Patent Application
20120152571
The present invention generally relates to a high pressure discharge valve and more particularly to a high pressure discharge valve to be equipped with a low pressure triggering device and to be used in a fire-extinguishing system or in an explosion-prevention system.
The applicant offers an automatic fire-extinguishing system under the commercial designation “FireDeTec®”. A “FireDeTec®” system enables automatic detection and release of extinguishing agent without any external power source. This is achieved by means of a passive triggering device, more specifically, by means of a heat-sensitive tubing that bursts under the influence of heat. A core component of this system is a specially designed discharge valve, to which the heat sensitive tubing is to be connected. The discharge valve is designed for pressurizing the heat sensitive tubing and for setting off discharge of high pressure extinguishing agent from a pressurized container in case of rupture of the tubing.
A high pressure discharge valve of this type is known from European Patent EP 0 888 152. This valve comprises a valve body defining an inlet channel, an outlet channel and a valve seat there between. A closing piston is slidably movable within the valve body in axial prolongation of the valve seat. It further includes a triggering chamber for connection to the aforementioned triggering device, i.e. the heat sensitive tubing. A first end portion of the closing piston forms a pressure surface in the triggering chamber. At a second end portion, the closing piston forms a sealing surface, with which it can be pressed against the valve seat to seal the seat. The closing piston further has a pressure compensation channel through which the triggering chamber communicates with the inlet channel when the closing piston rests on the valve seat. A triggering port, to which the triggering device can be connected, communicates with the triggering chamber to pressurize the triggering device. Upon rupture, the triggering device causes a pressure drop in the triggering chamber whereby the closing piston moves off the seat to cause the valve to discharge.
A particular aspect of the discharge valve of EP 0 888 152 resides in that a pressure-reducing valve is provided in between the triggering chamber and the triggering port. The pressure-reducing valve reduces the pressure of high pressure gas, at which the inlet channel and, due to the compensation channel, also the triggering chamber are pressurized, to a reduced pressure. This allows pressurizing the triggering device, i.e. the heat sensitive tubing, at a lower pressure. Thus, by virtue of the pressure-reducing valve, the heat sensitivity of the triggering tubing, which depends on its internal pressure, is rendered less dependent on changes in ambient temperature causing a variation in pressure of the high pressure gas in the container and thus at the inlet. This advantage enables, among others, the use of CO2 as fire extinguishing agent. Moreover, a discharge valve equipped with a pressure-reducing valve according to EP 0 888 152 enables setting the internal pressure of the triggering tubing independently of the inlet pressure, i.e. the container pressure, whereby the same type of tubing can be used for different extinguishing agents and container pressures, and whereby tubing pressure may be adjusted according to local requirements. Moreover, the service life of the tubing increases with lower internal operating pressure.
Due to their undeniable advantages, “FireDeTec®” systems equipped with a discharge valve according to EP 0 888 152 have found widespread use during the last decade. Besides their successful use in fire-extinguishing systems, “FireDeTec®” systems have also been proposed as explosion-preventing systems for high-pressure containers, especially high-pressure fuel containers, such as CNG cylinders. Nevertheless, minor drawbacks of a discharge valve according to EP 0 888 152, when compared to prior art discharge valves without pressure-reduction, reside in the comparatively larger size of the discharge valve and, in that (re-)filling of the container onto which the valve is mounted must be carried out very carefully and slowly to prevent inadvertent discharge. A discharge valve that has been enhanced to facilitate the filling operation has been proposed by the Applicant in international patent application WO 01/80955. A valve design according to WO 01/80955 however further increases the valve size and, moreover, the manufacturing cost of the valve.
In view of the above, the invention provides a high pressure gas discharge valve, in particular for a fire-extinguishing or for an explosion-preventing system, that has a more compact size while facilitating (re-)filling of a gas container onto which the valve is mounted.
A high pressure gas discharge valve in accordance with the present invention comprises: a valve body with an inlet channel and an outlet channel, a valve seat arranged between the inlet channel and the outlet channel and a triggering chamber; a closing piston, which is slidably movable within the valve body in axial prolongation of the valve seat, this closing piston having a first end portion forming a pressure surface in the triggering chamber, a second end portion forming a sealing surface, with which it can be pressed against the valve seat to seal the latter, and a pressure compensation channel through which the triggering chamber can communicate with the inlet channel when the closing piston rests on the valve seat. The valve further has a triggering port in communication with the triggering chamber, for connecting thereto a low pressure triggering device, this low pressure triggering device being capable of generating a pressure drop in the triggering chamber; and a pressure-reducing valve for reducing a pressure (P1) of high pressure gas in the inlet channel to a reduced pressure (P2) suitable for the low pressure triggering device.
