The invention relates to a moving ramp intended e.g. for transportation of people, comprising plates supported by wheels, which are guided for movement at an upper level to form the loaded part of the moving ramp, and at a lower level which is substantially parallel with the upper level, to form the returning part of the moving ramp, adjacent plates in each part being close to each other, wherein stationary guides are provided as upper and lower runway tracks for the wheeled plates, the plates at the edges thereof are pivotally connected to endless chains at one end of the plates said chains extending along the parts to be driven in one direction in the upper part and in the opposite direction in the lower part, the other end of the plates being free for angular adjustment in cooperation with guides at the ends of the moving ramp to lower and raise, respectively, the plates by vertical displacement thereof in a substantially horizontal position one at the time from one part to the other. US-A-3 447 666 describes a moving ramp of this kind wherein the chains move in a substantially rec- tangular path, turning sprockets being provided at the four corners of the rectangle, and wherein a transition portion of each chain between the upper part and the lower part being utilized to transfer the end of the plates which is connected to the chain, from the upper part to the lower part, and vice versa. For the transfer of the free end of the plates there is provided at each end of the moving ramp endless auxiliary chains which are also guided

in a rectangular path over turning sprockets in the four corners of the rectangle, vertical transfer por¬ tions being provided in parallel with the transition portions to take care of the free end of the plates and transfer this end from the upper part to the lower part, and vice versa, the plates being guided for parallel movement.

In another prior art moving ramp according to US-A-2 893 538 wherein no endless chains are provided and wherein the plates are guided on upper and lower guide rails in the supporting and returning part, respectively, the plates are driven by means of gear wheels engaging racks on the plates in the upper part as well as the lower part. The plates are transferred between the parts at the two ends of the moving ramp by means of synchronously driven arms engaging the plates at the two ends thereof to transfer the plates by a parallel movement between the parts.

These prior art devices necessitate a large con- s ruction height in order that means provided for the transfer of the plates from one part to the other at the ends of the endless chains and for advancing the plates in the upper and lower parts will function in a satisfactory way.

If it is necessary to have the loaded part lo¬ cated substantially at the level of the supporting floor structure a substantial space must be provided below the loaded part to receive the returning part and the driving machinery, which means that the floor structure must form a "ditch" providing the necessary space.

The purpose of the invention is to provide a moving ramp of the kind referred to above which allows an extremely small construction height which may be less than 150 mm so that no modification at

all of the supporting floor structure is necessary and the moving ramp does not interfere with existing space below the floor structure due to the fact that the moving ramp can be disposed directly on the floor structure. By this arrangement the further advantage is achieved that the moving ramp can easily be re¬ located should this be necessary when the room or other premises where the moving ramp is located have to be remodelled.

The said purpose is achieved by the moving ramp of the kind referred to above having obtained the characterizing features of claim 1.

Embodiments of the invention will be described in more detail below reference being made to the ac- companying drawings in which

FIG 1 is a diagrammatic side view of an embodi¬ ment of the moving ramp according to the inven¬ tion,

FIG 2 is a fragmentary cross-sectional view along line II-II in FIG 1,

FIG 3 is a fragmentary cross-sectional view along line III-III in FIG 1,

FIG 4 is a fragmentary view similar to FIG 1 showing the moving ramp in another functional position,

FIG 5 is a plan view of the embodiment in FIG 1, FIG 6 is an enlarged fragmentary side view of the rotating guide element at the left-hand end of the moving ramp, FIG 7 is a view corresponding to FIG 6 and shows a press-down element cooperating with the plate, FIG 8 is a diagram showing the force distribu¬ tion in a chain at normal operation, FIG 9 is a corresponding diagram showing the force distribution in the chain in the novel

drive wheel arrangement, and

FIG 10 is a diagrammatic side view of a drive wheel device when the chain is driven according to FIG 9. The moving ramp comprises a number of plates 10 the upper side 11 of which forms the surface for car¬ rying goods or people to be transported on the moving ramp. Each plane has two wheels 12 rotatably mounted to the plate both wheel pairs having the same wheel track. At each end the plate is bevelled at the lower side thereof to form an inclined surface 13. Each plate is connected at the edges thereof at the shaft 12A of one wheel pair only to two endless drive chains 14 running over turning wheels 15 indicated diagrammatically only herein. The wheels are mounted in stationary bearing means. Two upper stationary supporting rails 16 extend in parallel with each other and with the upper parts of the endless chains mutually spaced horizontally a distance adjusted to the whee ^~ π-rack of the wheel pairs. In the same way two lower support rails 17 are provided along the lower parts of the endless chains in parallel with the upper support rails.

