US3135250A - Steam generator utilizing a recirculating system - Google Patents

Steam generator utilizing a recirculating system Download PDF

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Publication number
US3135250A
US3135250A US127289A US12728961A US3135250A US 3135250 A US3135250 A US 3135250A US 127289 A US127289 A US 127289A US 12728961 A US12728961 A US 12728961A US 3135250 A US3135250 A US 3135250A
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US
United States
Prior art keywords
flow
pump
recirculating
steam generator
fluid
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
Application number
US127289A
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English (en)
Inventor
John I Argersinger
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Combustion Engineering Inc
Original Assignee
Combustion Engineering Inc
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority to BE620762D priority Critical patent/BE620762A/xx
Application filed by Combustion Engineering Inc filed Critical Combustion Engineering Inc
Priority claimed from US127176A external-priority patent/US3202138A/en
Priority to US127395A priority patent/US3135252A/en
Priority to US127289A priority patent/US3135250A/en
Priority to CH881962A priority patent/CH402001A/de
Priority to CH883162A priority patent/CH394249A/de
Priority to DES80569A priority patent/DE1253723B/de
Priority to FR905223A priority patent/FR1416315A/fr
Priority to FR905222A priority patent/FR1334598A/fr
Priority to ES0279529A priority patent/ES279529A1/es
Priority to SE8314/62A priority patent/SE308529B/xx
Priority to GB2903462A priority patent/GB1008795A/en
Priority to GB29028/62A priority patent/GB1008793A/en
Priority to US331196A priority patent/US3202135A/en
Publication of US3135250A publication Critical patent/US3135250A/en
Application granted granted Critical
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G5/00—Controlling superheat temperature
    • F22G5/02—Applications of combustion-control devices, e.g. tangential-firing burners, tilting burners
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B29/00—Steam boilers of forced-flow type
    • F22B29/02—Steam boilers of forced-flow type of forced-circulation type
    • F22B29/023—Steam boilers of forced-flow type of forced-circulation type without drums, i.e. without hot water storage in the boiler
    • F22B29/026—Steam boilers of forced-flow type of forced-circulation type without drums, i.e. without hot water storage in the boiler operating at critical or supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B29/00—Steam boilers of forced-flow type
    • F22B29/06—Steam boilers of forced-flow type of once-through type, i.e. built-up from tubes receiving water at one end and delivering superheated steam at the other end of the tubes
    • F22B29/12—Steam boilers of forced-flow type of once-through type, i.e. built-up from tubes receiving water at one end and delivering superheated steam at the other end of the tubes operating with superimposed recirculation during starting and low-load periods, e.g. composite boilers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B35/00—Control systems for steam boilers
    • F22B35/06—Control systems for steam boilers for steam boilers of forced-flow type
    • F22B35/10—Control systems for steam boilers for steam boilers of forced-flow type of once-through type
    • F22B35/12—Control systems for steam boilers for steam boilers of forced-flow type of once-through type operating at critical or supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B35/00—Control systems for steam boilers
    • F22B35/06—Control systems for steam boilers for steam boilers of forced-flow type
    • F22B35/10—Control systems for steam boilers for steam boilers of forced-flow type of once-through type
    • F22B35/12—Control systems for steam boilers for steam boilers of forced-flow type of once-through type operating at critical or supercritical pressure
    • F22B35/125—Control systems for steam boilers for steam boilers of forced-flow type of once-through type operating at critical or supercritical pressure operating with superimposed recirculation during starting or low load periods, e.g. composite boilers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G5/00—Controlling superheat temperature
    • F22G5/06—Controlling superheat temperature by recirculating flue gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G5/00—Controlling superheat temperature
    • F22G5/10—Controlling superheat temperature by displacing superheater sections

