WO1992000904A1

WO1992000904A1 - Device for shifting loads and forces

Info

Publication number: WO1992000904A1
Application number: PCT/CH1991/000147
Authority: WO
Inventors: Georg Hirmann
Original assignee: Georg Hirmann
Priority date: 1990-07-10
Filing date: 1991-07-09
Publication date: 1992-01-23

Abstract

The invention relates to means for increasing the efficiency in shifting loads in accordance with the sliding stage basis described in European patent No. 0 155 235, e.g. by converting in the movement stage from surface to rolling friction. Fig. 2 shows a device similar to that of Fig. 1 in which the force (21) acting in an inclined manner against the load is supplemented by two forces (22 and 23) acting on the load (20) via rollers (24, 25). The simultaneous action of the forces (21, 22, 23) reduces the floor friction beneath the load during the forward movement. Thus the load-guiding diagonal line is shifted in direction (26) and the floor frictional resistance is reduced to a fraction of that in the sliding stage of Fig. 1.

Description

Device for moving loads and forces

The subject of the invention is a means of increasing the efficiency when shifting the loads in accordance with the principle of the sliding step set out in European Patent No. 0 155 235.

The sliding step occurs in which a low-friction force, which acts perpendicularly with respect to this plane, is acted on a plane inclined to the guideway of the load in such a way that a force parallel to a guideway and a guideway relieving force component arises, whereby the frictional resistance on the guideway during the action of the above-mentioned force drops to a fraction of the frictional resistance present in the rest position.

An important feature of the load shift via the sliding step is the clocked binary movement, which results from movement and standstill when switching off the energy, a standstill of the load with precisely calculable positioning accuracy. This possibility also exists in the case of a continuous sliding step, which can result from the switching of two sliding step systems activated in push-pull.

The illustrations show three ways to reduce the frictional resistance on the load guideway even more during load shifting, as a result of which the energy requirement can be reduced to a further fraction, namely: by switching over from surface static friction to the movement phase

Rolling friction (Fig. 2, 3, 4), by step translation by rolling (Fig. 5, 6, 7) by relative movement on two wedge tracks (Fig. 12-15). The shifting of loads and forces with the "active wedge", as Fig. 1 shows is already state of the art.

The force 4 acting on the - preferably - rolling bearing 1, on the wedge flank 3 inclined with respect to the horizontal floor plane 2, is divided into a load-lifting 5 and a load-displacing 6 force component.

After the angle 7 of the active wedge 8 is chosen so that the coefficient of friction at the bearing point 1 is smaller than the tangent of the wedge angle 7, the bevel gear is not self-locking at this point, i. H. the load 8 can not be lifted in the position shown, but only moved. The force 4 required to achieve the equivalence of the frictional resistance on the horizontal floor level, the force 4 must reach a certain size.

For the graphic determination of the necessary force 4, the weight is applied proportionally through the center of gravity, the size of which corresponds to the equal sum of the forces 5 and 9 = L in the representation. The friction resistance 10 (L ■ M _D ) for the rest position and the vector diagram corresponding to the load are also plotted. The side length 11 gives the maximum size of the thrust component.

To determine the beginning of the push, the load is divided by the diagonal connection 12 into a 9 remaining as a floor load and into a 5 component carried by the active wedge. The vector diagram belonging to the force component 5 gives the force necessary for the equivalence of the thrust and resistance forces. F ₄ = _____

COS d <

In order to overcome the restoring force 13, the spring 14, 14 can additionally be added horizontally and projected onto 4. This increases the necessary

Magnitude of the force 4. F4 = F55. _ + ^{F 3} . ^cos θ (si öt ' Another slight increase in F overcomes the frictional resistance at bearing 1. The remaining thrust component 14 causes the load to be shifted and gives its maximum size for accelerating the load.

(The described "sliding step" phenomenon was first taught by the inventor in Germany at a university of applied sciences.)

The present innovation aims to further increase the technical and economic efficiency of the use of the "active wedge" for shifting loads and forces.

Such wedge thrust drives can be on the bottom side like 1 and the other Dar ^¬ settings are applied on the load side show or.

Fig. 2 shows a FIG. 1 similar device, in which two forces 22 and 23 additionally act against the load 20 via rollers 24, 25 for the force 21 acting inclinedly against the load. The simultaneous action of the forces 21, 22, 23 reduces the ground friction under the load during the feed. As a result, the load-conducting diagonal line is shifted in direction 26 and the floor friction resists the sliding step according to FIG. 1, reduced to a fraction of that.

