US3216044A - Long travel soot blower with contoured rail - Google Patents

Long travel soot blower with contoured rail Download PDF

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Publication number
US3216044A
US3216044A US232010A US23201062A US3216044A US 3216044 A US3216044 A US 3216044A US 232010 A US232010 A US 232010A US 23201062 A US23201062 A US 23201062A US 3216044 A US3216044 A US 3216044A
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United States
Prior art keywords
lance tube
rail
carriage
travel
tube
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Expired - Lifetime
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US232010A
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English (en)
Inventor
Robert E Chappell
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Babcock and Wilcox Co
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Diamond Power Specialty Corp
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Priority to US232010A priority Critical patent/US3216044A/en
Priority to GB38137/63A priority patent/GB971618A/en
Priority to SE11225/63A priority patent/SE301020B/xx
Priority to DED42753A priority patent/DE1301423B/de
Application granted granted Critical
Publication of US3216044A publication Critical patent/US3216044A/en
Assigned to BABCOCK & WILCOX COMPANY THE, A CORP. OF NJ. reassignment BABCOCK & WILCOX COMPANY THE, A CORP. OF NJ. MERGER (SEE DOCUMENT FOR DETAILS). EFFECTIVE DATE:03/31/78 Armed Forces in Europe, the Middle East, Africa, and Canada Assignors: DIAMOND POWER SPECIALTY CORPORATION
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Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28G—CLEANING OF INTERNAL OR EXTERNAL SURFACES OF HEAT-EXCHANGE OR HEAT-TRANSFER CONDUITS, e.g. WATER TUBES OR BOILERS
    • F28G9/00—Cleaning by flushing or washing, e.g. with chemical solvents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28G—CLEANING OF INTERNAL OR EXTERNAL SURFACES OF HEAT-EXCHANGE OR HEAT-TRANSFER CONDUITS, e.g. WATER TUBES OR BOILERS
    • F28G15/00—Details
    • F28G15/02—Supports for cleaning appliances, e.g. frames
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28G—CLEANING OF INTERNAL OR EXTERNAL SURFACES OF HEAT-EXCHANGE OR HEAT-TRANSFER CONDUITS, e.g. WATER TUBES OR BOILERS
    • F28G3/00—Rotary appliances
    • F28G3/16—Rotary appliances using jets of fluid for removing debris

