EP3074335A1 - Mécanisme d'entraînement de main courante pour un escalier mécanique ou un trottoir roulant - Google Patents

Mécanisme d'entraînement de main courante pour un escalier mécanique ou un trottoir roulant

Info

Publication number
EP3074335A1
EP3074335A1 EP14799744.9A EP14799744A EP3074335A1 EP 3074335 A1 EP3074335 A1 EP 3074335A1 EP 14799744 A EP14799744 A EP 14799744A EP 3074335 A1 EP3074335 A1 EP 3074335A1
Authority
EP
European Patent Office
Prior art keywords
drive
counter
handrail
pressure
tension spring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP14799744.9A
Other languages
German (de)
English (en)
Other versions
EP3074335B1 (fr
Inventor
Csaba BOROS
Michael Matheisl
Wolfgang Neszmerak
Robert Schulz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Inventio AG
Original Assignee
Inventio AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Inventio AG filed Critical Inventio AG
Priority to EP14799744.9A priority Critical patent/EP3074335B1/fr
Publication of EP3074335A1 publication Critical patent/EP3074335A1/fr
Application granted granted Critical
Publication of EP3074335B1 publication Critical patent/EP3074335B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B23/00—Component parts of escalators or moving walkways
    • B66B23/02—Driving gear
    • B66B23/04—Driving gear for handrails
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B23/00—Component parts of escalators or moving walkways
    • B66B23/16—Means allowing tensioning of the endless member
    • B66B23/20—Means allowing tensioning of the endless member for handrails
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B23/00—Component parts of escalators or moving walkways
    • B66B23/22—Balustrades
    • B66B23/24—Handrails

