The present invention relates to a driving system for driving a conveyer band of a conveyer apparatus and a corresponding conveyer apparatus comprising a first rotatable shaft coupled with at least one sprocket, wherein the at least one sprocket is adapted to be coupled with at least one chain of the conveyer band, and comprising a second rotatable shaft coupled with a motor, wherein the motor is adapted to set the second rotatable shaft into a rotary motion.

Prior art

In a conveyer apparatus, e.g. an escalator or a moving walkway, a conveyor band (step band or pallet band) is driven by means of a motor. The conveyor band is usually connected with chains, comprising a plurality of chain links connected by corresponding connection means, e.g. pins, plates, rollers, etc. A main shaft of the conveyer apparatus, usually located in one end of the apparatus, is connected with at least one sprocket. This sprocket has a number of teeth on its circumference, which engage the connection means of the corresponding chain. The motor can convert electric energy into mechanical energy, by means of which the main shaft can be set into rotation, thus moving the conveyor band. A conveyer apparatus of this kind is e.g. described in EP 1 680 348 Al or in US 5 950 797 A.

A disadvantage of this kind of conveyor apparatus is that vibrations due to the so called polygon effect are generated, as e.g. described in EP 2 033 928 Al. Vibrations of that kind arise due to interaction of the chains with the sprockets: A chain comprises several of discrete chain links connected with each other by connection means, such as pins, plates, rollers, etc. The engagement of these connection means with the teeth of the sprocket causes vibration and fluctuation of the chain, which is referred to polygon effect. These vibrations cause undesirable friction between the chain and the sprocket, thereby reducing the service life time of these components. Moreover, the ride experience of a user of the conveyor apparatus can be negatively affected by this polygon effect. On the one hand, a user can feel these vibrations, which can result in an unpleasant sensation. On the other hand, noise is generated by the vibrations, which can be perceived as annoying by users or by people in the vicinity of the conveyor apparatus.

US 2008/0067034 Al describes an escalator and moving walk drive, wherein the possibility to use a cycloidal gear box integrated in a hollow shaft is described. The drive is located in between step or pallet band. An axial gear is mounted on the shaft. A low speed shaft is a hollow shaft connected to the drive wheels and to the low speed housing. With this configuration, only the ring gear housing of the cycloidal drive can be used as output shaft. Using a hollow shaft to connect the chain drive wheels to the ring gear housing further limits the minimum height of the escalator; otherwise there would be a possible collision of the tow roller of the step with the hollow shaft. Besides, the proposed configuration limits the access for maintenance and inspection of the different bearings and power transmission elements; as they are enclosed in the hollow shaft. Many maintenance activities will require disassembling completely the main shaft from the escalator, which is not desirable.

It is an object of the invention to improve a driving system for driving a conveyer band of a conveyer apparatus. It is particularly desirable to provide a possibility to reduce vibrations due to the polygon effect by having a compact and space saving driving system, which advantageously offers an easy access for inspections and maintenance. Disclosure of the invention

The invention relates to a driving system for driving a conveyer band of a conveyer apparatus and a corresponding conveyer apparatus with the features of the independent claims. Further advantages and embodiments of the invention will become apparent from the description and the appended figures.

The conveyer apparatus can especially be an escalator or a moving walkway. In case of an escalator, the conveyer band is particularly a step band. In case of a moving walkway, the conveyer band is especially a pallet band.

A first rotatable shaft is coupled with at least one sprocket. The at least one sprocket is adapted to be coupled with at least one chain of the conveyer band. Particularly, the conveyer band comprises two chains, one on each side of the conveyer apparatus. Hence, the first shaft especially comprises two sprockets, one for each chain. The first shaft is particularly a main shaft or chain wheel drive shaft of the conveyer apparatus. The first shaft can especially be directly connected with the sprockets by means of a rotationally fixed connection.

Each sprocket especially comprises a profiled wheel with a number of teeth for meshing and engaging connection means of the corresponding chain. These connection means connect the corresponding chain links with each other. Thus, the chain and the conveyor band are moved as the sprocket rotates.

If the conveyer apparatus comprises more than one chain and thus more than one sprocket, these sprockets can e.g. also be connected by other means than the first shaft, e.g. by another shaft of by other power transmission elements adapted to keep the motion of the chains synchronised. A motor or electric machine is provided for driving the conveyor band. Electric energy is converted into mechanical energy by the motor. This mechanical energy is used to drive the conveyor band. A second rotatable shaft is coupled with the motor. The motor is adapted to set the second rotatable shaft into a rotary motion. The second rotatable shaft can be coupled directly to the motor. Particularly, the second shaft can be constructed as a motor shaft. It is also possible that the second shaft is coupled to the motor shaft via other elements.

