TECHNICAL FIELD

The present disclosure relates in general to lifting devices of a machine, structure or vehicle body, for momentary needs, from a normal rest or suspension position to a higher elevation position, and in particular to lifting devices adapted to be associated to a suspension damper of the mass of the liftable load.

BACKGROUND

Typically lifting devices are of three types: electromechanical, pneumatic or hydraulic, each type having typical characteristics that makes it adapted to respective categories of application.

An electromechanical system typically comprises transmissions, gears and endless screw devices in order to transform the rotation motion of an electrical motor in a linear motion and suffers from relatively large "start off frictional forces. Low supply voltage applications (e.g. in vehicles) imply start up currents (cross sections of conductors of electrical cables) proportionately large. Moreover, the mechanical components must have good wear resistance and require high precision machining; aspects that make the device relatively expensive.

Pneumatic lifting devices, typically driven by a source of compressed air and controlled by electrovalves, operate at relatively low pressure thus requiring relatively large dimensions of the actuators, hardly compatible with the requirement of reducing encumbrances.

Hydraulic lifting devices use one or several cylinders eventually driven in parallel with a work fluid that is pressurized by a pump, commonly by a volumetric pump, associated to a reservoir of hydraulic fluid, for example a mineral oil. Control of the actuating cylinder or cylinders is implemented through electrovalves normally installed together with the control unit, from which depart pipes of connection to the respective actuating cylinders. These devices, though offering robustness, compactness of the actuators cylinders and reasonable costs, generally imply a complex hydraulic circuit layout that require qualified personal for assembling it, characteristic that lead to a marked criticalness of the accuracy of the installation which ends up to practically increasing overall cost.

There are innumerable applications wherein the numerosity of lifting devices that are required, the need of reducing encumbrance of the devices and of substantially overcoming the laboriousness of assembling and commissioning of the installed lifting device, favor the choice of a more costly electromechanical device notwithstanding its drawbacks and criticalness of optimizing electrical and mechanical parameters and of managing of the large start-off electrical power requirement.

For example, a temporary lifting of the body of a vehicle suspended on common dampers for varying its elevation from the pavement, for example for permitting to run over curbs, pot-holes or abrupt changes of slope or for improving performances and similar needs, requires that the lifting device may be associated to the suspension damper to form an integrated device as compact as possible and which would require connections, for actuating the lifting of the suspended body of the vehicle from the pavement, of maximum simplicity and reliability, in consideration of the harsh solicitations these connections must withstand during travel of a land vehicle.

SUMMARY

Vis-a-vis the known options that under different respects are far from being completely satisfactory for the reasons mentioned above, and specially for applications subject to strong solicitations that require an enhanced level of reliability and simplicity of installation and reduced encumbrance, the applicant has found and developed a solution of surprising effectiveness that offers significant advantages in terms of costs, simplicity of connection to command devices of the lifter, reduced encumbrance and an exceptional adaptability to be integrated in a common suspension damper.

Basically, the device of the present disclosure has an annular body in form of a robust ferrule, an inner-threaded end of which screws over an outer-threaded salient end of a tubular core, in order to define a cylindrical gap space between the annular body and an outer cylindrical wall of the tubular core. The cylindrical gap space thus defined constitutes the chamber of a single-effect actuating cylinder, closed toward said salient end threaded joint by a sealing gasket, and by a cylindrical sleeve piston, telescopically sliding in the cylindrical gap space, between counter opposing ring seals held in annular grooves of the outer cylindrical surface of the tubular core and of the inner cylindrical surface of the annular body.

Within the annular body, is defined a hydraulic circuit that comprises:

a) a variable volume reservoir containing a volume of hydraulic work fluid adapted for the variations of volume of said cylindrical gap chamber of actuating cylinder closed by the sleeve piston, and a compensation air chamber separated by a mobile wall;

b) a bidirectional volumetric electropump for said hydraulic work fluid having a stator windings through which a drive current is passed; c) a one way electrovalve having a coil electrically connected in series to the stator windings of the electropump;

d) a pressure relief safety valve of over pressurized hydraulic work fluid from the chamber of the actuating cylinder back to the variable volume reservoir; and

e) a position sensor of the sleeve piston in said cylindrical gap chamber of actuating cylinder.

