US1525611A - Fuel pump for internal-combustion engines - Google Patents

Description

L. ILLMER FUEL PUMP FOR INTERNAL COMBUSTION ENGINE S Filed Dec. 7, 1921 3 Sheets-Sheet 1 bQa Feb. 10, 1925.

7 1,525,611 L. ILLMER FUEL PUMP FOR INTERNAL COMBUSTION ENGINES A yam/5353 LL Mr; L

Filed Dec; 7,1921 3 Sheets-Sheet 2 J? INVENTOR 5 Feb. 10, 1925.

1,525,611 L. ILLMER FUEL PUMP FOR INTERNAL, COMBUSTION ENGINES F] I N l g E I "I P I ME ,1 I-- E IQ; *i'i f 5? gal I as I! O 55 o 55 O y I 3 26 a6 a l u Q 0 IL 3: J0 5/' o o /ok J L )l 1 7 55 l} ib r H E J u u 6 Fun; WFTNESSES1- INVENTOR 4 after.

Patented Feb. 10, 1925.

UNITED STATES PATENT. OFFICE."

LOUIS-'ILLMER, or oonrnannnnw YORK.

FUEL PUMP roe INTERNAL-COMBUSTIONENGINES.

Application filed December 1,1921. Serial No. 520,493.

which the following is a specification.

My invention relates-particularly to improvements in high pressure injection pumps for so-ealled solid injection liquid fuel ongines, and its object is to provide a device which without the use of compressed air,

maintains a high injection velocity through the spray nozzle of an'internal combustion engine regardless of the engine speed.

I he primary aim of this device is to break up the injected liquid fuel into a finely atomized formation so that the increased surfacing will admit of rapidly and more perfectly mixing such injected fuel with all the available cylinder air, thereby improving the combustion process and augmenting the power 'apacity of a given engine cylinder.

Another object is to provide a directly reversible fuel pump that will run an injection oilengine equally well in either direction of rotation without resorting to-a reverse gear for shifting the phase of the plunger movements in relation to the engine piston movements. 1

Still another object is to provide a device as above described in which one pump.

plunger running at a multiple speed ratio with respect to the engine crankshaft is capable of successively serving a plurality of power cylinders.

The present invention also embodies improvements in the spring drive or plunger impulsion element of this type of fuel pump, and in the co-ordination of the. required valve and spray nozzle parts with respectlo the fuel pump, and it furthermore comprises a spare pump means and various other features of structure and organization, all of which will be setforth in detail herein- Refereuce is had to the accompanying two sheets of drawings which illustrate examples of various forms of my invention; like characters of reference indicate like parts in the several views, and in which drawings:

Fig. 1.. is an elevational end view of my impulsion fuel pump eqnipt with a reduction gear for actuating thedischarge valves thereof.

Fig. 2., is an elevatioualside view of the pump illustrated in Fig. 1., showing a partial sectional view of thepumpblock as taken on. the line 1-1 of Fig. 1. v

Fig. 3., is a sectional detail of the mechanically operated discharge valves as taken on the line of Fig. 4-,, is an elevational view of the assembled pump in section as taken along the line of Fig. 3.

Fig. 5., represents a detail of a toggle linkage adapted to adjust the regulation and to. control the reversing of the pump shown in Fig. i p

Fig. 6., is a sectional view through the power cylinder as taken along the line (r-(i of Fig. 7.

Fig. 7.. represents an elevational side view of a four-stroke oil engine equipt with my fuelpump. in which the multiple discharge valves of the pump are independently actuated from the camshaft of the engine.

Fig. shows a sectional detail of the combined spray and discharge valve casing as taken along the line 4- 1 of Fig. 6.

Fig. 9., represents a further del ail of Fig. 8.. as taken along the line 55.

Fig. 10, represents a control gear detail for cutting out of service a defective main fuel pump and in its stead of quickly throwing into service a duplicate or spare unit.

Fig. 11, is a plan view of Fig. 10. showing the cross-connected delivery pipes between the main and the spare pumping units.

Referring first to Figs. 2 and 4.,' the numeral 10 represents a flanged pump brackct which is intended to be fastened to a convenient part of the engine; This bracket is provided with projecting ribs 10 carrying a pair of split bearings 11 for the .purpose of mounting the driveshaft 12, which shaft intended to be driven from the engine which it serves. The eccentric 13 mounted upon the drivcsluift 12, engages with the wristpin 16 and imparts reciprocating movement to the spring casing 14: in synchrmiism with the engine piston movements. and these parts taken together, constitute the 'rigid actuating partof-the impulsion fuel pump:

The said casing 14 is slidably mounted within the guide 15 which is preferably formed integral with the bracket casing-10. The plunger drive part 16 having a flanged portion 16 and an enlarged collar 16", is.

slidably mounted with respect to the casing 14. Thrusting between the flange 16 and the lower casing shoulder 14 is a relatively powerful primary drive spring 17*, while above said flange is mounted a similar secondary spring 17 thrusting against the shoulder lug, 14 and set to-act in opposition to the primary spring.

