GB2511826A

GB2511826A - Cover system

Info

Publication number: GB2511826A
Application number: GB201304652A
Authority: GB
Inventors: Carl Justin Holroyd
Original assignee: Oldbury UK Ltd
Current assignee: Oldbury UK Ltd
Priority date: 2013-03-14
Filing date: 2013-03-14
Publication date: 2014-09-17
Also published as: GB201304652D0

Abstract

A cover system for a vehicle having an open-topped container, for example a skip (5, Figure 1), comprises a pair of swinging arms 13 mountable on either side of the vehicle to move between stowed and deployed positions to extend a flexible cover 11 over the top of the container. Cover 11 may be extended or retracted, for example by unwinding and rewinding, in response to movement of swinging arms 13. During deployment, swinging arms 13 are relatively moveable, for example using a mechanism comprising undulating cams (39, 41, Figure 5) with alternating peaks (43, Figure 5) and troughs (45, Figure 5), to change the spacing between them. For example, arms 13 may be at a minimum spacing when stowed and deployed and at a maximum spacing at an intermediate position; this may provide increased clearance for the container when deploying cover 11.

Description

I

COVER SYSTEM

This invention relates to a cover system. The invention has particular application to a cover system for use with vehicles provided with an open-topped container for transporting a load.

The invention seeks to provide a cover system that can be fitted to a vehicle within the overall dimensions of the vehicle and which can be deployed to cover an open-topped container while transporting a load within the container to prevent loss of the load.

According to the present invention we provide a cover system for a vehicle having an open-topped container, the cover system having a pair of swinging arm assemblies adapted to be mounted on either side of the vehicle, and a cover assembly, wherein the swinging arm assemblies are movable from a stowed position to a deployed position to extend a flexible cover of the cover assembly over the top of the container, and wherein the swinging arm assemblies are relatively moveable to change the spacing between the swinging arm assemblies during movement from the stowed position to the deployed position.

It may be that the spacing between the swinging arm assemblies is a minimum in at least one and preferably in both of the stowed position and the deployed position.

It may be that the spacing between the swinging arm assemblies is a maximum between the stowed position and the deployed position.

It may be that the spacing increases from the minimum to the maximum and then returns to the minimum as the swinging arm assemblies move from the stowed position to the deployed position and vice versa.

It may be that the maximum spacing is provided at an intermediate position between the stowed position and the deployed position to provide increase dearance relative to the container or a loading system for the container.

It may be that the swinging arm assemblies are mounted on the vehicle for pivotal movement about a pivot axis between the stowed position and the deployed position and for relative movement parallel to the pivot axis to change the spacing thcrcbctwccn.

It may be that a cam mechanism is provided for changing the spacing between the swinging arm assemblies in response to pivotal movement between the stowed position and the deployed position.

It may be that the cam mechanism includes a fixed cam member on the vehicle and a cam member on the swinging arm assembly that is rotatable relative to the fixed cam member in response to pivotal movement of the swinging arm assembly.

It may be that the cam members have opposed cam faces profiled to move the swinging arm assembly parallel to the pivot axis in response to pivotal movement of the swinging arm assembly.

It may bc that thc cam mcmbcrs arc cngagcablc under a biasing forcc, for example a spring, operable to maintain engagement between the cam members while allowing the swinging arm assembly to move parallel to the pivot axis during pivotal movement of the swinging arm assembly between the stowed position and the deployed position.

It may be that the cover assembly extends between the swinging arm assemblies and the cover is extendible from and retracted into the cover assemble in response to movement of the swinging arm assemblies to and from the deployed position.

The invention will now be described in more detail by way of example only with reference to the accompanying drawings, wherein: Figure 1 is a perspective view of part of a vehicle fitted with a cover system embodying the invention with the load cover system stowed; Figure 2 is a perspective view similar to Figure 1 with the cover system deployed; Figure 3 is a perspective view of the load bed with parts removed showing the cover system stowed; Figure 4 is a side view of the load bed with parts removed showing the cover systcm deploycd; Figure 5 shows a coupling mechanism on one side of the cover system in the stowed position; Figure 6 is a perspective view of the coupling mechanism of Figure 5 in the stowed position; Figure 7 shows the coupling mechanism of Figure 5 in an intermediate position between thc stowcd position and the deployed position; Figure 8 is a perspective view of the coupling mechanism of Figure 7 in the intermediate position; Figure 9 shows the coupling mechanism of Figure 5 in the deployed position; and Figure 10 is a perspective view of the coupling mechanism of Figure 9 in the deployed position.

