US3537650A - Two-stage sonic atomizing device - Google Patents
Two-stage sonic atomizing device Download PDFInfo
- Publication number
- US3537650A US3537650A US825091*A US3537650DA US3537650A US 3537650 A US3537650 A US 3537650A US 3537650D A US3537650D A US 3537650DA US 3537650 A US3537650 A US 3537650A
- Authority
- US
- United States
- Prior art keywords
- vortex
- chamber
- steam
- outlet bore
- energy
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
- F23D11/34—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space by ultrasonic means or other kinds of vibrations
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
- B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
- B05B7/00—Spraying apparatus for discharge of liquids or other fluent materials from two or more sources, e.g. of liquid and air, of powder and gas
- B05B7/02—Spray pistols; Apparatus for discharge
- B05B7/08—Spray pistols; Apparatus for discharge with separate outlet orifices, e.g. to form parallel jets, i.e. the axis of the jets being parallel, to form intersecting jets, i.e. the axis of the jets converging but not necessarily intersecting at a point
- B05B7/0807—Spray pistols; Apparatus for discharge with separate outlet orifices, e.g. to form parallel jets, i.e. the axis of the jets being parallel, to form intersecting jets, i.e. the axis of the jets converging but not necessarily intersecting at a point to form intersecting jets
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
- B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
- B05B7/00—Spraying apparatus for discharge of liquids or other fluent materials from two or more sources, e.g. of liquid and air, of powder and gas
- B05B7/02—Spray pistols; Apparatus for discharge
- B05B7/08—Spray pistols; Apparatus for discharge with separate outlet orifices, e.g. to form parallel jets, i.e. the axis of the jets being parallel, to form intersecting jets, i.e. the axis of the jets converging but not necessarily intersecting at a point
- B05B7/0892—Spray pistols; Apparatus for discharge with separate outlet orifices, e.g. to form parallel jets, i.e. the axis of the jets being parallel, to form intersecting jets, i.e. the axis of the jets converging but not necessarily intersecting at a point the outlet orifices for jets constituted by a liquid or a mixture containing a liquid being disposed on a circle
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
- B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
- B05B7/00—Spraying apparatus for discharge of liquids or other fluent materials from two or more sources, e.g. of liquid and air, of powder and gas
- B05B7/02—Spray pistols; Apparatus for discharge
- B05B7/10—Spray pistols; Apparatus for discharge producing a swirling discharge
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
- F23D11/10—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
- F23D11/10—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour
- F23D11/106—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour medium and fuel meeting at the burner outlet
- F23D11/107—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour medium and fuel meeting at the burner outlet at least one of both being subjected to a swirling motion
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
- F23D11/24—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space by pressurisation of the fuel before a nozzle through which it is sprayed by a substantial pressure reduction into a space
Definitions
- a liquid atomizer having a cylindrical vortex chamber with at least one tangential inlet, and a concentric outlet tube. A substantially sharp corner marks the transition from the chamber to the outlet tube and the chamber wall through which the outlet tube opens is substantially normal to the latter.
- a liquid feed tube is provided axially within the outlet tube and has a port for expelling a jet of liquid centrifugally toward the outlet tube Walls.
- This invention relates to devices for atomizing liquids, and has to do particularly with the application of the rotary vortex to the problem of liquid atomization.
- a particular application of the device to which this invention is directed relates to the atomization of fuel oils.
- One way of promoting a high recirculation rate of the combustion gases is to provide a fuel atomizer which has a wide spray angle.
- a further object of this invention is to provide an atomizing device utilizing the principle of gas-vortex atomization, which is capable of utilizing a high-pressure vortex medium, and can efiiciently atomize certain thick, viscous liquid, such as the heavier fuel oils and pitch fuels.
- the apparatus of this invention achieves the above objects by utilizing a particular rotary-vortex chamber design to produce a high-speed rotary vortex of an atomizing medium such as steam or air, in combination with a two-stage atomizing technique carried out at the downstream end of an outlet tube in which the atomizing medium is rotating.
- the special design of the vortex chamber and outlet tube produces a desired ratio of axial to tangential velocity within the outlet tube and results in a wide-angle spray cone, while the two-stage atomizing technique ensures that a high degree of comminution and nebularization of the heavy viscous oil will occur.