These o'pposeddrive springs are intended to be forced into place under a considerable initial tension, so that the flange 16 is normally made to assume the relatively fixed balanced positionwith respect to the rasing 14 that is indicated by dotted lines in Fig. 4., and it will be seen that the resilient member 17 and 17 serve as an impulsion drive for the plun or parts 16 and 16".- The extent to which t e drive flange 16 is intended to be displaced .out of its balanced position with respect to the casing 1 1 is -in- -dicated in Fi 4:. by the distance marked 7 multiplied by displacement distance will be a measure of the impulsi on energy that may be stored and subsequently released for impelling the driven.plunger part forward with respect to the casing movement.

The pump block 18 is preferably made of machinery steel and securely fastened to a projecting portion of the bracket casting 10. Within this block is mounted the reciprocating plunger 19, which is suitably sealed against pressure leakage by means of the packing 20 and this packing may be ad justed by means of the gland 21 The plunger 19 is intended to work reasonably free throu h said packing so as not to interfere un uly with the action'of the impulsion drive springs. 'The plunger is;

fastened into the drive part 10 so as virtual 1y to become an integral part thereof.

As is best shown in'Fig. 2., the pump block 18 is further provided with an automatic suction valve 22 which takes its fluid supply through the feed pipe 23. The pump block is furthermore provided with a pair of discharge valves 24" and 24*, either of which positively controls the pump delivery. Thesaid suction valve and the set of discharge valves communicate with the plunger bore through the common passage valves comprises a cam disc 26 which is .centered by the cam spindle 27 and slidably mounted for lateral' movement along the axis thereof. The spring 27- normal-ly thrusts the cam disc against the bracket cast.- ing 10 into the position shown by full lines in Fig." 2. The cam disc 26 is provided with a raised part 26 and an opposite depressed part 26 while between these parts the cam face is of 'cireular'contour. This cam is driven at half speed with respect "to the drive shaft 12 by means of a set of spur gears 28 and 28", the latter being shown as: an integral part of the cam disc 26.

This cam engages with a lever pa1t29 mounted on the fulcrum;29". The lever 'toe 29 isheld in enga ement with the cam face by a relatively stifi spring 30 and the movement imparted to the lever 29 is transmitted to the actuating spindles of the discharge valve by the tie rod 31.

The pair of bodies 32 and 32 which respectively mount the discharge valves 24: and 24", are of similar construction except that they are fashioned as right and left hand bodies as will appear from Fig. 3. Referring in detail to the sectional assembly of the removable left hand discharge valve shown in1Fig'.'-2., the body part 32 is provided with a threaded shank portion having an encircling ground seat 33 engaging with the pump block 18 and held in lace by the threaded shank nut 34. The s ank of this nut is enlarged at its lower end to form the annular seat 35 which also thrusts against the block 18 but acts counter to the to place the respective shank nuts in communication' with the pump chamber 25 so as to become a part thereof.

.VVithin the body part 32, an actuating spindle head 38" is rotably mounted and this is slotted to constitute the lip 39 which engages with the stem -of the discharge valve 2 1. This spindle is further provided with a reduced stem' part 40" extending through the tubular nut tl, the head of which nut bears'tightly against'the body 32 to make an hydraulic joint therewith.v The 'pose of opening thelattcr.

spindle shoulder 44 serves as aground annular seat which bears against the inner end of the tubular nut 41 and allows the spindle 38 to revolve with respect to the body part 32, The equalizing hole 45 throws the pump discharge pressure against'the rear. face of the spindle head 38 for the purpose of maintaining a pressure tight joint at the seat 4 t. i The outer or free end of the spindle stem 40 is provided with'a bell crank 42, one arm of which engages with the tie rod 31 while the other arm'connects with the ad jacent rocker 42 through the strap 43, whereby both spindles 40* and 40 are positivcly actuatedfrom the cam disc 26. As shownin Fig. 3, the discharge check valve :24 is preferably offset from the axis of the spindle 40 and slidably mounted with respect to the body part 32 to forma pres-- sure tight control for the oil discharge from the pump chamber. The lip Eli) of the oscillating spindle periodically engages with the free end of the stem of valve 24 for the pur- The spindle head 38 is also provided with a small hole drilled crosswise of its' axis to maintain i-ommunicat'ion between the discharge valve and the nozzle pipe 4'6": and in a twin cylinder engine this pipe leads directly to the spray nozzle of one power cylinder while the similar pipe. 46 is intended to serve the other cylinder.

