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WO1996010707A1 - Appareil pour surveiller d'eventuelles fuites de fluide d'arret d'un systeme a deux joints d'etancheite - Google Patents

Appareil pour surveiller d'eventuelles fuites de fluide d'arret d'un systeme a deux joints d'etancheite Download PDF

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Publication number
WO1996010707A1
WO1996010707A1 PCT/US1995/012581 US9512581W WO9610707A1 WO 1996010707 A1 WO1996010707 A1 WO 1996010707A1 US 9512581 W US9512581 W US 9512581W WO 9610707 A1 WO9610707 A1 WO 9610707A1
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WIPO (PCT)
Prior art keywords
barrier fluid
pressure
leakage
barrier
fluid chamber
Prior art date
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Ceased
Application number
PCT/US1995/012581
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English (en)
Inventor
Donald P. Arbuckle
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Individual
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Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to AU38249/95A priority Critical patent/AU3824995A/en
Publication of WO1996010707A1 publication Critical patent/WO1996010707A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K37/00—Special means in or on valves or other cut-off apparatus for indicating or recording operation thereof, or for enabling an alarm to be given
    • F16K37/0075—For recording or indicating the functioning of a valve in combination with test equipment
    • F16K37/0091—For recording or indicating the functioning of a valve in combination with test equipment by measuring fluid parameters

Definitions

  • the present invention generally relates to techniques for controlling emissions from dual seals of a variety of types of equipment, such as pumps, valves, compressors, turbines, agitators, centrifuges, mixers and generators, and, more particularly, is concerned with an apparatus for controlling barrier fluid (liquid or gas) leakage from a dual seal so as to maintain a proper level of barrier fluid pressure in the dual seal.
  • VOCs volatile organic compounds
  • the focus of these new regulations is the atmospheric emission of VOCs from chemical and petroleum processing equipment. Many VOCs change phase from a liquid to a gas and become airborne pollutants when leaked from processing equipment. Leakage of VOCs from valves, fittings and mechanical pump seals (the three primary sources of VOC emissions) is referred to as "fugitive" emissions.
  • the present invention provides a dual seal barrier fluid leakage control apparatus designed to satisfy the aforementioned need.
  • the fluid leakage control apparatus of the present invention controls barrier fluid leakage from a dual seal by measuring the amount of barrier fluid leakage and compensating for the amount of barrier fluid leakage measured so as to maintain a proper volume of barrier fluid pressure in the dual seal.
  • the barrier fluid can be a gas or a liquid, depending upon the particular application.
  • the fluid leakage control apparatus of the present invention thus overcomes the problems of dual seals, particularly as employed in the fluid handling equipment of the chemical and petroleum industry where control of fugitive emissions has been identified as an important environmental issue. Also, the fluid leakage control apparatus of the present invention requires little or no periodic maintenance or adjustment, and automatically compensates the barrier fluid pressure with changes in process fluid pressure. Furthermore, quantitative monitoring and measurement of seal leakage is made easy and inexpensive by the fluid leakage control apparatus of the present invention. Such quantitative monitoring and measurement of barrier fluid leakage facilitates the evaluation of when the dual seals should be serviced or replaced.
  • the present invention is directed to an apparatus for controlling leakage of a barrier fluid from a dual seal assembly in fluid handling equipment so as to maintain the barrier fluid at a preset level of pressure above the pressure of process fluid in the equipment.
  • the dual seal assembly includes a process fluid chamber containing pressurized process fluid, a barrier fluid chamber containing pressurized barrier fluid, a primary seal between the process fluid chamber and barrier fluid chamber, and a secondary seal between the barrier fluid chamber and the external atmosphere.
  • the barrier fluid leakage control apparatus comprises first means in the form of a barrier fluid supply arrangement connected to the barrier fluid chamber of the dual seal assembly, second means in the form of a pressure intensifier mechanism, and third means in the form of a pressure monitoring and control arrangement.
  • the pressure intensifier mechanism is coupled to the process fluid chamber and the barrier fluid chamber of the dual seal assembly and is operable to maintain the pressure of the barrier fluid at a preselected level above the pressure of the process fluid in response to the absence of barrier fluid leakage from the dual seal assembly and to decrease the pressure of the barrier fluid below the preselected level in response to the presence of leakage of barrier fluid from the dual seal.
  • the pressure monitoring and control arrangement is coupled to the barrier fluid supply arrangement and to the pressure intensifier mechanism and is operable to detect and measure the difference between the process fluid pressure and barrier fluid pressure and to compensate for the difference by actuating the barrier fluid supply arrangement to supply barrier fluid to the barrier fluid chamber when the difference is below the preset level and until the difference has increased above the preset level.
  • the pressure monitoring and control arrangement is also operable to calculate and provide a readout of the average and instantaneous leakage rates.
  • the barrier fluid leakage control apparatus comprises first means in the form of a barrier fluid supply arrangement connected to the barrier fluid chamber of the dual seal assembly, second means in the form of a pressure intensifier mechanism, and third means in the form of an elongated rod attached and extending from a piston reciprocally mounted in a hollow cylinder of the pressure intensifier mechanism with the rod being movable through a linear displacement directly proportional to the change in volume of barrier fluid in the barrier fluid chamber, and fourth means in the form of a pressure monitoring and control arrangement.
  • the pressure intensifier mechanism is coupled to the process fluid chamber and the barrier fluid chamber of the dual seal assembly and maintains the pressure of the barrier fluid at a preselected level above the pressure of the process fluid in the absence of barrier fluid leakage from the dual seal assembly.
  • the pressure monitoring and control arrangement is coupled to the barrier fluid supply arrangement and to the elongated rod and is operable to measure the linear displacement of the rod to calculate the current position thereof and to compare it with maximum and minimum stored postions and as a result of the comparison to compensate by actuating the barrier fluid supply arrangement to supply barrier fluid to the barrier fluid chamber when the calculated current position is greater or equal to the maximum stored position and by deactuating the barrier fluid supply arrangement to terminate supply of barrier fluid to the barrier fluid chamber when the calculated current position is less than or equal to the minimum stored position of the rod.
  • the pressure monitoring and control arrangement is also operable to calculate and provide a readout of the average and instantaneous leakage rates.
  • the barrier fluid leakage control apparatus comprises first means for supplying barrier fluid to the barrier fluid chamber of the dual seal assembly, second means coupled to the process fluid chamber for sensing and measuring the pressure of the process fluid, third means coupled to the barrier fluid chamber for sensing and measuring the pressure of the barrier fluid, fourth means coupled to the barrier fluid chamber for sensing and measuring the temperature of the barrier fluid, and fifth means coupled to the first means and to the second means, third means and fourth means for receiving measurements of the process fluid pressure and the barrier fluid pressure and temperature, for comparing the process fluid pressure to the barrier fluid pressure and if the barrier fluid pressure is less than the process fluid pressure by a first predetermined amount, then actuating the first means to increase the barrier pressure above the first predetermined amount.