According to the invention, the driving system comprises a gearbox, which is adapted to transfer the rotary motion of the second shaft into a rotary motion of the first shaft. Herein, at least one stage of the gearbox is provided as a cycloidal drive. Hereby, the at least one sprocket is set into rotatory movement and hence the conveyor band is moved.

The invention is based on the realisation that the use of a cycloidal drive in a conveyor apparatus yields distinct advantages. Particularly, efficiency of the drive system can be increased and environmental impact can be reduced. Costs and effort for installation, operation, and maintenance of the conveyor apparatus can be reduced.

By the use of a cycloidal drive vibrations due to the so called polygon effect can be minimised or even prevented. The intensity of the polygon effect particularly depends on the speed of the chain. In conventional drive systems, the speed of the chain can not be controlled precisely enough to reduce vibrations due to the polygon effect. Particularly, the motor does not enable a very accurate control of the chain speed. By means of the cycloidal drive of the gearbox according to the invention, the speed of the chain can expediently be controlled in order to reduce or prevent vibrations due to the polygon effect. Particularly, due to the specific design of the cycloid drive a variable speed pattern of the rotation of the first shaft can be enabled. The cycloid drive is especially specifically designed to enable a specific speed pattern of the first shaft, by means of which a specific speed pattern of the chain, particularly a constant speed chain, can be achieved. Thus, by reducing vibrations due to the polygon effect, the riding experience of a user can be improved and noise pollution can be reduced. Moreover, no undesirable friction between the chain and the sprocket is caused, which can arise due to the polygon effect. Thus, the service life time of these components can be increased and maintenance costs can be reduced.

Moreover, the cycloidal drive has minimal space requirements, especially compared with other kinds of gearboxes. Particularly, by means of the cycloidal drive a relatively high gear ratio can be achieved with minimal space requirements. Thus, dimensions of the conveyor apparatus can be reduced or the saved space can be used for other elements or purposes. Logistics and installation of the conveyor apparatus can hence be simplified.

There is especially no danger of disconnection of the motor and the first shaft. In common drive systems a motor can be connected to a gearbox, which is connected via a chain, e.g. a duplex or triplex chain, to a main shaft, on which sprockets are arranged. In these conventional systems, there is the danger of e.g. breakage of the duplex or triplex chain or loosening of supporting screws of the motor and the gearbox. In this case, the steps or pallets of the corresponding conveyor band may move without any control, possibly resulting in injuries of passengers or damage of transported goods. These dangers can be prevented by means of the cycloidal drive.

Advantageously the cycloidal stage is located either outside the step or pallet band, or parallel to the main shaft and at a lower height if it is inside the pallet band. In other words the cycloidal stage is not mounted on the shaft area in between the chain drive wheels. Particularly, the rotation axis of the cycloidal drive is either coaxial with the first rotatable shaft or located in between the conveyor band. That means that the rotational axis of the cycloidal gear advantageously is not meeting the following two conditions at the same time:

- being coaxial with the first rotatable shaft;

- being located in between the conveyor band.

One advantage of this configuration is that the height of the escalator or moving walkway can be reduced, either when the position of the gearbox is outside of the step or pallet band as the potential conflict with steps is eliminated; or when the position is parallel to the main shaft at a lower height, due to the inclined position of the steps in the return path. Another advantage is that inspection and maintenance access can be easily done by opening the gear box covers. Replacement of components does advantageously not require disassembling the main shaft. A further advantage is that the number of components (bearings, and other transmission elements) is reduced; and so, the complexity of the solution is reduced.

According to a preferred embodiment, a first gear is provided, which is in rotationally fixed connection with the first shaft. A second gear is provided, which is in rotationally fixed connection with an element of the cycloidal drive. The first gear and the second gear are coupled with each other. Thus, these two gears particularly form a gearbox train, which is preferably provided as a second stage of the gearbox. Particularly, the rotary motion of the second shaft is transferred via the cycloidal drive into a rotary motion of the second gear. In this second stage of the gearbox, this rotary motion of the second gear is transferred into a rotary motion of the first gear and hence into the rotary motion of the first shaft.

Particularly the connection between motor and main shaft is made with gears instead of belts, chains, ropes or the like. This makes the connection a more robust and safer connection, which requires less maintenance. With this construction, the cycloid stage is located advantageously outside the main shaft, which allows building an escalator with lower height and makes maintenance easier.