Definitions

  • the present invention broadly pertains to apparatus for cleaning the heat exchanger surfaces of heat exchanger apparatus such as high capacity power boilers and the like, and more particularly to a cleaning apparatus employing a cleaning tube provided with at least one nozzle in the forward end thereof which is movable to and from a retracted position and a projected position within the interior of a heat exchanger apparatus during which a pressurized blowing medium is discharged against the heat exchanger surfaces to be cleaned.
  • the present invention relates to an improved cleaning apparatus incorporating compensating means therein for compensating for the gravitational deflection of the cleaning tube during the projecting and retracting travel thereof maintaining a substantially linear path of travel of the forward nozzle end thereof assuring uniform cleaning of the heat exchanger surfaces traversed thereby.
  • Cleaning apparatuses of the general type to which the present invention is applicable are in widespread use in industry for effecting a removal of soot, slag, and other extraneous deposits from the surfaces of heat exchanger apparatuses of various types.
  • Cleaning apparatuses, or soot blowers as they are conventionally referred to, of the so-called long-retracting or long-travel type incorporate a cleaning or lance tube which is adapted to be disposed exteriorly of and in alignment with a wall port in the wall of a heat exchanger apparatus and is movable from a retracted position wherein the forward or nozzle end thereof is disposed contiguous with the wall port to a projected position within the interior of the heat exchanger apparatus.
  • the lance tube is rotated during its longitudinal movement and a pressurized blowing medium such as steam or air, for example, is discharged in a helical blowing pattern from one or a plurality of nozzles disposed along the forward end portion of the lance tube.
  • a pressurized blowing medium such as steam or air, for example.
  • the impingement of the pressurized blowing medium against the heat exchanger surfaces effects a removal of the soot, slag and other extraneous deposits therefrom maintaining a high thermal efiiciency of the heat exchanger apparatus.
  • the increasing length of the lance tube employed in long retracting type soot blowers has caused an increasing problem as a result of the gravitational deflection of the lance tube which results in an arcuate path of travel of the nozzle end portion of the lance tube creating interference and nonuniform cleaning in some instances.
  • This vertical deflection of the nozzle end of the lance tube becomes progressively greater as the lance tube approaches the fully projected position.
  • the resultant progressive vertical deflection of the nozzle end portion of the lance tube with respect to a true linear path of travel causes a deviation in the distance of the nozzles from the heat exchanger surfaces to be cleaned resulting in a nonuniform cleaning pattern.
  • a primary object of the present invention to provide an improved soot blower of the long retracting type which overcomes the problems associated with lance tube deflection that have been encountered in soot blowers of similar type heretofore known.
  • Another object of the present invention is to provide an improved long retracting type soot blower employing guide means therein which effects a controlled vertical displacement of the lance tube in an amount so as to compensate for the vertical displacement of the nozzle end portion of the lance tube as occasioned by lance tube deflection providing for a substantially linear path of travel of the nozzles relative to the heat exchanger surfaces being cleaned.
  • Still another object of the present invention is to provide an improved soot blower of the long retracting type which is of simple design, durable operation, of economical manufacture and which embodies compensating means therein which are readily adaptable for compensating for the vertical deflection of the nozzle end of the lance tube consistent with such factors as the length of the lance tube, the specific direction of travel thereof, and the clearance and interference characteristics of the heat exchanger surfaces to be cleaned.
  • FIGURE 1 is a longitudinal side elevation view of a soot blower constructed in accordance with the preferred embodiments of the present invention and illustrated in two sections which are connected to each other along the lines indicated at AA;
  • FIG. 2 is a fragmentary perspective view of the forward end portion of the soot blower shown in FIGURE 1;
  • FIG. 3 is a fragmentary end elevation view partly in section of the forward end of a lance tube employed in the soot blower shown in FIGURE 1;
  • FIG. 4 is an alternate satisfactory form of a nozzle arrangement in the forward end portion of a lance tube
  • FIG. 5 is a graphical illustration of the vertical deflection of a typical lance tube as a function of its longitudinal projecting position
  • FIG. 6 is a typical substantially linear path of travel of the nozzle end of a lance tube of a long retracting type soot blower incorporating compensating means in accordance with the present invention.
  • a long retracting or long travel type soot blower to which the present invention is applicable, comprises guide means such as a rail 10 which is adapted to be positioned exteriorly of a wall 12 of a heat exchanger apparatus provided with an opening or wall port 14 therethrough.
  • a carriage 16 is movably supported on a track plate 18 aflixed to the underside of the lower flange of the rail 10 such as by rollers 20 disposed in rolling bearing contact against the upper projecting surface of the track plate.
  • the carrier 16 is movable along the rail from a fully retracted position as shown in FIGURE 1 to a fully projected position in which the carriage is positioned at the forward end portion of the rail 10 adjacent to the wall 12 of the heat exchanger apparatus.
  • a lance tube 22 is rotatably supported at the rearward end thereof by the carriage 16 and extends therefrom in a direction in alignment with the wall port 14.
  • the forward end portion of the lance tube 22 is rotatably and rnovably supported by suitable supporting means such as a roller support 24 connected to the forward end of the rail 10 and is disposed adjacent to the wall port 14.
  • suitable supporting means such as a roller support 24 connected to the forward end of the rail 10 and is disposed adjacent to the wall port 14.
  • the forward roller support 24 as best seen in FIGURE 2, comprises a yoke-shaped member 28 aflixed to and depending from the forward end of the rail 10.
  • a roller bracket 30 is pivotally secured by means of a pin 32 to the lower portion of each of the legs of the yokeshaped member 28.
  • a roller 34 is rotatably mounted in each of the roller brackets 30 and is adapted to rotatably and slidably contact the peripheral surface of the lance tube 22.
