GEARING DEVICE OF A PASSAGEWAY DEVICE

Abstract

A gearing device for discontinuously moving at least two elements, in particular barrier elements of a passageway device, having a drive axis, a first active axis of rotation, formed for a torque-transmitting operative connection with the first element, in particular barrier element, a first non-uniformly translating gearing stage between the drive axis and the first active axis of rotation, a second active axis of rotation formed for a torque-transmitting operative connection with the second element, in particular barrier element, a second non-uniformly translating gearing stage between the drive axis and the second active axis of rotation.

Claims

1. A gearing device for discontinuously moving at least two elements, in particular barrier elements, of a passageway device, comprising: a drive axis, a first active axis of rotation formed for torque-transmitting operative connection to the first element, in particular the barrier element, a first non-uniformly translating gearing stage between the drive axis and the first active axis of rotation, a second active axis of rotation formed for torque-transmitting operative connection to the second element, in particular the barrier element, a second non-uniformly translating gearing stage between the drive axis and the second active axis of rotation.

2. The gearing device according to claim 1, wherein the first gearing stage includes a first translation curve, defined as the translation ratio over the angle of rotation of the drive axis, wherein the second gearing stage includes a second translation curve, defined as the translation ratio over the angle of rotation of the drive axis, and wherein the first translation curve of the first gearing stage and the second translation curve of the second gearing stage are the same, however, offset to each other, preferably by 180° with regard to the angle of rotation of the drive axis.

3. The gearing device according to claim 1, wherein a drive wheel, in particular a toothed drive wheel, is disposed on the drive axis, wherein on the first active axis of rotation is disposed a first axis of rotation wheel, in particular axis of rotation toothed wheel, which is in torque-transmitting operative connection with the drive wheel, in particular in contact or in engagement, for forming the first gearing stage, and on the second active axis of rotation is disposed a second axis of rotation wheel, in particular axis of rotation toothed wheel, which is in torque-transmitting operative connection with the drive wheel, in particular in contact or in engagement, for forming the second gearing stage.

4. The gearing device according to claim 3, wherein the drive wheel and the axis of rotation wheels have respective non-round rolling curves.

5. The gearing device according to claim 3, wherein the rolling curves of both axis of rotation wheels are the same.

6. The gearing device according to claim 4, wherein the rolling curves of the axis of rotation wheels and the rolling curve of the drive wheel are different or the same.

7. The gearing device according to claim 3, wherein the first axis of rotation wheel has a first rotation-based changeable effective radius and, the drive wheel has an associated rotation-based changeable drive radius, wherein the sum of the first effective radius and the drive radius is constant during a rotation of the drive wheel, and/or wherein the second axis of rotation wheel has a second rotation-based changeable effective radius and the drive wheel has an associated rotation-based changeable drive radius, wherein the sum of the second effective radius and the drive radius is constant during a rotation of the drive wheel.

8. The gearing device according to claim 4, wherein, with regard to a respective symmetry axis, the axis of rotation wheels and the drive wheel are symmetric, in particular convex, and along the respective symmetry axis, have a length and, vertically to the symmetry axis, have a width, and wherein the active axis of rotation is located on the symmetry axis of the associated axis of rotation wheel and/or the drive axis is located on the symmetry axis of the drive wheel.

9. The gearing device according to claim 7, wherein the length of the axis of rotation wheels is respectively greater than the width of the axis of rotation wheels, and/or wherein the length of the drive wheel is smaller than the width of the drive wheel.

10. The gearing device according to claim 1, further comprising: a hollow output shaft for the torque-proof connection to the first element, in particular the barrier element, wherein the first active axis of rotation is in torque-transmitting operative connection with the hollow output shaft via a third gearing stage, and an output shaft, which is at least partially disposed in the hollow output shaft, for the torque-proof connection to the second element, in particular barrier element, wherein the second active axis of rotation is in torque-transmitting operative connection with the output shaft via a fourth gearing stage.