Definitions

  • the turbine is only 'a small percentage of that required when operating atfull load.
  • a much higher percentage flow of fluid is required through the waterwalls of the furnace to prevent them from being damaged during start-up.
  • One method of accomplishing this in a supercritical once-through steam generator is to provide a recirculating system around the waterwalls of the furnace, so that some of the fluid. flowing through the once-through flow system is recirculated back through the waterwalls again, thus maintaining the flow velocity through this section of the through-flow system suflicient- 1y high to prevent the tubes from being damaged.
  • the invention comprises an arrangement, construction and combination of the elements of the inventive organization in such a manner as to attain the results desired as hereinafter more particularly set forth in the following detailed description of the illustrative embodiment, said embodiment being shown by the accompanying drawing wherein:
  • FIGURE 1 shows a once-through steam generator utilizing a recirculating system and incorporating the novel features of my invention
  • FIGURE 2 is a horizontal cross section taken at line 2-2 of FIGURE 1.
  • a circulating system is added to the once-through flow system, which recirculates fluid leaving the outlet of waterwall tubes 34 back to the inlet of centerwall tubes 28.
  • the circulating system comprises pipe 48 which extends from the outlet header 36to mixing header 24.
  • Pipe 48 contains check valve 50, the purpose of which is to prevent reverse flow through pipe 48.
  • Recirculating pump 52 which is preferably a centrifugal pump although other types could also be used, maintains flow through the recirculating system when the steam generator is first being started up, and also when it is operating below a predetermined percentage of its full load capacity. Pump 52 is driven by motor 53, which is activated and deactivated by switch 51.
  • Reserve pump 60 is provided in parallel with pump 52 to handle the flow when the main recirculating pump 52 is not operating properly. If maintenance or replacement of pump 52 is necessary, motor actuated gate valve 54, located upstream of pump 52 can be closed, motor actuated gate valve 62 in bypass pipe 58 can be opened, and switch 59 closed to actuate motor 61, thus putting reserve pump 60 into operation. Check valves 56 and 64 prevent reverse flow through pumps 52 and 60, respectively.
  • FIGURE 1 10 is'a once-through I boiler operating at supercritical pressure, or pressure above 3206.2 p.s.i.a.
  • Fuel burning means 12 are provided for the furnace 14, and the hot combustion gases flow through the furnace and associated gas pass 16, thus heating the fluid flowing through the various. heat exchange members, which fluid will ultimately be used to drive a turbine 46 to generate electricity.
  • Fluid at approximately 3500 p.s.i. is supplied to the through-flow system by feedpump 17.
  • the feedpump 17, at full load, should supply the through-flow system with fluid at a pressure somewhat more than 3500 p.s.i., so that the ultimate pressure of the steam leaving the boiler circuit will be at 3500 p.s.i., afterthe pressure losses in-
  • the recirculating pump 52 should be of such capacity that it will insure a minimum velocity flow, for example three feet per second, through the tubes 28 and 34 at all times. As the turbine 46 is gradually brought up to full load by opening valve 44 more, a point will be reached at which the flow through the once-through system will be suflicient to. protect the tubes 28 and 34 within furnace 14. At this time the recirculating pump is not required, and may be de-energized if desired. In one installation, this point was determined to be of full load. However, the percent required may vary between installations, depending on such factors as the size of the tubes lining the furnace walls, the tube material, the temperature of the combustion gases within the furnace, etc.
  • feedwater pump 17 When it is desired to start up the unit, feedwater pump 17 is energized, and forces cold water through the economizer, centerwall tubes, waterwall tubes, and other sections of the once-through flow system.
  • the recirculating pump 52 is then started up, and induces flow through the recirculating system. Fuel is then supplied to the fuel burning means and ignited.
  • the fluid in the system will gradually increase in temperature, and in pressure, until eventually steam will be created, and also the pressure will be above critical pressure, at approximately 3500 p.s.i., which is the pressure the unit has been designed to operate at. It is desirable to operate at pressures above critical, since the single phase fluid at this pressure continuously changes temperature in its transition from Water heating to steam superheating and at no single point in this type of steam generation are there fluids with simultaneously difiering densities such as exists at subcritical pressure, or below 3206.2 p.s.i.a. If the unit were operated at subcritical pressure, then when a small amount of the liquid in the system started turning to steam, the recirculating pump 52 would not becapable of pumping this mixture.
  • valve 44 up stream of the turbine 46 is cracked open, and a very small percentage of fluid is allowed to flow through the turbine. This percent is gradually increased by opening valve 44 more as the turbine warms up.
  • the turbine must be slowly warmed up to prevent undue stresses and strains from being created therein by allowing a large amount of extremely high temperature steam to pass therethrough instantaneously.
  • the time required to warm up a turbine can be six hours or longer.
  • An example of operating pressures for a once-through unit containing a recirculating system in accordance with this invention might be as follows: fluid would leave the once-through circuit at 3500 p.s.i. The feedpump would supply fluid at approximately 3500 p.s.i. when the unit is operating at 70 percent load or less.
  • the recirculating pump positioned in the once-through circuit would have a capacity capable of adding 100 p.s.i. pressure to the fluid passing therethrough.
  • the boiler circuit would be designed such that when the unit operating at 70 percent load the pressure loss of the fluid flowing through the circuit would be 10Q p.s.i. Thus recirculation through the recirculating system will stop at this 70 percent load point.
  • the feedpump should be capable of supplying fluid at 3650 p.s.i. to the inlet of the once-through circuit, in order to have the fluid leaving-the once-through circuit at 3500 p.s.i.
  • the recirculating pump 52 may be deactivated by opening switch 51, and the pump will then float or idle in the line. With the pump deenergized, it will act as a restriction in the through-flow system above 70%.
  • motor-actuated gate valve 62 in bypass pipe 58 can be opened at this time, if it is not already open, and a portion of the flow can then be allowed to pass through this pipe.
  • Gate valve 62 can either be opened manually by the operator by energizing its motor, or it could be automatically opened when the unit reaches 70% load. Any suitable control which is related to and varies directly with the load on the unit could'be used, such as the fuel feed input control, or the feedwater flow control.
  • control unit 82 which pressure drop is indicative of steam flow and thus proportional to the load on the steam generator. This control is used to deactivate pump 52 and open motor-actuated gate valve 62, when 70% full load is reached.