Referring now to the control means for regulating the oil discharge from the fuel pump to the engine cylinders, the block'lS,- as best shown in Fig. 4., is provided with a bypass valve 47 having a seat ti' formed in a recessed portion of the block 18. Mounted wiihinsiu-h block recess is a spring 48 which thrusts against theplug nut 49' and serves to close the bypass valve. This valve is placed in communication with the plunger bore and the rest of the pump chamber through the passage 50. The stem of the bypass valve 47 is undercut just' below its seated head part so that when open, the valve may freelyvent the pump chamber into the return pipe 51, which may be con uccted to discharge into the supply pipe 23 if so desired. The stem of the bypass valve 47 is extended downward through the pump. block 18 and is sealed against leakage by the packing 52, the free end of the stem being formed into a tit 47 to engage with the floating lever 53. ,One of the lever ends rests upon the plunger drive collar 16" and reciprocatcd thereby, while the other lever end is fulcrumed in the stanchion 54 by means of the pin 54. This stanchion is slidably mounted within a portion of the bracket casting 10 and rests upon the control shaft 55, which is also slidably mounted but set to. move normally with respect to the stanchion axis.

As is best shown in Fig. 2., the control shaft is provided with'an actuating pin 55 and a recessed cam face 55 adapted to lift or lower the stanchion'54 in accordance with the lateral adjustment given to the sliding shaft 55. After the fulcrum pin, 54 has been raised to a predetermined height, the

flat portion of thecain face 55'. comes into action and this allows the control shaft 55 to be further shifted without augmenting the stanchion lift. When the shaft assumes this critical position, the overhung shaft toe 55 will have engaged with the edge of the gear. 28". Since this gear together with the cam disc 26 is slidably mounted on the spindle 27, any further movement of thecontrol shaft will ultimately cause the cam disc 26 to be shifted into the dotted position indicated in Fig. 2., without however'throwing out of mesh the gears 28 and 28". The raised cam lug 26 as also the depressed part 26" of the cam disc 26 are made relatively short as measured lengthwise of the spin dle 27, so that when shifted into thedotted position, the lever toe 29 will be'riding on a perfectly round portion of the cam-disc 26, and no inovementwill be imparted to the tie rod 31, thus disengaging the actuating gear of the positively operated discharge valves 2ft and 24*.-

Referring now to Fig. this detail shows a toggle link control mechanism for adjustably setting the position of the shaft The notched sector 56 is fixedly mounted on the fulcrum pin 57, while pivotably mounted thereon is a bell crank 58 comprising a latched adjusting lever and a link arm for the actuating toggle. The link strap 59 engages with the pin 55 so that any movement of the adjusting lever to either side of its central or stop position will cause the control shaft 55 to be drawn toward the fulcrum pin 57, W'hcn the control shaft is set in,the aligned toggle position as shown in Fig. 5., the toe 55 will cause the discharge. valve gear to be disengaged from the actuating cam '26 in the manner previously set forth.

Having thus described in detail the parts of the preferred form of my invention, the

manner in which said follows:

Assuming the parts to be in -the position show in Figs. 1 to 4 inclusive and with the parts operate is as spring casing-1 L moving upward and-the eccentric 13 approaching its upper or inner dead center position when rotating in the direction indicated by the arrows. then the plunger 19 will during its preceding downward st roke already have sucked a charge of oil into the pump chamber 25 through the suction valve 22. During suchsuction stroke, the negligible resistance of the plunger packing allows the drive flange 16 to remain in substantially its balanced po-,

-'sition witlrrespect to the casing 14.] As

I versal of movement promptly closese the automatic suctiom-valv'e 22 and thereafter this as well as the other pump valves remain closed until suclrtin'ie as the'eccentric 13 has almost completed its discharge stroke and reached a predetermmed position as mdicatedin Fig. 4.,- by the letter a.

kick and its' action is essentially as that more fully explained in my co-pend- Since during the stated period, none of the oil is allowed to discharge from the pump chamber, the effect of such initial lifting of the casing 14 is to hold the driven plunger part-16in a virtually stationary position except for plunger slip while the flange 16 is being displaced from its balanced position against the combined resistance of the impulsion springs 17" and 17" by an amount of deflection indicated in Fig. 4, by the letter K,,which inthe case illustrated is made approximately equal to the full eccentric travel, The dis lacement e termed the same K of the impulsion drive ma ing patent application Serial' No. 229,556. Such displacement not only stores impulsion energy within said drive springs but also sets up a relatively high' hydraulic pre sure throughout the pump chamber,

