lonergan safety valve free sample

. 4 Emma 4 v I @zgngzzbaj Patented May 20, 1952 SAFETY VALVE Theodore W. Bergquist, Willow Grovel Pa, assignor to J. E. Lonergan Company, Philadelphia, Pal, a. corporation of Pennsylvania Application April 12, 1946, Serial No. 661,709 2 Claims. (01.13743) This invention relates to new and useful im provements in valves, and more particularly to safety valves for the protection of vessels and systems containing gases, vapors and other fluids under pressure.

Prior to the present invention the practice in respect to safety valves of the stated type has been to provide valves having a lift of considerable extent and the attainment of high capacity with the usually required blow down or prese sure drop of about four per cent to effect reclosing of the valve. However, as the capacity of any given size of valve is increased, the ability to control the valve action is made more difficult with the result that instabilities such as flutter, long blow down, undue simmer and drag, which manifests itself when the valve fails to close sharply and tight, are undesirable characteristics which are considered inherent in conventional safety valve design.

Various arrangements have been proposed heretofore to control the blow down or pres.- sure drop below the four per cent usually re.- quired in valves of this type without inducing the foregoing undesirable operating characteristics of the valve. Thus, arrangements have been proposed to utilize pressure in the popping. chamber to assist in reclosing the valve, for example, by varying the orifice size so as to regulate the rate of fluid flow to the upper chamber of the valve disk, or by utilizing an orifice of predetermined size to admit the proper amount of fluid to create the required back-pressure. These proposed ar rangements, all of which involved regulation of the amount of fluid admitted above the valve disk, proved undesirable for the reasons that (1) no provision was made for cut-off of the flow of fluid to the upper chamber of the disk thereby producing a continuing back-pressure when the valve is in the open position and reducing both the lift of the disk and rate of flow through the valve, (2) large over-pressures tend to build up the back pressure in the upper chamber to which fluid is constantly admitted thereby limiting the lift and in turn reducing the rate of discharge so that the pressure in the systemor vessel eontinues to increase and ultimately reaches" the danger point with accompanying possibility of rupturing the system or vessel, (3) such fixed orifice type of valves present manufacturing problems due to the difliculty in maintaining uniform leakage past the valve guide and disk and, (4) no provision exists for eliminating crawl of the valve under the conditions of very low blow down.

With the foregoing in mind, the principal object of the present invention is to provide a safety valve of the type set forth wherein the aforementioned difficulties and undesirable characteristics are eliminated.

Another object of the invention is to provide a safety valve of the stated character embodying novel features of construction and operation whereby the blow down" or pressure drop required to reclose the valve is effectively controlled and maintained below four per cent.

Another object of the invention is to provide a novel safety valve of the type described wherein a portion of the static pressure existing in the popping chamber is utilized to effect a sharp or abrupt reclosing of the valve under all conditions of blow down.

Another object of the invention is to provide a novel safety valve of the character set forth wherein the reclosing cycle of the valve may be repeated indefinitely free from crawl or, in other words, without reclosing at a successively higher pressure on each cycle than the pressure for which the valve is set to operate.

A furtherobject of the invention is to provide a novel safety valve having the features and characteristics set forth which is of relatively simplified and inexpensive construction, and

Fig. 1 is a sectional view vertically through a valve made according to the present invention and showing the valve element and associated parts in their closed positions; and

Referring now to the drawing, a valve made according to the present invention comprises a valve body I in which is formed a main chamber 2", an inlet duct 3 and an outlet or discharge duct 4. The outlet duct 4 is in direct communic"ation with the main chamber 2 while the inlet duct 3 has communication with the main chamber 2 only through a hollow inwardly tapered nozzle 5, which isthreaded in said inlet duct 3 as indicated at 6, and constitutes the primary orifice of the valve. The inner end of the nozzle 5 is provided with an annular axial extension 1 having a flat circular endface 8 which is disposed in a plane at right angles to the axis of the nozzle 5 and constitutes the seat of the valve.

Below the axial extension I the nozzle 5 is externally threaded as at 9 to receive internal threads of an adjustable warn ring Ill. The ring I is provided with a fiat annular end face II which like the valve seat 8 likewise is disposed at right angles to the axis of the nozzle and is adapted for adjustment to various positions parallel to the surface of the valve seat 8 axially of the nozzle 5.

