US2381931A - Metal spray gun of the wire feed type - Google Patents

Metal spray gun of the wire feed type Download PDF

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Publication number
US2381931A
US2381931A US421194A US42119441A US2381931A US 2381931 A US2381931 A US 2381931A US 421194 A US421194 A US 421194A US 42119441 A US42119441 A US 42119441A US 2381931 A US2381931 A US 2381931A
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Prior art keywords
speed
rotor
turbine
spring
disc
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US421194A
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English (en)
Inventor
Arthur P Shepard
Herbert S Ingham
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METALLIZING ENGINEERING COMPANY Inc
Metallizing Engineering Co Inc
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Metallizing Engineering Co Inc
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Priority to US421194A priority Critical patent/US2381931A/en
Priority to GB12519/42A priority patent/GB559629A/en
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Publication of US2381931A publication Critical patent/US2381931A/en
Priority to FR919983D priority patent/FR919983A/fr
Priority to DEM6763A priority patent/DE853238C/de
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    • 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
    • B05B7/16—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 incorporating means for heating or cooling the material to be sprayed
    • B05B7/20—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 incorporating means for heating or cooling the material to be sprayed by flame or combustion
    • B05B7/201—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 incorporating means for heating or cooling the material to be sprayed by flame or combustion downstream of the nozzle
    • B05B7/203—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 incorporating means for heating or cooling the material to be sprayed by flame or combustion downstream of the nozzle the material to be sprayed having originally the shape of a wire, rod or the like