Referring first to Figures 1 to 4 of the drawings there is shown part of a vehicle having a chassis I supporting a load bed 3 on which a skip 5 (or similar open-topped container) is shown in Figures 1 and 2. The vehicle has a conventional mechanism for picking up and setting down the skip S by means of a pair of loading arms 7 and chains 9. Such mechanisms are well known to those skilled in the art and are not described further.

The vehicle also has a cover system for movement from a stowed position shown in Figures 1 and 3 to a deployed position shown in Figures 2 and 4 to extend over the open top of the skip S so as to retain the contents of the skip 5 therein during transportation to a site for unloading the skip 5.

The cover system includes a roller assembly 11 extending transversely between two swinging arm assemblies 13 positioned on opposite sides of the load bed 3 outboard of the skip loading arms 7. The roller assembly 11 includes a roller bar 15 on which a flexible cover 17 is wound. The cover 17 may be a length of sheeting or netting or other material capable retaining the contents of the skip S therein.

In the stowed position shown in Figures 1 and 3, the roller assembly 11 is positioned in an elevated cradle 19 at the front end of the load bed 3 from where it can be moved to extend the cover 17 over the open top of the skip 5.

The swinging arm assemblies 13 are similar and are pivotally mounted at one end on the chassis with the roller assembly II rotatably supported at the other end. Each swinging arm assembly 13 includes a short drive arm 21 mounted intermediate the ends for pivotal movement about a horizontal pivot axis PA coaxially aligned with thc pivot axis of the drivc arm 21 on the opposite side of the load bed 3.

A hydraulic or pneumatic piston/cylinder unit 23 extends between the chassis 1 and one end of the drive arm 21. The other end of the drive arm 21 is rigidly connected to one end of an elongate link arm 25. The other end of the link arm 25 is rigidly attached to a bracket 27.

A cranked support arm 29 is pivotally connected at one end to the bracket 27 and rotatably supports the roller assembly 11 at the other end.

A hydraulic or pneumatic piston/cylinder unit 31 extends between the bracket 27 and a position intermediate the ends of the support arm 29.

In the stowed position, the swinging arm assemblies 13 are positioned so that the link arms 25 extend generally horizontally on each side of the load bed 3 towards the front end and the cranked support arms 29 extend upwards at the front end to locate the roller assembly 11 in the cradle 19.

To extend the cover 11 over the top of the skip 5, the piston/cylinder units 23 attached to the drive arms 21 on both sides of the load bed 3 are extended to rotate the drive arms 21 about the horizontal axis PA to raise the link arms 25 which in turn raise the support arms 29 to lift the roller assembly 11 off the cradle 19.

As thc drive arms 21 rotate, the roller assembly 11 moves in an arc towards the rear of the vehicle and is raised above aild passes over the top of the loading arms 7 before being lowered to extend down behind the skip 5 in the deploycd position shown in Figurcs 2 and 4.

The cover 17 unwinds from the roller bar 15 as the roller assembly 11 moves from the stowed position to the deployed position. The width of the cover 17 is such that it passes between the loading arms 7 over the top of the skip 5 and preferably overhangs the sides of the skip 5. A tensioning mcchanism (not shown) may be providcd to hold the cover 17 taut when it is deployed. If necessary the piston/cylinder units 31 can be extended to pivot the support arms 29 to move the roller assembly 11 towards the rear of thc skip 5 to position thc cover 17 to engage the rcar end of the skip 5.

The cover system is returned to the stowed position by reversing the above-described operation. In a modification (not shown), the roller assembly may be attached to the chassis and the cover attached to the swinging arm assemblies so as to unwind from and rewind on the roller assembly as the swinging arm assemblies move to the deployed position and return to the stowed position.

Referring now to Figures 5 to 10 of the drawings, a coupling mechanism for pivotally mounting one of the swinging arm assemblies 13 is shown, it being understood that a similar coupling mechanism is employed for pivotally mounting the other swinging arm assembly.

As shown, the drive arm 21 is rotatably mounted on a stub axle 33 for pivotal movement mounted the pivot axis PA. The stub axle 33 is mounted on the chassis I by means of a bracket 35 at one end of the axle 33 on the onboard side of the drive arm 21. The drive arm 21 is biased towards the bracket 35 by a spring 37, for example a compression spring, that surrounds the axle 33 on the outboard side of the drive arm 21 and extends between the other end of the axle 33 and the drive arm 21.

The axle 33 is provided with a cam member 39 and the drive arm 21 is provided with a cam member 41 opposed to the cam member 39. The cam member 39 is fixed and the cam member 41 is rotatable with the drive arm 21 as the drive arm 21 rotates on the axle 33 to move the swinging arm assembly 13 from the stowed position to the deployed position.

