JP2008150138A - Handrail driving device for passenger conveyor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a handrail driving device for a passenger conveyor capable of easily adjusting the travelling speed of moving handrails. <P>SOLUTION: A spindle 21 is inserted into a spindle insertion opening 13b, each bearing 18 and a collar 19. A first presser member 24 arranged on a third handrail driving sprocket 23 side, a first wheel member 25 and a second presser member 26 arranged on a side opposite to the third handrail driving sprocket 23 side are inserted into the spindle 21 for installation. A doughnut-like outer ring 29 made of a soft material is fitted to the peripheral surface of the first wheel member 25. The outer ring 29 is pinched by the first and the second presser members 24 and 26 from both sides thereof. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a handrail drive device for a passenger conveyor that travels a moving handrail by power from a drive device that travels a step.

  In a handrail drive device for a general passenger conveyor, power from a driving machine is transmitted to a plurality of handrail drive rollers in the handrail drive device via a plurality of sets of sprockets and a plurality of winding chains. And the moving handrail pinched | interposed into each handrail drive roller and a press roller is driven with the motive power transmitted to each handrail drive roller (for example, refer patent document 1).

Japanese Utility Model Publication No.59-192084

Here, the traveling speed (relative speed) of the moving handrail relative to the traveling speed of the step is the number of sprocket teeth interposed between the driving machine and the handrail driving roller, and each handrail driving roller and moving handrail. And the slip generated on the contact surface.
And when setting the traveling speed of the moving handrail at the time of designing the passenger conveyor, after predicting the size of the slip, each of the traveling speed is the same as the traveling speed of the step or slightly faster than the traveling speed of the step. The number of sprocket teeth is calculated.
However, the measured value of the traveling speed of the moving handrail may deviate from the design value due to variations in assembly accuracy after installation of the passenger conveyor, processing errors of each sprocket, and the like. Also, when the size of the slip generated on the contact surface of each handrail drive roller and moving handrail deviates from the expected value due to the installation environment of the passenger conveyor, the measured value of the traveling speed of the moving handrail deviates from the design value. There is.
In this way, if the measured value of the traveling speed of the moving handrail deviates from the design value, it is necessary to change the number of installed handrail driving rollers, readjust the number of teeth of each sprocket, etc. It takes a great deal of time during installation. In particular, when the combination of the number of teeth of the sprocket is changed, the traveling speed of the moving handrail may become extremely fast or slow, which makes it difficult to adjust the traveling speed of the moving handrail.

  The present invention has been made to solve the above-described problems, and an object thereof is to obtain a handrail drive device for a passenger conveyor that can easily adjust the traveling speed of a moving handrail.

  A handrail drive device for a passenger conveyor according to the present invention has a handrail drive roller whose part of the outer peripheral surface is in contact with a moving handrail and whose diameter can be adjusted, and receives a driving force from a driving machine that runs a step. A handrail drive mechanism that travels the moving handrail by rotating the handrail drive roller by the driving force is provided.

  In the handrail drive device for passenger conveyors of this invention, the diameter of the handrail drive roller can be adjusted. Therefore, by adjusting the diameter, the rotation speed of the handrail drive roller remains constant. By increasing or decreasing the pushing amount of the moving handrail of the roller, the traveling speed of the moving handrail can be easily adjusted.

The best mode for carrying out the present invention will be described below with reference to the drawings.
Embodiment 1 FIG.
FIG. 1 is a side view showing an outline of an end portion of an escalator according to Embodiment 1 of the present invention (partially cut away).
In the figure, a truss 1 is bridged across the floors in the building escalator installation space. A pair of balustrades 2 is erected on the upper surface of the truss 1. Between the pair of balustrades, steps (not shown) connected endlessly are provided so as to be able to travel. A handrail rail 3 is provided on the surface of each balustrade 2. The handrail rail 3 is provided with an endless moving handrail 4 so that it can travel. The travel of the moving handrail 4 is guided by the handrail rail 3.