Suitably secured upon the valve body I, for example, by means of bolts or the like I2 is a sub stantially cylindrical housing I3, and clamped between the adjacent faces of said body I and housing I3 is an annular flange portion I4 which is provided at the upper end of a cylindrical guide sleeve I5 that extends downwardly within the valve chamber 2 coaxially with respect to the in-- let nozzle 5. The guide sleeve I5 is of greater diameter than the inner end portion of the nozzle 5 and the length of said sleeve is such that its inner end terminates at a level a short distance below the level of the valve seat 8.

Slidably mounted within the guide sleeve I5 for axial movement in opposite directions therein is a valve piston I6 which is provided with a substantially flat end face I! disposed in a plane substantially at right angles to the axes of said piston I6 and the surrounding guide sleeve I5. In the center of the end face I! of the piston I5 is a downwardly projecting spreader cone I8 by which fluid impinging against the piston face I! is directed radially outward in all directions toward an annular rib I9 formed on said face I! concentric to the axis of the piston I6 (see Fig. 2). The rib I9 is provided with a fiat circular face 26 of substantially the same inside and outside diameter as the valve seat 8 against which the said face is adapted to bear to close off the flow of pressure fluid from the bore of the nozzle 5 into the valve chamber 2.

The piston seating surface 20 normally is maintained in contact with the valve seat 8 by a loading spring 2| which is housed Within the housing I3. The piston I6 is provided with a suitable stem 22 having one end 23 thereof rounded and seated in an internal recess 24 formed in the solid end portion of the head 25 of the piston I5. The piston stem or rod 22 is provided with radially extending pins 26 which extend into the recess 24 below the lower end of a suitable nut 21 threaded therein. The piston stem or rod 22 projects from the piston head 25 axially through the hollow body or chamber 28 of the piston, the guide sleeve I5, and into and through the housing I3. The other end of the rod or stem 22 is slidably mounted in an axial bore formed in an adjusting screw 29 which is threaded into a hub or boss 3|! formed at and closing the upper end of the spring housing I3.

Mounted on and resting against an annular shoulder 3| on the stem 22 within the housing I3 is a spring abutment washer 32 against which bears one end of the loading spring 2 I, the opposite end of said spring bearing against a loose abutment washer 33 slidably mounted on the stem 22 and resting against the inner end of the adjusting screw 29. The loading spring 2| may be set to any desired popping pressure of the valve by proper adjustment of the screw 29, and the screw is secured in its tightened position by means of a lock nut or the like 34. A cap 35 coversthe adjusting screw and its lock nut, and is removably 4 threaded onto the exterior of the central boss 30 in which the adjusting screw 29 is mounted.

In accordance with the present invention there is provided radially through the guide sleeve I5 adjacent the upper end thereof, a back pressure port 36 which is so positioned lengthwise of said sleeve I5 with respect to the axial length of the piston I6 that said port 36 will remain open at all times and is not closed by the piston I6 when the latter is actuated into its fully open position with respect to the valve seat 8. In addition, there is also provided laterally through the guide sleeve I5 a stabilizer vent 31 which is positioned just above the upper end of the piston I6 in the relation shown so that said vent 31 is fully opened when the piston I6 is closed upon the valve seat 8 and is closed by said piston as the latter moves from said closed position to the full open position thereof with respect to said valve seat 8, for example, in the relation shown in Fig. 2 of the drawmg.

Means are provided to vary the flow area through the port 36 in the guide sleeve I5 to thereby control back pressure internally of the chamber 28 of the piston I6 and the guide sleeve I5, and this may be accomplished effectively by means of a threaded plug or the like 38 which is mounted for adjustment coaxially toward and away from said port 36 within an internally threaded bore 39 provided in the valve body I.