Definitions

  • the invention relates to a conveyor system which is designed as an escalator or moving walk and a handrail drive for such a conveyor system.
  • a handrail drive for an escalator is known.
  • the known handrail drive has a drive device and a pressure device. Between the drive device and the printing device, a handrail is guided, wherein the top of the handrail pressure rollers facing the printing unit.
  • the upper side is that side of the handrail on which the users of the escalator lay their hand to hold on to the handrail. Furthermore, the
  • Drive means rollers which are assigned to a part of the pressure rollers, wherein between the rollers of the drive means and the handrail a drive belt runs.
  • the drive belt is also passed around a drive wheel and a tensioning wheel to tension the drive belt.
  • the pressure rollers press the handrail against the driven drive belt, the drive belt from the rollers of the
  • the pressure force with which the pressure rollers act on the handrail is applied by a spring of the pressure device.
  • the handrail drive known from EP 0 644 149 A1 has the disadvantage that it results in a large structural height, because the pressure rollers are initially mounted in an arrangement further away from the upper side of the handrail. This arrangement is acted upon by the spring of the printing device, which is further away from the top of the handrail. Since such handrail drives are usually in
  • Balustrade plinth are arranged, they must because of their height of the side of the
  • Step band can be arranged. This inevitably leads to a broader
  • Escalator structure the operator of an escalator or moving walk at a given installation width due to the building dimensions as broad as possible step band or pallet band to achieve the highest possible capacity of the conveyor and to increase ride comfort for the user.
  • the handrail drive arranged on the side of the step belt can also lead on site to deeper pits, so that the handrail drive, in particular the spring of the
  • Handrail drive has enough space.
  • the object of the invention is to provide a handrail drive for driving a handrail of a conveyor system, the predetermined width of the
  • Transport system allows the use of the widest possible step band or pallet band is optimized in terms of its height.
  • the handrail drive for driving a handrail of a conveyor system has at least one drive device and at least one counterpressure device, wherein the counterbinching device includes at least one tension spring and at least one counterpressure roller.
  • the handrail is guided between the drive device and the at least one counter-pressure roller approximately in a linear direction and is acted upon by the at least one counter-pressure roller against the drive means with a pressure force caused by the tension spring.
  • the optimized overall height is achieved in that the tension spring is arranged approximately parallel to the running direction, that the at least one counter-pressure roller is at least partially disposed in an extension of the tension spring and that the
  • Handrail drive has a mechanical deflection, by means of the
  • the drive device has at least one driven one
  • the drive belt and the at least one counter-pressure roller are arranged to each other that the handrail between the drive belt and the at least one counter-pressure roller is feasible and of the at least one
  • the handrail of the conveyor system is not part of the handrail drive.
  • the handrail drive can also be manufactured and distributed independently of a handrail suitable for this purpose.
  • the handrail drive can also be suitable for differently configured handrails or optionally also be adaptable in the sense of a modular design for different applications, in particular different types of handrails.
  • transport systems that are designed as an escalator or moving walk.
  • a preferred use of the handrail drive is for moving walks, which are designed flat construction. This can be realized by the inventive design a moving walkway, which sits flat on the ground. The floor of a building, a covered feeder area or the like can then be designed just. This is to be understood that the floor does not need to be opened for installation of the conveyor system, since the handrail drive can be completely housed in the balustrade base.
  • a low-profile handrail drive is also for a modernization of a
  • a new balustrade can be arranged with a hand running on the existing escalator or the existing moving walk in the simplest way without making extensive changes to existing components of the conveyance plant, for example, on the truss, on the rails or on the rail blocks.
  • the ease of maintenance is improved, since the handrail drive according to the invention is very compact and can be mounted on the framework, instead of extending to the side of the framework.
  • the drive device may comprise at least one drive wheel, at least one tensioning wheel and a plurality of contact pressure rollers.
  • the drive belt is driven by the drive wheel and is arranged circumferentially between this and the tensioning wheel.
