Pressure regulator

Abstract

A pressure regulator includes a body having a high and a low pressure gas chambers that respectively communicate with high pressure gas inlet and a lower presure gas outlet and are divided by a pressure reducing valve having a valve seat on the wall partitioning the two chambers, and a cut-off with a flared head cooperating with the valve seat and a stembconnected thereto. The cut-off is longitudinally displaceable inside the high pressure chamber, causing the flared head to appraoch or move away from the valve seat to close or open the valve. The stem is slidingly and sealingly supported in an opening in the high pressure chamber, opposite to the valve seat and does not communicate with other parts of the regulator, causing the pressure in the opening to be null or unrelevant for the thrust exerted by the cut-off against the valve seat.

Claims

1. A pressure regulating device, comprising: a body provided with an inlet (311) connected to a breathable high pressure gas source and an outlet (312) for the breathable gas at a pressure lower than the high pressure, said body being partitioned into at least one high-pressure gas chamber (301) communicating with said inlet (311), and an intermediate-pressure gas chamber (302) communicating with said outlet (312), the intermediate-pressure gas chamber (302) communicating with the high-pressure gas chamber (301) through a pressure reducing valve, wherein said pressure reducing valve comprises a valve seat (313) defined on a wall (303) partitioning the high pressure chamber (301) from the intermediate pressure chamber (302), and a cut-off (1) comprising a flared head (102) connected to a stem (101), the flared head cooperating with said valve seat for closing and opening said valve, and wherein said cut-off (1) is displaceable in two directions along a longitudinal axis of the stem inside the high pressure chamber (301) such that the flared head (102) travels to be alternatively detached and moved away from said seat for opening the valve, and travels to move closer and in abutment against said valve seat (313) for closing the valve; and an elastically deformable diaphragm (2) adapted to be elastically preloaded (401), the diaphragm being exposed to a pressure outside the pressure regulating device and sealingly separates the intermediate pressure chamber from an external environment, the diaphragm controlling a mechanical actuator (6) for pushing the cut-off (1) along an opening direction in addition to a pressure in the intermediate pressure chamber 302, wherein the stem (101) is slidingly and sealingly supported in a guide opening in a wall of the high pressure chamber (501), opposite to the wall partitioning the high pressure chamber (301) from the intermediate pressure chamber (302) and provided with said valve seat (313), due to a sealing gasket (5), said opening (501) not communicating with other parts of the pressure regulating device such that a pressure in said opening is substantially null or such to not affect a thrust exerted by the cut-off (1) against the valve seat (313).

2. The pressure regulating device according to claim 1, wherein the cut-off (1) has a blind hole axially crossing the flared head (102) and the stem (101) to reach a given depth such to create a housing seat of a thrust shaft (6) constituting said mechanical actuator.

3. The pressure regulating device according to claim 2, wherein in the high pressure chamber (301) there is an elastic element (500) acting on the cut-off (1) to close the valve, and wherein the elastically deformable diaphragm (2) acts on the thrust shaft, a spring (401) and ambient pressure (Pa) acting on the thrust shaft to open the valve, such that on the cut-off (1) the following forces act overall: an elastic force (k.sub.1.Math.X.sub.1) of the spring (2); the elastic force (k.sub.2.Math.X.sub.2) of the elastic element (500) of the high pressure chamber (301); a force due to the high pressure P.sub.H acting on the cut-off flared head (P.sub.H.Math.(A.sub.3A.sub.3)); a force due to the intermediate pressure acting on the diaphragm (Pi.Math.(A.sub.2A.sub.4)); a force due to the intermediate pressure acting on the flared head (102) of the cut-off (Pi.Math.(A.sub.3A.sub.4)); and the a force due to the ambient pressure acting on the diaphragm (Pa.Math.A.sub.2).

4. The pressure regulating device according to claim 3, wherein the valve seat (313) and the head (102) of the cut-off (1) have such size and shape to minimize the force exerted by the high pressure on the cut-off (1).

5. The pressure regulating device according to claim 1, further comprising a relief valve communicating with a chamber formed by the guide opening (501) with the external environment.

6. The pressure regulating device according to claim 5, wherein the relief valve is an automatic valve calibrated to open when the pressure inside the guide opening (501) is higher than a given threshold.

7. The pressure regulating device according to claim 5, wherein the relief valve configured to be manually operated such to reduce the pressure exerted on the cut-off to close the valve when the sealing gasket (5) causes a high-pressure leakage in the guide opening (501).

