EP0972946A1 - Pneumatic-hydraulic force intensifier - Google Patents

Abstract

The force multiplier utilizes separate pneumatic and hydraulic chambers to provide motive force to a pneumatically or hydraulically activated unit. The force multiplier comprises a principal cylinder (51) with a principal piston (9) and a rear chamber (C8) which is coaxially extended by a cylindrical chamber (C5) through the interior of the piston. A second transverse cylinder has a second piston (7) and a rear chamber (C3) activated by pressurized air and a front oil chamber (C4) in communication with the principal cylinder rear chamber. A third cylinder (53) with a rear chamber (C6) activated by pressurized air has a third piston (15) coaxial with the principal piston which is introduced by its displacement in the principal piston rear chamber. Oil seals (8,20) in combination with the principal piston prevent communication between the chambers of the cylinders.

Description

This multiplier applicable to any type of mooring operates using pressurized air as the power source. This air pressure, by means of a hydraulic multiplying cylinder, is converted in mechanical thrust force. Furthermore, this invention has a stroke automatic advance and return using only pressurized air. So therefore, it is a pneumo-hydraulic force-pressure multiplier which obtains an automatic stroke then a multiplying transformation of the supply air pressure in mechanical push-mooring force.

In known technology, a multiplier is used a very long pneumatic cylinder which is integral with a reservoir hydraulic. The action of the inner piston of the pneumatic cylinder and its stroke is break it down into two phases; the automatic movement of advancement and go back, then multiply action. Which requires a large length of the device.

Our invention distributes this double action on two pistons placed transversely. We thus obtain that the whole is of least length.

It should be emphasized in particular that the invention does not need only pressurized air, present on most work center sites, without the need for external devices. In addition, we start from a bass pressure 6-8 bar to reach a large mooring force of 4-5 tonnes, which simply requires an air inlet, which makes the operator's job easier.

a) transvasant l'huile d'une chambre à un autre, ce qui produit un mouvement linéaire automatique de la seconde;

b) maintenant cette chambre étanche; et

c) y introduire un piston qui, du fait de la loi de Pascal, multiplie la force d'entrée et convertit la force hydraulique en poussée mécanique.

The pneumo-hydraulic force multiplier object of the invention, due to the action of pressurized air, achieves its objective by:

a) transferring the oil from one chamber to another, which produces an automatic linear movement of the second;

b) maintaining this sealed chamber; and

c) introduce a piston which, due to Pascal's law, multiplies the input force and converts the hydraulic force into mechanical thrust.

• l'utilisation de deux pistons pneumatiques successifs dans le temps, durant la phase de course automatique et serrage et vice-versa
• l'utilisation des deux bagues d'étanchéité qui ferment les chambres de manière successive avec le piston pneumatique.

The novelty of the invention is due to:

• the use of two successive pneumatic pistons over time, during the automatic stroke and tightening phase and vice versa
• the use of two sealing rings which successively close the chambers with the pneumatic piston.

The device can be used on any tool of thrust, whether it is mooring parts like the press or the jaws, or for closing or other utilities.

La figure 1 est une représentation longitudinale d'une réalisation pratique de l'objet de l'invention.

La figure 2 est une vue en coupe A:A de la figure 1.

To better understand the object of the present invention, there will be shown on the plans a preferential form of practical embodiment, capable of accessory changes which do not divert the foundation.

Figure 1 is a longitudinal representation of a practical embodiment of the object of the invention.

Figure 2 is a sectional view A: A of Figure 1.

The following description describes an example of practical, non-limiting embodiment of the present invention.

Some of the elements represented were neither numbered nor described to the extent that they are conventional and are not the subject of the invention.

The flange (1) has been perforated in a multiform way to allow the conduct of fluids. Some of the exits of said conduits have not function, from where they were closed by plugs (t).

There is a main cylinder (5 ₁ ) with a piston (9), with a rear chamber (C ₈ ) which is extended by a cylindrical chamber (C5) through the interior of the main piston (9) and which is full of oil.

The main piston (9) pushes the mechanical plunger (11) which will exert the multiplied force where the user wants it, or the mechanism of which the user will need, for example, by means of a washer (22).

The mechanical pusher moves in the chamber anterior (C9) against the action of a spring (10).

There is a second cylinder (5 ₂ ) with a second piston (7) a rear chamber (C ₃ ) actuated by fluid, for example pneumatic and a front chamber (C ₄ ) full of oil and in communication (P ₄ ) with the rear chamber (C ₈ ) of the main cylinder (5 ₁ ).

There is a third cylinder (5 ₃ ) with a rear chamber (C ₆ ) actuated by fluid, for example pneumatic, a third piston (15) coaxial with the main piston (9) and which is introduced during its movement in the cylindrical chamber (C ₅ ) of said main piston (9).

At the outlet (s) of the third piston (15) there is a first oil seal ring (8).

