のチェーンローラ１７の軸心位置に応じた変位装置４１の伸縮量の変化、すなわち駆動チェーン４の押え量を求めることができる。また、この手順の中で各時刻または、往路側Ｉを移動する搬送台駆動チェーン１０のチェーンローラ１７ａの軸心位置に応じた主軸駆動スプロケット５の変位角度θ_Ｓの変化も求めることができるが、これが、往路側Ｉを移動する搬送台駆動チェーン１０のチェーンローラ１７の軸心の速度をほぼ一定にできる主軸６の角速度の変化すなわち、脈動である。
図４は、横軸を経過時間とし、変位装置４１による駆動チェーン４の屈曲量を上記手順により連続的に求め、その変化を表した特性図である。
このようにして求めた変位装置４１による駆動チェーン４の屈曲量の変化を、駆動中の駆動チェーン４に与えることによって主軸６の回転速度を適当に変化させれば、往路側Ｉを移動する搬送台駆動チェーン１０のチェーンローラ１７の軸心の速度、そして搬送台駆動チェーン１０に取り付けられた搬送台１５の速度をほぼ一定にすることができる。
またこの発明の場合、従来技術に示されるチェーンコンベヤとは異なり、従来形のチェーンコンベヤと同様に往路側Ｉを走行する搬送台駆動チェーン１０の走行を案内する駆動ローラガイド１４を設けたので、往路側Ｉを移動する搬送台１５の搬送面の高さを一定にすることが可能である。 Next, a procedure for obtaining the relationship between the position of the shaft center of the chain roller 17 of the carriage drive chain 10 moving on the forward path side I and the amount of chain push-down of the drive chain 4 that can reduce the speed change of the carriage drive chain 10 is performed. State.
FIG. 2 shows a state where the axis of the chain roller 17b of the carriage drive chain 10 is on a vertical line passing through the axis of the main shaft 6. The displacement angle θ of the carriage drive sprocket 7 at this time is shown in FIG. _H
θ _H = 0 °
far. If the coordinates of the axis of the main shaft 6 are (0, 0), the coordinates of the axis of the chain roller 17a moving on the forward path side I adjacent to the chain roller 17b is (−P, R _H ). Note that _RH is a distance that is half the pitch circle diameter of the carriage drive sprocket 7. At this time, the amount by which the drive chain 4 is pushed down by the displacement device 41 may be freely designed. And the point D which is in contact with the main shaft drive sprocket 5 of the drive chain 4, keep the reference length L ₀ of the length of the drive chain 4 up to point E in contact with the drive sprocket 3 through the chain guide device 38.
Next, FIG. 3 shows a state after a minute time Δt has elapsed from the state of FIG.
Because consider the velocity V _H of the transfer table drive chain 10 to be constant, the axis of coordinates of the chain rollers 17 to move the forward path I when in FIG. 3 is a _{(-P + V H × Δt,} R H) . Accordingly, the coordinates (X ₁ , Y ₁ ) of the axis of the chain roller 17 of the transport table drive chain 10 wound around the transport table drive sprocket 7 are expressed as follows. Since this is the intersection of the pitch circle with the radius _RH centered on the axis (0, 0) and the circular arc with the radius P centered on the chain roller axis (−P + V _H × Δt, R _H ), X ₁ =

Y ₁ = p · X ₁ + q
However,

Can be calculated. At this time, the displacement angle θ _H1 of the carriage drive sprocket 7 is