Preferably, the motor is directly connected to the cycloidal stage, particularly without any transmission elements. Such an embodiment advantageously further decreases the complexity of the driving system and therefore also the maintenance effort, because there are no belts, chains, ropes or the like.

Preferably, the cycloidal drive comprises at least one eccentric disc and at least one cycloidal disc. The at least one cycloidal disc has an external surface with a number of lobes. The at least one eccentric disc is preferably set into rotation by the second shaft. The at least one eccentric disc is adapted to set the at least one cycloidal disc in motion, particularly in an eccentric, cycloidal motion. Particularly, the at least one eccentric disc is arranged in the centre of the at least one cycloidal disc. The at least one cycloidal disc and the at least one eccentric disc are especially coupled with each other via a bearing, e.g. a rolling bearing.

The second shaft is advantageously in a rotationally fixed connection with the at least one eccentric disc. Thus, the second shaft and the eccentric disc(s) are preferably connected directly with each other. Alternatively, the second shaft is connected with the at least one eccentric disc preferably via a planetary stage of the gearbox. For this purpose, the second shaft can particularly set a pinion in rotary motion, which engages at least one sprocket of the corresponding planetary gear. This at least one sprocket is in particularly in rotationally fixed connection with the at least one eccentric disc.

According to a further advantageous embodiment the cycloidal drive comprises a first pin element and a second pin element, wherein the first pin element is arranged coaxial to the second shaft and the second pin element is arranged coaxial to the second shaft, wherein the second pin element is fixed and wherein the gearbox is adapted to transfer a rotary motion of the first pin element into the rotary motion of the first shaft.

According to another advantageous embodiment the cycloidal drive comprises a first pin element and a second pin element, wherein the first pin element is arranged coaxial to the second shaft and the second pin element is arranged coaxial to the second shaft, wherein the first pin element is fixed and wherein the gearbox is adapted to transfer a rotary motion of the second pin element into the rotary motion of the first shaft.

Advantageously, the cycloidal drive comprises a first pin element and a second pin element. The first pin element or ring gear element is arranged preferably coaxial to the second shaft and comprises a number of first pins. These first pins are especially arranged on a circumference or circle coaxial to the second shaft. The at least one cycloidal disc is arranged inside this circumference or circle. The number of first pins is preferably larger than the number of lobes of the at least one cycloidal disc. There is especially at least one more first pin than second pins. Particularly, there are at most five more first pins than second pins. Thus, the first pins roll on the external surface of the at least one cycloidal disc. For this purpose, the first pins can be provided as rotating and/or low friction pins.

The second pin element is preferably also arranged coaxially to the second shaft and comprises a number of second pins. The at least one cycloidal disc comprises a number of holes equal to or larger than the number of second pins. The number of holes and second pins can especially be identical. Particularly, there are at most five more holes than second pins. Preferably, the second pins are adapted to engage the holes in the at least one cycloidal disc. Analogously to the first pins, the second pins can be provided as rotating and/or low friction pins. It is also possible, that the second pin element is connected to sprocket shafts of the aforementioned planetary stage of the gearbox. The second pin element can e.g. also be constructed as a shaft. According to a first preferred embodiment, the second pin element is fixed, e.g. to a housing of the motor or of the gear box. The first pin element is in this case preferably pivotable. A corresponding bearing for the first pin element can e.g. be provided in a housing of the gearbox. The rotary motion of the second shaft is thus especially transferred into a rotary motion of the first pin element. The gearbox is in this case preferably adapted to transfer the rotary motion of the second shaft into a rotary motion of the first pin element and to transfer this latter motion into the rotary motion of the first shaft. For this purpose, the first pin element is preferably in rotationally fixed connection with the second gear or the chain sprocket. Thus, rotary motion of the first pin element is transferred into rotary motion of the second gear or of the chain sprocket.

Alternatively, according to a second preferred embodiment, the first pin element is fixed and the second pin element is pivotable. For example, the first pin element can in this case be fixed to the conveyor apparatus, e.g. to the housing of the motor or of the gear box. A corresponding bearing for the second pin element can be provided in the gearbox housing. The gearbox is in this case preferably adapted to transfer the rotary motion of the second shaft into a rotary motion of the second pin element and to transfer this latter motion into the rotary motion of the first shaft. The second pin element is in this case advantageously in rotationally fixed connection with the second gear or the chain sprocket. Thus, in this case, the rotary motion of the second pin element is transferred into rotary motion of the second gear or the chain sprocket.

