FR3141900A1 - ADVANCED BREAKDOWN-TOWING ASSEMBLY FOR TOW VEHICLE, AND TOW VEHICLE INCLUDING SAME - Google Patents

Abstract

RECOVERY-TOWING ASSEMBLY FOR TOWING VEHICLE, AND TOWING VEHICLE COMPRISING SAME The present invention relates to a recovery-towing assembly (1) comprising a boom (4) intended to be articulated on a towing vehicle and an articulated towing basket (2). on the boom (4) and comprising an arm (5) supporting a crosspiece (6) pivotally mounted relative to the arm (5) around a first pivot axis (A1) perpendicular to the plane of the arm (5) and the crosspiece (6) and carrying at each end a fork (7) carrying a wheel. The basket (2) is movable between a transport position, in which the forks (7) are raised above the ground, and a loading and unloading position, in which the forks (7) rest flat on the ground. The arm (5) is mounted in free pivot connection, over a certain angular range, relative to the arrow (4) around a second pivot axis (A2) parallel to the first pivot axis (A1). The assembly (1) comprises locking means (50, 60) capable of blocking the pivoting of the crosspiece (6) around the first pivot axis (A1) when the towing basket (2) is in the transport position . The present invention also relates to a towing vehicle comprising such a recovery-towing assembly (1). Figure to be published with the abstract: Figure 5.

Description

ADVANCED RESCUE-TOWING ASSEMBLY FOR TOW VEHICLE, AND TOW VEHICLE INCLUDING SAME

The technical field of the invention is that of towing vehicles of the type allowing the towing of vehicles that have been damaged, damaged, broken down or illegally parked, for example improperly or inconveniently parked.

Towing vehicles are commonly equipped at the rear with a lifting and towing device.

Currently, these lifting and towing devices are intended to be mounted at the rear of a vehicle and they generally consist of a boom and a towing basket comprising an arm and a crosspiece with wheel-carrying forks , as well as several cylinders.

Conventionally, the boom is pivotally mounted, around a first horizontal axis of rotation, on a first support assembly secured to the chassis of the vehicle, and a first cylinder makes it possible to rotate the boom around the first horizontal axis of rotation . A first end of the arm of the towing basket is pivotally mounted, around a second horizontal axis of rotation, on the free end of the boom and a second cylinder makes it possible to rotate the arm around the second horizontal axis of rotation. The crosspiece is pivotally mounted around a third axis of rotation, on a second end of the arm. The third axis of rotation is vertical when the arm extends substantially horizontally.

The combined action of the first and second cylinders, on the arm and the boom respectively, allows the lifting and towing device to take different positions, namely a rest position, a loading/unloading position and a transport position. In the rest position, the arm has been bent towards the arrow. In the loading/unloading position, the arm extends in a direction slightly inclined to the horizontal and the second end of the arm, the crosspiece and the forks rest on the ground. In the transport position, the arm, crossbar and forks extend substantially horizontally above the ground.

In operation, at the pick-up location, the lifting and towing device is brought from the rest position to the loading/unloading position, such that the front or rear wheels of the vehicle to be towed are arranged in the towing basket, then the device is brought into the transport position so as to raise the front or rear of the vehicle to be towed and allow it to be towed by the towing vehicle.

On arrival at the repair or storage location, a symmetrical maneuver is carried out consisting of returning the device from the transport position to the loading/unloading position, such that the front or rear wheels of the vehicle to be towed are brought back to the ground and then released from the towing basket, then returning the device to the rest position.

However, the known lifting and towing device with a standard towing basket, as presented above, cannot support a vehicle to be towed that is difficult to access, such as for example a vehicle to be towed positioned on a non-coaxial longitudinal axis. to that of the towing vehicle, as is the case when the vehicle to be towed is parked between two vehicles and the towing vehicle is on the adjacent traffic lane.

There is therefore a need for a lifting and towing solution having good maneuverability and allowing a towing vehicle equipped with it to easily take charge of a vehicle to be towed that is difficult to access and to move it in complete safety.

The Applicants therefore propose to respond to this need by using a recovery-towing assembly making it possible to position the towing basket along an axis offset from the axis of the towing vehicle in order to easily support a vehicle. difficult to access and allowing the vehicle to be towed to be moved without danger, namely by having road behavior similar to that of a trailer, while maintaining the secondary objective of not increasing the operating time or the number of manipulations for the 'operator.

The present invention therefore relates to a recovery-towing assembly making it possible to tow a vehicle with a raised axle, in particular a broken down, damaged or illegally parked vehicle, which assembly comprises a boom, intended to be articulated on a towing vehicle of so as to extend along a vertical longitudinal plane, and a towing basket articulated on the boom around a first articulation axis which is transverse to said plane of the boom and which is horizontal once the assembly is articulated on the vehicle tugboat, the towing basket comprising an arm having a first end articulated on the boom and a second end, and a crosspiece pivotally mounted at the second end of the arm around a first pivot axis perpendicular to the longitudinal plane along which extend the arm and the crosspiece, the crosspiece carrying at each of its two ends a wheel-carrying fork capable of receiving a wheel of a vehicle to be towed, the boom and the arm being intended to be pivoted by first motor means to move the towing basket between a transport position, in which the carrier forks are raised above the ground, and a loading/unloading position, in which the carrier forks rest flat on the ground, the recovery-towing assembly being characterized by the fact that the arm is mounted so as to be, at least in the transport position, freely pivotable, over an angular range, relative to the arrow around a second pivot axis parallel to the first pivot axis and located in the vicinity of the first end of the arm, the recovery-towing assembly comprising blocking means capable of blocking the pivoting of the crossmember around the first pivot axis when the towing basket is in the transport position.

Thus, the present invention relates to a recovery-towing assembly suitable for towing a broken down vehicle because the assembly can lie flat on the ground for loading a broken down vehicle. It should, however, be emphasized that the use of the recovery-towing assembly according to the present invention is not limited to broken down vehicles, but extends to any vehicle that needs to be moved with one of the axles. raised. As a result, the recovery-towing assembly according to the invention could be articulated both to a towing vehicle of the impound vehicle type and to a towing vehicle of the recovery vehicle type. We also emphasize that the towing vehicle can be both a light vehicle and a heavy vehicle.

With such a recovery-towing assembly, in use, during the loading/unloading phase, the towing basket is able to pivot around two vertical pivot axes at a distance from each other, namely a first axis vertical pivot between the crosspiece and the arm and a second vertical pivot axis between the arm and the boom. This makes it possible to place the towing basket along an axis offset from the axis of the towing vehicle, by pivoting the arm in a first direction around the second vertical pivot axis and by pivoting the crosspiece in a second, opposite direction. said first direction, around the first vertical pivot axis to place the crosspiece perpendicular to said offset axis, and therefore to more easily load a vehicle to be towed which could not be positioned in the axis of the towing vehicle.

Thanks to the presence of the blocking means, in use, during the transport phase, the towing basket is able to pivot freely around a single vertical pivot axis, namely the second vertical pivot axis. This makes it possible to shift the pivoting movement towards the front of the towing basket, in other words towards the rear of the towing vehicle, and therefore to bring the behavior of the towing basket closer to that of a conventional trailer, particularly with regard to the tracking of the towing vehicle, the second vertical pivot axis then behaving in a manner equivalent to a conventional towing ball. In particular, these blocking means make it possible to avoid jackknifing of a towing vehicle comprising such a recovery-towing assembly, in other words to prevent the towing basket from getting in the way of the towing vehicle, especially when braking.