The spring 37 biases the drive arm 21 to maintain contact between the cam members 39, 41 and the opposed end faces 39a, 41a of the cam members 39, 41 are profiled to cause the drive arm 21 to move in a direction parallel to the pivot axis PA as it rotates to change the spacing between the swinging arm assemblies 13 during movement from the stowed position to the deployed position and during the reverse movement from the deployed position to the stowed position. In this embodiment, the opposed end faces 39a, 41a of the cam members 39, 41 have an undulating form generally in the shape of a sinusoidal wave having alternating peaks 43 and troughs 45. Other profiles may be employed according to requirements.

The drive arm 21 extends through an elongate slot 47 in the chassis I and Figures 5 and 6 show the cam members 39, 41 in the stowed position of the swinging arm assembly 13 in which the drive arm 21 is in its innermost or inboard position adjacent to one side of the slot 47 such that the spacing bctwecn the swinging arm assemblics 13 on opposite sides of the chassis 1 is a minimum. In this position, the peaks 43 of each cam member 39, 41 engage the troughs 45 of the other cam member 39, 41.

The engagement of the peaks 43 and troughs 45 in this position under the biasing of the spring 37 may assist to maintain the swinging arm assembly 13 in the stowed position.

On rotation of the drive arm 21 to move the swinging arm assembly 13 from the stowed position, the cam member 41 rotates relative to the cam member 39 about the pivot axis PA and the peaks 43 of the cam member 41 ride up the angled faces of the troughs 45 of the cam member 39 causing the cam member 41 move outwards in a direction parallel to the pivot axis to compress the spring 37 and increase the spacing between the swinging arm assemblies 13 on opposite sides of the load bed 3.

Figures 7 and S show the cam members 39, 41 in an intermediate position of the swinging arm assembly 13 in which the drive arm 21 is in its outermost or outboard position adjacent to the other side of the slot 47 such that the spacing between the swinging arms assemblies 13 on opposite sides of the chassis I is a maximum. In this position, the peaks 43 of each cam member 39, 41 engage the peaks 39 of the other cam member 39, 41. The peaks 43 have rounded tips. With this arrangement the maximum spacing is provided over a limited range of pivotal movemcnt. This may not be essential and the tips may be flat or otherwise configured to increase the range of pivotal movement with maximum spacing.

On continued rotation of the drive arm 21 to move the swinging arm assembly 13 from the intermediate position, the cam member 41 rotates relative to the cam member 39 about the pivot axis PA and the peaks 43 of the cam member 41 ride down the angled faces of the troughs 45 of the cam member 39 under the biasing of the spring 37 causing the cam member 41 move inwards in a direction parallel to the pivot axis to reduce the spacing between the swinging arm assemblies 13 on opposite sides of the load bed 3.

Figures 9 and 10 show the cam members 39, 41 in the deployed position of the swinging arm assembly 13 in which the drive arm 21 is again in its inncrmost or inboard position and the spacing between the swinging arm assemblies 13 on opposite sides of the chassis 1 is again a minimum. In this position, the peaks 43 of each earn member 39, 41 engage the troughs of the other cam member 39, 41. The engagement of the peaks 43 and troughs 45 in this position under the biasing of the spring 37 may assist to maintain the swinging arm assembly 13 in the deployed position.

Reversing the above operation returns the swinging arm assemblies 13 to the stowed position.

The profile of the end faces 39a, 41a of the cam members 39, 41 is chosen such that the maximurn spacing between the swinging arm assemblies 13 on opposite sides of the chassis I coincides with movement of the swinging arm assemblies 13 past the loading arms 7 and the minimum spacing between the swinging arm assemblies 13 on opposite sides of the chassis 1 coincides with the stowed and deployed positions of the swinging arm assemblies 13. The roller assembly 11 may be telescopic to accommodate changes in the spacing of the swinging arm assemblies 13.

Alternatively, the change in spacing may be accommodated by the swinging arm assemblies flexing or bending.

Increasing and then decreasing the spacing between the swinging arm assemblies 13 as they move from the stowed position to the deployed position and back again has the advantage that the swinging arm asscmblics 13 can bc locatcd with minimum spacing in both thc stowed and deployed positions and the spacing increased during movement to and from stowed and deployed positions to provide increased clearance and reduce the risk of the swinging arm assemblies 13 coming into contact with the loading arms 7. By having the minimum spacing between the swinging arm assemblies 13 in both the stowed and deployed positions, the assemblies 13 can be installed within the overall width of the vehicle both when installing the cover system on new vehicles and when retro-fitting the cover system to existing vehicles.