  Further, an escalator driving machine (motor) 5 as a driving machine and a guide sprocket 6 are provided at the upper end of the truss 1. A main sprocket 7 is attached to the rotating shaft of the escalator driving machine 5. Further, on the upper floor side of the inclined portion of the truss 1, a first handrail driving sprocket 8, a pair of second handrail driving sprockets 9, and a pair of handrail driving devices 10 for driving each moving handrail 4, Is provided.

  The first handrail driving sprocket 8 and the main sprocket 7 are connected to each other by a first handrail driving chain 11. The path of the first handrail driving chain 11 is guided by the guide sprocket 6. The first handrail driving sprocket 8 and the second handrail driving sprocket 9 are disposed on the same rotation shaft and rotate integrally with each other. The second handrail driving sprocket 9 and the handrail driving device 10 are connected to each other by a second handrail driving chain 12.

  FIG. 2 is an enlarged side view showing the handrail drive device 10 of FIG. The handrail drive device 10 includes a mounting plate 13 fixed to the truss 1, a plurality of handrail drive mechanisms 14, tension sprockets 15, a plurality of leaf springs 16, and a plurality of press rollers 17. Each handrail drive mechanism 14 and tension sprocket 15 are rotatably attached to the attachment plate 13, respectively. Each handrail drive mechanism 14 has a handrail drive roller (transmission roller) 14a in which a part of the outer peripheral surface and the back surface of the movable handrail 4 abut against each other.

  Each handrail drive mechanism 14 and the tension sprocket 15 are connected to the second handrail drive sprocket 9 by a second handrail drive chain 12. The tension of the second handrail driving chain 12 is kept constant by the tension sprocket 15. Therefore, the power from the escalator driving machine 5 is transmitted through the main sprocket 7, the first handrail driving chain 11, the first handrail driving sprocket 8, the second handrail driving sprocket 9, and the second handrail driving chain 12. It is transmitted to the handrail drive mechanism 14. The handrail driving roller 14a is rotated by the driving force transmitted to the handrail driving mechanism 14.

  An intermediate portion of the leaf spring 16 is fixed to the mounting plate 13. Both end portions of the leaf spring 16 are connected to the pressure roller 17 respectively. The pressure roller 17 is disposed such that a part of the outer peripheral surface thereof and the surface of the moving handrail 4 are in contact with each other. Each press roller 17 receives a pressing force (spring force) from the leaf spring 16 toward the handrail driving roller 14a. That is, the moving handrail 4 is sandwiched between the front and back surfaces of the handrail driving roller 14 a and the pressure contact roller 17. When the handrail driving roller 14a rotates, the moving handrail 4 is pushed and driven.

  Next, the handrail drive mechanism 14 will be specifically described. 3 is a cross-sectional view taken along line III-III in FIG. FIG. 4 is an exploded view showing an exploded state of the handrail drive mechanism 14 of FIG. The mounting plate 13 is provided with a cylindrical bearing housing portion 13a that protrudes toward the movable handrail 4 and a shaft insertion opening 13b that corresponds to the position of the bearing housing portion 13a. At the end of the inner wall of the bearing housing portion 13a on the moving handrail 4 side, a retaining ring groove 13c is provided over the entire circumference. In the bearing housing portion 13a, a pair of bearings 18 and a collar 19 interposed between the pair of bearings 18 are provided. Each bearing 18 and collar 19 are fixed to the inner wall of the bearing housing portion 13a by a peripheral edge portion of the shaft insertion opening portion 13b and a C-type retaining ring 20 fitted in the retaining ring groove 13c.

  A main shaft (main shaft) 21 is inserted through the shaft insertion opening 13b, each bearing 18, and the collar 19. A retaining ring groove 21a is provided at a position corresponding to the tip of the bearing housing portion 13a of the main shaft 21 and a position corresponding to the shaft insertion opening 13b. A C-type retaining ring 22 is fitted in each retaining ring groove 21a. Oscillation of the bearing 18 in the axial direction is regulated by each C-type retaining ring 22. Further, a third handrail driving sprocket 23 connected (engaged) to the second handrail driving chain 12 is fixed to the end of the main shaft 21 on the side opposite to the moving handrail 4.