Definitions

  • This invention relates to new and useful improvements in metal spray guns of the wire feed type.
  • Metal spray guns of the wire feed type are devices in which a metal rod or wire is continuously fed into a melting zone, from which zone the metal is propelled in finely subdivided form by suitable means such as a blast of air or other gas.
  • the rod or wire is fed into the melting zone by suitable rod or wire feeding means, such as knurled burs pressing against opposite sides of the wire.
  • rod or wire feeding means are driven, preferably operating through reduction gears, by a compressed gas motor, i. e., a motor, the rotor of which is rotated by the force of compressed gas.
  • the load on the motor varies from time to time due to the changes in the position of the operator, kinks in the wire, etc.
  • low melting point metals may be fed and sprayed more rapidly than higher melting point metals and larger diameter wires must be fed and sprayed more slowly than smaller diameter wires of the same material.
  • the ordinary gas turbine is very susceptible to variations in the operating load.
  • the ordinary gas turbine has sufficient power for feeding the wire under normal conditions as long as a sufficient quantity of gas is supplied to the turbine rotor at a suiiiciently high pressure.
  • the power requirements of the turbine necessitate the feeding thereto of sufficient impelling gas to cause the turbine to operate at a very high speed.
  • the turbine operates with a given inflow and pressure of gas, all the power is used up and no excess power is available to take care of variations in the operating load.
  • the governor construction in accordance with our invention makes it possible for the first time to utilize a governor of the centrifugal type to govern the rotor of a metal spray gun or the wire feed type through a wide speed range whereby the governing action, 1. e., the mechanical movement of the actuating mechanism is substantially approximately proportional to the change in speed of the rotor throughout the speed range covered by the governor.
  • Y is the axis of rotation of a governor element having an arm of the length l and carrying at its end the mass M and pivotally connected at X.
  • R is the distance of M from the axis oi rotation Y, and o the angle of deflection or the arm I from the axis of rotation Y.
  • the force F can be considered to be resolved into a component force indicated by the vector arrow C, Perpendicular to the arm I, and a component force indicated by the vector arrow S, in the direction of the arm 1.
  • the component force C tends to deflect the arm l and. assuming the latter to move outwardly against a spring resistance, indicated by the vector arrow P, is balanced by the spring resistance P at any given operating position of I.
  • Equation 12 the value of K for equilibrium at that deflection may be found by inserting the various values in Equation 12 resolved for K.
  • Table III [Deflection range 7 to 88] R. P. S 32. 56 109. 41 179. 6 309.8 461.2 666
  • Table IV [Deflection range 1 to 88 ⁇ R.P.S 0 40.7 147.9 286.8 450.0 666
  • Table V [Deflection range 7 to 88] R.P.S 0 59.6 147.9 252.9 434.8 666
  • Table VI [Deflection range 7 to 88] R.P.S 0 80.3 210.5 417.7 666
  • the curves plotted for each series of values for and R. P. 8., given in the foregoing tables, are illustrated in Fig. 21 as II, III, IV, V and VI corresponding respectively to the tables of the same designation.
  • the section of curve I between 10 and 70 angular deflection though roughly approximating a constant in its slope, has a very steep pitch with respect to the abscissa and covers for a total of 60 deflection an R. P. S. range of only from 115 to 220 R. P. S. that is a total R. P. S. range of only 105 R. P. S.
  • the pitch with respect to the abscissa of these sections is not as steep.
  • the R. P. S. range is from 330 to 666 Or a total of only 333 R. P. S. for 8 deflection.
  • curves II, III, IV, V, and VI Analyzing the curves based on a predetermined initial angular position of the arm l (curves II, III, IV, V, and VI) it will be seen that curves II and III also do not possess any section above minimum operating R. P. S. of 100 for which the slope roughly approximates a constant and which defines an R. P. S. range covering in excess of 200% speed variation.
  • curves IV, V, and VI it will be seen that these curves roughly approximate a constant all the way between the minimum operating R. P. S. of 100 and the maximum operating R. P. S. of 666 which is equivalent to an R. P. S. range covering in excess of 500% speed variation.
  • variable speed governing mechanism for a metal spray gun construction of the wire feed type, having a compressed gas motor, comprises at least one arm, rotatable with the rotor of such motor and centrifugally deflectable for angular deflection with respect to its axis of rotation, against spring resistance, from a predetermined initial position, preferably of at least 60, with respect to such axis; speed control means, composed of at least one first and one second element, the first element being positioned and adapted to be operatively acted upon by the arm or arms upon centrifugal actuation of the arm or arms to cooperate, by mechanical movement, with the second element to thereby eiiect speed control of the rotor; and means for variably adjusting the relative position between the second element and the initial position of the first element within a range of mechanical movement of the first element defined by angular deflection of the arm between minimum and maximum operating speeds of the rotor.
  • the initial position of the first element of the speed control means referred to here
  • the metal spray gun of the wire feed type embodying our invention does not require any change of gearing.
  • the same is capable of maintaining any number of practical wire feeding speeds and may be shifted from one speed to another by a simple adjustment of the preferably manual control means.
  • the motor or turbine of such metal spray gun is at all times maintained in a stable operating condition.
  • the particular construction in accordance with our invention permits the use of these metal spray guns under substantially stable operating conditions, over a much wider range of wire feed speeds than was heretofore possible.