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0025] These and other characteristics and advantages of the present invention will be more evident from the following description of some exemplary embodiments depicted in the attached drawings wherein:

[0026] FIG. 1 shows a longitudinal section of a pressure regulating device, specifically a first diaphragm stage for underwater use with lateral high pressure gas inlet according to an embodiment of the invention.

[0027] FIG. 2 shows an enlargement of the preceding figure with the highlighted forces acting on the cut-off in the direction of closing and opening the same.

[0028] FIG. 3 shows the intermediate pressure Pi trend by varying the immersion depth in a device according to known art.

[0029] FIG. 4 shows the same curve as FIG. 3 with a superimposed curve obtained with the device according to the invention.

[0030] FIG. 5 shows the trend of the intermediate pressure/depth curves with overall O-ring leakage for different pressure values of the cylinder.

DETAILED DESCRIPTION OF EMBODIMENTS OF THE INVENTION

[0031] With reference to FIG. 1, the pressure regulating device provides a main body partitioned in at least one high pressure chamber 301 having an inlet for the high pressure gas 311 and a lower pressure chamber, so-called intermediate pressure chamber 302, with an outlet of the reduced pressure gas 312.

[0032] The high pressure chamber 301 is partitioned from the intermediate pressure chamber 302 by a valve seat 313 made on the partitioning element 303 of said high pressure chamber 301 from said intermediate pressure chamber 302, which seat 313 cooperates with a plunger cut-off 1, also called poppet in the present description. This moves inside the high pressure chamber 301 along a longitudinal axis of said high pressure chamber 301, traveling alternatively to be detached and moved away from said seat 313 for opening the valve and traveling to move closer and in abutment against said valve seat 313 for closing the valve.

[0033] A guide element to guide the axial movement of the cut-off 1 inside said high pressure chamber 301 can be provided.

[0034] The cut-off 1 is composed of a stem 101 connected to a radially flared head 102 with respect to said stem 101, preferably made in one piece. The flared head 102 has a side facing the valve seat 313 and a rear side opposite to the valve seat 313 and to the approaching direction of the cut-off 1 to said seat.

[0035] The cut-off 1 is constituted by hard material resistant to high pressures, such as metal or the like, with a relatively soft surface where it interfaces with the sealing surface, i.e. with an annular lip of the valve seat.

[0036] The valve seat 313 is composed of an opening made on the partitioning element 303 partitioning said high pressure chamber 301 from said intermediate pressure chamber 302, the opening having an annular sealing lip of rigid material and with a pointed ridge that can cooperate with the upper surface of the flared head 102 of the plunger cut-off 1 such to ensure a perfect sealing of said seat 313 when the cut-off 1 is in closing position.

[0037] The plunger cut-off 1 has in its inside a blind hole, specifically coaxial with the stem and the flared head 102 and axially crossing the flared head 102 and the stem 101 until a given depth such as to create a housing seat of a thrust shaft 6 constituting the mechanism actuator.

[0038] The end of the stem 101 opposite to the flared head 102 is therefore completely closed towards the balancing chamber 501, i.e. it has a solid cross section.

[0039] The end of the stem 101 opposite to the flared head 102 is sealingly and slidingly supported in a balancing chamber 501 made in a wall opposite to the wall with the valve seat 313 thanks to a gasket element 5, such as an o-ring or the like, provided for insulating said opening.

[0040] The bottom of the high pressure chamber 301 is a supporting base of a resilient element 500 such as a spring adapted to push the cut-off 1 against the valve seat in closed condition, during the operation of the pressure regulating device.

[0041] According to an embodiment, as shown in FIG. 1, said wall opposite to the valve seat 313 consists of a plug closing the high pressure chamber 301, which plug is screwed in a threaded ending length of said high pressure chamber. The seal is obtained thanks to an o-ring and the side facing the inside of the high pressure chamber has a notch, in particular coaxial with the stem 101 of the cut-off 1 forming the balancing chamber 501.

[0042] The thrust shaft 6 ends in the inflection chamber 801 where it is coupled with the disc 421 resting on an elastically deformable diaphragm 2 having a wall facing a chamber communicating with the external environment and on which an elastic pre-load 401 acts such that the pressure of the external environment and the elastic pre-load cause an inflection of the diaphragm 2 itself in the opening direction of the dispensing valve at the inhaling, i.e. in the direction away from the cut-off 1 of the valve seat 313.