Since the carriage drive sprocket 7 is integrally formed with the spindle 6 together with the spindle drive sprocket 5, the displacement angle θ _S1 of the spindle drive sprocket 5 at this time is equal to the displacement angle θ _H1 of the carriage drive sprocket 7. equal. When the distance half the pitch circle diameter of the carriage drive sprocket 7 is R _S , the length L _S1 of the drive chain 4 pulled from the carriage drive sprocket 7 during the minute time Δt is:
L _S1 = R _S × θ _H1
Can be calculated.
On the other hand, since the drive sprocket 3 is driven at a constant angular velocity ω _H by the drive unit 1, the length L _{K of the} chain taken up by the drive sprocket 3 during a minute time Δt is half the pitch circle diameter of the drive sprocket. If the distance is R _K , L _K (constant) = R _K · ω _K
It is.
Thus, 'from the point E which is in contact with the drive sprocket 3 through the chain guide device 38' point D which is in contact with the main shaft drive sprocket 5 of the drive chain 4 length L ₁ of the drive chain 4 up to the reference time of FIG. 2 Compared with the length L ₀ , it changes as follows.
_{L 1 = L 0 -L K +} L S1
At this time, since the length of the drive chain 4 in this section changes from L ₀ to L ₁ , the chain guide device is extended so that the length of the drive chain 4 in this section becomes L ₁ by extending the displacement device 41. 38 position is determined.
Further, in the same procedure, the displacement angle θ _S2 of the main shaft drive sprocket 5 at that time is calculated from the axial center position of the chain roller 17 of the transport table drive chain 10 after the minute time Δt has passed, and the minute time Δt The length L _{S2 of the} chain that is pulled away from the main shaft drive sprocket 5 is obtained. Then, the length of the chain winding drive sprocket 3 In this time is L _K, driven from a point in contact with the main shaft drive sprocket 5 of the drive chain 4, to the point of contact with the drive sprocket 3 through the chain guide device 38 the length _{L 2} of the chain 4,
L ₂ = L ₁ −L _K + L _S2
It is. This length of the drive chain 4 sections of this time is changed from L ₁ to L _2, and further stretching the displacement device 41, the chain guide so that the length of the drive chain 4 of this section is L ₂ The position of the device 38 is determined.
Further, the length of the drive chain 4 from the point of contact with the main shaft drive sprocket 5 of the drive chain 4 to the point of contact with the drive sprocket 3 via the chain guide device 38 when a minute time Δt has passed is calculated, From this, the position of the chain guide device 38 is obtained, and when this procedure is continuously repeated, the displacement device 41 corresponding to each time or the axial center position of the chain roller 17 of the carriage drive chain 10 moving on the forward path side I. The change in the amount of expansion / contraction, that is, the amount of pressing of the drive chain 4 can be obtained. Further, in this procedure, the change in the displacement angle θ _S of the main shaft drive sprocket 5 can be obtained at each time or according to the axial center position of the chain roller 17a of the carriage drive chain 10 moving on the forward path side I. This is a change in the angular speed of the main shaft 6 that can make the speed of the axis of the chain roller 17 of the carriage drive chain 10 moving on the forward path side I substantially constant, that is, pulsation.
FIG. 4 is a characteristic diagram showing the change in which the horizontal axis is the elapsed time and the bending amount of the drive chain 4 by the displacement device 41 is continuously obtained by the above procedure.
If the rotation speed of the main shaft 6 is appropriately changed by giving the change in the bending amount of the drive chain 4 by the displacement device 41 obtained in this way to the drive chain 4 that is being driven, the conveyance moves on the forward path side I. The speed of the axis of the chain roller 17 of the table drive chain 10 and the speed of the conveyance table 15 attached to the conveyance table drive chain 10 can be made substantially constant.
Further, in the case of the present invention, unlike the chain conveyor shown in the prior art, the drive roller guide 14 is provided to guide the traveling of the carriage drive chain 10 traveling on the forward path side I like the conventional chain conveyor. It is possible to make the height of the transfer surface of the transfer table 15 moving on the forward path side I constant.

