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
  • F16J—PISTONS; CYLINDERS; SEALINGS
  • F16J15/00—Sealings
  • F16J15/16—Sealings between relatively-moving surfaces
  • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
  • F16J15/3404—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal
  • F16J15/3408—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface
  • F16J15/3412—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface with cavities
  • F16J15/342—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface with cavities with means for feeding fluid directly to the face
• • 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
  • F16J—PISTONS; CYLINDERS; SEALINGS
  • F16J15/00—Sealings
  • F16J15/16—Sealings between relatively-moving surfaces
  • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
  • F16J15/3496—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member use of special materials
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D29/00—Details, component parts, or accessories
  • F04D29/04—Shafts or bearings, or assemblies thereof
  • F04D29/041—Axial thrust balancing
  • F04D29/0413—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D29/00—Details, component parts, or accessories
  • F04D29/04—Shafts or bearings, or assemblies thereof
  • F04D29/041—Axial thrust balancing
  • F04D29/0416—Axial thrust balancing balancing pistons
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D29/00—Details, component parts, or accessories
  • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
  • F04D29/051—Axial thrust balancing
  • F04D29/0513—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D29/00—Details, component parts, or accessories
  • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
  • F04D29/051—Axial thrust balancing
  • F04D29/0516—Axial thrust balancing balancing pistons
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D29/00—Details, component parts, or accessories
  • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
  • F04D29/056—Bearings
  • F04D29/057—Bearings hydrostatic; hydrodynamic
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D29/00—Details, component parts, or accessories
  • F04D29/08—Sealings
  • F04D29/10—Shaft sealings
  • F04D29/102—Shaft sealings especially adapted for elastic fluid pumps
  • F04D29/104—Shaft sealings especially adapted for elastic fluid pumps the sealing fluid being other than the working fluid or being the working fluid treated
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D29/00—Details, component parts, or accessories
  • F04D29/08—Sealings
  • F04D29/10—Shaft sealings
  • F04D29/12—Shaft sealings using sealing-rings
  • F04D29/122—Shaft sealings using sealing-rings especially adapted for elastic fluid pumps
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D29/00—Details, component parts, or accessories
  • F04D29/08—Sealings
  • F04D29/10—Shaft sealings
  • F04D29/12—Shaft sealings using sealing-rings
  • F04D29/122—Shaft sealings using sealing-rings especially adapted for elastic fluid pumps
  • F04D29/124—Shaft sealings using sealing-rings especially adapted for elastic fluid pumps with special means for adducting cooling or sealing fluid
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C17/00—Sliding-contact bearings for exclusively rotary movement
  • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C3/00—Shafts; Axles; Cranks; Eccentrics
  • F16C3/02—Shafts; Axles
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
  • F16C33/02—Parts of sliding-contact bearings
  • F16C33/04—Brasses; Bushes; Linings
  • F16C33/06—Sliding surface mainly made of metal
  • F16C33/12—Structural composition; Use of special materials or surface treatments, e.g. for rust-proofing
  • F16C33/128—Porous bearings, e.g. bushes of sintered alloy
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
  • F16C33/72—Sealings
  • F16C33/74—Sealings of sliding-contact bearings
• • 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
  • F16J—PISTONS; CYLINDERS; SEALINGS
  • F16J15/00—Sealings
  • F16J15/16—Sealings between relatively-moving surfaces
  • F16J15/162—Special parts or details relating to lubrication or cooling of the sealing itself
• • 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
  • F16J—PISTONS; CYLINDERS; SEALINGS
  • F16J15/00—Sealings
  • F16J15/16—Sealings between relatively-moving surfaces
  • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
  • F16J15/3404—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal
• • 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
  • F16J—PISTONS; CYLINDERS; SEALINGS
  • F16J15/00—Sealings
  • F16J15/16—Sealings between relatively-moving surfaces
  • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
  • F16J15/3492—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member with monitoring or measuring means associated with the seal
• • 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
  • F16J—PISTONS; CYLINDERS; SEALINGS
  • F16J15/00—Sealings
  • F16J15/16—Sealings between relatively-moving surfaces
  • F16J15/40—Sealings between relatively-moving surfaces by means of fluid
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
  • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
  • F05D2300/00—Materials; Properties thereof
  • F05D2300/50—Intrinsic material properties or characteristics
  • F05D2300/514—Porosity
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C2360/00—Engines or pumps
• • 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
  • F16J—PISTONS; CYLINDERS; SEALINGS
  • F16J15/00—Sealings
  • F16J15/16—Sealings between relatively-moving surfaces
  • F16J15/40—Sealings between relatively-moving surfaces by means of fluid
  • F16J15/406—Sealings between relatively-moving surfaces by means of fluid by at least one pump

Definitions

• This subject application provides externally-pressurized porous media technology to create a porous media ventless seal for turbomachinery applications.