  • Fig. 1 is a sideview of the metal spray gun illustrating one embodiment of a construction in accordance with the invention
  • Fig. 2 is a vertical section through the construction shown in Fig. 1 on the plane indicated by IIII;
  • Fig. 3 is an illustration of the stopwasher as seen in the plane IIIIII of Fig. 2;
  • Fig. 4 is a vertical section through the construction shown in Fig. 1 on the plane indicated by IVIV;
  • Fig. 5 is a vertical section through the construction shown in Fig. 1 on the plane indicated by V-V except for the construction of the structure illustrated in Fig. 7 which is shown on the plane indicated by the section line VV' in Fig. 'l;
  • Fig. 6 illustrates a view of part of the section shown in Fig. 5;
  • Fig. 6A is a plan view of the interior of the construction shown in Fig. 6;
  • Fig. 8 is a view of part of the construction shown in Fig. 7 at right angles thereto;
  • Fig. 10 is a vertical section through the construction shown in Fig. 5 on the plane indicated by X-X;
  • Fig. 13 is a vertical section through the construction shown in Fig. 5 on the plane indicated by XIII-XIII;
  • Figs. 14, 15, and 16 illustrate sectional views of variations in the construction of a spray gun embodying our invention
  • Fig. 18 is a vertical section through the construction shown in Fig. 17 on the plane indicated by XVIIIXVIII;
  • Fig. 20 is a sideview of one element shown in the construction of Fig. 19;
  • Fig. 21 is a graphic representation of the principle underlying the invention and Fig. 22 is a diagrammatic representation for deriving governor weight positions.
  • the speed control means in accordance with our invention may be any suitable means for accomplishing that purpose. They may, for instance, comprise as is by way of example illustrated in connection with Figs. 1 to 16 inclusive 9.
  • power absorption mechaniwalternatively comprise as is exemplified by gs. 1'? to 20 inclusive a control mechanism for the regulation of the compressed gas supply to the motor or turbine.
  • the arm in accordance with our invention operating against sprin resistance when centrifugally actuated may be any one or a multiple number of suitable spring force controlled arms though we prefer a construction where the arm or arms comprise a spring element such as for instance one or more spring arms, i. e., arms made of spring material, set at the desired predetermined initial angle.
  • I indicates the inlet for oxygen or other combustion supporting gas
  • 2 the inlet for acetylene or other combustible gas
  • 3 the inlet for air or other gas for atomization of the metal, projection of the metal spray and driving of the turbine.
  • plug 4 of valve 5' When plug 4 of valve 5' is in the position shown, each of the inlets registers with a corresponding hole in the plug, these holes being indicated by numerals 5, 6 and I respectively.
  • oxygen flows through duct HI into duct II.
  • the combustible gas flows through duct I! to mix with the oxygen in duct II and the air flows through duct l5 into chamber l6 and also flows through the side connection ll into turbine manifold l9.
  • Openings 5, 6 and 1 in plug 4 are so arranged that as handle 8 is turned from the off position, which is at a right angle to the showing in Fig.
  • the washer 20 (Fig. 3) defines a hole 2
  • the washer 20 is formed with the depression 23 (Fig. 3). This washer is spring pressed and this depression slips onto the head of pin 24 when handle 8 is in the correct position for lighting the burner.
  • the construction of that part of the gun by which the rod or wire is melted and projected will be explained by reference to Fig. 9.
  • the wire 31 moves forward to guide 3
  • the mixture of air and oxygen move forward through the duct II, which is immediately behind duct 32 (the arrangement is shown in Fig. 2) and into the annular space 35. From this annular space 35 the combustible mixture moves forward through a number of holes to be discharged through convergent orifices 35 against the wire.
  • the air from the chamber I0 advances through the annular space 40 surrounding burner tip 34 and is projected by air nozzle 4
  • is threaded to the outer shell 42 of the burner so that the orifice 43 defined by conical interior of air tip 4
  • is locked in position by the lock nut 44. It will be noted that the air in passing forward from the chamber l6 goes through the constricted annular space 45 which exerts a definite control over the volume of air passing.
  • the wire 31 enters the gun through the annular guide 50 of hardened material in which is the duct 5
  • the upper and lower surfaces of the wire are engaged respectively by the burs 52 and 53.
  • Bur 53 is carried by shaft 54, which shaft is driven by an air turbine through suitable intermediate gearing which will be hereinafter described.
  • Shaft 54 (Fig. 4) also drives the gear 55 in mesh with gear 56, which in turn drives the upper bur 52.
  • Both gear 58 and bur 52 are secured to the tubular member 51 which rotates on the spool 58 carried by pin 50 (Fig. 4).
  • the screw 59 lS-T'Cfil'lled by the saddle 00 and this saddle is pivotally secured (Fig. 9) to frame SI of the gun by the hinge 62.
  • cap 65 When cap 65 is turned the threaded end 06 of the screw 81 advances into the threaded member 53 which is a part of frame GI and the spring I0 exerts pressure on the saddle 80, thereby forcing the upper bur 5.: toward the lower bur 53 and thereby causing the burs to engage and advance the wire 31. Conversely, when cap 65 is turned in the reverse direction, pressure of spring I0 on saddle 60 is released and the burs move freely without engaging and advancing the wire.
  • the shaft 54 (Fig. 4) which drives bur 53 is mounted in ball-bearings I0 and II. Bearing I0 is held in frame GI and bearing II is held in the housing I2 which is attached to frame 6
  • the shaft 54 is driven by the worm gear 13, which in turn is driven by the worm I4, carried by the shaft 15.
  • Shaft I5 (Fig. 10) is carried by ballbearings I5 and I1 mounted in the housing 12. Shaft I5 is in turn driven through the worm gear I0 by the worm I9.
  • the worm I9 (Fig. 5) is integral with the shaft carried by bearings 35 and 86. Bearing 85 is mounted in housing 12 and bearing 06 is mounted in the cap or cover of the turbine 9