  • the apparatus also includes sixth means connected to the barrier fluid chamber for relieving the barrier fluid pressure such that if the barrier fluid pressure is greater than the process fluid pressure by more than a second predetermined amount, then the fifth means actuates the sixth means to decrease the barrier fluid pressure to less than the second predetermined amount.
  • the pressure monitoring and control arrangement is also operable to calculate and provide a readout of the average and instantaneous leakage rates.
  • the present invention is also directed to a reporting network which comprises a plurality of pumps and/or valves, a plurality of fluid leakage control and measurement apparatuses each being connected to one of the pumps and/or valves and adapted to measure and output data concerning leakage of each of the plurality of pumps and/or valves, a host computer, and means for connecting each of the fluid leakage control and measurement apparatuses in electrical communication to the host computer.
  • the host computer is operable to poll each of the apparatuses to collect the data on leakage from each of the plurality of pumps and/or valves.
  • the host computer enters the leakage data into a database. Reporting software in the computer processes the data and generates leakage status and maintenance reports for the plurality of pumps and/or valve.
  • Fig. 1 is an elevational view of a prior art pump driven by a motor and employing a prior art dual mechanical pump seal assembly to prevent leakage of fluid from the pump to the external environment.
  • Fig. 2 is a longitudinal axial sectional view of the prior art dual mechanical pump seal assembly employed by the pump of Fig. 1.
  • Fig. 3 is a diagrammatic view of a first embodiment of a dual mechanical seal barrier fluid leakage control apparatus of the present invention connected with the dual mechanical pump seal assembly of Fig. 1.
  • Fig. 4 is a diagrammatic view of a second embodiment of the dual mechanical seal barrier fluid leakage control apparatus of the present invention.
  • Fig. 5 is a diagrammatic view of an alternative embodiment of the barrier fluid supply arrangement which can be employed with the leakage control apparatus of the present invention.
  • Fig. 6 is a diagrammatic view of a third embodiment of the dual mechanical seal barrier fluid leakage control apparatus of the present invention.
  • Fig. 7 is a longitudinal axial sectional view of a prior art dual mechanical seal assembly employed by a valve.
  • Fig. 8 is a diagrammatic view of the third embodiment of the control apparatus applied to the valve of Fig. 7 wherein the pumpage and barrier fluids are liquid.
  • Fig. 9 is a fragmentary diagrammatic view of a modified form of the third embodiment of the control apparatus of Fig. 8.
  • Fig. 10 is a diagrammatic view of another modified form of the third embodiment of the control apparatus applied to the valve of Fig. 7 wherein the pumpage and barrier fluids are gases.
  • Fig. 11 is a fragmentary diagrammatic view of a further modified form of the modified third embodiment of the control apparatus of Fig. 10.
  • Fig. 12 is a fragmentary diagrammatic view of another modified form of the modified third embodiment of the control apparatus of Fig. 8.
  • Fig. 13 is a fragmentary diagrammatic view of another modified form of the modified third embodiment of the control apparatus of Fig. 10.
  • Fig. 14 is a fragmentary diagrammatic view of still another modified form of the modified third embodiment of the control apparatus of Fig. 10.
  • Fig. 15 is a diagrammatic view of a fourth embodiment of the dual mechanical seal barrier fluid leakage control apparatus of the present invention.
  • Fig. 16 is a diagrammatic view of a modification to the fourth embodiment of the control apparatus of Fig. 15.
  • Fig. 17 is a diagrammatic view of another modified form of the fourth embodiment of the control apparatus of Fig. 15.
  • Fig. 18 is a diagrammatic view of still another modified form of the fourth embodiment of the control apparatus of Fig. 15.
  • Fig. 19 is a diagrammatic view of yet another modified form of the fourth embodiment of the control apparatus of Fig. 15.
  • Fig. 20 is a diagrammatic view a reporting network of pumps and valves wherein each employs the dual mechanical seal barrier fluid leakage control apparatus of the present invention.
  • fluid handling equipment such as a prior art pump 10 having a central rotary drive shaft 12 coupled to and driven by a pump motor 14 and employing a prior art seal assembly 16 adapted to prevent leakage of environmentally-hazardous pumpage fluid along the rotary drive shaft 12 from the pump 10 to the external environment.
  • the pump 10 has a housing 18 and an impeller (not shown) disposed within the housing 18. The impeller is attached on the rotary shaft 12 to undergo rotation therewith to pump the pumpage fluid, received into the housing 18 through an axial inlet port 20, from the housing 18 through a tangential discharge port 22.
  • the seal assembly 16 is attached to one axial end of the pump housing 18 and disposed along the rotary drive shaft 12 between the pump housing 18 and the pump motor 14.
  • the seal assembly 16 shown is a dual mechanical seal type.
  • the dual seal assembly 16 basically includes a seal housing 24, a pumpage fluid chamber 26, a primary pump seal 28, a secondary pump seal 30, a barrier fluid chamber 32 and a secondary seal impeller 34.
  • the seal housing 24 is disposed about the rotary drive shaft 12 and attached by a plurality of bolts 36 (only one shown) to the one axial end of the pump housing 18.
  • the seal housing 24 in conjunction with the pump housing 18 defines the pumpage fluid chamber 26 which contains the pumpage fluid under a pressure substantially near the operating pressure of the pump 10.
  • the primary pump seal 28 of the dual seal assembly 16 is disposed about the rotary drive shaft 12 proximate to the region of mating between the pump housing 18 and seal housing 24.
  • the primary pump seal 28 includes an annular stationary seal member 28A disposed about the rotary drive shaft 12 and fixedly mounted to the seal housing 24 and an annular rotary seal member 28B disposed about the rotary drive shaft 12 within the pumpage fluid chamber 26 and mounted to the rotary drive shaft 12 for rotation therewith and axially slidable movement therealong.
  • the secondary pump seal 30 is disposed about the rotary drive shaft 12 within the barrier fluid chamber 32 and is axially spaced from the primary pump seal 28.
  • the secondary pump seal 30 includes an annular stationary seal member 30A disposed about the rotary drive shaft 12 and fixedly mounted to the seal housing 24 and an annular rotary seal member 30B disposed about the rotary drive shaft 12 within the barrier fluid chamber 32 and mounted to the rotary drive shaft 12 for rotation therewith and axially slidable movement therealong.
  • Attachment means in the form of another collar 44 fixedly attached to the rotary drive shaft 12 and another spring 46 disposed between the collar 44 and rotary seal member 30B mount the rotary seal member 30B to the rotary drive shaft 12 and also bias the rotary seal member 30B toward and into a sealing relationship with the stationary seal member 30A.
  • the secondary pump seal 30 at one side communicates with the barrier fluid chamber 32 and at an opposite side communicates with an annular passageway 48 defined in the seal housing 24 which leads from the secondary pump seal 30 to the exterior of the dual seal assembly 16 and to the atmosphere.