. passages as well as behind both of the closed discharge valves 24 and 24".

hen the eccentric 13 approaches the given position a, the cam lug 26 engages with the lever 29 to lift the tie rod 31 and shift the tiestrap 43 intoits leftward position b which in turn opens the discharge valve 24 against the existing chamber pressure; -Th1s valve controls the release of' the stored energy in the impulsion drive and when opened, the pump plunger is immediately impelledforward with respectto the'movement of the easing 14, and the pump sends forth its delivery through the pipe 46 and thence to the spray nozzle 0 the engine 0 linder.v The released fplunger will surge orward as rapidly as the unbalanced spring force iscapable of crowding oil through the restricted area of the spray nozzle and it will be seen that the impulsion ,drive serves to maintainjhigh' nozzle velocity 'until the balanced or equilibrium position between the primary and secondary drivesprings is again restored.

It is intended that the drive springs be made sufiiciently powerful to completely inject the fuel into the engine cylinder dur-' ing .a comparatively small angular travel of the eccentric and prior to the closure of A the discharge valve 24.

explained, the suction valve 22 is again.

opened by the return or downward stroke of the plunger and a fresh charge of oilis drawn into the pump chamber. During the nexttsucceeding upward travel or discharge stroke of the casing 14, this will again cause the'impulsion spring drive to be displaced and charged with energy in the manner previously described, and by the time the eccentric 13 reaches the position a for a second time, the cam de- .pression 26" located directly opposite to the cam' lug 26 which is running at half-speed with respect to-the drive shaft 12, will have come into engagement with the lever toe 29*, which in turn allows the spring 30 to shift the strap 43 into its rightmost position C and open the dischar e valve 24 without however, disturbing tie adjacent seated valve 24. As a result, the pump will now deliver through the pipe 46 and-'send forth oil to the spray nozzle of the alternatecylinder which is intended to be operated from a crank setat a suitable angle with respect to the crank used for the cylinder that is served by the discharge valve 24.

As applied to the case of a twin cylinder four-stroke oil engine, the pump eccentric 13 may be driven at crankshaft speed when the valve gear for the adjacent power cylinders is set to alternately fire the cylinder charges. \Vhen the directly reversible fuel pump shown in Figs. 1 to 4., is made to serve such an engine, the position of the lUU cam disc 26 is preferably set in phase or setting indicated, the cam disc 26 used foralternately opening the discharge valves 24* and 24 is still correctly timed .to inject a little in advance of the proper dead center position of the respective twin power cylinder; when running the engine in either direction of'rotation. It will be seen therefore that the impulsion plunger drive makes it possible to carry the-pump eccentric up close to its dead center position prior to discharge valve opening and the energy that has in the mean time been stored within such drive may still be instantly released by opening the discharge valve to impart a rapid kick-like movement to the plunger.

this fuel pump with- In this improved pump, the plunger movement is made entirely independent of the slow moving actuating gear parts, a feature which affords some important advantages in starting up oil engines and for variable speed injection engines such as are essen' tial for automotive work. A further feature of this pump resides in the construction details of the discharge valve body 32 and its associated parts. In-

the construction shown, the stem of the check valve 24 is guided in the body part 32 so that the valve head may accurately align itself with respect to-its ground seat, and when closed. the free end of the stem tit may be held out of engagement with the spindle lip 39 to insure tight seating of the check valve. It is also pointed outthat the head portion of the valve 24 can be kept relatively small in size so as to open against a high chamber pressure without undue ac tuating forte.- Furthermore the oscillatory movement given the spindle head 38 to open the valve 24 does not in any way interfere with the measured pump displacement of the impelled plunger 19.

Referring-now to the action of the control means for regulating the pump and for preventing any oil being sent forth into the power cylinders of a reversing oil engine while the adjusting lever for such control means is set in its stop position. In Fig. 5., the toggle lever 58 is shown asset in such stop position with thecontrol shaft 55.

shifted to its furthermost leftward'position, thus putting the pin 55 into the position at for which the shaft toe 55 has disen gaged the actuating gear of the discharge valves 24 and 24", as previously explained. In addition, the stanchion 54 will have been raised to ride upon the fiat cam face 55", which in turn causes the floating lever 53 to hold the bypass valve '47 oil its'seat for all positions of the plunger part 16 It will be seen therefore that when the lever 58 is set in its stop position, this not only prevents opening either of the discharge valvesbut at the same time breaks the-pressure in the pump chamber and thus doubly insures against: any oil discharge into the engine cylinders. l

The latch notches in the sector 57 correspond to the respective control positions d to g of the pin 55. \Vhen the lever 58 is thrown into the first notch to either side of its aligned or stop position, such movement may be made to throw starting air into the power cylinders and the pin 55 will then assume .the position 6 while the cam disc 26 will again be back in its normal position as shown by full lines in Fig. 2., but the stanchion 54 will still be raisedsufficiently to hold open the bypass 47.