  • Turbine 9I (Fig. 5) includes the turbine rotor drum secured to shaft 80. Details of the blading I00 are apparent from Figs. 7 and 8. As evident from Fig. 6, cover 90 includes the mounting
  • the washer-shaped member I03 is made of fine wire mesh and rests directly upon ridges I02. The washer I04 rests directly on the washer I03. The washer I04 defines the perforations I05 (Fig.
  • nozzle arrangement operating the turbine is shown in Fig. 11. Face 5 together with the housing 90 defines the space in which the turbine drum rotates; (the drum is not shown to facilitate inspection of the nozzle structure).
  • a nozzle I30 is permanently connected to the manifold I3. Hence, part of the air or other gas which enters through connection 3 and into manifold I9 can flow through Jet and hence propel the turbine. All of these connections are made large enough to propel the turbine at the maximum speed at which it will be required to operate, and hence an excessive amount of gas is supplied for every speed except the maximum.
  • rotor 95 carries governor spring element 200 mounted thereon by means of screws -20
  • This spring element is set with respect to the axis of shaft 80 at an angle of approximately 75.
  • the weights 202 in this case consist of screws clamped through a hole in each end of the spring 200 by the nuts 200.
  • the weights 202 take the position shown.
  • the centrifugal force acting on the weights 202 tends to pull them away from the axis of the shaft and in so doing tends to deflect the arms of the spring 200 forwardly towards a perpendicular position to the axis of shaft 90.
  • Thi tendency of the springs to straighten under the centrifugal force acting on the weights is increased by the weight of nuts 203, which, because they extend beyond the bent spring, exert a twisting force due to the action of centrifugal force which twisting force is also in the direction to deflect the spring arm 200 nearly perpendicular to the axis of shaft 80.
  • the spring arms 200 When the rotor 95 is operating at the lower end of its speed range, the spring arms 200 are but slightly deflected from their initial position. In this speed range a slight change of speed causes a motion of the buttons or weights essentially in the direction of axis of shaft 00, due to the change in the amount of centrifugal force acting on weight 202 and nuts 203. The deflection of the spring is not proportional to the square of the speed of rotation but is approximately directly proportional to the speed of rotation. As the speed increases and the buttons 202 move approximately parallel to the axis of shaft 80. they deflect the spring arms 200 to a position more nearly perpendicular to the axis of shaft 80. The buttons 202 therefore operate in and out essentially parallel to the axis of shaft throughout the entire large speed range required for a metallizing gun, and the position of the buttons 202 at any speed represents a measore of that speed.
  • brake disc subassembly 204 Slidably mounted on shaft 80 is brake disc subassembly 204.
  • This sub-assembly consists of hub 205, disc 200 and bent clip 201. Bent clip 201 and disc 205 are mounted on hub 205 and secured thereto by screws 208. The ends of the arms of the piece 201 are bent up to form ears or prongs 209. As assembled these ears 209 fit on either side of each weight button 202, hence, as rotor 95 rotates, brake disc sub-assembly 204 also rotates being driven by the contact of weight buttons 202 with ears 209 of spring clip 201.
  • Mounted on shaft 80 next to bearing 06 is washer 2l0.
  • the weight buttons 202 move parallel to the axis of shaft 90 towards the brake disc sub-assembly 204, and by the contact of the buttons 202 with the spring clip 201 force the brake disc sub-assembly 204 to slide along the shaft 00 in opposition to the coil spring H2.
  • the turbine housing 90 is cut away at three sections 213, so as to permit the three segments 2 of spider or friction ring 2 l to fit loosely through the resulting openings.
  • the outer periphery of the three segments 2, of spider 2l5 are threaded.
  • Ring nut 215, substantially forming an extension of the turbine housing 90, is threaded in its bore to engage the threads of spider Hi. This thread extends on the bore of ring nut 2l5 to a neck at the end of the thread which is terminated by shoulder 2".
  • Ring nut 2 l 6 is rotatably mounted on housing 90 and is located by bearing surface 2 l 8.
  • Disc 219 is secured to housing 00 by screws 220, and acts to restrain the ring nut 2l0 on the housing 90 between the housing shoulder 22! and itself so that the ring nut 2l5 is free to rotate but cannot move longitudinally.
  • Ring nut 2l8 is provided with grooves 222 and 223, which extend around its faces and which are packed with a packing material such as cork or graphite-impregnated cotton string.
  • This construction serves the double purpose of keeping dirt out of the mechanism and also of providing a necessary amount of friction so that ring nut 216 will not turn accidentally.
  • a section of the outer periphery of ring nut 215 is knurled at 224 to provide an easy grip to the fingers for turning. As that portion of the housing 90 which has not been cut away to allow space for the spider segments 2l4 straddles these segments of the spider 2l5, the spider H5 is not permitted to rotate, but is permitted to move parallel to the axisof shaft 00.
  • the ring shaped face 225 of spider 2 l 5 (Fig. 63) represents a braking surface to contact the face of the brake disc 206.
  • Brake disc 205 is preferably made of hardened steel and polished on its contacting surface.
  • 5 is preferably made of sprayed metal, most preferably of sprayed bronze. For smooth operation it is important that the coefllcient of friction, between these two surfaces remain as constant as possible throughout varying conditions of service, as well as throughout varying conditions of lubrication.
  • Sprayed metal is particularly adapted for this purpose because of its constant coefficient of friction and because due to its porosity it will absorb lubricant and hence operate under at least semilubricated conditions when it might otherwise be operating dry.
  • the braking face 225 may be divided into segments if desired by cutting a number of radial shallow slots 228. Such slots 226 will tend to collect foreign matter and prevent scratching of the braking surface.
