US2757968A - campbell - Google Patents

Description

NOZZLE 6 Sheets-Sheet l Allg- 7, 1956 J. F. CAMPBELL.

Filed Aug. 2s, 1954 NSW w m N mn. h T #N lv Ii m mm T .IN V EN TOR. JOHN f. CA MPfLL f ghn? i /|w FT Aug. 7, 1956 J. F. CAMPBELL NOZZLE 5 Sheet's-Sheet 2 Filed Aug. 23, 1954 n Nv Aug. 7, 1956 J. F. CAMPBELL NOZZLE 6 Sheets-Sheet 4 Filed Aug. 25, 1954 Y /ME mf/Wv V5 E mp `0 MV. C A WW, J n

w Z M 5 w 3 Z Aug. '7, 1956 J. F. CAMPBELL 2,757,968

NozzLE Filed Aug. 23, 1954 s sheets-sheet 5 A TTO2A/5V5.

Aug. 7, 1956 J. F. CAMPBEPL 2,757,968

NOZZLE Filed Aug. 23, 1954 6 Sheets-Sheet 6 INVENTOR. l0/IN f GQMPEELL A from/575.

United States Patent AUTOMAHC nmBoN `REWIND CUT-oFF Vincent J. Gilmore, Wappingcrs Falls, N. Y., assignor to International Business Machines Corporation, New York, N. Y., a corporation of New York Application July 30, 1953, Serial No. 371,331

` s claims. (cl. A197.--151) This invention relates to typewriting machines, and more particularly to an improved ribbon winding mechanism for such machines.

When the ribbon of a typewriter becomes worn and needs to be replaced by a new ribbon, it is `necessary that the operator either manually rotate the ribbon spool which has the most ribbon wound thereon until the remaining spool is exhausted, or make use of some mcchanical rewinding mechanism.

The Hazleton Patent 2,540,031 discloses a ribbon rewinding mechanism which operates continuously as long as a rewind key is held depressed. As soon as the ribbon is completely wound on one spool, the mechanism automatically reverses the winding operation if the 4key kis held depressed. With the Hazleton device, the operator must visually determine when the ribbon is wholly wound on one spool. At this point, the operator must release the key before the reversing mechanism operates to wind the ribbon back on the empty spool.

The manual rotation of the ribbon spool is slow, tedious, and very apt to soil the hands of the operator. The mechanism disclosed by Hazleton is vfaster but requires the careful and continuous attention of the operator.

A broad object of the present invention is to provide an improved ribbon winding mechanism.

Another object of the invention is to provide an improved ribbon rewinding mechanism which operates by the depression of a key to rewind the ribbon on one or the other of two spools.

Yet another object is to provide an improved power operated ribbon winding mechanism which ,operates continuously, upon the depression of a key, until all the ribbon is `wound on one or the other of two ribbon spools and then stops automatically.

Other objects of the invention will be pointed vout in the following description and claims and illustrated in the accompanying drawings, which disclose by way of eX8-.II1P1e, the principle of the invention and the best mode which has been contemplated of vapplying that principle.

In the drawings:

Fig. 1 is a sectional view of a typewriter showing a single type bar and its actuating mechanism.

Fig. 2 is a side elevational view of the improved ribbon winding device in its normal inoperative position.

Fig. 3 is an enlarged view of mechanism partially lshown in Fig. 2 for actuating a power unit to effect stepby-step winding of the ribbon.

Fig. 4 is a .detail view of certain parts of the winding mechanism shown yin Fig. 2.

Figs. 5 and 6 are views similar t0 Fig. 4 but showins parts in different positionsln Fig. 1 is shown a vertical sectionV of a power operated typewriter in which keys 1 are pivoted on a cross rod 2 and guided at their front ends by a suitable-key cfmib 3, 1th,@ .keys being restored by .Springs 4. The keys 1 .control Power mechanisms which are driven by :a power relier 6 normally rotating .countrclockwise as .in

2,757,776 Patented Aug. 7, 1956 Fig. l. Each key controls its own power unit, all of which coact with the power roller 6 to operate the corresponding type bars 7.