• a centrifugal compressor such as but not limited to centrifugal compressors (hereinafter a centrifugal compressor is used as a primary example), require shaft sealing in order to prevent leakage of process gas into the atmosphere, or migration of process gas across the seals or into the bearing side of the equipment.
• shaft sealing mechanisms exist, including but not limited to, labyrinth seals (a radial seal), oil film seal rings (a radial seal), mechanical contact seals (a face seal), and the most elaborate type of shaft seal - the dry gas seal (a face seal). Dry gas seals provide the best barrier to leakage of all seal types, and are therefore considered the incumbent prior art technology for comparison to the subject invention. Dry gas seals utilize rotating rings that contain micron-sized grooves that allow for face "lift-off during operation, and thus allow for a minimal controlled amount of seal leakage.
• tandem dry gas seal arrangement include a primary seal is comprised of a primary (stationary) ring and a mating (rotating) ring, which withstands total pressure, and the secondary seal is comprised of a stationary ring and mating (rotating) ring, which acts as a backup.
• Primary rings are typically made from carbon, and mating rings are typically made using tungsten carbide, silicon carbide or silicon nitride.
• Dry sealing gas (which is typically the same as the process gas, but treated) is injected, and is typically at least 50 psi above the process side pressure. Most of the injected dry sealing gas flows across an inner labyrinth seal and into the compressor (into the process gas).
• a single seal arrangement there is only a primary face and a mating face, with no secondary seal. Otherwise the functionality of a single seal is similar to that of a tandem seal, except for the fact that leakage across the primary seal gets vented, and there is no back-up seal.
• a "double opposed" dry gas seal arrangement is comprised of a primary inboard stationary ring and a primary inboard mating (rotating) ring. Also, there is a secondary outboard stationary ring and a secondary outboard mating (rotating) ring.
• an inert gas such as nitrogen
• the seal gas supply flowing past the primary (inboard) seal migrates into the process side flow, and the seal gas supply flowing past the secondary (outboard) seal goes to a vent.
• tandem seals are the most widely-accepted arrangement for industry when considering the best sealing possibility.
• Double-opposed dry gas seals have not been widely accepted in the industry (tandem seals are more widely accepted).
• Flow across the seal faces for dry gas seals can contain sealing gas and process gas. This is a bad fundamental design to allow these gases across the seal gap.
• Dry gas seals have a large flow of seal gas past the inner labyrinth seal, into the process side of compressors.
• Dry gas seals have very high flow rates.
• Seal faces can "ring” together during shut-down, resulting in very high start-up torques, or no-start conditions.
• Seal faces can distort as a result of high pressures or local heating.
• an embodiment presented utilizes a porous material which is externally pressurized with gas to effect the key sealing function, which occurs as a face seal arrangement.
• the embodiment removes or minimizes the aforementioned disadvantages for tandem and double-opposed seals as mentioned in the previous section.
• the subject embodiment allows for the integration of porous media sealing into existing single, tandem, or double-opposed arrangements. In each of these arrangements, there are numerous advantages over the prior art, and these are explained herein. Furthermore, a so-called Ventless Seal arrangement allows for zero emissions of process fluid, and also allows use of clean process gas as the buffer gas to the Ventless Seal. [0029] In all proposed arrangements, low flow rates of external gas are required, thus allowing for large savings in injected gas cost. Also, a drastic reduction in seal panel complexity results from the use of externally-pressurized porous media as seals.