Aswill be more fully explained presently, the starting air control may be made interthen-rides upon the curved cam face 55 and the fuel pump discharge-will be correspondingly increased until finally. when the pin 55' reaches'its extreme position g, th

stanchion 54 will be riding on the lowest portion of the. curvedface 55*. quence the kick of the plunger 19 must raisethe floating lever 55 to its highest position as shown by dotted lines in Fig. 4..

before it lifts the bypass valve '47 off its seat. For any intermediate position of the control shaft 55, the increment of plunger movement that is allowed to discharge oil through either of the valves 24*. and 24" is "from its aligned position, the stanchion 54 As a conseaccuratelv fixed by the setting of the control shaft 55' The lever 53 periodically lifts the bypass valve 47 in a definite but alterable point in the path of the impelled plunger part 16* and thereafter interrupts the further delivery of oil through the particulardischarge valve that may have released the impulsion drive.

Furthermore the use of the toggle linkage shown in Fig. 5;, represents an element that may be various incorporated in an engine reverse gear, since its underlying principle is to insure cutting oft the .oil pump delivery to the engine cylinders whenever the adjusting lever 58' passes through its stop or aligned position and to gradually increase the pump delivery .in a fixed proportion to the -'movement given the toggle to either side of its aligned position.

. As a further'modification of the described control features of my fuel pump, it is pointed out that the -multiple discharge valve bodies32 -and 32 together with their drivin mechanism may, with advantage, be entirely detached from'thepump block 18 and incorporated with other parts of the engine valve gear in the manner shown in Figs. 6 and 7. These views represent a twin cylinder four-stroke solid injection oil en gine, in which the two throw crankshaft 60 is provided with a spiral g'earfil for driving thevertical shaft 62- at engine speed. The

upper end of this shaft is further provided with a set of miter gears 62 which also drive the fuel pump 64 at engine speed. In this particular application, the fuel pump proper need only comprise the essential elements shown in Fig. 4., with the addition of the suction valve 22 shown in Fig. 2., while the plural. discharge valves 24 and 24 required to release the impulsion drive of such pump 64 and the actuating gear for said valves, are placed close up to their respec tive power cylinders and incorporated as a part of the valve gear of the engine proper in the conventional manner by means of the reverselever 66. In the position shown in Fig. 7., this lever stands in its mid or stop position, for which the various ahead and astern cams on the shaft 63 are set to straddle their respective bellcrank levers so as not to impart movement to any of the cam actuated valves. 1

The similar equipment of each of the power cylinder parts is designated by the respective subscripts a, and b as applied to the 'part numeral. Thus the starting valve 67 of the one cyl'hider is actuated bythey separate ahead and astern cams 68 while the axis of the exhaust valve 76*. as-

is best shown .in Fig. 6.. is set inclined with respect to the power cylinder axis and actuated by the separate ahead and astern cams 69. Lastly, the combined discharge and spray valve casing 70*, which functions in a manner similar to the valve 24 shown in Fig.

, 2., is-also actuated by the separate ahead and astern cams 71, either ofmvhich cams may at will be thrown into engagement with the tie rod 72*, which is similar to the rod 31 of Fig. 1,, and is intended to be held against-the cams 71 by means of a suitable spring (not' shown). As will be seen from Fig. 8., the tie rod 72 oscillates the spindle'40' mounted-in the casing and thus positively opens the discharge valve 24 in a manner identical with that previously described for the similar parts shown in Fig. 3.

The fuel pump 64 'is provided with a single plunger-wand a delivery pipe 73 having distributing branch pipes 46*. and 46 which are in common communication with' the connected pump chamber passages 25 and 50 and these branch pipes deliver the pump discharge to the respective control 24 and 24 in the casings 70 and 70",

which check valves are again made to open against the pressureexerted by the impulsion plunger drive -of the ,pump 64.

-; The oil after leaving the cont-rolof the opened discharge valve-2 P- passes a small c eck valve 74 on its way to the spray I nozzle 7 5 which injectsinto the power cyl- 4 spray nozzle from the axis of the drumshaped combustion chamber 77%,; which chamber encircles the axis of the exhaust tions as shown in Figs. 6 and 7., and that I the eccentric of the fuel pump 64 is set to align with the same so as to operate its spring casing 15!.- in synchronismwith the power piston movements, then in order to start the engine, the reverse lever 66 is pulled out of its mid or stop, position into .the first latch notch to either side of the stop posi tion depending upon the direction of rotation desired. This serves to put into action the corresponding set of air starting cams 68 and 68 and thus successively throws properly timed compressed air on the pistons to start the-engine in the customary manner.

