LIFTING MEANS

The invention relates to an automobile scissor lift for raising an automobile, a method for raising an automobile, and a use of said automobile scissor lift.

BACKGROUND

Within the automobile preparation and repair service industry it is often necessary to be able to lift the automobile in order to get access to the automobile from underneath. Such lifting mechanism may for example be provided by an automobile scissor lift comprising actuation means for extending the automobile scissor lift to different heights.

It is an object of the present invention to provide an improved automobile scissor lift for lifting an automobile. Specifically, it is an object to provide an automobile scissor lift, of more simplistic but reliable design and which can lift an automobile in a safe manner.

BRIEF DESCRIPTION OF THE INVENTION

The first aspect of the present invention relates to an automobile scissor lift for raising an automobile, wherein the automobile scissor lift comprises a structural arrangement comprising a base structure, a platform structure, and a scissor mechanism interconnecting said base structure with said platform structure, wherein the scissor mechanism is arranged to allow the platform structure to be extended in a lifting direction from a lowermost position, in which the automobile scissor lift is fully retracted, to an uppermost position, in which the automobile scissor lift is fully extended, wherein the automobile scissor lift further comprises a lifting system for lifting the platform structure to platform positions including the lowermost position and the uppermost position, wherein the lifting system comprises: a primary lifting device comprising a fluid powered linear actuator, preferably a hydraulic linear actuator, comprising a piston in a cylinder housing, wherein the linear actuator is pivotally attached to the structural arrangement and configured to provide an extension of the scissor mechanism and to lift the platform structure to the uppermost position, an auxiliary lifting device configured to provide an extension of the scissor mechanism and to lift the platform structure from the lowermost position to an intermediate position being located between the lowermost position and the uppermost position, wherein the auxiliary lifting means comprises one or more pneumatic bellow actuators.

The automobile scissor lift further comprises a separation mechanism for elevating the platform structure, wherein the separation mechanism comprises an intermediate arm pivotally connected to the scissor mechanism and to the primary lifting device by pivot connections, so that the intermediate arm rotates about the pivot connections of the intermediate arm in response to retraction and extension of the primary lifting device.

By the present invention, the auxiliary lifting device imparts an initial lift to overcome reduced mechanical advantage of the primary lifting device at the lowermost position.

Advantageously, the auxiliary lifting means of the present invention can provide an initial expansion of the scissor mechanisms by lifting the platform structure from the lowermost position to the intermediate position. This can lessen the requirements on the primary lifting device at the lowermost positions of the platform, which is advantageous, since at the lowermost position, the longitudinal extent of the piston of the primary lifting device is close to perpendicular to the lifting direction. Such orientation can be very ineffective in providing a sufficient force transmission from the primary lifting device to the platform structure in order to lift the platform structure to elevated platform positions.

Generally, the higher the first angle is, the higher force is required by the primary lifting device to expand the scissor mechanism from the lowermost position. This in turn increase the strength requirements on the structural arrangement of the automobile scissor lift. Advantageously, by the present invention, at the intermediate position of the platform structure, the scissor mechanism has undergone an initial extension. As the primary lifting device is pivotally connected to the expanding scissor mechanism, the expansion in turn pivots the linear actuator and provides a larger angle between the lifting direction and the longitudinal extent of the piston, such that a larger force transmission can be provided for a more effective lifting operation by the primary lifting means.

Further, by the separation mechanism is obtained an effective initial lift, which is advantageous when working with newer automobiles, e.g. electrically driven cars. Electrically driven cars often have a lower undercarriage compared to older fossil fuel driven cars. When having an older car with a high undercarriage, the automobile scissor lift used for lifting it can often be raised above the lowermost position before the platform structure comes in contact with the undercarriage. This reduced the requirements to the lift. However, when having a newer car with a low undercarriage, the undercarriage will often be almost directly in contact with the platform structure before the automobile scissor lift used for lifting it can be raised above the lowermost position. The combination of the separation mechanism and the primary and secondary lifting devices ensures an effective initial lift overcoming reduced mechanical advantage of the primary lifting device at the lowermost position. The present invention thereby provides an automobile scissor lift, which can provide a more even, and potentially smoother, lifting operation as the platform is more easily lifted from the lowermost position. Furthermore, the automobile scissor lift potentially provides a more efficient utilization of the actuating powers provided by the primary and auxiliary lifting devices, e.g. as the majority of the lifting power of the auxiliary device, potentially all, is transmitted directly along the lifting direction and as the lifting power required from the primary lifting device becomes more even across the lifting operation due to lifting power provided by the auxiliary actuator in the initial lift. Consequently, a primary lifting device of reduced power capacity may be chosen for the inventive automobile scissor lift.

In one or more embodiments, the scissor mechanism is preferably arranged to be retractable and extendable along the lifting direction, so as to transfer the platform structure to different platform positions, e.g. different separation distances from the base structure. In one or more embodiments, the platform positions are defined between the lowermost position and the uppermost position. In one or more embodiments, the automobile scissor lift is arranged so the platform structure is closely adjacent to the base structure at the lowermost position and the platform structure is remote from the base structure, at the uppermost position. In one or more embodiments, the lifting direction is generally perpendicular to the major extent of the platform structure, e.g. in the vertical direction.

In one or more embodiment, the primary lifting device may be arranged to provide a lifting force to the platform structure below the intermediate position, e.g. so that both the primary and auxiliary lifting devices assist in lifting the platform structure below the intermediate position.

In one or more embodiments, the primary linear actuator is pivotally arranged relative to the base structure and/or the platform structure. In one or more embodiments, the linear actuator may be arranged so that an extension of the scissor mechanism decreases the angle measured between the lifting direction and the longitudinal extent of the piston.

In one or more embodiments, the primary lifting device may comprise more than one fluid powered linear actuators, preferably two fluid powered linear actuators. The fluid powered linear actuators may be the same or different. The fluid powered linear actuator preferably operates on differential pressure, and preferably is arranged to lifts the platform in response to an increase in fluid pressure, e.g. by using compressed fluid. In one or more embodiments, the fluid powered linear actuator is a hydraulic or pneumatic linear actuator. Preferably, the fluid powered linear actuator of the primary lifting device is a hydraulic actuator, configured to operate with oil as the working fluid. The fluid powered linear actuator typically comprises a piston providing a second end of the linear actuator and a cylinder, in which the piston can be displaced, and providing a first end of the linear actuator. The fluid powered actuator is preferably connected to a pump (e.g. driven by an electrical motor) and controlled via a control system comprising an interface, such as a control panel, which is configured to control the linear actuator based on inputs on the control panel, preferably from a user. The interface may for example comprise electrical switches.

In one or more embodiments, the primary lifting device comprises two fluid powered linear actuators or the combination of a single fluid powered linear actuator and a mechanical lock for locking the automobile scissor lift at a platform position, so that it does not decrease in case of failure of the single fluid powered linear actuator.

In one or more embodiments, the fluid powered linear actuator is configured to provide a retraction of the scissor mechanism towards the lowermost position of the platform structure. E.g. the fluid powered linear actuator may be arranged with valve(s) allowing for retraction of the scissor mechanism, by fluid pressure forcing a retraction of the linear actuator. Alternatively, or additionally, the linear actuator may enable a retraction of the scissor mechanism by releasing the pressure within the actuator, e.g. on the piston, e.g. by opening a valve.

In one or more embodiments, a longitudinal extent of the fluid powered linear actuator of the primary lifting device extends at a first angle (Al) equal to or above 85°, such as above 88°, to the lifting direction, at the lowermost position of the platform structure.

In one or more embodiments, the first angle may be equal to or above 87°, preferably equal to or above 89°, or above 89.4° or even above 89.7°.