- a liquid atomizer comprising: means defining a substantially cylindrical chamber having a forward end wall and a rearward end wall, a cylindrical outlet nozzle defining at least part of said forward end wall and having an outlet bore of diameter less than that of said chamber and extending co-axially away from the chamber, the forward end wall and the outlet bore meeting to define a substantially sharp corner around which gas must pass when moving from said chamber into said outlet bore, at least one substantially tangential inlet to said chamber, means for causing a gas to pass under pressure through said inlet and into said chamber so as to set-up a rotating vortex in said chamber, the said pressure being sufiicient to cause the rotational speed of the gas in the chamber at a radius equal to that of the outlet bore to be greater than sonic, whereby the gas exits from the chamber through the outlet bore while rotating at a speed greater than sonic and establishes a rotating vortex along the outlet bore the speed of which decreases, due to friction, to substantially sonic velocity near the downstream end of the
- FIG. 1 is an axial sectional view through the nozzle of an oil burner equipped with a vortex-type atomizer
- FIG. 2 is a transverse sectional view taken at the line 2-2 in FIG. 1;
- FIGS. 3, 4 and 5 are diagrammatic axial views of three vortex chamber designs, utilized in a discussion of comparative energy requirements
- FIGS. 6, 7 and 8 are axial sectional views of the vortex chamber designs shown in FIGS. 3, 4 and 5, respectively;
- FIG. 9 is a graph showing energy conversion, for the three vortex chamber designs shown in FIGS. 3 to 8, as the atomizing medium passes from the tangential inlet through the device to the downstream end of the outlet tube.
- FIG. 1 shows an oil burner nozzle 10, which includes a cylindrical atomizer mounting sleeve 12 into the open end of which is threaded a conical vertex body 14.
- apex of the conical vortex body 14 has an axial bore 15 which is widened at 16 to define an annular shoulder 17.
- a gas nozzle 18 is shaped to fit snugly within the bore 15 and the widened portion 16 in the conical vortex body, and is held in position by a vortex chamber housing 20 which is threaded into the conical vortex body 14.
- a feed tube 22 extends in sealed relationship through an axial aperture 23 in the vortex chamber housing 20, and passes centrally through the vortex chamber 21 to enter concentrically a co-axial outlet bore 24 in the gas nozzle 18.
- the diameter of the outlet bore 24 is greater than the outside diameter of the feed tube 22, such that an annular space 26 is defined therebet-ween.
- the feed tube 22 is connected, by welding or press-fitting, to a tubular connecting element 28 which is in turn connected to a fuel line (not shown) which delivers fuel under pressure to the connecting element 28 and thence to the feed tube 22.
- the connecting element 28 is secured centrally through a partition 30 which is threaded into the upstream end of the conical vortex body 14.
- a pressurized gaseous medium is delivered to the nozzle through a line (not shown) located inside the atomizer mounting sleeve 12 and fastened in eccentric port 31.
- the medium is considered to be steam, although other gases can be used, as is later discussed.
- the steam passes into an antechamber 32 defined by the partition 30, the conical vortex body 14 and the vortex chamber housing 20. From the antechamber 32 the pressurized steam enters the vortex chamber 21 through a tangential inlet 34 constituted by a bore hole drilled through the wall of the vortex chamber housing 20, as shown in FIGS. 1 and 2.
- the steam rotates within the vortex chamber 21 in a counter-clockwise sense as seen in FIG. 2.
- the steam exits from the vortex chamber 21 by way of the annular space 26 defined between the outlet bore 24 and the feed tube 22.
- the steam in progressing from the periphery of the vortex chamber 21 toward its centre, undergoes an increase in rotational speed, the increase varying inversely with the square root of the radius.
- the steam passes into the outlet bore 24 and continues to spin at this higher rotational speed as it passes along the outlet bore 24 slowing slightly due to friction, and it finally spins out into the open at the right-hand end of the outlet bore 24.
- This invention provides a two-stage atomization of the liquid to be atomized.
- the first stage involves forcing the fuel under pressure through one or more restricted ports 36 drilled in the periphery of the feed tube 22.
- the downstream end of the feed tube 22 is closed as shown, and the ports 36 are drilled in the feed tube 22 closely adjacent the closed downstream end.
- the ports 36 function as nozzles which expel thin jets of the liquid centrifugally outwardly into the periphery of the vortex created by the spinning steam. Because of the high rotational speed of the vortex, most of the steam is thrown outwardly and forms a rotating film or layer adjacent the walls of the axial bore 24. As the thin jets of the liquid impinge upon the rotating steam layer, they are further broken up, and more finely atomized.
- the size, number, orientation and axial position of the ports should be properly selected.
- the size of the ports should be such that there is no danger of the liquid clogging or blocking the ports.
- the number of ports should be such that the required liquid flow is achieved at the desired pressure.