11. The gearing device according to claim 10, further comprising: for transmitting torque, a first idler wheel connected, in particular torque-proof, to the first axis of rotation wheel and in torque-transmitting operative connection, in particular in contact or in engagement, with the hollow output shaft, and for transmitting torque, a second idler wheel connected, in particular torque-proof, to the second axis of rotation wheel and in torque-transmitting operative connection, in particular in contact or in engagement, with the output shaft.

12. The gearing device according to claim 1, comprising an electric motor connected to the drive axis and/or a damping device connected to the drive axis and/or a coupling connected to the drive axis and/or a brake connected to the drive axis.

13. A tripod barrier for controlling access and/or singularization, comprising a gearing device according to claim 1 and at least two barrier elements formed as barrier stiles, which are rotatably supported about a common output axis and are torque-transmitting connected to a respective one of the active axes of rotation of the gearing device-.

14. A turnstile for controlling access and/or singularization, comprising a gearing device according to claim 1 and at least two barrier elements formed as turnstile leaves, which are rotatably supported about a common output axis and are torque-transmitting connected to a respective one of the active axes of rotation of the gearing device.

15. A use of the gearing device according to claim 1 in a passageway device, in particular in a tripod barrier for moving barrier elements formed as barrier stiles of the tripod barrier, or in a turnstile for moving barrier elements formed as turnstile leaves of the turnstile, or in a revolving door for moving the barrier elements, formed as revolving door leaves of the revolving door, or in a double-leaf swing door for moving the barrier elements, formed as door leaves of the swing door.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0058] Now, the disclosure is described in more detail based on an exemplary embodiment. In this case, it shows:

[0059] FIG. 1 a perspective of an inventive passageway device, formed as a tripod barrier, with the inventive gearing device according to an exemplary embodiment, and

[0060] FIG. 2 a detail of the inventive gearing device according to FIG. 1.

DETAILED DESCRIPTION OF THE DRAWINGS

[0061] In the following based on FIGS. 1 and 2 is explained a passageway device 40 formed as a tripod barrier. The passageway device 40 comprises a gearing device 1 for discontinuously moving two barrier elements 41, 42, herein formed as barrier stiles. In the following, unless otherwise stated, reference is always made to all the Figures.

[0062] For example, the passageway device 40 is passed in the passageway direction 100 indicated in FIG. 1. In this case, in passageway direction 100, the first barrier element 41 prevents the passing individual from passing, respectively when moving the first barrier element 41, the passing individual can follow said first barrier element 41 and thereby pass the passageway device 40. When passing the passageway device 40, the two barrier elements 41, 42 rotate about an output axis 22.

[0063] The gearing device 1 comprises a housing 2, which is diagrammatically illustrated in FIG. 2. A drive axis 3 is rotatably mobile supported in the housing 2. With a dashed line, FIG. 1 shows the imaginary extension of said drive axis 3. A pulley 5 is located coaxially on the drive axis 3.

[0064] Furthermore, the gearing device 1 comprises an electric motor 4, which drives a further pulley 5 rotating about a crank axis 60. The two pulleys 5 are drivingly connected to each other via a belt 6 so that, with rotating electric motor 4, also the drive axis 3 rotates.

[0065] Furthermore, the gearing device 1 includes a first active axis of rotation 8 and a second active axis of rotation 10. FIG. 1 shows the imaginary extension to said two active axes of rotation 8, 10 in a dashed illustration.

[0066] The drive axis 3 and the two active axes of rotation 8, 10 are offset and parallel to each other. Also, said three axes are parallel to the output axis 22.

[0067] A drive wheel 7, herein formed as a toothed drive wheel, is located on the drive axis 3. A first axis of rotation wheel, herein formed as a first axis of rotation toothed wheel, is located on the first active axis of rotation 8. A second axis of rotation wheel, herein formed as a second axis of rotation toothed wheel, is located on the second active axis of rotation 10.