Communication between the openings of the ports 40 and 4| in the side wall of the piston I6 is provided by a continuous annular channel or recess 42 which is formed in the internal wall surface of the guide sleeve I5, and the arrangement of said channel42 and the ports 40 and 4| is such as to establish and. provide communication therethrough from the valve main chamber 2 to the piston chamber 28 and the interior of the guide sleeve during opening and closing movement of the piston I6 with respect to the valve seat 8, and to close-off or preclude flow"therethrough from chamber 2 to the piston" chamber 28 when the piston I6 is in the full open position.

In the illustrated embodiment of the invention, the arrangement of thechannel 42 and ports 40 and 4| is such that they are also open to permit flow therethrough from chamber 2 to the piston chamber 28 and interiorly of the sleeve I5 when the piston I6 is in the full closed position upon the valve seat 8, but this is not essential and the sole requirements for effective operation of the valve according to the present invention are that the ports 40 and 4| be open and in communication to permit flow therethrough during travel of the piston between full closed and full open positions, and that said ports and 4| be closed to preclude flow in said full open p sition of the piston.

Preparatory to operation of the valve shown in the drawing, the loading spring 2| is set, by adjustin the screw 29, to any desired pressure at which the valve is to pop or blow-01f, i. e. the pressure at which the piston l6 will be actuated upwardly slightly from its fully closed position thereby displacing the piston face 20 from the valve seat 8. The warn ring i0 also is adjusted axially of the nozzle to provide the proper pop action eifect by exposing an enlarged area of the piston [6 to the pressure of the fluid. The ring It) may be secured in the position to which adjusted by a pin 43 which has an enlarged outer end 44 threaded into and through the"valve body and a pointed inner end 45 engaging longitudinal flutes or the like 46 in the lower portion of the periphery of the said ring l0.

In accordance with the invention, attainment of the stated objectives and elimination of the dificulties and undesirable characteristics encountered in prior valves of the present type, is accomplished by utilizing a portion of the static pressure in the piston chamber 28 and sleeve IE to augment the force of the spring 2| at a predetermined position of the piston l6 and effeet a sharp and abrupt closure of said piston i6 upon the valve seat 8 under any required condition of blow-down and without crawl.-

In operation of the embodiment of the valve shown in the drawing, when the pressure of fluid in the nozzle 5 reaches the set load pressure of the spring 2| the resulting pop action of the valve causes the piston Hi to rise to full open position thereby forming between the nozzle 5 and piston 25 a chamber 41 having a stricture or opening between the piston and warn ring ID to the valve main chamber 2, the said stricture or opening being designed and constructed so that there is maintained within the chamber 41 a predetermined pressure considerably in excess of the pressure existing in the valve main chamber 2. Returning to the operation of the valve, the aforesaid pop action which takes place causes the piston IE to rise to full open position so rapidly that no appreciable amount of fluid entering chamber 41 from the nozzle 5 will enter the piston chamber 28 through ports 40 and 4| and channel 42, and hence no appreciable back-pressure exists in said chamber 28 on the opening stroke of the cycle due to the fact that flow through said ports 40 and 4| and channel 42 is shut-01f in the full open position of the piston It. However, a slight reduction in the fluid pressure in the inlet nozzle 5 acting on the end face ll of the piston allows the latter to move downwardly thereby establishing communication between the ports 40 and 4| so that pressure fluid from the chamber 41 is admitted to the piston chamber 28.

The amount of back pressure built-up in the piston chamber 28 as the result of pressure fluid admitted thereto from the valve chamber 41 through ports 48 and 4| is controlled by adjustment of the plug 38 to increase or decrease the flow area through the port or bleed orifice 36. Thus, by restricting the port or orifice 36, by adjustment of the plug 38, to the proper degree the magnitude of the pressure within the piston chamber 28 may be increased to the value desired to augment the force of the spring 2| and eifect a reclosing of the piston l6 upon the valve seat 8.

It is to be noted that as the flow area through the port or orifice 36 is further restricted by adjustment of the plug 38, the magnitude of the pressure within the piston chamber 28 will progressively increase and, in practice, the pressure within the piston chamber 28 is regulated to effect opening and closing of the piston with respect to the valve seat 8 in response to extremely small differences in the pressure of the fluid entering the valve through the nozzle.