The first driving means for the pivoting of the boom and the arm around the horizontal articulation axes will be, for example, cylinders.

The arm can be mounted in free pivot connection around the second pivot axis. In this case, during the loading/unloading phases, the arm can be pivoted directly by the operator, by hand or by foot. This free pivot connection could be implemented in any appropriate form, such as for example simply by a shaft received in a plain bearing, or for example by a rotating crown.

Alternatively, the arm is connected to the boom by a pivot connection and second motor means are also provided capable of pivoting the arm in one or the other direction to place the towing basket in the loading position /unloading, the second motor means being configured to allow free pivoting of the arm around the second pivot axis in the transport position.

This is particularly useful in the case where the arm is long, such as for example for an application for a heavy goods vehicle, the operator then being able to rotate the arm by simple remote control of the second motor means. Here again, the pivot connection and the second motor means can be produced in any appropriate form, as is well known per se, and can for example include a rotating crown whose rotation in both directions is controlled by cylinders which will be placed in free circuit in the transport phase to allow free pivoting of the arm. We could also provide, for example, second motor means comprising an electric motor with the interposition of a clutch between it and the ring of the crown which is integral with the arm.

In a particular embodiment, the arm is a telescopic arm comprising a hollow main arm and secondary arm slidably mounted in the main arm by means of sliding control means, the first pivot axis being integral with the secondary arm, the blocking means comprising at least one cutout in the main arm capable of receiving by nesting at least one complementary part of the crosspiece, the sliding control means being capable of moving the secondary arm relative to the main arm between an deployed position, in in which the or each complementary part is not received in the cutout, such that the crosspiece is free to pivot around the first pivot axis, and a retracted position, in which the or each complementary part is received by nesting in the cutting, such that pivoting of the crosspiece around the first pivot axis is prevented.

Advantageously, in order to facilitate the correct positioning of the crosspiece relative to the main arm during movement towards the retracted position, the main arm can also have a longitudinal slot, one end of which is open and facing the crosspiece, the slot being parallel to the longitudinal axis of the main arm and in the same vertical plane as the latter, and the crosspiece carries a pin positioned so as to belong to said vertical plane when the crosspiece is orthogonal to the main arm, the slot and the pin being positioned such so that the pin enters the slot when the secondary arm is moved to the retracted position. Preferably, the open end of the slot will be flared to guide the entry of the pawn into the slot.

The sliding control means may include a cylinder, for example hydraulic.

Preferably, the recovery-towing assembly further comprises means for limiting the angle of pivoting of the arm relative to the arrow around the second pivot axis, which limiting means authorizing pivoting over an angular range for example less than 180°. The angular range can be adapted as necessary, and thus be greater or lesser, depending on the length of the arm of the towing basket, particularly with the aim of avoiding any contact with the rear of the towing vehicle.

In use, such means of limiting pivoting around the second pivot axis, and therefore limiting rotation in the horizontal plane, make it possible to prevent the towing basket from colliding with the towing vehicle.

In a particular embodiment, the means for limiting the pivot angle comprise a finger parallel to the second pivot axis and secured to the arm, engaged in an arcuate slot centered on the second pivot axis and formed in a plate crossed by the second pivot axis and articulated to the arrow around the first articulation axis. It is easy to understand that in this case the angular range for the pivoting of the arm around the second pivot axis is defined by the length of the slot provided in the plate.

Alternatively, said limiting means can simply consist of at least one projection carried by the arm and two end stops carried by the plate and positioned on the trajectory of the at least one projection so as to define said angular range .

Preferably, the recovery-towing assembly also comprises means for blocking the pivoting of the arm around the second pivot axis, configured to block the arm in alignment with the arrow during folding/unfolding of the arm relative to the arrow when the towing basket leaves the stowed position towards the loading/unloading position and vice versa. These locking means can for example comprise a lockable indexing finger carried by the arm and positioned to be able to engage selectively in a bore formed in an element secured to the arrow, where appropriate secured to said plate. In the engaged position, the indexing finger prevents any pivoting of the arm around the second pivot axis, and after the arm has been unfolded, the operator disengages the indexing finger to allow said pivoting. The operator re-engages the indexing finger when the arm needs to be folded and the towing basket moved to the stowed position.

For safety, we can have a device for detecting the position of the indexing finger, configured to determine whether the latter is in the engaged position or in the disengaged position, such as for example a feeler placed opposite the bore, passing through , through which the indexing finger extends in the engaged position, and the recovery-towing assembly can be configured to prevent the pivoting cylinder of the towing basket around the first articulation axis, from rotating the towing basket upwards if the indexing pin is not in the engaged position.

This avoids any risk of the arm tilting to one side or the other by pivoting around the second pivot axis while it is folded upwards towards the stowed position.

Preferably, the recovery-towing assembly further comprises a support or load balancing system comprising at least two wheels each connected to the arm by a connection assembly such that the wheels are movable between a folded position in which the wheels are located between the cross member and the arm and do not extend below the plane of the cross member, and a deployed position in which the wheels extend below the plane of the cross member and in the alignment of the crosspiece, in particular are located directly under a part of the carrying forks, and that in use the weight that the vehicle to be towed applies on the crosspiece is transmitted to the wheels by the connection assemblies, the recovery-towing assembly comprising in addition a means of damping the pivoting movement of the arm.

Alternatively, each connection assembly could be connected to the crosspiece.

Connecting the load support system to the arm rather than to the cross member saves length for the overhang.

The load support system allows you to transform a classic tow basket into a trailer-type system. In particular, this load support system, in its deployed position, makes it possible to take up the weight of the towed vehicle, and therefore to move the towed vehicle over long distances, in particular over a distance exceeding 500 meters, the second pivot axis being then positioned generally in the position that a conventional towing ball would occupy and ensuring the same function as the latter. If we consider a towing vehicle equipped with the recovery-towing assembly according to the present invention and towing a broken down vehicle with a raised axle, the load support system then constitutes a third axle and allows the towing vehicle to have safe and stable driving behavior.

It should be noted that the load support system as defined above can be an integral part of the recovery-towing package or can be supplied in the form of a kit adaptable to a standard towing basket.

In a particular embodiment, the damping means is constituted by the cylinder controlling the pivoting movement of the arm around the first articulation axis, which cylinder is a double-acting hydraulic cylinder connected to the hydraulic circuit of the towing vehicle and the two supply ports of which are connected to each other by a connecting pipe, a valve being provided at each node between a supply port of the cylinder, the connecting pipe and the hydraulic circuit of the towing vehicle, the valves being able to be controlled in such a way that when the valves close the passage between the hydraulic circuit of the towing vehicle and the two supply ports of the cylinder, oil circulates freely in the supply line of the arm by the intermediary of the connecting pipe.

The passage of oil in the connecting pipe makes it possible to maintain a residual pressure in the supply line of the arm of the towing basket which ensures damping of said arm, and therefore of the recovery-towing assembly, and flexibility of rolling.