Each power unit includes a lever 8 which is pivoted by means of a notch 9 on an individual fulcrum bar il mounted on a support bar 12. The levers 8 are held in engagement with the bars 11 by springs 13 anchored to suitable lugs on the bars 11. The upper end of each lever 8 is connected by a link 14 to an arm 16 on the associated type bar 7 which is pivotally mounted at a point 17.

Each power unit also includes an L-shaped lever i8 pivoted at 19 on the lever 8 and urged in a counterclockwise direction by a spring 21 anchored to an ear formed on the lever. An interposer 22 having an upper lug 23 and a lower lug 24 is pivotally mounted at 26 on the lever 8 and is urged in a clockwise direction by a spring 27. The depression of the key 1 causes an extension 23 of the lever 1 to engage the lug 23 and rock the interposer 22 in a counterclockwise direction. The lug 24 then forces the lever 18 in a clockwise direction and causes the serrated tread portion 29 of the cam to engage the power roller 6 and be gripped thereby. Rotation of the power roller causes the cam 18 to swing about its pivot 19, and due to the eccentricity of the cam tread 29 with respect to the pivot 19, eiect a rocking of the lever 8 in a clockwise direction about the pivot 9, against the tension of the spring 13 thereby actuating the type bar 7 to printing position.

Pivotally mounted on the framework of the machine is a cross shaft 31 on which is pivotally `mounted a universal bar or bail 32. This bail 32 is engaged by the nose piece 33 of the lever 8 whereby each time the lever is operated, the bail 32 is actuated in a counterclockwise direction. This movement of the bail 32 is utilized to trip a power unit in a manner to be explained.

Referring to Fig. 2, suitably supported in the machine framework by a Xed frame piece 36 is a power unit generally designated 37. The power unit 37 includes a suitable frame 38 pivoted at 39 on the frame 36. An elliptical cam 41 is pivoted at 42 in the frame 38, and the cam 41 is provided with two pins 43 located on diametrically opposite sides of the pivot 42. One of the pins 43 is normally engaged by an arm 44 pivoted at 46 in the frame 38. This arm 44 is urged in a clockwise direction by a torsion spring 47 partly coiled around the pivot 46 and hooked to lugs formed in the ann 44 and in the yframe 38.

Also pivoted at 46 is a trip lever 43 having an offset lug 49 coacting with one of two pins 51 set in the cam 41 on diametrically opposite sides of the pivot 42 to limit rotation of the cam 41. Thespring actuated lever 44 pressing on one of the pins 43 tends to rotate the cam 41 in a clockwise direction about its pivot point 42. In this position of the parts, there is a small clearance between the tread of the cam 41 and an enlarged portion 52 formed on or suitably secured to the continuously running power roller 6.

When the trip lever 48 is pivoted in a clockwise direction about the pivot 46 by means to be disclosed, the lug 49 is moved upwardly out of the path of the pins 5,1 and the cam 4 1 is rotated slightly clockwise by action of the spring tensioned lever 44 on one of the pins 43. This slight clockwise rotation brings a high portion of the cam 41 into contact with the portion 52 of the power roller 6, causing clockwise rotation of the cam 41 about pivot 42.

The trip lever 48 may be rocked in a clockwise direction by two diierent means to actuate the pOWel' unit 37. Referring to Fig. 3, the iirst means is the above described individual type bar power units. When the nose piece 33 of theS lever 8 engages the bail 32 and rotates itin a counter-clockwise direction, the bail engages an arm S3 (Fig. 3), pivoted on the end of the cross shaft 31, and rotates it in a counterclockwise direction about the shaft 31, thereby shifting downwardly a link 54 joining the arm 53 and the actuating lever 48. The downward movement of the link 54 rotates the lever 48 in a clockwise direction and disengages the lug 49 from the pin 51. At the same time, a lug 56 also formed in the trip lever 48, is positioned in the path of movement of the second pin 51 so as to allow only one-half revolution of the cam 41. The trip lever 48 is then rocked in a counterclockwise direction by a spring 57 anchored to the frame 3S und to a lug carried by the trip lever 48. The lug 56 slips off the pin 51 but the pin 51 is then immediately engaged by the lug 49 and further rotation is prevented.