- the orientation of the ports although here considered to be radial, can also be partially or fully tangential to the feed tube 22 and/or tilted in the axial direction at an angle between 0 and where conditions warrant it. Even angles exceeding 90 (i.e. the liquid jet is directed, partially, against the flow of the vortex medium) may be of advantage under certain circumstances.
- the word centrifugally as applied to the ports 36 and to the direction of the liquid sprayed from the feed tube 22, is meant to include all tangential angles and all axial inclinations.
- the location of the ports is dependent upon several considerations. Firstly, the ports should be inside of the outlet bore 24 to ensure that the liquid particles spend a long enough time in the region of violent disturbance to become properly atomized. However, since the liquid particles are swirled around in an ever increasing spiral path due to both the radial component of liquid velocity and the centrifugal force, the ports 36 must be close enough to the downstream open end of the annular space 26 to ensure that most of the particles leave the nozzle before they contact the walls of the outlet bore 24. The presence of the rotating layer of steam adjacent the wall of the outlet bore 24 helps to ensure that contact between the liquid particles and the wall will be minimal.
- the ports 36 are all at the same axial location, it is conceivable that two or more sets of ports could be provided at different axial locations, or that the individual ports could be arranged along the feed tube 22 in a random distribution, both axially and radially.
- the atomizing medium should be moving at sonic velocity at the point of atomization.
- Supersonic velocities as a rule, generally involve heavy energy losses, while subsonic velocities require an unduly high consumption for a given energy requirement.
- the layer of the atomizing medium in the discharge of the outlet bore must be sufficiently thick to prevent the penetration of the fuel, since penetration leads to agglomeration on the inside wall, and thus to the formation of large particles. It will be obvious, then, that with a 1:1 velocity ratio, there will be a mathematical inter-relationship between the diameter of the discharge nozzle, the flow rate of the atomizing medium, and its axial velocity component.
- the energy requirement, in B.t.u.s per pound of atomizing medium, can be minimized by selecting a D/d ratio within a given range, where D is the diameter of the vortex chamber, and d is the diameter of the outlet bore 24.
- FIGS. 4 and 7 show the comparative diameters in an actual experimental prototype which was built and tested under working conditions.
- the D/ d ratio was 3.312, and the actual dimensions of the prototype were as follows:
- the vortex chamber had six tangential inlets, each one being 0.125 inch in diameter.
- Air was delivered to the tangential inlets at 48 p.s.i.g. pressure and at negligible velocity, and the transforma tions of the total available pressure energy as the air travelled through the prototype was determined primarily on the basis of pitot tube measurements, and plotted as the solid line in FIG. 9. Attention is now directed to FIG. 9.
- the total energy available in the pressurized medium prior to entering the tangential inlets is indicated by the upper circled dot with the number 1.
- the energy available in the pressurized medium is 42 /2 B.t.u.s per pound.
- the medium is considered to be motionless, and so the kinetic energy is zero, as shown by the circled dot at the bottom bearing the number 1.
- the rotating air next moves spirally inwardly toward the centre of the vortex chamber, and its kinetic energy increases in inverse ratio to the diameter.
- the axial component is zero
- the radial component is negligible
- the tangential component increase from 666 feet per second on the periphery to 1215 feet per second on the one inch diameter line.
- This stage is shown in the FIGS. 4 and 7 and in the graph of FIG. 9 as a progression from point 3 to point 4. Irreversible frictional losses result in a slight reduction in the total available energy to about 31.3 B.t.u.s per pound, while nearly all of the available pressure energy is converted to kinetic energy through the increase of speed, as will be seen by the closeness of the two points marked 4 in FIG. 9.
- the next stage is the entry of the rotating air into the outlet bore 24, and at this stage a part of its tangential velocity is converted to axial velocity.
- the energy loss is appreciable, as can be seen by the steep drop of the two lines 4-5 in FIG. 9.
- the ratio of tangential velocity to axial velocity becomes constant.
- the air velocity was found to be sonic at 1,046 feet per second, with a tangential component of 768 and an axial component of 538 feet per second. Virtually all of the air is discharged on the periphery, in a layer of 0.10 inch thickness. In the central core, the density is small and the axial velocity is negligible.
- the cylindrical outlet bore is considered an essential part of this invention, because it is necessary for the stabilization of the flow. Without the discharge nozzle, the conditions in the region of atomization would be so unstable that uniform atomization would not be possible.