  • Shaft is provided with lubricant holes 221 and 228, which extend from the lubricant chamber 229 behind the bearing to the surface of the shaft beneath hub 205. Housing is provided with the grease plug 290 which may be removed for the introduction of grease to chamber 229 and to the holes in the shaft 221, 229 to the sliding bearing surface between shaft 00 and hub 205.
  • Bent clip 201 performs the double function, first of providing a driving means through the ears 209, the buttons 202, the spring 200 and the rotor 96 between the rotor and the brake disc sub-assembly 204.
  • the other function is that of absorbing by its resiliency the pounding action of weight buttons 202.
  • the weight buttons 202 which are mounted on the ends of spring arms 200 to enter into a vibratory motion. This motion is quickly absorbed by the resiliency of the arms of bent clip 201. It will be understood that bent clip 201 may be eliminated from the sub-assembly 204 and that the weight buttons 202 may then be made to bear directly against brake disc 206.
  • bent clip 201 is eliminated, however, some other means such as keying, gearing or other drive connection should be used to drive brake disc sub-assembly 204 and cause it to rotate with rotor 35.
  • the brake disc 265 may be made lighter than would otherwise be possible, as piece 201 also serves to apply thrust load from the weight buttons 202 more nearly at the center of disc 203, hence minimizing the distortion due to an unevenly applied load.
  • ring nut H6 is turned to locate spider 215 in any desired position corresponding to a desired speed.
  • this rotor will tend to increase its speed, causing the weight buttons 202 to move toward brake disc sub-assembly 204 and cause the brake disc sub-assembly to move toward the friction surface 225 of spider 2 l5.
  • the brake disc 206 brushes against friction surface 225, generating heat by friction, thus absorbing any excess power which may be developed by the turbine rotor 35. Any heat which is thus developed is absorbed and carried away by the exhaust gas from the turbine which must pass around the spider 2
  • the speed of the rotor 95 is, therefore, accurately established by the position of the spider 2l5, for if the rotor 35 tends to travel faster, increased pressure is exerted between brake disc 206 and braking surface 225, causing an increase in friction. If due to a kink or bend in wire 31 or some other cause an increased load is imposed on the driving mechanism of the metallizing gun, this load causes the rotor 95 to slow down very slightly. However, even a very slight reduction in speed is sufficient to cause the weight buttons 202 to move slightly away from the brake disc sub-assembly 204 and hence release the pressure between the friction surfaces 206 and 225.
  • the action of the governor is practically instantaneous so that a very steady wire feed drive is provided, which can easily be adjusted to any given speed over a wide range of speeds by the simple expedient of turning ring nut 2l6. This constancy of wire feed is maintained even with variations in the amount or pressure of the blast gas supplied for the operation of the turbine.
  • brake disc subassembly 204" is forced to contact friction surface 235 until sufficient friction is generated and absorbed to permit the turbine to arrive at and maintain its pro-determined speed.
  • the speed is pre-determined or adjusted by the location of friction surface 235 which is obtained by screwing the screw 23l in or out by means of the knurled knob 233.
  • Fig. 16 The construction shown in Fig. 16 is similar to the construction described in connection with Fig. 5 except that brake disc assembly 204 (of Fig. 5) has been replaced by friction button sub-assembly 235.
  • This assembly consists of a hub 231, slidably mounted on shaft and a bent clip 238 similar to bent clip 201, of Fig. 5, which is secured to hub 231 by screws 239.
  • Ears 240 are provided at the ends of bent clip 238 for the same purpose as described in connection with bent clip 201 of Fig. 5.
  • On each end of bent clip 238 is mounted a friction button 24l.
  • clip sub-assembly 236 is moved along shaft 30 as described in connection with subassembly 204 in Fig. 5.
  • sliding hub GM is provided with a pin 300 which extends radially through it.
  • Shaft 602 has a slot 3! which is wide enough to permit space for pin 300 and which is long enough, parallel to the axis of the shaft, to permit considerably longitudinal movement of hub 6M, along the shaft when pin 300 is in place extending through the slot 30!.
  • Hole 302 is centrally located in shaft 602 and extends from its end past slot 30I.
  • pin 303 Located in hole 302 is pin 303 which is fitted as to be freely slidable in hole 302.
  • One end of pin 303 extends beyond the end of shaft 002 and is smooth and rounded oil on this extending end.
  • Valve plunger 304 is slidably mounted in housing 603 and is forced in the direction toward the shaft 602 by the action of coil spring 305 which acts against pin 306 in one end of valve plunger 304.
  • valve body 301 Threadedly mounted in housing 003 is valve body 301 which has threads 300 and finger wheel 300 and valve seat 3l0. Nut 3 holds packing material 3I2 against the thread 308 to prevent leakage of air around the threads.
  • Air passage M3 is provided and leads from the air duct I9 to the space 3 between the valve body 301 and the housing 603. Hole 3
  • valve plunger 304 When valve plunger 304 is not in contact with valve seat 3
  • Air passage 3! connects space 3 with the short duct BIS.
  • Turbine air jet 604 extends from short duct 3 l to the surface of housing 605 at such an angle that air emer ing from jet 604 impinges against turbine blades I00 to cause turbine rotor 95 to rotate.
  • buttons 202 which contact the ends of spring clip cause hub 60I to move along the shaft 602 in a direction away from the rotor 35.
  • pin 300 travels along the shaft with the hub G0l it forces pin 303 to press against the end of valve plunger 304 causing valve plunger 304 to approach valve seat 3 I 0.
  • valve plunger 304 approaches valve seat M0 the air supplied to jet 004 is restricted thus reducing the energy supplied to turbine rotor 05. Consequently at a predetermined speed the air flow will be sufficiently restricted to prevent a further increase of the speed of turbine rotor 95 and the rotor will operate at this predetermined speed.