By having the lifting direction being almost perpendicular to the force direction of the linear actuator at the lowermost position, only a small part of the force generated from the linear actuator is transmitted in the lifting direction. This in turn increases the requirements to the strength of the structural arrangement, increases the forces needed from the linear actuator and potentially requires complicated systems to allow sufficient force transmission. However, by the invention of the present disclosure, the auxiliary lifting device enables providing this close to horizontal orientation of the linear actuator, by aiding or overtaking the lifting from the lowermost position to the intermediate position. In turn, this potentially increases the capability of the automobile scissor lift to lift an automobile from the lowermost position, e.g. having a load up to 3500 kg. Consequently, a more simple, reliable and cheaper automobile scissor lift may be provided.

In one or more embodiments, the linear actuator is configured to ensure that the automobile scissor lift can be kept in elevated platform positions, e.g. by means of suitable valves. In one or more embodiments, the longitudinal extent of the linear actuator is at an angle between 20-30° to the lifting direction at the uppermost platform position. In one or more embodiments, the auxiliary lifting device may comprise more than one pneumatic bellow actuator. The pneumatic bellow actuators may be the same or different, e.g. they may be of different size, shape and/or lifting power. The pneumatic bellow actuators are preferably considered as pneumatic bellow actuator actuators, configured to lift an automobile in a lifting direction.

In one or more embodiments, the pneumatic bellow actuator is preferably arranged to lift the platform in response to an increase in fluid pressure, preferably by increasing air pressure within the bellow. The pneumatic bellow actuator is preferably arranged in fluid communication with a compressed gas source, e.g. compressed air source. The pneumatic bellow actuator may be connected to a pump (e.g. driven by an electrical motor) and controlled via control system comprising a control panel, which is configured to control the pneumatic bellow actuator based on inputs on the control panel, preferably from a user. In one or more embodiments, the primary and auxiliary lifting devices are controlled by the same or separate control units of the control system. In one or more embodiment, the pneumatic bellow actuator is preferably arranged to be filled with air to expand the bellow. Alternatively, the bellow may be a pneumatic bellow arranged to be expanded by other sources.

In one or more embodiments, the lifting devices are in fluid communication with fluid sources/reservoirs, fluid supply lines, valve(s) and pump(s) for supplying the desired fluid properties, e.g. pressures, within the actuators. In one or more embodiments, the automobile scissor lift comprises a control system for controlling the lifting device and thereby the extension and retraction of the scissor mechanism. The control system preferably further controls the fluid sources/reservoirs, fluid supply lines, valve(s) and pump(s).

In one or more embodiments, a longitudinal extent of the fluid powered linear actuator of the primary lifting device extends at a second angle (A2) equal to or less than 88°, such as equal to or less than 86°, to the lifting direction at the intermediate position of the platform structure. In one or more embodiments, the second angle is below 90°, such as between 70-90°, such as between 75°-88° or such as between 80°-87°. Advantageously, at the intermediate position, the angle between the linear actuator and the lifting direction is sufficiently decreased for the primary lifting device to take over the lifting operation.

In one or more embodiments, the angle between the longitudinal extent of the linear actuator and the lifting direction is above 70°, such as above 80°, preferably equal to or above 85° at platform positions between the lowermost position and the intermediate position. In one or more embodiments, the angle is between 70°-90°, such as between 80°-90°, such as between 82-87°, preferably between 84-86° when the platform is at platform positions between the lowermost position and the intermediate position.

In one or more embodiments, the auxiliary lifting device is fixed to the structural arrangement between the base structure and the platforms structure.

In one or more embodiments, the pneumatic bellow actuator comprises a first end and an oppositely arranged second end arranged for force transfer from the pneumatic bellow actuator to the structural arrangement, the first end of the pneumatic bellow actuator being fixed to the structural arrangement, and the second end of the pneumatic bellow actuator being in contact with the structural arrangement, when the platform structure is in platform positions between the lowermost position and the intermediate position and the second end of the auxiliary lifting device being separated from the structural arrangement, when the platform structure is in platform positions between the intermediate position and the uppermost position.

By the present embodiment, the pneumatic bellow actuator avoids being continuously expanded as the scissor mechanism is extended, since the auxiliary lifting device is preferably not needed beyond the initial lift. Instead the free end of the pneumatic bellow actuator is allowed to be separated from the structural arrangement, and for example be fully exposed to the surrounding air. The lifting force provided by the pneumatic bellow actuator is preferably substantially perpendicular to the ends of the pneumatic bellow actuator. In one or more embodiments, the ends of the pneumatic bellow actuator may be configured for force transfer from the pneumatic bellow actuator to the structural arrangement.

In one or more embodiments, the pneumatic bellow actuator comprises a hollow flexible body and two oppositely arranged end plates attached to the hollow body. Each end of the pneumatic bellow actuator may comprise such end plate. The lifting force provided by the pneumatic bellow actuator is preferably perpendicular to the end plates and provided by an increase in fluid pressure inside the hollow body. The hollow flexible body may comprise one or more bellows, e.g. the pneumatic bellow actuator may be a convoluted pneumatic bellow actuator, such as a double convoluted pneumatic bellow actuator.

In one or more embodiments, the pneumatic bellow actuator has a maximum lifting height, corresponding to the height of the pneumatic bellow actuator when it is fully expanded, wherein the maximum lifting height is above 140 mm, such as above 160 mm.

In one or more embodiments, the pneumatic bellow actuator has a maximum lifting height (HBmax), being the height of the pneumatic bellow actuator when it is fully expanded, between 150-250 mm, such as between 160-220 mm, or such as between 170- 190mm.

In one or more embodiments, the pneumatic bellow actuator has a minimum storing height (HBmin), corresponding to the height of the pneumatic bellow actuator when it is fully retracted, wherein the minimum storing height is below 110 mm, such as below 100 mm, e.g. between 50-100 mm, such as between 60-90 mm, or such as between 70-80mm. The heights of the pneumatic bellow actuator may be measured perpendicularly to the major extent of the ends, e.g. end plates, of the pneumatic bellow actuator. The pneumatic bellow actuator height is preferably further substantially parallel to the lifting direction.

In one or more embodiments, first end plate of the pneumatic bellow actuator is fixed to the structural arrangement, preferably such that the position of the first end plate of the air spring bellow is fixed relative to the base structure. However, the first end plate could instead be fixed relative the scissor mechanism, e.g. a transverse support structure, or the platform structure. The fixation may be provided by any suitable fastening means, such as screws. The opposite end plate is preferably free, such that it can be separated, e.g. lifted off, the structural arrangement, e.g. the platform structure, upon expansion of the scissor mechanism.

In one or more embodiments, the automobile scissor lift is configured to expand the pneumatic bellow actuator when the platform structure is lifted between platform positions, i.e. in the lifting direction, at least between the lowermost position and the intermediate position. In the separated configuration, the pneumatic bellow actuator may be kept fully expanded, air supply to the bellow may be stopped and/or pressure may be released from the pneumatic bellow actuator. In one or more embodiments, the automobile scissor lift is configured to allow release pressure from the pneumatic bellow actuator, when the platform structure is lowered between platform positions, i.e. opposite the lifting direction, at least between the intermediate position and the lowermost position. The release of air from the pneumatic bellow actuator may be provided by suitable valves and may aided by the retraction of the primary lifting device.

In one or more embodiments, the pneumatic bellow actuator is arranged so that air can escape the pneumatic bellow actuator and the distance between the ends, e.g. end plates can be decreased to a minimum during retraction of the scissor mechanism by the primary lifting device. The free end, e.g. end plate may come into contact with a part of the structural arrangement, e.g. the platform structure, upon retraction of the scissor mechanism, whereby the pneumatic bellow actuator can be squeezed to a smaller height.

In one or more embodiments, at least the free end plate may be of a shape allowing re-engagement with the structural arrangement at platform positions between and including the lowermost position and the intermediate position. E.g. the free end plate may be provided with a hook for latching onto a part of the scissor mechanism or the like.