The second (5 ₂ ) and the third cylinder (5 ₃ ) are presented (Figure 1) inside a single block or flange (1).

In the rear part of the main cylinder (5 ₁ ) between its rear chamber (C ₈ ) and the front chamber (C ₄ ) of the second cylinder (5 ₂ ) there is a second oil sealing ring (20) made of 'an auxiliary part (21) fixed (threaded) coaxial with the third piston (15) and arranged opposite its / its outlet (s).

In the coaxial position are the main cylinder (5 ₁ ) and the third cylinder (5 ₃ ), that is to say, their pistons (9), (15) and in an indeterminate arrangement the second cylinder (5 ₂ ) although in this embodiment it is perpendicular to them.

The multiplier receives the air supply from the part rear or side of the support flange (1) by the accesses (2) or (3) which communicate with each other, this is also the reason why one of these must always remain closed.

The flange (1) is a compact piece pierced to obtain the various chambers of fluids, for example air, oil, water, etc. To join or moor to external elements, it has holes (a) which make it possible anchoring with bolts. In its front part, it has a hole threaded (4) which receives the main tank or main cylinder (5), giving rise to the assembly with double interlocking.

This compact and reduced form of the flange (1) -tank assembly main cylinder (5) is an important difference from art prior.

In FIG. 2, it can be appreciated that the air under pressure which enters through the orifices (2) or (3) arrives at the cavity (C ₁ ) occupied by the first valve assembly (V ₁ ). On this assembly (V ₁ ) is mounted a one-way valve (6) which prevents the inlet air from passing through it in the longitudinal direction.

The cavity (C ₁ ) communicates with the cavity (C ₂ ) where there is a second valve assembly (V ₂ ).

The air then passes through the conduit (P ₈ ) to the second valve assembly (V ₂ ) placed in the cavity (C ₂ ). The one-way valve (13) prevents it from crossing this assembly in the longitudinal direction and advances towards the point (P ₁ ) where it divides into two flows; one which continues towards (P ₂ ) and another which advances towards (P ₃ ).

Path P ₂ .- The air which goes to (P ₂ ) is introduced into the rear chamber (C ₃ ) of the second cylinder (Figure 1), located under the second piston (7). This causes the piston (7) to advance in a vertical direction against the action of the spring (17). This piston (7) pulses the oil located in the front chamber (C ₄ ) through the point (P ₄ ) to the cylindrical pressure chamber (C ₅ ) of the main cylinder reservoir (5 ₁ ) The cylindrical chamber (C ₅ ) is previously filled with oil. The sealing ring (8) and the piston (15) prevent the oil from escaping by preventing communication between the chambers of the main cylinder (C ₅ ) (C ₈ ) and the third cylinder (C ₇ ).

The oil thus displaced from the front chamber (C ₄ ) to the cylindrical chamber (C ₅ ) increases the volume of oil in the cylindrical chamber (C ₅ ) and causes the main piston (9) to advance inside the main cylindrical tank (5), compressing the spring. The piston (9) takes in its movement the mechanical plunger (11). This is responsible for transmitting the pressure. Thus, the automatic advance travel of the mechanical plunger is obtained.

Channel P ₃ .- The part of the air flow which advances towards the point (P ₃ ) passes to the chamber (C ₂ ) (figure 2). There is a minimum flow reduction and a pressure limiting valve (12), adjusted to the inlet pressure of the outside air.

These pressures are not compensated until the air has completely filled the rear chamber (C ₃ ) and the second piston (7) cannot advance further. And it is then that the air succeeds in defeating the pressure limiting valve (12). This valve (12) in turn opens the one-way valve (13). Thus the air which comes from the outside (2) or (3) sees its passage released, by finding the one-way valve (13) open. This air passes through point (P ₅ ) and through line (P ₉ ) at point (P ₆ ) of the first valve assembly (V ₁ ) and from this to (P ₇ ). From point (P ₇ ) it goes directly to the posterior chamber of the third cylinder (C ₆ ).

The air located in the rear chamber (C ₆ ) pushes the pneumatic piston (14) forward and the air located in the front chamber (C ₇ ) exits into the atmosphere, through a silencer filter located at the outside of the flange (1).

By advancing the piston (14) takes with it the rod (15), causing the spring (16) to compress.

The rod (15) passes through the sealing rings (8) (20) by entering the cylindrical chamber (C5). The main piston (9) cannot advance further, since it has already carried out its approach work, with the automatic stroke described above. The introduction of this rod (15) into the main chamber (C ₅ ) produces the multiplication of the pressure by application of the elementary law of Pascal hydraulic.

We will emphasize the function of the two oil sealing rings (8), (20) where the first sealing ring (8) of the third cylinder (53) with the piston (15) closes the front chamber (C ₇ ) movement - starting chamber - and the second ring (20) closes with the third piston (15) the pressure multiplication chamber (C ₅ ).