A further movement of the reverse lever 66 .into its last notch will serve to throw said air starting cams out of engagement and subsequently to throw into action the fuel discharge cams 71 and 71". In the mean time the plunger of the fuel pump 64 will have been put into operation and'this will send forth pressure impulses into the distributing branch pipes 46 and-46 which impulses are properly synchronized with the alternate openings of the pump discharge valves 24 and24". For the crank settings shown, it is intended that one of the power pistons will be completing its exhaust stroke while the other reaches the end of its compression stroke, the corresponding settings of the valve casings 71 and 71 being such that fuel is admitted only into the particular cylinder that is under compression. The

other discharge valve does not function therefore until the next following crank revolution, with the result that properly timed fuel is injected first into one and then into the other of the power cylinders.

As stated, the pump 64 is still provided with the control elements 53, 54, and 55,-and

- this admits of simultaneously regulating the pump to both power cylinders by the described action of the single bypass. valve t7.

It will be seen therefore that byuneans of this fuel pump and without requiring any substantial modification in the cam shifting arrangement commonly used in the conventional reversing four-stroke engine, the control of the distributed fuel pump'discharge valves become centralized inthe reverse lever 66. Furthermore the fact that the fuel pump is run at double speed and distributes the oil delivery into two or more power cylinders materially reduces the installation cost and makes for an effective and compact fuel injection means for. direct injection oil'engines.

-The further fact that the release of the energy stored behind the impulsion plunger isunderthe direct control of any one of the several mechanically operated discharge valves, allowsthese control elements to be placed. at a distance from the pump block and in close proximity to their respective spray nozzles, and further allows such control elements to be independentlyor selectively operated from the particular engine cylinder parts which the respective discharge valve is intended to serve.

In case the geared type of pump shown in Figs. 1 to 4 inclusive, is to be used for a multicylinder two-stroke oil engine, the pump drive shaft 12 may be'run at twice crankshaft speed and the one pump made to feed alternately into any twopower cylinders whose cranks are set oppositely, i. e.

180 apart. It will also be apparent that in case it should be preferred to operate the pump drive shaft for a two stroke engine at crankshaft speed, this'would elimi-- nate the reduction gears 28% and 28 as well as one of the discharge valves 24 and allow the remaining valve to be driven from a cam or an eccentric mounted upon the drive shaft 12.

In addition to providing a simple and compact fuel pumping means for serving a plurality of such cylinder'nozzles, the cen-' tralized control feature of this pump,

which essentially comprises the control shaft for adjusting the common bypass valve 47 as actuated by the plunger movements,

also affords another important advantage,

especially when applied to the case of marine oil engine drives. Suchcommon con trol for variably interrupting the distributed pump discharge together with the de-' scribed means for completely disengaging the discharge valve actuating mechanism,

permits of quickly cutting out of service at will a main fuel pump constructed in ac-- cordance with Figs. 1 to 5, and in its 'place, of instantly throwing into service'a duplicate or spare fuel pump thatis" purposely kept running in unison with the mainfuel pump. Thus in the event 'of-either pump becoming defective, the duplicate pump may be thrown into service to replace the functions of the otherand so maintainthe delivery of fuel to the .respective' poiver cylinders.

A shown in Figs. 10 and suit can readily be attained with, but slight modification in the parts previously de; scribed in connection with Figs. 1 to 5. Two independent adjusting levers58 and 58 are provided and these are mountedl upon a common fulcrum pin 57. The toggle link 59, of one such lever is intended to shift the control shaft 55, .of the main fuel pump designated as I, while the alternative toggle link 59, attached totheother ad]ust1ng lever serves to shiftthe control shaft 55 of the duplicate or.spare pump 'II. When both control levers 58, and 158 are set into their mid or stopposition as shown, the respective actuating cams '26,, and' 26 will then be shifted into the dotted position indicated in Fig. 2., and-thus disengage the actuating gears of both pumps from their respective discharge valves in the manner already set forth.

