EP1876135A1 - Drive system for conveying passengers - Google Patents

Abstract

The unit has a pair of pitch circles (5, 6) formed in such a manner that a pair of chain pins (3A, 3C) is in contact with the unit on the pitch circle (5) and another pair of chain pins (3B, 3D) is in contact with the unit on the pitch circle (6). The chain pins comprises rotatable, slidable and/or tiltably supported chain rollers and/or chain blades, over which the chain pins come into contact with the unit, where the unit is formed as a chain wheel (1) with teeth (7).

Description

The present invention relates to a drive and / or deflection element for a chain, in particular a drive and / or conveyor chain of a continuous conveyor for passenger transport or passenger transport plus their hand luggage.

Chains are used today in machine and plant construction in innumerable variants, for example as drive chains of continuous conveyors in passenger transport, especially in escalators or conveyors or moving walks.

Drive elements drive the chain or step chain or pallet chain in the direction of rotation, while deflecting elements convert their individual translatory track sections into one another by means of rotation. Preferably, but not necessary, fall driving and deflecting elements together and are designed for example in the form of sprockets or wedge wheels. Below is therefore briefly spoken of engagement elements that are in positive and / or non-positive engagement with the chain or step chain and drive and / or redirect.

Such engaging elements cause variations in the speed of the chain strand both in the longitudinal direction (i.e., in the direction of movement of the chain) and in the transverse direction normal thereto due to the so-called polygon effect. This results from the deflection of the individual chain links when entering the sprocket or engagement element. They experience abruptly an acceleration transverse or perpendicular to the direction of rotation of the chain strand, as the individual chain links shock-like an angular momentum is mediated - this leads to inlet joints or inlet bumps. In the outlet, this angular momentum reversely causes a rolling of the chain in the direction of rotation of the engagement member.

For a deeper understanding of the polygon effect, which is due to the induced vibrations, the main source of noise at maintained chains, promotes wear and in passenger conveyors as unpleasant nonuniformity of motion is noticeable, reference is made to the relevant literature, such as P.

Fritz: Dynamics of high-speed chain drives, VDI-Verlag, 1998, to which reference is made in full extent.

Simplified said, in particular neglecting the contact geometry, the polygon effect is explained with reference to FIG. 1: in a conventional engagement element 100, which is shown schematically in Fig. 1, the chain 200 runs tangentially into the pitch circle 500 such that the chain pins 300 then circulate on the pitch circle 500 with the radius R ₅₀₀ . If, as illustrated in idealized form in FIG. 1, a bolt first comes into engagement with the element 100 in a vertical plane shown in dot-dash lines, then it is forcibly guided from this point onwards at the speed v = R ₅₀₀ × ω, where ω designates the constant rotational speed of the engagement element , Its velocity L = v × cos (α) in the longitudinal direction of the load strand (horizontal in the drawing plane of FIG. 1) decreases with increasing angle α. Accordingly, the load strand is also moved at this decreasing speed L until the next pin 300 engages and is accelerated abruptly to v. This results in the periodically fluctuating running speed L = R ₅₀₀ × ω × cos (α).

To avoid the polygon effect beats the WO 00/07924 2, as shown schematically in FIG. 2, the chain pins 310 are continuously supported on the larger pitch circle 510 by a smaller active circle (dotted in FIG. 2) into which the chain 210 enters tangentially via a partially curved guide rail (not shown). in Fig. 2 by dashed lines) to convict. Simplified increases the radius r on which the incoming chain pin 310 is guided, in the ratio r (α) = R ₅₀₀ / cos (α), so that a constant Trumgeschwindikeit L = R ₅₀₀ × ω can be represented, while the speed of Chain bolt w accordingly increased steadily to w = R ₅₁₀ × ω.