Fig. 3 shows a device according to FIG. 2, in which, for example, the rollers 31, 32 and the roller 47 which moves the active wedge act simultaneously against the load by means of a hose cell 30 and gradually move it in the direction 33. Fig. 4 shows the displacement of a rod-shaped body 40 in the rest position, which is pressed onto the guide surfaces 44 by spring 41, via rollers 42, 43. The feed part of the device corresponds to Fig. 3 with the difference that the load cells for the rollers 45, 46 and for the active wedge can be controlled separately.

Fig. 5 shows a device for shifting the load 50, consisting of two rollers (rollers) guided over swivel arms 51, 52, which are supported with the larger diameter during feed against the load and with their smaller diameter on the guide surface of the active Keils 55 abut.

As an example of a reversible direction of movement, the active wedge held between centering springs 56 and 57 is provided with opposite wedge surfaces 58, 59. The direction of movement can be changed by the relative displacement of the wedge vertex relative to the role of the load cell 61.

6 shows a drive device of a similar function, in which the friction rollers 66, 67 and the drive roller 68, which are fixed to the shaft 65, are guided to the bearing axis 69 via the swivel arms 70, 71 and are driven via the active wedge 72. The active wedge is only shown symbolically here.

Such devices are mainly used to accelerate superimposed loads or moving objects.

FIG. 7 shows an application form of the drive principle of FIG. 6, for example for packet sorting switches operated by hand or by foot.

8 shows the direct tangential drive of a wheel 80 via the active wedge. Fig. 8 shows an active wedge 92 moved via push rod 90 and support surface 91, which moves load 94 in direction 95 when a force acts on the push rod. The coaxially arranged rollers 96 are in contact with suitable recesses either on the active wedge or on the support surface. Rollers can be pressed against the load in a similar way.

FIG. 9 shows a conveyor device assembled from a plurality of conveyor tracks 100, 101, 102, 103. The inner structure of the individual conveyor tracks consists of a multiple arrangement of sliding step elements as shown in FIG. 1.

A special property of the sliding-step conveyor tracks is that they can also move loads that are tensioned on the loading surface, provided that the fastening means have a slight extensibility. Conveyor tracks n l 04, 105 are installed in opposite directions to the load-moving conveyor tracks for the synchronous movement of the clamping elements.

FIG. 9 shows a load lashed to the fixed parts of the conveying surface 106, by means of belts 107, 108 and tensioning elements 109, 110, which load can be moved step by step in the predetermined direction when all the conveying tracks move synchronously.

10 shows an exemplary embodiment for loading and unloading flight luggage. About a fig. 10 similar conveying surface 120, a movable load support wall 121 is tensioned here and, as in FIG. 10 moves described. Inclined conveying surfaces 122 can be installed to guide the luggage, (only shown on one side)

In order to avoid any malfunctions due to the irregular shape of the luggage support surfaces, an additional support belt 123, support plate 124, as well as individual plates or pallets, can be placed on the conveyor surface and moved with it. In order to further simplify loading and unloading of the luggage, a loading device compatible with the in-flight conveyors can be used.

11 shows such a loading device 125 with the marking 126. If the loading basket 127 is in a position which corresponds to the internal conveyor tracks 128, 129, the luggage can be unloaded or taken over step by step.

The loading basket can be provided as a simple carrier element as a collecting container or container. In such a case, the laterally arranged conveyor tracks can be dispensed with.

Fig. 12 shows a load feed device actuated by means of pulling element 140, in which a movement in direction 141, the rollers 143 and 144 thus coupled via axis 142, pulling up via the support track 145, a force 148 acting via rollers 146, 147 on the lower running surface of the Exercise active wedge 149 and, by virtue of their action, shift load 150 in direction 151 using the sliding step method. The return of the moving parts to the starting position is not shown. The tension element 140 can be operated either selectively or simultaneously by a lever system, foot pedal, cable (Bowden cable), hydraulic or pneumatic working cylinder. The exemplary embodiment shown is recommended for reloading flight containers from the container dolly (without its own drive system) to the driven rollers of a transporter with a towing hook 152 moved by the transporter, for example hydraulically.

Similar devices can in principle be built in any length due to the multiple arrangement of the device shown, on a common tension element.

Due to the symmetrical arrangement of the support surfaces, a reversible device can be constructed. Fig. 13 shows an overall view of the container handling system according to FIG. 12 in a symbolic representation. The mutually arranged load feed devices 160 and 161 can be seen, of which the device facing the transporter 163 is always used. Also visible is the pull hook 164, which is attached to the dolly edge after the start and is actuated in pulses.