Preferably, each connection assembly is mounted to rotate around a third pivot axis parallel to the first and second pivot axes and secured to the arm, the rotational movement of each connection assembly around the third pivot axis being controlled by rotational drive means.

Advantageously, these rotation drive means are rack and pinion drive means, which means comprise, for each connection assembly, a rack carried by the secondary arm and a pinion secured in rotation to the third pivot axis and in taken with the rack, the third pivot axis being connected to the main arm, such that the sliding of the secondary arm towards the deployed position causes the rotation of the connection assemblies towards the folded position of the wheels and that the sliding of the secondary arm towards the retracted position causes the rotation of the link assemblies towards the deployed position of the wheels.

These rack and pinion drive means make it possible, where necessary, to avoid the use of jacks, and therefore to make savings in terms of cost and weight. However, we could of course provide, for example for considerations of power and wear, particularly in the case of heavy goods vehicles, drive means comprising cylinders balanced between the two arms, the operation of which could also be controlled. to the movements of the telescopic arm.

Furthermore, with such drive means, the user does not have to do anything to position the load support system in the folded position and in the deployed position, the latter being moved automatically under the effect of the sliding of the secondary arm.

Preferably, each connection assembly is an articulation arm assembly comprising a first arm extending in the plane of the crosspiece and mounted to rotate around the third pivot axis and a second arm articulated at the free end of the first arm around a fourth pivot axis orthogonal to the third pivot axis and oriented transversely to the longitudinal axis of the first arm, the second arm carrying a wheel support axis extending orthogonal to the longitudinal axis of the second arm, wheel support axle carrying at least one wheel.

Thus, the first arm is articulated to the arm of the towing basket so as to allow the load support system to be retracted behind the carrying forks during loading/unloading of a vehicle to be towed on the towing basket and to allow its installation under the carrier forks when transporting the vehicle to be towed. The second arm is articulated so as to allow the inclination of the wheel support axis to place the towing basket flat on the ground when loading/unloading the vehicle to be towed.

Preferably, each link assembly is arranged and dimensioned such that, when the load support system is in its deployed position, the link assemblies and the wheels of the load support system do not extend beyond of the free ends of the carrier forks.

Thus, the total width of the recovery-towing assembly corresponds to the width of the towing basket.

Preferably, each wheel support axis is mounted to rotate around its axis.

Thus, when the towing basket is placed flat on the ground, the wheels can be oriented with their tread in contact with the ground, despite the inclination of the wheel support axis.

Preferably, the load support system comprises two pairs of wheels.

The use of two pairs of wheels allows optimal weight recovery with better load distribution.

Preferably, in the case where the towing vehicle is a vehicle of less than 3.5T, the wheels are dimensioned such that the recovery-towing assembly has a load capacity of 1200 kg minimum.

In a particular embodiment, each carrier fork is articulated on the crossmember around a second articulation axis orthogonal to the first pivot axis and arranged such that in use, when the towing basket is in the position of transport and a wheel of a vehicle to be towed is received on the carrier fork, the fork is able to tilt towards the ground by rotation around the second articulation axis over an angular range limited by a means forming a stop.

Such automatic inclination of the forks towards the ground, under the effect of the weight of the vehicle to be towed, makes it possible to lower the train located on the side of the wheels received in the forks of the vehicle to be towed and therefore to improve safety during transport. This also makes it possible to tow vehicles with a larger rear overhang than is currently possible with known towing baskets.

It should be emphasized that this articulation axis, which, in use, in the transport position, is a horizontal axis positioned longitudinally to the axis of the crosspiece, can be adapted to any type of fork, namely a fork comprising a single arm parallel to the wheel, that a fork comprising a frame which frames the wheel, and can be adapted in any towing basket, namely both a classic towing basket and the towing basket of the assembly according to the present invention. In particular, it is emphasized here that such a tilting carrier fork could equip a conventional recovery-towing assembly, namely not comprising a load support system as defined above and/or not comprising a free pivot connection. between the arm and the arrow.

Also disclosed herein is a towing basket comprising an arm having a first end intended to be connected to a boom of a recovery-towing assembly making it possible to tow a vehicle with a raised axle, in particular a broken down or damaged vehicle. or in illegal parking, the arm having a second end, the towing basket also comprising a cross member mounted at the second end of the arm, the cross member carrying at each of its two ends a wheel carrying fork capable of receiving a wheel of a vehicle to be towed, the towing basket being intended to be moved by the boom between a transport position, in which the carrier forks are raised above the ground, and a loading/unloading position, in which the carrier forks rest at flat on the ground, the towing basket being characterized by the fact that each carrying fork is articulated on the crossmember around a hinge axis which is horizontal and orthogonal to the vertical longitudinal plane along which the arm extends and which is arranged such that in use, when the towing basket is in the transport position and a wheel of a vehicle to be towed is received on the carrier fork, the fork is able to tilt towards the ground by rotation around said articulation axis over an angular range limited by means forming a stop.

The towing basket defined in the paragraph above may include all or part of the characteristics of the recovery-towing assembly according to the present invention, such as in particular the characteristics of the particular embodiment described below for the carrier forks.

The present invention also relates to a towing vehicle, characterized in that it comprises a recovery-towing assembly as defined above.

Advantageously, the towing vehicle comprises a stabilizing device carried by the chassis of the towing vehicle and located between a rear axle of the towing vehicle and the second pivot axis of the recovery-towing assembly, which stabilizing device is configured to be moved between a stabilization position, in which it rests on the ground, and a raised position, in which it is away from the ground.

Such a stabilizing device makes it possible to prevent the towing vehicle from tipping when moving the towing basket from the loading/unloading position to the transport position. In the absence of such a stabilization solution, and more particularly in the case where the vehicle to be towed has a high weight, the front of the towing vehicle could risk being subjected to a lifting effect.

This risk of tipping being avoided, the towing vehicle can be a small vehicle with a low GVWR, for example 4x4 SUV type vehicles. The choice of a small towing vehicle allows the recovery-towing of a vehicle to be towed located in a difficult to access location, in particular an underground car park.

Preferably, the stabilizing device comprises a pair of hydraulic cylinders positioned on either side of the arm and configured to be moved towards the stabilization position by extension of each cylinder and towards the raised position by retraction of each cylinder.

Alternatively, the stabilizing device could include crutches operated manually or by electric motors.

To better illustrate the object of the present invention, we will describe below, for informational and non-limiting purposes, an embodiment with reference to the appended drawings.

