Hydraulic handling device

Abstract

 Hydraulic handling device comprising two rotation axles (X1, X2) to which are attached numerous elements in which a pressurised liquid is inserted. These two rotation axles (X1 and X2) are constrained to have a predetermined rotation ratio by means of transmission devices (M). At least one input conduit (I) is present and at least one output (U) for the pressurised liquid that determines the synchronous rotation of the axles. These elements are arranged in such way as to form a ring chamber for the pressurised liquid, in which a rotating piston moves; the movement of the latter fills a filling portion of said chamber with liquid and at the same time empties a draining portion of said chamber of liquid and conveys it towards the output conduit.

Description

[0001] This invention refers to a hydraulic handling device aimed at operating with uncompressible fluids. In particular, the device in this invention may be used as a hydraulic motor or as a pump in that it is completely reversible. Generally hydraulic motors use the kinetic energy possessed by a liquid under pressure, which, before discharging and returning into circulation to be compressed by a pump, activates a moveable piston in a cylinder (in the alternative type e.g. in the hydraulic jack) or one or more rotating organs (in the rotating type with caps, blades or lobes).

[0002] Depending on the type of use, hydraulic motors must be appropriately sized. In particular, the dimensions of the motor are closely linked with the required driving couple and the relative maximum rotation speed obtainable.

[0003] This invention refers to a hydraulic handling device manufactured in such way that by varying the quantity of liquid utilisable in the motor it is possible to vary the operating conditions: for instance, the maximum couple obtainable in case of operating as a motor and the consequent maximum rotation speed. The subject of this invention is a hydraulic handling device according to claim 1 to which one is referred to be brief.

[0004] Further features and advantages of the device according to this invention will be more clearly evident from the following description, giving examples but not limited, referred to the schematic drawings attached, in which:

Figure 1 shows the device described in this invention in a prospective view;

Figure 2 shows a view from above of the lower cylindrical element;

Figure 3 shows the central cross section of the element in Figure 2;

Figure 4 shows the view from above of the lower bowl;

Figure 5 shows the cross section along A-A of figure 4;

Figure 6 shows the view from above of the cylindrical piston-guide bowl;

Figure 7 shows the cross section along B-B of figure 6;

Figure 8 shows the view from above of the dual ring element;

Figure 9 shows the cross section along C-C of figure 8;

Figure 10 shows the schematic cross section of the positioning of the dual ring element, the cylindrical piston-guide bowl, the lower bowl and the lower cylindrical element;

Figure 11 shows an exploded view of the rotating parts of the device described in this invention;

Figure 12 shows the horizontal cross section of the piston;

Figure 13 shows the vertical cross section of the piston.

[0005] The device illustrated for the purpose of an example in the attached figures shows two rotation axles X1 and X2 substantially placed parallel to each other to which a number of cylindrical elements are attached in which the pressurised liquid is inserted.

[0006] These two rotation axles X1 and X2 are constrained to have a predetermined rotation ratio by means of transmission devices M having pulley gears, chains or equivalent means.

[0007] The device also comprises an input conduit I and one for output U for the pressurised liquid which determines the rotation of the same.

[0008] In detail, to one rotation shaft 2 which makes up the first axle X1 is associated a lower cylindrical element 21 not having an upper surface and a lower bowl 22 fitted with a number of U shaped slots 221 on the lateral surface. A second rotation shaft 3 makes up the second rotation axle X2, to which is associated a cylindrical covering element 31, below which is arranged a cylindrical bowl 32 piston-guide presenting a slot in which a radial piston 33 is housed. Between the two shafts a dual ring element 4 is formed which includes a first ring 41, below which the bowl 22 is perfectly located, intersected by a second ring 42 inside which is envisaged said radial piston 33 fixed to the second shaft 3 and which also presents a slot 321 in which said piston is housed and which rotates with it.

[0009] This radial piston is substantially made in the shape of an "L" inside which there are conduits for the pressurised liquid of the device. The piston rotates inside a peripheral ring portion 43 of the second ring which coupled with the base 322 of the bowl 32 piston-guide and with the side wall of the lower bowl causes a ring chamber closed by the bowl 22 in at least one of the two intersection points with the ring 42, into the chamber of which is inserted the liquid from the channel inside the piston.

[0010] In the functioning of the device as a motor, pumping the liquid through the conduit present in the piston one fills a filling portion of said chamber and this causes the rotation of the piston itself.

[0011] The slots 221 forming a "U" permit, in relation with the rotation synchronism determined by the transmission devices M, the free passage of the piston across the points of intersection 44 and 45 between the two rings of the dual ring element 4. These slots are sized in such way as to guarantee the total and permanent closing of the volume travelled by the liquid, therefore when a slot intersects the ring the piston moves through, the other intersection remains totally closed because there is no other slot in it.

[0012] At the same time, in a draining portion of the above mentioned ring chamber, the movement of the piston causes the emptying of the chamber itself and the channelling of the liquid towards the output conduit U.