An electrical control circuit powers the motor of the volumetric electropump embedded in the lifting device in function of a lift command or of return of the lifted structure to the original position and of a signal representative of the position of the sleeve piston produced by the embedded sensor that monitors the displacement of the load actuated by the lifting device.

Whether the control circuit be installed in a remoted position or within the annular body or near the lifting device, the connections that are required are exclusively electrical realized with common isolated cable. In practice, a two or three conductors power cable and eventually a two or three conductor isolated cable for transmission in one case of the signal produced by the position sensor or of the command signal in the other case, is all what is needed.

According to an embodiment practically suited for integrating the lifting device of this disclosure in a common suspension damper of a road vehicle, the tubular core has inner cylindrical surfaces the profile of which is defined by one or more bore diameters adapted to slip over a generic rest leg or specifically around the stem of a common car suspension damper which often is relatively long in order to allow for an ample excursion of the suspended car body in case of impact against curbs or pot holes and therefore perfectly suited to integrate the lifting device of the present disclosure.

In this case, the cylindrical sleeve piston may terminate with a thrust ring telescopically sliding over the stem of the damper for modifying the separation distance between the two anchoring terminals (effective lengths) of the suspension damper without altering its dynamic response to solicitations.

The different structure of features and the operations of the hydraulic lifting device of the present disclosure, the decisive advantages and particularly effective embodiments will be more easily described in detail by referring to several exemplary embodiments illustrated in the attached drawings purely for illustrative purposes.

The invention is defined in the annexed claims, the content of which is to be considered part of this description.

BRIEF DESCRIPTION OF THE DRAWINGS

Fig. 1 shows a lifting device of the present disclosure integrated in the common suspension damper, by way of orthogonal side views and cross sectional views, in rest position and in lifted position of the load sustained by the suspensions.

Fig. 2 shows a basic functional scheme of the lifting device of the present disclosure during a phase of shifting the load in opposition to a resisting force (typically the weight of the lifted body).

Fig. 3 shows the basic functional scheme during a phase of maintaining a lifted position. Fig. 4 shows the basic functional scheme during a phase of shifting the load in concourse with its weight force.

Figs. 5 and 6 show the basic functional scheme during phases of possible intervention of the safety valve of release of excessive pressure of the working fluid of the hydraulic lifting device.

Fig. 7 shows orthogonal views of a hydraulic lifting device according to an exemplary embodiment wherein significant cross section planes are identified.

Figs, from 8 to 14 are cross sectional views on the significant cross sectional planes of the views of Fig. 7.

DETAILED DESCRIPTION OF EXEMPLARY EMBODIMENTS FIG. 1 provides an immediate perception of the extraordinary compactness of the hydraulic lifting device of the present disclosure that is functionally connectable exclusively by a simple multi conductor cable, being the whole hydraulic circuit and all the functional components of power supply and control, integrated in the device, according to the illustrated embodiment.

Purely by way of exemplification of an important application of the device of this disclosure, in the outer views and in the cross section views of this figure, the hydraulic lifting device 1-4, is shown in association to a common suspension damper of a load, for example, the body of a road vehicle to be raised to a height from the pavement greater than the normal height of suspension when needed. In the two side views a) and b), as well as in the corresponding cross sectional views c) and d), the integrated assembly: namely the damper plus the hydraulic lifting device of this disclosure, is shown respectively in normal operation position and in a raised position.