According to an advantageous embodiment, the number of first pins is equal to a number of teeth of the at least one sprocket or equal to an integer multiple of this number of teeth. The number of lobes is preferably equal to the number of first pins minus a ratio between the number of first pins and the number of teeth of the at least one sprocket. The shape of the external surface of the at least one cycloidal disc is thus specifically modified to achieve a specific speed pattern of the first shaft in order to achieve a constant speed of the conveyor band and thus to minimise or even prevent vibrations due to the polygon effect. This configuration is especially advantageous if a gear ratio of the first and the second gear is 1: 1 or if a first and a second gear are provided. Moreover, this configuration is particularly advantageous for sprockets with less than 16 teeth. For example, if the number of teeth is 10 and the number of first pins is 10, the number of lobes will especially be 9. If, for instance, the sprockets have 10 teeth and if there are 20 first pins, the cycloidal disc(s) will especially have 18 lobes.

Preferably, the number of first pins is equal to a number of teeth of the at least one sprocket multiplied by a factor y or equal to an integer multiple of the number of teeth of the at least one sprocket multiplied by the factor y. This factor y preferably corresponds to a gear ratio of y: l of the number of teeth of the second gear and the number of teeth of the first gear. The number of lobes is preferably equal to the number of first pins minus a ratio between the number of first pins and the number of teeth of the at least one sprocket multiplied by the factor y. This configuration is also particularly advantageous for sprockets with less than 16 teeth. Also by this specific shape of the external surface of the cycloidal disc(s) a specific speed pattern of the first shaft and a constant speed of the conveyor band can especially be achieved in order to minimise or prevent vibrations due to the polygon effect.

According to a preferred embodiment, the number first pins z ₁ is given according to the formula, if z ₁ is an integer number: r is the difference of the number first pins zi and the number of lobes z ₂ :

r = _Zl - z ₂

- ti is the number of teeth of the at least one sprocket.

ii is the gear ratio of the number of teeth of the second gear and the number of teeth of the first gear. This configuration also yields the possibility to minimise or prevent vibrations due to the polygon effect.

Preferably, the second rotatable shaft is coupled to a shaft of the motor via a second gearbox, e.g. via a gear train with one gear connected with the motor shaft and one gear connected with the second shaft. This configuration particularly allows higher motor speeds.

The motor can be of an expedient design. According to a particularly advantageous embodiment, the motor is a permanent magnet synchronous motor (PMSM). This motor type presents advantages in torque density and efficiency.

Preferably, the motor is a PMSM with an axial flux or with radial flux with a diameter larger than the length (so called "pancake" type PMSM). In an axial flux motor of this kind, the magnetic force (through the air gap) is along the same plane as the motor shaft, i.e. along the length of the motor. The motor shaft or an output shaft coupled with the motor shaft is particularly arranged parallel with the first shaft of the conveyor apparatus. The motor can preferably be a PMSM with radial flux or with an axial flux with several discs (so called "sausage" type PMSM). In a radial flux motor of this kind, the magnetic force is perpendicular to the length of the motor or motor shaft. This PMSM with radial flux particularly has a longer, skinnier design than the "pancake" type PMSM.

It is possible to arrange the motor and/or the gearbox in between the two chains of the conveyor band. This design can be appropriate for escalators. The motor and/or the gearbox can also be arranged outside of the area between these two chains and especially outside a truss of the conveyor apparatus. This design can be advantageous for moving walkways. It is also possible to e.g. arrange the motor in between the two chains and the gearbox on the outside of the truss. It shall be understood that the driving system may comprise other elements, e.g. a brake and/or a handrail drive. For example a brake can be provided and can interact e.g. with the motor, the first shaft, the second shaft and/or other elements. The brake can have a holding function in order to stop a motion of the conveyor band. Moreover, the brake can have an emergency braking function.

A handrail drive can be provided to set one or several handrails of the conveyor apparatus in motion. The handrail drive can e.g. also be driven by the motor and can be coupled to the motor by means of power transmission, e.g. belts or chains. The handrail drive can also be driven by means of a mechanical connection with the at least one chain of the conveyor apparatus. It is also possible that a second motor for driving the handrails is provided, which is especially synchronised with the motor of the driving system.

Moreover, the conveyor apparatus especially comprises one or several of the following elements: a guiding system for the conveyor band and/or the chains; a supporting structure, e.g. a truss; plates provided to transfer passengers from the conveyor band to the surrounding area and vice versa; balustrades provided on both sides of the conveyor apparatus; handrails provided on both sides of the conveyor apparatus moving substantially at the same speed of conveyor band; control and/or safety systems.

It should be noted that the previously mentioned features and the features to be further described in the following are usable not only in the respectively indicated combination, but also in further combinations or taken alone, without departing from the scope of the present invention.