[0013] The passage ways of the liquid (introduction and expulsion) may be made inside the rod of the piston and thus of the axle and then transit in external piping by means of two frontal and coaxial junctions situated at two different points of the axle (one for introduction and the other for expulsion). Alternatively, the conduits may be made by means of concentric rings situated below the piston-guide bowl 32 and then run into the bowl itself in the immediate proximity of the piston. Any possible change in the volume of work of the chamber is made through transfer to the shaft 3 of the piston-support bowl 32 in relation to the dual ring element, with contemporary transfer to the shaft 2 of the bowl 22. A reduction or an increase of this volume means a decrease or increase of the driving couple delivered by the hydraulic motor. This regulation may be advantageously obtained by acting contemporaneously on the shaft 3 moving the point of joining of said piston-support bowl and on shaft 2 moving the point of joining of the bowl 22. The advantages attained by this invention are relative to the total absence of dead points, the direct operating with a circular movement, without the need for connecting rods and/or jack handles and perfect reversibility.

[0014] Furthermore, the motor according to this invention has the possibility of operating at low speeds and even step by step.

[0015] Varying the volume of work it will therefore be possible to obtain any speed and any power whatsoever, leaving the input energy unchanged: both in the case of energy supplied under the form of torque and in the case of energy supplied under the form of pressure in a fluid.

[0016] From the description carried out, the features of the device, subject of this invention, are clear just as the advantages are.

[0017] Finally, it is clear that numerous other variations can be made to the invention in question, without for this reason leaving the principles of novelty implied in the inventive idea, just as it is clear that in the practical activation of the invention, the materials, the shapes and the sizes of the details illustrated may be of whatsoever type depending on the needs and the same may be substituted with others that are technically equivalent.

[0018] The variations may contemplate motors in which the two rotation shafts are not parallel. However, for this case the volume of work may not be variable. Then again, it is possible to contemplate the presence of three shafts, one for the piston and another two for two different elements with slots, situated in two different points of the ring travelled by the piston and suitably synchronised. However, it remains true that the mouths for input and output of the fluid must rotate together with the piston and be located inside it or in the immediate vicinity. Furthermore, the ring travelled by the piston must be closed in two different points with synchronised elements, to open in order to allow passage of the piston and the relative mouths, but in such way that, when one of the two elements is totally or partially open, to allow this passage, the other is totally closed.

Claims

1. Hydraulic handling device, characterised by the fact that it comprises:

• at least two rotation axles (X1, X2) to which are associated a number of elements in which the pressurised liquid is inserted,

• said two rotation axles (X1 and X2) being constrained to have a predetermined rotation ratio by means of transmission devices (M),

• at least one input conduit (I) and at least one of output (U) for the pressurised liquid which determines the synchronised rotation of said axles,

• said elements being arranged in such way as to form a ring chamber for the pressurised liquid, in which a rotating piston moves, the movement of which fills with liquid a filling portion of said chamber and at the same time empties of liquid a draining portion of said chamber and its channelling towards the output conduit U,

• the input and output conduits opening onto the ring chamber by means of openings, rotating together with the rotating piston, created in the piston itself or in the immediate vicinity.

2. Device according to claim 1, in which the first axle (X1) is determined by a rotation shaft (2) to which is associated a static element of closure (21) and a rotating element (22) with the axle and fitted, on the lateral surface, with a number of slots (221).

3. Device according to claim 1, in which the second axle (X2) is determined by a second rotation shaft (3) to which is associated a static cylindrical element of cover (31), to which is associated a cylindrical element (32) piston-guide presenting a slot in which is housed a radial piston (33).

4. Device according to the previous claims, in which between the two shafts a dual ring element (4) is formed, which comprises the first ring (41) closed with the element (22), intersected by a second ring (42) inside which is envisaged said radial piston (33) linked to the second shaft (3) which also presents a slot (321) in which said piston is housed and which rotates with it.

5. Device according to the previous claims, in which the rotation synchronism determined by the transmission devices (M), determines by means of the slots (221) shaped into a "U", the free passage of the piston through the two points of intersection (44) and (45) between the two rings of the dual ring element (4), these slots being sized in such way as to guarantee the total and permanent closure of the volume crossed by the liquid, that is guaranteeing that the slots are never contemporaneously present either in all or in part, in the two points of intersection.

6. Device according to the previous claims, in which the paths of passage of the liquid (introduction and expulsion) are created inside the arm of the piston, or may be created in the immediate vicinity of the piston in slots to be made in the cylindrical guide element (32).

7. Device according to the previous claims, in which the variation of the volume of work of the chamber, in case the axles X1 and X2 are parallel, takes place by means of transfer to the second shaft (3) of the piston-support bowl (32) compared to the dual ring element with cotemporaneous transfer to the first shaft (2) of the element (22) rotating with the X1 axle.

Drawing