In the cross sectional views c) and d) of the illustrated embodiment, it may be observed how the tubular core 2 of the lifting device may be simply screwed onto the stem S of the damper, which often is sufficiently long in road vehicles in order to avoid end-of-travel hits when driving over bumps, curbs or pot holes in the road surface, or purposely made as long as necessary for integrating the lifting device of this disclosure by modifying the distance of suspension from the pavement of the body carried on the suspension damper. The sleeve piston 3 of the hydraulic lifting device terminates with a trust ring 4, which, upon commanding the lifting, extends the effective lengths of the damped suspension stem thus lifting the suspended body.

The so equipped suspension dampers allow lifting temporarily according to need the car body sustained on the dampers in order to vary its distance from the road pavement, for example for facilitating the run over obstacles, improve safety and performance intervalling over particularly ragged trains, etc.

Hydraulic lifting devices according to the present disclosure may be associated to all the four suspension dampers of a vehicle or only to the front dampers in order to modify the front suspension distance from the road pavement of the car, for example to avoid problems in travelling onto steep ramps or similar abrupt changes of slope.

Of course, the usefulness of the hydraulic raising device of the present disclosure is not limited to the automotive sector, being perfectly adapted to meet requirements of temporary raising any structure bearing on dampers or on rest legs, over which as many hydraulic lifting devices can be installed.

FIG. 2 is a basic scheme of the hydraulic lifting device that shows the integration within the annular body 1 of the whole hydraulic circuit and of all its components as well as of a sensor of the relative position between piston and cylinder (mobile and fixed part) of a hydraulic actuating device. The scheme further shows how the connection to external parts is essentially of electrical type and precisely for powering the electric motor A of the bidirectional volumetric pump B and possibly for conveying the electrical signal produced by the position sensor L.

The scheme of FIG. 2, shows the operation during the phase of shifting of the load in a direction opposite to a contrasting force, typically the weight force of the load to lift.

The control system, which in the exemplary embodiment is indicated with N, is contained in an appendix Ctrl, external to the annular body 1, though it may be installed, if desirable, at any location, even remote from the hydraulic actuating device. The control system normally receive a command (signal) that activates a power supply circuit that in the exemplary embodiment for a road vehicle, may even be a common inverter adapted to transform the DC voltage of the battery of the vehicle in a AC voltage suitable to power the stator windings of the electrical motor A, in a sequence adapted to make it rotate in the desired direction, in order for the pump B to drive work fluid from the variable volume reservoir F into the actuating cylinder I, through a control check valve C, the coil of which may be simply connected electrically in series to the stator windings of the motor and thus be open anyway in case of a lift command. In such a phase, the electrical opening of the check valve would be superfluous because of the flow direction through the check valve itself, though the possibility of connecting the coil of the control valve in series to the motor winding simplifies electrical connections within the annular body 1.

The compensation air chamber H has the function of compensating the variation of volume of the sealed chamber of the hydraulic fluid that has as mobile wall the wall G of the variable volume reservoir F. In this way, the cylindrical sleeve piston 3 of the actuating cylinder I is thrust out of the base of the annular body 1, thus lifting the suspended load. In this phase, the power required for extending out the cylindrical sleeve is provided by the electrical power source, while the control system N controls the speed of the motor in function of the position signal produced by the sensor L, thus controlling the speed at which the load is raised.

During this phase of operation, part of the fluid pumped by the volumetric pump B is sent also to small pistons E that shift the mobile diaphragm wall G of the reservoir F to vary its volume automatically reducing the volume of a quantity corresponding to the volume of fluid pumped into the actuating cylinder I. The position transducer L, for example a variable inductance transducer, measures the shift providing a signal to the control system N that manages the speed and the stop of the electrical motor upon reaching the desired position.

FIG. 3 replicates the scheme at the conditions of the phase of maintaining the load in the reached position (assuming to be the raised position). In this phase, the position reached by the sleeve piston 3 of the actuating cylinder I is maintained by virtue of the seal provided by the check valve C, which having ceased the excitation current of the motor A, remains closed. In any case, the control system N monitors the maintenance of the position through the signal provided by the position transducer L and eventually intervenes for reestablishing the correct position should it depart from the desired position reached at the end of the preceding phase. The pump B may be momentarily started in one or in the other direction by the control system on order to maintain the desired position (as symbolically indicated by the arrows).