According to an important aspect of the present invention, the pressure-reducing valve is integrated into the closing piston and is designed so as to seal the pressure compensation channel in the closing piston when the pressure in the triggering chamber is higher than the reduced pressure (P2) and to open this pressure compensation channel when the pressure in the triggering chamber is lower than the reduced pressure (P2). The pressure surface of the closing piston in the triggering chamber is dimensioned so that the closing piston is firmly pressed with its sealing surface against the valve seat, when the pressure in the triggering chamber equals the reduced pressure (P2).
As will be appreciated, integration of the pressure reducing-valve into the closing piston enables a considerable reduction in construction size of the discharge valve. In addition, since the pressure reducing-valve is configured to isolate the triggering chamber from the inlet in case the pressure in the triggering chamber is at least equal to the reduced pressure (P2), rapid filling without a risk of undesired opening of the discharge valve is enabled by simply pressurizing the triggering chamber at a pressure greater than (or at least equal to) the mentioned reduced pressure (P2), which the pressure reducing-valve is set to create in the triggering chamber.
In a preferred embodiment, the pressure-reducing valve includes a biasing means, in particular a spring, urging the pressure-reducing valve to open the pressure compensation channel in the closing piston. This embodiment enables adjusting the bias exerted by the biasing means and thereby the desired reduced pressure for the triggering device as required, e.g. by appropriate selection of the spring.
In a simple and cost-effective embodiment, the pressure-reducing valve is advantageously configured as a seat valve. In preferred embodiment for integration of the pressure-reducing valve into the closing piston, the former includes: a pressure-reducing valve seat equipping the pressure compensation channel in the closing piston; a pressure-reducing piston which is slidably movable within a bore of the closing piston and axially relative to the pressure-reducing valve seat. This pressure-reducing piston has a first end forming a pressure surface exposed to the pressure in the triggering chamber and a second end with a sealing means with which it can be pressed against the pressure-reducing valve seat. A spring is urging the pressure-reducing piston away from its pressure-reducing valve seat. In a preferred embodiment, the pressure-reducing piston includes an axial bore opening into the pressure surface at the first end of the piston and a sealing ring that is arranged in the axial bore to cooperate with a sealing pin that is fixed to the valve body in axial prolongation of the axial bore. Thereby, passage of gas through the pressure-reducing valve can be selectively prevented because the sealing pin seals the axial bore when the pressure-reducing piston is lifted off the pressure-reducing valve seat by a predetermined axial distance. Accordingly, the latter features selectively permit a total discharge of the triggered valve while maintaining compensation of small leakages, i.e. slow pressure drops in the triggering chamber. The pressure-reducing piston further advantageously includes: a cross bore near its second end, the cross bore being in communication with a chamber surrounding the pressure-reducing valve seat; and an axial bore opening with one end into the cross bore and with the other end into the pressure surface at the first end of the pressure-reducing piston or into the axial bore that cooperates with the sealing pin.
The pressure-reducing piston is advantageously configured as a stepped piston with a large diameter section at its first end and a small diameter section at its second end. In this case, the large diameter section of the pressure-reducing piston is guided, in sealed manner by means of a large diameter sealing ring, within a large diameter bore opening into the pressure surface at the first end portion of the closing piston whereas the small diameter section of the pressure-reducing piston is guided, in sealed manner by means of a small diameter sealing ring, within a small diameter bore of the closing piston, in which the pressure-reducing valve seat is arranged. The closing piston is also advantageously configured as a stepped piston with a large diameter section at its first end and a small diameter section at its second end. Accordingly, the large diameter section of the closing piston is guided by means of a large diameter sealing ring within a large diameter bore in the valve body; and the small diameter section of the closing piston is guided by means of a small diameter sealing ring within a small diameter bore in the valve body, in which the discharge valve seat is arranged. In a further enhancement of the latter embodiment of the valve, a first annular space is axially sealed by the large diameter sealing ring and the small diameter sealing ring of the closing piston. This space is vented by means of a vent bore in the valve body. A second annular space, which is axially sealed by the large diameter sealing ring and the small diameter sealing ring of the pressure-reducing piston, is in communication with the first annular space via a bore in the closing piston. The second annular space advantageously forms a spring chamber for the spring urging the pressure-reducing piston away from its pressure-reducing valve seat. An axial stopper for the pressure-reducing piston may be easily formed by a circlip arranged in the large diameter bore of the closing piston.