In one or more embodiments, at least the free end plate is preferably planar, e.g. disc shaped, ring-shaped or plate-shaped, and of a planar extent sufficient for natural and repeated engagement with the opposing part of the structural arrangement, e.g. a planar part of the base structure. Advantageously, by the configuration of the end plate, there is no need to attach both end plates of the pneumatic bellow actuator the structural arrangement, or provide any complicated re-engagement means for ensuring the correct location of the pneumatic bellow actuator during repeated extension and retraction of the automobile scissor lift.

In one or more embodiments, the pneumatic bellow actuator is arranged so that an expansion of the pneumatic bellow actuator provides a lifting force acting on the structural arrangement, wherein the lifting force is substantially parallel to the lifting direction.

Preferably, the lifting force is perpendicular to the ends of the pneumatic bellow actuator, e.g. end plate fixed to the structural arrangement. Advantageously, by providing a lifting force parallel to the lifting direction, an increased amount of the force generated is utilized. In one or more embodiments, the auxiliary lifting means are arranged to operate directly against the platform structure or base structure. In one or more embodiments, the intermediate position of the platform structure is located at a distance of at least 80 mm, such as at least 90 mm, preferably at least 100 mm from lowermost position of the platform structure.

In one or more embodiments, the intermediate position is located at a distance between 80 mm and 130 mm, such as between 90 mm and 115 mm from the lowermost position. The may be measured as the difference in location of a reference point on the platform structure at the intermediate and lowermost position.

In one or more embodiments, the auxiliary lifting device and the primary lifting device may be arranged to provide a lifting force to the structural arrangement simultaneously, and thereby both aid in lifting the platform structure at the same time. This may for example be the case at platform positions between the lowermost position and the intermediate position.

In one or more embodiments, the scissor mechanism comprises a number of pairs of elongated scissor arms arranged in X-shape, wherein several pairs may be attached to one another near ends thereof, so as to produce an array of criss-cross “X” patterns. In one or more embodiments, the scissor arms are arranged so that varying the horizontal distance between them in turn varies the vertical height of the scissor mechanism. The scissor mechanism is preferably based on a pantograph mechanism, i.e. a scissor mechanism with a series of connected parallelograms with hinged intersections that permit repeated elongation and retraction of the mechanism, while maintaining the integrity of the geometric structure.

In one or more embodiments, the scissor mechanism comprises at least one scissor array extending from the base structure to the platform structure, each scissor array may comprise one or more pairs of scissor arms, wherein each pair of scissor arms comprises two scissor arms pivotally attached to each other at a pivot point and arranged so that each scissor arm is rotatable about said pivot point. In one or more embodiments, both the linear actuator and the scissor arms lie in a substantially parallel, e.g. mainly horizontal orientation, when the scissor mechanism is retracted, making the extension of the scissor mechanism from the lowermost position difficult for the linear actuator alone. By the present invention, a more vertical orientation or the linear actuator and arms can be provided by the auxiliary lifting device, so that stresses on the primary lifting device and the scissor arms can be reduced. This is turn lessens the requirements on the scissor arms, such as their rigidity and strength, and may further reduce the amount of lifting force needed from the primary lifting device, since it no longer need to produce very high lifting forces to produce the initial lift, but may instead merely be used for lifting from the intermediate position, requiring much less lifting force.

In one or more embodiments, the scissor mechanism comprises one or more scissor arms, and wherein the scissor arms have a thickness equal or below 30 mm, such as equal or below 25 mm, or such as equal or below 20 mm.

In one or more embodiments, the scissor arms are preferably made of metal, such as metal beams, e.g. structural steel beams. The scissor arms may have a thickness (Tl) between 20-30 mm, such as between 22-27 mm, measured transversely to the longitudinal extent of the scissor arms. The scissor arms may preferably be made of structural steel, e.g. grade s355. The transverse support structures may be made by the same material and thickness.

Advantageously, the low thickness of the scissor arms may in turn enables a narrow width of the overall automobile scissor lift, as the scissor arms take up less space. A narrow automobile scissor lift width is desirable as it in turn covers less of the bottom of the vehicle, which is beneficial for repairs etc.

In one or more embodiments, the scissor mechanism comprises one or more scissor arrays of scissor arms, preferably two arrays of scissor arms, wherein each scissor array comprises at least one pair of scissor arms. Each pair of scissor arms preferably comprises two scissor arms mechanically linked at a pivot point by a first mechanical link. Preferably, the pivot point is located near the longitudinal centre point of each scissor arm, e.g. midway along the longitudinal extent of the scissor arm. The mechanical link may be provided with a shaft extending through both arms, and about which shaft the arms can rotate. Preferably, the mechanical link further comprises bushings for assisting in smooth rotation of the arms relative to each other. The bushings may be self-lubricating bushings. In one or more embodiments, each scissor array preferably bridges the gap between the base structure and the platform structure, e.g. they may preferably be extending from the platform structure to the base structure. The major extent of the platform structure preferably extents over the scissor arrays. Similarly, the major extent of the base structure preferably extents below the scissor arrays.

In one or more embodiments, the scissor mechanism comprises two scissor arrays. In one or more embodiments, the major extents of the scissor arrays are extending in parallel. The major extents further being the planes in which the scissor arms of the arrays can rotate. The shaft is preferably extending perpendicular to the major extend of the pair of scissor arms.

In one or more embodiments, the scissor mechanism comprises two scissor arrays, wherein each scissor array comprises at least one, preferably two, pairs of scissor arms. The pairs may be attached by a pivot point end-to-end to form the array. Two first ends of a first pair of scissor arms may each be attached to a second end of a second pair of scissor arms, so as to forms the array of “X”-shaped pairs. The attachment between arrays may be provided by a second mechanical link, preferably comprising a shaft extending through the arms to be attached and about which the arms may rotate. Preferably, the mechanical link further comprises bearings/bushings for assisting in smooth rotation of the arms relative to each other. The shaft(s) are preferably extending perpendicular to the major extend of the pair of scissor arms. In one or more embodiments, the scissor mechanism comprises one or more elongated transverse support structures structurally fixed at a first end thereof to a first array of the scissor mechanism and a second end thereof to a second array of the scissor mechanism, wherein the first and second array are preferably arranged in parallel. The support structures may each extent from the first array to the second array, and preferably extending perpendicular to the lifting direction. The transverse support structure may aid in stabilizing the scissor mechanism e.g. by fixing the horizontal position of two arrays relative to each other. The transverse supports structure may be metal bars, rods or beams. In one or more embodiments, the transverse support structure may be structurally attached, e.g. welded to scissor arms.

In one or more embodiments, the linear actuator(s) each comprise a first end and an opposite second end, which ends are both pivotally attached to the structural arrangement. E.g. the first end of the linear actuator may be attached to the scissor mechanism, e.g. a transverse support structure, or to the base structure and/or the second end of the linear actuator is attached to the scissor mechanism, e.g. a transverse support structure, or the platform structure.

In one or more embodiments, the first end of the linear actuator is pivotally attached to the structural arrangement and the second end is attached to the scissor mechanism of the structural arrangement, or vice versa.

In one or more embodiments, the linear actuator(s) are pivotally attached between two parts of the structural arrangement, which are mutually displaceable by the scissor mechanism. I.e. the distance between the parts can be varied by the linear actuators applying a force on the scissor mechanism.

In one or more embodiments, both the first and second end of the linear actuator are attached to a transverse support structure of the scissor mechanism. Preferably, these transverse support structures are not fixed to the same scissor arms, e.g. the first end of the linear actuator may be attached to a transverse support structure connected between a lowermost set comprising two lowermost pairs of the scissor mechanism (i.e. the lowermost pair of each scissor array), while the second end of the linear actuator may be attached to a transverse support structure connected between a different set, e.g. between the two second lowermost pairs of the scissor mechanism (i.e. the second lowermost pair of each scissor array), or any other sets above the lowermost set.