  • the operating speed of rotor 35 is predetermined or selected either in advance or during operation by turning the thumb wheel 30!! of valve body 301.
  • valve body 301 This screws the valve body 301 in and out on the thread 308 causing the valve seat 310 to get closer to or farther from the face of valve plunger 304.
  • valve body When more speed is desired the valve body is turned in a direction to provide more space between the seat and plunger and when it is desired to reduce the speed it is turned in the opposite direction thus providing less space between the valve seat and valve plunger.
  • the rotor 95 will maintain a speed which is nearly constant. If for any reason an increase of load should be applied to the mechanism, as for instance by a kink in the wire being fed then at first the speed of rotor 95 will be slightly reduced. After a very slight reduction in speed, however, the governor weight buttons 202 will move slightly toward the rotor permitting spring 2 to force hub 60l along shaft 602 toward rotor 95. This permits pin 303 to move back and hence spring 305 will move plunger 304 away from valve seat 0. This will permit more air to flow between the valve seat and the plunger and through the passage 3! and 3l9 to the jet 004.
  • This spring is so wound as to act between the housing 505' and the disc 400 so as to tend to force it as far as it will go in a counterclockwise direction as viewed in Fig. 20.
  • Slot 402 is cut wide enough so that the disc 400 does not cover the opening of airjet 004' when disc 400 has been forced by spring 405 to the limit of its travel in a counterclockwise direction (Fig. 20).
  • the location of pin 403 with respect to the location of the opening of Jet 304' and the length of slot 102 are such that when the disc 400 has been forced in a clockwise direction as far as it will go that part of the disc 400 indicated at 408 will cover up the opening of the Jet 8M.
  • Bearing H which is mounted on one end of shaft 602' is slidably fitted in housing I2 and housing 12' i made sufiiciently long to permit of a considerable longitudinal motion of shaft 602'.
  • bearing 86' is clamped to the shaft by nut 409 and is clamped in a housing 4 III by the threaded cap 4
  • the outside of housing M is provided with threads 4
  • thumb wheel I I3 If thumb wheel I I3 is turned, the housing M0 is screwed either in or out of the housing 603'; and as the bearing 86' is rigidly clamped in the housing 4 l 0 and to the shaft 602' the shaft and the whole rotor assembly are forced either in or out.
  • thumb wheel 3 it is possible to adjust the longitudinal position of shaft 602' and the whole rotor assembly including rotor 95', governor spring 200 and governor weight button 500.
  • the governor weight buttons 500 are made of a sufficient length so that they can contact the face of disc llill.
  • This speed is predetermined, or, may be adjusted during operation by an adjustment of the longitudinal position of the rotor assembly which is effected by screwing the thumb nut l l 3 either in or out. If more speed is desired the thumb nut 3 will be turned in such a direction as to screw the rotor assembly away from the face of disc 400 and if less speed is required it will be turned in the opposite direction. The farther removed the rotor assembly is from disc 400 the greater speed will have to be attained before the deflection of the spring 200 will be sufficient to permit the governor weight button 500 to contact and thus rotate disc lllll.
  • the turbine rotor 95' will maintain its predetermined speed with but slight variations. If for some reasons such as a kink in the wire being fed through me metal spray gun an increased load is imposed upon the turbine rotor 95' then it will slow down slightly. As soon as it slows down even a very small amount, the weight buttons son will move away from the disc 400; if they do not actually move away from disc "0 they will at least reduce the pressure which they exert against the disc 40 so as to produce less obstruction of the air jet 604'. Hence more energy is supplied to turbine rotor 55' to overcome the additional load which was imposed, and no further reduction of speed will occur.
  • the power absorption principle has been utilized to its best possible advantage in addition to the principle of control of the input energy to the turbine rotor.
  • the speed control means in accordance with the invention comprise a first element, capable of mechanical movement induced by the operation of the arm or arms, and a second element, cooperating with the first element to effect any desired speed variably adjustable within the entire speed range.
  • brake disc 2116 constitutes the first element operated by the movement of the spring arms 200 by way of the buttons 202 and clip 201.
  • the second element constitutes in this case the friction face 225 of spider iii variably adjustable within the range of mechanical movement of the brake disc 206 as controlled by the deflection of the spring arms 200 between minimum and maximum speeds of the rotor II.
  • the first element may be defined by the friction buttons 20! operated by the deflection of the spring arms 200 the second element in this case being the friction face 226' operating and variably adjustable similar to the second element described in connection with Fig. 5.
  • Further modifications of first and second elements in construction and operation similar to those exemplified by Figs. 5 and 14 are illustrated in Figs. 15 and 16.
  • the first element comprises valv plunger 8 operated by the movement of the spring arms 200 by way of the buttons 20!, clip "I, hub 60! and pins 300 and "I.
  • the second element in this case is valve seat III] of valve body 301 variably adjustable within the range of mechanical movement of the valve plunger 3" as controlled by the deflection of the spring arms 2 between minimum and maximum speeds of the rotor 95.
  • the first element comprises friction buttons 500 operated by the deflection of the spring arms 2"; the second element in this case is the disc m. In this instance, the initial position of the first element, 1.