FIG. 4 shows the functional scheme during the phase of shifting of the load in a direction coincident with the direction of the force opposing the lifting (typically the weight force of the load), typically for returning the temporarily lifted body to its normal rest position.

The control system N activates the motor A making it rotate in the direction such that the volumetric pump B sucks hydraulic fluid from the actuating cylinder I sending it into the variable volume reservoir F through the control check valve C which in this phase is maintained open by the current circulating through the stator windings of the motor. The compensation air chamber H compensates the air volume variation of the sealed chamber that has as a wall the mobile diaphragm wall G of the variable volume reservoir F.

In this way, the sleeve piston 3 of the actuating cylinder I returns inside the annular body 1. In this phase, the necessary power is provided by the weight force of the load, while the control system N controls the speed of the motor in order to control the speed of descent of the load. In this phase, the fluid sent to the variable volume reservoir F shifts the mobile wall G of the reservoir F such that its volume adapts itself automatically, increasing by a quantity equivalent to the volume of fluid returning from the actuating cylinder I.

Also in this phase, the position transducer L monitors the piston shift providing a position signal to the control system N that besides the speed of return to the normal suspended position of the load also manages the stop of the electrical motor upon reaching the normal rest position or any other intermediate position if so commanded.

FIGs. 5 and 6 show the scheme of operation at conditions of possible intervention of the safety valve D for limiting the pressure within the actuating cylinder I to design values of correct functioning while avoiding causing seepages of hydraulic fluid and possible breakages in case of malfunctioning or overloading, by providing a pressure relieving bypass path of the fluid pumped in the actuating cylinder I back to the variable volume reservoir F.

The overpressure limiting valve D may intervene in case of impact of the wheels of a vehicle against a curb or rim of a deep hole in the pavement at an excessively high speed such to cause an intense solicitation of the suspensions incorporating the lifting device of the car body or for other reasons of malfunctioning that could occur.

The two elevation views show the sleeve piston 3 terminating with the thrust ring 4, respectively in a completely retracted position and in a completely extended position, telescopically sliding over the cylindrical core 2 of the device, having at the end a common Seeger ring stop.

FIGs. 8 to 14 are layout and side view cross sections in the significant section planes identified in the view of FIG. 7, which make clearly observable the hydraulic connections and the structures of all the functional elements of the hydraulic circuits, identified in the figures by the respective letters: A, B, C, D, E, F, G, H and I, as already described with reference to the schemes of FIGs. 2 to 6, and of the electromagnetic position transducer L. The side view cross sections of FIGs 8 to 11, show the manner in which, in the depicted example, the annular body 1 connects to one end of the cylindrical core 2 like a robust ferrule, screwing on the outer thread 2a of a salient end portion of the outer profile of the cylindrical core 2, thus defining the cylindrical chamber 5 (FIG. 9) that is sealed at one end by the O-ring 6, and closed by the cylindrical sleeve piston 3, telescopically sliding over outer cylindrical surface of the core 2, between opposite scraper rings 7a and 7b, dynamic seals. The hydraulic connection to the chamber 5 of the actuating cylinder is made through ducts 8, defined through the bulk and at the outer coupling surface of the body 1.

The motor A and the volumetric pump B are constituted in an annular space defined within the body 1 resembling a robust ferrule surrounding one end of the tubular core 2, closed by an annular cap 9.

The layout cross section of FIG. 12 allows observing the electrovalve C and the safety valve D, installed in the respective cavities of body 1.

FIG. 13 is a cross sectional layout view (section plane G-G of FIG. 7) wherein is observable the structure of the permanent magnet motor A of the pump B.

The stator 12 is solidly connected to the underlying annular body 1 (FIG. 8) and carries the magnetic expansions with the respective stator windings 13.