Embodiment 2.
FIG. 5 is an enlarged view showing the configuration in the vicinity of the drive unit of the chain conveyor according to Embodiment 2 of the present invention. The present invention is different from the conventional chain conveyor in that the drive chain 4 between the drive sprocket 3 and the main shaft drive sprocket 5 is provided with a displaceable chain guide device 38 that contacts the drive chain 4 and the position of the chain guide device. A chain bending device 36 having a cam mechanism for changing the angle is arranged.
The chain bending device 36 is formed integrally with a rotatable chain guide device 38 that abuts on the drive chain 4 and the chain guide device 38, and can be rotated by a pulley 46 a and a cam shaft 44 that rotate together with the chain guide device 38. A cam 43 having a different shape, attached to the cam 43, a pulley 46b that rotates together with the cam 43, a cam rod 45 that has one end attached to the chain guide device 38 and the other end abuts against the cam 43. , A tensioner 49 rotatably attached to a tensioner shaft 48 attached to the elastic body 50, a pulley 46a attached to the chain guide device 38, a pulley 46b attached to the cam 43, and a pulley 46c of the tensioner 49 Consists of one endless belt 47 wound in a triangular shape It has been.

Next, the operation of the chain bending device 36 will be described.
When the drive chain 4 travels, the chain guide device 38 in contact with the drive chain 4 rotates, and the pulley 46a formed integrally with the chain guide device 38 also rotates. Since the belt 47 is wound around the pulley 46a, the belt 47 is driven as the pulley 46a rotates. A similar pulley 46b is formed integrally with the cam 43 at another part of the pulley 46a and is wound around the same belt 47. When the belt 47 is driven, the pulley 46b and the pulley 46b are integrated with it. The formed irregularly shaped cam 43 rotates.
Since the outer periphery of the irregularly shaped cam 43 is in contact with the end of the cam rod 45 which can reciprocate in the longitudinal direction, the cam shaft 44 is caused by a change in the distance from the axial center of the cam shaft 44 to the contact portion of the cam rod 45. The cam rod 45 reciprocates in the vertical direction, whereby the chain guide device 38 attached to the other end of the cam rod 45 is displaced in the vertical direction to change the amount of bending of the drive chain 4, and the main shaft drive sprocket of the drive chain 4 It is possible to change the length of the drive chain 4 from the point in contact with 5 to the point in contact with the drive sprocket 3 via the chain guide device 38.
At this time, if the outer shape of the irregularly shaped cam 43 is designed so that the relationship between the time and the amount of bending of the chain as shown in FIG. A change in the amount of expansion and contraction can be given to the drive chain 4 that is being driven, and if the drive chain 4 is appropriately bent and the rotational speed of the main shaft 6 is changed appropriately, the carriage drive chain that moves on the forward path side I The speed of the axis of the ten chain rollers 17 and the speed of the transport table 15 attached to the transport table drive chain 10 can be made substantially constant.
In the description of the second embodiment, the belt transmission device using the pulley 46 and the belt 47 is used as a means for transmitting the rotation of the chain guide device 38 to the cam 43, but this is a chain transmission using a sprocket and a chain. Of course, other transmission devices, such as devices, may be used.

Embodiment 3.
FIG. 6 is an enlarged view showing the configuration in the vicinity of the drive unit of the chain conveyor according to Embodiment 3 of the present invention. The present invention is different from the conventional chain conveyor in that a chain bending device 37 comprising a rotatable chain guide device 39 that is in contact with the drive chain 4 between the drive sprocket 3 and the main shaft drive sprocket 5 is disposed. By the way. The chain guide device 39 has an irregular shape in which the distance from the rotation center to the chain contact outer periphery is not constant.