The triggering port may be equipped with a shut-off valve, whereby interruption of the discharge is enabled as set out further below. Furthermore, the valve body advantageously includes a filling port opening into the inlet channel, for filling a container, e.g. a high pressure gas cylinder, as set out above.
The invention also provides a fire-extinguishing system comprising: a gas cylinder containing an extinguishing gas at high pressure; a high pressure gas discharge valve in accordance with the invention and, additionally, a low pressure triggering device, e.g. a heat sensitive tubing, which is in communication with the triggering chamber of the high pressure gas discharge valve and which is capable of generating a pressure drop in the triggering chamber.
The invention also provides an explosion-preventing system for protecting a high pressure gas tank against explosion in case of overheating. The latter system comprises: a high pressure gas discharge valve in accordance with the invention, which is configured as safety relief valve for the high pressure gas tank and connected at its triggering port to a low pressure triggering device capable of generating a pressure drop in the triggering chamber in case of a risk of overheating of the high pressure gas tank.
Further details and advantages of the present invention will be apparent from the following detailed—but not limiting—description of two preferred embodiments with reference to the attached drawings, wherein:
The valve 10 shown in
Reference number 12 identifies a low pressure triggering device, which is only schematically represented in
The valve 10 comprises a valve body 14 with a gas inlet channel 16 and a gas outlet channel 18. The gas inlet channel 16 is arranged in a threaded socket 20, which is configured to be screwed into a valve socket of the high pressure gas container (not shown). The gas outlet channel 18 is arranged in a lateral connecting socket 22 of the valve body 14. A valve seat 24 is arranged in the valve body 14 between the inlet channel 16 and the outlet channel 18. Reference number 26 identifies a triggering chamber in the valve body 14, in axial alignment with the valve seat 24. This triggering chamber 26 is closed by a valve cap 28, which includes a triggering port 30 opening into the triggering chamber 26. The triggering port 30 is equipped with a triggering port shut-off valve 32, to which the aforementioned low pressure triggering device 12 is connected.
Arrow 34 globally identifies a closing piston 34 that is slidably movable within the valve body 12 in axial prolongation of the valve seat 24. This closing piston 34 is a stepped piston with a large diameter section 36 at its first end and a small diameter section 38 at its second end. The large diameter section 36 of the closing piston 34 is guided in a sealed manner by means of a large diameter sealing ring 40 within a large diameter bore 42 in the valve body 14. Its rear end forms a pressure surface 44 within the triggering chamber 26. Reference A2 designates the area of the cross-section sealed by the large diameter sealing ring 40, i.e. the area of the pressure surface 44. The small diameter section 38 of the closing piston 34 is guided in a sealed manner by means of a small diameter sealing ring 46 within a small diameter bore 48 in the valve body 14, in which the valve seat 24 is arranged. Its front end supports a seat sealing ring 50. The latter forms a sealing surface with which the closing piston 34 can be pressed against the valve seat 24 to prevent high pressure gas from flowing from the gas inlet channel 16 over the valve seat 24 into the gas outlet channel 18. Reference Al designates the area of the cross-section sealed on the valve seat 24 by the closing piston 34.
The following description refers to the enlarged cross-section of
In the valve 10, an annular space 54 is provided, which is radially delimited by the stepped closing piston 34 in the stepped bore 42, 48 and is axially sealed by the large diameter sealing ring 40 on one side and the small diameter sealing ring 46 on the other side. This annular space 54 is vented via a vent bore 56 in the valve body 14. It follows that the annular backside 58 of the large diameter section 36 of the closing piston 34 is always exposed to atmospheric pressure and that the annular space 54 is duly vented during movement of the closing piston 34.
Reference number 60 points to a pressure compensation channel via which the triggering chamber 26 is in communication with the gas inlet channel 16. This pressure compensation channel 60 has an inlet opening 62 arranged within a throttling nozzle 63 located centrally within seat sealing ring 50, so that the pressure compensation channel 60 is always in communication with the high pressure gas in the gas inlet channel 16, even when the closing piston 34 is pressed against the valve seat 24.
Within the closing piston 34, the pressure compensation channel 60 opens into a pressure-reducing valve, which is globally identified with reference number 64 and has as an object to reduce the pressure (P1) of the high pressure gas to a reduced pressure (P2) that is suitable for the low pressure triggering device 12. This pressure-reducing valve 64 is integrated into the closing piston 34 and is designed so as to seal the pressure compensation channel 60 when the pressure in the triggering chamber 26 is higher than the reduced pressure (P2) and to open the pressure compensation channel 60 when the pressure in the triggering chamber is lower than the reduced pressure (P2).