In one or more embodiments, the linear actuator comprises a first end pivotally attached to the structural arrangement, e.g. the base structure or a transverse support structure, by a first pivot connection providing a first axis of rotation (XI) and a second end pivotally attached to the structural arrangement, e.g. a transverse support structure or the platform, by a second pivot connection providing a second axis of rotation (X2).

In one or more embodiments, the scissor mechanism comprises two scissor arrays and at least a first and second elongated transverse support structure, each extending from the first scissor array to the second scissor array, wherein the linear actuator comprises a first end pivotally attached to the first transverse support structure by a first pivot connection providing a first axis of rotation (XI) and a second end pivotally attached to the second transverse support structure by a second pivot connection providing a second axis of rotation (X2).

Advantageously, the pivotal attachment of the linear actuator(s) enables the linear actuator(s) to change orientation relative to the lifting direction, and thereby be more horizontal at the lowermost position, and be more vertical at position above the lowermost position for larger transfer of lifting force.

In one or more embodiments, the automobile scissor lift comprising a separation mechanism for elevating the platform structure, wherein the separation mechanism is configured to force the platform structure upwards in response to an extension of the primary lifting device. The separation mechanism preferably comprises an intermediate arm pivotally connected to the scissor mechanism (e.g. a transverse support structure) and to the primary lifting device (e.g. the second end thereof), so that the intermediate arm rotates about the pivot connections of the intermediate arm in response to retraction and extension of the primary lifting device. Preferably, the intermediate arm is arranged so that its vertical extension increases as the longitudinal extent of the primary lifting device increases, preferably at least in the beginning of the lifting operation, e.g. during extension from the lowermost position towards the uppermost position.

In one or more embodiments, the intermediate arm is pivotally attached at a first part to the second end of the linear actuator and pivotally attached at a second part to the structural arrangement, preferably a transverse support structure of the scissor mechanism. The intermediate arm may be arranged to be rotatable about the second axis at the first part of the intermediate arm and about a third axis at the second part of the intermediate arm. The intermediate arm is preferably designed so that upon extension of the linear actuator, the intermediate arm will abut a first attack area at a first end thereof and optionally abut a second attack area at a second end thereof, wherein the first attack area is fixed relative to the platform structure and the second attack area is fixed relative to the base structure, or vice versa, so that upon further extension the intermediate arm will rotate towards a more vertical orientation and thereby increase the vertical distance between the first attack area and the base structure, preferably the second attack area. The intermediate arm is preferably structurally rigid, e.g. made of structural steel. The first and second end of the intermediate arm may each be provided with a wheel or a bushing for allowing sliding or rolling along the attack area.

In one or more embodiment, the separation mechanism further comprises stop arrangement for limiting the rotation of the intermediate arm. The stop arrangement may be provided by a flange and a third attack area arranged between the intermediate arm and the scissor mechanism. The flange may be arranged on the intermediate arm and configured to come into contact and be retained by a third attack area fixed relative to a scissor arm on the scissor mechanism. The automobile scissor lift may be arranged so that in the lowermost position, there will exist a distance between the flange and the third attack area, and so that upon extension of the primary lifting device and the rotation of the intermediate arm the flange will move towards the third attack area. Near the intermediate position the flange abuts the third attack area, thereby preventing further rotation of the intermediate arm upon further extension of the primary lifting device. Instead the further extension of the primary lifting device will provide a lift of the platform structure via the scissor arms.

In one or more embodiments, the intermediate arm rotates by the applied force of the primary lifting device along at least 70%, such as at least 80%, or such as at least 90% of the distance between the lowermost positions to the intermediate position. Preferably the intermediate arm abuts the first and second attack area in the lowermost position. In one or more embodiments, the intermediate arm abuts the third attack area, before, at or after the intermediate position.

Alternatively, the second axis of rotation (X2) is fixed in position relative to the transverse support structure to which the second end of the linear actuator is attached.

In one or more embodiments, the position of the second axis of rotation is fixed relative to the transverse support structure, to which the linear actuator is attached, during extension and retraction of the scissor mechanism, e.g. the transverse support structure and the linear actuator may preferably be directly connected by the second pivot connection.

Advantageously, in the present embodiment, the invention does not need to enable movement of the second axis of rotation transverse to the second axis, which can otherwise be provided by an intermediate arm pivotally connected between the structural arrangement and the primary lifting device, wherein the intermediate arm is configured to induce a lift of the primary actuator, in response to applied force from the actuator itself, e.g. as explained above. Such intermediate arm may be advantageous for producing a larger opening angle and force transmission from the primary actuator to the scissor mechanism. Instead, the present invention may merely provide the auxiliary lifting device as an aid in the initial lifting operation.

Additionally, or alternatively, the position of the first axis of rotation may be fixed relative to the part of the structural arrangement, to which the linear actuator is attached, such as a transverse support structure or the base structure. E.g. said part of the structural arrangement and the linear actuator are directly connected by the first pivot connection.

In one or more embodiments, the first axis of rotation is fixed in position relative to the base structure and may be provided on the base structure, e.g. adjacent and above the base structure. The scissor mechanism may be rotatably fixed to the base structure by the first pivot connection providing a fixed pivot point for the linear actuator.

Alternatively, the first axis of rotation may be fixed in position relative to a transverse support structure of the scissor mechanism e.g. provided near or adjacent the base structure. The scissor mechanism may be rotatably fixed to the transverse support structure by the first pivot connection. The first axis of rotation may be parallel with the transverse support structure, such as coinciding with the longitudinal extent of the transverse support structure. In one or more embodiments, the first pivot connection may be provided by the primary lifting device may comprising one or more housings/through-holes through which the transverse support structure may extent.

In one or more embodiments, the second axis of rotation may be parallel and fixed in position relative to the longitudinal extent of the transverse support structure, such as coinciding with the longitudinal extent of the transverse support structure. In one or more embodiments, the second end of the linear actuator is fixed directly to the transverse support structure, e.g. by a pivot connection comprising a through- hole/housing of the primary lifting device extending about and receiving the transverse support structure.

In one or more embodiments, the first axis of rotation and/or the second axis of rotation may extent substantially in parallel with the major extent of the base structure.

In one or more embodiments, one or more of the pivot connections may comprises a pin/shaft and a housing e.g. a slot or through-hole, in which the pin/shaft can be retained and rotated. The pin may for example be provided by the transverse support structure and a through-hole fixed to the linear actuator may be arranged to enclose the transverse support structure. Alternatively, or additionally, one or more of the pivot connections may be provided by a pin fixed to the linear actuator and arranged to be retained and rotatable in slots, e.g. through holes in the scissor mechanism or in the platform or base structure. E.g. the first pivot connection may be provided by an elongated transverse structure, which at each end thereof is arranged to be retained in a slot in a scissor arm, preferably so that the transverse structure extents transversely between two opposing scissor arms. The linear actuator may be attached to said transverse structure.

In one or more embodiments, the platform structure may preferably comprise a substantially planar support platform, e.g. arranged to come into contact and support an exterior bottom surface of an automobile, such as a car.

In one or more embodiments, the base structure is configured to support the automobile scissor lift on a ground surface, so that the automobile scissor lift is stable at any platform positions of the automobile scissor lift. The base structure may comprise support structures, such as a frame made by brackets, spanning over an area sufficient for the automobile scissor lift to be stable. In one or more embodiments, the scissor mechanism comprises two fixed pivot points provided between a scissor arm and the base structure. Preferably, the remaining pivot points interconnecting the scissor arms and the scissor arms to the platform structure/base structure are moving pivot points. Moving pivot points change their horizontal and/or vertical position upon retraction and extension of the scissor mechanism. The two fixed pivot points preferably share a common pivot axis and may be interconnected by a joint pivot pin or separate pivot pins.