  • the friction buttons III is variably adjustable with respect to the position of the second element or disc m by means of the adjustment of the entire rotor assembly within the range of mechanical movement of the friction buttons GM as controlled by the deflection of the spring arms 2" between minimum and maximum speeds of the rotor 95'.
  • Our invention is not limited to the construction of a spray gun illustrated in the foregoing examples and may be used in connection with any other suitable gun constructions of the wire feed type, including those having other heating or melting means for the wire, such as an are or the like and further including those constructions of this type in which multiple wires are fed to the heating zone.
  • speed control mechanism is illustrated in connection with a motor of the air turbine type, it is within the scope of our invention to use our novel speed control construction to govern other types of compressed gas motors in wire feed type metal spray guns.
  • the present application broadly covers a speed governing mechanism having speed control means eifecting speed control of a rotor of a metal spray gun of the wire feed gasblast type by elements cooperating by mechanical movement and actuated by centrifugally operated and angularly defiectable arms; our co-pending application Serial No. 421,195 covers a speed governing mechanism having speed control means with friction elements; and our co-pending application Serial No. 421,196 covers a speed governing mechanism having speed control means regulating the compressed gas supply to the turbine of the metal spray gun.
  • a variable speed governing mechanism for a metal spray gun construction of the wire feed type having a compressed gas motor comprisin at least one arm, rotatable with the rotor of said motor and centrifugally defiectable for angular deflection with respect to its axis of rotation, against spring resistance, from a predetermined initial position of at least 60 with respect to said axis, speed control means composed of at least one first element and one second element, said first element being positioned and adapted be operatively actedmmfifientrifugal actuation thereof, to cooperate, by mechanical movement, with said second element to thereby efl'ect speed control of said rotor, and a separat mechanism for variably adjusting the relative position between said second element and the initial position of said first element within a range of mechanical movement of said first element defined by angular deflection of said arm between minimum and maximum operating speeds of said rotor.
  • a variable speed governing mechanism for a metal spray gun construction of the wire feed type having a compressed gas motor comprising a multiple number of substantially co-axially aligned, symmetrically arranged, radial arms, rotatable with the rotor of said motor and centrifugally defiectable for angular deflection with respect to their axis of rotation, against spring resistance, from a predetermined initial position of at least 60 with respect to said axis, speed control means, composed of at least one first and one second element, said first element being positioned and adapted to be operatively acted upon by said arms upon centrifugal actuation thereof, to cooperate, by mechanical movement, with said second element to thereby effect speed control of said rotor, and a separate mechanism for variably adjusting the relative position between said second element and the initial position of said first element within a range of mechanical movement of said first element defined by angular deflection of said arms between minimum and maximum operating speeds of said rotor.
  • a variable speed governing mechanism in accordance with claim 2 in which said arms are at least two spring arms centrifugally deflectable against their spring resistance.
  • a variable speed governing mechanism for a me al spray gun construction of the wire feed type having a compressed gas motor comprising at least one arm, rotatable with the rotor of said motor and centrifugally deflectable for angular deflection with respect to its axis of rotation, against spring resistance, from a predetermined initial position of at least 60 with respect to said axis, a resilient clip for said arm adapted and positioned to rotate with and bear against said arm, speed control means, composed of at least one first and one second element, said first element being positioned and adapted to be operativelyacted upon by said arm upon centrifugal actuation thereof, to cooperate, by mechanical movement, with said second element to thereby effect speed control of said rotor, and a separate mechanism for variably adjusting the relative position between said second element and the initial position of said first element within a range of mechanical movement of said first element defined by angular deflection of said arm between minimum and maximum operating speeds of said rotor.
  • a variable speed governing mechanism for a metal spray gun construction of the wire feed type having a compressed gas motor, comprising at least two substantially co-axially aligned,
  • a separate variably adjustable speed setting mechanism for said goveming mechanism and an actuator element for said speed setting mechanism including at least one arm, rotatable with the rotor of said motor and centriiugally defiectable for operative engagement with said speed control means by angular deflection with respect to their axis of rotation, against spring resistance, from a predetermined initial position of at least 60 with respect to said axis.
  • variable speed governing mechanism for a metal spray gun construction of the wire feed type, having a compressed gas motor
  • the improvement comprising a separate variably adjustable speed setting mechanism for said governing mechanism and an actuator element for said speed setting mechanism including at least two substantially coaxially aligned, symmetrically arranged, radial spring arms, carrying weights adjacent the ends thereof and rotatable with the rotor of said motor and centriiugally deflectable for operative engagement of said weights with said speed control means by angular deflection with respect to their axis of rotation, against their spring resistance from a predetermined initial position of at least 60 with respect to said axis.
  • K 1 page 3, second column, line 43, for first column, has 16, for disc 266 read disc 206; page 9, first column,

