EP0711725A1 - Guide apparatus for endless band of moving staircases or walkways - Google Patents

Abstract

The chain links (4) are joined by chain bolts (5) to adjacent chain links. The chain bolts holder chain rollers (3) running on the track (8) of a support rail (6) and on a track (16) of a compensating rail (7) and deflected by a chain wheel (1). The track of the support rail and that of the compensating rail ae positioned outside a tangent (13) extending in the belt's continuous direction of travel, on a chain wheel circle (12) of the chain wheel. One end of the track of the compensating rail leads to the chain wheel circle.

Description

The invention relates to a device for guiding a belt continuum for escalators or moving walks consisting of steps or pallets, of chain links which are connected to the adjacent chain links by means of chain bolts, and of chain rollers held by the chain bolts, the chain rollers on a track of a support rail and on one Travel the track of a compensating rail and be deflected by a sprocket.

From the patent specification DE 1 009 777, an escalator with a step-bearing step belt and chain wheels has become known. The chain wheels arranged at each end of the escalator serve to deflect and drive the step belt. The step belt consists of rollers connected by chain links, which are guided on support rails. When the step belt is deflected at the end of the escalator, the rollers are carried by the chain wheel from the entrance to the exit. The support rails are arranged so that the rollers on the sprocket rotate by 180 °. The path from the vertical central axis of the chain wheel to the support rail is bridged by a tangential guide arranged on the side of the chain wheel. At the entrance, the tangential guide takes over the rollers from the support rail and guides the rollers in the tangential direction onto the sprocket circle. At the exit, the rollers leave the sprocket circle after a rotation of 180 ° in the tangential direction and are then guided from the tangential guide to the support rail.

The tangential guides do not eliminate the jerky movements and noise of the chain links that occur when the rollers engage the teeth of the chain wheel and when the rollers are detached from the chain wheel. The jerking movements in the resonance range lead to longitudinal and transverse vibrations which are perceived by the passenger as unpleasant and which lead to a qualitative loss due to excessive wear of mechanical parts.

The invention seeks to remedy this. The invention, as characterized in the claims, solves the problem of avoiding the disadvantages of the known device and of guiding the belt continuum in such a way that the driving comfort perceived by the passenger is high, jerky movements and noises are avoided and the mechanical wear is kept low become.

Quiet running properties have an advantageous effect on the service life of the mechanical parts and cause less repair and maintenance work. It is also advantageous that smaller sprocket diameters and / or longer chain links are possible. Quiet running guarantees the passenger a fatigue-free stay on the means of transport. In addition, due to the shock, jerk and vibration-free stay on the escalator or on the moving walk, the passenger draws positive conclusions about the mechanical quality of the means of transport.

The invention is explained in more detail below with the aid of drawings which illustrate only one embodiment.

Fig. 1

eine schematische Darstellung eines Kettenrades mit einem Bandkontinuum einer Fahrtreppe oder eines Fahrsteiges,

Fig. 2

eine Draufsicht des Kettenrades und des Bandes gemäss Fig. 1,

Fig. 3

eine Seitenansicht des Kettenrades und des Bandes gemäss Fig. 1,

Fig. 4

einen Schnitt entlang der Linie A-A der Fig. 1,

Fig. 5

eine Ausgleichsschiene,

Fig. 6

eine Seitenansicht der Ausgleichsschiene gemäss Fig. 5 und

Fig. 7

eine schematische Darstellung des Kettenrades und des Bandes für den mathematischen Ansatz zur Herleitung einer optimalen Laufbahn der Ausgleichsschiene.

Show it:

Fig. 1

1 shows a schematic illustration of a chain wheel with a belt continuum of an escalator or a moving walk,

Fig. 2

a plan view of the sprocket and the belt of FIG. 1,

Fig. 3

a side view of the sprocket and the belt of FIG. 1,

Fig. 4

2 shows a section along the line AA in FIG. 1,

Fig. 5

a compensation rail,

Fig. 6

a side view of the compensating rail according to FIGS. 5 and

Fig. 7

is a schematic representation of the sprocket and the belt for the mathematical approach to derive an optimal track of the compensation rail.