In one or more embodiments, the base structure and/or the platform structure may comprise one or more, preferably two guide tracks. The guide tracks are preferably configured to allow a sliding movement by the scissor mechanism, e.g. an end of a scissor arm of the scissor mechanism, on the guide track. The guide track may preferably be arranged with a slide surface facing toward the scissor mechanism, preferably arranged in parallel with a major extent of the base structure/platform structure, e.g. length thereof extending from the front to the back of the structures.

In one or more embodiments, the scissor mechanism provides two scissor arms ends rotatably attached to the base structure, so that it can rotate about a fixed axis, and two scissor arm ends, which are movable relative to the base structure and slidably arranged within a guide track. Preferably, a similar configuration is provided at platform structure.

In one or more embodiments, the guide track is configured to retain an end of a scissor arm in the guide track. The arm end may be configured with sliding means, such as a sliding structure being e.g. a wheel or preferably a bushing, which is configured to be slidable in the guide track and simultaneously retainable therein.

In one or more embodiments, the base structure is coextensive with the platform structure. E.g. the major extents of the platform structure and the base structure are substantially arranged in parallel. In one or more embodiments, the platform structure provides the uppermost surface at all platform positions of the automobile scissor lift. In one or more embodiments, the base structure provides the lowermost surface at all platform positions of the automobile scissor lift.

In one or more embodiments, the lifting system is arranged between the base structure and the platform structure. E.g. preferably both the primary and auxiliary lifting means are confined between the base structure and the platform structure.

In one or more embodiments, the scissor mechanism is arranged between the base structure and the platform structure. Preferably, the scissor mechanism is confined to the space available between the base structure and the platform structure at all platform positions of the automobile scissor lift. I.e. at fully retracted configuration, e.g. at the lowermost position of the platform structure, the scissor mechanism does not extend beyond the platform and base structure. The same is preferably the case for the lifting system.

In one or more embodiments, the automobile scissor lift is of a height of less than 110 mm, such as less than 105 mm, when the platform structure is in the lowermost position.

In one or more embodiments, the automobile scissor lift is of a height (Hmin) of less than 120 mm, or such as less than 115 mm, when the platform structure is in the lowermost position.

The height is measured as the maximum extent of the automobile scissor lift along the lifting direction, preferably from the top of the platform structure to the bottom of the base structure. Advantageously, by the use of a pneumatic bellow actuator as the auxiliary lifting device, the automobile scissor lift may be retracted to a very low height, making it easier to drive onto by a vehicle and easier to stow away as it requires less storage space. Pneumatic bellow actuators can be retracted to a very low height, e.g. to between 70-75 mm, since they most of the volume between the end plates is fluid e.g. air, which can be removed.

Due to the pneumatic bellow actuator, the different elements of the automobile scissor lift can be simplified, e.g. the scissor arms do not need to be able to withstand large stresses, which would occur if the primary lifting device were to initiate the lift from lowermost position. The scissor arms may therefore potentially be made thinner. Additionally, an intermediate lifting arm in continuation of the primary lifting means may also not be needed further reducing space required by the automobile scissor lift. Potentially, the present invention provides a more energy saving and robust solution with increased exploitation of the capacities and functionalities of the different elements of the automobile scissor lift.

By providing a low height of the automobile scissor lift at the lowermost position, it potentially reduces the need for installing the automobile scissor lift below the ground level, e.g. at a workshop.

In one or more embodiments, the automobile scissor lift comprises a height of at least 500 mm, such as at least 1000 mm, or such as at least 1800 mm, when the platform structure is in the uppermost position. In one or more embodiments, the maximum lifting height may be capped at a pre-determined maximum height, e.g. at 2000 mm.

In one or more embodiments, the auxiliary lifting device is only affective in providing a lifting force to the structural arrangement along 20% or below, such as 15% or below or such as 10% or below, of the extension of the scissor mechanism in the uppermost position. In one or more embodiments, the automobile scissor lift can obtain a height between 80-2500 mm, such as between 90-2200 mm or preferably between 95-2000 mm in the uppermost position.

In one or more embodiments, the lift is a car lift, also known as a car elevator. The automobile scissor lift may for example be used for gaining access to the car from below, e.g. for reparation of the car.

In one or more embodiments, the present invention further relates to a second aspect relating to a system comprising two automobile scissor lifts according to claim 1. By the present invention, two automobile scissor lifts according to the first aspect, i.e. two primary and auxiliary lifting devices are provided for lifting a car, or other vehicle. Preferably, in one or more embodiments and aspects of the present disclosure, the primary lifting devices each comprise two linear actuators, arranged in parallel and preferably attached to the structural arrangement in the same or a similar manner.

In one or more embodiments, two automobile scissor lifts are arranged with a suitable distance between them, so that a safe and stable lift of the vehicle can be undertaken jointly by the automobile scissor lifts. The distance between them may for example be no wider than the width of a car, for example so that the automobile scissor lifts support the car by touching the car bottom between the front and rear set of wheels, e.g. in lifting area marked by the car manufacturer.

Two automobile scissor lift may be arranged adjacent one another with their longitudinal extents arranged in parallel and with a spacing between them, wherein the spacing is measured parallel to the width direction of each automobile scissor lift. Such arrangement may preferably be provided for lifting a car. Advantageously, the spacing allows for access to the bottom of the car, e.g. for repairs etc. Therefore, it is an object to ensure that each automobile scissor lift is not too wide, since that would in turn make the spacing narrower, limiting the access to the car. Advantageously, by the present invention, the requirements on the structural arrangement is lessened since they do not need to withstand large forces from the primary lifting device in the initial part of the lift, therefore making it possible to provide an effective car lift with sufficiently narrow scissor arms width and thereby a sufficiently narrow automobile scissor lift width. Preferably the spacing is free of any obstacles so that complete access to the automobile is possible from below.

In one or more embodiments, the automobile scissor lift comprises a maximum width between 500-700mm. In one or more embodiments, the spacing between the automobile scissor lifts are between 700-900mm.

In one or more embodiments, the platform structure if of a length between 1600- 2200 mm, such as between 1800-2100 mm. This preferably also correspond to the maximum length of the two automobile scissor lift arranged side by side in the system. In one or more embodiments, the automobile scissor lift, e.g. the platform structure comprises one or more inclination surfaces arranged at a longitudinal end of the platform structure. This inclination surface may provide a slope from the ground surface to the platform structure, and may be arranged such that automobiles may be more easily rolled onto said platform structure. In one or more embodiments, the length of the platform structure includes these inclination surface(s) if present.

In one or more embodiments, the system or the automobile scissor lift according to the first aspect further comprises a control system for controlling the operation of the automobile scissor lifts, in particular their platform positions. The control system is preferably shared by the automobile scissor lifts, but may alternatively be separately controlled by separate control units of the control system. In one or more embodiments, the control system is configured to provide synchronized control of the automobile scissor lifts, so that their lifting and lowering operations are synchronized, thereby preferably ensuring correct horizontal alignment of the platform structures and a stable lifting movement of the automobile to be lifted. The lifts are preferably controlled via control panel providing inputs to the control systems which in response thereto control the lifting devices to lower or lift the platform structure.

In one or more embodiments, the system further comprises fluid sources/reservoirs, fluid supply lines, valve(s) and pump(s), of which all or some may be controllable by the control system. Preferably, the valve(s) and pump(s) are controllable by the control system so as to provide the desired fluid properties within the lifting devices. The control system may be fitted with an interface for providing user input, which the control system may be arranged to control the system/automobile scissor lifts based on.

In one or more embodiments, the control system is arranged to increase the height of auxiliary lifting device by introducing air into the pneumatic bellow actuators, in response to user input. Simultaneously and/or subsequently, the control system may be arranged to increase the longitudinal extent of the primary lifting device in response to a user input (e.g. the same or different as the previous user input), e.g. by introducing fluid into the linear actuator, which in turn forces a piston out of a cylinder housing, thereby extending the linear actuator.