[0043] As it is known, in fact, in the first diaphragm pressure reduction stages for underwater use, whose function is to reduce the incoming air (i.e. the pressure of the cylinder to which the first stage is connected) to a predetermined intermediate pressure plus the ambient pressure, the air requirement by the diver creates a depression inside the intermediate pressure chamber 302, which depression causes the deformation of the elastic diaphragm 2. The thrust shaft 6 transfers the motion of the diaphragm 2 to the valve mechanism, i.e. to the cut-off 1. Therefore, when air is required, the cut-off 1 is removed from the valve seat 313 and allows the gas to flow from the high pressure chamber 301 connected to the cylinder, towards the intermediate pressure chamber 302 and therefore towards the user, through the outlet 312. When the diver is not inspiring, a balance condition of the forces due to the pressures and the elastic elements, i.e. to the springs, is set such that the cut-off 1 is hold in abutment and sealed against the valve seat 313 and the valve remains closed.

[0044] By denoting with D1 the diameter of the diaphragm 2, with D4 the diameter of the thrust shaft 6, with D3 the diameter of the hole obtained in the partitioning element 303 between the intermediate pressure chamber 302 and the high pressure chamber 301 inside which the thrust shaft is inserted, and with D3 the inner diameter of the balancing chamber 501, the equation expressing the balance of the forces acting on the cut-off 1 can be written in a first approximation such to highlight the characterizing feature of the invention.

[0045] By denoting with A.sub.1, A.sub.3, A.sub.3, A.sub.4 the surfaces corresponding to the diameters D1, D3, D3, and D4, with Pi the output pressure from the intermediate pressure chamber 302, P.sub.H the input pressure to the high pressure chamber 301, Pa the ambient pressure, Px the pressure in the balancing chamber acting on the end of the stem 101 of the cut-off opposite to the valve seat 313, k.sub.1 the modulus of the spring 401, X.sub.1 the compression with respect to the balance position of the spring 401, k.sub.2 the modulus of the spring 500, X.sub.2 the compression with respect to the balance position of the spring 500, as shown in FIG. 2, in the cut-off opening direction, the following forces are acting:

Pa**A.sub.1

k.sub.1*X.sub.1

Pi*(A.sub.3A.sub.4)

[0046] Where is a geometrical reduction factor which is function of D1, D2 as well as of the mechanical properties of the diaphragm 2. For simplicity, let's replace with A.sub.2

[0047] While in the cut-off closing direction the following forces act:

Px*A.sub.3

P.sub.H*(A.sub.3A.sub.3)

k.sub.2*X.sub.2

Pi*(A.sub.2A.sub.4)

from which one obtains

k.sub.1X.sub.i+PaA.sub.2+Pi(A.sub.3A.sub.4)+P.sub.H(A.sub.3A.sub.3)+PxA.sub.3+k.sub.2X.sub.2 (1)

[0048] By denoting with kX=k.sub.1X.sub.1k.sub.2X.sub.2 and simplifying, we obtain

Pi(A.sub.2A.sub.3)=kX+PaA.sub.2P.sub.H(A.sub.3A.sub.3)PxA.sub.3 (2)

[0049] For what till now mentioned, there are various possible values of Px:

[0050] Px=Pi is the known art as described already;

[0051] Px=0 or atmospheric pressure during the assembling step: it is the easiest embodiment object of the invention;

[0052] Px=Pa: the area behind the cut-off, i.e. the rear end of the stem 101 in the balancing chamber 501 is in contact with the external environment;

[0053] Px=Pa+15bars: is the condition wherein a relief valve is provided, which opens when a threshold value for example of 15 bars is reached.

[0054] This equation underpins the choice in the devices according to known art of piercing the cut-off such to bring the intermediate pressure to the balancing chamber 501, i.e. on the head side of the end of the stem 101 of the cut-off 1 which is opposite to the valve seat 313, or more generally in the area behind the cut-off with reference to the approaching direction of said cut-off 1 to the valve seat 313. In this case, in fact, Px=Pi thereby the equation (2) takes the form

[00001]$\begin{array}{cc}\mathrm{Pi}=\frac{{\mathrm{PaA}}_x-P_H\left(A_3^{}-A_3\right)}{A_2-A_3^{}+A_3}+\frac{\mathrm{kX}}{A_2-A_3^{}+A_3}& \left(3\right)\end{array}$

[0055] If A.sub.3 is kept as equal as possible to A.sub.3, not only the high pressure coming from the cylinder does not affect the outlet, but also the intermediate pressure has a trend linear with the external pressure by being:

Pi=Pa+kX (4)

[0056] Where k=k/A.sub.2. By calibrating the springs such that kX is 10 bars, a difference between intermediate pressure and ambient surface pressure is obtained equal to 10 bars, which represents the optimal value for this typology of devices and especially such a value does not depend on the immersion depth and the cylinder pressure.