The present invention will now be described further, by way of example, with reference to the accompanying drawings, in which , lb schematically show a conveyor apparatus with a preferred embodiment of a driving system according to the invention in perspective views. schematically shows a preferred embodiment of a driving system according to the invention in a perspective view. schematically shows a preferred embodiment of a driving system according to the invention in a side view. schematically shows a preferred embodiment of a driving system according to the invention in a top view. schematically shows a preferred embodiment of a driving system according to the invention in sectional top view. schematically shows a gearbox of a preferred embodiment of a driving system according to the invention in a sectional side view. schematically shows a rotation speed pattern of a main shaft of a preferred embodiment of a driving system according to the invention. schematically shows a part of a cycloidal drive of a preferred embodiment of a driving system according to the invention in a side view. schematically shows a preferred embodiment of a driving system according to the invention in a top view Figure 10 schematically shows a preferred embodiment of a driving system according to the invention in a top view.

Figure 11 schematically shows a gearbox of a preferred embodiment of a driving system according to the invention in a sectional side view.

Figure 12 schematically shows a preferred embodiment of a driving system according to the invention in a perspective view.

Figure 13 schematically shows a preferred embodiment of a driving system according to the invention in a sectional top view.

Figure 14 schematically shows a section of a conveyor apparatus with a preferred embodiment of a driving system according to the invention in a perspective view.

Figure 15 schematically shows a section of a conveyor apparatus with a preferred embodiment of a driving system according to the invention.

Figure 16 schematically shows a gearbox of a preferred embodiment of a driving system according to the invention in a sectional side view.

Figure 17 schematically shows a preferred embodiment of a driving system according to the invention in sectional top view.

Detailed description

Identical reference signs in the figures refer to identical or identically constructed elements. Figures la, lb schematically show a preferred embodiment of a conveyor apparatus 100 according to the invention. In this example, the conveyor apparatus 100 is an escalator. Figure la schematically shows the escalator 100 in a perspective view, which is provided between a first, lower floor 101 and a second, higher floor 102. The escalator 100 comprises a conveyor band 10, which is provided as a step band comprising a plurality of steps 1. Furthermore, the escalator 100 comprises two handrails 103, one handrail on each side of the conveyor band 10.

An upper head 104 of the escalator 100 is shown in Figure lb in a perspective view.

A preferred embodiment of a driving system 110 according to the invention for driving the conveyer band 10 of the conveyer apparatus 100 is provided in the upper head 104. This preferred embodiment of the driving system 110 is also schematically shown in Figure 2 in a perspective view, in Figure 3 in a side view, and in Figure 4 in a top view. Steps 1 of this step band 10 are connected to two chains 2 provided on both sides of the step band 10. For reasons of clarity, only one step 1 of the step band 10 is shown in Figure lb. Moreover two guides 3 are provided on both sides of the step band 10. The chains 2 run over theses guides 3. Two sprockets 402 with a number of teeth are provided on both sides of the step band 10. The sprockets 201 are in rotationally fixed connection with a first shaft 401 of main shaft of the escalator 100. The chains 2 are moved by the sprockets 402, which engage with chain rollers 201.

A motor 5 and a brake 7 are provided and are coupled with one of the sprockets 402 via a gearbox 6. This way, mechanical energy produced by the motor 5 can be used to drive the step band 10. A truss 11 is provided to support the elements of the conveyor apparatus 100. According to the invention, at least one stage of the gearbox 6 is provided as a cycloidal drive, as will be explained later on in detail.

As can be seen in the figures, the motor 5 and the brake 7 can be located between the chains 2 of the step band 10, such that space requirements in the upper head of the escalator 100 and thus the total length of the escalator 100 can be reduced. This length reduction especially reduces the logistic and installation requirements and particularly increases the rigidity of the escalator 100. However, it is also possible to arrange the motor 5 and/or the brake 7 at different locations of the escalator 100. For instance, the brake 7 could be connected to the first shaft 401 or to one of the sprockets 402.

The motor 5 is for example a permanent magnet synchronous motor with radial flux. This motor type presents advantages in torque density and efficiency. The brake 7 is in this example connected to a motor shaft of the motor 5. Particularly, the conveyor apparatus 100 can be stopped with by means of an electronic brake or of the motor 5 itself. The brake 7 is adapted to hold the conveyor apparatus 100 once it has stopped. The brake 7 can also have the function of an auxiliary brake. The brake 7 could also be used as service brake. It is also possible to locate the brake 7 in other elements of the driving system 110, for instance, in the main shaft 401.

