JP2006264818A - Chain conveyor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To obtain a chain conveyor changing the rotational speed of a main shaft by changing the speed of a drive chain to reduce speed change of a carriage. <P>SOLUTION: This chain conveyor is provided with a drive sprocket 3 rotated by a drive unit 1; the drive chain 4 hung around the drive sprocket 3; a main shaft drive sprocket 5 mounted to the main shaft 6 and rotated by the drive chain 4; a carriage drive sprocket 7 mounted to the main shaft 6 and rotated at equiangular speed with the main shaft drive sprocket 5; a driven sprocket 9 rotatably mounted to a driven shaft 8; and a carriage drive chain 10 to which the carriage 15 rotated by the carriage drive sprocket 7 and the driven sprocket 9 is mounted. The radius vector of a tooth profile reference point 32 of each tooth profile 31 of the drive sprocket 3 is changed in accordance with a displacement angle of the carriage drive sprocket 7. <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. 6 is a side view showing a schematic configuration of a conventional chain conveyor, and FIG. 7 is a cross-sectional view taken along 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 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 in the direction of the transport platform drive sprocket 7 from the driven sprocket 9 side, the transport platform drive chain 10 that moves on the forward path side I along the linear drive roller guide 14 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 a reversing operation.
Thereafter, the conveyance table 15 moves the conveyance surface downward, the drive roller 11 upward, and the return path III from the conveyance table drive sprocket 7 to the driven sprocket 9.
In the driven shaft side reversing portion 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. 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. 5 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。そして、チェーンローラ１７ａと往路側Iの軌道上に位置しているチェーンローラ１７ｂとの水平方向の距離Ｘ_２は、

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、

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、

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、

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１０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１１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. 8 is an explanatory view showing the configuration near the drive section of the conventional chain conveyor. The 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

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

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 base drive chain 10 and the transport base 15 attached to the transport base 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

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).

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 side I is consistent with 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.
10 based on the equation (5), the change in the displacement angle theta _{when H} has a varied in the range from theta _H0 to theta _HE, velocity v _X3 in the horizontal direction of the chain roller 17b of the carrier table drive sprocket 7 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, the mobile when the displacement angle theta _H of the transport table driving sprocket 7 changes from theta _H0 to theta _HE, since the arrangement of the chain rollers 17b corresponds to the arrangement in the case of theta _H0, later the forward path I 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. 11 is a diagram showing the time t on the horizontal axis and the speed v _x3 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.

である。
駆動チェーン４の速度ｖ_Ｋと主軸６の回転速度ω_Ｓとの関係は、

であるので、主軸の回転速度ωは、

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、

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、

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. 9 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 drive 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 drive roller guide 14 for guiding the movement of the drive roller 11 on the forward path side I as in the conventional chain conveyor shown in FIG. 7 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 drive roller 11 that moves on the forward path side can be given 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 ,

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

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.

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

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. In order to reduce the speed change of the transport table, the speed of the main shaft is changed by changing the speed of the drive chain to change the speed of the transport table. The present invention provides a chain conveyor that reduces the load.

  In the chain conveyor according to the present invention, the drive sprocket rotated by the drive unit, the drive chain wound around the drive sprocket, the spindle drive sprocket attached to the spindle and wound around the drive chain, the spindle attached to the spindle A carriage drive sprocket that is rotated at the same angular speed as the drive sprocket, a follower sprocket that is rotatably attached to the driven shaft, and a carriage drive chain that is attached to the carriage drive sprocket and the carriage that is wound around the follower sprocket. The moving radius of the tooth reference point of each tooth profile of the drive sprocket is changed according to the displacement angle of the carriage drive sprocket.

  According to this invention, since the moving radius of the tooth profile reference point of each tooth profile of the drive sprocket is changed according to the displacement angle of the carriage drive sprocket, the chain conveyor that reduces the speed change of the carriage that moves on the forward path side. Can be obtained.

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 view corresponding to FIG. 2 showing a state after a lapse of a minute time from the initial state, and FIG. 4 is an explanatory view showing the outer shape of the drive sprocket of the chain conveyor according to Embodiment 1 of the present invention.