The engagement element is designed as a sprocket 110 with a constant pitch circle 510. As a disadvantage, it can be seen that lift the chain rollers in the curved guide rail from the tooth root of the sprocket, ie they move relative to the engagement element on the pitch circle, which leads equally to noise and premature wear. For clarification, the engagement situation in which the chain pin 310 run in at the lowest point in the tooth base is shown in FIG. In the simplified representation, the earlier due to the real contact geometry is Neglected intervention without this affecting the basic principles. As can be seen in the unfilled tooth gaps in the left image area, the chain pin 310 travels from the smaller active circle to the larger pitch circle 510 and thereby slides upwards, in contrast to the teeth of the sprocket 110.

Object of the present invention is therefore to provide a drive and / or deflection for a chain or step chain or pallet chain available, which has no polygon effect and / or induces only a small shock and avoids the disadvantages mentioned above.

This object is achieved by an engagement element according to claim 1.

According to the invention, the engagement element or sprocket has a first pitch circle and a second pitch circle with different diameters such that alternately first chain pins on the first pitch circle and second chain pins on the second pitch circle come into engagement with the engagement element.

Alternating refers to any predefined sequence of chain pins, which can come alternately or mixed into engagement with the engagement element.

Preferably, a first chain pin on the first pitch circle and the following chain pin of the chain on the second pitch circle engage. (1-2-1-2 order ....)

But it is also possible that not only the first, but also one or more of the following chain pins of the chain come into engagement on the first pitch circle and only then engage one or more subsequent chain pins on the second pitch circle. For two consecutive chain pins on the first pitch circle and two subsequent chain pins on the second pitch circle, this will result in an order: 1-1-2-2-1-1-2-2 .... Similarly, there will be three consecutive chain pins on the chain the first pitch circle and three of these subsequent chain pins on the second pitch circle the order: 1-1-1-2-2-2-1-1-1-2-2-2 ..... Of course, even irregular sequences are possible where For example, two consecutive chain pins on the first pitch circle can only be tracked by a single chain pin on the second pitch circle (order: 1-1-2-1-1-2 ...) or vice versa where a single chain pin on the first pitch circle is followed by two chain pins on the second pitch circle (order: 1-2-2-1-2-2 ...). With knowledge of the present invention, any other order or combination of first and second link pins are possible which eliminate the polygon effect.

This principle is analogous to the mode of action of WO 00/07924 in Fig. 3 shown greatly simplified. If a chain pin 3A engages on the outer pitch circle 6, the result is the same as in FIG WO 00/07924 , That is, the subsequent chain pin 3 B is retracted due to the smaller pitch radius with constant load speed L. If this chain pin 3 B engages with the engagement element, it remains in the difference to WO 00/07924 however, on the smaller pitch circle 5. However, since the next chain pin 3C is in turn raised to the larger pitch circle 6, that pin 3C undergoes a vertical component in addition to its longitudinal speed, so that its overall speed, ie the speed at which the load strand is retracted , enlarged. Thereby, the decrease in the load circumferential speed explained with reference to FIG. 1 can be compensated due to the reduction in the longitudinal component of the speed of the chain pin 3B. The chain pin 3C is thereby accelerated to the rotational speed of the larger pitch circle 6 and then engages in this (in Fig. 3 drawn schematically).

So while in the WO 00/07924 Each chain pin engages first on the smaller circle of action and then slides in the tooth space on the larger pitch circle, engage according to the present invention, the chain pins alternately in different pitch circles. They must therefore not slide relative to the engagement element or sprocket to the outside or in the amount, but remain in the different pitch circles, which reduces both the wear and tear as well as the noise or noise due to the relative movement between the chain pin and engagement element.

In a preferred embodiment, the chain pins are supported during the entire deflection at the tooth base of the engagement element formed as a sprocket. This not only causes a more stable guidance, but also dampens and lowers vertical and vertical vibrations of the chain.

By reducing or eliminating the polygon effect, the noise and wear behavior of a chain drive with engagement elements according to the invention is greatly improved. Since the polygonal effect is approximately proportional to the chain pitch (distance between the chain pins), due to the reduced or eliminated polygon effect, larger pitches or smaller engagement element diameters or sprocket diameters can now also be realized. For sprockets, their diameter is proportional to their number of teeth, i. directly proportional to the pitch, larger pitches thus correspond to fewer teeth and simpler or easier to produce sprockets. This results in advantages in terms of material costs, the fabrication and mass production.