  • the Anpressdruckroi len are disposed within the drive belt loop and support the drive belt against the handrail.
  • Counter-pressure device has a plurality of counter-pressure rollers.
  • the counter-pressure rollers of the counter-pressure device on the one hand and the drive wheel, the tensioning wheel and the
  • the tensioning wheel is opposite to one of the counter-pressure rollers and that each of the contact pressure rollers is opposite to one of the counter-pressure rollers.
  • the driving force can be transmitted particularly advantageous to the handrail.
  • a slippage of the handrail is reliably avoided in this way.
  • the handrail can be guided in this way, at least largely without significant bending between the drive belt and the counter-pressure rollers in the direction.
  • not all rollers or wheels of the drive device is associated with one of the counter-pressure rollers.
  • the drive wheel and / or the tensioning wheel and / or one or more of the contact pressure rollers remain or remain without a directly associated counterpressure roller.
  • the drive wheel and the tensioning wheel can remain without a counter-pressure roller, wherein each of the Anpressdruckroi len of the pressing device is assigned to one of the counter-pressure rollers of the counter-pressure device.
  • Extension of the tension spring are arranged. This can be for the
  • Counter-pressure rollers anyway required height optimized and used in an advantageous manner to accommodate the tension spring.
  • the counter-pressure device has a bearing body on which the counter-pressure roller is mounted or the counter-pressure rollers are mounted.
  • a guide is provided which is at least indirectly connected to the drive device and that the bearing body is guided by means of the guide at least one point relative to the drive means at least approximately perpendicular to the direction. In this way, the position of the bearing body and thus each of the positions of the counter-pressure rollers in the running direction relative to the drive means, in particular the drive wheel and / or the tensioning wheel and / or the at least one contact pressure roller can be maintained, while in principle a movement play or a mobility
  • Counter-pressure rollers then, for example, so that when performing the handrail a necessary movement play can be achieved. This may optionally also provided on the handrail unevenness or adhering to the handrail
  • the guide is rigidly connected to a tension spring bearing, on which the tension spring is supported, and that the spring force of the tension spring acts on the bearing body via the deflection device.
  • At least one first axis is fixedly provided on the bearing body, that the order directing device has at least a first axle guide, in which the first axis is guided, and that the axle guide the first axis with a predetermined deflection angle with respect to the Direction of action of the spring force of the tension spring leads.
  • predetermined deflection angle defines that, irrespective of the position of the axle within the axle guide, there is always a gradient in the axle guide which converts the spring force into the pressure force.
  • a first axis and at least one second axis are provided fixedly on the bearing body, that the deflection device has a first axis guide, in which the first axis is guided, and at least one second axis guide, in which guided the second axis , that the first axis guide guides the first axis with a predetermined deflection angle with respect to the direction of the spring force of the tension spring, and that the second axis guide guides the second axis with the (same) predetermined deflection angle with respect to the direction of the spring force of the tension spring , In this way, the spring force of the tension spring is deflected in their direction.
  • the magnitude implementation of the spring force of the tension spring results in ideal implementation, are neglected in the friction forces and the like, from the determined by the deflection angle parallelogram of forces.
  • the spring force of the tension spring can be translated depending on the deflection angle.
  • the deflection angle does not necessarily have to be constant over the length of the axle guide.
  • a progressive or degressive gear ratio between spring force and pressure force can be achieved.
  • Vibration damping can be used. This friction can also be influenced by the choice of a corresponding deflection angle.
  • Counter-pressure device can be created in that the deflection device has at least one Gleitmentsschuh that the counter-pressure device has a sliding track and that the tension spring bearing on which the tension spring is supported, is arranged stationary to the slide. Further, the friction between the at least one Gleit Resultssschuh and the slide can also be used to dampen the vibration system present by the tension spring.
  • the deflection angle which is provided in the axle guide or the axle guides, is preferably selected from a range of 10 ° to 45 °. Further, it is advantageous that the deflection angle is selected from a range of 10 ° to 30 °. It is also advantageous that the deflection angle from a range of 15 ° to 25 ° and