First, the first embodiment of the present invention will be described. The rough configuration and operation are those shown in the above-described conventional chain conveyor (FIGS. 5 to 8) and the above-described conventional chain conveyor ( Since this is the same as FIG. 9), the detailed description is omitted, and here, the points of the present invention that are different from them will be mainly described.
The main shaft drive sprocket 5 has a large number of teeth like the above-described conventional chain conveyor, and is different from the main shaft drive sprocket 20 shown in the above-described prior art chain conveyor with a small number of teeth.
Further, the distance from the axis of the drive unit shaft 2 of the main shaft drive sprocket 20 shown in the conventional chain conveyor or the conventional chain conveyor to the tooth reference point 32, that is, the moving radius is shown in FIG. As shown in FIG. 5, the tooth profile reference points 32 of the drive sprocket 3 of the present invention are arranged on a single arc centered on the axis of the drive unit shaft 2 at the same distance at all the tooth profile reference points 32. As shown in FIG. 4, the moving radius L _{K of the} point 32 is set to a different distance for each tooth profile. Therefore, when a curved line connecting the tooth profile reference points 32 in order is drawn, the curved line 34 (hereinafter referred to as a pitch graphic 34) has a shape different from an arc or the like.
Furthermore, in the present invention, unlike the chain conveyor shown in the prior art, in order to eliminate the extreme change in the height of the carriage 15 during operation, the drive roller on the forward path side I is removed as in the conventional chain conveyor. 11 is provided with a driving roller guide 14 for guiding the movement of 11.

搬送台駆動スプロケット７は主軸６に取り付けられ、主軸６の軸心を中心に回動自在にされており、主軸駆動スプロケット５も、搬送台駆動スプロケット７と同様に主軸６に取り付けられ、主軸６の軸心を中心に回動自在にされているので、搬送台駆動スプロケット７がある角度を回転するためには、主軸駆動スプロケット５も同じ角度を回転させることになる。
この発明において駆動チェーン４は、前述した従来形のチェーンコンベヤや、従来技術のチェーンコンベヤに示されるものと同様に、チェーンピッチＰ_Ｋが短いものを使用するために、主軸駆動スプロケット５の歯数Ｎ_Ｓが多いものを使用する。したがって、主軸駆動スプロケット５の隣接する歯形同士を線でつないでいくと、半径Ｒ_Ｓの略円状になり、その半径Ｒ_Ｓは、

である。
一方、歯数がＮ_Ｋ歯である駆動スプロケット３は駆動ユニット軸２に取り付けられており、駆動チェーン４は、その駆動スプロケット３と主軸駆動スプロケット５に巻き掛けられて、駆動ユニット軸２の回転を主軸６に伝動する。駆動ユニット軸２が１回転したときの主軸６の回転数I_Ｋは

であり、このI_Ｋ が、駆動系の平均速比である。
チェーンコンベヤの往路側Iの上において搬送台１５を搬送台駆動チェーン１０のチェーンピッチＰの距離移動させるとき、一辺の長さがＰである正Ｎ_Ｈ角形の搬送台駆動スプロケット７は、割出し角度θ_Ｈ分回転するが、これに要する時間をＴとおくと、主軸６の平均角速度ω_Ｓ’は、

である。
そして主軸６をこの平均角速度ω_Ｓ’で回転させるための駆動ユニット軸２の回転角速度ω_Ｋは、

である。
ところで、先の背景技術の項では、従来形のチェーンコンベヤは、主軸６の回転角速度ω_Ｓを一定としていたため、搬送台１５の速度が搬送台駆動スプロケット７の変位角度θ_Ｈに応じて変化すると述べており、それを（５）式で表わした。
これに対し、この発明では、搬送台１５の速度ｖ_Ｐをほぼ一定に保つために主軸６の回転角速度ω_Ｓを変化させるように考えている。したがって、前述した（５）式の搬送台駆動チェーン１０の移動速度ｖ_Ｈは一定値となり、主軸６の回転角速度ω_Ｓは変化する。このようにして（５）式を主軸６の回転角速度ω_Ｓについて導くと、（２０）式のように搬送台駆動スプロケット７の変位角度θ_Ｈの関数で表される。