In one or more embodiments, the automobile scissor lifts are arranged in a spaced apart arrangement suitable for supporting the automobile when lifted off a ground surface by the system.

In one or more embodiments of the second aspect, the automobile scissor lifts are according to one or more embodiments of the first aspect of the invention.

A third aspect relates to a use of the automobile scissor lift according to the first aspect for lifting an automobile, such as a car, by

- placing the automobile scissor lift on a ground surface, - placing the automobile over the platforms structure, e.g. by driving the automobile over the automobile scissor lift until the automobile scissor lift is arranged between a front and rear wheel of the automobile,

- lifting the automobile by extending the scissor mechanism, and contacting the platform structure of the automobile scissor lift with the automobile, so as to lift the automobile.

The automobile scissor lift may be according to any embodiment(s) of the first aspect of the present disclosure. The automobile scissor lift may be configured to lift the automobile, so that it can be supported by the automobile scissor lift in elevated positions. E.g. the automobile scissor lift may be configured to lift the automobile in lifting areas arranged between the front and rear ends of the car, e.g. between each set of front and rear wheel extending along a line from the front to the rear of the car. In one or more embodiments, the scissor mechanism is extended and retracted by the lifting system, e.g. by at least the auxiliary lifting device from the lowermost position up until the intermediate position and by the primary lifting device from the intermediate position to the uppermost position.

A fourth aspect of the present invention relates to the use of a system comprising two automobile scissor lifts according to the above for lifting an automobile, such as a car, by placing the automobile scissor lifts on a ground surface, driving the automobile over the automobile scissor lifts until each automobile scissor lift is arranged between a front and rear wheel of the automobile, lifting the automobile by extending the scissor mechanisms, and contacting the platform structures of the automobile scissor lifts with the automobile, so that the automobile is lifted off the ground surface.

A fifth aspect of the present invention relates to a method for raising an automobile, such as a car, comprising the steps of: providing a system comprising two automobile scissor lifts according to the above; placing the two automobile scissor lifts on a ground surface; driving the automobile over the automobile scissor lifts until each automobile scissor lift is arranged between a front and a rear wheel of the automobile, lifting the automobile by extending the scissor mechanisms, and contacting the platform structures of the automobile scissor lifts with the automobile, so that the automobile is lifted off the ground surface.

By the uses of the automobile scissor lift and the method for raising an automobile using the automobile scissor lift according to the present disclosure, a potentially more smooth lifting operation is provided, as the difficult initial lift is more readily undertaken by the lifting device according to the present disclosure. Less force is required by the primary lifting device, which in turn lessens the requirements on strength and structure of the structural arrangement. A more durable automobile scissor lift may also be provided by the present invention as the automobile scissor lift is simple in design and requires no complicated parts to interact. Furthermore, the pneumatic bellow actuator is a cheap and reliable solution.

In one or more embodiments of the third, fourth or fifth aspect, a protective block or sheet may be provided between the platform structure and the automobile in order to protect the automobile. Due to the low height of the automobile scissor lifts in the lowermost position, the automobile scissor lift may advantageously simply be placed on the ground surface and do not need to be placed in a pit in the ground. Though that is also an option with the present automobile scissor lift. Also due to the low height of the automobile scissor lifts in the lowermost position, the automobile, e.g. car, may simply and easily drive over the automobile scissor lift in order to place the automobile scissor lifts between the front and back wheels, even heavy cars and cars with limited gap to the ground i.e. low ground clearance cars, e.g. with low spoilers or damaged suspension may overcome the low height. In one or more aspects/embodiments of the present disclosure the automobile scissor lift may be placed on a line extending along the longitudinal extent of the automobile, i.e. from the back to the front, between a front and back wheel. Manufactures often mark where the car may be lifted.

In one or more embodiments, the scissor mechanism is extended and retracted by the lifting system. The scissor mechanism may be extended by both the auxiliary device and/or the primary device or both simultaneously. In one or more aspects/embodiments of the present disclosure, the automobile scissor lift may be extended from the lowermost position by the auxiliary lifting device, then the auxiliary lifting device together with primary lifting device and then subsequently by the primary lifting device beyond the intermediate position.

The system may further comprise a control system for synchronized control of the operation of the automobile scissor lifts supporting an automobile, and the use may further comprise controlling the extension and retraction of the automobile scissor lifts between platform positions by the control system.

The system may be according to any embodiment s) of the second aspect and comprising automobile scissor lifts according to one or more of the embodiments according to the first aspect.

DRAWING

Aspects of the present disclosure will be described in the following with reference to the figures in which:

Fig. la shows a first embodiment of the automobile scissor lift according to the present invention, seen from the side,

Fig. lb shows the automobile scissor lift of Fig. la, seen from the front,

Fig. 2 shows a cross-sectional view of the automobile scissor lift of Fig. la in the lowermost position of the platform structure, Fig. 3 shows a cross-sectional view of the automobile scissor lift of Fig. la in the intermediate position of the platform structure,

Fig. 4 shows a force diagram of the generated force of the linear actuator in the lowermost position and in the intermediate position of Fig. 2 and Fig. 3,

Fig. 5 shows a cross-sectional view of the automobile scissor lift of Fig. la in the uppermost position of the platform structure, and, Fig. 6 shows a first embodiment of a system according to the present invention, wherein the system comprises two automobile scissor lifts.

DETAILED DESCRIPTION OF THE INVENTION

Fig. 1 illustrates a automobile scissor lift 1 according to embodiments of the invention, seen from the side. The automobile scissor lift 1 comprises a structural arrangement 2 including a platform structure 4 for supporting the automobile to be lifted and a base structure 3 for placing the automobile scissor lift 1 on a ground surface 20. The structural arrangement 2 further includes a scissor mechanism 5 between the platform structure 4 and the base structure 3. The scissor mechanism 5 provides an “X”-pattem of scissor arms 6 connected by pivot points 13, such that the scissor mechanism 5 is extendable and retractable along the lifting direction LD thereby providing a change the vertical distance between the platform structure 4 and the base structure 3. The extension of the scissor mechanism 5 is driven by the lifting device 15, which comprises a primary lifting device 16 and an auxiliary lifting device 17. In the present exemplary embodiment, the primary lifting device 16 comprises a two fluid powered linear actuators, preferably being a double hydraulic cylinder, which are pivotally attached to the structural arrangement 2. The auxiliary lifting device 17 comprises one or more pneumatic bellow actuators 17 arranged between the base structure 3 and the platform structure 4, so as to provide a lifting force onto the platform structure 4 upon expansion of the pneumatic bellow actuator(s) 17. In the present example, a single pneumatic bellow actuator 17 is used, which is fixed in position relative to the base structure 3. In Fig. lb the automobile scissor lift 1 of Fig. la is shown as seen from the front. The automobile scissor lift 1 is shown comprising two scissor arrays 8. As seen in Figs, la, each array 8 is a “double scissor” comprising two pairs of scissor arms 6, each pair being pivotally connected by a first mechanical link 14a near longitudinal centres thereof by a pivot point 13. For each array 8, the two pairs of scissor arms 6 are further pivotally connected by second mechanical links 14b by interconnecting two scissor arm ends 7 of each pair in a pivot point 13, so as to form the scissor array 8. Each scissor array 8 comprises two upper scissor ends 7 connected to the platform structure 4 and two lower scissor ends 7 connected to the base structure 3, which will be described in further details later in the present disclosure.

Fig. lb shows the two scissor arrays 8, which are preferably arranged in a substantially mirrored configuration about a longitudinal centre of the automobile scissor lift 1. The scissor arrays 8 are connected by a number of transverse support structures 2a, some which may further provide support for attachment of the primary lifting device 16 and/or a separation system 18, as described in further detail below. Each array 8 extends from the base structure 3 to the platform structure 4. The auxiliary lifting device is shown placed on the platform structure 3. The scissor arms 6 of the automobile scissor lift 1, can be made relatively thin since they do not need to be able to withstand large forces from the primary lifting device 16 in the initial lift. Thickness of scissor arm Tl, see Fig. lb, is in preferred embodiments between 20-30mm, such as below or equal to 25 mm. Other parts, e.g. the transverse support structure 2a may similarly be reduced in thickness and/or structural strength.