In these drawings:

is a perspective view of the recovery-towing assembly according to one embodiment of the present invention, the towing basket being in the loading/unloading position and the load support system being in the folded position;

is a top view of the recovery-towing assembly of the ;

is a side view of the recovery-towing assembly of the ;

is an enlarged perspective view of the connection between the load support system and the towing basket of the entire ;

is another perspective view of the recovery-towing assembly of the , the towing basket being in the transport position and the load support system being in the deployed position;

is a top view of the recovery-towing assembly of the ;

is a side view of the recovery-towing assembly of the ;

is a perspective view of the towing vehicle according to the present invention, which towing vehicle comprises the recovery-towing assembly of the in loading or unloading position;

is a side view of the towing vehicle of the ;

is a top view of the towing vehicle of the , showing the arm and crosspiece after they have been rotated by the operator;

is a side view of the towing vehicle according to the present invention, which towing vehicle comprises the recovery-towing assembly in the transport position as shown in the ;

is a side view of the fork of the recovery-towing assembly as shown in the , which fork is inclined towards the ground;

is a perspective view of the towing vehicle according to the present invention, which towing vehicle comprises a recovery-towing assembly according to another embodiment of the present invention, in the stowed position;

is a schematic view of the means for blocking the pivoting of the arm around the second pivot axis; And

is a schematic view of the means for damping the pivoting movement of the towing basket.

If we refer to Figures 1 to 13, we can see that a recovery-towing assembly 1 for towing vehicle V according to the present invention comprises a towing basket 2, a load support system 3 and a boom 4 .

The boom 4 is intended to be connected and articulated to a towing vehicle V, to support the towing basket 2 and to allow the movement of the towing basket 2 between a stowed or rest position ( ), a loading and/or unloading position (Figures 1 to 3, 8 to 10) and a transport position (Figures 5 to 7 and 11).

As can be seen in Figures 1 to 3 and 5 to 7, the boom 4 is a bent boom having a first end 4a intended to be articulated on the towing vehicle V and a second end 4b connected to the towing basket 2. The bent arrow 4 has three straight sections extending in the same plane, namely a first straight section 40 extending from the first end 4a to a second straight section 41, and a third straight section 42 extending from the second section right 41 at the second end 4b. The first 40 and third 42 straight sections are arranged relative to the second straight section 41 such that the angle formed between them is less than an angle of 90 degrees. Thus, the bent arrow 4 has substantially a V shape. Each straight section 40, 41, 42 can be made from an I-shaped cross-section profile having a core and two flanges. In this case, the soles of the second straight section 41 are parallel to each other, while the soles of the first 40 and third 42 straight sections approach each other as we approach the first 4a and second 4b ends of arrow 4, respectively.

We emphasize here that the arrow could also be in several parts articulated to each other.

The arrow 4 comprises a first drilling 43 at its first end 4a, a second drilling 44 at its second end 4b, as well as at least a third drilling 45 between its second 41 and third 42 straight sections. These holes 43, 44, 45 pass through the arrow 4 perpendicular to the plane of the arrow 4. In other words, these holes 43, 44, 45 pass through the core of the profile of each straight section 40, 41, 42.

The first hole 43 is intended to allow the passage of a horizontal axis pin (not visible), integral with the chassis of the towing vehicle V and transverse to it, and used for the articulation of the boom 4 on the vehicle towing vehicle V. This pin is arranged in such a way that, once the arrow 4 is articulated on the towing vehicle V by said pin, the arrow 4 extends in a vertical plane passing through the longitudinal axis of the towing vehicle V.

The second hole 44 is crossed by a first articulation axis in use, namely when assembly 1 is articulated on the towing vehicle V, this first articulation axis X1 is a first horizontal articulation axis, transverse to the longitudinal axis of the towing vehicle V.

The third bore 45, with an axis parallel to the axes of the first 43 and second 44 bores, receives a first end of a jack 9 mounted between the boom 4 and the towing basket 2 so as to move the basket 2 relative to the arrow 4 around the first articulation axis X1. Thanks to this cylinder 9, the towing basket 2 is able to pivot relative to the arrow 4, from the stowed position shown on the , in which the towing basket 2 is folded against the third straight section 42 of the boom 4, up to the transport position shown on the , passing through all intermediate positions.

The towing basket 2 is intended to receive and hold two wheels of a vehicle to be towed (not shown), in particular a broken down, damaged or illegally parked vehicle.

The towing basket 2 mainly comprises an arm 5 connected and articulated to the boom 4, a crosspiece 6 connected to the arm 5 and two forks 7 carrying wheels carried by the crosspiece 6.

In the preferred embodiment, as shown in Figures 1 to 13, the arm 5 is a telescopic arm comprising a hollow main arm 5a and a secondary arm 5b slidably mounted in the main arm 5a.

The main arm 5a is in the form of a profile with a rectangular cross section having a face on the arrow side 4, an opposite face on the ground side and two side faces. The main arm 5a has a first end intended to be articulated to the boom 4 and a second end on the crossbar side 6 beyond which the secondary arm 5b is capable of projecting.

At its second end region, the main arm 5a comprises at least one cutout 50 configured to receive, by interlocking shape, at least one complementary part 60 of the crosspiece 6. In the preferred embodiment, the at least one cutout 50 is a female cutout made at least in the edge of the arrow side face 4. This cutout 50 has a shape flared towards the outside of the arm 5, in particular a cutout 50 in the shape of an isosceles trapezoid. This cutout 50 is framed, on either side of the arrow side face 4, by a part projecting relative to the side faces and comprising a drilling oriented perpendicular to the plane of the arm 5.

The secondary arm 5b is dimensioned to be able to be received in the main arm 5a and slide inside it. Thus, the secondary arm 5b is in the form of a longitudinal beam of rectangular section. The secondary arm 5b can slide and be locked in position in the main arm 5a, in particular by means of a hydraulic cylinder (not shown). The secondary arm 5b has a first end in contact with the main arm 5a and a second end connected to the crosspiece 6.

With a view to its connection to the crosspiece 6, the secondary arm 5b comprises, near its second end, a bore receiving a first pivot axis A1 secured to the crosspiece 6. This first pivot axis A1 is perpendicular to the plane of the arm 5.

Furthermore, at its second end region, the secondary arm 5b carries a pair of racks 51, in particular a rack 51 along each of its lateral faces, namely its faces perpendicular to the plane of the arm 5. Each rack 51 includes teeth. The main arm 5a has openings in its side faces facing the racks 51. Thus, the racks 51 are exposed on either side of the arm 5 with a view to their cooperation with the load support system 3 by the intermediate of their teeth.

The crosspiece 6 is a pivoting crosspiece mounted on the second end of the secondary arm 5b, on which it is articulated by means of the first pivot axis A1. The first pivot axis A1 extends orthogonally to the longitudinal axis of the arm 5 and perpendicular to the plane in which the arm 5 and the crosspiece 6 are located, in other words orthogonal to the first hinge axis X1. The crosspiece 6 has two longitudinal ends. The first pivot axis A1 is located approximately halfway along the crosspiece 6, namely equidistant from each of the two longitudinal ends.

In the preferred embodiment, the crosspiece 6 generally has a T shape with a main branch secured to the first pivot axis A1 and a transverse branch carrying the two longitudinal ends. In particular, the crosspiece 6 has two opposite T-shaped walls whose main branch defines the complementary male part 60 of the crosspiece 6 capable of fitting into the female cutout 50 of the main arm 5a. The cutout 50 having the shape of an isosceles trapezoid, the complementary part 60 also has the shape of an isosceles trapezoid. In order to ensure the nesting of the complementary part 60 in the cutout 50, the face carrying the complementary part 60 is coplanar with the corresponding face of the main arm 5a carrying the cutout 50.