  Further, a speed adjusting scale portion 21 b is provided at an end portion (tip portion) of the main shaft 21 on the side opposite to the third handrail drive sprocket 23. Furthermore, a plurality of screw holes 21c are provided at intervals in the circumferential direction at a position corresponding to the center in the width direction of the moving handrail 4 of the main shaft 21. The main shaft 21 includes a first pressing member 24 disposed on the third handrail driving sprocket 23 side, a first wheel member 25 serving as an inner ring, and a second anti-third handrail driving sprocket 23 side. A pressing member 26 is inserted. The first pressing member 24 is provided with a plurality of screw holes 24a spaced from each other in the circumferential direction.

  Attachment holes 25a and 26a are provided at positions corresponding to the screw holes 24a of the first wheel member 25 and the second pressing member 26, respectively. Bolts 27 are inserted into the mounting holes 25a and 26a, and the bolts 27 are screwed into the screw holes 24a. That is, the first pressing member 24, the first wheel member 25, and the second pressing member 26 are integrated by screwing the bolt 27 into the screw hole 24a. On the outer peripheral surface of the first wheel member 25, a plurality of mounting holes 25b penetrating to the inner peripheral surface are provided at intervals in the circumferential direction. A hexagon socket head cap screw 28 is inserted into the mounting hole 25b, and the hexagon socket head cap screw 28 is screwed into the screw hole 21c. That is, the first wheel member 25 is fixed to the main shaft 21 by the hexagon socket head cap screw 28 being screwed into the screw hole 21c.

  An outer ring (transmission roller) 29 of a donut-shaped soft material (for example, rubber and vinyl) is attached to the outer peripheral surface of the first wheel member 25. The outer ring 29 is sandwiched from both side surfaces by the first and second pressing members 24 and 26. Further, the outer diameter of the outer ring 29 is deformed so as to expand and contract in the outer circumferential direction in accordance with the pressing force from the both side surfaces by the first and second pressing members 24 and 26. That is, the outer ring 29 can be expanded and contracted in the radial direction. Here, the main shaft 21, the third handrail drive sprocket 23, the first pressing member 24, the first wheel member 25, the second pressing member 26, and the outer ring 29 constitute the handrail driving mechanism 14, and the first The wheel member 25 and the outer ring 29 constitute a handrail driving roller 14a.

  Here, the relationship between the clearance dimension t and the outer diameter dimension φD of the outer ring 29 will be described. First, when the gap t between the first and second pressing members 24 and 26 is large, the pressing force acting on both side surfaces of the outer ring 29 from the first and second pressing members 24 and 26 is weak, as shown in FIG. In addition, the outer ring 29 has a shape that extends in the thickness direction. On the other hand, when the bolt 27 is tightened from the state shown in FIG. 5 to reduce the gap dimension t between the first and second pressing members 24 and 26, both sides of the outer ring 29 extend from the first and second pressing members 24 and 26. The pressing force acting on the surface is increased, and the outer ring 29 is elastically deformed so as to shrink in the thickness direction and to extend in the radial direction, as shown in FIG. That is, the outer diameter dimension φD of the outer ring 29 is larger than the outer diameter dimension φD of the outer ring 29 shown in FIG. 5 by increasing the pressing force acting on both side surfaces of the outer ring 29 from the first and second pressing members 24, 26. The diameter of the handrail driving roller 14a is increased.

  Further, the outer diameter dimension φD of the outer ring 29 becomes larger than the outer diameter dimension φD before the adjustment, that is, the diameter of the handrail driving roller 14a becomes larger than the diameter before the adjustment, so that one rotation of the handrail driving roller 14a is performed. The amount of push of the moving handrail 4 per hit increases. Further, the rotation speed of the handrail driving roller 14a is constant regardless of the diameter of the handrail driving roller 14a, and the amount of pushing of the moving handrail 4 per one rotation of the handrail driving roller 14a increases, thereby moving the handrail. The running speed of 4 is faster than the running speed before adjusting the diameter.