Operation in this manner whereby the piston is caused to open and close in response to an extremely small pressure difierential, is what is known as a condition of extremely low blowdown and when the orifice 36 is restricted by the plug 38 to the extent required to produce such operating condition, the restricted area of the orifice 36 generally is insufiicient to vent and completely dissipate the pressure within the piston chamber 28 rapidly enough when the piston |8 recloses upon the valve seat 8 with the result that the combined force of this unvented pressure and the spring force must be overcome before the piston IE will again rise or open with respect to said valve seat 8 thereby producing the undesirable condition known as crawl wherein the piston 6 opens at a pressure greater than 1 that for which the valve is set.

This condition of crawl is effectively eliminated in the present invention by the vent port 31 which is arranged in said sleeve l5 in the manner described so as to open fully the instant the piston I6 returns to the closed position upon the valve seat 8. The combined areas of the restricted orifice 36 and the vent port 31 are sufficient to effect a complete dissipation of the pressure within the piston chamber 28 as soon as the valve piston l6 reseats upon the face 8 so that the sole force opposing reopening of the valve is the spring 2| and hence the valve will again open at the pressure for which it was originally set.

From the foregoing description it will be apparent that the present invention provides a novel safety valve which is operable under conditions of very low blown down entirely free from crawl. The invention also provides a novel safety valve which is operable as described and is characterized by its relatively simplified and inexpensive construction and is highly foolproof and eflicient in operation and use.

1. A pressure relief valve comprising a valve body having a main chamber and a valve seat surrounding the inlet opening thereto, a piston movable coaxially with respect to said valve seat into and out of valve closing engagement therewith, tubular guide means for said piston defining therewith a substantially closed chamber at the opposite side of said piston from said valve seat, said guide means having in its inner surface a recess extending circumferentially of piston adjacent said valve seat, said piston having passages therein communicating respectively between said main chamber and said recess and between the latter and said closed chamber to provide communication between said main chamber and the closed chamber only during travel of said piston between closed and open positions thereof with respect to said valve seat and to shut oif communication between said main chamber and closed chamber when said piston reaches said open position, and said guide means having therein a first port arranged so that it is open in all positions of the piston and a second port located in the wall of the guide means immediately adjacent the said opposite side of the piston in the closed position thereof and providing communication between said closed chamber and the main chamber in the closed position only of said piston.

2. A pressure relief valve comprising a valve body having a main chamber and a valve seat surrounding the inlet opening thereto, a piston movable coaxially with respect to said valve seat into and out of valve closing engagement therewith, tubular guide means for said piston defining therewith a substantially closed chamber at the opposite side of said piston from said valve seat, said guide means having in its inner surface a recess extending circumferentially of piston adjacent said valve seat, said piston having passages therein communicating respectively between said main chamber and said recess and between the latter and said closed chamber to provide communication between said main chamber and the closed chamber only during travel of said piston between closed and open positions thereof with respect to said valve seat and to shut off communication between said main chamber and closed chamber when said piston reaches said open position, and said guide means having therein a first port arranged so that it is open in all positions of the piston and a second port located in the wall of the guide means immediately adjacent the said opposite side of the piston in the closed position thereof and providing communication between said closed chamber and the main chamber in the closed position only of said piston, and means operable to regulate the flow area through said first port.

A little product education can make you look super smart to customers, which usually means more orders for everything you sell. Here’s a few things to keep in mind about safety valves, so your customers will think you’re a genius.

A safety valve is required on anything that has pressure on it. It can be a boiler (high- or low-pressure), a compressor, heat exchanger, economizer, any pressure vessel, deaerator tank, sterilizer, after a reducing valve, etc.

There are four main types of safety valves: conventional, bellows, pilot-operated, and temperature and pressure. For this column, we will deal with conventional valves.

A safety valve is a simple but delicate device. It’s just two pieces of metal squeezed together by a spring. It is passive because it just sits there waiting for system pressure to rise. If everything else in the system works correctly, then the safety valve will never go off.

A safety valve is NOT 100% tight up to the set pressure. This is VERY important. A safety valve functions a little like a tea kettle. As the temperature rises in the kettle, it starts to hiss and spit when the water is almost at a boil. A safety valve functions the same way but with pressure not temperature. The set pressure must be at least 10% above the operating pressure or 5 psig, whichever is greater. So, if a system is operating at 25 psig, then the minimum set pressure of the safety valve would be 30 psig.