  • the barrier fluid chamber 32 is generally annular in shape and so is defined about the rotary drive shaft 12 within the seal housing 24 between and in communication with the primary and secondary pump seals 28, 30.
  • the secondary seal impeller 34 is attached to the collar 44 and so rotates with the rotary drive shaft 12, acting as an auxiliary pump and causing the barrier fluid to flow through the barrier fluid chamber 32 and about a recirculation circuit 50 connected to the seal housing 24 via inlet and outlet ports 24A, 24B.
  • the barrier fluid flows in the recirculation circuit 50 in the direction of arrows A shown in Fig. 1.
  • the barrier fluid picks up and carries away some of the heat generated by the primary and secondary pump seals 28, 30.
  • the heat-bearing barrier fluid flows through a heat exchanger 52 interposed in the recirculation circuit 50 which receives the transfer of heat from the barrier fluid and thereby cools the barrier fluid and the primary and secondary pump seals 28, 30 as well.
  • the pressure of the barrier fluid must remain a desired amount, for example 10%, above the pressure of the pumpage fluid.
  • Pumpage fluid leakage problems therefore arise when the pumpage fluid pressure increases and nears or even exceeds the barrier fluid pressure due to changes in processing conditions or pump speed, or when the barrier fluid leaks due to the high differential pressure across the secondary pump seal that seals the barrier fluid from the external atmosphere.
  • a first embodiment of the dual seal barrier fluid leakage control apparatus of the present invention being generally designated 54, which alleviates the aforementioned problems of the prior art dual seal assembly 16.
  • the barrier fluid leakage control apparatus 54 integrates a pressure intensifier mechanism 56, a barrier fluid supply arrangement 58 and a pressure monitoring and control arrangement 60, with the dual seal assembly 16. Such integration maintains the pressure of the barrier fluid in the barrier fluid chamber 32 at the desired level greater than the pressure of the pumpage fluid in the pumpage fluid chamber 26.
  • Such integration also supplies barrier fluid to the dual seal assembly 16, as needed, to compensate leakage, and calculates the barrier fluid leakage rates in order to provide vital information that is useful for scheduling pump seal maintenance.
  • the leakage control apparatus in the first embodiment as well as the other embodiments of the present invention, is not limited to fugitive emissions as defined by the EPA, nor limited to dual mechanical seals.
  • the term "mechanical” seal is a special term for a rotating face seal used for pumps.
  • the seal barrier fluid leakage control apparatus of the present invention can be used for any type of dual seal on any type of equipment that uses a barrier fluid.
  • the term “pumpage” fluid is used herein since the equipment being referred in the illustrated example of the application of the present invention is a pump.
  • the term “process” fluid would be used.
  • the term “pumpage” fluid is also meant to represent other "process” fluids.
  • the pressure intensifier mechanism 56 of the control apparatus 54 includes a mounting assembly 62 having a pair of first and second opposite end caps 62A, 62B and a plurality of elongated bolts 62C extending between and interconnecting the end caps 62A, 62B.
  • the pressure intensifier mechanism 56 also includes a pair of first and second solid opposite end bodies or manifolds 64, 66 secured by the mounting assembly 62 at opposite ends of a hollow tubular body 67, an elongated piston 68 reciprocally mounted in the hollow tubular body 67, and means in the form of a resilient compressible spring 70 disposed in the hollow tubular body 67 between the piston 68 and the first end manifold 64.
  • the hollow tubular body 67 is formed by a pair of large and small diameter hollow cylinders 72, 74 being disposed in tandem relationship along a common central axis.
  • the large and small cylinders 72, 74 are open at respective inner ends 72A, 74A disposed adjacent to one another and at respective outer ends 72B, 74B disposed remote from one another.
  • the first and second solid opposite end manifolds 64, 66 have respective ports 76, 78 defined therethrough connected respectively in flow communication with the open outer ends 72B, 74B of the large and small cylinders 72, 74.
  • the port 76 is also connected by flow lines 80, 82 in flow communication respectively with the pressure monitoring and control arrangement 60 and an orifice 84 defined in the seal housing 24 to lead to the pumpage fluid chamber 26 and provide communication of the pumpage fluid with the pressure intensifier mechanism 56.
  • the port 78 is also connected by flow lines 86, 88 in flow communication respectively with the barrier fluid circuit 50 and the barrier fluid supply arrangement 58.
  • the elongated piston 68 reciprocally mounted in the large and small cylinders 72, 74 has a large diameter body portion 68A disposed in the large diameter cylinder 72 and a small diameter body portion 68B disposed in the small diameter cylinder 74 and in tandem relation with the large diameter body portion 68A.
  • the piston 68 also has opposite ends 68C, 68D of large and small surface areas on the respective large and small diameter body portions 68A, 68B and disposed adjacent to the respective first and second end manifolds 64, 66.
  • the pumpage fluid communicates through the port 76 of the first end manifold 64 into the outer open end 72B of the large cylinder 72 and into contact with the large surface area end 68C of the large diameter body portion 68A of the piston 68.
  • the pressure of the pumpage fluid acts upon the large surface area end 68C of the piston 68, forcing the piston 68 to move toward the second end manifold 66, compressing the barrier fluid and thereby intensifying, or increasing, the barrier fluid pressure to a predetermined higher pressure at the small surface area end 68D of the small diameter body portion 68B of the piston 68 in contact with the barrier fluid.
  • the difference in, or ratio of, the surface areas of the opposite ends 68C, 68D of the piston 68 is predetermined so as to increase the pressure of the barrier fluid to and thereby maintain the pressure of the barrier fluid at a preset level, such as 10%, above the pressure of the pumpage fluid.
  • a preset level such as 10%, above the pressure of the pumpage fluid.
  • seals 89 are provided in the first and second opposite end manifolds 64, 66 to prevent leakage of pumpage and barrier fluids.
  • a small bore 90 is defined through the center of the piston 68. The small bore 90 transfers barrier fluid from the small diameter cylinder 74 to a lantern ring 92 which separates a pair of annular seals 94, 96 that seal the pumpage fluid on the large diameter body portion 68B of the piston 68, creating a seal barrier for the pumpage fluid.
  • the spring 70 of the pressure intensifier mechanism 56 located in the small diameter cylinder 74 positions the piston 68 toward the left ends of both large and small diameter cylinders 72, 74, as viewed in Fig. 3.
  • the piston 68 will move toward the right ends thereof as a result of barrier fluid leakage from the primary and secondary pump seals 28, 30.
  • Pressure in the small diameter cylinder 74 is decreased or reduced by the compression of the spring 70 acting against the force of the piston 68.
  • the more the piston 68 is moved toward the right ends of the cylinders 72, 74 the greater the counteracting spring force on the piston 68 and the greater the decrease in the pressure of the barrier fluid in the small diameter cylinder 74.
  • the decrease in the pressure of the compressed barrier fluid is proportional to the amount of the barrier fluid leakage.