In Figure 5, a sectional top view of a preferred embodiment of a driving system according to the invention is schematically shown. Particularly, Figure 5 shows a sectional view of the driving system 110 of Figure 3 along the line A- A.

Figure 6 schematically shows a sectional side view of a preferred embodiment of a driving system according to the invention. Particularly, a sectional side view of the driving system 110 of Figure 4 along the line C-C is shown in Figure 6. As can be seen in Figure 5 and Figure 6, the gearbox 6 has at least one gear train 601, 602 with a gear ratio A first gear 601 is coupled to one of the sprockets 402. For this purpose, the first gear 601 is particularly in rotationally fixed connection with the first shaft 401. A second gear 602 is supported by bearings 620 to a gearbox frame 650. The first shaft 401 is e.g. also supported by bearings 622 in the gearbox frame 650.

One stage of the gearbox 6 is provided as a cycloidal drive 610. The gearbox 6 is adapted to transfer a rotary motion of a second shaft 614 into a rotary motion of the first shaft 401, thus driving the conveyor band 10. The second shaft 614 is supported by bearings 621 in the gearbox frame 650.

This second shaft 614 is an input shaft of the cycloidal drive 610. The second shaft is moreover coupled with the motor 5 and the motor 5 is adapted to set the second shaft 614 into rotary motion. As can be seen in Figure 5, the second shaft 614 can for example be in rotationally fixed connection with a motor shaft of the motor 5.

This cycloidal drive 610 comprises at least one eccentric disc 613 (e.g. two eccentric discs 613), which are in rotationally fixed connection with the second shaft 614.

At least one cycloidal disc 612 (e.g. two cycloidal discs 612) are provided, which can be moved and set in an eccentric cycloidal motion by the eccentric discs 613. An external surface 612a of each cycloid disc 612 comprises a number z ₂ of lobes. In this example, nine lobes are provided.

A first pin element (or ring gear element or ring gear housing) comprises a first number z ₁ of first pins 611. In this example, ten first pins are provided. This number z ₁ of first pins 611 (i.e. ten) is larger than the number z ₂ of lobes (i.e. nine) of each cycloidal disc 612. The first pin element is arranged coaxial to the second shaft 614. In the example of Figures 5 and 6, the second gear 602 also acts as this first pin element. Thus, the first pins 611 are arranged on the second gear 602, particularly on a circumference or circle coaxial to the second shaft 614. The cycloidal discs 612 are arranged inside this circumference or circle. Thus, the first pins 611 roll on the external surface 612a of the cycloidal discs 612.

A second pin element comprises a number of second pins 615. Particularly, six second pins are provided in this example. These second pins 615 and the second pin element are arranged coaxial to the second shaft 614. Each cycloidal disc 612 comprises a number of holes 612b equal to or larger than the number of second pins 615. As shown in Figure 6, six holes are provided. Thus, the number of second pins 615 and the number of holes 612b are identical in this example. The second pins 615 are adapted to engage the holes 612b in the cycloidal discs 612. The second pins 615 can roll over the surface of the holes 612b of the cycloid discs 612.

In the example of Figures 5 and 6, the second pins 615 are connected to the gearbox frame 650. Thus, the gearbox frame 650 acts as the second pin element in this example. The second pins 615 are thus fixed in this example and hence also the second pin element is fixed in this embodiment. The first pin element, i.e. the second gear 602, is pivotable in this embodiment. It is also possible, that the first pin element is fixed and that the second pin element is pivotable, as will be explained later on in reference to Figures 12 and 13. One of the advantages of the cycloidal drive 610 is that it allows a relatively high gear ratio with comparatively small space requirements. The gear ratio i ₂ of the cycloidal drive 610 is especially given by the following formula: Another distinct advantage of using the cycloidal drive is that it can be specifically designed to reduce or prevent vibrations due to the polygonal effect. For his purpose, the first shaft 401 is especially set into a rotary movement following a predetermined speed pattern. Such a rotation speed pattern 700 of a main shaft of a conveyor apparatus is schematically shown in Figure 7.

Particularly, Figure 7 shows an exemplary rotation speed pattern 700 of the first shaft 401 of the escalator 100 of the Figures 1 to 6, wherein the main sprocket 402 has e.g. 10 teeth. By this speed pattern, a constant speed of the chains 2 can be achieved. This rotation pattern can also be modified, to achieve a predetermined level of vibrations below a reference level without affecting the present invention.

The external part 612a of the cycloid discs 612 can specifically be designed to either achieve a constant gear ratio i ₂ or to achieve a variable gear ratio, as will now be explained with reference to Figures 8.