The rotor 15, solidly connected to the underlying block carrying the small pistons 18

(shown in the successive FIG. 14) of the pump B, by keys 16. On the rotor 15 are glued the permanent magnets 14.

A modulated current driven through the stator windings 13 creates a torque on the rotor that is transmitted to the block 18 carrying the small pistons 17 (shown in the successive FIG. 14) of the pump B, the direction of which depends from the direction of flow of the current of excitation in the stator windings 13.

A separation bell 11, installed in the gap space of magnetic coupling of the motor, through static O-rings gaskets 10a and 10-b (FIG. 8) seals the rotor region, completely filled of fluid, from the external environment, thus avoiding the use of a dynamic seal gasket, known to be likely to wear and fail.

FIG. 14 is a cross sectional view in the section plane H-H of the volumetric pump B.

In the block 18, rotating around a recessed portion of the annular body 1, there are radially oriented holes into which move pumping pistons 17, which, or more precisely the ends of their stems, are held in contact with the inner cylindrical surface of an outer roll bearing 19 (for example a ball bearing) by the pressure of the work fluid in the hydraulic circuit of the pumping pistons 17 and by the centrifugal force.

The bearing 19 is installed with a certain eccentricity in respect to the rotational axis of the block 18 carrying the small pistons 17 and, as a consequence, during revolution of the block 18 carrying the small pistons, dragged by the overlying rotor 15 (FIG. 13), the pistons 17 held in sliding contact with the inner track ring of the eccentrically installed outer bearing, have a reciprocating motion from a fully inserted position (PMI) to a fully extracted position (PMS).

Therefore, during transitions from PMI to PMS, the pistons 17 "suck in" fluid and during transitions from PMS to PMI, the pistons 17 "compress" the fluid sucked in during the preceding phase.

Semi-circular recesses 20a and 20b, separated by diametrically opposed sealing ridges, respectively at the dead points PMI and PMS, are defined by machining the in the annular body 1, constitute intake and delivery ports of the hydraulic fluid, traveled over by the pistons 17 during revolution of the block 18, and physically separate the two phases of operation of the pump: namely when the pistons suck fluid from the intake recess 20a, and when the pistons compress the fluid in the delivery recess 20b, which are in communication with the respective branches of the hydraulic circuit, upstream and downstream of the pump B, respectively.

Naturally, the construction materials may be chosen during the design phase of the lifting device of the present disclosure taking into account the intended use of the device, the contemplated loads, temperature range of operation, supply voltage as well as of encumbrance and eventual special requirements of light weight, etc.

In the following table are indicated usable materials adapted for automotive applications of the novel lifting device, though special requirements may lead the designer to different choices. REF. DESCRIPTION MATERIALS

A Motor

21 stator Fe-Si laminae

22 stator windings enameled Cu wire

25 rotor malleable iron

24 permanent magnets Ferrite, Neodymium, Samarium, Cobalt

B Volumetric pump

18 rotor carrying the small bronze

pistons

17 small pistons chromium steel

C Control check valve

body of check valve malleable iron

seal reinforced polyamide

D Safety valve alloy steel

E Pistons shifting the chromium steel

mobile wall of the

reservoir

Structural components

1 annular body

2 tubular core

3 sleeve piston Al-Cu alloy (series 2000) or Al-Zn alloy

4 thrust ring (series 7000)

9 annular cap

G mobile wall of variable

volume reservoir

I actuating cylinder chromium coated carbon steel

11 separation bell reinforced polyamide resin or polyacetalic resin

Sealing elements

6 O-ring static gaskets acryl nitril butadiene (nitrilic-NBR rubber) or

7 dynamic seal rings fluorocarbide rubber (Viton-FKM)

scraper rings of pistons

anti seepage packings PTFE (polyetrafluoroethylene) slide guides PTFE resin mix with antifrictional materials

(e.g. bronze, etc.), commercial product: TURCITE