  • a counter-pressure roller is mounted on the first axis.
  • the counter-pressure roller, which is mounted on the first axis, is preferably the closest to the tension spring arranged counter-pressure roller. This embodiment also contributes to a compact construction of the handrail drive.
  • one of the counter-pressure rollers is mounted on the second axis. In the case of several counter-pressure rollers this means that one of the counter-pressure rollers is mounted on the second axle. If a plurality of counter-pressure rollers are provided, then it is advantageous that one of the counter-pressure rollers is mounted on the first axis and that one of the counter-pressure rollers is mounted on the second axis. In the case of several axes, which also includes the case of two axes, it is advantageous that in each case one of the counter-pressure rollers is mounted on each of the axes or at least on a part of the axes. This allows a space-saving design.
  • the counter-pressure roller which is mounted on the second axis, which is furthest away from the tension spring counter-pressure roller. If further axes, that is, more than two axes, are provided, then further counter-pressure rollers can be arranged in an advantageous manner between the first axis and the second axis.
  • a second axis is provided fixedly on the bearing body, that the deflection device has a second axle guide, in which the second axis is guided and that the second axle guide the second axis with the
  • Counter-pressure rollers may also be arranged on axles which are not guided in this way in the deflection device.
  • the Befrd ceremoniessstrom may have one or more handrail drives.
  • the individual handrail drive has due to the Umlcnk adopted on the direction of travel dependent pressing force.
  • Umlcnk adopted on the direction of travel dependent pressing force.
  • a suitable orientation for example, a higher pressure force can be achieved for the upward travel, while a lower pressure force is achieved for the downward movement. This allows the handrail in the
  • the handrail drive can also have two counter-pressure devices, which are arranged mirror-symmetrically to a mirror plane. These two counter-pressure devices are only half as long as the drive device, so that one half of the required counter-pressure rollers of the first counter-pressure device are assigned and the other half of the required counter-pressure rollers of the second counter-pressure device are assigned.
  • the mirror plane extends orthogonal to the direction of travel of the handrail and is positioned approximately centrally of the drive means.
  • the conveyor system can of course also have several handrail drives.
  • two handrail drives can be used, which are oriented against each other. If the same pressure force is required in both directions, then the two handrail drives can be arranged mirror-symmetrically to each other.
  • Each handrail drive here has its own tension spring. In a modified embodiment can also be targeted in this way
  • Handrail drive according to the invention is replaced with a deflection device.
  • Figure 2 in a schematic representation of a moving walkway with a supporting structure and two
  • Figure 3 the handrail drive shown in Figures 1 and 2 and a section of the handrail in a sectional view;
  • Figure 4 is a side view of the handrail drive shown in Figure 3;
  • Figure 5 a counter-pressure device of the handrail drive shown in Figure 3 in a schematic, spatial representation according to the embodiment of the invention
  • Figure 6 schematically in side view of a handrail drive with two
  • Counterpressure devices which are arranged mirror-symmetrically to each other.
  • FIG. 1 shows schematically in side view a Be portionsan leash 100, which is designed as escalator 100 and connects a first floor E l with a second floor E2.
  • the escalator 100 has a supporting structure 106 or a framework 106 with two deflection regions 107, 108, between which a step belt 105 is guided circumferentially with a plurality of steps 104.
  • a handrail 3 is arranged circumferentially on a balustrade 102.
  • the balustrade 102 is at the lower end by means of a
  • Balustradensockels 109 connected to the structure 106 or truss 106.
  • the advance of the handrail 3 runs along the upper edge of the balustrade 102 and the return of the handrail 3 takes place in the interior of the balustrade pedestal 109.
  • a handrail drive 2 is arranged in the interior of the balustrade pedestal 109.
  • the handrail drive 2 is fixed due to its low height to a top flange of the structure 106.
  • Escalator 100 two balustrades 109, each with a handrail 3, wherein the step band 105 is disposed between the two balustrades 102. Accordingly, two handrail drives 2 are required to drive the two rotating handrails 3.
  • Figure 2 shows schematically in side view as a moving walkway 1 10 designed conveyor system 1 10, which also has a balustrade 1 12 with balustrade 1 19, a handrail 3, a supporting structure 116, and two deflection regions 1 17, 1 18 ,
  • a moving walk 110 connects for example a third floor E3 with a fourth floor E4.
  • the hand-barrel 3 and the handrail drive 2 of the moving walk 1 10 correspond to the