The cutout 50 and the complementary part 60 are configured such that, when the secondary arm 5b has slid into the main arm 5a and its second end projects relative to the second end of the main arm 5a, the complementary part 60 is not in contact with the cutout 50 and is not received therein, then allowing the crosspiece 6 to pivot around the first pivot axis A1. And, when the secondary arm 5b has slid in the main arm 5a such that the complementary part 60 is received in the cutout 50 and fitted into it, the crosspiece 6 is no longer allowed to pivot around the first axis of pivot A1. Thus, the at least one cutout 50 and the at least one corresponding complementary part 60 constitute means for blocking the pivoting of the crosspiece 6 relative to the arm 5.

The crosspiece 6 carries, at each of its two longitudinal ends, a wheel-carrying fork 7. The two wheel-carrying forks 7 are intended to receive two wheels from the same axle of a vehicle to be towed, for example the two front wheels or the two rear wheels.

Each fork 7 comprises a first rectilinear branch 70 which extends in the extension of the longitudinal axis of the transverse branch of the crosspiece 6, and a second L-shaped branch 71, which extends behind the crosspiece 6 , that is to say on the side of the crosspiece 6 opposite the arm 5. The second branch 71 is connected to the corresponding longitudinal end of the crosspiece 6 by a pivot axis 72, such that the angle formed between the second branch 71 and the crosspiece 6, and therefore the space between the first 70 and second 71 branches, is adjustable. Thus, the second branch 71 is capable of pivoting between a position in which the second branch 71 is facing the first branch 70, and a position in which the second branch 71 is facing the crosspiece 6.

The second branch 71 is also articulated to the corresponding longitudinal end of the crosspiece 6 by a second articulation axis X2, such that the angle formed between the plane of the second branch 71 and the plane of the crosspiece 6 is variable. The second hinge pin 6 when the second branch 71 faces the first branch 70. This second hinge pin 6 and the second branch 71.

In order to limit the pivoting movement of the second branch 71 opposite the arrow side face 4 of the arm 5, therefore towards the ground when the basket 2 is placed above the ground in the transport position, the edge of the connecting part 73 and the edge of the end of the second branch 71 which is opposite this connecting part 73 are configured so as to allow rotation around the second articulation axis X2 over a certain angular range and to constitute means forming a stop beyond this angular range. In particular, the edge of the connecting piece 73 has a cavity shape against which the corresponding edge of the second branch 71 is able to come to bear.

Alternatively, each wheel-carrying fork 7 could be in the form of a frame intended to frame the wheel it receives. In particular, the second branch 71 could be U-shaped instead of L-shaped.

The characteristics of the fork 7 described above, in particular the presence of a second articulation axis X2, are independent of the other characteristics of the recovery-towing assembly 1, in particular of those linked to the support system of load 3, and we can therefore plan to equip a conventional towing basket with such a fork 7.

The wall 70a of the first branch 70 intended to come opposite the second branch 71 is an inclined wall 70a, thus making it possible to receive a wheel and hold it in place in the space between the two branches 70, 71.

The first branch 70 carries, on its wall located on the arm 5 side, a locking member 10 capable of allowing the load support system 3 to be maintained in position. In the embodiment shown, this locking member 10 is presented under the form of two inclined axes 10 opposite the arm 5 and projecting relative to the first branch 70.

This towing basket 2 is connected and articulated to the boom 4 via the arm 5, in particular the hollow main arm 5a, and a plate 8 interposed between the second end 4b of the boom 4 and the first end of the main arm 4a.

Plate 8 is in the form of a U-shaped profile having a core and two wings perpendicular to the core and arranged facing each other. The core bears against the main arm 5a and is therefore in a plane parallel to the plane of the arm 5 and the crosspiece 6. This core includes a through hole 80 receiving a second pivot axis A2 secured to the main arm 5a and parallel to the first pivot axis A1, in other words extending perpendicular to the plane of the arm 5 and the crosspiece 6. The wings include holes made facing each other and receiving the first articulation axis X1 which also passes through the second end of the boom 4. The wings also include holes made facing each other and receiving a second end of the jack 9, in particular the hydraulic jack, connected to the third hole 45 of the boom 4. Such an arrangement therefore allows the cylinder 9 to control the pivoting of the arm 5 relative to the arrow 4 around the first articulation axis X1, which is a horizontal articulation axis once the arrow 4 is articulated to the towing vehicle V.

Furthermore, with such an arrangement, the second pivot axis A2 constitutes a free pivot connection between the arm 5 and the plate 8, and therefore between the towing basket 2 and the boom 4, which allows vertical axis pivoting, therefore in a horizontal plane, when the towing basket 2 is in a horizontal plane.

This free pivot connection allows rotation of the arm 5 relative to the arrow 4 over a certain angular range which is limited by means for limiting the pivot angle. These limiting means include a finger 82 secured to the arm 5 and an arcuate slot 81 made in the plate 8. In particular, the finger 82 is a cylindrical rod with an axis parallel to the second pivot axis A2 and positioned in the alignment of the second pivot axis A2 along the longitudinal axis of the arm 5. This finger 82 extends between the first end of the arm 5 and the second pivot axis A2. The circular arc light 81 is produced in the core of the plate 8 and describes an arc of a circle centered on the through hole 80. The finger 82 is engaged in the light 81, thus making it possible to limit the rotation of the arm 5 by relative to arrow 4 between two extreme angular positions defined by the stop of finger 82 at each end of light 81.

Alternatively, the free pivot connection between the arm 5 and the arrow 4 could be enabled by a rotation ring comprising an external ring and an internal ring, for example, an external ring secured to the arm 5 and movable in rotation around a internal ring attached to plate 8.

Advantageously, as illustrated schematically on the , the recovery-towing assembly 1 also comprises means for blocking the pivoting of the arm 5 around the second pivot axis A2, configured to block the arm 5 in alignment with the arrow 4 during folding/unfolding of the arm 5 when the towing basket 2 leaves the stowed position towards the loading/unloading position and vice versa. These blocking means here comprise a lockable indexing finger 17 carried by the arm 5 to engage selectively in a bore 18 formed in an element 19 secured to the plate 8 and thus prevent any pivoting of the arm 5 around the second pivot pin A2. The finger 17 will be disengaged by the operator once the arm 5 has been unfolded, to allow said pivoting in order to place the towing basket 2 in the loading/unloading position and in the transport position, and will be reengaged when the arm 5 must be folded and the towing basket 2 moved to the stowed position.

For safety, it is also possible to have a device for detecting the position of the indexing finger 17, configured to determine whether the latter is in the engaged position or in the disengaged position, as for example illustrated in the a feeler 20 carried by the plate 8 and placed opposite the through bore 18, through which the indexing finger 17 extends in the engaged position. We can then prevent the cylinder 9 from pivoting the towing basket 2 upwards if the indexing finger 17 is not in the engaged position.

The load support system 3 makes it possible to transform the towing basket 2 described above into a trailer type system. In particular, this load support system 3 is capable of taking on the weight of a towed vehicle, and therefore makes it possible to move the towed vehicle over long distances.

The load support system 3 comprises two articulation arm assemblies 12-13 each carrying a wheel support axle 14 and at least one wheel 15.

Each hinge arm assembly 12-13 comprises a first arm 12 and a second arm 13.