Figure 8a shows a part of the cycloidal drive 610 of the driving system 110 according to Figures 1 to 6. An enlarged view of the section referred to as "B", which is a part of the external surface 612a of the cycloid discs 612, is schematically shown in Figure 8b. Particularly, Figure 8b shows a comparison of two different external surfaces 612al and 612a2.

The external surface 612al follows a hypocycloid curve in order to achieve a constant gear ratio i ₂ of the cycloidal drive 610. By means of the modified profile 612a2, a predetermined variable gear ratio can be achieved. In this way, vibrations produced by the polygonal effect associated to the chain transmission can be reduced or eliminated. As can be seen in Figure 8, the necessary variations between the different surface profiles 612al and 612a2 are comparatively small.

The optimum profile depends on parameters of the conveyor apparatus, like the number of teeth in the step chain sprocket. In this way, the vibrations produced by the polygonal effect associated to the step chain transmission can be reduced or eliminated.

The modified profile 612a2 can e.g. be developed, if provided that z ₁ is an integer number. r is the difference of the number first pins zi and the number of lobes z ₂ :

r = z _l - z ₂

ti is the number of teeth of the at least one sprocket and i _t is the gear ratio of the number of teeth of the second gear and the number of teeth of the first gear.

In the configurations in which such gear train does not exist, then the modified profile 612a2 can also be developed if z _l = r * t _l . Alternative configurations could also be achieved by modifying the inner surfaces 612b and/or the external surfaces 612a of the cycloid discs 612.

Figures 9 to 17 schematically show other preferred embodiments of the driving system according to the invention.

In Figure 9 a preferred embodiment 110' of the driving system according to the invention is schematically shown in a sectional view, wherein the first shaft 614 is not directly connected to the motor shaft, but via another gear, e.g. a gear train 661, 662.

One gear 661 of this gear train is connected with the first shaft 614 of the cycloidal drive 610 and the other gear 662 of this gear train is connected to a shaft of the motor 5 and the brake 7. This configuration especially allows a higher motor 5 speed. Another preferred embodiment 110" of the driving system according to the invention is schematically shown in Figures 10 and 11, according to which the gearbox 6" comprises another stage provided as a planetary stage 663, 664. Figure 10 shows the driving system 110" with this embodiment of a gearbox 6" in a sectional top view. Figure 11 shows this gearbox 6" in a sectional side view.

The eccentric discs 613 and the cycloidal discs 612 are coupled via this planetary stage 663, 664. The cycloidal discs 612 are moved by eccentric discs 613, which are connected to a number of eccentric shafts 616, which are supported by bearings 623 in the gearbox frame 650. External gears 663 of the planetary stage move the eccentric shafts 616. An internal gear 664 of the planetary stage is connected to the motor 5 and the brake 7.

In this example, three shafts with the planetary gears 663 are moving the cycloid discs 612 using the eccentric discs 613, which are in this example not connected to the second shaft 614. The pins 615 can e.g. just be fixed if there is enough clearance in the cycloid discs 612 and contribute to the rigidity of the gear box frame 650 or can also be rotating or low speed pins 615. As aforementioned it is also possible that the first pin element is fixed and that the second and that the second pin element is pivotable. A corresponding preferred embodiment 110"' of the driving system according to the invention is schematically shown in Figures 12 in a perspective view and in Figure 13 in a sectional top view.

In this embodiment 110"', the gear train 601, 602 of the gearbox is arranged in between the sprockets 402 and the chains 2. Analogously to the Figures 1 to 6, the first gear 601 is in rotationally fixed connection with the first shaft 401 and the second gear 602 is supported by bearings 620 in the gearbox frame 650. The gear box frame 650 has in this example one support point in the first shaft 401, using adequate bearings 624. The second gear 602 is in this embodiment provided as the second pin element comprising the second pins 615. In this example, the zi first pins 611 are fixed to the gearbox frame 650. The gearbox frame 650 acts as the first pin element in this example.

Analogously to Figures 1 to 6, the second shaft 614 is also connected with eccentric discs 613, which move the cycloidal disc 612 and set them into an eccentric, cycloidal motion. The number z ₂ of lobes in the outer surface 612a of the cycloidal disc 612 is smaller than the number z ₁ of first pins 611. The first pins 611 roll over the outer surfaces 612a of the cycloid discs 612. The pins 615 of the low speed shaft 618 roll over the holes 612b in the cycloidal discs 612.