  • a bracket 36 is connected to the lower end of the yoke-shaped member 28 and is provided with a pair of adjusting screws 38 which extend upwardly and are disposed with the ends of the shank portions thereof in abutting relationship against the undersides of the roller brackets 30 providing for appropriate vertical adjustment of the lance tube relative to the wall port 14.
  • the intermediate roller support 26 which is usually employed when lance tubes of about 25 feet or greater in length are used, comprises a trolley bracket 40 which is disposed in rolling engagement on the track plate 18 of the rail 10, and is movable therealong from a position substantially in the middle of the rail when the carriage is in the fully retracted position to a position adjacent to the wall port 14 along the forward end portion of the rail when the carriage and the lance tube are in the fully projected position.
  • the intermediate roller support 26 is movable from the mid-position to the forward position in response to the projecting travel of the carriage and is retracted to the mid-position by suitable latching means on the carriage which are disengaged when the intermedi ate roller support attains the mid-position during the retracted travel of the carriage.
  • the lower portion of the intermediate roller support 26 is provided with suitable sliding or rolling supports on which the peripheral surface of the lance tube is rotatably and rnovably disposed.
  • the forward end of the lance tube 22 is slidably disposed within the wall port 14 which conventionally incorporates suitable sealing means (not shown) for preventing the escape of the hot combustion gases from within the interior of the heat exchanger apparatus through the wall port.
  • the forward end of the lance tube as best seen in FIGURES 3 and 4, is provided with one or more nozzles through which a pressurized blowing medium such as air or steam, for example, is discharged during the traversing movement of the lance tube during a cleaning operation.
  • a pair of diametrically disposed nozzles 42 are provided in the nozzle end of the lance tube 22 which discharge the blowing medium in a direction substantially perpendicular to the longitudinal axis of the lance tube.
  • FIGURE 4 An alternate satisfactory arrangement is illustrated in FIGURE 4 wherein a nozzle 44 is provided for discharging the blowing medium in a direction substantially perpendicular to the axis of the lance tube 22 and an angularly disposed nozzle 46 is incorporated for discharging the blowing medium in a direction forwardly of and angularly inclined relative to the longitudinal axis of the lance tube.
  • the use of one or more angularly inclined nozzles in accordance with the embodiment shown in FIGURE 4 provides advantages in some installations particularly when the angle of deflection of the nozzle end of the lance tube becomes relatively large. In either event, the particular type of nozzle arrangement employed is selected in consideration of the nature and configuration of the heat exchanger surfaces to be cleaned so as to provide substantially uniform coverage and optimum cleaning action.
  • the nozzle end of the lance tube When the lance tube 22 is in the fully retracted position, the nozzle end thereof is disposed in the wall port 14 whereby the nozzle end of the lance tube is protected from the hot combustion gases within the interior of the heat exchanger apparatus.
  • the lance tube commences to rotate and is advanced from the fully retracted position outwardly toward the projected position. The discharge of the blowing medium from the nozzle in the forward end of the lance tube is delayed until the lance tube has travelled to a position slightly beyond the water wall tubes 48 positioned along the inner surface of the heat exchanger apparatus.
  • the discharge of the blowing medium from the nozzle is halted prior to the completion of the retracting movement of the lance tube when the nozzles approach a position spaced from the water wall tubes 48 to avoid direct close range impingement of the blowing medium thereagainst which may result in the erosion thereof.
  • the supply of a pressurized blowing medium to the interior of the lance tube 22 is conveniently achieved by a feed tube 50 that is stationarily connected at its rearward end to a supply valve 52 mounted at the outward end of the rail 10.
  • the supply valve 52 is connected to a suitable supply conduit 54 which is disposed in communication with a main supply header (not shown) to which each of the other soot blowers mounted on the heat exchanger apparatus may suitably be connected.
  • the supply valve 52 can be operated mechanically such as by linkage 55 responsible to the coaction with the carriage 16 during its longitudinal movement along the rail 10 and is conventionally moved to an open position when the carriage has advanced to a position wherein the nozzle end of the lance tube is disposed beyond the water wall tubes 48 along the inner surface of the heat exchanger apparatus.
  • the supply valve 52 can be actuated by a suitable solenoid operative responsive to the tripping of suitable limit switches by the carriage in response to its movement between the fully projected position and retracted position.
  • the feed tube 50 extends forwardly from the supply valve 52 and is disposed in telescopic relationship within the interior of the lance tube 22.
  • the feed tube extends for substantially the entire length of the rail 10 to assure constant communication with the interior of the lance tube as the carriage is advanced to the fully projected position.
  • Suitable sealing means are incorporated in the carriage 16 providing a pressure-tight connection between the periphery of the feed tube and the inner surface of the lance tube to prevent the escape of any pressurized blowing medium therebetween.
  • feed tube support roller 56 as shown in FIGURE 1 which is movably mounted on the rail 10 in a manner similar to the intermediate roller support 26 and is movable by the carriage 16 to a position substantially at the midpoint of the rail 10. Suitable stop means are provided on the feed tube support roller 56 and the rail to prevent further movement of the feed tube support roller beyond the midpoint of the rail during the continued advancing movement of the carriage.
  • the feed tube support roller 56 is returned to the fully retracted position as shown in FIGURE 1 by the coaction with the carriage during the latter half of its retracting movement.
  • the sag of the feed tube is minimized when the carriage is on the fully projected position by providing support at substantially the mid-point thereof preventing any binding or skewing of the feed tube during its telescopic sliding movement into and out of the lance tube.
  • a reversible motor 58 drivingly connected to a gear box 69 mounted adjacent to the forward end of the rail 10 as may be best seen in FIGURE 2.
  • the reversible motor 58 may either be of a fluid actuable type such as an air or hydraulic motor or, alternatively, may comprise a reversible electric motor.
  • the output shaft of the gear box 60 is drivingly coupled to a suitable elon gated drive shaft 62 of an irregular cros section such as a square cross section, for example, which extends substantially for the entire length of the rail 10 and is slidingly and rotatably coupled to a driven member on the carriage having a correspondingly contoured bore therethrough for slidably engaging the drive shaft.