  • the pressure monitoring and control arrangement 60 detects and measures the barrier fluid pressure relative to the pumpage fluid pressure and together with the barrier fluid supply arrangement 58 compensate for any barrier fluid leakage so as to maintain the barrier fluid pressure at. the preset level higher, such as about 10% higher, than the pumpage fluid pressure.
  • the barrier fluid supply arrangement 58 includes a pump 98 connected in flow communication between a barrier fluid reservoir or tank 100 and the flow line 88 via a one-way check valve 102 connected to the barrier fluid side of the pressure intensifier mechanism 56 and to the circuit 50 via the flow line 86.
  • the supply arrangement 58 also includes a motor 104 drivingly coupled to the pump 98.
  • Operation of the motor 104 drives the pump 98 to inject barrier fluid under pressure from the tank 100 through the one-way check valve 102 toward the circuit 50 which increases the volume of barrier fluid in the circuit 50. Injection of barrier fluid from the supply arrangement 58 is controlled by an electrical input to the motor 104 from the pressure monitoring and control arrangement 60.
  • barrier fluid leaks from the dual seal assembly 16 Since the barrier fluid pressure is always higher than the pumpage fluid pressure, barrier fluid leaks into the pumpage fluid from across the primary pump seal 28. However, because of the high differential seal pressure, leakage is more likely across the secondary pump seal 30 that seals the barrier fluid from the external environmental atmosphere. Barrier fluid leakage across the primary or secondary pump seals causes a change in volume which is compensated for by the movement of the intensifier mechanism piston 68 toward the right and also by compression of the spring 70 in the small diameter cylinder 74. The spring 70 compression will decrease or reduce the barrier fluid pressure to less than the desired 110% of the pumpage fluid pressure.
  • the pressure monitoring and control arrangement 60 includes a pair of differential pressure switches 106, 108, a pressure switch 110, a motor control logic circuit (MCLC(l)) 112, a microprocessor 114 and a digital display 116.
  • the one differential pressure switch 106 is set to activate at a preset high pressure and the other differential pressure switch 108 is set to activate at a preset low pressure.
  • the two differential pressure switches 106, 108 are disposed in parallel with the pressure intensifier mechanism 56 and in parallel with one another in a flow line 118 which extends between and connects with the respective flow lines 82, 88 so as to sense the pressures of the pumpage and barrier fluids at the respective opposite sides of the differential pressure switches 106, 108.
  • the pressure switch 110 is connected by the flow line 82 to pumpage fluid side of the pressure intensifier mechanism 56.
  • the outputs from the pressure switches 106, 108, 110 are connected to the MCLC(l) 112 as inputs.
  • the MCLC(l) 112 is a digital logic or latching relay circuit that performs the following control functions:
  • the pressure switch 110 connected to the pumpage fluid side of the intensifier mechanism 56 is checked for low pressure, which indicates that the pump 10 is not operating. If the pressure is low, output from the MCLC(l) 112 is disabled.
  • MCLC(l) 112 to cause termination of the operation of the motor 104 and pump 98, ceasing the injection of more barrier fluid into the circuit 50. This process of barrier fluid injection occurs each time a single intensifier piston stroke (volume) of barrier fluid is leaked.
  • an output signal is sent to the microprocessor 114 which records the event date and time. Consecutive dates and times are subtracted from one another to determine the time from the last injection of barrier fluid. The time calculated is divided into the known volume of barrier fluid for a single stroke of the intensifier mechanism piston 68. The resulting calculation is an average leakage rate displayed on the digital display 116.
  • FIG. 4 there is illustrated a second embodiment of the barrier fluid leakage control apparatus 54 of the present invention which differs from the first embodiment thereof of Fig. 3 only in the pressure monitoring and control arrangement 60 and the method of calculating the leakage rate.
  • the average leakage rate calculations as described above with respect to the first embodiment of the barrier fluid leakage control apparatus 54 of Fig. 3 can require long periods of time before an updated leakage calculation takes place. The long period may provide misleading information about the pump seal status, particularly if the leakage rate is increasing over time.
  • An improved approach is taken by the second embodiment of the barrier fluid leakage control apparatus 54 of Fig. 4 wherein an instantaneous and an average leakage rate for the pump seals are calculated.
  • the pressure monitoring and control arrangement 60 of the second embodiment of the barrier fluid leakage control apparatus 54 includes a pair of first and second pressure transducers 120, 122 respectively connected to the flow lines 82, 88 and thus to respective pumpage fluid and barrier fluid sides of the pressure intensifier mechanism 56.
  • a d.c. voltage proportional to pressure is generated as the outputs from the first and second pressure transducers 120, 122.
  • Two outputs are generated from each pressure transducer 120, 122 and are connected as inputs to an analog-to-digital (A/D) converter 124 and another motor control logic circuit (MCLC(2)) 126.
  • the MCLC(2) 126 which is an analog and/or digital circuit or is functionally incorporated into the software of the microprocessor 114, performs the following control functions:
  • the first pressure transducer 120 connected to the pumpage fluid side of the intensifier mechanism 56 is checked for a zero pressure, which indicates that the pump 10 is not operating. If the pressure is zero, then the output from the MCLC(2) is disabled.
  • the difference in pressure is compared to a minimum allowable pressure. If the difference in pressure between the second pressure transducer 122 and the first pressure transducer 120 is less than or equal to the minimum allowable differential pressure, then the electrical signal output to the motor 104 of the barrier fluid supply arrangement 58 is turned “on". Barrier fluid is injected by the pump 98 into the circuit 50 of the dual seal assembly 16 and barrier fluid side of the intensifier mechanism 56 until the pressure difference between the second pressure transducer 122 and the first pressure transducer 120 reaches a predetermined maximum value, indicating that the pressure intensifier mechanism piston 68 has moved to the far left thereof. Once the pressure difference has reached a maximum, the motor 104 operating the pump 98 of the barrier fluid supply arrangement 56 is turned “off".
  • an output signal from the MCLC(2) 126 is sent to the microprocessor 114 and an average leakage rate is calculated by the microprocessor 114 similar to the average leakage rate calculated for the leakage control apparatus 54 of the first embodiment of Fig. 3 described above.
  • outputs from the first and second pressure transducers 120, 122 are connected to the A/D converter 124 which takes the voltage outputs from the pressure transducers and converts the voltages to digital outputs.
  • the digital output signals are sent to and stored in the memory of the microprocessor 114.
  • leakage rates can be transmitted to a central computer and entered into a database.
  • Thg database in turn, can be used for plant maintenance scheduling.
  • FIG. 5 there is illustrated an alternative embodiment of the barrier fluid supply arrangement 58 which can be employed with the leakage control apparatus 54 of the present invention.
  • the barrier fluid supply arrangement 58 injects barrier fluid under pressure into the barrier fluid recirculation circuit 50 to replace barrier fluid leaked from the primary and secondary pump seals 28, 30 respectively into the pumpage fluid chamber 26 and to the external environment.
  • the barrier fluid supply arrangement 58 in Fig. 5 utilizes a solenoid controlled valve 132 and a pressure accumulator 134 in place of the pump 98, tank 100 and motor 104 of the barrier fluid supply arrangement 58 of Figs. 3 and 4.