  • Reservepump 60 also can be put into operation in the event the main recirculating pump 52 fails. If this happens, gate valve 54 is closed, gate valve 62 is opened, and switch 59 is closed to energize pump 60. Recirculating pump 52 may then be isolated from the system by gate valve 54 andcheck valve 56, and can be repaired or replaced, as required.
  • the reserve pump 60 and its associated bypass pipe 58 has a threefold purpose. It can be put into use, thus permitting continued operation of the boiler, in the event the main recirculating pump 52 fails; it permits repair or replacement of the main recirculating pump 52 with the boiler in operation; and the bypass pipe 58 can be used to handle a portion of the flow when operating in excess of 70% after the pump 52 has been deactivated, so that it does not act as a substantial restriction in the throughflow circuit.
  • parallel pump arrangement has been illustrated as located upstream of the centerwall tubes 28, it could also be used in other locations in the throughflow system, such as downstream of the centerwall tubes 28, or downstream of the Waterwall tubes 34, as illustrated in FIGURES 12 and 13 of the commonly assigned application of W. W. Schroedter application, Serial No. 127,395, now Patent No. 3,135,252 of June 2, 1964, and entitled Recirculating System for Steam Generator.
  • the recirculating pump receives fluid from mixing header 24.
  • the fluid in the recirculating system will be hotter than that coming from the economizer, and the mixing header 24 is for the purpose of mixing these two fluids, so that a single fluid of uniform temperature flows to pump 52 at all times.
  • a through-flow system supplying fluid to a turbine, a furnace, fuel burning means associated with said furnace, part of said through-flow system residing in said furnace, a feedpump for supplying fluid to said through-flow system, a recirculating system around a portion of said through-flow system so that some of the fluid flowing in said through-flow system can be withdrawn through said recirculating system and made to flow through said portion again, a first pump located in said portion of the through-flow system, said first pump having a limited capacity which is just sufficient to maintain flow through said recirculaing system until 1 the steam generator is operating at a predetermined percentage of full load capacity, and above said predetermined percentage said first pump acts as a restriction in the through-flow system, means for automatically deactivating said first pump when the steam generator reaches said predetermined percentage, a bypass pipe around said first pump, and a second pump located in said bypass pipe.
  • a through-flow system a furnace, fuel burning means associated with said furnace, part of said through-flow system residing in said furnace, a feedpump for supplying fluid to said throughflow system, a recirculating system around a portion of said through-flow system, so that some of the fluid flowing in said through-flow system can be withdrawn through said recirculaing system and made to flow through said portion again when the steam generator is operating below a predetermined percentage of its full load capacity, a first pump located in said portion of the through-flow system, said first pump having such a limited capacity that it just maintains flow through said recirculating system until said predetermined percentage is reached, a first valve in said portion to prevent reverse flow therethrough, a bypass pipe having an inlet connected to said portion upstream of said first pump and first valve, the outlet of said bypass pipe connected to said portion downstream of said first pump and valve,v a second pump located in said bypass pipe, a second valve located in said bypass pipe to prevent reverse flow therethrough, a third valve
  • a feedpump for supplying fluid to said through-flow system, a recirculating system around a portion of said through-flow system, so that some of the fluid flowing in said through-flow system can be Withdrawn through said recirculating system and made to flow through said portion again when the steam generator is operating below a predetermined percentage of its full load capacity, a centrifugal pump located in said portion of-the through-flow system, said centrifugal pump having such a limited capacity that it just maintains flow through said recirculating system until said predetermined percentage is reached, and above said predetermined percentage it acts as a restriction in the through-flow system, a centrifugal pump located in said portion of-the through-flow system, said centrifugal pump having such a limited capacity that it just maintains flow through said recirculating system until said predetermined percentage is reached, and above said predetermined percentage it acts as a restriction in the through-flow system, a centrifugal pump located in said portion of-the through-flow system, said centrifugal pump having such a limited capacity
  • first valve in said portion upstream of said centrifugal pump a second valve in said portion downstream of said to said portion upstream of said first valve, the outlet of said bypass pipe connected to said portion downstream of said second valve, a second pump located in said bypass pipe, a third valve located in said bypass pipe upstream of said second pump, and a fourth valve located in said bypass pipe downstream of said second pump, and means responsive to load conditions for deactivating saidfirst pump and opening said fourth valve when the steam generator reaches said predetermined percentage.
  • a vapor generator having a through-flow circuit comprised of a number of heat exchange sections in series flow relation with the through-flow being heated to its desired temperature upon traversal of said several sections
  • the method of operation comprising introducing suflicient flow of the working medium through said circuit to satisfy the load on the generator by pumping said working medium into said circuit at a zone at the beginning thereof, establishing a recirculation of the working medium through a portion of said system by a limited pumping action produced in the through-flow system at a zone downstream of the first-mentioned zone, maintaining this pumping action below a predetermined load on the generator to maintain the recirculation below said load, terminating said pumping action above said load while continuing to pass at least a portion of thethrough-flow through the second mentioned zone, bypassing the remainder of the through-flow around the second-mentioned zone.
  • feedpump means connected into the upstream portion of said circuit, a recirculating system superimposed upon the through-flow circuit for recirculating a working medium through a portion of the throughflow circuit and including a bypass conduit connected around said portion, recirculating pump means connected into the through-flow circuit intermediate the ends of said bypass conduit so that the through-flow must pass therethrough, said recirculating pump means including a pair of pumps connected in parallel and having check valves associated therewith to prevent reverse flow therethrough, and means for selectively activating one or the other of said pumps, the method of operation comprising establishing by the said feedpump means sufiicient flow of the working medium through the through-flow circuit to meet the demand on the generator, activating one of said pumps in parallel and eliecting suflicient pumping action thereby to cause a recirculation of working medium through said portion of the through-flow circuit at and below a predetermined load but above said predetermined load the pumping action being incapable of effecting