Furthermore the plural delivery pipes. of

the main fuel pump are separately crossconnected with the corresponding deliverypipes of the duplicate or spare pump so that one set of such. pipes may deliver to their common spray nozzle in the manner indicated in Fig. 11.. From the main pump I.

the discharge pipe 46 delivers to the spray nozzle in the-one power cylinder designated as 77*, while its other discharge pipe 46" delivers to the spray nozzle '15 in the second similar cylinder 77. From the spare pump, the discharge pipe 46 likewise delivers-to the spray nozzle 75 through its nozzle checkvalve 74, while the discharge pipe 46f delivers to, the spray nozzle 75" through its check valve 74.

When such duplicate pumps are equipped with the cross-connections indicated, eitherofthe said control levers 58, or 58 'may be moved out of its stop position provided the other is kept'therein, and thiswill cause the displaced cont-rol lever of the one pump is first broughtback to its mid or aligned toggle position to cut off the oil discharge to "the engine cylinders-after which the alter native central lever may be moved out of its mid position and this Will immediately cause the spare pump I to resume the delivery of fuel to the several power cylinders. If so desired; the duplicate control levers 58, and 5851112. be interlocked in suchfashion that onlyone of said levers at a time may he 7 moved out of its respective stop or mid 11.,'. this reposition.

" Since the fuel pump "constitutes the heart"- -'offa-'direct1injection oil engine and its proper 'functioning is absolutely essential to reliable operation, it will be seen that such duplication of this relatively inexpensive but vital adjunct as provided for in the present invention, materially contributes to the attainment of dependable oil engine service.

In view of the cited modifications, it-will be understood that I'do not wish to be limited to the particular construction set forth and scope of the present invention or destroying any of the advantages contained in the same, heretofore described and more particularly defined in the appended" claims.

. Claims. 1. In a fuel pump, an intermediary impulsion drive for the plunger comprising a reciprocating actuating ;me'mber and a driven member slidably mounted with re- S act to said actuating member, a primary rive spring thrusting betweensaid members, and a secondary drive spring also thrusting between said members but set to act in opposition to the first named spring.

2. In' a fuel pump, an intermediary impulsion drive-for the plunger comprising a reciprocating spring casing having shoulderlike lugs near the ends thereof, a' plungerdrivehaving a flange-like part slidably mounted with respect' to said casing, and

drive springs mounted on each side of said drive flan e and respectively thrusting against said casing lugs. p v

3. In a liquid fuel pumpeomprising a reciprocating actuating part and a driven plunger part slidably mounted with respect to the actuating part, a primary drive spring thrusting between said parts and a secondary spring also thrusting between said parts but set to act in opposition to the primary spring to constitute a floating impulsion drive for the plunger part, means for forcing the plunger part out of its balanced position with respect to the actuating part, and means for subsequently releasing such displaced impu 'on drive to impell the plunger onward and ischarge-liq'uid fuel from the pii'nijizhamber. g a

4. a pump provided with suction valve and a positively opened ischarge valve, aieciprocating actuating member and a driven plunger member slidably mounted with respect to the. actuating member, a primary spring and a secondary spring actmg between said members and each set to thrust in opposition to the other and serving as a floatin impulsion drive 'forsai plunger mem er, meansfordisplacing said plunger member out-of its balanced position y the movement of'said actuating member,

I and means for opening said discharge valve to; release said impulsion drive and,impel the -plunger member onward with respect to the actuating member.

5. In a:pu1np having a rotating drive shaft ,'-'a reciprocating. art actuated from the drive shaft and a riven plunger part with an impulsion sprin drive acting between said parts,'means I017 storing energy within said drive during a portion of the discharge stroke of the reciprqcating part,

a plurality of positively opened discharge valves each adapted toindependently-control the release ofsaid energy, a cam and areduction gear operating said cam at a slpwer ener within said drive durin a ortion of each discharge stroke of the actuating part, a plurality of positively opened discharge valves each adaptedto independently control the release of said energy, means for selectively opening any one of said discharge valves in s nchronism with the actuating part movements, .3. common bypass valve adapted to interru t the discharge through said opened Va ve, and control means including a floating lever serving to open said bypass valve in a definite but alterable point in the path of the impelled plunger part.

'7. In a pump,- comprising a reciprocating actuating part and a driven plunger part with an impulsion spring drive acting be tween said parts, means or storm energy within said drive during a portion of the discharge stroke of the reciprocating part, a

positively opened, discharged valve controlling the release of said energy to impel the plunger onward, means for opening said discharge valve, a bypass valve adapted to interrupt the flow through such opened discharge valve, a floating lever adapted to open said bypass valve, said lever having an 'end portion actuated in unison with the plunger, a control shaft means engaging with the other. end portion of sa d lever, and

a toggle linkage for adjustably setting the. position at which said bypass valve is opened y'said floating -lever. 8.- In a pump comprising a reciprocating plunger,-a chamber and, a fluid supply therefor, a positively opened discharge valve, means for opening said valve in unison with the'plunger movements, a bypass valve between the pump chamber and the fluid supply serving to interrupt the flow through said discharge valve, afloating lever adapted to open said bypass valve said lever having an end portion actuated'in unison with the plunger, a :control shaft means engaging with the other endportio'n-of said lever, and a togglek-for adjustably setting the controlsha f and fixing the position at which said bypass valve is opened, said valve, a. control shaft means adapted to regulate the pump discharge, ato'ggle linkage for adjustably settin'gthe control shaft,

said shaft being further adapted to disengage the discharge valve actuating means when said toggle links "are moved through their-aligned position. A