The second means for actuating the power unit 37 utilizes a member 58. Referring to Figs. 2 and 5, the member 58 is supported for vertical sliding movement by means of two slots 59 and 61 engaging studs 62 and 63 which are rigidly mounted in a frame plate adjacent the power unit 37. The member 58 is held in its normal,

raised position, Figs. 2 and 4, by a spring 67 tensioned between the frame stud 63 and a lug 68. The member 58 may be manually depressed to a position in which a notch 69 at one end of the slot 61 lies adjacent the stud 63. At this time, the member is pivoted by the spring 67 about the stud 62 to engage the notch 69 with the stud 63 for holding the member depressed. With the member in this depressed position, its lower end 71 acts against a pin 72 on the lever 48 for holding the latter in such a position that both the lugs 49 and 56 on the lever 48 are raised out of the path of the pins 51 and leave the cam 41 free to rotate continuously.

With the rotation limiting lug 49 and the repeat preventing lug 56 out of the path of the pins 51, the cam 41 contacts the roller portion 52 and rotates in a clockwise direction continuously until the trip lever 48 is allowed to rock in a counterclockwise direction under the tension of the spring 57, again placing the lug 49 in the path of the pins 51.

Due to the eccentricity of the lobes on the cam 41 and the action of a spring 73 connecting the frame 38 to a lng 74 on the xed frame 36, an oscillating motion is imparted to the frame 38. Fixed to the frame 36 is a resilient bumper 76 for limiting the counterclockwise rocking movement of the frame 38.

Referring to Fig. 2, the cross shaft 31 is provided at its opposite ends with two arms 77, the left one of which is connected by a link 78 to the pivoted frame 38. The shaft 3l. is rocked in synchronism with the oscillation of the frame 38 through the connecting link 78 and left arm 77. Attached to each of the arms 77 is a link 79 which actuates a ribbon mechanism associated with a ribbon spool. Fig. 2 shows the ribbon feeding mechanism located on the left hand side of the machine, but it will be understood that the two mechanisms are similar in construction and the description of one will suffice for both. The side plate 81 of the main framework is formed with a large open, cut-out portion 82 t'o accommodate the ribbon mechanisms. Each of these mechanisms has a spool 83 and various control means mounted as a unit in the cutout 82 of the associated side frame 81, by means of a plate 84 attached by three screws 86.

The link 79 for the left hand spool 83 is connected to one arm of a lever 87 which is pivoted on a stud 88 carried by the plate 84. Another arm of the lever 87 has pivoted at 89 a feed pawl 91 which is urged in a clockwise direction by a spring 92 to engage the usual ratchet teeth 94 of the ribbon spool 83 when the ribbon feed mech-k anism is in condition to feed the ribbon onto the left hand spool.

When the power unit 37 is rendered operative in the manner described above to impart an oscillating movement to the shaft 31, both links 79 are oscillated up and down. This movement of the links 79 will cause the lever 87 associated with the pawl 91 to be actuated in a clockwise direction and, if the pawl 91 is engaged with the teeth 94, the spool 83 will be rotated in a clockwise direction. It will be understood that the levers 87 for both feeding mechanisms will be oscillated each time the links 79 are oscillated, but the driving of a ribbon spool depends upon whether or not the pawl 91 for that particular spool is engaged with the ratchet teeth.