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Jet Pumps And Other Pumps (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
  • Fluidized-Bed Combustion And Resonant Combustion (AREA)
  • Pipeline Systems (AREA)
  • Combustion Of Fluid Fuel (AREA)
US127289A 1961-07-27 1961-07-27 Steam generator utilizing a recirculating system Expired - Lifetime US3135250A (en)

Priority Applications (13)

Application Number Priority Date Filing Date Title
BE620762D BE620762A (en:Method) 1961-07-27
US127395A US3135252A (en) 1961-07-27 1961-07-27 Recirculation system for steam generator
US127289A US3135250A (en) 1961-07-27 1961-07-27 Steam generator utilizing a recirculating system
CH881962A CH402001A (de) 1961-07-27 1962-07-20 Zwanglaufdampferzeuger
CH883162A CH394249A (de) 1961-07-27 1962-07-23 Verfahren zum Betrieb eines Zwanglaufdampferzeugers und Zwanglaufdampferzeuger zum Durchführen des Verfahrens
DES80569A DE1253723B (de) 1961-07-27 1962-07-24 Zwangdurchlaufdampferzeuger fuer Betrieb mit ueberkritischem Druck
FR905223A FR1416315A (fr) 1961-07-27 1962-07-26 Générateurs de vapeur et en particulier systèmes de recirculation de générateurs de vapeur hypercritique
FR905222A FR1334598A (fr) 1961-07-27 1962-07-26 Procédé de réglage de la température de la vapeur de générateurs
ES0279529A ES279529A1 (es) 1961-07-27 1962-07-26 Generador de vapor de paso forzado y procedimiento para el funcionamiento del mismo
SE8314/62A SE308529B (en:Method) 1961-07-27 1962-07-27
GB2903462A GB1008795A (en:Method) 1961-07-27 1962-07-27
GB29028/62A GB1008793A (en) 1961-07-27 1962-07-27 Improvements in and relating to forced flow vapour generators
US331196A US3202135A (en) 1961-07-27 1963-12-17 Vapor temperature control method