In the embodiment shown in Figures 1 to 13, the first arm 12 is in the form of a bent bar with three branches, for example of square section, having a first end and a second end.

The first end of the first arm 12 is articulated to the arm 5 at the level of the second end of the main arm 5a. In particular, the first arm 12 is mounted to rotate around a third pivot axis A3 secured to the main arm 5a. The third pivot axis A3 is parallel to the first pivot axes A1 and second A2. The third pivot axes A3 of the two articulation arm assemblies 12-13 are arranged on either side of the first pivot axis A1, and more precisely, through the drillings of the projecting parts on either side of the cutout 50 formed in the arm 5. The first arm 12 is therefore movable in a plane parallel to the plane of the towing basket 2, between the arm 5 of the towing basket 2 and the crosspiece 6.

The rotation of the first arms 12 around the third pivot axes A3 is automatically controlled by rack 51 and pinion 11 drive means, comprising the racks 51 carried by the secondary arm 5b and pinions 11 integral in rotation with each third axis of pivot A3. In particular, for each articulation arm assembly 12-13, a pinion 11 is mounted around the third pivot axis A3. The pinion 11 has teeth that mesh with the teeth of the corresponding rack 51. Thus, when the secondary arm 5b slides inside the main arm 5a, each rack 51 moves in translation along the longitudinal axis of the arm 5 and causes each pinion 11 to rotate in one direction or the other, depending on the direction of translation. The rotation of each pinion 11 causes each third pivot axis A3 to rotate, and therefore each first arm 12 to rotate relative to the arm 5, either in the direction of the crosspiece 6, or in the direction of the arm 5, in function of the direction of sliding of the secondary arm 5b.

The second arm 13 is a connecting part between the first arm 12 and the wheel support axle 14. The second arm 13 has a first end for connection with the first arm 12 and a second, opposite end. The second arm 13 comprises a fourth pivot axis A4 at its first end, a through bore 13a and through holes 13b of the locking member 10 at its second end.

The fourth pivot axis A4 of the second arm 13 passes through the second end of the first arm 12. The fourth pivot axis A4 is orthogonal to the third pivot axis A3 and extends transversely to the longitudinal direction of the branch at the second end of the first elbow arm 12.

The through bore 13a is a cylindrical bore whose axis is orthogonal to the fourth pivot axis A4 and transverse to the longitudinal direction of the second arm 13.

At its second end, the second arm 13 has two pairs of through holes 13b facing each other. The axis of the holes 13b is parallel to the fourth pivot axis A4. These holes 13b are sized and arranged so as to be able to receive the two inclined axes 10 secured to the corresponding fork 7.

The second arm 13 is therefore movable in a plane perpendicular to the plane of the towing basket 2, between a position in which the second arm 13 is in the same plane as the first arm 12, and a position in which the second arm 13 forms a angle of approximately 90 degrees with the first arm 12.

The wheel support axle 14 is a cylindrical axle dimensioned so as to be pivotally received in the through bore 13a of the second arm 13. Each wheel support axle 14 carries at least one wheel 15. In the embodiment preferred, each wheel support axle 14 carries a pair of wheels 15 or twin wheels. The four wheels 15 are dimensioned such that the recovery-towing assembly 1 has a high load capacity, in particular 1200 kg minimum in the case of a towing vehicle V of less than 3.5T. Each wheel support axis 14 is connected to the wheel(s) 15 which it carries in such a way that it is offset relative to the central axis of the wheel(s) 15. In other words, the axis central of the wheel(s) 15 is not in the same plane as the wheel support axis 14. Thus, as can be seen in the , in the deployed position of the load support system 3, the wheels 15 are located below the first branch 70 of each supporting fork 7 and the wheel support axis 14 is located in front of said first branch 70.

Alternatively, each hinge arm assembly 12-13 could be articulated to the crosspiece 6, as shown in the , and be rotated relative to the crosspiece 6 manually or by means of jacks.

It should be emphasized that although the recovery-towing assembly 1 according to the preferred embodiment of the present invention comprises the towing basket 2 equipped with the load support system 3, the load support system 3 could also be supplied in the form of a separate kit, to be adapted to a conventional towing basket or to an existing towing basket similar to the towing basket 2 of assembly 1 according to the invention.

In use, the recovery-towing assembly 1 is carried by a towing vehicle V and articulated on the chassis of the towing vehicle V so as to be able to be placed in a position allowing the loading of a vehicle to be towed or its unloading , as shown in Figures 1 to 3, 8 to 10, and in a position allowing the transport of the vehicle to be towed over an unlimited distance, as shown in Figures 5 to 7 and 11. When not in use, the The recovery-towing assembly 1 is also capable of being placed in a stowed position, as shown in the .

As can be seen in Figures 8 to 13, the towing vehicle V is equipped with the recovery-towing assembly 1 according to the present invention, the towing basket 2 being positioned at the rear thereof and the arrow 4 being articulated to its chassis at the rear axle.

Preferably, the towing vehicle V is also equipped with a stabilizing device S aimed at preventing the front of the towing vehicle V from lifting when the assembly 1 carrying a vehicle to be towed is placed in the transport position. In the preferred embodiment, the stabilizing device S comprises a pair of hydraulic cylinders. These cylinders are carried by the chassis and extend vertically between the rear axle and the rear of the towing vehicle V. The two cylinders are arranged on either side of the arrow 4, symmetrically in relation to it. The cylinders are movable between a stabilization position (Figures 8 and 9), in which they rest on the ground, and a raised position (Figures 11 and 13, in which they are away from the ground. More precisely, each cylinder comprises a body S0 fixed to the chassis, and a movable rod S1 carrying a support plate S2 at its free end. The support plate S2 is pivotally connected to the free end of the rod S1 around a horizontal axis and. transverse to the longitudinal axis of the vehicle V. This support plate S2 is intended to come into contact with the ground when the cylinder is in the stabilization position, and therefore makes it possible to protect the rod S1 and prevent its damage.

Due to the presence of such a stabilization device S, the towing vehicle V can be a small vehicle and therefore a vehicle which can be used more easily in places that are difficult to access.

In the position shown in Figures 1 to 3, 8 to 10, the towing basket 2 is placed in the loading/unloading position, the load support system 3 is placed in a folded position and the stabilizing device S is placed in the stabilization position.

In its loading/unloading position, the towing basket 2 is placed flat on the ground by rotation of the arrow 4 around its axis of articulation to the chassis and by movement of the arm 5 relative to the arrow 4 around the first axis of articulation to use lifting equipment.

To move into this loading/unloading position, the secondary arm 5b is slid towards its maximum extension position relative to the main arm 5a so that the crosspiece 6 is able to pivot relative to the arm 5 around the first pivot axis A1, which is then a vertical axis. To allow each wheel of the vehicle to be towed to abut against the first branch 70 of each carrying fork 7, the second branch 71 is positioned facing the crosspiece 6. Furthermore, the arm 5 is free to pivot, according to the authorized angular range, relative to arrow 4 around the second pivot axis A2, which is then a vertical axis. Thus, when passing into the loading/unloading position, the crosspiece 6 is able to pivot relative to the arm 5 around a first vertical axis A1 and the towing basket 2 is able to pivot relative to the arrow 4 around of a second vertical axis A2. As can be seen on the , the combination of these two pivoting movements, in a horizontal plane, makes it possible to position the carrying forks 7 of the towing basket 2 in a position offset from the longitudinal axis of the towing vehicle V, and therefore to easily recover a vehicle to tow that is difficult to access, in particular a vehicle to be towed in the axis of which the towing vehicle V could not be placed. These pivoting movements can be carried out by the operator himself, by hand or foot, or be obtained by motor means, as indicated previously.