主軸駆動スプロケット５は主軸６に取り付けられており、その回転角速度は搬送台駆動スプロケット７の回転角速度ω_Ｓと同じであるので、主軸駆動スプロケット５に巻き掛けられている駆動チェーン４の速度ｖ_Ｋは、

であり、駆動チェーン４の速度ｖ_Ｋも搬送台駆動スプロケット７の移動角度θ_Ｈの関数となるので、搬送台駆動チェーン１０の移動速度ｖ_Ｈを一定にするためには、駆動チェーンの速度ｖ_Ｋをθ_Ｈに応じて変化させなければならないことになる。
一方、駆動ユニット軸２に取り付けられている駆動スプロケット３の回転角速度ω_Ｋは、主軸６の平均回転角速度ω_Ｓ’に合わせて一定に設定しているが、駆動スプロケット３に巻き掛けられている駆動チェーン４の速度ｖ_Ｋは、（２１）式のように変化させなければならない。そこで、この発明では、駆動スプロケット３の駆動チェーン４と噛合う歯形の基準点と駆動ユニット軸２の軸心からの距離、すなわち動径Ｌ_Ｋを変化させて、駆動スプロケット３の回転角速度ω_Ｋが一定でも、チェーン速度を変化させることができるようにしたのである。
その動径Ｌ_Ｋとチェーン速度ｖ_Ｋとの関係は

であるから、（２２）式に（１９）式と（２１）式を代入すると

となり、これにより、搬送台駆動チェーン１０と搬送台駆動チェーン１０に取り付けられている搬送台１５の速度を一定にすることが可能な、駆動スプロケット３の動径Ｌ_Ｋを搬送台駆動スプロケット７の移動角度θ_Ｈに応じて求めることができる。 Then, in the present invention, the distance from the axis of the drive unit shaft 2 of each tooth reference point 32 of the drive sprocket 3, i.e. the relationship between the radius L _K and the displacement angle theta _H of the transport table driving sprocket 7 is described .
In the case of the chain conveyor in the present invention shown in FIG. 1, the length P ′ of the transport table 15 and the chain pitch P of the transport table drive chain 10 are made equal. Further, the distance P ″ between adjacent tooth profiles of the carriage drive sprocket 7 is also equal to the length P ′ of the carriage base 15. If the number of teeth of the carriage drive sprocket 7 is _NH , the length of one side of the sprocket is P. It is a regular _NH square that is "". When a straight line is drawn from the adjacent tooth profile toward the center of rotation of the carriage drive sprocket 7, that is, the center of the main shaft 6, each length is half _RH of the pitch circle diameter of the carriage drive sprocket 7 and adjacent to each other. An isosceles triangle can be drawn by a straight line drawn from the tooth profile reference point 32 toward the center of the main axis 6 and a straight line connecting the adjacent tooth profile reference points 32. The central angle θ _{HE at} this time is the index angle of the carriage drive sprocket 7, and θ _HE and R _H can be obtained by the following equations (14) and (15).

The carriage driving sprocket 7 is attached to the main shaft 6 and is rotatable about the axis of the main shaft 6. The main shaft driving sprocket 5 is also attached to the main shaft 6 in the same manner as the carrier driving sprocket 7. Therefore, in order to rotate the carriage drive sprocket 7 at a certain angle, the main shaft drive sprocket 5 is also rotated at the same angle.
In the present invention, the drive chain 4 has a short chain pitch P _K as in the conventional chain conveyor and the chain conveyor of the prior art. N _S to use those often. Therefore, when we connect the adjacent teeth with each other of the main shaft drive sprocket 5 by a line, becomes substantially circular with a radius R _S, the radius R _S is

It is.
On the other hand, the drive sprocket 3 number of teeth is N _K tooth is attached to the drive unit shaft 2, the drive chain 4 is wound around the drive sprocket 3 and the main shaft drive sprocket 5, the rotation of the drive unit shaft 2 Is transmitted to the main shaft 6. The rotational speed I _K of the main shaft 6 when the drive unit shaft 2 makes one rotation is