• FIG. 1A shows a depiction of a cross section of a typical dry gas tandem seal
• FIG. IB shows a depiction of a cross section of a dry gas tandem seal with porous media incorporated.
• FIG. 2A shows a depiction of a cross section of a typical dry gas double-opposed seal.
• FIG. 2B shows a depiction of a cross section of a dry gas double- opposed seal with porous media incorporated.
• FIG. 3 shows a depiction comparing flow area of aerodynamic and aerostatic seal faces.
• FIG. 4 is an example of a 2-port ventless seal arrangement.
• FIG. 5 is an example of a 3-port ventless seal arrangement.
• FIG. 6 is an example of a multiphase ventless seal.
• FIG. 7 is an example of a 2-port ventless seal with two porous media members.
• FIG. 8 is a depiction of a ventless seal showing details of conductive passages for adjustability options.
• FIG. 9A shows a depiction of the gap pressure profile for a ventless seal having low input pressure at the outside diameter of the porous media ring, and high input pressure at the inside diameter of the porous media ring.
• FIG. 9B shows a depiction of the gap pressure profile for a ventless seal having high input pressure at the outside diameter of the porous media ring, and low input pressure at the inside diameter of the porous media ring
• porous media seals for the following configurations: a porous media single seal, a porous media tandem seal, and a porous media double-opposed seal, resulting in numerous benefits from the incorporation, thereof.
• turbomachinery such as, but not limited to, centrifugal compressors.
• a typical tandem dry gas seal arrangement has a primary seal, comprised of a primary (stationary) ring 101A and a mating (rotating) ring 102A, which withstands total pressure, and the secondary seal, comprised of a stationary ring 101B and mating (rotating) ring 102B, acts as a backup.
• Primary rings are typically made from carbon, and mating rings are typically made using tungsten carbide, silicon carbide, or silicon nitride.
• a shaft sleeve 104 is coupled to a rotating shaft 105, and the compressor head is shown as 106.
• Springs 103A and 103B create force to maintain a bias of the stationary rings onto the face of the mating rings 102A and 102B.
• Dry sealing gas (which is typically the same as the process gas, but treated) is injected at seal gas supply location 108, and is typically at least 50 psi above the process side pressure.
• the dry sealing gas must be a very "clean" gas, having solid particles at least 10 microns or less in size (preferably only 3-4 microns in size).
• Most of the injected dry sealing gas flows across an inner labyrinth seal 113 and into the compressor (into the process gas). A small amount of the dry sealing gas flows across the primary seal and then out of the primary vent 109.
• an inert seal gas is injected at inert seal gas supply location 110 with a dual purpose: it keeps leakage from the primary seal from escaping out of the secondary vent 111 by flowing inert gas across an intermediate labyrinth seal 114, and it also flows past the secondary seal, and out of the secondary vent 111.
• the remainder of the gas passing out of the secondary vent 111 is separation gas supply 112 which passes over a barrier seal 107, which is designed to keep oil lubrication (from the bearing side) from migrating to the secondary or primary gas seals.
• flow through the primary vent 109 is a combination of injected (treated) dry sealing gas and inert gas
• flow through the secondary vent 111 is a combination of inert gas and separation gas.
• a typical single seal arrangement is comprised of only a primary face and a mating face, with no secondary seal. Otherwise the functionality of a single seal is similar to that of a tandem seal, except for the fact that leakage across the primary seal gets vented, and there is no back-up seal.
• FIG. 2A shows a typical "double opposed" dry gas seal arrangement.
• a primary inboard stationary ring 20 IB and a primary inboard mating (rotating) ring 202B.
• a secondary outboard stationary ring 201 A and a secondary outboard mating (rotating) ring 202A are coupled to a rotating shaft 205, and the compressor head is shown as 206.
• Springs 203A and 203B create force to maintain a bias of the stationary rings onto the face of the mating rings.