Preferably, the chain pins comprise, in a manner known per se, rotatably mounted chain rollers or steel or plastic rollers or bushes via which they engage with the engagement element. Whenever reference is made of chain pins, so are also addressed surrounding these chain rollers or chain sleeves, which contribute due to the rolling instead of the sliding friction to reduce friction and wear.

As already explained above in the explanation of the basic principle, the engagement element is formed in a preferred embodiment of the present invention as a sprocket with a toothing, wherein the chain pins engage in tooth gaps of the sprocket. This allows a positive and reliable engagement between the chain pin and engagement element. The toothing then advantageously has alternating first tooth gaps on the first pitch circle and second tooth gaps on the second pitch circle. Alternating refers to any predefined sequence of tooth gaps, which can be arranged alternately or mixed in any desired order.

Similarly, the engagement member may be formed in an alternative embodiment as a pair of wedge disks, the chain pins come into frictional contact with the wedge disks. To represent the different pitch circles, the wedge disks can alternately first areas with a first wedge angle and second Regions having a different second wedge angle, wherein the first pitch circle is defined by the contact points of the first chain pin with the first areas and the second pitch circle through the contact points of the second chain pin with the second areas. Although wedge discs require a minimum contact force to produce the necessary frictional connection, but allow on the other hand, the continuous adjustment of different deflection radii and drive ratios with the same drive units without additional gear or step transmission.

According to the invention, at least two different pitch circles are formed, onto which the chain pins accumulate alternately. However, an inventive engagement element may have a third pitch circle such that alternately first chain pins on the first pitch circle, second chain pin on the second pitch circle and third chain pin on the third pitch circle are engaged with the engagement element. The third or even further pitch circles thus represent intermediate stages, which allow a finer division of the chain while maintaining the basic principle of the alternating pitch circles.

In a particularly preferred embodiment of the present invention, an engagement element comprises a first and / or second guide rail, which guides the first and second chain pins on the first and second pitch circle. In particular, that guide rail which guides the chain pins onto the larger pitch circle imparts to this chain pin an additional vertical speed perpendicular to the longitudinal speed and thus compensates for the decreasing longitudinal component of the preceding chain pin. Equally, however, the chain pins can also be guided by the engagement element itself, such as the tooth gaps of a sprocket on the corresponding pitch circles, then depending on the geometry a small polygon effect remains, which is significantly reduced compared to conventional systems. A sliding of the chain pin relative to the engagement element can continue to be prevented.

Depending on the contact geometry, such relative sliding must not be completely avoided, but is generally reduced by remaining on different pitch circles.

In a further development of the above particularly preferred embodiment, the first or second guide rail guides the first and second chain pins on the first and second pitch circle, respectively, until they come out of engagement with the engagement element. Thus, a rolling of the chain can be avoided or at least reduced. In addition, a sliding of the chain pin relative to the engagement element is also reduced or eliminated.

An above-explained guidance of the chain pins on the pitch circles is preferably realized in a known manner in an inventive engagement element in that the first and / or second chain pins run on the first and second guide rail. In a particularly advantageous embodiment of the present invention, a two-part in the circumferential plane of the chain strand guide is provided, wherein a first half, the first, one of these opposite second half forms the second guide rail. The first chain pins have on the first half of the facing side a larger diameter, in particular for a first chain roller, and thus run on the first guide rail, while analogously, the second chain pin on the opposite side have a smaller diameter, in particular for a second chain roller and thus run on the second guide rail.

To avoid additional suggestions in the vertical or vertical direction, an engagement element according to the invention is preferably designed such that the chain runs tangentially onto the first and / or second pitch circle and / or runs out tangentially from the first and / or second pitch circle.