This I _K is the average speed ratio of the drive system.
When the carriage 15 is moved a distance of the chain pitch P of the carriage drive chain 10 on the forward path side I of the chain conveyor, a regular _NH square carrier carriage drive sprocket 7 whose side is P is indexed. The angle θ _H rotates, and if the time required for this is T, the average angular velocity ω _S ′ of the spindle 6 is

It is.
The rotational angular velocity ω _K of the drive unit shaft 2 for rotating the main shaft 6 at this average angular velocity ω _S ′ is:

It is.
By the way, in the previous background art section, the conventional chain conveyor has a constant rotational angular velocity ω _S of the main shaft 6, so that the speed of the carriage 15 changes according to the displacement angle θ _H of the carriage drive sprocket 7. This is expressed by equation (5).
On the other hand, in the present invention, the rotational angular velocity ω _S of the main shaft 6 is considered to be changed in order to keep the speed v _{P of the} carriage 15 substantially constant. Accordingly, the moving speed v _H of the above-described carrier drive chain 10 of the formula (5) becomes a constant value, and the rotational angular speed ω _S of the main shaft 6 changes. In this way, when the equation (5) is derived with respect to the rotational angular velocity ω _S of the main shaft 6, it is expressed as a function of the displacement angle θ _H of the carriage drive sprocket 7 as in the equation (20).

Since the main shaft drive sprocket 5 is attached to the main shaft 6 and its rotational angular velocity is the same as the rotational angular velocity ω _S of the carriage drive sprocket 7, the speed v _{K of the} drive chain 4 wound around the main shaft drive sprocket 5. Is

Since the speed v _K of the drive chain 4 is also a function of the movement angle θ _H of the carriage drive sprocket 7, in order to make the movement speed v _H of the carriage drive chain 10 constant, the speed v of the drive chain It will have to be varied according to _K on theta _H.
On the other hand, the rotational angular velocity ω _K of the drive sprocket 3 attached to the drive unit shaft 2 is set constant according to the average rotational angular velocity ω _S ′ of the main shaft 6, but is wound around the drive sprocket 3. The speed v _K of the drive chain 4 must be changed as shown in equation (21). Therefore, in this invention, the distance from the axis of the drive chain 4 engaged caries reference point type and the drive unit shaft 2 of a drive sprocket 3, i.e. by changing the radius L _K, the rotational angular velocity omega _K of the drive sprocket 3 Even if is constant, the chain speed can be changed.
The relationship between the radius L _K and the chain speed v _K is

Therefore, substituting (19) and (21) into (22)

Next, thereby, a velocity of the carrier table 15 that is attached to the carrier table drive chain 10 and the carrier table drive chain 10 can be made constant, the carrier table drive sprocket 7 a radius L _K of the drive sprocket 3 it can be determined in accordance with the movement angle theta _H.

である。
そしてこのときの状態を初期状態と呼ぶことにする。
次に、図３を用いて、初期状態から微少時間Δｔが経過したときの状態を説明する。
往路側を移動する搬送台駆動チェーン１０は一定速度ｖ_Ｐであるので、微少時間Δｔが経過したときのチェーンローラ軸心Ｂは、Ｂ’の位置に移動し、その座標は

である。
そしてこのときの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軸心Ａの座標は、チェーンローラ軸心Ｂ’を中心とし、搬送台駆動チェーン１０のチェーンピッチＰを半径とした円弧と、主軸６の軸心を中心とし、搬送台駆動スプロケット７のピッチ円直径の半分Ｒ_Ｈを半径とする円弧との交点Ａ’に移動する。このときのチェーンローラ軸心Ａ’の座標は（Ａ’_Ｘ ， Ａ’_Ｙ）であり、次の（２５）式と（２６）式で求まる。これらの式は、２円の交点を求める一般式であるので、式の説明はここでは省略する。

そして（２５）式と（２６）式により求めたＡ’の座標値を次の（２７）式に代入すると、搬送台駆動スプロケット７の変位角度θ_Ｈを計算することができる。

このθ_Ｈの値を（２２）式に代入すれば、微少時間Δｔが経過したときの、駆動チェーン４と駆動スプロケット３との噛合い位置Ｅ’点の動径Ｌ_Ｋ’を求めることができる。
このとき駆動スプロケット３と駆動チェーン４との噛合い個所Ｅ点は、角度θ_Ｋを時計方向に回転し、駆動チェーン４との噛合い個所は、Ｅ’点に移る。Ｅ点とＥ’点との相対角度θ_Ｋ’は、