  • Fig. 6 there is illustrated a third embodiment of the dual mechanical seal barrier fluid leakage control apparatus 54 of the present invention.
  • the third embodiment of the leakage control apparatus 54 of Fig. 6 is similar to the first and second embodiments thereof described above and illustrated respectively in Figs. 3 and 4.
  • the leakage control apparatus 54 is coupled with the dual mechanical seal assembly (not shown in Fig. 6) in the same manner.
  • the barrier fluid is maintained at the higher pressure than the pumpage fluid by the use of the pressure intensifier mechanism 56.
  • the pressure monitoring and control arrangement 60 charges the barrier fluid circuit (not shown in Fig. 6) with barrier fluid, as needed, from the barrier fluid supply arrangement 58 and calculates average and instantaneous seal leakage rates.
  • the pressure intensifier mechanism 56 shown in Fig. 6 includes a cylinder 136, a pair of first and second end manifolds 138, 140"respective mounted to pumpage fluid and barrier fluid ends of the intensifier mechanism 56, a piston 142 reciprocally mounted in the cylinder 136, and an elongated rod 144 connected at one end to the piston 142 and protruding from the second end manifold 140 through a passage 146 defined therethrough at the barrier fluid end of the intensifier mechanism 56.
  • the rod 144 reduces the effective area on the right or barrier fluid side of the piston 142, thereby creating a higher fluid pressure in the right end of the cylinder 136.
  • the intensifier mechanism 56 of the leakage control apparatus 54 of Fig. 6 ensures that the barrier fluid pressure is always higher than the pumpage fluid pressure.
  • the leakage control apparatus 54 in the third embodiment of Fig. 6 includes an electronic linear measurement device 148 coupled to the protruding end portion 144A of the elongated rod adjacent to and exterior of the second end manifold 140.
  • the measurement device 148 measures the movement and position of the piston 142 relative to the cylinder 136.
  • the electronic linear measurement device 148 can take the form of any one of several types of passive or active electronic linear meansurement components, such as variable resistance type, electromagnetic-linear transformer type, acoustic type, optical type and mechanical switch type. All types of the linear measurement device 148 generates an electrical output signal (voltage, current or digital pulses) indicating movement of the intensifier piston 142.
  • Movement of the piston 142 is directly proportional to the amount of barrier fluid leaked or added to the barrier fluid circuit (not shown in Fig. 6) via the flow lines 86, 88.
  • the resulting electrical signal from the linear measurement device 148 is inputted to the pressure monitoring and control arrangement 60 that adds barrier fluid to the circuit as needed and calculates average and instantaneous seal leakage rates.
  • the pressure monitoring and control arrangement 60 includes an analog-to-digital converter 150, a pressure switch 152, a microprocessor 154 and digital displays 156, 158.
  • the output signal from the electronic linear measurement device 148 is sent to the A/D converter 150 if the output is analog and then is sent to the microprocessor 154. If the output is digital or generated by limit switches, then the output is routed directly to the microprocessor 154.
  • the microprocessor 154 also may collect information from the pressure switch 152 connected to the pumpage fluid end of the intensifier mechanism 56 concerning the status of the pump (not shown). However, the provision of pressure switch 152 is an option, not essential to the operation of the arrangement 60.
  • a software program stored in the microprocessor 154 operates and controls three functions.
  • the first function controls the barrier fluid supply arrangement 58 to ensure at all times an adequate supply of barrier fluid in the intensifier mechanism 56 and in the barrier fluid circuit connected with the dual seal assembly. This function is similar to the tjat performed by the MCLC(l) 112 and MCLC(2) 126 in the first and second embodiments of the leakage control apparatus 54 in Figs. 3 and 4.
  • the logic for this first software program function is as follows:
  • step (1) Go to step (1) .
  • this control function is performed digitally with software, it could be performed by a control logic circuit when the same software logic is designed into the hardware.
  • the second software program control function calculates an average leakage rate of the barrier fluid, knowing the displacement of the piston 142, the area of the barrier fluid side of the piston, and the time duration for the displacement.
  • the logic for the second software program function is as follows:
  • the logic for the second software program function can be simplified by using the minimum stored position in the first software program function for the initial position, and by using the maximum stored value in the first software program function for the final position.
  • the third software program function calculates an instantaneous leakage rate of the barrier fluid. Calculating the instantaneous leakage rate follows the same logic as the average leakage rate, except that the distances, volumes and times are much smaller.
  • Another software program or algorithm can be used to calculate the average and instantaneous leakage rates.
  • This software function is time based rather than positional based.
  • the logic for this alternative software function is as follows:
  • FIG. 7 there is illustrated fluid handling equipment in the form of a prior art valve 160 having a valve bonnet 162 and a central shaft 164 mounted through an elongated central bore 166 defined through the valve bonnet 162.
  • the shaft 164 is mounted to undergo both rotational and axial movement relative to the valve bonnet 162 by rotation of a handle 168 on the outer end 164A of the shaft 164 in order to cause respective seating and unseating of an enlarged head 170, being attached to the inner end 164B of the shaft 164, onto and from an opening 172 formed in a flow coupler 174.
  • the uncovered opening 172 will permit flow of fluid through the coupler 174.
  • the valve 160 incorporates a seal assembly 176 also being in the form of a dual mechanical seal type.
  • the dual seal assembly 176 is composed of packing elements that are equivalent in function to the above- described primary and secondary seals 28, 30 of the dual seal assembly 16 of the pump 10 and therefore need not be described in detail.
  • the valve bonnet 162 is modified to incorporate two fluid flow lines 178, 180, the one fluid flow line 178 being connected in flow communication to the pumpage fluid flowing through the coupler 174 and controlled by the head 170 on the valve shaft 164 and the other fluid flow line 180 being connected in flow communication to the annular chamber 182 surrounding the shaft 164 and containing the barrier fluid.
  • the valve 160 can be coupled via the fluid flow lines 178, 180 to various embodiments of the leakage control apparatus 54 which are similar to those described above with reference to the rotary pump 10.
  • FIG. 8 there is illustrated a leakage control apparatus 54 which is similar to the apparatus 54 already described earlier with reference to Fig. 6.
  • the components of the apparatus 54 in Fig. 8 which are similar to the components of the apparatus 54 in Fig. 6, are identified by the same reference numerals as used in Fig. 6.
  • the only difference now is the absence from the pressure intensifier mechanism 56 of Fig. 8 of the pressure switch 152 on the side of the pumpage fluid flow line 178 of the pressure intensifier mechanism 56 in Fig. 6.
  • the pressure switch 152 is not essential to the operation of the leakage control apparatus 54.
  • the apparatus 54 operates satisfactorily for valves controlling high or low pressure at temperatures near ambient.
  • FIG. 9 there is illustrated a leakage control apparatus 54 which is similar to the leakage control apparatus 54 of Fig. 8.