10. In a reciprocating pump comprising a chamber, a plunger and adischarge valve opening inwardly into said chamber, an actuating spindle provided with an annular seat and a lip means adapted to open said valve against chamber pressure, a' tubular thrust member surrounding said spindle and engagingwith the annular seat thereof to form a rotary 'hydraulic joint, and means for positively actuating said spindle in unison with the plunger movement&

11. In a reciprocating pump comprising a chamber, a plunger and a plurality of discharge check valves opening into said chamber, independent actuating spindles for each of the several valves said spindles being each provided with an annular seat, separate tubular thrust members surrounding each of saidspindles and engaging with the respective annular seats thereof, and actuating means for selectively opening any one of said valves against chamberpressure.

12. In a reciprocating pump comprising a chan'iber, a plunger and a discharge check valve, a body part. an actuating spindle dapted to open said valve against chamber 1111, a head portion for the spindle .ng an annular scat therefor, a tubular seat member engaging with the body part and forming a rotary hydraulic joint with said spindle seat, andmeans for actuating said spindle in unison with the plunger movements. V

13. In a reciprocating pump comprising a. plunger, a pump block having a recessed chamber therein, a discharge valve opening into said chamber, a removable bod part having an annular seat surrounding'said valve axis adapted to bev r against the pump block and enclose said chamber recess, an actuating spindle mounted in said body part serving to open said valve against chamber pressure, and means holding the body part against said block to form a breakable hydraulic joint therewith.

14. In it directly reversible fuel pump having a drive shaft, and comprising a reciprocating part actuated from said shaft and a driven plunger partwith an impulsion spring drive acting between said parts, means for storing energywithin said drive during a portion of the discharge stroke 15. In a directly reversing fuel pump having a rotating drive shaft, a reciprocating plunger member actuated therefrom, a, discharge valve, actuating means for said valve adapted to maintain proper timing of said valve 1n either the forward or reverse rotation. of the drive shaft and means adapted to suitably shift the phase relation of the pump plunger without resort to a reverse gear.

16. In a multicylinder oil engine served by 11 directly reversing fuel pump, said pump comprising a rotating drive shaft and a reciprocating plunger member actuated therefrom, branch pipes distributing the pump delivery to the several engine cylinders', a separate positively opened discharge valve commanding each of said branch .pipes, actuating means for said valves adapted to maintain proper timing of thepiunp when running the drive shaft in either direction, and means to suitably shift the phase relation of the pump plunger without need of a reverse gear.

17. In it directly reversible oil engine served by a fuel pump having a drive shaft and a reciprocating plunger actuated there-' from, a positively opened discharge valve, means for actuating said valve in synchronisin with'the engine piston movements and adapted to properly time the injection of fuel from the pump into the engine cylinder and means serving to bring about a lag in the plunger movement when running in either the forward or reverse direction.

1S. Ina fuel pump for a direct injection oil, engine, a bypass valve adapted to interrupt the pressure within the pump chamber, a mechanically operated discharge valve, an actuating means for said discharge valve, means adapted to open said bypass valve and to disengage said actuating means serving to discontinue the fuel delivery to the engine cylinder.

19. In a fuel pump for a direct in- ]0.'lil()ll (nl engine, control means. connuandmg the full delivery to the engine cylinder,

an actuating means for said control means, 4

means to disengage said actuating means while the engine is running, and means including a bypass valve adapted to break the pump pressure while. the actuating awn-us disengaged.

:20. In a. multi ilunger fuel pump serving 1'. multirylinder oil engine, separate control means commanding the fuel delivery to respective cylinders, an independent actuating means for each of said control- Ineans, and In testimony whereof, I have hereunto set means for Selectively disengaging saidactumy hand this 6th day of December, 1921. ating means -to throw the corresponding pump out ofservice and means including 5 a bypass' valve adapted to break the pres- Witnesses:

surein said pump while its actuating means 'EDWA'RD L. DONNELLY, is disengage v FREDJ. GAMPBEIL.

' LOUIS ILLMER.

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