であるので、駆動ユニット軸２を原点とするＥ’点の極座標（θ_Ｋ’，Ｌ_Ｋ’）を得ることができる。
そしてさらに時間Δｔが経過したものとして同じ計算を繰り返し、順々に駆動スプロケット３と駆動チェーン４との噛合い個所を求め、駆動ユニット軸２を原点としたときの、初期状態の駆動スプロケット３と駆動チェーン４との噛合い個所Ｅ点に対する相対極座標を連続的に求めていき、それらの点をプロットすれば、図４に示すような駆動スプロケット３の歯形基準点３２が配置されるピッチ図形３４を、点の集合体として描くことができる。
また、往路側を移動するチェーンローラ１７の軸心Ｂが時間Ｔ経過後に、搬送台駆動チェーン１０のチェーンピッチＰの距離を移動したとき、チェーンローラ１７の軸心Ｂは初期状態のチェーンローラの軸心Ａの位置に一致し、往路側を移動するチェーンローラ１７の軸心Ｂに隣接するチェーンローラ１７の軸心Ｃが初期状態のチェーンローラ１７の軸心Ｂの位置に一致するが、以降の計算はチェーンローラ１７の軸心Ｂをチェーンローラ１７の軸心Ａに、チェーンローラ１７の軸心Ｃをチェーンローラの軸心Ｂに置き換えて、前述の手順を繰り返していけばよい。
そして、隣接する駆動スプロケット３の歯形基準点３２間の距離は、駆動チェーン４のチェーンピッチＰ_Ｋと同じであるので、初期状態の駆動スプロケット３と駆動チェーン４との噛合い個所Ｅ点から、距離Ｐ_Ｋ毎に先に求めたピッチ図形３４を刻んでいき、その刻み位置の近傍に駆動スプロケット３の歯形基準点３２を配置し、駆動スプロケット３の歯形３１を形成すれば、搬送台駆動スプロケット７の変位角度θ_Ｈに応じて駆動スプロケット３の噛合い部の動径Ｌ_Ｋを適当に変化させることができる駆動スプロケット３となる。これにより、往路側Iを移動する搬送台１５の速度変化を軽減したチェーンコンベヤとすることができる。
なお、

とし、駆動スプロケット３の歯数Ｎ_ＫをＫの倍数になるように設計しておけば、駆動スプロケット３が初期状態から１回転したときに、搬送台駆動チェーン１０と搬送台駆動スプロケット７との噛合い状態も初期状態と同じになるので、搬送台１５の位置や、搬送台駆動スプロケット７の変位角度θ_Ｈに対する駆動チェーン４と駆動スプロケット３との噛合い個所Ｅ’点の駆動ユニット軸２の軸心よりの動径Ｌ_Ｋの変化の関係を常に保った状態で、搬送台１５の駆動を続けることができる。 Next, the pitch figure 34 of the drive sprocket 3 in this invention is demonstrated.
FIG. 2 is an explanatory view schematically showing a state in the vicinity of the main shaft 6 of the chain conveyor in the present invention.
One axis of the chain roller 17 of the conveying table drive chain 10 hanging up on the conveying table drive sprocket 7, when present on the vertical line passing through the axis O _S of the spindle 6, the coordinates of the chain rollers axis A ( a _X, a _Y) is,
_{(A X, A Y) =} (0, R H)
However, the coordinates O _S (O _SX , O _SY ) = (0, 0).
It is. The distance between the chain roller axis B and the chain roller axis A adjacent to the chain roller axis A, which is located on the forward path side I separated from the horizontal line passing through the axis of the main shaft 6 by the distance _RH, is the carriage drive chain. Since the chain pitch P is 10, the coordinates (B _X , B _Y ) of the chain roller axis B are
_{(B X, B Y) =} (-P, R H)
It is. At this time, the meshing position between the main shaft drive sprocket 5 and the drive chain 4 is designated as point D, and the meshing position between the drive sprocket 3 and the drive chain 4 is designated as point E. In order to make the explanation easy to understand, the drive chain portion between point D and point E is horizontal here, but the angle of the straight line connecting point D and point E is not particularly particular.
The state shown in FIG. 2, since the movement angle of the transport table driving sprocket 7 in theta _{H0 = 0,} by substituting this value in (22), between the axis O _K and E point of the drive unit shaft 2 , That is, the moving radius L _K0 of the engagement point E point of the tooth profile of the drive chain 4 and the drive sprocket 3 in the initial state is