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US127395A US3135252A (en) 1961-07-27 1961-07-27 Recirculation system for steam generator
US127289A US3135250A (en) 1961-07-27 1961-07-27 Steam generator utilizing a recirculating system
US127176A US3202138A (en) 1961-07-27 1961-07-27 Vapor temperature control method
US331196A US3202135A (en) 1961-07-27 1963-12-17 Vapor temperature control method

Publications (1)

Publication Number Publication Date
US3135250A true US3135250A (en) 1964-06-02

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Application Number Title Priority Date Filing Date
US127289A Expired - Lifetime US3135250A (en) 1961-07-27 1961-07-27 Steam generator utilizing a recirculating system
US127395A Expired - Lifetime US3135252A (en) 1961-07-27 1961-07-27 Recirculation system for steam generator
US331196A Expired - Lifetime US3202135A (en) 1961-07-27 1963-12-17 Vapor temperature control method

Family Applications After (2)

Application Number Title Priority Date Filing Date
US127395A Expired - Lifetime US3135252A (en) 1961-07-27 1961-07-27 Recirculation system for steam generator
US331196A Expired - Lifetime US3202135A (en) 1961-07-27 1963-12-17 Vapor temperature control method

Country Status (7)

Country Link
US (3) US3135250A (en:Method)
BE (1) BE620762A (en:Method)
CH (2) CH402001A (en:Method)
DE (1) DE1253723B (en:Method)
FR (2) FR1334598A (en:Method)
GB (1) GB1008793A (en:Method)
SE (1) SE308529B (en:Method)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3267911A (en) * 1964-02-05 1966-08-23 Foster Wheeler Corp Supercritical steam power plants
US3357407A (en) * 1965-01-14 1967-12-12 Struthers Thermo Flood Corp Thermal recovery apparatus and method

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3308792A (en) * 1965-08-26 1967-03-14 Combustion Eng Fluid heater support
US3307524A (en) * 1965-09-16 1967-03-07 Combustion Eng Fluid heater support
US3401674A (en) * 1966-09-20 1968-09-17 Combustion Eng Steam generator recirculating pump operation

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB509746A (en) * 1939-01-03 1939-07-20 Babcock & Wilcox Ltd Improvements in or relating to forced flow vapour generators
US2255612A (en) * 1936-07-14 1941-09-09 Bailey Meter Co Control system
GB831175A (en) * 1957-02-07 1960-03-23 Sulzer Ag Apparatus and method for controlling a forced flow once-through steam generator
US2969048A (en) * 1953-11-20 1961-01-24 Sulzer Ag Feed water supply system for steam generators

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE9022C (de) * Gebr. SIEMENS & Co. in Charlottenburg, Salzufer 2 Periodisch betriebene Apparat-Kombination in ihrer Anwendung auf Maischbrenn- und Rektifizir-Apparate
US2088623A (en) * 1936-07-22 1937-08-03 Gen Electric Elastic fluid power plant control and protection
GB719753A (en) * 1951-10-23 1954-12-08 Siemens Ag Improvements in or relating to forced through-flow boilers
US2822784A (en) * 1955-05-09 1958-02-11 Babcock & Wilcox Co Apparatus for and method of generating and superheating vapor
NL224694A (en:Method) * 1957-02-07
NL229328A (en:Method) * 1958-06-13

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2255612A (en) * 1936-07-14 1941-09-09 Bailey Meter Co Control system
GB509746A (en) * 1939-01-03 1939-07-20 Babcock & Wilcox Ltd Improvements in or relating to forced flow vapour generators
US2969048A (en) * 1953-11-20 1961-01-24 Sulzer Ag Feed water supply system for steam generators
GB831175A (en) * 1957-02-07 1960-03-23 Sulzer Ag Apparatus and method for controlling a forced flow once-through steam generator

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3267911A (en) * 1964-02-05 1966-08-23 Foster Wheeler Corp Supercritical steam power plants
US3357407A (en) * 1965-01-14 1967-12-12 Struthers Thermo Flood Corp Thermal recovery apparatus and method

Also Published As

Publication number Publication date
GB1008793A (en) 1965-11-03
US3202135A (en) 1965-08-24
SE308529B (en:Method) 1969-02-17
FR1416315A (fr) 1965-11-05
CH394249A (de) 1965-06-30
FR1334598A (fr) 1963-08-09
DE1253723B (de) 1967-11-09
BE620762A (en:Method)
CH402001A (de) 1965-11-15
US3135252A (en) 1964-06-02

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