- the forward wall of the vortex chamber is a cone with an enclosed angle of considerably less than 180, for example from 30 to then the dominant velocity component in the vortex chamber will be an axial one, and this will be the case even more so in the outlet bore, resulting in a very narrow angle spray which would not produce a recirculating type of pattern in the combustion chamber.
- the flow rate of the atomizing medium would have to be significantly higher to provide an acceptable layer thickness around the inside wall of the outlet tube at its discharge end.
- this invention relates essentially to an atomizer utilizing a high-pressure medium, it is particularly adapted for use with high-pressure steam.
- compressed air or steam is used for the atomization of heavy oil fuels.
- steam is the most common for economic reasons.
- the largest portion of the required energy (heat) is used for the evaporation of the water, and the pressure of the steam requires only a small portion of energy by comparison. For example, to generate 1 pound of steam (100% quality) at 5 p.s.i.g. requires 976 B.t.u.s, While the generation of 1 pound of steam at 75 p.s.i.g. requires 1,005 B.t.u.s.
- atomization energy of 100 B.t.u.s can be derived from either (a) 17.5 pounds of 5 p.s.i.g. steam, generated at the cost of 17,100 B.t.u.s of heat, or
- a liquid atomizer comprising:
- a cylindrical outlet nozzle defining at least part of said forward end wall and having an outlet bore of diameter less than that of said chamber and extending co-axially away from the chamber, the forward end wall and the outlet bore meeting to define a substantially sharp corner around which gas must pass when moving from said chamber into said outlet bore,
- liquid feed means located substantially axially within said outlet bore for expelling at least one jet of liquid centrifugally into the vortex where the latter has substantially sonic velocity.
- liquid feed means comprises a feed tube which extends from a liquid source co-axially through said cylindrical chamber and into said outlet bore to a point adjacent the downstream end of the outlet bore, the downstream end of the feed tube having at least one jet port for expelling said jet of liquid centrifugally into the vortex.
- a liquid atomizer as claimed in claim 4 in which a ratio D/ d lies between 3 and 4, where D is the internal diameter of the cylindrical chamber,
Description
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US82509169A | 1969-04-14 | 1969-04-14 |
Publications (1)
Publication Number | Publication Date |
---|---|
US3537650A true US3537650A (en) | 1970-11-03 |
Family
ID=25243087
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US825091*A Expired - Lifetime US3537650A (en) | 1969-04-14 | 1969-04-14 | Two-stage sonic atomizing device |
Country Status (3)
Country | Link |
---|---|
US (1) | US3537650A (en) |
DE (1) | DE7013257U (en) |
GB (1) | GB1248711A (en) |
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3958759A (en) * | 1974-01-04 | 1976-05-25 | Seamus Gearoid Timoney | Directed atomized fuel jet apparatus |
FR2308865A1 (en) * | 1975-04-22 | 1976-11-19 | Coulon Christian | METHOD AND DEVICE FOR SPRAYING AND BURNING LIQUID FUELS |
US4415123A (en) * | 1980-08-22 | 1983-11-15 | H. Ikeuchi & Co., Ltd. | Atomizer nozzle assembly |
US5687905A (en) * | 1995-09-05 | 1997-11-18 | Tsai; Shirley Cheng | Ultrasound-modulated two-fluid atomization |
EP1081487A2 (en) | 1999-09-06 | 2001-03-07 | Hitachi, Ltd. | Nebulizer |
US20080296787A1 (en) * | 2007-06-01 | 2008-12-04 | Wet Enterprises, Inc. | Gas Splattered Fluid Display |
US20100331428A1 (en) * | 2007-11-07 | 2010-12-30 | Aridis Pharmaceuticals | Sonic Low Pressure Spray Drying |
CH702598A1 (en) * | 2010-01-29 | 2011-07-29 | Alstom Technology Ltd | Injection nozzle and method for operating such an injection nozzle. |
US20120145050A1 (en) * | 2010-12-08 | 2012-06-14 | Vladimir Vladimirovich Fisenko | Apparatus for combustion products utilization and heat generation |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1476774A (en) * | 1921-09-16 | 1923-12-11 | Parkscramer Company | Vaporizer |