Landscapes

  • Chemical & Material Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Nozzles (AREA)
  • Control Of Turbines (AREA)
US421194A 1941-12-01 1941-12-01 Metal spray gun of the wire feed type Expired - Lifetime US2381931A (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US421194A US2381931A (en) 1941-12-01 1941-12-01 Metal spray gun of the wire feed type
GB12519/42A GB559629A (en) 1941-12-01 1942-09-04 Improvements in metal spray guns of the wire feed type
FR919983D FR919983A (fr) 1941-12-01 1946-01-14 Pistolet métalliseur perfectionné du type à fil métallique
DEM6763A DE853238C (de) 1941-12-01 1950-10-01 Regeleinrichtung fuer Metallspritzpistolen der Drahttype

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US421194A US2381931A (en) 1941-12-01 1941-12-01 Metal spray gun of the wire feed type

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Publication Number Publication Date
US2381931A true US2381931A (en) 1945-08-14

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ID=23669550

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Application Number Title Priority Date Filing Date
US421194A Expired - Lifetime US2381931A (en) 1941-12-01 1941-12-01 Metal spray gun of the wire feed type

Country Status (4)

Country Link
US (1) US2381931A (fr)
DE (1) DE853238C (fr)
FR (1) FR919983A (fr)
GB (1) GB559629A (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2681220A (en) * 1950-05-26 1954-06-15 Bendix Aviat Corp Centrifugal speed responsive apparatus having spring supported weights
US2691516A (en) * 1949-12-31 1954-10-12 Garrett Corp Centrifugal snap-action mechanism

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE943268C (de) * 1952-12-24 1956-11-22 Arnold Otto Meyer Fa Elektro-Metallspritzpistole

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2691516A (en) * 1949-12-31 1954-10-12 Garrett Corp Centrifugal snap-action mechanism
US2681220A (en) * 1950-05-26 1954-06-15 Bendix Aviat Corp Centrifugal speed responsive apparatus having spring supported weights

Also Published As

Publication number Publication date
GB559629A (en) 1944-02-28
FR919983A (fr) 1947-03-24
DE853238C (de) 1952-10-23

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