The single slide is shown in Fig. 14 shown. In the resting initial phase, the load 172 resting on the slideway 171 lies above the slide 173 designed as an active wedge, which is guided by rollers 174 and 175 in the quill-like guide 176 of the slideway, with a vertical clearance such that it rests in the rest position Load not touched. The carriage is also tensioned by spring 179 against stop 180. The feed step is carried out by the force 182 acting, for example, via tension rod 181, which allows the roller 186 to roll up from the preferably coaxially arranged rollers 185, 186, 187, over the supporting wedge 188, whereby the rollers 185 and 187 first against the slide 173 and subsequently against the load 172 is tensioned and when the tension rod 181 is moved further, the load with reduced ground friction against spring 179 is shifted in the direction of 190 using the already known sliding step method.

The tension rod is then returned to the starting position, with the carriage 173 also returning to the starting position by spring force.

In order that the feed movement of the slide can be switched independently of the clock movement of the push rod, the support wedge can be articulated via axis 192 and supported by, for example, rocker-shaped stop 193. The stop can be released before the start of the feed cycle. When the stop is released, the support wedge moves down and the load advance cannot take place despite the push rod movement. Find. The support wedge is reset by the spring 196 against the stop 197, after which the stop 193 can be pivoted in again or is automatically pivoted in by the spring 198.

Such switching devices are used in particular in the multiple arrangement of the feed chiitten, as shown in FIG. 15. The illustration shows a modular accumulation conveyor track which enables loads to be added irregularly with a space in between. In order to activate the following sledges after the empty spaces, the above-described, for example rocker-like stops are designed here as sensors 200, 201. The picture shows the carriage 203 activated by the empty space 202, furthermore the carriage 204 passivated by the pressed-down sensor 201. The load 206 is pushed forward during the subsequent cycle of the push rod 205, which is only indicated here. Electrical control of a stop 207 can be carried out, for example, via Solenoid 208 take place.

The push or push rod can be moved in other ways, such as a working cylinder, magnet, hand lever or foot pedal.

A style-conforming type of push rod movement is indicated by an active wedge actuation 209.

The figures show:

Fig. 1 Moving loads and forces with the "active wedge".

Fig. 2 device in which to act inclined against the load, two additional forces act via rollers against the load.

Fig. 3 A device in which the rollers and the active wedge act against the load simultaneously through a hose cell.

Fig. 4 The displacement of a rod-shaped body.

Fig. 5 A device for shifting the load, rollers (rollers) guided over swivel arms.

Fig. 6 drive device similar function.

Fig. 7 Application form of the drive principle.

Fig. 8 An active wedge moved over the push rod and support surface.

Fig. 9 A conveyor with multiple conveyor tracks.

Fir. 10 A conveyor with mutually arranged conveyor tracks.

Fig. 11 A flight luggage loading device.

Fig. 12 An active wedge moved over the tension element and support surface.

Fig. 13 A container transfer system.

Fig. 14 A single sled.

Fig. 15 A modular accumulation conveyor.

Claims

1. Device for shifting loads and forces predominantly using the active wedge, characterized by additional means which increase the technical efficiency of such systems.

(Fig. 2 - 14)

2. Device for moving loads and forces according to claim 1, characterized by controlled support rollers.

(Fig. 2, 3, 4)

3. Device for shifting loads and forces according to at least one of the preceding claims, characterized by translation rollers between active wedge and part of the load to be driven. (Fig. 5, 6, 77

4. Device for shifting loads and forces according to at least one of the preceding claims, characterized by conveyor tracks arranged in opposite directions with respect to the load-carrying conveyor tracks, in order to move the feed of loads clamped over them or loading aids such as partition.

(Fig. 9, 10)

5. Apparatus for shifting load and force according to at least ^"to be able to promote any of the preceding claims, characterized by guided over the conveying path elastic or rigid liners. To loads with non-planar bearing ^surfaces'. (Fig. 10)

6. Device for shifting loads and forces according to at least one of the preceding claims, characterized by conveyor-compatible loading devices.

(Fig. 11)

7. Device for shifting loads and forces according to at least one of the preceding claims, characterized by a tension element whose load sliding track parallel movement via a support track inclined to the direction of movement, moving and thus coaxially coupled rollers via an active wedge, the sliding step movement of the load. (Fig. 12)

8. Clock-controlled and driven by a rail-parallel force sliding step conveyor track according to claim 1, characterized by at least one support wedge that can be switched on and off.

(188)

9. Clock-controlled conveyor track according to claims 1 and 8, gekennzeich¬ net by sensor-like support wedge stops.

(200, 201)

10. Clock-controlled conveyor track according to claims 1, 8 and 9, marked by mechanically, electrically or pneumatically controlled support wedge stops. (201, 208)