  On the other hand, when the diameter of the handrail driving roller 14a is smaller than the diameter before the adjustment, the amount of push of the moving handrail 4 per rotation of the handrail driving roller 14a is reduced. And since the pushing amount of the moving handrail 4 per rotation of the handrail driving roller 14a decreases, the traveling speed of the moving handrail 4 becomes slower than the traveling speed before the diameter is adjusted. Here, even if the diameter of the handrail driving roller 14a changes, if the change in the diameter is within an allowable range of deformation of the leaf spring 16, the leaf spring 16 is deformed to follow the change in diameter. Thus, the contact state between the outer peripheral surface of the handrail driving roller 14a and the moving handrail 4 is maintained.

  In the escalator handrail drive device as described above, the diameter of the handrail drive roller 14a can be adjusted. Therefore, by adjusting the diameter, the rotation speed of the handrail drive roller 14a remains constant. The travel speed of the movable handrail 4 can be easily adjusted by increasing / decreasing the pushing amount of the movable handrail 4 of the handrail drive roller 14a.

  Further, since the travel speed of the movable handrail 4 can be adjusted, the travel speed of the movable handrail 4 that changes for each installation environment of the escalator can be easily adjusted, and also changes due to variations in assembly accuracy of the escalator. The traveling speed of the moving handrail 4 can be easily adjusted.

  Further, since the scale portion 21b is provided at the tip end portion of the main shaft 21, the diameter of any one handrail drive roller 14a among the plurality of handrail drive rollers 14a in the adjustment operation of the traveling speed of the moving handrail 4 by the worker. When adjusting the diameter of the remaining unadjusted handrail drive roller 14a, the numerical value of the scale portion 21a of the adjusted handrail drive roller 14a is read, and the numerical value of the scale portion 21a of the unadjusted handrail drive roller 14a By adjusting the diameter of the unadjusted handrail drive roller 14a so that the value becomes the numerical value of the scale portion 21a of the adjusted handrail drive roller 14a, the diameters of all the handrail drive rollers 14a can be uniformly adjusted and moved. The work efficiency of the travel speed adjustment of the handrail 4 can be further improved.

Embodiment 2. FIG.
Next, a second embodiment of the present invention will be described.
7 is a cross-sectional view showing the handrail drive mechanism 14 according to the second embodiment (a cross-sectional view taken along the line VII-VII in FIG. 2). FIG. 8 is an exploded view showing an exploded state of the handrail drive mechanism 14 of FIG. In the figure, in the first embodiment, the main shaft 21 having a circular cross section is used, but in the second embodiment, the main shaft 31 having a hexagonal cross section is used. A retaining ring groove 31a and an elongated pin insertion hole 31b are provided at a position corresponding to the tip of the bearing housing portion 13a of the main shaft 31 (an intermediate portion of the main shaft 31). Further, the main shaft 31 is provided with a screw rod insertion hole 31c extending in the axial direction from the tip portion to the intermediate portion. The pin insertion hole 31b and the screw rod insertion hole 31c are connected to each other. A plurality of screw holes 31d are provided between the tip end portion of the main shaft 31 and the pin insertion hole 31b at intervals in the circumferential direction.

  A cylindrical collar 32 is inserted between the intermediate portion of the main shaft 31 and the third handrail drive sprocket 23. The collar 32 is fixed to the main shaft 31 by a retaining ring groove 31 a and a C-shaped retaining ring 33. A retaining ring groove 32a is provided at a position corresponding to the tip of the bearing housing portion 13a of the collar 32 and a position corresponding to the shaft insertion opening 13b. Further, the collar 32 is restricted from swinging in the axial direction by each retaining ring groove 32 a and the C-shaped retaining ring 34. That is, the main shaft 31 is supported by the bearing 18 via the collar 32.