• an inert gas (such as nitrogen) is injected at seal gas supply location 208, and flows past both seal faces.
• the seal gas supply flowing past the primary (inboard) seal migrates into the process side flow, and the seal gas supply flowing past the secondary (outboard) seal goes to the vent 210.
• the treated flushing gas introduced at port location 209 between the inner labyrinth seal 212 and the inboard seal is typically maintained at a pressure higher than that of the process side, in order to prevent untreated process gas from contaminating the face of the primary seal.
• the inert gas flow across the primary seal flows across the inner labyrinth seal 212, and into the process side, and is not vented.
• Separation gas, used to prevent leakage across barrier seal 207 is introduced at port location 211.
• the inert gas flow across the secondary seal is mixed with separation gas and is vented through the vent 210.
• FIGS 1A and 2A Existing technology, as represented by FIGS 1A and 2A, are comprehensively described in the John Stahley's "Dry Gas Seals Handbook", ⁇ 2005.
• FIGS. IB and 2B show the incorporation of a porous media, which acts as a seal, into the primary rings in both figures.
• FIG. IB a porous media ring 115 is included in the primary stationary ring 101A, and a porous ring 116 is included in the secondary stationary ring 101B.
• a porous media ring 212 and 213 are included in the primary rings.
• Employing a porous media gas seal as shown in FIGS. IB and 2B will result in the porous media functioning as discussed in US 8,753,014 by Devitt.
• a shaft sleeve 104 is coupled to a rotating shaft 105, and the compressor head is shown as 106.
• Springs 103A and 103B create force to maintain a bias of the stationary rings onto the face of the mating rings 102A and 102B.
• Seal gas pressure from location 108 can be supplied to the plenums 117 under the porous ring 115 at a pressure of 50-300 psig greater than the process gas side pressure.
• This seal gas flows through the porous ring 115 at a low flow rate of 1-10 scfm.
• This flow through the porous ring 115 will allow the seal gas to flow through the inner labyrinth 113 and into the process gas side. Also, some leakage may exit the porous ring 115 and flow to the primary vent 109.
• inert gas will be injected at location 110, and can be directed into plenums 118, migrating through the porous ring 116.
• Inert gas leakage across porous ring 116 will migrate across the intermediate labyrinth 114 to prevent primary seal leakage from reaching the secondary vent 111, and inert gas leakage across the porous ring 116 will also migrate to the secondary vent 111.
• the remainder of the gas passing out of the secondary vent 111 is separation gas supply 112 which passes over a barrier seal 107, which is designed to keep oil lubrication (from the bearing side) from migrating to the secondary or primary gas seals.
• flow through the primary vent 109 is a combination of injected (treated) dry sealing gas and inert gas
• flow through the secondary vent 111 is a combination of inert gas and separation gas.
• the treated sealing gas which is injected into the primary seal may be replaced with an inert gas (such as Nitrogen), if permitted by the turbomachinery provider. Although this would leak inert gas into the process side, this would prevent any leakage of treated seal gas out of the primary vent.
• an inert gas such as Nitrogen
• inert gas such as Nitrogen
• Nitrogen is injected at location 208. It is directed into plenums 215 and 216, and allows leakage through the porous rings 213 and 214. This leakage through porous ring 213 migrates into the process gas side, and leakage through porous ring 214 migrates through the vent 210. Otherwise, functionality of this arrangement is similar to that of FIG. IB.
• FIGS. IB and 2B arrangements may include:
• External pressurization may allow frozen seal faces to pop open before rotation.
• porous media faces are thin enough to conform to the surface of the mating ring.
• Managing the quality of the injected gas stream through a ventless seal may be significantly easier than that of a dry gas seal.
• the reason for this is due to the fact that the flow rate through porous media, and specifically through the ventless seal, will be at least an order of magnitude less than that of prior art. With such low flow leakage across the process seal, much less filtering of the injected gas stream will be required, greatly simplifying the overall system.
• External pressure may allow for increased gap sizes.