Fig. 1

eine schematische Darstellung zur Erläuterung des Polygoneffektes bei einem herkömmlich Eingriffselement;

Fig. 2

eine schematische Darstellung eines Kettenrades nach dem Stand der Technik, bei dem der Polygoneffekt unter Gleiten der Kettenbolzen in den Zahnlücken abgeschwächt wird;

Fig. 3

eine den Fig. 1, 2 entsprechende vereinfachte Seitenansicht eines Eingriffselements nach einer Ausführung der vorliegenden Erfindung;

Fig. 4

eine schematische Seitenansicht eines Kettenrades nach einer weiteren Ausführung der vorliegenden Erfindung; und

Fig. 5A, 5B

das Kettenrad nach Fig. 4 in perspektivischer Ansicht mit erster und zweiter Führungsschiene, einem Teil einer Kette und einem weiteren erfindungsgemäßen Kettenrad am anderen Ende des Kettenstrangs.

Other objects, features and advantages of the present invention will become apparent from the claims and the embodiments. This shows

Fig. 1

a schematic representation for explaining the polygon effect in a conventional engagement element;

Fig. 2

a schematic representation of a sprocket according to the prior art, in which the polygon effect is weakened under sliding of the chain pins in the tooth spaces;

Fig. 3

a simplified side view corresponding to Figures 1, 2 of an engagement element according to an embodiment of the present invention;

Fig. 4

a schematic side view of a sprocket according to another embodiment of the present invention; and

Fig. 5A, 5B

the sprocket of Fig. 4 in a perspective view with first and second guide rail, a part of a chain and another sprocket according to the invention at the other end of the chain strand.

The invention will be explained in more detail with reference to a sprocket. Equally, however, it can also be realized by other engagement elements, in particular the already mentioned wedge disk pairs, toroid pairs or similar transmissions or machine components.

Fig. 4 shows an engagement element according to an embodiment of the present invention in the form of a sprocket 1 from one side. The opposite page is also drawn in unfilled outline.

The sprocket 1 deflects a chain 2 between an upper load and a lower slack side by 180 ° and thereby drives them by means of a (not shown) drive, the engagement member to. Deflection and wrap angles as well as entry and exit direction are purely exemplary, other angles and directions can be realized equally by engagement elements according to the invention.

The sprocket has a first pitch circle 5 and a second pitch circle 6 with different diameters. In the exemplary embodiment, the second pitch diameter is the larger by way of example. The sprocket can be designed, for example, as involute toothing 7 with alternating tooth space depths, wherein first tooth gaps 8A, 8C define the first pitch circle 5, second tooth gaps 8B, 8D define the second pitch circle 6, which at a different radial distance from the axis or center of the chain wheel, Otherwise, however, with similar or the same tooth geometry (for example, with respect to undercut, head rounding and the like) are formed.

The chain 2 comprises chain pins with chain rollers or skids or runners 3A, 3B, 3C, 3D, which are rotatably or slidably mounted on them, or sledges or chain runners 3, which are connected to one another via link plates or chain links 4. In this case, the first chain pins 3A, 3C only comprise chain rollers on the first side, while with these alternating second chain pins 3B, 3D have chain rollers only on the second side.

By a first guide rail 9, which is arranged on the first side of the central longitudinal plane of the chain and the engagement member (in Fig. 4 below the plane and therefore shown in outline) on which run the first chain pins 3A, 3C, these first chain pins the first pitch circle 5 fed tangentially and are from the vertical center plane of the engagement member 1 with this engaged. You will experience a constant circumferential speed v = R ₅ × ω, where R ₅ denotes the radius of the first pitch circle 5 and ω the rotational speed of the sprocket 1.

In an analogous manner, a second guide rail 10 is arranged on the opposite second side of the central longitudinal plane next to the engagement element 1, run on the second chain pin 3 B, 3D and the second pitch 6 are fed tangentially so that they from the vertical center plane of the engagement element 1 with this are engaged. Find out while a constant circumferential speed ω w = R ₆ X, wherein R ₆ is the radius of the second pitch circle. 6

In a further embodiment of the present invention which is not shown, the chain pins 3A, 3B, 3C, 3D have continuous or divided chain rollers within the link plates 4. The first chain pins 3A, 3C protrude to the first, the second chain pins 3B, 3D to the second side. The tabs 4 alternately inside each roll. These run on the first or second guide rail 9 or 10 arranged there.