  • Fig. 3 shows the handrail drive 2 of Figures 1 and 2 and a portion of the handrail 3 in a partial, schematic sectional view according to an embodiment of the invention.
  • the handrail drive 2 can be manufactured and distributed independently of the other components of the conveyor system.
  • the handrail drive 2 according to the invention is preferably used in transport systems or transport facilities, which are designed as escalator 100 or moving walkway 1 10.
  • the hand-operated drive 2 has a drive device 4 and a counter-pressure device 5.
  • the Handiaufantrieb 2 for example, also have a further counter-pressure device 5, which corresponds to the
  • Counter-pressure device 5 is configured. Furthermore, the conveyor system 100, 1 10 may also have a plurality of handrail drives 2, for example, to drive a plurality of handrails 3. In particular, viewed in the running direction left and right of the floor space for persons and / or objects of the conveyor system 100, 1 10 provided handrails 3 can be driven.
  • the drive device 4 has a drive wheel 6, a tensioning wheel 7 and a
  • the drive belt 8 is guided around the drive wheel 6 and the tensioning wheel 7.
  • the drive wheel 6 and the tensioning wheel 7 on their running surfaces 9, 10 each have a ring gear.
  • the drive belt 8 is designed as a toothed belt 8.
  • a poly-V belt could be used as a drive belt 8.
  • the tensioning wheel 7 is controlled by an adjustable clamping device 15, the one
  • Belt tension spring 16 comprises, acted upon by the drive wheel 6 away. As a result, the drive belt 8 is tensioned.
  • the drive device 4 also has a plurality of contact pressure rollers 17 to 22.
  • the running surfaces 17 'to 22' of the contact pressure rollers 17 to 22 each have a toothed rim 17 'to 22'. With the sprockets 17 'to 22' engage the contact pressure rollers 17 to 22 in the teeth of the drive belt (toothed belt) 8 a.
  • the contact pressure rollers 17 to 20 are mounted on stationary axes 23 to 26 within the drive device 4.
  • the contact pressure rollers 21, 22 are mounted on movable axes 27, 28.
  • the handrail 3 for example, run in a running direction 29.
  • Another, possible running direction 30 is opposite to the direction 29.
  • the contact pressure rollers 17 to 22 also have a tooth profile.
  • the movable axes 27, 28 are movable within the mechanically provided limits in and counter to the direction 31, which is perpendicular to the running direction 29.
  • the contact pressure rollers 21, 22 are preferably urged in the direction 31 against the drive belt 8.
  • the counter-pressure device 5 has counter-pressure rollers 32 to 39.
  • Counter-pressure rollers 32 to 39 have running surfaces 32 'to 39', which in this
  • Embodiment as smooth running surfaces 32 'to 39' are configured. While an inner side 40 of the handrail 3 faces the contact pressure rollers 17 to 22 and the drive wheel 6 and the tensioning wheel 7, an upper side 41 of the handrail 3 faces the counter-pressure rollers 32 to 39. However, the contact pressure rollers 17 to 22 and the drive wheel 6 and the tensioning wheel 7 are not directly on the inside 40 of the handrail 3 at. The drive belt 8 is partially directly to the inside 40 of the handrail 3 at. Thus, the contact pressure rollers 17 to 22 and the act
  • Running direction 29, 30 are transmitted to the handrail 3.
  • the counter-pressure rollers 32 to 39 are in this embodiment, with their running surfaces 32 'to 39' directly to the top 41 of the handrail 3 at.
  • the handrail 3 is of the counter-pressure rollers 32 to 39 against the drive belt 8 with a
  • Pressing force applied which is caused by a tension spring 42.
  • the pressing force 45 preferably acts counter to the direction 31 and thus perpendicular to the running direction 29 of the handrail third
  • the tension spring 42 of the counter-pressure device 5 is arranged parallel to the running direction 29 in this embodiment.
  • the at least one tension spring 42 is arranged at least approximately parallel to the running direction 29. This means that a direction of action 43 of the tension spring 42, along which also the Spring force 44 of the tension spring 42 acts, is oriented parallel to the direction 29.
  • the parallel orientation is to be understood here in relation to the relevant central longitudinal axes and includes a so-called antiparallel orientation.
  • the drive belt 8 of the drive means 4 and the Gegenpecializingroilen 32 to 39 are arranged to each other so that the handrail 3 between the drive belt 8 and the Gegenchristroilen 32 to 39 in the direction 29 is feasible.
  • the handrail is thus acted upon by the counter-pressure rollers 32 to 39 against the drive belt 8 with the pressing force 45.
  • the pressing force 45 in turn is caused by the tension spring 42, that is, the spring force 44 of the tension spring 42.
  • the counter-pressure rollers 32 to 39 are in this case at least partially in an extension