  A screw rod 35 is inserted into the screw rod insertion hole 31c. A bolt portion 35a in which a thread is formed is provided at the tip of the screw rod 35 (the end on the side opposite to the third handrail drive sprocket 23). A pin insertion hole 35b is provided in the vicinity of the end portion of the screw rod 35 on the third handrail driving sprocket 23 side. A screw rod retaining pin 36 is inserted into the pin insertion holes 31b and 35b. That is, the main shaft 31 and the screw rod 35 are integrally combined with each other by the pin insertion holes 31 b and 35 b and the screw rod retaining pin 36. The screw rod 35 can slide in the screw rod insertion hole 31c.

  The main shaft 31 is disposed on the side of the second wheel member 37 (one of a pair of inner rings) 37 that contacts both ends of the screw rod retaining pin 36 in the vertical direction, the spring receiving member 38, and the anti-third handrail drive sprocket 23 side. The third wheel member (the other of the pair of inner rings) 39 is inserted. The cross-sectional shape in the radial direction of the inner peripheral portions of the second and third wheel members 37 and 39 is a hexagonal shape and is slidable on the main shaft 31. Moreover, the shape of the 2nd and 3rd wheel members 37 and 39 is a taper shape (cone shape) that an outer peripheral surface (conical surface) tapers from one side to the other. Further, anti-slip grooves 37a and 39a are formed on the outer peripheral surfaces of the second and third wheel members 37 and 39, respectively.

  The surface of the second wheel member 37 on the side opposite to the third handrail drive sprocket 23 is provided with a screw hole 37b. A mounting hole 39 b is provided at a position corresponding to the screw hole 37 b of the third wheel member 39. Spring mounting holes 37c and 39c are provided on the surface of the second wheel member 37 on the side opposite to the third handrail driving sprocket 23 and the surface of the third wheel member 39 on the side of the third handrail driving sprocket 23 so as to face each other. Is provided. The surface of the third wheel member 39 on the side opposite to the third handrail drive sprocket 23 is provided with a plurality of screw holes 39d spaced from each other in the circumferential direction.

  The spring receiving member 38 is provided with a plurality of mounting holes 38a spaced from each other in the circumferential direction. Further, a partition plate portion 38 b that protrudes toward the outer peripheral direction is provided between the mounting holes 38 a of the spring receiving member 38. A hexagon socket head bolt 40 is inserted into the mounting hole 38a, and the hexagon socket head bolt 40 is screwed into the screw hole 31d. That is, the spring receiving member 38 is fixed on the main shaft 31 by the hexagon socket head cap screw 40 being screwed into the screw hole 31d. On the outer peripheral surfaces of the second and third wheel members 37 and 39, an outer ring 41 made of a donut-shaped soft material is provided straddling each other. A part of the outer peripheral surface of the outer ring 41 is in contact with the moving handrail 4. Moreover, the cross-sectional shape of the inner peripheral part of the outer ring | wheel 41 is V shape which becomes thin toward the thickness direction center and radial direction center from both side surfaces. Here, the outer ring 41 and the second and third wheel members 37 and 39 constitute a handrail driving roller 14a.

  A rod-shaped scale member 42 is inserted into the mounting hole 39b. A scale portion 42 a for adjusting the handrail speed is provided at the tip of the scale member 42. Further, a bolt portion 42 b is provided at the other end portion of the scale member 42. Further, a nut-like turning part 42 c is provided in the middle part of the scale member 42. One end of a spring 43 is inserted into each spring mounting hole 37c, 39c. The other end of each spring 43 is in contact with the partition plate 38b. That is, the spring force of the spring 43 having the same size acts on the second and third wheel members 37 and 39, and the spring force between the second wheel member 37 and the spring receiving member 38 is caused by the spring force. The gap dimension and the gap dimension between the third wheel member 39 and the spring bearing member 38 are both held to be equal.