  • the components of the apparatus 54 of Fig. 9 which are similar to the components of the apparatus 54 in Fig. 8, are identified by the same reference numerals as used in Fig. 8.
  • the only differences between the arrangement of Fig. 9 and that of Fig. 8 are the absence of the barrier fluid supply arrangement 58 in Fig. 9 and the addition of a charging valve 184 in Fig. 9.
  • the barrier fluid supply arrangement 58 is only needed in applications where large leakage quantities can be tolerated.
  • the apparatus 54 of Fig. 9 the apparatus 54 of Fig.
  • the reservoir for the barrier fluid is the pressure intensifier mechanism 56 itself and only a small amount of barrier fluid can be leaked before more liquid must be added.
  • the charging valve 184 is used for charging the pressure intensifier mechanism 56 with barrier fluid.
  • This apparatus 54 of Fig. 9 also works well for valves controlling high or low pressure at temperatures near ambient.
  • a leakage control apparatus 54 adapted for handling a gas fluid whose arrangement is similar to the apparatus 54 of Fig. 8 which is adapted for handling a liquid fluid.
  • the components of the apparatus 54 in Fig. 8 which are similar to the components of the apparatus 54 in Fig. 10, are identified by the same reference numerals as used in Fig. 8.
  • the basic operation of the apparatus 54 of Fig. 10 in a gas barrier fluid application is the same as in the liquid barrier fluid application; gas barrier fluid is maintained at a higher pressure than the valve gas fluid pressure and leakage is detected from movement of the protruding rod 144 of the pressure intensifier mechanism 56, indicating a change in gas barrier fluid volume.
  • pressure and temperature of the barrier gas must be measured and converted to a digital input for leakage rate calculations.
  • pressure and temperature transducers 186, 187 are added to the apparatus 54 of Fig. 10 to sense the pressure and temperature of the barrier gas in the intensifier mechanism 56 and output the sensed temperature to the A/D converter 150.
  • the quantity of barrier gas between the seals of the dual seal assembly 176 of the valve 160 is controlled by the position of the piston 142 of the pressure intensifier mechanism 56, using the same software program or algorithm as described earlier for a liquid barrier fluid.
  • Another software program or time-based algorithm used for calculating leakage rates for a gas barrier fluid is as follows:
  • FIG. 11 there is illustrated a leakage control apparatus 54 which is similar to the leakage control apparatus 54 of Fig. 10.
  • the components of the apparatus 54 of Fig. 11 which are similar to the components of the apparatus 54 in Fig.
  • Fig. 11 are identified by the same reference numerals as used in Fig. 10.
  • the only differences between the arrangement of Fig. 11 and that of Fig. 10 are the absence of the barrier fluid supply arrangement 58 in Fig. 11 and the addition of a charging valve 184 in Fig.
  • the barrier fluid supply arrangement 58 is only needed in applications where large leakage quantities can be tolerated.
  • the reservoir for the barrier fluid is the pressure intensifier mechanism 56 itself and only a small amount of barrier fluid can be leaked before more liquid must be added.
  • the charging valve 184 is used for charging the pressure intensifier mechanism 56 with barrier fluid.
  • the apparatus 54 of Fig. 11 also works well for valves controlling fluid at high or low temperatures.
  • FIGs. 12 and 13 there is illustrated respective arrangements of the apparatus 54 for liquid and gas barrier fluid applications that are similar to respective arrangements of the apparatus 54 of Figs. 8 and 10.
  • the arrangements of Figs. 12 and 13 use a pressure transducer 188 interposed in the barrier fluid flow line 180 between the barrier fluid chamber 182 of the valve 160 and the pressure intensifier mechanism 56, and a barrier fluid isolation valve 190 interposed in the barrier fluid flow line 180 between the pressure transducer 188 and the pressure intensifier mechanism 56.
  • the barrier fluid isolation valve 190 is used to determine where the barrier fluid is leaking.
  • the isolation valve 190 is normally left open during operation.
  • this valve 190 is closed and the pressure of the barrier fluid is monitored over time. If the barrier fluid pressure drops to the process fluid pressure but no lower, then the barrier fluid is leaking into the process fluid and not into the atmosphere. But, if the barrier fluid pressure drops below the pressure of the process fluid, then the barrier fluid is leaking into the atmosphere and may also be leaking into the process fluid as well. The system continues with its normal operation after determining where the leakage is located. Determining where barrier fluid is leaking can also be accomplished without the addition of the isolation valve 190 to the apparatus 54.
  • Finding where the barrier fluid is leaking without an isolation valve is accomplished by waiting for the barrier fluid to leak enough until the intensifier mechanism piston 142 has moved all the way to the right of the cylinder 136 without recharging the intensifier mechanism 56 with barrier fluid. After the piston 142 has moved all the way to the right end of the cylinder 136 and "bottomed out," the pressure of the barrier fluid is monitored over time as described above. If the barrier fluid pressure drops to the process fluid pressure but no lower, then the barrier fluid is leaking into the process fluid and not into the atmosphere. But, if the barrier fluid pressure drops below the pressure of the process fluid, then the barrier fluid is leaking into the atmosphere and may also be leaking into the process fluid as well. The apparatus continues with its normal operation after determining where the leakage is located. However, the advantage of the use of the isolation valve 190 is that the test for leakage can be done at any time. The other method of making this test requires time for the piston 142 to move all the way to the right in the cylinder 136 before the test can be performed.
  • a leakage control apparatus 54 which is similar to the leakage control apparatus 54 of Fig. 10.
  • the components of the apparatus 54 of Fig. 14 which are similar to the components of the apparatus 54 in Fig. 10, are identified by the same reference numerals as used in Fig. 14.
  • the only differences between the arrangement of Fig. 14 and that of Fig. 10 is the use of a pressure relief valve 194 connected to the barrier gas volume in the pressure intensifier mechanism 56.
  • the barrier gas pressure relief valve 194 is used to control the barrier gas pressure where there are large changes in the process fluid pressure. For example, closing the valve 160 connected to the intensifier mechanism 56 can cause a drop in process fluid pressure causing the piston 142 to move to the left as the barrier gas is allowed to expand.
  • the piston 142 will move to the left end of the cylinder 136 and stop. Once the piston 142 is positioned at the left end of the cylinder 136, the barrier gas pressure cannot be lowered to compensate for the lowering of the process fluid pressure. Although the barrier gas pressure is still higher than the process fluid pressure, it is no longer at a pre-set level above the process fluid.
  • the pressure relief valve 192 is added along with controlling software to open the valve when necessary.
  • the controlling software senses the position of the piston 142 by reading the output from the electronic linear measurement device 148. If the piston 142 is at the far left end of the cylinder 136, just about to contact the end of the cylinder, then the pressure relief valve 192 is opened, reducing the barrier fluid pressure and preventing the piston from making contact with the left end of the cylinder 136.
  • the pressure relief valve 192 is closed when the piston 142 moves to the right, back from the left end of the cylinder 136 to the normal operating range of the piston's stroke.