A mechanism is provided for causing the pawls 91 to engage the teeth 94 of the ribbon spools in alternation so as to cause one ribbon spool to feed until the other is exhausted and then to automatically render the other spool effective to feed. This mechanism is controlled by the tension produced in the ribbon when the free-running spool is exhausted. Pivoted at 96 on a plate 97, which is shaped somewhat like a letter G reversed right to left, is an interposer 98 which is connected by a link 99 to one arm of a tension lever 101 pivoted at 102 on the plate 84. The tension lever 101 is formed with a ribbon guide lug 103 having an open ribbon guiding slot formed therein and is urged in a clockwise direction against a stop lug 104 by a spring 106. Due to the fact that the ribbon is secured to the spools, sufficient tension will be built up in the ribbon when a spool is exhausted to cause the tension control lever 101 of the free-running spool to pivot in a counterclockwise direction, while the tension control lever of the driven spool is unaffected. When all the ribbon has been wound onto one of the spools, the angles between the ribbon on the full spool and the lever 101 are such that an increase in tension on the ribbon has no tendency to swing the lever about its pivot. The ribbon at the empty spool, however, extends from the associated lever at such angles that an increase in the tension on the ribbon causes the lever to swing. Through the link connection 99, the interposer 98 will be rotated in a clockwise direction by the movement of the control lever 101 and into the path of an offset lug 107 formed on the lever 87 Consequently, the next oscillation of the lever 87 by the link 79 will cause the plate 97 of the free-running spool mechanism to be shifted upwardly rendering the pawl 91 effective to drive the previously free-running ribbon spool 83 With each clockwise oscillation of the lever 87. The plate 97 is formed with a long offset lug 108, like the cross bar of a G, disposed between the pawl 91 and the teeth 94 so that with the plate 97 in the lower position, Figs. 4 and 6, the pawl 91 is prevented from engaging the teeth 94, but when the plate 97 is shifted upwardly as in Figs. 2 and 5, the pawl 91 will be permitted to engage the teeth 94.

A manual means also is provided for controlling the driving of the spools so as to obtain a winding of the ribbon onto the spool containing the greater portion of the ribbon. Pivotally connected to the left hand member 97 at 109 and to the frame piece 84 at 111 is a manual lever 112, the operation of which will disengage the feed pawl 91 from the teeth 94 of one spool and engage the other feed pawl with the teeth of the other spool.

' (not shown) similarly has a loose pin connection 117 with a lever 118 disposed on the right end of the cross shaft 116 adjacent the plate 97 for the right hand spool feeding mechanism so that the pins 113 and 117 are approximately 180 apart with respect to the cross shaft 116. When the left hand plate 97 is shifted upwardly, as in Figs. 2 and 5, to engage the left hand pawl 91 with the ratchet teeth 94 of the left hand ribbon spool 83, the cross shaft 116 is rotated in a clockwise direction by means of the pin 113 and the lever 114 to shift the right hand plate 97 downwardly by means of the lever 118 and the pin 117. This disengages the right hand pawl 91 from the ratchet teeth 94 of the right hand spool 83 and renders the right hand spool free-running.

In order to hold the plates 97 in their alternate shifted positions, the lever 118 is provided with an arm 119 which is engaged by one branch of a toggle spring 121,

arcanes justing screw 32 in conjunction with the thickness of a selected washer or shim 74 will determine the fluid pressure required thus to reciprocate valve member 14 to admit fluid pressure past such bevelled contour. Of course, the opposed surface of bore 13 may be contoured in the regions adjacent such inlet ports to determine the change in rate of fluid flow as the valve member is reciprocated instead of bevelling valve member 14 as shown, or both may be contoured.

The operation of my nozzle may now be understood, being generally similar to that described in my aforesaid Patent No. 2,656,218 and my tro-pending application Serial No. 333,569. Fluid such as liquid fuel enters the nozzle from the fuel manifold and is discharged through exit orice 12 into a relatively low pressure exterior chamber. Since inlet ports 18, 19 and 20 are ordinarily always open, uid pressure in inlet 11 is exerted both against the end of valve member 14 and also against the inner surface of vtappet valve member 27 and when such pressure reaches a sufficient point as determined by preset compression spring 34, such valve members 14 and 27 will be shifted in unison to open exit orifice 12. The fluid from channels 15, 16 and 17 passes through helical swirl grooves 24 to enter swirl chamber 26 and pass through the exit orifice in the form of a spray cone. Such spray cone is formed even when exit valve member 27 is only very slightly opened inasmuch as inlet ports 18, 19 and Ztl are nevertheless normally wide Iopen and thereby admit substantial lluid pressure to chamber 26.