  A cap member 44 that is in contact with the surface of the third wheel member 39 on the side opposite to the third handrail drive sprocket 23 is inserted at the tip of the screw rod 35. The cap member 44 is provided with a plurality of mounting holes 44a spaced from each other in the circumferential direction. The cap member 44 is attached to the third wheel member 39 by inserting a screw 45 into each attachment hole 44a and screwing the screw 45 into the screw hole 39d. Furthermore, the shape of the cap member 44 is a hat shape, and the inner peripheral portion protrudes from the outer peripheral portion. Two nuts (double nuts) 46 are screwed to the bolt portion 35a. FIG. 9 is an enlarged perspective view showing the main shaft 31 and the screw rod 35 of FIG. FIG. 10 is an enlarged perspective view showing the spring receiving member 38 of FIG. Other configurations are the same as those in the first embodiment.

  Here, the relationship between the gap dimension t between the second and third wheel members 37 and 39 and the outer diameter dimension φD of the outer ring 41 will be described. First, when the gap t between the second and third wheel members 37, 39 is large, the pressing force acting on the inner peripheral portion of the outer ring 41 from the second and third wheel members 37, 39 is weak, as shown in FIG. It will be in such a state. Then, when the nut 46 is tightened from the state shown in FIG. 11, the screw rod retaining pin 36 is slid in the elongated pin insertion hole 31b as shown in FIG. As a center, the gap dimension t between the second and third wheel members 37, 39 is reduced. And the contact | abutting range of the outer peripheral surface of the 2nd and 3rd wheel members 37 and 39 and the inner peripheral surface of the outer ring | wheel 41 is large because the clearance gap dimension t between the 2nd and 3rd wheel members 37 and 39 becomes small. Thus, the pressing force acting on the inner peripheral portion of the outer ring 41 from the second and third wheel members 37, 39 is increased, and the outer ring 41 is pushed and expanded in the radial direction by the second and third wheel members 37, 39. It will be elastically deformed. That is, the outer diameter dimension φD of the outer ring 41 changes according to the pressing force acting on the inner peripheral portion of the outer ring 41 from the second and third wheel members 37 and 39.

  In the handrail drive device for the escalator as described above, even when the outer ring 41 is deformed in the radial direction in accordance with the pressing force acting on the inner peripheral portion of the outer ring 41, the same effect as in the first embodiment can be obtained. Can do.

  Further, since anti-slip grooves 37a and 39a are formed on the outer peripheral surfaces of the second and third wheel members 37 and 39, respectively, the outer peripheral surfaces of the second and third wheel members 37 and 39 and the inner periphery of the outer ring 41 are provided. Generation | occurrence | production of the slip in the contact location with a surface can be suppressed.

Embodiment 3 FIG.
In the second embodiment, the main shaft 31 having a hexagonal cross section is used. However, as shown in FIG. 13, a main shaft 51 having a spline shape may be used. In connection with this, you may use the 2nd and 3rd wheel members 52 and 53 whose inner periphery shape is a spline shape. Further, the shape is not limited to a hexagon, and may be a polygon such as a quadrangle.

  Furthermore, although the handrail drive device of the escalator was demonstrated in Embodiment 1-3, this invention is applicable also to the handrail drive device of a moving sidewalk.

  Furthermore, in the first to third embodiments, the outer rings 29 and 41 are deformed so as to expand and contract in the radial direction according to the pressing force by the pair of pressing members 24 and 26 or the pressing force by the pair of wheel members 37 and 39. The diameter of the handrail driving roller 14a can be adjusted by the deformation. However, the present invention is not limited to this example, and the diameter of the handrail driving roller only needs to be adjustable.