DECOMMISSIONING AND RETURN PHASE

We remove the air from the entry point (2) or (3). The air located in the rear chamber (C ₆ ) flows back, crosses the point (P ₇ ), goes to point (P ₆ ) of the first valve assembly (V ₁ ) and leaves outside through its one-way valve (6). The spring (16) of the front chamber (C ₇ ) of the third cylinder (5 ₃ ) and the pressure existing in the cylindrical chamber (C ₅ ) cause the pneumatic piston (14) to return to its initial position.

This causes the third piston (15) to occupy the rest position next to the sealing ring (8), allowing the passage of oil from the chamber (C ₅ ) to the front chamber (C ₄ ) of the second cylinder (5 ₂ ).

The air located in the rear chamber (C ₃ ) of the second cylinder (5 ₂ ) leaves behind and exits through point (P ₂ ) at (P ₁ ) (figure 2) and advances freely towards the outside, crossing transversely the first and second valve assembly (V ₁ ) and (V ₂ ).

Under the effect of the springs (10), (16), (18) and (19), the various moving parts of the invention return to their original position even if the replacement of these springs by other return means, for example, by the action of fluid, falls within the object of the invention.

Claims (8)

Pneumo-hydraulic force multiplier, characterized in that it consists of: a) a main cylinder (5 ₁ ) comprising a main piston (9) and a rear chamber (C ₈ ) which is extended coaxially by a cylindrical chamber (C ₅ ) by the interior of said piston (9) and which is full of oil; b) a second cylinder (5 ₂ ) comprising a second piston (7), a rear chamber (C ₃ ) with fluid actuation and a front chamber (C ₄ ) for oil and in communication with the rear chamber (C ₈ ) of the main cylinder; c) a third cylinder (5 ₃ ) comprising a rear chamber (C ₆ ) actuated by fluid and a third piston (15) coaxial with the main piston (9) and which is introduced during its movement in the cylindrical chamber ( C ₅ ) of said main piston (9); d) a first oil sealing ring (8) coaxial with the third piston (15) and in the third cylinder (5 ₃ ) which prevents the passage of oil in the front chamber (C ₇ ) of the third cylinder; e) a second oil sealing ring (20) coaxial with the third sealing ring (15) and in the main cylinder (5 ₁ ) which prevents the passage of oil from the cylindrical chamber (C ₅ ) to the front chamber (C ₄ ) of the second cylinder (5 ₂ ) when the third piston (15) is located in said sealing ring (20); f) fluid means for actuating the second and third cylinder (5 ₂ ), (5 ₃ ). Pneumo-hydraulic force multiplier according to the preceding claim, characterized in that the fluid of the fluid actuating means is pressurized air which acts on the second cylinder (52) when the pressure of the air in question exceeds a preset value, intervenes on the third cylinder (5 ₃ ) while acting on the second cylinder (5 ₂ ). Pneumo-hydraulic force multiplier, according to previous claims, characterized in that it comprises a flange (1) in the body of which are placed the second and the third cylinder (5 ₂ ), (5 ₃ ), the main cylinder (5 ₁ ) attaching to said flange in coaxial extension with the third cylinder (5 ₃ ). Pneumohydraulic force multiplier according to previous claims, characterized in that the main piston (9) pushes in its movement a mechanical plunger (11) which moves inside the front chamber (C ₉ ) of the main cylinder (5 ₁ ) Pneumo-hydraulic force multiplier, according to claim one, characterized in that the main cylinder (51) and the second and third cylinder (5 ₂ ), (5 ₃ ) are provided inside with return springs (10) , (16), (17). Pneumo-hydraulic force multiplier, according to claim one, characterized in that in the rear part of the main cylinder (5 ₁ ) is arranged between its rear chamber (C ₈ ) facing the exit zone (s) of the third piston ( 15) an auxiliary part carrying the second oil sealing ring (20). Pneumo-hydraulic force multiplier, according to claim one, characterized in that the fluid means are placed in the flange (1) and operate with a single air inlet (2) or (3) which arrives at a cavity ( C ₁ ) in which there is a first valve assembly (V ₁ ) which consists of a one-way valve (6) for its longitudinal direction, allowing the passage of air in the transverse direction to a second valve assembly (V ₂ ) which consists of a one-way valve (13) for its longitudinal direction, allowing the passage of air in the transverse direction to a duct which communicates with the rear chamber (C3) of the second cylinder (5 ₂ ) and the rear chamber (C ₆ ) of the third cylinder (5 ₃ ) by means of a pressure limiting valve (12). Pneumohydraulic force multiplier according to claim seven, characterized in that the pressure limiting valve (12) is part of the second valve assembly (V ₂ ) so that its movement opens its one-way valve (13) which allows passage air from the second valve assembly (V ₂ ) to the first valve assembly (V ₁ ) and from the latter to the posterior chamber (C ₆ ) of the third cylinder.

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