  • a barrier fluid leakage control apparatus 194 which operates using a liquid barrier fluid (or, alternatively, a gas barrier fluid), but does not use the pressure intensifier mechanism 56 nor the electronic linear measurement device 148 of the control apparatus 54 described above with reference to Figs. 6 to 14.
  • the operation of barrier fluid leakage control apparatus 194 begins with measurement of the process fluid pressure via process inflow line 178 with a first pressure transducer 196.
  • the analog voltage output from the first pressure transducer 196 is converted to a digital signal by an analog to digital (A/D) converter 198 and transmitted therefrom to a microprocessor 200.
  • a second pressure transducer 202 measures the barrier liquid pressure between the dual seals. This pressure, also represented by an analog voltage, is converted to a digital signal with the aid of the A/D converter 198 and sent to the microprocessor 200.
  • a temperature transducer 204 measures the temperature of the gas volume in an accumulator 206 and generates a third analog voltage representing such temperature which is converted by the A/D converter 198 to a digital signal and sent to the microprocessor 200.
  • the pressure measurement PI from the process fluid is compared to the pressure measurement P2 from the barrier fluid.
  • pressure P2 is less than 109% of PI, then a signal is sent to the barrier fluid supply arrangement 208 to increase the barrier pressure. If pressure P2 is more than 111% of PI, then a signal is sent to the pressure relief valve to lower the barrier fluid pressure. This process operates continuously maintaining the pressure P2 at 110% of PI with plus or minus 1% tolerance. Other percent pressure ranges can be used for various applications by changing parameters within the microprocessor software.
  • the first calculation calculates the volume of barrier fluid between the dual seals before the addition to the barrier fluid is made.
  • calculation two the volume of barrier fluid between the dual seals is calculated after the addition of barrier fluid is made.
  • calculation three the difference is calculated between the volume calculated after the previous correction cycle, or volume calculation number two, and before the next pressure correction cycle, or volume calculation number one, and then is divided by elapsed time.
  • the first two calculations are computed using an equation "of state" for the accumulator gas, e.g. van der Waal's equation and the other more accurate equations mentioned earlier.
  • the last of these calculations, the third calculation is the amount of barrier fluid leaked from the volume between the dual seals divided by the elapsed time between barrier fluid addition. This is the leakage rate of barrier fluid.
  • the process of recalculating the leakage rate every time a correction is made to the barrier fluid pressure may not be frequent enough to give accurate leakage results. For example, if there is very little leakage and the tolerance for pressure control is relatively high, there may be a long time before an updated leakage value is calculated and displayed on displays 210, 212 connected to the microprocessor 200. Furthermore, there will be a problem with the first pressure correction cycle calculation since no previous calculation exists. To prevent these problems the microprocessor 200 can be programmed to recalculate the barrier fluid leakage after a given elapsed time period, for example, once every minute. Another possible approach to these problems is to recalculate the leakage rate after the microprocessor 200 has been sent a signal from a local switch or another microprocessor.
  • Another useful piece of information about the barrier fluid leakage rate is the long term average leakage rate displayed on display 212. This calculated value, compared to the instantaneous leakage rate displayed on display 210, indicates if there is a progressive leakage problem. Average leakage rates are calculated by storing and averaging leakage rates over long periods, for example, one week.
  • this software program determines where the barrier fluid is leaking by suspending the pressure correction control software and measuring the change in barrier fluid pressure over time. If the barrier fluid pressure drops to the process fluid pressure but no lower, then the barrier fluid is leaking into the process fluid and not into the atmosphere. But, if the barrier fluid pressure drops below the pressure of the process fluid, the barrier fluid is leaking into the atmosphere and may also be leaking into the process fluid as well. After this software execution is completed, the pressure control and leakage measurement software execution is reinstated.
  • a software program or alogrithm for pressure control and leakage measurement is as follows:
  • a heat exchanger 216 should be used in high temperature environments to cool the barrier liquid (or gas) if the electronic components of the detection and measurement arrangement 194 are located nearby.
  • An additional temperature probe 217 is located on the heat exchanger 216 and connected to temperature transducer 204. The additional temperature measurement is used in the calculations for more accurate results.
  • FIGs. 17 to 19 there are illustrated leakage control apparatuses 194 which are similar to the fourth embodiment of the leakage control apparatus 194 of Fig. 15.
  • the components of the apparatuses 194 of Figs. 17 to 19 which are similar to the components of the apparatus 194 in Fig. 15, are identified by the same reference numerals as used in Fig. 15. Only the differences between the arrangements of Figs.
  • the modified form of the leakage control apparatus 194 being illustrated is directed to sealing applications which have a process fluid pressure that is relatively constant. In such applications, the apparatus 194 of Fig. 15 will function satisfactorily. However, the apparatus 194 of Fig. 15 has more than enough components to do the job. Since the process fluid pressure is constant, there is now no need for the pressure transducer 196 connected to the process fluid nor for the pressure relief valve 214 connected to the barrier fluid. Both of these components were used to regulate the barrier fluid pressure in response to a change in process fluid pressure.
  • the leakage control apparatus 194 of Fig. 17 used for applications that have constant pressure is thus identical with the apparatus 194 of Fig. 15 after elimination of the use of the pressure transducer 196 and pressure relief valve 214 therefrom.
  • FIG. 18 another modified form of the leakage control apparatus 194 which is illustrated therein is like the apparatus 194 of Fig. 17 and is also directed to sealing applications which have a process fluid pressure that is relatively constant.
  • the only difference between the apparatus 194 of Fig. 17 and that of Fig. 18 is how the barrier fluid pressure is measured.
  • the barrier fluid pressure is measured by the pressure transducer 202 and sent to the microprocessor 200 via the analog- to-digital converter 198.
  • the apparatus 194 of Fig. 18 uses high and low pressure switches 203 to respectively sense maximum and minimum pressure limits, and sends this information directly to the microprocessor 200.
  • FIG. 19 yet another modified form of the leakage control apparatus 194 which is illustrated therein is derived from the apparatus 194 of Fig. 17 and also is directed to sealing applications which have a process fluid pressure that is relatively constant.
  • the barrier fluid supply arrangement 208 of the apparatus 194 of Fig. 17 has been eliminated and a low-pressure alarm 205 has been added to the apparatus 194 of Fig. 19.
  • the elimination of the barrier fluid supply reduces the cost of the apparatus and reduces the power requirements for the apparatus (recall that the barrier fluid supply has either a solenoid-operated valve or a small electric motor-driven pump) .
  • the elimination of the barrier fluid supply requires that barrier fluid must be added manually by operating a charging valve 207 to replace leaked barrier fluid.
  • the aforementioned low-pressure alarm 205 has been added in the apparatus 194 of Fig. 19.
  • a pump and valve reporting network generally designated 218.
  • the network 218 can be constructed using several different types of communication media and communication standards.
  • Each pump/valve 220 node has an advanced communication chip that allows a host computer 222 connected to the network 218 to poll each pump/valve node 220 for leakage information.