When the towing basket 2 is positioned flat on the ground, the load support system 3 must be positioned in the folded position so as not to obstruct the passage of the vehicle to be towed.

In this folded position, the first arm 12 of each articulation arm assembly 12-13 is pivoted around the third pivot axis A3 in the direction of the arm 5 of the basket 2, in other words at a distance from the crosspiece 6. In the mode preferred embodiment of the present invention, the movement of each first arm 12 towards the arm 5 of the basket 2 is carried out automatically by the rack 51 and pinion 11 drive means, during the sliding of the secondary arm 5b towards its position d maximum extension.

In addition, the second arm 13 of each articulation arm assembly 12-13 is pivoted around the fourth pivot axis A4 away from the ground, in other words so as to extend substantially vertically upwards. Without this upward pivoting movement, it would not be possible to place basket 2 flat on the ground. Furthermore, each wheel support axle 14 is oriented in the through bore 13a of its second arm 13 such that the tread of each wheel 15 is in contact with the ground.

In the position shown in Figures 5 to 7, 11 and 12, the towing basket 2 is placed in the transport position, the load support system 3 is placed in an deployed position and the stabilizing device S is placed in the raised position.

In the transport position, the towing basket 2 is raised above the ground by rotation of the boom 4 around its axis of articulation to the chassis and by movement of the arm 5 relative to the boom 4 around the first axis d articulation X1 via cylinder 9. Thus, one of the two axles of the vehicle to be towed is no longer in contact with the ground.

When the towing basket 2 moves from the loading/unloading position to the transport position, the secondary arm 5b is slid towards its retracted position relative to the main arm 5a. In this position, the complementary part 60 of the crosspiece 6 is blocked by fitting into the cutout 50 of the main arm 5a, so that the crosspiece 6 can no longer pivot relative to the arm 5.

Furthermore, in this transport position, in order to retain the two wheels of the vehicle to be towed in the carrier forks 7, and therefore to prevent any longitudinal movement of the vehicle to be towed relative to the basket 2, the second branch 71 of each fork carrier 7 is positioned opposite the first branch 70 once the wheels of the vehicle to be towed are supported against the inclined wall 70a of the first branch 70.

Furthermore, in this transport position, the arm 5 is free to pivot relative to the arrow 4, according to the authorized angular range, around the second pivot axis A2, which is then a vertical axis. Thus, in the transport position, the towing basket 2 is able to pivot only around the second pivot axis A2, therefore around a vertical pivot axis which is located near the rear of the towing vehicle V. traffic, the road behavior of the towing basket 2 is therefore similar to that of a conventional trailer.

Furthermore, as can be seen in the , in the transport position, the weight of the vehicle to be towed causes the rotation of the second branch 71 of each fork 7 around the second hinge axis X2, which is then a horizontal axis and transverse to the longitudinal axis of the arm 5 This rotation makes it possible to tilt the second branch 71 towards the ground and therefore to lower the raised part of the vehicle to be towed, in other words, to reduce the angle between the vehicle to be towed and the ground.

In order to take up the weight of the vehicle to be towed, which then rests on the two carrying forks 7, the load support system 3 must be placed in the deployed position.

In this deployed position, the first arm 12 of each articulation arm assembly 12-13 is pivoted around the third pivot axis A3 in the direction of the crosspiece 6, until the first arm 12 is in contact with the first branch 70 of the fork 7. In the preferred embodiment of the present invention, the movement of each first arm 12 towards the crosspiece 6 is carried out automatically by the rack 51 and pinion 11 drive means, during sliding of the secondary arm 5b towards its retracted position.

Furthermore, the second arm 13 of each hinge arm assembly 12-13 is pivoted downwardly around the fourth pivot axis A4, until the second arm 13 and the branch having the second end of the first bent arm 12 is aligned along the same longitudinal axis, the wheels 15 then coming into contact with the ground. In this position, the two inclined axes 10 secured to the first branch 70 of each fork 7 are received in the corresponding holes 13b of the second arm 13, thus allowing locking in the deployed position of each arm assembly 12-13. It should be noted that the inclined axes 10 and the corresponding holes 13b could be replaced by an automatic locking means of the hydraulic type. Furthermore, each wheel support axis 14 is oriented in its through bore 13a such that the wheel(s) 15 which it carries have their axis of rotation transverse to the direction of advance or retreat of the towing vehicle V. The total length of each articulation arm assembly 12-13 in this deployed position is such that the wheels 15 are positioned under the first branch 70 of each carrying fork 7.

In this deployed position, it is the wheels 15 of the load support system 3 which take up the weight of the towed vehicle, and no longer the rear axle of the towing vehicle V. Thus, in its deployed position, the load support system 3 according to the invention can be considered as a third axle, the first axle being the rear axle of the towing vehicle V and the second axle being the axle of the vehicle to be towed (not shown) in contact with the ground. Thus, thanks to the load support system 3 according to the present invention, the weight of the raised part of the vehicle to be towed no longer rests on the rear axle of the towing vehicle V.

A means is also provided for damping the pivoting movement of the arm around the first hinge axis X1 during transport. The cylinder 9 is a hydraulic cylinder which controls this pivoting movement of the arm 5. This cylinder 9 is also intended to be connected to a hydraulic circuit 16 of the towing vehicle V. As can be seen in the , cylinder 9 is a double-acting hydraulic cylinder. Thus, the cylinder 9 has two supply ports 9a, 9b which are each connected with the hydraulic circuit 16 of the towing vehicle V.

In order to obtain a damping effect on the pivoting movement of the arm 5, and thus to avoid too sudden a vertical movement at the level of the carrying forks 7 which could lead to the lifting of the vehicle to be towed, the jack 9 is configured to constitute a means for damping the arm 5. The two supply orifices 9a, 9b are interconnected by a connecting pipe 9c and the passage of oil in the connecting pipe 9c is allowed by the control of two valves 9d located at each end of the connecting pipe 9c. In particular, a first valve 9d is provided at the node between one of the supply ports 9a of the cylinder 9, the connecting pipe 9c and the hydraulic circuit 16 of the towing vehicle, and a second valve 9d is provided at the level of the node between the other supply port 9b of the cylinder 9, the connecting pipe 9c and the hydraulic circuit 16 of the towing vehicle. The 9d valves can be controlled via a switch or buzzer which generates an electrical signal and intended to be placed in the driving cabin of the towing vehicle. The main arm 5a integrates a supply line (not shown) whose inlet and outlet are connected to the hydraulic circuit of the cylinder 9. Thus, when the valves 9d close the passage between the hydraulic circuit 16 of the towing vehicle V and the two supply ports 9a, 9b of the cylinder 9, oil circulates freely in the supply line of the arm 5, which makes it possible to have a residual pressure in the line having the effect of acting as a shock absorber in the main arm 5a.