The pressure-reducing valve 64 comprises a pressure-reducing valve seat 66, which is associated with the pressure compensation channel 60 in the closing piston 34, a pressure-reducing piston 68, which is slidably movable within a stepped bore of the closing piston 34, in axial prolongation of the pressure-reducing valve seat 66, and a spring 70, which urges the pressure-reducing piston 68 away from its pressure-reducing valve seat 66. A circlip 72 in the stepped bore forms an axial stopper for the pressure-reducing piston 68.
The pressure-reducing piston 68 is a stepped piston with a large diameter section 74 at its first end and a small diameter section 76 at its second end. The large diameter section 74 of the pressure-reducing piston 68 is guided in a sealed manner, by means of a large diameter sealing ring 78, within a large diameter bore 80 opening into the pressure surface 44 of the closing piston 34 (B2 is the cross-section sealed by the large diameter sealing ring 78). Its rear end forms a pressure surface 82 exposed to the gas pressure in the triggering chamber 26. The small diameter section 76 of the pressure-reducing piston 68 is guided in a sealed manner, by means of a small diameter sealing ring 84, within a small diameter bore 86 of the closing piston 34. Its front end supports a sealing member 88, cooperating with pressure-reducing valve seat 66, which is arranged in the small diameter bore 86 of the closing piston 34 (B1 is the cross-section sealed on the pressure-reducing valve seat 66 by the pressure-reducing piston 68).
A cross bore 90 is arranged in the small diameter section 76 of the pressure-reducing piston 68. This cross bore 90 is in communication with a seat chamber 92 located in the small diameter bore 86 and surrounding the pressure-reducing valve seat 66. An axial bore 94 extending through the pressure-reducing piston 68 opens with one end into the cross bore 90 and with the other end into the pressure surface 82 at the first end of the pressure-reducing piston 68. It follows that if the pressure-reducing piston 68 lifts from its pressure-reducing valve seat 66, gas from the gas inlet channel 16 flows through the throttling nozzle 63, the pressure compensation channel 60 and the pressure-reducing valve seat 66 into the seat chamber 92, from where it flows through the cross bore 90 and the axial bore 94 into the triggering chamber 26.
Reference number 96 points to an annular space surrounding the stepped pressure-reducing piston 68 in the stepped bore 80, 86 and housing the spring 70. This annular space 96 is axially sealed by the large diameter sealing ring 78 on one side and the small diameter sealing ring 84 on the other side. The annular space 96 communicates, via a bore 98 in the closing piston 34, with the annular space 54, which is vented via the vent bore 56 in the valve body 14. It follows that the annular backside of the large diameter section 74 of the pressure-reducing piston 68 is always exposed to atmospheric pressure and that the annular space 96 is duly vented during movement of the pressure-reducing piston 68.
Given the following values: P1 is the pressure in the gas inlet channel 16; P2 is the reduced pressure for which the low pressure triggering device 12 has been designed; B1 is the cross-section sealed on the pressure-reducing valve seat 66 by the pressure-reducing piston 68; B2 is cross-section sealed by the large diameter sealing ring 78 of the pressure-reducing piston 68; and FS is the spring force; then the sealed cross-sections B1 and B2 and the spring 70 shall be dimensioned to satisfy:
B1·P1+FS=B2·P2
It will be noted that B1/B2 shall be dimensioned as small as technically and economically feasible in order minimize the influence of P1 on P2.
Similarly, given the following values: A1 is the cross-section sealed on the valve seat 24 by the closing piston 34 and A2 is the cross-section sealed by the large diameter sealing ring 40, then the sealed cross-sections A1 and A2 shall be dimensioned to satisfy:
A2·P2=X·P1·A1
where X is a security factor greater than 1 (i.e.: X>1). Normally, X should be in the range of about 1.1 to 1.4, more preferably in the range of 1.2 to 1.3. In other words, the pressure in the triggering chamber 26 must fall below P2/X before the pressure P1 will be capable of lifting the closing piston 34 from its valve seat 24.