[0068] The toothed drive wheel 7 is in engagement with the first axis of rotation wheel 9 and thereby forms a first gearing stage 12. Furthermore, the drive wheel 7 is in engagement with the second axis of rotation wheel 11 and thereby forms a second gearing stage 13.

[0069] A first idler wheel 14 is located coaxially and torque-proof on the first active axis of rotation 8. A second idler wheel 16 is located coaxially and torque-proof on the second active axis of rotation 10.

[0070] An output shaft 20 and a hollow output shaft 21 are provided coaxially to the output axis 22. The output shaft 20 is partially located in the hollow output shaft 21. The output shaft 20 is torque-proof connected to the second barrier element 42. The hollow output shaft 21 is torque-proof connected to the first barrier element 41. A first driven wheel 19 is placed on the hollow output shaft 21. A second driven wheel 18 is placed on the output shaft 20. Said two driven wheels 18, 19 are respectively torque-proof connected to the output shaft 20 or to the hollow output shaft 21 and are coaxially placed on the output axis 22.

[0071] The first idler wheel 14 is in engagement with the first driven wheel 19 and thereby forms a third gearing stage 15. The second idler wheel 16 is in engagement with the second driven wheel 18 and thereby forms a fourth gearing stage 17.

[0072] The third gearing stage 15 and the fourth gearing stage 17 realize a forced drive of the hollow output shaft 21 and the output shaft 20 and thus also of the two barrier elements 41, 42 during a rotation of the drive axis 3 or of the drive wheel 7.

[0073] Now, if an individual passes the barrier in passageway direction 100, based on the following described gearing device 1, initially the first barrier element 41 moves slowly and later fast, while the second barrier element 42 initially moves fast and later slowly. In this way, allowing for a better singularization, in that the trailing barrier element 42 initially moves fast and later slowly, so that another individual can hardly squeeze between the individual and the trailing barrier element 42.

[0074] FIG. 2 shows the gearing device 1, the drive wheel 7 between the two axis of rotation wheels 9, 11 in a top view. Accordingly, the two axis of rotation wheels 9, 11 have a respective rolling curve 30. The rolling curves 30 of said two axis of rotation wheels 9, 11 are congruent. The drive wheel 7 has a rolling curve 30′. The rolling curves 30 and 30′ of all three wheels are non-round.

[0075] With regard to the indicated symmetry axis 31, the axis of rotation wheels 9, 11 and the drive wheel 7 are formed symmetrically. The respective centre of rotation of the drive wheel 7, of the first axis of rotation wheel 9 or of the second axis of rotation wheel 11 is located on the associated symmetry axis 31.

[0076] The width 33 of the axis of rotation wheels 9, 11, or the width 33″ of the drive wheel 7 is defined vertically to the symmetry axis 31. A length 32 of the axis of rotation wheels 9, 11 or a length 32″ of the drive wheel 7 is defined parallel to the symmetry axis 31 and thus vertically to the width.

[0077] For the two axis of rotation wheels 9, 11, the length 32 is respectively greater than the width 33. For the drive wheel 7, the width 33″ is greater than the length 32″.

[0078] Furthermore, FIG. 2 shows a first effective radius r1 of the first axis of rotation wheel 9 and a second effective radius r2 of the second axis of rotation wheel 11, respectively measured from the centre of rotation to the contact point with the drive wheel 7. The drive wheel 7 has a drive radius rA to the contact point with the first axis of rotation wheel 9. The drive radius to the second axis of rotation wheel 11 is indicated with rA′.

[0079] Furthermore, it is provided that the individual effective radii r1, r2 as well as the drive radii rA, rA′ change during rotation of the gearing device 1, however, the sum of r1 and rA as well as the sum of r2 and rA′ remain constant during rotation.

[0080] Such formed gearing device shows a compact and reliable solution for discontinuously moving two forcibly connected elements.