Most valve manufacturers prefer a 10 psig differential just so the customer has fewer problems. If a valve is positioned after a reducing valve, find out the max pressure that the equipment downstream can handle. If it can handle 40 psig, then set the valve at 40. If the customer is operating at 100 psig, then 110 would be the minimum. If the max pressure in this case is 150, then set it at 150. The equipment is still protected and they won’t have as many problems with the safety valve.

Here’s another reason the safety valve is set higher than the operating pressure: When it relieves, it needs room to shut off. This is called BLOWDOWN. In a steam and air valve there is at least one if not two adjusting rings to help control blowdown. They are adjusted to shut the valve off when the pressure subsides to 6% below the set pressure. There are variations to 6% but for our purposes it is good enough. So, if you operate a boiler at 100 psig and you set the safety valve at 105, it will probably leak. But if it didn’t, the blowdown would be set at 99, and the valve would never shut off because the operating pressure would be greater than the blowdown.

All safety valves that are on steam or air are required by code to have a test lever. It can be a plain open lever or a completely enclosed packed lever.

Safety valves are sized by flow rate not by pipe size. If a customer wants a 12″ safety valve, ask them the flow rate and the pressure setting. It will probably turn out that they need an 8×10 instead of a 12×16. Safety valves are not like gate valves. If you have a 12″ line, you put in a 12″ gate valve. If safety valves are sized too large, they will not function correctly. They will chatter and beat themselves to death.

Safety valves need to be selected for the worst possible scenario. If you are sizing a pressure reducing station that has 150 psig steam being reduced to 10 psig, you need a safety valve that is rated for 150 psig even though it is set at 15. You can’t put a 15 psig low-pressure boiler valve after the reducing valve because the body of the valve must to be able to handle the 150 psig of steam in case the reducing valve fails.

The seating surface in a safety valve is surprisingly small. In a 3×4 valve, the seating surface is 1/8″ wide and 5″ around. All it takes is one pop with a piece of debris going through and it can leak. Here’s an example: Folgers had a plant in downtown Kansas City that had a 6×8 DISCONTINUED Consolidated 1411Q set at 15 psig. The valve was probably 70 years old. We repaired it, but it leaked when plant maintenance put it back on. It was after a reducing valve, and I asked him if he played with the reducing valve and brought the pressure up to pop the safety valve. He said no, but I didn’t believe him. I told him the valve didn’t leak when it left our shop and to send it back.

If there is a problem with a safety valve, 99% of the time it is not the safety valve or the company that set it. There may be other reasons that the pressure is rising in the system before the safety valve. Some ethanol plants have a problem on starting up their boilers. The valves are set at 150 and they operate at 120 but at startup the pressure gets away from them and there is a spike, which creates enough pressure to cause a leak until things get under control.

If your customer is complaining that the valve is leaking, ask questions before a replacement is sent out. What is the operating pressure below the safety valve? If it is too close to the set pressure then they have to lower their operating pressure or raise the set pressure on the safety valve.

Is the valve installed in a vertical position? If it is on a 45-degree angle, horizontal, or upside down then it needs to be corrected. I have heard of two valves that were upside down in my 47 years. One was on a steam tractor and the other one was on a high-pressure compressor station in the New Mexico desert. He bought a 1/4″ valve set at 5,000 psig. On the outlet side, he left the end cap in the outlet and put a pin hole in it so he could hear if it was leaking or not. He hit the switch and when it got up to 3,500 psig the end cap came flying out like a missile past his nose. I told him to turn that sucker in the right direction and he shouldn’t have any problems. I never heard from him so I guess it worked.

If the set pressure is correct, and the valve is vertical, ask if the outlet piping is supported by something other than the safety valve. If they don’t have pipe hangers or a wall or something to keep the stress off the safety valve, it will leak.