Next, the operation of the chain bending device 37 will be described.
The chain guide device 39 that is in contact with the drive chain 4 rotates as the drive chain 4 is driven, but the outer periphery of the contact with the drive chain 4 is not a perfect circle, but has a different shape. The distance from the rotation center of the device 39 to the contact point with the drive chain 4 changes. As a result, the bending amount of the drive chain 4 changes with time, and the drive chain length from the point D ′ that contacts the main shaft drive sprocket 5 of the drive chain 4 to the point E ′ that contacts the drive sprocket 3 via the chain guide device 39. Changes.
At this time, if the outer peripheral shape of the chain guide device 39 is designed so as to have the relationship between the time and the chain bending amount as shown in FIG. 4, the change in the chain bending amount similar to that in the first embodiment is driven. If the drive chain 4 is appropriately bent and the rotational speed of the main shaft 6 is changed, the speed of the axis of the chain roller 17 of the carriage drive chain 10 that moves on the forward path side can be provided. The speed of the transport table 15 attached to the transport table drive chain 10 can be made substantially constant.

Embodiment 4.
FIG. 7 is an enlarged view showing the configuration in the vicinity of the drive unit of the chain conveyor according to Embodiment 4 of the present invention. The present invention is different from the conventional chain conveyor in that a chain bending device 37 comprising a substantially circular rotatable chain guide device 40 in contact with the drive chain 4 between the drive sprocket 3 and the main shaft drive sprocket 5 is provided. I have just placed it. The chain guide device 40 has a substantially circular shape center and a rotation center provided at different positions, that is, the shape center and the rotation center are considered to be eccentric, and the drive chain 4 is contacted from the rotation center. It is designed so that the distance to the contact circumference is not constant.

Next, the operation of the chain bending device 37 will be described.
The chain guide device 40 that is in contact with the drive chain 4 rotates as the drive chain 4 is driven, but the center of the substantially circular shape and the center of rotation are decentered. The distance from the center to the contact point with the drive chain 4 changes. As a result, the amount of bending of the drive chain 4 changes with time, and the drive chain length from the point D ′ in contact with the main shaft drive sprocket 5 of the drive chain 4 to the point E ′ in contact with the drive sprocket 3 via the chain guide device 40. Changes.
At this time, if the position of the rotation center with respect to the center of the substantially circular shape is determined so as to be close to the relationship between the time and the chain bending amount as shown in FIG. 4, that is, the shape center and the rotation center. If the amount of eccentricity is determined, the change in the amount of chain bending similar to that of the first embodiment can be applied to the driving chain being driven, and the rotational speed of the main shaft 6 is changed by appropriately bending the driving chain 4 By doing so, the speed of the axis of the chain roller 17 of the carriage drive chain 10 moving on the forward path side and the speed of the carriage 15 attached to the carriage drive chain 10 can be made substantially constant.

Embodiment 5.
FIG. 8 is an explanatory view showing an irregularly shaped chain guide device according to Embodiment 5 of the present invention. The outer periphery of this irregularly shaped chain guide device 39 is characterized by forming a continuous uneven portion.
The concave portion of the concavo-convex portion corresponds to a tooth profile 31 in the case of a chain sprocket, and the shape thereof is such that when the drive chain 4 is wound around the chain guide device 39, the chain roller 22 of the drive chain 4 fits smoothly. Has been. And the shape is made into the circular arc shape substantially equal to the radius of the chain roller 22, so that harmful play does not occur when the chain roller 22 fits smoothly. Further, the tooth profile reference point 32 is a reference position in the contour design of the tooth profile 31 so that the chain roller 22 has a contour that opens from the arc toward the outer periphery so that the chain roller 22 can be smoothly fitted. Further, the distance L _K from the rotation center of the chain guide device 39 to the tooth profile reference point 32 is considered to be appropriately different depending on each tooth profile 31, and the tooth profile reference points 32 of the adjacent tooth profiles 31 are sequentially connected. Then, the trajectory has an unusual shape similar to the outer periphery of the chain guide device 39 in the third embodiment.
The interval between the tooth profile reference points 32 of the tooth profile 31 formed on the outer periphery of the chain guide device 39 is formed so as to coincide with the chain pitch p of the drive chain 4, that is, the interval between the chain rollers 22. Is driven, the chain roller 22 of the drive chain 4 sequentially fits into the tooth profile 31 formed on the outer periphery of the chain guide device 39 and rotates the chain guide device 39. As described above, this chain guide tooth reference point 32 of the device 39 is designed to differently the distance L _K from the center of rotation for each tooth 31. Therefore, since the distance to the tooth profile 31 into which the chain roller 22 fits is sequentially changed by the rotation of the chain guide device 39, the bending amount of the drive chain 4 also changes with time, and is in contact with the main shaft drive sprocket 5 of the drive chain 4. The length of the drive chain 4 from D ′ to the point E ′ that contacts the drive sprocket 3 through the chain guide device 39 changes.
At this time, if the tooth profile reference point 32 of the chain guide device 39 is arranged so that the relationship between the time and the amount of bending of the chain as shown in FIG. Change in the amount of bending of the chain can be applied to the driving chain 4 that is being driven, and if the rotational speed of the main shaft 6 is changed by appropriately bending the driving chain 4, The speed of the axis of the chain roller 17 and the speed of the transport table 15 attached to the transport table drive chain 10 can be made substantially constant.