When the uid pressure bearing against valve member 14 is effective to shift the same to uncover annular inlet port 42, additional fluid flow is now admitted to the remaining helical grooves 24 and delivered to swirl chamber' 26. lt will be appreciated that the fluid pressure bearing against the end of valve member 14 is principally effective in controlling the reciprocation of both valve members (through the intermediary of rod 29) inasmuch as the effective area of exit valve member 27 subject to fluid pressure thereagainst is much smaller and so of relatively little consequence. The spinning inertia of fuel particles in the envelope formed at the opening of exit valve 27 causes such particles to break away and disintegrate the envelope into a finely atomized mist which then further disintegrates into a relatively dry vapor.

Constricted helical channels 24 prevent a high fluid pressure from developing in swirl chamber .26 when the exit valve has been thus initially rather widely opened, and accordingly the initial fluid discharge of the nozzle will be at a relatively low rate. Such constricted helical channels likewise ensure that substantial intake pressure is maintained against regulator valve member 14.

As the rate of fuel flow is increased, regulator valve member 14 is gradually shifted from left to right as viewed in Figs. l-3 and 10-12, bringing the bevelled shoulder `of the same past the edge of annular inlet port 64 (Fig. l2). Fuel accordingly enters such port to an increasingT extent as the valve opens and passes therefrom through channels 555-63 inclusive and swirl slots 66 to swirl chamber 26 and thence out orifice 12. Exit valve member 27 has, of course, been correspondingly opened as regulator valve 14 was opened, due to reciprocation of resilient rod 29 connecting such two valve members. There continues to be a certain amount of fuel flow through channels -17 and channels 36-41 and spiral passages 24, but this soon becomes relatively inconsequential when compared to the very much larger llow entering through port 64 and thence passing through channels 55-63.

The bevel or contour 73 of valve member 14 will ordinarily be selected so that at maximum rated fuel flow the pressure drop between port 64 and swirl chamber 26 will be as low as possible and still afford sufficient swirling action through slots 66 to provide satisfactory atomization of the fuel at the orifice. Such bevelled contour need not necessarily be a straight line and other curves may be employed when suitable. The swirl slots 66 afford a result at higher rates of flow similar to that of helical passages 24 at low fuel llow, but the pressure loss through slots 66 is much less since they are of relatively large cross-section.

lt will be seen from the foregoing that l have provided a fluid pressure responsive nozzle having a set of normally open ports 18, 19 and 26 in communication with the swirl chamber immediately upstream of the exit orifice 12 and a plurality (in this case, two) of sequentially valved ports for admitting increased fluid flow to such swirl chamber in response to increasing inlet pressure. By this arrangement I have succeeded in considerably extending the range of fluid flow obtainable while maintaining at least the minimum velocity in the swirl chamber effective to afford satisfactory atomization of the fuel passing through exit on'ce 12. At the same time l avoid the production of too high a velocity ilow through the channels within the nozzle leading to such swirl chamber. A ratio of maximum flow to minimum flow of 87 to l is readily obtainable with my new construction while thus affording proper swirl chamber velocity both at maximum flow and minimum flow. Consequently, an engine utilizing my new nozzles may be throttled up or down for precise control without the necessity of cutting additional nozzles in and out. If desired, eyen more precise control may be obtained by providing additional channels and ports sequentially opened as valve member 14 is recipro-cated.