The automobile scissor lift 1 in Fig. la and lb further comprises two inclination surfaces 9, at each longitudinal end of the platform structure 4. This provide surfaces 9 for aiding in smooth passage of an automobile, e.g. a car, onto and off the automobile scissor lift 1. However, these inclination surfaces 9 are optional features. Fig. la depicts the length of the automobile scissor lift LI, which in the present example includes the inclination surfaces 9, and which may be between 1800-2200 mm.

Fig. 2 shows a cross-sectional view of the automobile scissor lift 1, when the automobile scissor lift 1 is in the lowermost position PL. The cross-section is provided in a longitudinal plane substantially extending along the longitudinal direction and height direction of the automobile scissor lift 1. The auxiliary lifting device 17 of the automobile scissor lift is in this lowermost position in a collapsed position in which preferably no fluid is being pumped to the inside of the bellow actuator 17. As seen in Fig. 2, a cylinder housing 27 and a piston 28 arranged in the housing 27 of one of the hydraulic linear actuators of the primary lifting device 16 is shown. The same configuration is provided for the second hydraulic linear actuator of the primary lifting device (not shown). The first angle Al measured between longitudinal extent of the primary lifting device LP, e.g. the piston, and the lifting direction LD at the lowermost position PL, may be above 89.2° and 89.5°. At such angles, the force component of the force of the piston upon expansion F PL being parallel to the lifting direction LD, i.e. the X-component Fx_PL is very small, as can be seen in Fig. 4.

Fig. 3 shows a cross-sectional view of the automobile scissor lift 1, when the automobile scissor lift 1 is the intermediate position PI. The cross-section is provided in a longitudinal plane substantially extending along the longitudinal direction and height direction of the automobile scissor lift 1, preferably coinciding with the plane of Fig. 2. In Fig. 2 the automobile scissor lift 1 has been lifted to the intermediate position PI by the auxiliary lifting device 17, optionally in collaboration with the primary lifting device 16. The pneumatic bellow actuator 17 is seen expanded to its maximum height HBmax. The height of the pneumatic bellow actuator is in general measured along the lifting direction LD, e.g. between a first end 17a and second end 17b of the pneumatic bellow actuator 17. Due to the expansion of the pneumatic air bellow 17, the angle between the longitudinal extents of the primary lifting device 16, indicating the direction of the generated force, and the lifting direction is at a second angle A2 measured to be below 88°, such as below 86° or such as below 80°. In the present exemplary embodiment it is between 82-84°. The decreased angle, increases the force transfer in the lifting direction, which is also depicted in Fig. 4.

Fig. 4 shows a force diagram of the force F_PI, F PL applied by the primary lifting device at the lowermost position (solid line) and at the intermediate position (dashdot line). The force F PL is shown divided into its x- and y-components, being denoted Fx_PL and Fy_PL, respectively, wherein the y-component extents parallel to the lifting direction LD. The force F_PI is shown divided into its x- and y- components, being denoted Fx_PI and Fy_PI, respectively, wherein the y-component extents parallel to the lifting direction LD. As can be seen in Fig. 4, the y-component, provided by the primary lifting device in the lowermost position, Fy_PL, is very small compared to the y-component provided by the primary lifting device in the intermediate position, Fy_PI. In the intermediate position, more of the force generated by the primary lifting device is thereby transferred along the lifting direction LD, than in the lowermost position. If the primary lifting device was to provide the lifting operation from the lowermost position alone, it would according to the force diagrams, thereby require a very large force F PL to provide enough force along the lifting direction LD. By the present invention comprising the auxiliary lifting device, the force requirements on the primary lifting device in the lowermost position are thereby significantly reduced.

As shown in Fig. 2, by the present invention the automobile scissor lift 1 can obtain a minimum automobile scissor lift height Hmin, measured between the base structure 3 and the platform structure 4, which is below 110 mm, such as below 105 mm. As shown in Fig. 3, by the present invention the automobile scissor lift 1 can obtain an intermediate automobile scissor lift height Hint, measured between the base structure 3 and the platform structure 4, which may be at least 150 mm, such as between 150- 300mm, such as between 175-225mm. In one or more embodiments, the distance between the lowermost position PL and intermediate position PI may be measured by subtracting the minimum automobile scissor lift height from the intermediate automobile scissor lift height, Hint-Hmin. The distance may be between 30-200mm, such as between 50-150mm. In the intermediate position PI, the auxiliary lifting device 17 of the automobile scissor lift is preferably in it most expanded state, e.g. providing a maximum height HBmax of the bellow actuator 17.

As seen in Fig. 2, the primary lifting device 16 is at a first end 16a pivotally attached by a first pivot connection 21 to the scissor mechanism 5, e.g. a first transverse support structure, so that it may rotate about a first axis of rotation XI, and at a second end 16b pivotally attached by a second pivot connection 22 to separation system 18 comprising an intermediate arm 19 connecting the second end of the primary lifting device 16b, e.g. an end of the piston, to the scissor mechanism 5, e.g. a second transverse support structure. The intermediate arm 19 comprises a first end 19a pivotally attached to the second end of the primary lifting device 16b at the second pivot connection 22, preferably so that both the intermediate arm 19 and the primary lifting device 16 can rotate about the second axis of rotation X2. The intermediate arm 19 further comprises a second end 19b arranged opposite the first end 19a. The intermediate arm 19 is preferably pivotally attached to the scissor mechanism 5, preferably so that the intermediate arm 19 can rotate relative to the scissor mechanism 5, e.g. about a third axis of rotation X3.

As seen in Figs. 2 and 3, from the lowermost position PL to the intermediate position PI, the expansion of the scissor mechanism 5 has caused the primary lifting device 16 to rotate to a more vertical orientation. The rotation may be undertaken about the first axis XI and/or a pivot point 13 connecting the first end 16a to the base structure 3 (see also Fig. 5). The rotation is preferably further undertaken about the second axis of rotation X2. As seen in Fig. 3, the automobile scissor lift 1 is preferably arranged so that an expansion of the piston 28 from the housing 27, e.g. from the lowermost position, causes a first end of the intermediate arm 19a to push against a first attack area 23, fixed relative to the platform structure 4, so as to provide a lifting force on the platform structure 4. Upon further extension of the piston 28 from the housing 27, the intermediate arm 19 in return preferably rotates about a pivot point providing the third axis of rotation X3, preferably towards a more vertical orientation, and eventually a second end of the intermediate arm 19b will pushes against a second attack area 24, fixed relative to the base structure 3. Preferably, during at least a part of the lifting operation of the platform from the lowermost position to the uppermost position, e.g. from the lowermost position towards the intermediate position PI, the arrangement of the separation system 18 is such that the first end 19a abuts the first attack area 23 and simultaneously, the second end 19b abuts the second attack area 24 and in this configuration, upon further extension of the piston 28 the platform structure 4 and the base structure 3 are forced apart by the help of the intermediate arm 19, as a more vertical orientation of the longitudinal extent of the arm 19 is generated. The rotation of the intermediate arm 19 is preferably stopped by a stop arrangement comprising a flange 26 of the intermediate arm 19, which at a specific extension, will abut against a third attack surface 25 preventing further rotation of the intermediate arm 19. The stop arrangement may be activated close to the intermediate position PI of the automobile scissor lift 1, or beyond the intermediate position towards the uppermost position. Thereafter, the force generated by the primary lifting device 16 is transferred to the scissor mechanism 5 and utilized in providing an extension thereof.

