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Publication numberUS2179354 A
Publication typeGrant
Publication dateNov 7, 1939
Filing dateAug 7, 1935
Priority dateAug 7, 1935
Publication numberUS 2179354 A, US 2179354A, US-A-2179354, US2179354 A, US2179354A
InventorsScott Philip Lane
Original AssigneeSuper Diesel Tractor Corp
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
US 2179354 A
Abstract  available in
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Claims  available in
Description  (OCR text may contain errors)

P. L. SCOTT Nov. 7, 1939.


Filed Aug. 7. i935 DEGREES fkyfizar I 1% /z' J. 500624 Y Jffar'nqys.

Patented Nov. 7, 1939 PATENT OFFICE PUMP Philip Lane Scott, Chicago, 11]., assignor to Super Diesel Tractor Corpora corporation of New York tion, La Porte, Ind., a

Application August, 7, 1935, Serial No. 35,108

1 Claim.

This invention relate's to fluid pumps and particularly liquidfuel pumps of the typeused in internal combustion engines for delivering liquid fuel to an atomizing valve, although it is not 5 limited to pumps of this type. One object of my invention is to provide a simple means of changing the delivery characteristic or flow rate of the pump without altering the shape of the driving cam.

in Other objects 'willappear from time .to time throughout the specification and claim.

The invention is illustrated more or less diagrammatically in the accompanying drawing wherein:

15 Figure 1 is a vertical section through a cam driven fuel pump; 7

Figure 2 is a plan view of the adjusting structure including a partial section along 2-2 of Figure 1 of the pump housing; 3 Figure 3 is a graph showing a certain pump delivery characteristic; and

Figure 4 is a graph showing another pump delivery characteristic.

Like numerals refer to like parts throughout.

25 As shown in the drawing, I is a pump base supporting a cam shaft 2 carrying a series of cams, one of which is shown 3. 4 is a pump body adjustably mounted on the base I and locked in any desired position bythe cap screws 5, 5 3 which are inserted through the slots 5a, 5a. Mounted within the pump body'is a slider 6, adapted to slide within the bore 1. Uponthe lower end of the slider is a roller 8, mounted upon a pin 9. Within the body 4 is a barrel II] 35 screwthreaded into the body. Within the barrel ID is a plunger I I adapted to reciprocate therein. The plunger and slider are spring returned by means of the spring I2 acting on the washer I3 and in turn on the hardened button' It positioned m within the slider 6. I5 is a suction valve assembly screwthreaded into the body 4 and leading in to the pump chamber I 6. I1 is adischarge valve assembly screwthreaded into the body 4.

' Figures 3 and 4 show pump discharge rates. gr, The abscissae represent degrees rotation of the cam shaft and the ordinates represent the percentage of discharge occurring. during the preceding selectedmumber of degrees of cam shaft rotation, each of these degree intervals of rota- ;0 tion being conveniently chosen, as say each five degrees, all such intervals being equal.

plunger pumps the rate of discharge varies from zero to a maximum and again to zero during each 55 delivery period. The discharge obviously is zero body which carries the cam showing the condition existing when the axis of at the beginning and end and occurs at varying rates during equal time intervals in the pump-: ing stroke, reaching a maximum at various positions in the stroke depending upon the type of drive used. In cam driven pumps this variation 5 in rate of discharge, or pmnp delivery characteristic can be controlled to a considerable extent by the shape of the cam.

When such pumps are used for feeding fuel to I the atomiaerv of a Diesel engine, this variation in in the rate of discharge becomes highly important, since it has a pronounced eflect upon combustion. Certain type of combustion chambers, for example, operate most satisfactorily with relatively low initial rates of discharge and with the peak obtained well along in the stroke. Other cham bers operate bestwhen the initial rates rise rapidly and the peak is reached relatively early in the stroke. Pressure and temperature conditions also require different pump delivery characteristics. It istherefore highly desirable in commercial pumps to arrange to provide for con siderable variation in the discharge character'- istics.