is best shown in Fig. l, the edges of ports 42 and 64 are very close together, and also port 4.2 is very narrow where it enters bore 13, preferably only a few thousandths of an inch wide, so that in case the Wire connector rod 29 should fail (with the loss of exit valve member 27) the regulator valve member 14 will need to move only a short distance under the inluence of the relaxing spring preload in order to close both ports 64 and 42. Ports 42 and 64 may desirably be spaced only a few thousandths of an inch apart, the space therebetween preferably not exceeding eight thousandths of an inch for a common size of jet engine nozzle, and the Width of the opening of port 42 may likewise desirably not exceed eight thousandths of an inch in such case. Opening movement of regulating valve member 14 is thus effective to bring into use the second set of normally closed passages promptly after opening the lirst set, under influence of fluid intake pressure. Obviously the passages may be subdivided as convenient if symmetrically arranged to aord a balanced lluid llow. Thus, there is a normally open passage (subdivided into 15, 16 and 17) leading to the swirl chamber through the small helical slots 24, a normally closed passage of larger capacity (subdivided into 36-41) also leading to the swirl chamber through helical slots 24, and a still larger normally `closed passage adapted for subsequent opening by reciprocation of valve member 14 (subdivided into 55- 63).

Referring now to Fig. 13 of the drawing, another embodiment of my invention is there illustrated comprising an open orifice form or nozzle generally similar to that above described but without provision of an exit orifice valve member. Thus, inner end member 75, preferably having a reduced neck 76 extending through and slightly beyond the open end orifice 12, serves to close the bore `13 of member 9 except for a small vent passage 77 leading to the exterior of the nozzle. If desired, member 75 may be formed Without the neck 76, otherwise being similarly constructed and operative. The intake end lll of the nozzle will normally be in communication with the combustion chamber of the engine or other external environment through the open exit orifice 12. The size of such orice may be somewhat more restricted than when a tappet valve member protrudes therethrough. A snap ring 78 may desirably be employed to ensure that valve member 14 does not reciprocate too far to the left as viewed in Fig. 13. As shown in such figure, spring 34 is compressed so that fluid is escaping through both ports 42 and 64. Shim 74 will be selected, however, so that under normal conditions with minimum intake pressure, valve member 14 will close both such ports but will not close port 18. There will consequently normally be a very slight escape of iiuid through exit orifice 12 when the intake end pressure is very low. While this form of nozzle obviously does not include various advantageous features of the closed orifice type of nozzle above described, nevertheless it is capable of delivering a uid spray over a broad range of fiow and will be adequate for some purposes.

Other modes of applying the principle of the invention may be employed, change being made as regards the details described, provided the features stated in any of the following claims or the equivalent of such be employed.

I therefore particularly point out and distinctly claim as my invention:

1. In a nozzle having an exit orifice, a swirl chamber of fixed dimensions immediately upstream of such orifice, a small passage leading from the intake end of said nozzle to such orifice, two larger passages leading from the intake end of said nozzle to such orifice, an exit valve member normally closing such orifice, a regulating valve member operative sequentially to open said two larger passages in response to increase in fluid intake pressure, said small passage being normally open, and means connecting said exit valve member and regulating valve member for reciprocation in unison, said exit valve member being arranged upon reciprocation to open such exit orifice before said regulating valve opens the rst of said larger passages.

2. In a nozzle having an exit orifice, a normally open passage leading from the intake end of said nozzle to such orifice, a plurality of normally closed passages leading from the intake end of said nozzle to such orifice, an exit valve member normally closing such orifice externally thereof, a regulating valve member operative sequentially to open said normally closed passages in response to increase in uid intake pressure, and means connecting said exit valve member and regulating valve member for reciprocation in unison, said exit valve member being arranged upon reciprocation to open such exit orifice before said regulating valve opens the first of said normally closed passages.

3. In a nozzle having an exit orifice, a normally open passage leading from the intake end of said nozzle to such orifice, a plurality of normally closed passages leading from the intake end of said nozzle to such orifice, an exit valve member normally closing such orifice externally thereof, a regulating valve member operative sequentially to open said normally closed passages in response to increase in fluid intake pressure, means connecting said exit valve member and regulating Valve member for reciprocation in unison, and resilient means urging said exit valve member to closed position thereby likewise to close said normally closed passages, said exit valve member being arranged upon reciprocation to open such exit orifice before said regulating valve opens the first of said normally closed passages.