Embodiment 6.
FIG. 9 is an explanatory view showing a chain guide device in which the center of rotation is eccentric in the sixth embodiment of the present invention. The outer periphery of the chain guide device 40 having the eccentric center of rotation forms a tooth profile 31 that is a continuous uneven part.
The shape of the tooth profile 31 is the same as that shown in the fifth embodiment, and when the adjacent tooth profile reference points 32 are sequentially connected, the locus thereof is the same as the outer periphery of the chain guide device 40 in the fourth embodiment. A similar arc shape is formed. In addition, the substantially arc-shaped center is provided such that the rotation center of the chain guide device 40 is provided at a different position, that is, the center of the shape and the rotation center are considered to be eccentric, and the distance from the rotation center to the tooth profile reference point 32. Is designed to be constant.
The interval between the tooth profile reference points 32 of the tooth profile 31 formed on the outer periphery of the chain guide device 40 is formed so as to coincide with the interval between the chain rollers 22 of the drive chain 4 as in the fifth embodiment. Therefore, when the drive chain 4 is driven, the chain roller 22 of the drive chain 4 sequentially fits in the tooth profile 31 formed on the outer periphery of the chain guide device 40 and rotates the chain guide device 40. This tooth reference point 32 of the chain guide device 40 is designed as different distances L _K from the center of rotation for each tooth 31, as described above, the chain roller 22 is fitted by rotation of the chain guide device 40 If the distance to the tooth profile 31 is changed sequentially, the amount of bending of the drive chain 4 also changes with time. From the point D ′ that contacts the main shaft drive sprocket 5 of the drive chain 4, the drive sprocket 3 passes through the chain guide device 40. The length of the drive chain 4 up to the contact point E ′ changes.
At this time, if the position of the rotation center with respect to the center of the substantially circular shape is determined so as to be close to the relationship between the time and the chain bending amount as shown in FIG. 4, that is, the shape center and the rotation center. The change in the amount of chain bending similar to that in the first embodiment can be applied to the driving chain 4 that is being driven, and the rotational speed of the main shaft 6 can be increased by appropriately bending the driving chain 4. If changed, the speed of the axis of the chain roller 17 of the transport table drive chain 10 moving on the forward path side and the speed of the transport table 15 attached to the transport table drive chain 10 can be made substantially constant.