  • the driven member on the carriage may suitably be coupled to suitable gears for effecting rotation of the lance tube and for translation of the carriage along the rail 10.
  • the translation of the carriage between the projected and retracted positions is achieved by a rack 64 afi ixed to and extending centrally of the under side of the rail 10 with which a pinion 66 is disposed in constant meshing relationship and which is drivingly connected to the drive shaft 62 by the driven member on the carriage.
  • the rotation of the reversible motor 58 in one direction eifects movement of the carriage and translation and rotation of the lance tube in one direction and upon reversal of the direction of rotation of the reversible motor, the direction of rotation and translation of the lance tube is likewise reversed.
  • Energization of the reversible motor can be achieved manually or remotely by the operator or alternatively, can be achieved in accordance with a preselected sequentially phased operating cycle as controlled by an automatic control system.
  • the carriage On energization of the reversible motor, the carriage commences to advance toward the projected position until it trip a suitable sensing device such as a limit switch LS1 mounted on the rail 10 as shown in FIGURE 1.
  • a suitable sensing device such as a limit switch LS1 mounted on the rail 10 as shown in FIGURE 1.
  • the tripping of the forward control limit switch LS1 signals the control circuit of the soot blower which reverses the direction of rotation of the reversible motor whereby the carriage commences its retracting movement.
  • the carriage When the fully re tracted position is attained, the carriage actuates a suitable sensing device such as a rear travel limit switch LS2 which signals the control circuit and de-energizes the reversible motor.
  • a suitable sensing device such as a rear travel limit switch LS2 which signals the control circuit and de-energizes the reversible motor.
  • the carriage and lance tube remain in the fully retracted position preparatory to the next cleaning cycle.
  • Alternate satisfactory power means for effecting movernent of the carriage and lance tube along the rail can be achieved by installing a suitable electric or fluid actuated reversible motor directly on the carriage 16 which is drivingly connected to the pinion 66 and the gearing for rotating the lance tube.
  • the reversible motor 58 and gear box 60 as shown in FIG- URES 1 and 2 can be mounted at the rearward end of the rail 10 adjacent to the supply valve providing the 6 same driving action as hereinbefore described.
  • the motor means as well as the entire rail of the soot blower is preferably protected by a suitable canopy or shroud 68 to protect the several components of the soot blower from the elements and any dust or dirt particles which might interfere with the proper function thereof.
  • the vertical deflection expressed in inches of the nozzle end portion of a non-compensated lance tube having a length of 45 feet attains a magnitude of almost 3 feet at the point of maximum projection. This necessitates a relatively large cavity in the tube bundles to provide satisfactory clearance for the lance tube in addition to causing a non-uniform cleaning pattern.
  • the specific deflection obtained on a lance tube will vary, depending on the specific physical characteristics of the material of which it is comprised as well as the weight, diameter, and wall construction thereof. This deflection occurs whether the lance tube travels in a sub stantially horizontal plane or is angularly inclined from the horizontal in accordance with a specific layout of the tube bundles and heat exchanger surfaces. In either event, it will be apparent that a deviation in the position of the nozzles in the nozzle end of the lance tube occurs between the initial portion of its outward travel and at the fully projected position which, if not compensated for, results in an unevenness in the cleaning action as well as in some instances producing mechanical interference and erosion of the tubes being cleaned.
  • the vertical deflection of the lance tube is compensated for so as to provide a substantially linear path of travel of the nozzle end portion thereof between the fully retracted and the fully projected positions.
  • the compensation is achieved by providing an appropriate contour in at least a portion of the rail 10 whereby the carriage and the rearward end of the lance tube 22 is vertically displaced in response to the longitudinal travel of the carriage therealong providing a corresponding corrective vertical displacement of the nozzle end portion of the lance tube.
  • FIGURE 6 A graphical illustration of a compensated path of travel of the nozzle end portion of the lance is illustrated in FIGURE 6 wherein it is noted that the deviation of the path of travel of the nozzle end from a true linear path is relatively low throughout the entire travel of the lance tube.
  • the particular path of travel of the nozzle end of the lance tube as shown in FIGURE 6 was obtained on the same soot blower employed for tabulating the curve shown in FIGURE 5.
  • the soot blower was not provided with an intermediate roller support such as the support 26 as shown in FIGURE 1 whereby a sagging of the lance tube in the fully retracted position occurred.
  • the initial outward movement of the lance tube produced an upward movement of the nozzle end above the horizontal zero reference line.
  • the compensating means hereinafter described eflect correction of the downward nozzle deflection maintaining a substantially linear path in comparison to the arcuate path of the non-compensated lance tube shown in FIGURE 5.
  • the corrective deflection of the nozzle end portion of the lance tube is achieved, as may be best seen in FIG- URE 1, by providing an arcuately vertically depressed contour along at least a portion of the rail which deviates from a reference line indicated generally at 70 by a magnitude selected relative to the longitudinal spacing thereof from the front roller support 24 to provide an angular deviation of the outer end portion of the lance tube relative to the reference line that will effect a vertical lifting of the nozzle end portion of the lance tube in an amount sufficient to place it in a position substantially coinciding with a linear path of travel.
  • the rearward end portion of the rail 10 along the section generally designated as W is of a substantially straight configuration corresponding substantially to the plane of the reference line 70.
  • the length of the section W is dictated by the length of the overhanging portion of the lance tube beyond the wall port 14 which will produce only a negligible deflection from the linear path of travelobviating the need of any compensation.
  • the rail 10 then commences a downward arcuate contour as provided by the section generally indicated at X until a point generally indicated at Y of maximum deviation of the rail from the reference line 70 is attained.