The normal operation of the valve 10 is as follows: If the triggering chamber 26 is filled with gas at the pressure P2, the pressure-induced force acting on the pressure surface 44 of the closing piston 34 will be sufficient to keep the closing piston 34 on its valve seat 24. If there is a small leakage of gas out of the triggering chamber 26, the pressure in the triggering chamber 26 will fall below P2 and the pressure-reducing valve 64 will open the pressure compensation channel 60 in the closing piston 34. Gas from the gas inlet channel 16 may now flow via the throttling nozzle 63, the pressure compensation channel 60, the pressure-reducing valve seat 66, the seat chamber 92, the cross bore 90 and the axial bore 94 into the triggering chamber 26, where it will compensate the small leakage. When the pressure in the triggering chamber 26 becomes equal to P2 again, the pressure-reducing valve 64 will close the pressure compensation channel 60 in the closing piston 34. Thus, the valve 10 is capable of maintaining a relatively constant and reduced pressure in the triggering chamber 26 even if there are small leakages of gas out of the triggering chamber 26.
However, if the low pressure triggering device 12 generates an important leakage rate over the triggering port 30 out of the triggering chamber 26, the compensation gas flowing via the throttling nozzle 63, the pressure compensation channel 60 and the open pressure-reducing valve 64 into the triggering chamber 26 will no longer be capable of compensating this important leakage rate. It follows that the pressure in the triggering chamber 26 will fall below the pressure P2/X, i.e. the pressure necessary to maintain the closing piston 34 on its valve seat 24. The pressure P acting onto the closing piston 34 resting on the valve seat 24 will consequently lift the closing piston 34 from the valve seat 24. High pressure gas will then be discharged by the valve 10 through the open valve seat 24 and the gas outlet channel 18.
It will be appreciated that the high pressure gas discharge valve 10 as described hereinbefore facilitates refilling of a gas container equipped with this valve 10. In
It will therefore be appreciated that with a valve 10 as described hereinbefore, such an inopportune opening during refilling can be easily prevented by simply pressurizing—prior to the refilling operation—the triggering chamber 26 with gas at a pressure P0 higher than P2/X. Preferably, the pressure P0 shall be equal to or slightly higher than the reduced pressure P2 for which the low pressure triggering device 12 has been dimensioned. This pressurized gas in the triggering chamber 26 will safely close the valve 10 by firmly pressing the closing piston 34 onto its valve seat 24. Simultaneously, it will close the pressure-reducing valve 64, thereby closing the pressure compensation channel 60 in the closing piston 34, which will reliably prevent a gas leakage from the triggering chamber 26 into the empty or partially empty gas container. After having pressurized the triggering chamber 26, a fast increase of pressure in the filling port 100 at the start of the refilling operation will no longer be capable of lifting the closing piston 34 from its valve seat 24.
Pressurizing of the triggering chamber 26 prior to a refilling operation may e.g. be carried out through the triggering port shut-off valve 32. The triggering chamber 26 may also be provided with a separate pressurizing port (not shown in the drawings) opening into the triggering chamber 26. Such a separate pressurizing port is advantageously equipped with a filling port check-valve. The solution with a separate pressurizing port is of course recommended if the low pressure triggering device 12 remains connected to the triggering port shut-off valve 32 during a refilling operation.
It will also be appreciated that, contrary to functionally comparable prior art valves according to EP 0 888 152 and WO 01/80955, which are designed as “total-discharge” valves, the presently disclosed valve 10 allows partial discharge of the gas container to which its inlet channel 16 is connected. When using valves according to EP 0 888 152 and WO 01/80955, the cylinder connected to the valve is always discharged completely once the triggering device 12 causes the closing piston to open. In contrast, by virtue of a valve 10 as described hereinbefore, discharge may be interrupted by closing the triggering port shut-off valve 32, so as to allow the pressure-reducing valve 64 to compensate the stopped leakage, i.e. to allow pressure in the triggering chamber 26 to raise back to P2. As will be understood, this capability is particularly advantageous for demonstration purposes, since it avoids the need to refill the cylinder after each demonstration. Furthermore, using a motorized shut-off valve 32, e.g. a solenoid valve, connected to a control system, the proposed valve 10 also allows automatically dosed discharge in function of actual needs. In safety-relevant applications however, the shut-off valve 32 is preferably omitted or blocked in open position using appropriate means.
Finally, a valve 10 as described hereinbefore may further have a manometer port and/or an overpressure safety discharge port (not shown in the drawings), both opening into the gas inlet channel 16. Such an overpressure safety discharge port may e.g. be equipped with a rupture disk. Furthermore, the triggering chamber 26 may be equipped with a separate manometer (not shown in the drawings) for checking the reduced pressure in the triggering chamber 26.
As seen in
As appears from
In conclusion, as opposed to the valve of
| Number | Date | Country | Kind |
|---|---|---|---|
| 91 581 | Jun 2009 | LU | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/EP2010/058781 | 6/22/2010 | WO | 00 | 3/6/2012 |