There was a plant in Springfield, Mo. that couldn’t start up because a 2″ valve was leaking on a tank. It was set at 750 psig, and the factory replaced it 5 times. We are not going to replace any valves until certain questions are answered. I was called to solve the problem. The operating pressure was 450 so that wasn’t the problem. It was in a vertical position so we moved on to the piping. You could tell the guy was on his cell phone when I asked if there was any piping on the outlet. He said while looking at the installation that he had a 2″ line coming out into a 2×3 connection going up a story into a 3×4 connection and going up another story. I asked him if there was any support for this mess, and he hung up the phone. He didn’t say thank you, goodbye, or send me a Christmas present.

We’ve got your back. Let us find the exact part you’re looking for in our 100,000 sq. ft. warehouse stocked with 35,000 ready-to-ship valves from the world’s most renowned brands. We’ll put our decades of experiencing cross-referencing valves to work fast. Just give us a call.

Originally known as J.E. Lonergan Valve Company of Philadelphia, Lonergan Valves has undergone a series of owners, but the original Lonergan safety relief valve SRV and pressure relief valve PRV have maintained their integrity. Ownership has gone from Pentair to Reyco, from Reyco to Tyco

The original product line included Navy valves, pressure gauges, steam whistles, oiling devices, water level gauges SRV’s and PRV’s, is now just safety relief valves SRV, and pressure relief valves PRV.

Original J.E. Lonergan Valve Company series model numbers: ABS, ABB, ACA, AAA, FBF, FBT, FBA, D, DB, DO, GIF, GBF, L14, JL14, L40, JL40, L41, DH, EIF, BBJ, LCT-14, LCT-40, DS, R, BBJ, BIA, BCA, BAS, YBJ, YIA, H, HK, HU, TBB, HCA, HSS, VAK, have now taken on new part numbers, but designs remain the same. There are also a series of interim numerical codes that have now been replaced. 11-H-200, 12-H-200, 13-H-200, 14-H-200, 23-H-200, 34-H-200, 41-H-200, 42-H-200, 44-H-200, 41-W-200, LCT-20, LCT-11, 11-W-200, 15-W, ARV, HDF, FSS, T, TR, TL, TLG, HRV, HRN, HRX, HTC, T-DP, 13-W, and 43-W. For Datasheets for these models, accurate detailed information is available in the form of pdf or an electronic data manual that contains individual technical data sheets to support the selection of valve.

When replacing a Lonergan Valve it is important to obtain inlet and outlet sizes, end connections, set pressure, coding requirements (for capacity of steam Lbs./hr, an air of gas cfm, or liquid, GPM values). Inlet and outlet flange class options are Class 150, 300, 600, 900, 1500, 2500, and 4500. If Ring Type Joint (RTJ) is required, please specify. Buttweld end or socket weld end connections must include bore schedules when generating an RFQ or order. They are available as standard, 40, 60, XH, 80, 100, 120, 140, 160, or XXH.

The Lonergan valve will also be embossed with a body material code. This can be represented as ASTM A126 Cast Iron, B62 Bronze, A105 Carbon Steel, ASTM A182, Grade F11, Grade F316 / F316L, Grade F22, Alloy 20, or Monel. The standard spring material is Chrome Vanadium

Safety relief valves, SRV, and pressure relief valves PRV, are manufactured in conformance to Section VIII of the ASME Boiler and Pressure Vessel Code for air, steam, and liquid service. Capacities certified by the National Board of Boiler and Pressure Vessel Inspectors. NACE Code valve certification included.

Please include Size and Model Number, or: Size, Valve Type, Body and Trim material, Pressure Class, end connections, and any special code requirements. Include set pressure, service media, and temperature, and required capacity, if any.

Lonergan Valve replacement parts are available for virtually every component of a valve assembly. Valve body, valve bonnet, replacement gasket kit, spring, nozzles, guides, discs, and spring steps, if identified by model number and size are normally stocked.

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The primary purpose of a safety valve is to protect life, property and the environment. Safety valves are designed to open and release excess pressure from vessels or equipment and then close again.

The function of safety valves differs depending on the load or main type of the valve. The main types of safety valves are spring-loaded, weight-loaded and controlled safety valves.

Regardless of the type or load, safety valves are set to a specific set pressure at which the medium is discharged in a controlled manner, thus preventing overpressure of the equipment. In dependence of several parameters such as the contained medium, the set pressure is individual for each safety application.