  • the rearward end of the lance tube is vertically moved downwardly effecting a corresponding upward vertical movement of the lance tube about the fulcrum provided by the forward roller support 24 compensating for the progressive increase in the deflection of the nozzle end portion of the lance tube relative to the front support.
  • Movement of the carriage toward the fully projected position beyond the point Y is achieved along a track section generally indicated at Z which is arcuately inclined upwardly and progressively approaches the reference line 70.
  • the decrease in the vertical deflection of the rail section Z relative to the reference line 70 is necessitated by the decrease in the length of the leverage arm between the front roller support 24 and the carriage 16 which provides for a magnification of the vertical correction of the nozzle end portion of the lance tube as the carriage approaches the fully projected position.
  • the angularity of the portion of the lance tube disposed exteriorly of the wall of the heat exchanger apparatus decreases as the carriage moves along the rail section Z toward the projected position whereby the nozzle end portion of the lance tube is maintained in a substantially linear path of travel.
  • a corresponding correction of the deflection of the nozzle end portion of the lance tube is achieved during the retracting movement of the lance tube providing therewith a substantially linear path of the retracting travel of the nozzle end thereof.
  • the corrective action supplied by the arcuate contour of the rail sections W, X and Z, is illustrated in FIGURE 6 and corresponds to that achieved by the contoured rail having a configuration as shown in FIGURE 1.
  • a rail contoured in accordance with the configuration as shown in FIGURE 1 is effective to provide a substantially linear path of travel of the nozzle end portion of the lance tube in accordance with the graph as portrayed in FIGURE 6.
  • the maximum deviation of the nozzle end portion of the lance tube from a true linear path throughout its travel is less than 7 inches in comparison to a maximum deflection of almost 3 feet of a non-compensated lance tube as portrayed in FIGURE 5.
  • a further improvement in the linearity of the path of travel of the nozzle end of the lance tube can be provided by incorporating an intermediate roller support such as the roller support 26 shown in FIGURE 1 whereby the sag of the lance tube when the carriage is in the fully retracted position is substantially eliminated.
  • the contoured portion of the rail is comprised of a series of straight sections rigidly aflixed in end-abutting relationship to provide the desired contour.
  • a long travel soot blower comprising an elongated rail, a carriage movably mounted on said rail, a lance tube having the rearward end thereof movably supported on said carriage and extending therefrom in a direction in alignment with a wall port in the wall of a heat exchanger apparatus, said lance tube formed at its forward end with at least one nozzle for discharging a pressurized blowing medium against the heat exchanger surfaces to be cleaned, means for rotating said lance tube and for moving said carriage and said lance tube to and from a retracted position and a projected position, sup port means disposed adjacent to the Wall port for movably supporting said lance tube while in said projected and retracted positions and during its movement therebetween, at least a portion of said rail formed with a contour vertically displaced from a reference plane extending between the ends of said rail for vertically moving said carriage and said rearward end of said lance tube relative to said support means in response to movement of said carriage along said rail compensating for the gravitational deflection of said lance
  • a long travel soot blower comprising an elongated rail adapted to be disposed exteriorly of a heat exchanger apparatus, a carriage movably mounted on said rail, a lance tube having the rearward end thereof movably supported on said carriage and extending therefrom in a direction in alignment with a wall port in a wall of a heat exchanger apparatus, said lance tube formed at its forward end with at least one nozzle for discharging a pressurized blowing medium against the heat exchanger surfaces to be cleaned, power means for rotating said lance tube and for moving said carriage and said lance tube to and from a retracted position wherein the nozzle end of said lance tube is disposed contiguous to the wall port and a projected position wherein said nozzle end is disposed within the interior of the heat exchanger apparatus, support means disposed adjacent to the wall port for movably supporting said lance tube, at least a portion of said rail formed with a contour vertically displaced from a reference plane extending between the ends of said rail for vertically moving said carriage and
  • a long travel soot blower comprising an elongated rail adapted to be disposed in a substantially horizontal stationary position exteriorly of a heat exchanger apparatus, a carriage movably mounted on said rail, a lance tube having the rearward end thereof movably supported on said carriage and extending therefrom in a direction in alignment with a wall port in a wall of a heat exchanger apparatus, said lance tube formed at its forward end with at least one nozzle for discharging a pressurized blowing medium against the heat exchanger surfaces to be cleaned, power means for rotating said lance tube and for moving said carriage and said lance tube in a substantially horizontal direction along said rail to and from a retracted position and a projected position, support means for movably supporting said lance tube at a position adjacent to the wall port, at least a portion of said rail formed with a longitudinally extending contour vertically displaced from a horizontal reference plane extending between the ends of said rail for vertically moving said rearward end of said lance tube relative to said support means in response to the longitudinal
  • a long travel soot blower comprising a rail adapted to be disposed exteriorly of a heat exchanger apparatus, a carriage movably mounted on said rail, a lance tube having the rearward end thereof movable and rotatably supported on said carriage and extending therefrom in a direction in alignment with a wall port in a wall of a heat exchanger apparatus, said lance tube formed at its forward end with at least one nozzle for discharging a pressurized blowing medium against the heat exchanger surfaces to be cleaned, power means for rotating said lance tube and for moving said carriage and said lance tube to and from a retracted position and a projected position, supporting means for movably supporting said lance tube at a position adjacent to the wall box, at least a portion of said rail formed with a vertically disposed arcuate contour for vertically moving said rearward end of said lance tube relative to said supporting means responsive to the longitudinal travel of said carriage compensating for the gravitational deflection of said lance tube and providing for a substantially linear path of travel of