If the separation system 18 and the intermediate arm 19 is not used, the primary lifting device 16 may instead in an alternative example not covered by the invention, be pivotally connected to a second transverse support structure. The intermediate arm 19 may in an alternative example not covered by the invention be omitted, if the auxiliary lifting device 16 can provide the initial lift and increase the angle between the longitudinal extent of the primary lifting device LP and the lifting direction LD, see Fig. 2.

Fig. 5 shows a cross-sectional view of the automobile scissor lift 1 extended to the uppermost platform position PU which preferably is provided at a height Hmax below 2000 mm, such as at 1995 mm. Further extension may be prevented by electrical or mechanical means for safety reasons. The auxiliary lifting device 17 is shown arranged at the base structure 3, and in this platform position, there is preferably no air being supplied to the interior of the pneumatic bellow actuator 17 in this platform position. The primary lifting device 16 is extended to provide the extension of the scissor mechanism 5, which is undertaken by rotation in the pivot points 13, 13a, 13b. Furthermore, the flange of the optional intermediate arm 26 is preferably abutting the third attack area 25.

As seen in Fig. 5, a first lower scissor arm end 7 of the scissor array 8 is attached to the base structure 3 by a pivot point 13b, preferably by being slidably retained to the base structure 3, and a first upper scissor arm end 7 of the scissor array is attached to the platform structure 4 by a pivot point 13b, preferably by being slidably retained to the platform structure 4, so that a retraction and extension of the scissor mechanism 5 can be undertaken. The slidable retention of the pivot points 13b at the base structure 3 and platform structure 4 may be provided by fitting the scissor arm end 7 with a bushings 10a, which is received in a guide rail 10 on the base structure 3 / platform structure 4, so that it is slidably retained therein, as seen in Figs, lb and 5. The guide rails 10, bushings 10a for each array 8 are further depicted in Fig. lb. Other means for providing the slidable retention may alternatively be provided, e.g. by using wheels instead of bushings.

Fig. 5 further shows a second lower scissor arm end 7 of the array 8 attached to the base structure 3 by a fixed pivot point 13a, preferably such that the pivot point 13a is fixed in position during operation of the automobile scissor lift 1. The array 8 further comprises an second upper scissor arm end 7 attached to the platform structure 4 by a pivot point 13, which is fixed relative to the platform structure 4, but which vertical position changes upon retraction and extension of the automobile scissor lift 1.

In the view of Fig. 5, only one scissor array 8 of the scissor mechanism is visible, however, the second scissor array (as seen in Fig. lb) preferably comprises the same arrangement of pivot points 13, 13a, 13b, preferably arranged in a mirrored configuration about a longitudinal centre plane of the automobile scissor lift. Preferably, the slidably retained pivot points 13b of the arrays 8 are arranged either at the front or the back of the automobile scissor lift 1. In the present examples, the slidably retained pivot points 13b of the arrays 8 are arranged in the front end of the automobile scissor lift 1, as seen e.g. in Fig. 5.

In one or more embodiments, e.g. as seen in Figs. 1-5, the automobile scissor lift 1 is arranged so that in order to lift the platform structure 4 from the lowermost position PL, fluid, such as air, is pumped into the pneumatic bellow actuator 17, so as to expand the pneumatic bellow actuator 17 so that it provides a separation of the base structure 3 and the platform structure 4 and thereby provides a lifting force on the platform structure 4 towards an elevated position. Simultaneously or subsequently, the hydraulic actuator 16 is activated by hydraulic supply so as to provide an extension of the piston 28 from the housing 27 and a force onto the structural arrangement 2. The force may be translated into a lifting force by being provided directly on to the structural arrangement 2, e.g. the platform structure 4 or the scissor mechanism 5, in a suitable position, and/or by the aid of a separation system 18. Both lifting devices 16, 17 are preferably further extended until the intermediate position PI, in which the maximum height of the pneumatic bellow actuator 17 preferably is reached, and after which, the pneumatic bellow actuator 17 may separate at one end thereof from the structural arrangement 2. At higher elevated positions beyond the intermediate position PI, the pneumatic bellow actuator 17 may thereby no longer aid in lifting of the platform structure 4. From the intermediate position PI to the uppermost position PU, preferably only the primary lifting device 16 provides the lifting of the platform structure 4, by acting on the structural arrangement 2 so as to extend the scissor mechanism 5.

The automobile scissor lift 1 may be used for lifting an automobile, e.g. a car or smaller vehicles. The automobile may be placed over or on the platform structure 4 and lifting by the automobile scissor lift 1. Fig. 6 shows a system 30 according to embodiments of the invention, seen in perspective, wherein the system 30 comprises two automobile scissor lifts 1 according to the invention e.g. as shown in any of the Figs. 1-5. The system 30 is configured to be used as a car lift system, e.g. by positioning the automobile scissor lifts 1 so that the longitudinal extent of the platform structures 4 thereof are arranged between the wheels of the car and substantially parallel to the length of the car measured from the front end to the back end of the car. The automobile scissor lifts 1 are preferably arranged with a distance SI apart suitable for lifting the car at areas between the front and back wheels. The distance SI is preferable between 750- 850mm. The total width of each automobile scissor lift 1 W1 is preferably between 550-650mm. The automobile scissor lifts 1 are preferably controlled by a control system 12 and connected to appropriate drive means and fluid sources, e.g. by fluid lines 11. As seen in Fig. 6, each automobile scissor lift 1 is equipped with a pneumatic bellow actuator 17, e.g. fixed to the base structure 3, and a primary lifting device 16, e.g. two hydraulic linear actuators.

The system 30 of Fig. 6 may be used as a car lift by driving the car over the automobile scissor lifts 1 in the lowermost position e.g. until each automobile scissor lift 1 is arranged between a front and rear wheel of the car, lifting the car by extending the scissor mechanisms 5. The platform structure 4 preferably provides the interface between the car and the automobile scissor lift 1 for transferred the lifting force and lifting the car.

REFERENCE LIST

1 automobile scissor lift

2 structural arrangement

2a transverse support structure

3 base structure

4 platform structure

5 scissor mechanism

6 scissor arm

7 scissor arm end

8 scissor array

9 inclination surface

10 guide track

10a bushing

11 fluid lines

12 control system

13 pivot point

13a fixed pivot point

13b slidably retained pivot point

13c pivot point of the separation system

14a first mechanical link

14b second mechanical link

15 lifting system

16 primary lifting device, e.g. fluid powered linear actuator

16a first end of primary lifting device

16b second end of primary lifting device

17 auxiliary lifting device, e.g. an pneumatic bellow actuator

17a first end of pneumatic bellow actuator, e.g. first end pate

17b second end of pneumatic bellow actuator, e.g. second end plate

18 separation mechanism

19 intermediate arm

19a first end of intermediate arm 19b second end of intermediate arm

20 ground surface

21 first pivot connection of the primary lifting device

22 second pivot connection of the primary lifting device

23 first attack area

24 second attack area

25 third attack area

26 flange on intermediate arm

27 cylinder housing

28 piston

30 system of automobile scissor lifts

Al first angle

A2 second angle

F PL Primary lifting device force in the lowermost position

Fx_PL X component of the primary lifting device force F PL

Fy_PL Y component of the primary lifting device force F PL

F_PI Primary lifting device force in the intermediate position Fx_PI X component of the primary lifting device force F_PI

Fy_PI Y component of the primary lifting device force F_PI

HB height of air below

Hmax maximum height of the automobile scissor lift, at uppermost position

Hmin minimum height of the automobile scissor lift, at lowermost position

Hint height of the automobile scissor lift at intermediate position W 1 width of automobile scissor lift, e.g. platform structure

LI length of automobile scissor lift, e.g. platform structure

SI spacing between automobile scissor lifts of a system LD lifting direction

LP longitudinal extent of the fluid powered linear actuator

PL lowermost position

PI intermediate position PU uppermost position

T1 scissor arm thickness

XI first axis of rotation

X2 second axis of rotation X3 third axis of rotation