At the left end of the moving ramp two rotatable guides 20 are provided on a common drive shaft which - in case of drive chains driven to move the upper part of the moving ramp from the right to the left according to the arrow 21 - are driven in counter¬ clockwise direction by means of the drive chains 14. Said guides are shaped, located and position syn¬ chronized such that they can engage without jamming the trailing free wheel pair of the plate 10E which occasionally is being carried around the turning wheels 15 at the left end of the moving ramp at the leading wheel pair thereof so that the trailing end

of the plate as a consequence thereof will be posi¬ tively guided while moving from the upper part to the lower part where the guides will again disengage the wheels. At the right-hand end of the moving ramp corre¬ sponding rotating guides 22 are provided which are shaped in a corresponding manner as the guides 20 to receive the wheels at the free end of the plate. They are driven synchronously with the drive chains in counter-clockwise direction by means of auxiliary chains 14B to engage the plate at the right-hand free end thereof and raise the plate when it shall be transferred from the lower part to the upper part of the moving ramp so that the plate also at the right- hand end thereof will be positively guided during this movement.

In the upper support rails gaps 23 must be pro¬ vided to allow the movement of the wheel pair con¬ nected to the drive chains, upwards onto and down- wards from, respectively, the upper support rails. In order that the wheels at the trailing end of the plate at the right-hand end of the moving ramp and the leading end of the plate at the left-hand end of the moving ramp can pass over this gap when the plates are moving to the left in -the upper part of the moving ramp a rotatably mounted support roller 24 is provided to support the plate by engaging the lower side thereof when the plates are passing over the gaps 23 so that the plates are prevented from falling down into the gaps.

FIG 6 discloses in more detail how the guide 20 should be constructed. The path to be described by the centre of the wheel 12 on the plate 10E at the transfer from the upper part to the lower part of the moving ramp is a circle 25 having the centre 0, .

However, the guide 20 should rotate about a centre 0 ₂ which is displaced to the left upwards, the angle and the distance c being related to the radius r of the wheel 12 and the radius R of the path 25 according to the relationship c > R sin α and _.

2(R - r) c <

1 + sin wherein a > 0 and α preferably is great because lower normal forces in the mechanism are obtained as a consequence thereof. The guide surface 25 of the guide 20 should be semicircular and it can be ar- ranged to engage the wheel 12 proper but it can also be arranged to engage a specific engagement wheel provided on the wheel shaft, such as a ball bearing, having a smaller diameter than the wheel, and in that case it is of course the radius of this specific guide wheel which is the radius r in the above rela¬ tionship.

When the .moving ramp is driven at high speed the mass forces will have such influence on the plates that these will disengage the guide 20. In order to eliminate this disadvantage a press-down cam 27 is provided, FIGS 1 and 7, located on a wheel 27' the circumference of which should be as large as the pitch of the plates. This means that the press-down wheel will rotate one revolution for each plate. The press-down wheel rotates in clockwise direction about the centre 0.,. However, the plate must be pressed down during about 1/6 only of a revlution of the press-down wheel from the moment when the guide 20 has just engaged the wheel of the trailing end of the plate. The contour of the press-down cam should be

shaped in view hereof. The wheel should not unneces¬ sarily engage the plate because in that case the wheel may interfere with the guide 20. Preferabaly, the press-down cam is coated with a soft material (rubber or polyurethane) .

The guide 22 at the right-hand end of the moving ramp can be shaped in a similar manner as shown in FIG 6 but in this case it is not necessary to provide a press-down cam because the wheel 12 is guided by the guide rail ^' 17.