• FIG. 3 highlights the advantage of how a porous media face allows for a much larger flow area than that of an aerodynamic seal, such as a dry gas seal.
• an aerodynamic seal such as a dry gas seal.
• flow enters the gap 303 established between the primary face 302 and mating face 301.
• the flow area is defined by the following equation: n*(DouTSiDE DIAMETER)* GAP.
• the flow area 304 for a porous media aerostatic seal encompasses the entire distance 305 across the face of the aerostatic seal, and is defined by n*(D 2 ouTSiDE DIAMETER - D3 ⁇ 4NSIDE DIAMETER).
• the flow area for an aerostatic seal is thousands of time greater than the flow area for an aerodynamic seal.
• Ventless Seal uses porous media and may provide for all of the benefits discussed heretofore for the FIGS. IB and 2B arrangements, and may provide even further advantages.
• FIG. 4 shows a rotating shaft 401, compressor head 402, and a stationary member 403 containing grooves 407 and 409, which continue through the stationary member 403 and also into holder 408.
• Treated process gas is introduced into port 405, and inert gas (such as Nitrogen) is introduced into port 406.
• inert gas such as Nitrogen
• Both gases are to be at a pressure which is higher than gas on the compressor side of the seal.
• the seal is a porous media ring 404, and functions similarly to that taught by Devitt in US 8,753,014.
• the injected gases will flow through grooves 407 and 409 and then through the porous media ring 404 and create a very small (lto 10 micron) gap. Since the two gases shown will be at the same pressure, as shown in FIG.
• the injected (treated) process gas will flow through the porous media and into the process side of the compressor.
• the inert gas will flow through the porous media and then will flow in the direction opposite that of the treated seal gas flow, and can be vented.
• Both gases will be injected across the porous media at 50 to 300 psi higher than the pressure in the process side of the compressor, but the flow rate will be very low (such as on the order of 1 to 10 scfm). Since there will be such a high pressure differential, yet such a low flow rate, this will provide a significant benefit as compared to managing conventional dry sealing (buffer) gas.
• the pressure of the treated process gas through groove 407 could be at 2,200 psig, and the pressure of the inert gas through groove 409 could also be adjusted to a pressure to balance the pressure in the gap so that there is no flow from the process side into the porous media gap. This would result in all of the treated process gas flowing into the system process gas, and would prevent system process gas from entering the porous media seal area.
• the adjustable pressure of the inert gas would flow in the opposite direction, and could be vented. Neither gas would overcome the other gas within the porous media, and therefore treated process gas would not flow in the direction of the vent.
• Total seal leakage for a typical seal running at over 10,000 rpm at 1,000+ psig may be in the range of 150-200 scfm.
• the ventless seal may consume on the order of 20 scfm per compressor. The key advantage of this arrangement is that zero (treated) process gas will need to be vented. Also, there will be no possible way for any of the actual process gas from the compressor ever migrating past the seal, as well.
• FIG. 8 shows additional details, as used in a working prototype of a ventless seal.
• Shaft 801 is coupled to a runner 810 which provides an opposing face to porous media 809, which is held by holder 808.
• the conductive passages to the porous media are shown as 802 and 803.
• Passage 802 allows treated gas to flow through porous media gap and into the process gas.
• Passage 803 is for the injected inert gas which will provide balance in the porous media gap so that no flow of process gas occurs across the porous media gap.
• FIG. 5 shows an alternate arrangement of the Ventless seal, in which more than two ports are used.
• holder 503 is attached to compressor head 502, and holder 503 contains grooves 504, 505 and 506, with groove 506 being an additional groove, as compared to the arrangement in FIG. 4.
• a porous media ring 507 may be contained in holder 503, and a runner 508 may be attached to a rotatable shaft 501 via O-ring 509.
• treated process gas can be injected into a port which flows into groove 504, and an inert gas can be injected into another port which flows into groove 505.
• Each of these two gases can have the same pressure, so that, as in FIG. 4, the treated process gas will flow through the porous media and into the process side of the compressor.