4. In a nozzle having an exit orifice, an exit valve member normally closing such orice externally thereof, a plurality of passages leading from the intake end of said nozzle to such orifice, a regulating valve member mounted for reciprocation toward such exit orifice in response to iiuid intake pressure sequentially to open said passages to permit increasing flow of fluid to such orifice, and means connecting said regulating valve member and exit valve member for reciprocation in unison to control the position of said exit valve member relative to the rate of fluid flow.

5. In a nozzle having an exit orifice, a swirl chamber immediately upstream of such orifice, an exit valve member normally closing such orifice externally thereof, a small passage leading from the intake end of said nozzle to said swirl chamber including a helical terminal portion adapted to deliver a swirling fiow generally axially of said chamber, a second larger passage leading from the intake end of said nozzle to said swirl chamber including a helical terminal portion adapted to deliver a swirling flow generally axially of said chamber, a third still larger passage leading from the intake end of said nozzle to said swirl chamber including a terminal portion generally tangential to said chamber to deliver a swirling flow thereto, a regulating valve member upstream of said swirl chamber operative sequentially to open said second and third passages by movement toward such exit orifice in response to increase in fluid intake pressure, said first small passage being normally open, and means connecting said exit valve member and regulating valve member for reciprocation in unison, said exit valve member being arranged upon reciprocation to open such exit orifice before said regulating valve opens said second passage.

6. In a nozzle having an exit orifice, a normally open passage leading from the intake end of said nozzle to such orifice, a plurality of normally closed passages leading from the intake end of said nozzle to such orifice, an exit valve member normally closing such orifice externally thereof, a regulating valve member operative sequentially to open said normally closed passages in response to increase in fluid intake pressure, the valved inlet openings of said passages being closely adjacent and not more than eight thousandths of an inch apart, and means connecting said exit valve member and regulating valve member for reciprocation in unison, said exit valve member being arranged upon reciprocation to open such exit orifice before said regulating valve opens the first of said normally closed passages.

7. In a nozzle having an exit orifice, an exit valve member normally closing such orifice externally thereof, a plurality of passages leading from the intake end of said nozzle to such orifice, a regulating valve member spaced upstream of said orifice mounted for reciprocation in response to fluid intake pressure sequentially to open said passages to permit increasing iiow of iiuid to such orifice, the valved inlet openings of said normally closed passages being extremely close together for prompt sequential opening and closing by said regulating valve member, and means connecting said regulating valve member and exit valve member for reciprocation in unison to control the position of said exit valve member relative to the rate of fiuid flow.

8. The nozzle of claim 7, wherein the inlet opening of the first of said normally closed passages to be uncovered by said regulating valve member does not exceed eight thousandths of an inch in width longitudinally of said nozzle.

9. In a nozzle having an exit orifice, a swirl chamber immediately upstream of such orifice, a small passage leading from the intake end of said nozzle to said swirl chamber including a helical terminal portion adapted to deliver a swirling iiow generally axially of said chamber, a second larger passage leading from the intake end of said nozzle to said swirl chamber including a helical terminal portion adapted to deliver a swirling liow generally axially of said chamber, a third still larger passage leading from the intage end of said nozzle to said swirl chamber including a terminal portion generally tangential to said chamber to deliver a swirling flow thereto, and a regulating valve member operative sequentially to open said second and third passages in response to increase in fluid intake pressure, said rst small passage being normally open.

l0. In a nozzle having an exit orifice, a swirl chamber immediately upstream of such orifice, a small normally open passage leading from the intake end of said nozzle to said swirl chamber including a helical terminal portion adapted to deliver a swirling ow to said chamber, a plurality of normally closed passages leading from the intake end of said nozzle to said swirl chamber each of which includes a helical terminal portion adapted to deliver a swirling flow to said chamber, and a regulating 5 valve member operative sequentially to open said normally closed passages in response to increase in uid intake pressure.

References Cited in the le of this patent UNITED STATES PATENTS FOREIGN PATENTS Germany June 14, 1930

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