  • a height 50 of the counter-pressure device 5 can be optimized, that is, as small as possible. Accordingly, the height 51 of the handrail drive 2, which is composed of the height 50 of the counter-pressure device 5, a height 52 of the drive device 4, a height 53 of the handrail 3 and optionally structurally required additional heights 54, 55, are reduced. However, such additional heights 54, 55 can be reduced comparatively easily if it makes sense in the respective application. It is essential here that a vertical dimension 56 of the tension spring 42 has no influence on the overall height 51 of the handrail drive 2. Because the dimension 56 of the tension spring 42 is completely within the height 50 of the counter-pressure device 5. The dimension 56 is determined by the distance between the upper limit 47 and the lower limit 48. In this embodiment, the dimension 56 is equal to the outer diameter of the tension spring 42. The tension spring 42 is not
  • tension spring 42 also includes a pack of a plurality of coil springs arranged side by side in a direction 57 (FIG. 5) that is both perpendicular to the running direction 29 and perpendicular to the direction 31.
  • the tension spring 42 is also a package Be disc springs.
  • Spiral springs which serve as a tension spring 42 are arranged in a horizontal plane parallel to each other, without thereby increasing the vertical dimension 56.
  • the handrail drive 2 on a support 58 on which the drive means 4 and the counter-pressure device 5 are attached.
  • Mounting bracket 59 of the counter-pressure device 5 is in this case firmly connected to the carrier 58 and the support plate 58.
  • FIG. 4 shows the handrail drive 2 shown in FIG. 3 in an excerptional, schematic representation according to the exemplary embodiment of the invention.
  • FIG. 5 shows the counter-pressure device 5 of the handrail drive 2 in accordance with FIG. 4
  • the counter-pressure device 5 has a tension spring bearing 60, which with the
  • the counter-pressure device 5 has a bearing body 61 which comprises bearing plates 62, 63 (FIG. 3) for supporting axles 72 to 79.
  • the counter-pressure device 5 on a slider 64 which is formed in this embodiment by a sliding plate 64.
  • the slider 64 may be formed in a correspondingly modified embodiment but for example by slide rails.
  • a slide 65 is formed on the sliding plate 64. There the sliding plate 64 is fixedly connected to the mounting bracket 59, the slide 65 is stationary with respect to the carrier 58 is positioned.
  • the counter-pressure device 5 also has a guide 66 (FIG. 3), which is connected to the carrier 58 and thus to the drive device 4 by means of the sliding plate 64 and the fastening angle 59.
  • the bearing body 61 has a guide pin 67 which is connected on the one hand to the bearing plate 62 and on the other hand to the bearing plate 63. The guide pin 67 is guided in the guide 66.
  • Guide pin 67 is the bearing body 61 at this point relative to the
  • the guide is at least approximately perpendicular to the running direction 29.
  • the direction of the pressing force 45 along the guide of the guide pin 67 results in the guide 66th
  • the counter-pressure rollers 32 to 39 are mounted on axles 72 to 79, which are each connected on the one hand to the bearing plate 62 and on the other hand to the bearing plate 63. As a result, the counter-pressure rollers 32 to 39 are mounted in the bearing body 61.
  • Counter-pressure rollers 32 to 39 are mounted one behind the other in the extension 46 of the tension spring 42 on the bearing body 61.
  • the axis 72 to 79 may be referred to as the first axis and the axis 79 as the second axis. Since in this embodiment more than two axes 72 to 79 are provided, on which the counter-pressure rollers 32 to 39 are mounted, the axes 73 to 78 may be referred to as further axes.
  • the first axis 72 and the second axis 79 are provided fixedly to the bearing body 61.
  • the counter-pressure roller 32 and on the second axis 79, the counter-pressure roller 39 are mounted on the first axis 72.
  • the counter-pressure roller 32 is in this case associated with the tensioning wheel 7.
  • the counter-pressure roller 39 is assigned to the drive wheel 6.
  • first axis 72 can also be integrated as an additional axis in the bearing body 61, on the no Counter-pressure roller is arranged.
  • second axis 79 may be integrated as an additional axis in the bearing body 61, on the no
  • Counter-pressure roller is arranged.
  • the embodiment described with reference to the exemplary embodiment represents a preferred special case in that the counter-pressure rollers 32, 39 are arranged on the first axis 72 and on the second axis 79.
  • no additional axes are required, which reduces the space requirement for the counter-pressure device 5.
  • the counter-pressure device 5 of the handrail drive 2 has a deflection device 80.
  • the deflection device 80 has Gleitschreibungs vom 81 to 83, connecting rods 84 to 87 and other components.
  • Gleitschreibungs vom 81 to 83 the connecting rods 84 to 87 and other components.
  • FIGS. 3 and 5 the connecting rods 84 to 87.
  • the deflecting device 80 is mounted on the sliding track 65 via its sliding shoes 81 to 83. Here is a mobility of the deflection 80 along the
  • Mode of action 43 allows.
  • the direction of action 43 is in this case oriented parallel to the slideway 65.
  • the tension spring bearing 60 is in this case stationary to the slide 65.