It is.
The state at this time is referred to as an initial state.
Next, a state when a minute time Δt has elapsed from the initial state will be described with reference to FIG.
Since the carriage drive chain 10 moving on the forward path side has a constant speed v _P , the chain roller axis B when the minute time Δt has passed moves to the position B ′, and its coordinates are

It is.
At this time, the coordinates of the chain roller axis A wound around the carriage drive sprocket 7 are an arc centered on the chain roller axis B ′ and having a chain pitch P of the carriage drive chain 10 as a radius, and the main shaft 6. Is moved to an intersection A ′ with an arc whose radius is half of the pitch circle diameter _RH of the carriage drive sprocket 7. The coordinates of the chain roller axis A ′ at this time are (A ′ _X , A ′ _Y ), and are obtained by the following equations (25) and (26). Since these equations are general equations for obtaining the intersection of two circles, explanation of the equations is omitted here.

Then, by substituting the coordinate value of A ′ obtained by the equations (25) and (26) into the following equation (27), the displacement angle θ _H of the carriage drive sprocket 7 can be calculated.

By substituting the value of this theta _H in (22), can be obtained when the short time Δt has elapsed, 'radius L _{K points'} engagement position E of the drive chain 4 and the driving sprocket 3 .
Meshing point E point in this case the drive sprocket 3 and the drive chain 4, the angle theta _K rotates clockwise, the meshing point between the drive chain 4 proceeds to point E '. The relative angle θ _K 'between point E and point E' is

Therefore, polar coordinates (θ _K ′, L _K ′) of point E ′ with the drive unit axis 2 as the origin can be obtained.
Then, the same calculation is repeated assuming that the time Δt has passed, and the meshing positions of the drive sprocket 3 and the drive chain 4 are sequentially obtained, and the drive sprocket 3 in the initial state when the drive unit shaft 2 is the origin and If the relative polar coordinates with respect to the meshing point E with the drive chain 4 are continuously obtained and these points are plotted, the pitch figure 34 on which the tooth profile reference point 32 of the drive sprocket 3 is arranged as shown in FIG. Can be drawn as a collection of points.
In addition, when the axis B of the chain roller 17 moving on the forward side moves the distance of the chain pitch P of the carriage drive chain 10 after the time T has elapsed, the axis B of the chain roller 17 is the chain roller in the initial state. The axial center C of the chain roller 17 that coincides with the position of the axial center A and is adjacent to the axial center B of the chain roller 17 that moves on the outward path side coincides with the position of the axial center B of the chain roller 17 in the initial state. This calculation can be performed by replacing the axis B of the chain roller 17 with the axis A of the chain roller 17 and the axis C of the chain roller 17 with the axis B of the chain roller 17 and repeating the above procedure.
Since the distance between the tooth profile reference points 32 of the adjacent drive sprockets 3 is the same as the chain pitch P _K of the drive chain 4, from the meshing point E point between the drive sprocket 3 and the drive chain 4 in the initial state, If the pitch figure 34 obtained previously is engraved for each distance P _K, the tooth profile reference point 32 of the drive sprocket 3 is arranged in the vicinity of the notch position, and the tooth profile 31 of the drive sprocket 3 is formed, then the carriage drive sprocket The driving sprocket 3 can appropriately change the moving radius L _K of the meshing portion of the driving sprocket 3 in accordance with the displacement angle θ _{H of} 7. Thereby, it can be set as the chain conveyor which reduced the speed change of the conveyance stand 15 which moves the outward side I.
In addition,

And then, if designing a tooth number N _K of the drive sprocket 3 so that a multiple of K, when the drive sprocket 3 is rotated one from the initial state, the carrier table drive chain 10 and the transport table driving sprocket 7 Since the meshing state is the same as the initial state, the drive unit shaft 2 at the point E ′ where the drive chain 4 and the drive sprocket 3 mesh with the position of the transport table 15 and the displacement angle θ _H of the transport table drive sprocket 7. always maintaining the state of the relationship between changes in the moving radius L _K of the axial center of the can continue the driving of the carrier table 15.