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Incineration Of Waste (AREA)
  • Machines For Laying And Maintaining Railways (AREA)
US232010A 1962-10-22 1962-10-22 Long travel soot blower with contoured rail Expired - Lifetime US3216044A (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US232010A US3216044A (en) 1962-10-22 1962-10-22 Long travel soot blower with contoured rail
GB38137/63A GB971618A (en) 1962-10-22 1963-09-27 Improvements in and relating to long travel soot blowers
SE11225/63A SE301020B (de) 1962-10-22 1963-10-12
DED42753A DE1301423B (de) 1962-10-22 1963-10-18 Langvorschub-Russblaeser

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DE (1) DE1301423B (de)
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SE (1) SE301020B (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3439376A (en) * 1965-09-09 1969-04-22 Diamond Power Speciality Long retracting soot blower
FR2519130A1 (fr) * 1981-12-29 1983-07-01 Babcock & Wilcox Co Nettoyage de surfaces tres chaudes du type a jet de liquide pulse
DE3420318A1 (de) * 1983-06-01 1984-12-06 The Babcock & Wilcox Co., New Orleans, La. Russblaeser
EP0159128A1 (de) * 1984-03-16 1985-10-23 The Babcock & Wilcox Company Düsenartiger Apparat zur Russreinigung
US20100199930A1 (en) * 2009-02-06 2010-08-12 Clyde Bergemann, Inc. Sootblower having a nozzle with deep reaching jets and edge cleaning jets