At the ends of the moving ramp where the pro¬ cedure of transferring the plates from one part to the other takes place the moving ramp should be covered by an approach ramp 28 on which goods or per- sons pass onto and out from the upper load carrying part of the moving ramp.

Due to the manner in which the plates are con¬ nected to the drive chains and are guided for trans¬ fer from one part to the other of ^' the moving ramp the distance between the parts can be kept very small so that an extremely low construction height can be im¬ parted to the .moving ramp said height being below about 150 mm. This means that the moving ramp can be disposed on a supporting basement having flat upper side, and accordingly it is not necessary to have this basement shaped in a specific manner to provide space for the drive and turning machinery and for the returning lower part of the moving ramp. By this location of the moving ramp it is also possible that the ramp can be relocated in a simple manner from one place to the other.

It is not necessary that the moving ramp extends horizontally; it can also be inclined from one end to the other up to 10 a 12°.

As will be easily realized the rotating guides

20 and 22 and the support rollers 24 will function in the same manner as described above but reversely in case the drive direction of the moving ramp is re¬ versed so that the upper part of the moving ramp is driven in a direction opposite to the arrow 21.

If the moving ramp is driven by the sprocket wheels at one end of- the moving ramp being connected to a drive motor the force distribution in the upper part of the chains, which drives the plate in the upper loaded part of the moving ramp will be obtained as shown in FIG 8 wherein the greatest stress is de¬ signated F and will be obtained at the driven sprocket wheel, the right-hand wheel in FIG 8. This stress can be considerable and necessitates heavy drive chains to be provided. Such chains have a large pitch and require large sprocket wheels because the number of teeth of the sprocket wheels cannot be lower than a predetermined minimum number of teeth due to the so-called polygon effect and poor engage- ent between the chain and the sprocket wheel. How¬ ever, large sprocket wheels require a great construc¬ tion height of the moving ramp which is contrary to the purpose of the invention.

In order to overcome this drawback several drive stations therefore are provided along the upper part of the drive chain said stations being distributed along said part and each comprising for example an electric motor, a gear and a sprocket wheel. For very long moving ramps it may be necessary to provide cor- responding drive stations also for the lower part of the drive chains. This embodiment is shown diagram- matically in FIG 9 wherein also the stress distribu¬ tion in the chain is illustrated. If n drive stations are provided there will be obtained at a load cor- responding to that in FIG 8 a maximum stress in the

chain, which is about F/n. In this way the dimension¬ ing of the drive chains will be independent of the length of the moving ramp and it is possible to main¬ tain a weak chain and thus small turning wheels for all lengths of the moving ramp.

An embodiment of a drive station for the ar ^¬ rangement according to FIG 9 is shown in FIG 10. A larger chain sprocket 29 is drivingly engaging the upper part as well as the lower part of the drive chain 14 and shall be connected over a gear to an electric drive motor. The upper part is kept in en ^¬ gagement with the sprocket wheel by means of a holding-on wheel 20 while a slide bearing 31 can pro¬ vide the necessary holding-on of the lower part. In the same way as a distribution of the stresses in the drive chains is obtained in an ar¬ rangement having several drive stations as described above, the acceleration and breaking forces will be distributed over the length of the drive chains. The drive stations can be made rather small so that they can be built into the balustrades commonly arranged one at each side of the moving ramp.

At the ends of the moving ramp the plates when being transferred from one part to the other will move against each other due to the fact that the end connected to the chains will describe a circular movement (with the radius R) . If the ends were straight a large initial spacing between the plates would be necessary which is unsuitable from the security point of view considering the risk of people being caught. By this plates being bevelled at 13, FIG 1, the initial spacing between the plates can be reduced considerably. If the spacing is designated

S _Q and the height of adjacent surfaces of the plates is designated h the following relationship can

be established:

S _Q

If R = 32 mm and h = 32 mm there will be obtained

S _n - 6 mm while in the case of h being instead 10

> mm (bevelled plate) S _n . -=■! mm.

In a known manner the plates can form inter- engaging teeth or fingers at the ends thereof.