With this configuration, the gear ratio i ₂ of the second shaft 614 to the low speed shaft 618 is given as:

^• _ ^Z 2 ^{~ Z} l

^Z 2

As explained before, the cycloid discs in all the above described preferred embodiments of the driving system according to the invention can have modified external curves 612a to specifically reduce or eliminate vibrations due to the polygonal effect.

Another preferred embodiment 110"" of the driving system according to the invention is schematically shown in Figure 14 in perspective views, wherein the motor 5 is arranged outside the conveyor band or outside the area in between the chains 2. Figure 14a schematically shows in a perspective view an upper head of a preferred embodiment of a conveyor apparatus 100"" according to the invention, which is in this example embodied as a moving walkway. A conveyor band 10"" of the moving walkway 100"" is provided as pallet band. The corresponding embodiment of the driving system 110"" without the pallet band 10"" is shown schematically in Figure 14b. In order to reduce the number of gears, a double cardan shaft 8 can be used to connect the motor 5 and the gear box 6.

It is also possible to locate the motor and the brake on one side of the first shaft. In such cases, the motor can especially be a "pancake" type motor; either a permanent magnet synchronous motors with axial flux or a permanent magnet synchronous motor with radial flux and a diameter larger than the motor width. An example of a preferred embodiment of a corresponding driving system 110* is schematically shown in the Figures 15 to 17.

Figure 15a schematically shows an upper head of a conveyor apparatus 100*, which is embodied as an escalator. The corresponding driving system 110* is shown in Figure 15b in a perspective view and in Figure 15c in a top view. Figure 16 shows a sectional view of the driving system 110* of Figure 15 along the line E- E and Figure 17 shows a corresponding sectional view along the line D-D.

The motor 5* is in this example provided as an axial flux motor with a corresponding brake 7*. The cycloid stage of the corresponding gearbox 6* is located in the middle of the motor 5*. A stator housing 510 supports coils 511 and a rotor 520 supports magnets 521. A corresponding second shaft 614* of the cycloid stage is in this case fixed to the rotor 520 and rotates with it. This shaft 614* moves the corresponding cycloid discs 612* through adequate eccentric discs 613* attached to it. The stator housing 510 holds the corresponding number of first pins 611*, which roll over the external cycloid profile 612a* of the cycloid discs 612*.

Corresponding second pins 615* engage holes 612b* in the cycloid discs 612*. The second pins 615* can for example be connected to the sprocket 402*. One of the sprocket 402* can be supported by the motor housing 510 by means of an adequate cross roller bearing 625*. The other one of the sprockets 402* can be supported by the escalator truss 11 by another adequate bearing 622*. The first shaft is in this example provided as a double cardan shaft 403. Both sprockets 402* are connected by means of this double cardan shaft 403.

It is also possible to connect the first pins 611* to the sprocket 402* and the second pins 615* to the stator housing 510. It is e.g. also possible to modify the external shape of the cycloid discs and to use a conjugate surface instead of the first pins.

Reference list

100 conveyor apparatus, escalator

101 first floor

102 second floor

103 handrail

104 upper head of the conveyor apparatus 100

100"" conveyor apparatus, moving walkway 100* conveyor apparatus, escalator

110 driving system

110' driving system

110" driving system

110"' driving system

110"" driving system

110* driving system

1 Steps of the conveyor band 10

2 chains

3 guides

5 motor

5* motor

6 gearbox

6" gearbox

6* gearbox

7 brake

7* brake

8 cardan shaft

10 conveyor band, step band conveyor band, pallet band

truss

201 chain rollers

401 first shaft

402 sprockets

402* sprockets

403 first shaft, double cardan shaft

510 stator housin;

511 coils

520 rotor

521 magnets

601 first gear 601

602 second gear

610 cycloidal drive; cycloidal stage of the gearbox 6

611 first pins

612 cycloidal disc(s)

612a external surface of the cycloid disc(s) 612

612b holes in the cycloidal disc(s)

612al hypocycloid curve

612a2 modified curve

613 eccentric disc(s)

614 second shaft

615 second pins

616 eccentric shaft

618 low speed shaft

620 bearings of the second gear 602

621 bearings of the second shaft 614

622 bearings of the first shaft 401 623 bearings of the eccentric shafts

624 bearing

650 gearbox frame

661 gear of gear train

662 gear of a gear train

663 external gears of a planetary stage of the gearbox 6

664 internal gear of a planetary stage of the gearbox 6

665 bearings of the motor shaft 611* first pins

612* cycloid discs

612a* external surface of the eccentric discs 612* 612b* holes in the cycloid discs 612*

613* eccentric discs

614* second shaft

615* second pins

622* bearing

625* bearing 700 rotation speed pattern