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4443128B4 (de) * 1994-12-03 2011-06-01 Clyde Bergemann Gmbh Maschinen- Und Apparatebau Rußbläsereinheit
DE10336763B4 (de) 2003-08-08 2013-09-05 Siemens Aktiengesellschaft Verfahren zur Überwachung einer Messung auf Basis eines resistiven Sensors, Überwachungseinrichtung und Industriewaage

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1599283A (en) * 1920-09-13 1926-09-07 Worthington Pump & Mach Corp Condenser and tube cleaner therefor
GB439291A (en) * 1934-06-01 1935-12-02 Babcock & Wilcox Ltd Improvements in or relating to cleaners for boilers and the like
US2897532A (en) * 1959-08-04 Retractable soot blower of the long travel type
US3160907A (en) * 1964-12-15 tollow

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2897532A (en) * 1959-08-04 Retractable soot blower of the long travel type
US3160907A (en) * 1964-12-15 tollow
US1599283A (en) * 1920-09-13 1926-09-07 Worthington Pump & Mach Corp Condenser and tube cleaner therefor
GB439291A (en) * 1934-06-01 1935-12-02 Babcock & Wilcox Ltd Improvements in or relating to cleaners for boilers and the like

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3439376A (en) * 1965-09-09 1969-04-22 Diamond Power Speciality Long retracting soot blower
FR2519130A1 (fr) * 1981-12-29 1983-07-01 Babcock & Wilcox Co Nettoyage de surfaces tres chaudes du type a jet de liquide pulse
DE3420318A1 (de) * 1983-06-01 1984-12-06 The Babcock & Wilcox Co., New Orleans, La. Russblaeser
EP0159128A1 (de) * 1984-03-16 1985-10-23 The Babcock & Wilcox Company Düsenartiger Apparat zur Russreinigung
US4567622A (en) * 1984-03-16 1986-02-04 The Babcock & Wilcox Company Sootblower nozzle apparatus
US20100199930A1 (en) * 2009-02-06 2010-08-12 Clyde Bergemann, Inc. Sootblower having a nozzle with deep reaching jets and edge cleaning jets
WO2010091342A3 (en) * 2009-02-06 2011-03-03 Clyde Gergemann, Inc. Sootblower having a nozzle with deep reaching jets and edge cleaning jets
US8770155B2 (en) * 2009-02-06 2014-07-08 Clyde Bergemann Power Group Americas Inc. Sootblower having a nozzle with deep reaching jets and edge cleaning jets
US9279627B2 (en) 2009-02-06 2016-03-08 Clyde Bergemann Power Group Americas Inc. Sootblower having a nozzle with deep reaching jets and edge cleaning jets

Also Published As

Publication number Publication date
GB971618A (en) 1964-09-30
DE1301423B (de) 1969-08-21
SE301020B (de) 1968-05-20

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