  • the tension spring 42 thus has the function of pulling the deflection device 80 toward the tension spring bearing 60.
  • the tension spring 42 is in a suitable manner at least indirectly with the
  • the deflection device 80 serves for deflecting the spring force 44 of the tension spring 42 into the pressing force 45 of the counter-pressure rollers 32 to 39.
  • the deflection device 80 is designed as a mechanical deflection device 80.
  • the deflection device 80 has a first axle guide 90 with a guide track 91.
  • the first axle guide 90 is configured in the Gleit Resultssschuh 81 in this embodiment.
  • the first axle guide 90 is designed as a double-sided axle guide 90, which guides the first axis 72 at its two ends.
  • the first axle guide 90 thereby guides the first axle 72 on the one hand in the vicinity of the bearing plate 62 and on the other hand in the vicinity of the bearing plate 63 of the bearing body 61.
  • the guideway 91 is thereby formed, as it were, by two surface elements lying in a guide plane 92.
  • the guide plane 92 and the action direction 43 include a predetermined deflection angle 93.
  • Feature predetermined deflection angle 93 defines that regardless of the position of the axis 72 within the axle guide 90, in the Achsschreibung 90 and the guide plane 92 always a spring force 44 implementing pitch is present.
  • the deflection angle 93 is thus greater than 0 °.
  • the deflection angle 93 is an acute deflection angle 93, that is, less than 90 °.
  • the deflection angle 93 is preferably selected from a range of 5 ° to 45 °. In particular, the
  • Deflection angle 93 can be selected from a range of 10 ° to 30 °. In particular, the deflection angle 93 can be selected from a range of 15 ° to 25 °. Specifically, the deflection angle 93 may be about 17 ° to 20 °.
  • the spring force 44 acts along the direction of action 43 between the first axis 72 and the guide track 91 of the first axis guide 90
  • the guide 66 is rigidly connected via the carrier 59 with the tension spring bearing 60, on which the tension spring 42 is supported, wherein the spring force 44 of the tension spring 42, the bearing body 61 via the directing device 80 acts upon.
  • the sliding guide shoe 82 has a second axle guide 94 with a guide track 91.
  • the guide track 91 formed by two patches lies in a guide plane 95.
  • the guide plane 95 closes with the
  • Bearing body 61 are integrated, to be mounted in further axle guides 90, in turn, the same deflection angle 93 is provided. Furthermore, the deflection can optionally also take place on a single axle guide or, as shown in the present exemplary embodiment, also in the region of the guide pin 67 and the guide 66.
  • the Jacobiie 32 which is mounted on the first axis 72, the closest to the tension spring 42 and the tension spring bearing 60 arranged counter-pressure roller 32, Further, the counter-pressure roller 39 which is mounted on the second axis 79, the furthest In this way, the stability of the arrangement of the bearing body 61 in the deflection 80 can be improved by the tension spring 42 and the tension spring bearing 60 remotely located counter pressure roller 39. For example, thereby tilting and associated jamming or wedging can be avoided.
  • guide rollers 120 to 123 are provided in this embodiment, which are shown in Figures 3 and 4. This ensures that the drive belt 8 runs reliably over the drive wheel 6 and the tensioning wheel 7 and thus also over the running surfaces 17 'to 22' of the contact pressure rollers 17 to 22.
  • Anpressdruckrollen 17 to 20 are mounted in the direction of the pressing force 45 is not movable, thus adjusts a balance of power when the handrail 3 at least substantially in a straight line between the drive means 4 and the Counter-pressure device 5 in the running direction 29 runs.
  • FIG. 6 shows schematically in side view a handrail drive 202 with two
  • Counter-pressure devices 205 and 206 which are arranged mirror-symmetrically to a mirror plane S.
  • the mirror plane S extends orthogonally to the running direction 29, 30 of the handrail 3 and is arranged approximately centrally of the drive device 4.
  • Counterpressure devices 205, 206 are divided, then the
  • Counter-pressure device 205 and the other, mirror-image counter-pressure device 206 are assigned to a single drive device 4. However, too
  • the conveyor system 100, 1 10 may have per handrail 3 to be driven also two mirror-image handrail drives 2, which are arranged for example at the two ends of the traveling floor space for people and / or objects or in front of the balustrade end curves, where the handrail 3 also is diverted.
  • Variations in the knowledge of the present invention can be created, for example, be used instead of compression springs, tension springs or disc springs.
  • the two tension springs can also be replaced by a central spring between the two Counter-pressure devices 205, 206 is arranged.
  • the Zentraifeder can be a tension spring or a compression spring. This arrangement also eliminates the two tension spring bearings.
  • the handrail drive 2 according to the invention can be used both in an escalator and in a moving walk.