It is a side view which shows the outline of the edge part of the escalator by Embodiment 1 of this invention. It is a side view which expands and shows the handrail drive device of FIG. It is sectional drawing which follows the III-III line of FIG. It is an exploded view which shows the decomposition | disassembly state of the handrail drive mechanism of FIG. It is sectional drawing which shows the handrail drive mechanism of FIG. 3 when the clearance gap between 1st and 2nd pressing members is large. It is sectional drawing which shows the handrail drive mechanism of FIG. 3 when the clearance gap between 1st and 2nd pressing members is small. It is sectional drawing which shows the handrail drive mechanism by Embodiment 2 of this invention. It is an exploded view which shows the decomposition | disassembly state of the handrail drive mechanism of FIG. It is a perspective view which expands and shows the main axis | shaft and screw rod of FIG. It is a perspective view which expands and shows the spring receiving member of FIG. It is sectional drawing which shows the handrail drive mechanism of FIG. 7 when the clearance gap between 1st and 2nd wheel members is large. It is sectional drawing which shows the handrail drive mechanism of FIG. 7 when the clearance gap between 1st and 2nd wheel members is small. It is a perspective view which shows a part of handrail drive mechanism by Embodiment 2 of this invention.

Explanation of symbols

  4 Moving handrails, 5 Escalator driving machine, 14 Handrail driving mechanism, 14a Handrail driving roller, 21, 31, 51 Main shaft, 21b, 42a Scale part, 24 First pressing member, 25 First wheel member (inner ring), 26 Second Holding member, 29, 41 Outer ring, 37, 52 Second wheel member (inner ring), 39, 53 Third wheel member (inner ring), 37a, 39a Non-slip groove.

Claims (7)

A handrail driving roller whose part of the outer peripheral surface abuts on the moving handrail and whose diameter is adjustable, receives the driving force from the driving machine that runs the step, and rotates the handrail driving roller by the driving force. A handrail drive device for a passenger conveyor, comprising: a handrail drive mechanism that causes the moving handrail to travel. The outer periphery of the handrail drive roller is composed of an outer ring made of a soft material,
The passenger conveyor according to claim 1, wherein the outer ring receives a pressing force from the handrail driving mechanism and elastically deforms in a radial direction in accordance with the pressing force, whereby the diameter of the handrail driving roller expands and contracts. Handrail drive device. The inner peripheral portion of the handrail driving roller is configured by a circular inner ring in which the inner periphery of the outer ring fits on the outer periphery,
The handrail driving mechanism includes a main shaft that passes through the inner ring and receives the power from the driving machine to rotate the inner ring and the outer ring, and a pair of pressers provided on the main shaft so as to sandwich the outer ring from both side surfaces. And further having a member,
The handrail drive device for a passenger conveyor according to claim 2, wherein the outer ring is deformed so as to expand and contract in a radial direction in accordance with a pressing force from both side surfaces by the pair of pressing members.   4. The handrail drive device for a passenger conveyor according to claim 3, wherein the handrail drive mechanism is provided with a scale portion for adjusting the pressing force by the pair of pressing members. The inner peripheral portion of the handrail driving roller is composed of a pair of inner rings facing each other at an interval,
The handrail drive mechanism further includes a main shaft that passes through the pair of inner rings and receives power from a driving machine to rotate the pair of inner rings and the outer ring.
The shape of the pair of inner rings is a tapered shape in which the outer peripheral surface becomes thinner from one to the other,
Non-slip grooves are provided on the outer peripheral surfaces of the pair of inner rings,
The cross-sectional shape of the inner periphery of the outer ring is a V-shape that narrows from both side surfaces toward the thickness direction center,
The outer ring is disposed across the outer peripheral surfaces of the pair of inner rings, and is deformed so as to expand and contract in the radial direction in accordance with the pressing force from the inner peripheral portion by the pair of inner rings. The handrail drive device for a passenger conveyor according to claim 2.   6. The handrail drive device for a passenger conveyor according to claim 5, wherein the handrail drive mechanism is provided with a scale portion for adjusting the pressing force of the pair of inner rings.   The cross-sectional shape of the said main axis | shaft is polygonal shape, The handrail drive device of the passenger conveyor of Claim 5 or Claim 6 characterized by the above-mentioned.

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