In the stowed position shown on the , the arm 5 of the basket 2 is folded against the third straight section 42 of the arrow 4, by rotation of the plate 8 relative to the arrow 4 around the first articulation axis X1, the crosspiece 6 is blocked in rotation relative to at arm 5, the second branch 71 of each fork 7 faces the crosspiece 6, the articulation arm assemblies 12-13 are in the deployed position and the stabilizing device S is placed in the raised position. Such a stowed position of the recovery-towing assembly 1 allows the towing vehicle V to move easily to recover a vehicle to be towed or after having deposited a vehicle which has been towed.

It is of course understood that the particular embodiment which has just been described has been given for informational and non-limiting purposes, and that modifications can be made without departing from the present invention.

Claims (11)

Recovery-towing assembly (1) for towing a vehicle with a raised axle, in particular a broken down, damaged or illegally parked vehicle, which assembly (1) comprises a boom (4), intended to be articulated on a towing vehicle (V) so as to extend along a vertical longitudinal plane, and a towing basket (2) articulated on the boom (4) around a first articulation axis (X1) which is transverse to said plane of the boom (4) and which is horizontal once the assembly (1) is articulated on the towing vehicle (V), the towing basket (2) comprising an arm (5), having a first end articulated on the boom (4) and a second end, and a crosspiece (6) pivotally mounted at the second end of the arm (5) around a first pivot axis (A1) perpendicular to the longitudinal plane along which the arm (5) and the crosspiece ( 6), the crosspiece (6) carrying at each of its two ends a wheel-carrying fork (7) capable of receiving a wheel of a vehicle to be towed, the boom (4) and the arm (5) being intended to be pivoted by first motor means (9) to move the towing basket (2) between a transport position, in which the carrying forks (7) are raised above the ground, and a loading/unloading position, in which the carrying forks (7) rest flat on the ground, the recovery-towing assembly (1) being characterized by the fact that the arm (5) is mounted so as to be, at least in the transport position, freely pivotable, over an angular range, relative to the arrow (4) around a second parallel pivot axis (A2) to the first pivot axis (A1) and located in the vicinity of the first end of the arm (5), the recovery-towing assembly (1) comprising blocking means (50, 60) capable of blocking the pivoting of the crosspiece (6) around the first pivot axis (A1) when the towing basket (2) is in the transport position. Recovery-towing assembly (1) according to claim 1, characterized in that the arm (5) is a telescopic arm comprising a hollow main arm (5a) and secondary arm (5b) slidably mounted in the main arm (5a) by means of sliding control means, the first pivot axis (A1) being integral with the secondary arm (5b), the blocking means (50, 60) comprising at least one cutout (50) in the main arm ( 5a) capable of receiving by nesting at least one complementary part (60) of the crosspiece (6), the sliding control means being capable of moving the secondary arm (5b) relative to the main arm (5a) between an deployed position , in which the or each complementary part (60) is not received in the cutout (50), so that the crosspiece (6) is free to pivot around the first pivot axis (A1), and a retracted position , in which the or each complementary part (60) is received by nesting in the cutout (50), such that the pivoting of the crosspiece (6) around the first pivot axis (A1) is prevented. Recovery-towing assembly (1) according to any one of claims 1 and 2, characterized in that it further comprises means (81, 82) for limiting the pivot angle of the arm (5) by relative to the arrow (4) around the second pivot axis (A2), which limiting means authorizing pivoting over an angular range for example less than 180°. Recovery-towing assembly (1) according to claim 3, characterized in that the means (81, 82) for limiting the pivot angle comprise a finger (82) parallel to the second pivot axis (A2) and integral of the arm (5), engaged in an arcuate light (81) centered on the second pivot axis (A2) and made in a plate (8) crossed by the second pivot axis (A2) and articulated to the arrow (4) around the first hinge axis (X1). Recovery-towing assembly (1) according to any one of claims 1 to 4, characterized in that it also comprises means for blocking the pivoting of the arm (5) around the second pivot axis (A2), configured to lock the arm (5) in alignment with the boom (4) during folding/unfolding of the arm (5) relative to the boom (4) when the towing basket (2) leaves the stowed position towards the position loading/unloading and vice versa, these blocking means comprising for example a lockable indexing finger (17) carried by the arm (5) and positioned to be able to engage selectively in a bore (18) provided in an element (19) secured to the arrow (4). Recovery-towing assembly (1) according to any one of claims 1 to 5, characterized in that it further comprises a load support system (3) comprising at least two wheels (15) each connected to the arm (5) by a connection assembly (12, 13) such that the wheels (15) are movable between a folded position in which the wheels (15) are located between the crosspiece (6) and the arm (5) and do not extend below the plane of the crosspiece (6), and a deployed position in which the wheels (15) extend below the plane of the crosspiece (6) and in alignment with the crosspiece (6), in particular are located directly under a part of the carrying forks (7), and that in use the weight that the vehicle to be towed applies on the crosspiece (6) is transmitted to the wheels (15) by the connection assemblies (12, 13), the recovery-towing assembly (1) further comprising means for damping the pivoting movement of the arm (5). Recovery-towing assembly (1) according to claim 6, characterized in that each connection assembly (12, 13) is mounted to rotate around a third pivot axis (A3) parallel to the first (A1) and second (A2) pivot axes and integral with the arm (5), the rotational movement of each connection assembly (12, 13) around the third pivot axis (A3) being controlled by rotation drive means (11, 51). Recovery-towing assembly (1) according to claim 7 taken as a dependence on claim 2, characterized in that the rotation drive means (11, 51) are rack (51) and pinion drive means (11), which means comprise, for each connection assembly (12, 13), a rack (51) carried by the secondary arm (5b) and a pinion (11) integral in rotation with the third pivot axis (A3) and in engagement with the rack (51), the third pivot axis (A3) being connected to the main arm (5a), such that the sliding of the secondary arm (5b) towards the deployed position causes the rotation of the connection assemblies ( 12, 13) towards the folded position of the wheels (15) and that the sliding of the secondary arm (5b) towards the retracted position causes the rotation of the connection assemblies (12, 13) towards the deployed position of the wheels (15). Recovery-towing assembly (1) according to any one of claims 1 to 8, characterized in that each carrying fork (7) is articulated on the crosspiece (6) around a second articulation axis (X2) orthogonal to the first pivot axis (A1) and arranged such that in use, when the towing basket (2) is in the transport position and a wheel of a vehicle to be towed is received on the carrier fork (7), the fork (7) is able to tilt towards the ground by rotation around the second articulation axis (X2) over an angular range limited by means forming a stop. Towing vehicle (V), characterized in that it comprises a recovery-towing assembly (1) according to any one of claims 1 to 9. Towing vehicle (V) according to claim 10, characterized in that it comprises a stabilizing device (S) carried by the chassis of the towing vehicle (V) and located between a rear axle of the towing vehicle (V) and the second axis pivot (A2) of the recovery-towing assembly (1), which stabilizing device (S) is configured to be moved between a stabilization position, in which it rests on the ground, and a raised position, in which it is removed from the ground.