1 to 7, 1 denotes a chain wheel which serves to deflect and drive a belt continuum 2 of an escalator or moving walk. 1 shows the entry of the belt continuum 2 onto the chain wheel 1. The outlet of the belt continuum 2, which is a mirror image of the inlet, is not shown. The belt continuum 2 consists of steps or pallets (not shown) and of chain rollers 3, which are connected by means of chain links 4 and chain pins 5. The chain rollers 3 run on a support rail 6 and on a side arranged on the chain wheel 1 Compensating rail 7. Sprocket teeth 9 arranged on the circumference of the sprocket 1 form tooth gaps 10 in which the chain rollers 3 engage. The axis of a tooth space 10 is designated 11 and is at right angles on a sprocket circle designated 12. A tangent 13 to the sprocket circle 12 that runs parallel to a raceway 8 of the support rail 6 is at a tangent point 14 at right angles to the respective tooth gap axis 11. At the tangent point 14, the chain roller 3 engages with the sprocket 1 on the input side or leaves the sprocket 1 on the output side and then arrives on the output side arranged compensating rail 7. On the sprocket 1, the chain bolts 5 move at an angular velocity w on a wheel center circle 15 with a radius r and on the raceway 8 of the support rail 6 at the speed v. The straight running track 8 of the support rail 6 merges into a curved track 16 of the compensating rail 7, which ends at the tangent point 14. The track 8 of the support rail 6 lies at a certain distance h₀ outside the tangent 13, so that the chain rollers 3 move on the track 16 of the compensating rail 7 in the forward direction and at right angles to the forward direction.

5 and 6 show the compensating rail 7. It consists of a rail body 17 with the track 16 and a rail foot 18 on which bores 19 are arranged. The compensation rail 7 is attached to the frame of the sprocket 1 by means of the holes 19 penetrating screws.

Durch Auflösen der Differentialgleichung [4] ergibt sich die Gleichung $$\begin{array}{c}\begin{array}{c}\text{∫}{\dot{\text{x}}}_{\text{2}}\text{= -∫f *}\dot{\text{φ}}\text{* r}\\ \begin{array}{}\text{[4']}{\text{x}}_{\text{2}}\text{= -f * φ * r + C}\end{array}\end{array}\end{array}$$

Aufgrund der zyklischen Bewegung gilt die Anfangsintegrationskonstante φ = 0 und die Endintegrationskonstante φ = 2π/z. z ist die Zähnezahl des Kettenrades 1. Der Geschwindigkeitsfaktor f kann mit der Gleichung [4'] und den Anfangs- und Endintegrationskonstanten bestimmt werden. Für einen optimalen Kurvenverlauf muss die rotatorische Geschwindigkeit w und die translatorische Geschwindigkeit v durch den Geschwindigkeitsfaktor f gekoppelt sein, der beispielsweise für ein Kettenrad 1 mit 16 Kettenradzähnen den Wert 0,993587 hat.Fig. 7 shows schematically the sprocket and the band for the mathematical approach to deriving an optimal curve shape of the raceway 16 of the compensating rail 7. The division of the band continuum 2 is with the variable l shown. The variable l is the distance between two adjacent chain pins 5. The instantaneous angle between the tangent point 14 'and the chain pin 5 on the wheel center circle 15 is shown by φ. Two adjacent chain bolts 5 lying on the wheel center circle 15 form an angle φ _m with the center point of the chain wheel 1. The variables ε₁ and ε₂ represent the current angle of the chain link 4 with respect to the tangent 13 'to the wheel center circle 15. The variables x₂ and y describe the current path in the tangent direction or perpendicular to the tangent direction. The optimal curve shape of the raceway 16 of the compensating rail 7 is calculated using the following system of equations: $$\begin{array}{c}\begin{array}{c}\begin{array}{}\text{[1]}{\text{H}}_{\text{0}}{\text{+ r = l * <figure-callout id="1" label="sinε" filenames="imgf0001.png" state="{{state}}">sinε</figure-callout>}}_{\text{1}}{\text{+ sinε}}_{\text{2nd}}\text{+ r * cos φ}\end{array}\\ \begin{array}{}\text{[2]}{\text{x}}_{\text{2nd}}{\text{= l * <figure-callout id="1" label="cosε" filenames="imgf0001.png" state="{{state}}">cosε</figure-callout>}}_{\text{1}}{\text{+ l * cosε}}_{\text{2nd}}\text{- r * sin φ}\end{array}\\ \begin{array}{}\text{[3]}{\text{y = l * sinε}}_{\text{1}}\end{array}\\ \begin{array}{}\text{[4]}{\dot{\text{x}}}_{\text{2nd}}\text{= -f *}\dot{\text{φ}}\text{* r}\end{array}\end{array}\end{array}$$