• the inert gas will flow through the porous media and then in the opposite direction, and can be vented. Both gases will be injected across the porous media at 50 to 300 psi higher than the pressure in the process side of the compressor, but the flow rate will be very low (such as on the order of 1 to 10 scfm).
• the third groove 506 can be used to allow the introduction of inert gas at a different pressure.
• the pressure of the treated process gas through groove 504 could be at 2,200 psig, and the pressure of the inert gas through groove 505 could also be adjusted to a pressure to balance the pressure in the gap so that there is no flow across the porous media gap. This would result in treated process gas flowing into the system process gas, and would prevent system process gas from entering the porous media seal area.
• the adjustable pressure of the inert gas would flow in the opposite direction, and could be vented. Neither gas would overcome the other gas within the porous media, and therefore treated process gas would not flow in the direction of the vent.
• this third groove 506 could allow for the introduction of a different pressure.
• inert gas could be introduced into the third groove at an intermediate pressure, and could be used for additional balancing at the seal face.
• a fluid in another state (such as water) could be used, constituting a multiphase ventless seal.
• holder 602 is attached to compressor head 607, and holder 602 contains grooves 604 and 605.
• a porous media ring 603 may be contained in holder 602, and a runner 606 may be attached to a rotatable shaft 601 via O-ring 608.
• treated process gas can be injected into a port which flows into groove 604, and a fluid can be injected into another port which flows into groove 605. Both the gas and the fluid can have the same pressure, so that, as in FIGS.
• the treated process gas will flow through the porous media and into the process side of the compressor.
• the injected fluid will flow through the porous media and then in the opposite direction, and can be vented.
• Both the treated process gas and the fluid will be injected across the porous media at 50 to 300 psi higher than the pressure in the process side of the compressor, but the flow rate will be very low (such as on the order of 1 to 10 scfm).
• gases and fluids can both be introduced into the porous media, and can exist in the "gap" formed on the surface of the porous media.
• FIG. 5 a the possibility exists for a multiphase ventless seal to have more than two grooves.
• porous media face is shown as two separate members
• FIG. 7 This allows the individual members to be sealed at the interface line shown, in order to provide a barrier to prevent any mixing of gases or fluids (within the porous media), which enter through the ports shown.
• Other items in FIG. 7 include porous media holder 702, which is attached to compressor head 707, and holder 702 may contain grooves 704 and 705.
• a runner 706 may be attached to a rotatable shaft 701 via O-ring 708.
• FIGS. 9A and 9B are presented. It is assumed that in both cases (FIGS.
• FIGS. 9A and 9B show the effect of introducing a high pressure into one port, and a low pressure into another port.
• the resulting pressure profiles at the porous media faces 901 and 902 are proportional to the magnitude of pressures introduced in each port.
• ventless seal Another potential use for the ventless seal is to incorporate this arrangement in place of a typical inner labyrinth seal, as shown by items 113 in FIG. 1A and 212 in FIG. 2A, or in place of a typical barrier seal, as shown by items 107 and 207 in FIGS, 1A, IB, 2A, and 2B.
• porous media discussed herein may be comprised of any porous or sintered material such as graphite, carbon, silicon carbide, porous diamond, Tungsten carbide, alumina, carbon-carbon, a porous carbon base material with a diamond or diamond-like coating, etc.
• the manufacture of porous media may employ ceramic casting techniques commonly known in the art, but may also employ other methods such as 3-D printing.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Physics & Mathematics (AREA)
• Fluid Mechanics (AREA)
• Metallurgy (AREA)
• Ocean & Marine Engineering (AREA)
• Structures Of Non-Positive Displacement Pumps (AREA)
• Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
• Mechanical Sealing (AREA)
• Magnetic Bearings And Hydrostatic Bearings (AREA)
• Sliding-Contact Bearings (AREA)
• Sealing Devices (AREA)

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• 2015
  • 2015-09-29 CA CA2962897A patent/CA2962897C/en active Active
  • 2015-09-29 JP JP2017516903A patent/JP6853168B2/ja active Active
  • 2015-09-29 US US14/869,456 patent/US10030666B2/en active Active
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• 2018
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