It is a side view which shows schematic structure of the chain conveyor in Embodiment 1 of this invention. It is an enlarged view which shows the structure of the drive part vicinity of the chain conveyor in Embodiment 1 of this invention. FIG. 3 is a view corresponding to FIG. 2 showing a state after a lapse of a minute time from the initial state of FIG. It is a characteristic view showing the bending angle of the drive chain bent by the drive chain bending device with time. It is an enlarged view which shows the structure of the drive part vicinity of the chain conveyor in Embodiment 2 of this invention. It is an enlarged view which shows the structure of the drive part vicinity of the chain conveyor in Embodiment 3 of this invention. It is an enlarged view which shows the structure of the drive part vicinity of the chain conveyor in Embodiment 4 of this invention. It is explanatory drawing which shows the unusual shape chain guide apparatus in Embodiment 5 of this invention. It is explanatory drawing which shows the chain guide apparatus in which the rotation center in Embodiment 6 of this invention is eccentric. It is a side view which shows schematic structure of the conventional chain conveyor. It is sectional drawing along the ZZ line of FIG. It is an enlarged view which shows the structure of the drive part vicinity of the conventional chain conveyor. It is an enlarged view which shows the structure of the drive part vicinity of the chain conveyor in a prior art. It is a characteristic view showing the change of the speed of the horizontal direction of the chain roller which moves an outward path when changing the displacement angle of the conveyance stand drive sprocket of the conventional chain conveyor. It is a characteristic view showing the change of the speed of the conveyance stand which moves the forward path side I of the conventional type chain conveyor. It is explanatory drawing which shows the external shape of the drive sprocket of the conventional chain conveyor.

Explanation of symbols

1 Drive unit 2 Drive unit shaft 3 Drive sprocket 4 Drive chain
5 Spindle drive sprocket 6 Spindle 7 Carrier stand drive sprocket 8 Driven shaft
9 Driven sprocket 10 Carriage stand drive chain
11 Driving roller
12 Drive roller shaft 13 Drive roller shaft bracket
14 Drive roller guide
15 Transport stand 16 Chain link
17a, 17b Chain roller 20 Spindle drive sprocket 21 Carrier stand drive sprocket
22 Chain roller 31 Tooth profile
32 Tooth profile reference points 36, 37 Chain bending device
38, 39, 40 Chain guide device 41 Displacement device 42 Control device 43 Cam 44 Cam shaft 45 Cam rod 46 Pulley 47 Belt 48 Tensioner shaft 49 Tensioner 50 Elastic body I Outbound side
II Drive side reversing part
III Return side IV Driven side reversing part

Claims (6)

A drive sprocket rotated by the drive unit;
A drive chain wound around the drive sprocket;
A spindle drive sprocket attached to the spindle and hung around the drive chain;
A chain bending device that is provided between the drive sprocket and the main shaft drive sprocket and bends the drive chain in contact with the drive chain;
A carriage drive sprocket attached to the spindle and rotated at an equal angular speed to the spindle drive sprocket;
A driven sprocket pivotally attached to the driven shaft;
A transport table drive chain to which a transport table that is hung around the transport table drive sprocket and the driven sprocket is attached;
The chain conveyor according to claim 1, wherein the chain bending device changes the amount of bending of the drive chain in accordance with the position of the transport table.   The chain bending device comprises a displaceable chain guide device that abuts the drive chain, a displacement device that changes the position of the chain guide device, and a control device that controls the operation of the displacement device. Chain conveyor.   2. The chain conveyor according to claim 1, wherein the chain bending device comprises a displaceable chain guide device that contacts the drive chain, and a cam mechanism that changes a position of the chain guide device.   The chain bending device is a rotating body that abuts on the drive chain and rotates as the drive chain travels, and is formed such that the distance from the rotation center to the abutment position with the drive chain changes continuously. The chain conveyor according to claim 1, wherein the chain conveyor is a chain guide device.   The chain bending device is a rotary body having a substantially circular outline of a drive chain abutting portion that abuts the drive chain and rotates when the drive chain travels, and the center of the circle and the rotation center are decentered at different positions. The chain conveyor according to claim 1, wherein the chain conveyor is provided. The chain guide device is configured such that irregularities are formed in a contact portion with the drive chain, the irregularities mesh with the drive chain, and are rotated by running of the drive chain. The chain conveyor in any one of Claims 2-5.

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