The obtained pitch figure 34 is a shape different from a geometric figure such as an arc, and is difficult to handle when drawing using CAD or the like. In this case, the obtained pitch figure 34 is made into a figure approximated by continuous arcs, ellipses, and straight lines suitable for drawing, the tooth shape reference point 32 of the drive sprocket 3 is arranged, and the tooth shape 31 of the drive sprocket 3 is formed. also, since it is possible to appropriately change the radius L _K of the meshing portion of the drive sprocket 3 in accordance with the displacement angle theta _H of the transport table driving sprocket 7, the speed change of the transport platform 15 to move forward path I Reduced chain conveyor.

Further, even if the obtained pitch figure 34 is approximated by an ellipse, the tooth profile reference point 32 of the drive sprocket 3 is arranged, and the tooth profile 31 of the drive sprocket 3 is formed, depending on the displacement angle θ _H of the carriage drive sprocket 7. since the radius L _K of the meshing portion of the drive sprocket can be appropriately changed, it may be a chain conveyor with reduced speed variation of the transfer table 10 to move forward side I.

In the first embodiment of this invention, carrier table 15 had attached to the carrier table drive chain 10 via a drive roller shaft 12, in this invention, it is affected by the displacement angle theta _H of the transport table driving sprocket 7 Therefore, the same effect can be obtained by a method of directly attaching the transport table 15 to the main body of the transport table drive chain 10 because the change in the speed of the transport table drive chain 10 is reduced.

Further, the first embodiment of this invention has assumed that fitted with the driving roller 11 on the outside of the transfer table drive chain 10, in this invention, without being influenced by the displacement angle theta _H of the transport table driving sprocket 7 Since the change of the speed of the carriage drive chain 10 is considered to be reduced, the mounting position of the drive roller 11 with respect to the carriage drive chain 10 or the presence or absence of the drive roller 11 is not a big problem. Even in this case, the present invention can be applied.

  Furthermore, in the first embodiment of the present invention, the carriage 15 having the same length P ′ as the chain pitch is attached to each chain pitch P of the carriage drive chain 10, but this is an interval that is a multiple of the chain pitch P. Even if the carriage 15 is attached or the length of the carriage 15 is not the same as the chain pitch, the present invention has been considered to reduce the speed change of the carriage drive chain 10. The interval and length are not a big problem and can be applied even in such a case.

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 explanatory drawing which shows the external shape of the drive sprocket of the chain conveyor in Embodiment 1 of this invention. It is explanatory drawing which shows the external shape of the drive sprocket of the conventional chain conveyor. 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 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 point 33 Drive unit shaft axis 34 Pitch figure
I Outward side
II Drive side inversion section
III Return side
IV Driven side inversion section

Claims (3)

A drive sprocket rotated by a drive unit, a drive chain wound around the drive sprocket, a spindle drive sprocket attached to the spindle and wound around the drive chain, and an equiangular speed with the spindle drive sprocket attached to the spindle A chain conveyor having a carriage drive sprocket that is rotated by a carriage, a driven sprocket that is rotatably attached to a driven shaft, and a carriage drive chain that is attached to the carriage drive sprocket and a carriage that is wound around the driven sprocket. In
A chain conveyor characterized in that a moving radius of a tooth profile reference point of each tooth profile of the drive sprocket is changed in accordance with a displacement angle of the carriage drive sprocket.   Each tooth reference point is placed on a figure composed of continuous arcs, straight lines, and ellipses so that the radius of each tooth reference point of the drive sprocket can be changed according to the displacement angle of the carriage drive sprocket. The chain conveyor according to claim 1, wherein:   A chain conveyor characterized in that each tooth profile reference point is arranged on an ellipse so that the moving radius of each tooth profile reference point of the drive sprocket can be changed according to the displacement angle of the carriage drive sprocket.

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