Landscapes

  • Escalators And Moving Walkways (AREA)

Abstract

L'invention concerne un mécanisme d'entraînement de main courante (2) destiné à l'entraînement d'une main courante (3) d'un équipement de transport, lequel possède au moins un dispositif de transport (4) et au moins un dispositif de contre-pression (5). Le dispositif de contre-pression (5) contient au moins un ressort tendeur (42) et au moins un galet de contre-pression (32 à 39). La main courante (3) est disposée entre le dispositif d'entraînement (4) et ledit galet de contre-pression (32 à 39) approximativement dans un sens de déplacement linéaire (29, 30), et elle est soumise par ledit galet de contre-pression (32 à 39) à une force de pression (45) contre le dispositif d'entraînement (4) produite par le ressort tendeur (42). Le mécanisme d'entraînement de main courante (2) possède un dispositif de renvoi mécanique (80) à l'aide duquel la force de ressort (44) du ressort tendeur (42) peut être retournée dans la force de pression (45) dudit galet de contre-pression (32 à 39).
EP14799744.9A 2013-11-27 2014-11-14 Entraînement de main courante pour un escalier ou un trottoir roulant Not-in-force EP3074335B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP14799744.9A EP3074335B1 (fr) 2013-11-27 2014-11-14 Entraînement de main courante pour un escalier ou un trottoir roulant

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP13194551 2013-11-27
PCT/EP2014/074631 WO2015078709A1 (fr) 2013-11-27 2014-11-14 Mécanisme d'entraînement de main courante pour un escalier mécanique ou un trottoir roulant
EP14799744.9A EP3074335B1 (fr) 2013-11-27 2014-11-14 Entraînement de main courante pour un escalier ou un trottoir roulant

Publications (2)

Publication Number Publication Date
EP3074335A1 true EP3074335A1 (fr) 2016-10-05
EP3074335B1 EP3074335B1 (fr) 2018-01-03

Family

ID=49709494

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14799744.9A Not-in-force EP3074335B1 (fr) 2013-11-27 2014-11-14 Entraînement de main courante pour un escalier ou un trottoir roulant

Country Status (5)

Country Link
US (1) US9745173B2 (fr)
EP (1) EP3074335B1 (fr)
CN (1) CN105764832B (fr)
ES (1) ES2657419T3 (fr)
WO (1) WO2015078709A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2696523T3 (es) * 2014-11-28 2019-01-16 Inventio Ag Accionamiento de pasamanos para una escalera mecánica o un pasillo rodante
US10674285B2 (en) 2017-08-25 2020-06-02 Starkey Laboratories, Inc. Cognitive benefit measure related to hearing-assistance device use
CN107651549B (zh) * 2017-10-25 2023-12-15 广州广日电梯工业有限公司 一种自动扶梯的模块式扶手龙头
EP3511284B1 (fr) 2018-01-10 2021-09-15 Otis Elevator Company Trottoir roulant

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4875568A (en) 1989-01-05 1989-10-24 Otis Elevator Company Escalator handrail drive
US5117960A (en) * 1991-08-15 1992-06-02 Otis Elevator Company Linear belt handrail drive
US5341909A (en) * 1993-08-30 1994-08-30 Otis Elevator Company Linear wheel escalator handrail drive
US5307920A (en) * 1993-09-14 1994-05-03 Otis Elevator Company Moving handrail drive
US7954619B2 (en) * 2007-06-01 2011-06-07 Kone Corporation Load sharing handrail drive apparatus
CN201777766U (zh) * 2010-05-19 2011-03-30 蒂森克虏伯扶梯(中国)有限公司 一种扶手带驱动装置

Also Published As

Publication number Publication date
ES2657419T3 (es) 2018-03-05
US9745173B2 (en) 2017-08-29
CN105764832A (zh) 2016-07-13
WO2015078709A1 (fr) 2015-06-04
US20170001843A1 (en) 2017-01-05
CN105764832B (zh) 2017-09-22
EP3074335B1 (fr) 2018-01-03

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