GB879224A (en) * | 1956-10-17 | 1961-10-11 | Marc Marie Paul Rene De La Fou | Improvements in or relating to mixing and atomizing device |
US3254846A (en) * | 1965-01-21 | 1966-06-07 | Hauck Mfg Co | Oil atomizing burner using low pressure air |
-
1969
- 1969-04-14 US US825091*A patent/US3537650A/en not_active Expired - Lifetime
-
1970
- 1970-04-10 DE DE7013257U patent/DE7013257U/en not_active Expired
- 1970-04-14 GB GB07830/70A patent/GB1248711A/en not_active Expired
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1476774A (en) * | 1921-09-16 | 1923-12-11 | Parkscramer Company | Vaporizer |
GB879224A (en) * | 1956-10-17 | 1961-10-11 | Marc Marie Paul Rene De La Fou | Improvements in or relating to mixing and atomizing device |
US3254846A (en) * | 1965-01-21 | 1966-06-07 | Hauck Mfg Co | Oil atomizing burner using low pressure air |
Cited By (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3958759A (en) * | 1974-01-04 | 1976-05-25 | Seamus Gearoid Timoney | Directed atomized fuel jet apparatus |
FR2308865A1 (en) * | 1975-04-22 | 1976-11-19 | Coulon Christian | METHOD AND DEVICE FOR SPRAYING AND BURNING LIQUID FUELS |
US4415123A (en) * | 1980-08-22 | 1983-11-15 | H. Ikeuchi & Co., Ltd. | Atomizer nozzle assembly |
US5687905A (en) * | 1995-09-05 | 1997-11-18 | Tsai; Shirley Cheng | Ultrasound-modulated two-fluid atomization |
EP1081487A2 (en) | 1999-09-06 | 2001-03-07 | Hitachi, Ltd. | Nebulizer |
EP1081487A3 (en) * | 1999-09-06 | 2003-07-16 | Hitachi, Ltd. | Nebulizer |
US20080296787A1 (en) * | 2007-06-01 | 2008-12-04 | Wet Enterprises, Inc. | Gas Splattered Fluid Display |
US8500038B2 (en) * | 2007-06-01 | 2013-08-06 | Wet Enterprises, Inc. | Gas splattered fluid display |
US8268354B2 (en) | 2007-11-07 | 2012-09-18 | Aridis Pharmaceuticals | Sonic low pressure spray drying |
US20100331428A1 (en) * | 2007-11-07 | 2010-12-30 | Aridis Pharmaceuticals | Sonic Low Pressure Spray Drying |
US8673357B2 (en) | 2007-11-07 | 2014-03-18 | Aridis Pharmaceuticals | Sonic low pressure spray drying |
CN102141245A (en) * | 2010-01-29 | 2011-08-03 | 阿尔斯托姆科技有限公司 | Injection nozzle and method for operating an injection nozzle |
US20110185741A1 (en) * | 2010-01-29 | 2011-08-04 | Fulvio Magni | Injection nozzle and method for operating an injection nozzle |
CH702598A1 (en) * | 2010-01-29 | 2011-07-29 | Alstom Technology Ltd | Injection nozzle and method for operating such an injection nozzle. |
US8567198B2 (en) | 2010-01-29 | 2013-10-29 | Alstom Technology Ltd. | Injection nozzle having constant diameter pin and method for operating the injection nozzle |
HRP20110066B1 (en) * | 2010-01-29 | 2014-12-19 | Alstom Technology Ltd. | Injection nozzle and method for operating an injection nozzle |
CN102141245B (en) * | 2010-01-29 | 2015-11-25 | 阿尔斯托姆科技有限公司 | The method of nozzle and the operation for this nozzle |
US20120145050A1 (en) * | 2010-12-08 | 2012-06-14 | Vladimir Vladimirovich Fisenko | Apparatus for combustion products utilization and heat generation |
US8551222B2 (en) * | 2010-12-08 | 2013-10-08 | Fisonic Holding Limited | Apparatus for combustion products utilization and heat generation |
Also Published As
Publication number | Publication date |
---|---|
GB1248711A (en) | 1971-10-06 |
DE7013257U (en) | 1971-02-25 |
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Owner name: GULF CANADA CORPORATION/CORPORATION GULF CANADA,CA Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:GULF CANADA LIMITED;REEL/FRAME:004555/0478 Effective date: 19860224 Owner name: GULF CANADA CORPORATION/CORPORATION GULF CANADA, P Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:GULF CANADA LIMITED;REEL/FRAME:004555/0478 Effective date: 19860224 |
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Owner name: GULF CANADA CORPORATION/ CORPORATION GULF CANADA, Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:GULF CANADA LIMITED/ GULF CANADA LIMITEE;REEL/FRAME:004645/0530 Effective date: 19861014 Owner name: GULF CANADA CORPORATION/ CORPORATION GULF CANADA, Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:GULF CANADA LIMITED/ GULF CANADA LIMITEE;REEL/FRAME:004645/0530 Effective date: 19861014 |