Solving the differential equation [4] gives the equation $$\begin{array}{c}\begin{array}{c}\text{∫}{\dot{\text{x}}}_{\text{2nd}}\text{= -∫f *}\dot{\text{φ}}\text{* r}\\ \begin{array}{}\text{[4 ']}{\text{x}}_{\text{2nd}}\text{= -f * φ * r + C}\end{array}\end{array}\end{array}$$

Due to the cyclical movement, the initial integration constant φ = 0 and the final integration constant φ = 2π / z. z is the number of teeth on the chain wheel 1. The speed factor f can be determined using equation [4 '] and the initial and final integration constants. For an optimal curve, the rotary speed w and the translatory speed v must be coupled by the speed factor f, which has the value 0.993587 for a sprocket 1 with 16 sprocket teeth, for example.

From the equations [1], [2] and [4 '] sinε₁ of the equation [3] and thus from y the optimal curve shape of the raceway 16 can be determined. For a certain number of sprocket teeth, for a certain chain pin distance l and for a certain radius r of the wheel center circle 15 there is exactly one speed factor f, exactly one distance h₀ and only one optimal curve shape of the raceway 16.

Claims (3)

Device for guiding a belt continuum (2) for escalators or moving walks consisting of steps or pallets, of chain links (4) which are connected to the adjacent chain links (4) by means of chain bolts (5), and of chain rollers held by the chain bolts (5) (3), the chain rollers (3) moving on a track (8) of a support rail (6) and on a track (16) of a compensating rail (7) and being deflected by a chain wheel (1),
characterized,
that the raceway (8) of the support rail (6) and the raceway (16) of the compensating rail (7) are arranged outside a tangent (13) extending in the running direction of the belt continuum (2) to a chain wheel circle (12) of the chain wheel (1) , wherein the track (16) of the compensating rail (7) is guided at one end to the sprocket circle (12). Device according to claim 1,
characterized,
that the track (8) of the support rail (6) is arranged parallel to the tangent (13) and at a distance (h₀) from the tangent (13) and
that the raceway (16) of the compensating rail (7) is curved at one end, the chain rollers (3) changing from a straight-line movement into a curved movement and at a tangent point (14) into a circular movement. Device according to claim 2,
characterized,
that the curve shape of the raceway (16) of the compensating rail (7) and the distance (h₀) from the number of sprocket teeth (9), from the chain pin spacing (l) and from the radius (r) of the wheel center circle (15) by means of the system of equations $$\begin{array}{c}\begin{array}{c}{\text{H}}_{\text{0}}{\text{+ r = l * sinε}}_{\text{1}}{\text{+ sinε}}_{\text{2nd}}\text{+ r * cos φ}\\ {\text{x}}_{\text{2nd}}{\text{= l * cosε}}_{\text{1}}{\text{+ l * cosε}}_{\text{2nd}}\text{- r * sin φ}\\ {\text{y = l * sinε}}_{\text{1}}\\ {\dot{\text{x}}}_{\text{2nd}}\text{= -f *}\dot{\text{φ}}\text{* r}\end{array}\end{array}$$

is calculated, the variables ε₁ and ε₂ the instantaneous angle of a chain link (4) with respect to the tangent (13 ') to the wheel center circle (15), the variable φ the instantaneous angle between the tangent point (14') and a chain pin (5) on the wheel center circle (15), f a speed factor and the variables x₂ and y mean the current path in the tangent direction or perpendicular to the tangent direction of a chain pin (5).

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