In the exemplary embodiment shown, the alternating first and second tooth spaces 8A, 8C and 8B, 8D are successively equipped with first and second chain pins or chain rollers 3A, 3B, 3C, 3D. These come by means of the guide rails 9, 10 tangentially to the respective pitch circle 5 and 6 in or to engage, without in the sequence in to slide or push the tooth spaces. They are advantageously based continuously in the tooth base and thus reduce vertical or vertical vibrations, upwards or downwards to the direction of movement of the chain strand 2.

As already explained in principle with reference to FIG. 3, the inner chain pins 3A, 3C are retracted into the sprocket by the respective preceding outer chain pins 3B, 3D at a constant longitudinal speed on the first guide rail 9, since the preceding outer chain pins 3B, 3D on the outer pitch circle 6 are deflected. Conversely, the outer chain pins 3B, 3D, being brought onto the outer pitch circle 6, are also accelerated in the vertical direction so that their total speed along the guide rail (s) 6 remains constant, although the longitudinal component of the inner chain pins 3A and 3C pulling them decreases with increasing sprocket rotation.

Thus, the polygon effect is prevented or greatly reduced.

Claims (13)

Drive and / or deflecting element (1) for a chain (2) with a plurality of first and second chain pins or chain rollers or chain runners (3A, 3B, 3C, 3D) and connecting them link plates or chain links (4), in particular a drive and / or conveyor chain of a continuous conveyor for passenger transport, the drive and / or deflection element having a first pitch circle (5) and a second pitch circle (6) such that alternately first chain pins (3A, 3C) on the first pitch circle (5) and second chain pins (3B, 3D) on the second pitch circle (6) are in engagement with the drive and / or deflection element. Drive and / or deflecting element according to claim 1, wherein the chain pins comprise rotatable or slidably mounted or swivel chain rollers or chain skids over which they come into engagement with the drive and / or deflection element. Driving and / or deflecting element according to one of the preceding claims, which is formed as a sprocket with a toothing (7), wherein the chain pins or chain rollers engage tooth spaces (8A, 8B, 8C, 8D) of the sprocket. Drive and / or deflecting element according to claim 3, wherein the toothing alternately first tooth gaps (8A, 8C) on the first pitch circle (5) and second tooth spaces (8B, 8D) on the second pitch circle (6). Drive and / or deflecting element according to claim 1 or 2, which is designed as a wedge disk pair, wherein the chain pins or chain rollers come into frictional contact with the wedge disks. Drive and / or deflecting element according to claim 5, wherein the wedge disks alternately first portions having a first wedge angle and second portions having a different second wedge angle, wherein the first pitch circle (5) through the contact points of the first chain bolt with the first areas and the second pitch circle (6) is defined by the contact points of the second chain pin with the second areas. Drive and / or deflecting element according to one of the preceding claims, further comprising a third pitch circle such that alternately first chain pins (3A, 3C) on the first pitch circle (5), second chain pin (3B, 3D) on the second pitch circle (6 ) and third chain pins on the third pitch circle are in engagement with the drive and / or deflection element. Driving and / or deflecting element according to one of the preceding claims, comprising a first guide rail (9) which guides the first chain pin on the first pitch circle; and / or having a second guide rail (10), which guides the second chain pin on the second pitch circle. Drive and / or deflecting element according to claim 8, wherein the first and second guide rail, the first and second chain pins on the first and second pitch circle leads, until they come out of engagement with the drive and / or deflection. Drive and / or deflecting element according to claim 8 or 9, wherein the first and / or second chain pins run on the first and second guide rail or slide. Drive and / or deflecting element according to one of the preceding claims, wherein the chain runs tangentially on the first and / or second pitch circle. Drive and / or deflecting element according to one of the preceding claims, wherein the chain runs tangentially out of the first and / or second pitch circle. Chain system, in particular for a continuous conveyor for passenger transport, comprising a chain (2) with a plurality of first and second chain pins (3A, 3B, 3C, 3D) and linking link plates (4) and a drive and / or deflection element according to one of the preceding claims.

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