Although the invention has been described for use of the cover system on a skip loading vehicle to provide a cover that extends over the top of a skip, it will be understood that the invention has wider application to vehicles having any type of open-topped container where it is desired to covcr the open upper face of the container when transporting a load to retain the load within the container. The container may be permanently attached to the vehicle such as a tipper truck or it may be detachable such as a skip.

It will also be understood that various modifications and changes can be made to the embodiment above-described within the scope of the invention. For example, the profile of the opposed cam faces of the cam members may be chosen to provide any desired range of movement of the drive arms to alter the spacing between the swinging arm assemblies. The cam faces maybe profiled to increase the spacing and maintain the increased spacing for part of the pivotal movement before reducing the spacing. The cam faces may be profiled to provide an increased spacing at any position between the stowed position and the deployed position requiring increased clearance for the swinging arms assemblies to pass freely through without risk of contacting the container or vehicle. While a cam mechanism has been described for changing the spacing between the swinging arm assemblies, it will be understood that any other suitable mechanism for changing the pacing in response to pivotal movement of the swinging arm assemblies may be employed. Thus a screw thread mechanism may be employed in place of the cam mechanism.

Claims

CLAIMS1. A cover system for a vehicle having an open-topped container, the cover system having a pair of swinging arm assemblies adapted to be mounted on either side of the vehicle, and a cover assembly, wherein the swinging arm assemblies are movable from a stowed position to a deployed position to extend a flexible cover of the cover assembly over the top of the container, and wherein the swinging arm assemblies are relatively moveable to change the spacing between the swinging arm assemblies during movement from the stowed position to the deployed position.
2. The cover system of claim 1 wherein the spacing between the swinging arm assemblies is a minimum in at least one of the stowed position and the deployed position.
3. The cover system of claim 2 wherein the spacing between the swinging arm assemblies is a minimum in both the stowed position and the deployed position.
4. The cover system of claim 2 or claim 3 wherein the spacing between the swinging arm assemblies is a maximum between the stowed position and the deployed position.
5. The cover system of claim 4 wherein the spacing increases from the minimum to the maximum and then returns to the minimum as the swinging arm assemblies move from the stowed position to the deployed position and vice versa.
6. The cover system of claim 4 or claim 5 wherein the maximum spacing is provided at an intermediate position between the stowed position and the deployed position to provide increased clearance relative to the container or a loading system for the container.
7. The cover system according to any preceding claim wherein the swinging arm assemblies are mounted on the vehicle for pivotal movement about a pivot axis between the stowed position and the deployed position and for relative movement parallel to the pivot axis to change the spacing therebetween.
8. The cover mechanism according to claim 7 wherein a cam mechanism is provided for changing the spacing between the swinging arm assemblies in response to pivotal movement between the stowed position and the deployed position.
9. The cover system of claim 8 wherein the cam mechanism includes a fixed cam member on the vehicle and a cam member on the swinging arm assembly that is rotatable relative to the fixed cam member in response to pivotal movement of the swinging arm assembly.
10. The cover system of claim 9 wherein the cam members have opposed cam faces profiled to move the swinging arm assembly parallel to the pivot axis in response to pivotal movement of the swinging arm assembly.
11. The cover system of claim 10 wherein the cam faces have an undulating form with alternating peaks and troughs.
12. The cover system of claim 11 wherein a minimum spacing of the swinging arm assemblies is provided when the peaks of each cam face engage the troughs of the opposed cam face.
13. The cover system of claim 12 wherein the peaks of each cam face engage the troughs of the opposed cam face in the stowed position and deployed position of the cover system.
14. The cover system of any of claims 11 to 13 wherein a maximum spacing of the swinging arm assemblies is provided when the peaks of each cam face engage the peaks of the opposed cam face.
15. The cover system of claim 14 wherein the peaks of each cam face engage the peaks of the opposed cam face in an intermediate position between the stowed position and deployed position of the cover system.
16. The cover system of any of claims 9 to 15 wherein the cam members are engageable under a biasing force operable to maintain engagement between the cam members while allowing the swinging arm assembly to move parallel to the pivot axis during pivotal movement of the swinging arm assembly between the stowed position and the deployed position.
17. The cover system of claim 16 wherein the biasing force is provided by a spring.
18. The cover system of any preceding claim wherein the cover assembly extends between the swinging arm assemblies and the cover is extendible from and retracted into the cover assembly in response to movement of the swinging arm assemblies to and from the deployed position.
19. The cover system of any of claims 1 to 17 wherein the cover assembly is adapted to be mounted on the vehicle and the cover is attached to the swinging arm assemblies so as to unwind from and rewind on the roller assembly as the swinging arm assemblies move to the deployed position and return to the stowed position.
20. A cover system for a vehicle having an open-topped container substantially as hereinbefore described with reference to the accompanying drawings.