[0057] Actually the surfaces A.sub.3 and A.sub.3 can hardly be considered equal due to the unavoidable tolerances and, especially, to the valve geometry wherein the dome configuration of the valve seat causes the effective surface on which the high pressure acts being different on the rear face from the one acting on the front face of the flared head 102, also in case of perfect matching between the diameter of the cut-off 101 and the diameter of the hole of the partitioning element 303 between the intermediate pressure chamber 302 and the high pressure chamber 301.

[0058] By way of example, from eq. (3) it can be verified as, by assuming a typical value for A.sub.2 equal to 30A.sub.3, a difference of 10% between A.sub.3 and A.sub.3, i.e. A.sub.3=1.1A.sub.3, results in a change of the intermediate pressure Pi from 0.6 to 0.15 bars for changes of the cylinder pressures P.sub.H from 200 to 50 bars, which is a negligible value, thereby in practice we can consider A.sub.3=A.sub.3 and simplify the equation of force balance, taking this fact into account.

[0059] In contrast to the theory, the inventor realized that by making the poppet blind, i.e. not allowing the intermediate pressure to flow to the rear of the cut-off, performance comparable to that of the regulator devices according to known art can be obtained.

[0060] In this case Px takes the 0 value, therefore the eq. 2 becomes:

Pi(A.sub.2A.sub.3)=kX+PaA.sub.2P.sub.H(A.sub.3A.sub.3) (5)

[0061] If A.sub.3=A.sub.3, we obtain

[00002]$\begin{array}{cc}\mathrm{Pi}=P.Math..Math.a.Math.\frac{A_2}{A_2-A_3}+k^{}.Math.X& \left(6\right)\end{array}$

[0062] Where k=k/(A.sub.2A.sub.3). By calibrating the springs such that kX takes the same value seen above (for example 10 bars), an increase in the intermediate pressure with depth is obtained which is penalized by the factor A.sub.2/(A.sub.2A.sub.3) which, by taking A.sub.2=30A.sub.3, is equal to about 1.03. This means that, in ideal conditions of balanced poppet i.e. with A.sub.3=A.sub.3, the blind hole always ensures a trend linear with the external pressure, but with an increase of about 3% of the angular coefficient.

[0063] FIG. 3 shows the trend of the intermediate pressure Pi by changing the immersion depth obtained by calibrating the springs such to have a surface pressure of 10 bars (intersection with the ordinate axis).

[0064] FIG. 4 shows the same curve as FIG. 3 with a superimposed curve obtained with the blind poppet according to the invention, the initial calibration being the same. As expected, the trend is always linear, albeit with a larger slope with a change of 0.2 bars at 60 m.

[0065] At the expense of an increment of the line slope, the device according to the invention, in addition to be easier to be implemented, allows compensating for the drawback caused by the leakage from the O-ring 5 in the conventional poppets. In the latter, in fact, a high-pressure leakage in the guide opening of the poppet stem results in direct passage of high pressure to the intermediate pressure chamber, with following malfunction of the second stage as already described.

[0066] In the device according to the invention the high-pressure leakage in the guide opening 501 results in an increase in the force tending to close the valve (Px passes from 0 to P.sub.H), which increase is compensated by a reduction of the intermediate pressure thus causing a device operation which at most makes breathing a little more difficult, since the contribution by the intermediate pressure to actuate the second stage valve is lacking and therefore the user has to exert a more intense suction action.

[0067] FIG. 5 shows the trend of the intermediate pressure/depth curves with overall leakage of the O-ring 5 for different values of P.sub.H. In the situation of very high cylinder pressure, the effort required to the diver can result excessive, but being an emergency situation it is better than the alternative showing in the devices according to known art and consisting in the uncontrolled gas leak. Furthermore, in the leakage condition with the device according to the present invention, the diver can help inhaling by pushing on the second stage drain. According to an embodiment, it is still possible, as described, communicating the guide opening 501 with the external environment by providing a release valve which can act automatically or by manual diver actuation.

[0068] In the text and drawings a cylindrical geometry is referred to for the high pressure and intermediate pressure chambers and for the reducing valve, this geometry being the most suitable to be obtained by machining. Furthermore, pressurized containers almost always have cylindrical geometry for controlling the strains. However the inventive concepts described and claimed are not limited to said geometry, any type of geometry being possible to be provided for said chambers and said valve, for example chambers with polygonal plan-shape.

[0069] The device can be widely varied constructively. For example it can be adapted for a use with any pressure regulating stage also not underwater, such as for example a device for dispensing air or other gases in emergency situations, which provides in its inside a gas pressure reducing valve from high pressure to lower pressure or use pressure, which valve is composed of a valve seat that can be opened or closed by a plunger cut-off. All without departing from the guiding principle afore described and claimed hereinbelow.