  • Leakage data from each node 220 is collected by the host computer 222 over the network 218 and entered into a database.
  • Reporting software located on the host computer 222 runs against the database, generating leakage status and maintenance reports for the entire network.
  • Pump/valve reporting networks can include hundreds of nodes spanning entire chemical refinery processing plants.
  • the seal barrier fluid leakage control apparatus 54 can be used for any type of dual seal that uses a barrier fluid.
  • a barrier fluid For example, it has been suggested that oil and gas wells have a dual seal with barrier fluid to prevent contamination of water-bearing formations.
  • Another example is a dual piping system wherein an inner pipe contains contaminated fluid and an outer pipe contains a barrier fluid between the annulus defined by the pipes.
  • Still another example is a storage tank which has a liner surrounding the tank.
  • the storage tank contains some unsafe fluid and the liner contains the barrier fluid.

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Abstract

Un appareil pour surveiller les fuites de fluide d'arrêt d'un système à deux joints d'étanchéité dans des appareils tels qu'une pompe ou une vanne, comprend un système d'alimentation (58) en fluide d'arrêt, en communication avec une chambre (32) de fluide d'arrêt du système (16) à deux joints d'étanchéité, un mécanisme (56) permettant d'augmenter la pression coopérant avec une chambre (26) de pompage du fluide et la chambre (32) de fluide d'arrêt du système (16) à deux joints d'étanchéité. Cet appareil permet de maintenir la pression du fluide d'arrêt à un niveau déterminé au-dessus de la pression du fluide traité en absence d'une fuite de fluide d'arrêt du système (16) à deux joints d'étanchéité. Un système (60) de surveillance de la pression coopérant avec le système (58) d'alimentation en fluide d'arrêt et le mécanisme (56) permettant d'augmenter la pression détecte et mesure toute chute de pression en dessous du niveau déterminé et la compense.
PCT/US1995/012581 1994-09-30 1995-09-29 Appareil pour surveiller d'eventuelles fuites de fluide d'arret d'un systeme a deux joints d'etancheite Ceased WO1996010707A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU38249/95A AU3824995A (en) 1994-09-30 1995-09-29 Dual seal barrier fluid leakage control apparatus

Applications Claiming Priority (4)

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US31582194A 1994-09-30 1994-09-30
US08/315,821 1994-09-30
US53535695A 1995-09-28 1995-09-28
US08/535,356 1995-09-28

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2764037A1 (fr) * 1997-06-03 1998-12-04 Samson Ag Appareil de regulation
EP1243772A3 (fr) * 2001-03-23 2003-06-04 C.R.F. Società Consortile per Azioni Système de diagnose pour des fuites des systèmes de refoulement à gaz et procédé d'inspection des soupapes de ces systèmes
US7118114B2 (en) 2003-05-15 2006-10-10 Woodward Governor Company Dynamic sealing arrangement for movable shaft
US7426936B2 (en) 2005-11-29 2008-09-23 Woodward Governor Company Fully independent, redundant fluid energized sealing solution with secondary containment
WO2008115064A1 (fr) * 2006-10-13 2008-09-25 Framo Engineering As Dispositif de système d'étanchéité
CN102971487A (zh) * 2010-06-22 2013-03-13 韦特柯格雷斯堪的纳维亚有限公司 压差控制式马达和泵阻隔流体压力调控系统
NO337180B1 (no) * 2014-04-07 2016-02-01 Aker Subsea As Overvåking av undervannspumpe- eller kompressorakslingstetning
NO338790B1 (no) * 2014-11-24 2016-10-17 Vetco Gray Scandinavia As Fremgangsmåte og system for regulering av fluid

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US3176996A (en) * 1962-10-12 1965-04-06 Barnett Leon Truman Oil balanced shaft seal
US3987663A (en) * 1974-10-29 1976-10-26 Federal-Mogul Corporation Method and apparatus for quickly testing the sealing effectiveness of a radial-lip shaft seal
US4206928A (en) * 1977-09-10 1980-06-10 Nippon Piston Ring Co., Ltd. System for recirculating sealing liquid in a Stirling engine
US5209495A (en) * 1990-09-04 1993-05-11 Palmour Harold H Reciprocating rod pump seal assembly

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3176996A (en) * 1962-10-12 1965-04-06 Barnett Leon Truman Oil balanced shaft seal
US3987663A (en) * 1974-10-29 1976-10-26 Federal-Mogul Corporation Method and apparatus for quickly testing the sealing effectiveness of a radial-lip shaft seal
US4206928A (en) * 1977-09-10 1980-06-10 Nippon Piston Ring Co., Ltd. System for recirculating sealing liquid in a Stirling engine
US5209495A (en) * 1990-09-04 1993-05-11 Palmour Harold H Reciprocating rod pump seal assembly

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2764037A1 (fr) * 1997-06-03 1998-12-04 Samson Ag Appareil de regulation
EP1243772A3 (fr) * 2001-03-23 2003-06-04 C.R.F. Società Consortile per Azioni Système de diagnose pour des fuites des systèmes de refoulement à gaz et procédé d'inspection des soupapes de ces systèmes
US6830026B2 (en) 2001-03-23 2004-12-14 C.R.F. Società Consortile Per Azioni Diagnostics system for tracing leaks from a gas-supply system and for checking operation of the valves forming part of said system
US7118114B2 (en) 2003-05-15 2006-10-10 Woodward Governor Company Dynamic sealing arrangement for movable shaft
US8074999B2 (en) 2003-05-15 2011-12-13 Woodward, Inc. Dynamic sealing arrangement for movable shaft
US7426936B2 (en) 2005-11-29 2008-09-23 Woodward Governor Company Fully independent, redundant fluid energized sealing solution with secondary containment
CN101675251A (zh) * 2006-10-13 2010-03-17 弗拉莫工程公司 密封系统装置
WO2008115064A1 (fr) * 2006-10-13 2008-09-25 Framo Engineering As Dispositif de système d'étanchéité
RU2439377C2 (ru) * 2006-10-13 2012-01-10 Фрамо Инжиниринг Ас Устройство для уплотнительной системы
AU2007349360B2 (en) * 2006-10-13 2012-08-16 Framo Engineering As Sealing system device
CN101675251B (zh) * 2006-10-13 2013-05-01 弗拉莫工程公司 密封系统装置
US9297377B2 (en) 2006-10-13 2016-03-29 Framo Engineering As Sealing system device
CN102971487A (zh) * 2010-06-22 2013-03-13 韦特柯格雷斯堪的纳维亚有限公司 压差控制式马达和泵阻隔流体压力调控系统
NO337180B1 (no) * 2014-04-07 2016-02-01 Aker Subsea As Overvåking av undervannspumpe- eller kompressorakslingstetning
NO338790B1 (no) * 2014-11-24 2016-10-17 Vetco Gray Scandinavia As Fremgangsmåte og system for regulering av fluid

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