Such changes in delivery characteristic have heretofore been accomplished by changing the cam or by using only a portion of the drive face of the cam for actual delivery and changinggthe mechanism which determines the portion of the cam face to be used, thereby obtainingthe result by using different portions of the driving face. Both these methods are expensive and cumber- I some. themechanism which'is the subject of this iiiivention the desired result is easily and 'quickly accomplished by setting the axis of the slider and roller (the cam follower) off center from the center line of the cam 'sha It is easily demonstrated that the amount of t is offset caus'esa marked change in the position of the peak rate of discharge with respect to th total discharge period. -Figures Sand 4 are graphs showing two distinct delivery characteristics obtained by merely shifting the axisof the pump followenFigure 3 the pump body is shifted away fromthe axis of the cam shaft in the direction of rotation of the cam, the condition shown in Figure 1. In this case it will be noted that the maximum rate of discharge occurs early in the, stroke, which as explained is desirable for certain engines. To move It is well known that for all reciprocating ward the axis of the camshaft against the direc- 2 I an s tion of the rotation of the cam. Thus, this peak rate of discharge may be moved along the degree base line, as shown in the graph, by merely shifting the pump body back and forth. The con- 5 structionwhich makes this possible is simply to' provide some slots in the body section of the pump and some cap screws or bolts to lock the body when the desired position is reached.

The movement of the pump body above described will produce varying positions of the plunger and cam follower assembly. As the body is moved to the right, as shown in Figure 1, the plunger and cam follower will move downward somewhat toward the cam shaft, acting under the influence of. the spring i2. This occurs without materially changing the stroke, although there may be a slight tendency to increase the stroke. With the plunger and pump body moved to the right, the plunger merely reciprocates approximately the same amount, but in a different portion of the barrel. In general this does not appreciably affect the operation of the pump.

The use and operation of the invention are as follows:

The operation of such pumps generally'when used on Diesel engines is too well known to need detailed description. A source of oil supply is connected to the inlet valve assembly i5, whereby oil is admitted on the suction stroke of the pump into the chamber i6 and then, upon the discharge stroke, expelled from the chamber it through the discharge valve assembly ii to the atomizing valve in the engine. The cam and cam follower are conventional structures. The particular cam 85 shown has a flat driving face and a long circular eccentric return or suction face. The novelty of the device consists in' the ability to shift the pump body with respect to the cam shaft to obtain varying delivery characteristics as already de- 40 scribed. Assuming the pump to be placed in operation on an engine and a particular delivery rate to be found unsuited to the specific engine construction and conditions, it is merely necessary to loosen the cap screws I and shift the pump to right or to the left as the particular requirements of the engine indicate is desirable. The body may be locked in an approximate position and the engine again operated and if improvement is noted the pump may be shifted further in the same direction and this process repeated until the optimum is passed and 'a decrease in performance is observed. The body may be then shifted backward to the point determined as giving the best operation.

Such changes of delivery characteristic are. of exceptional importance when changes in fuel are made, even though other engine conditions remain the same. It is therefore highly desirable to be able to vary delivery characteristic in an installed pump without expensive or complicated changes orreplacements.

It is of course obvious that this principle may be applied to a wide variety of pump construction and it is in no wise limited to the particular form shown.

A variety of locking devices may be employed, and the shifting of the body may be accomplished by sorewthreadeddevices such as are used to position electric motors. A calibrated scale may be attached to identify various body positions as best for certain purposes.

I claim: I

In a pump, a base member, a pump driving cam shaft supported in said member, a cam on said shaft, 9. pump body provided with inlet and outlet valves, a plunger reciprocally mounted in said body, a follower positioned to actuate said plunger and to be acted upon directly by the cam, and means for movably mounting said body upon said base for movement at right angles to the axis of the cam shaft, to adjust the axial distance between the center line of the cam shaft and the center line of the follower.


Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US2533965 *Dec 24, 1946Dec 12, 1950Parker Appliance CoFluid pump
US3040723 *Mar 11, 1960Jun 26, 1962Daimler Benz AgFuel-injection adjusting device
US3108436 *Jul 18, 1961Oct 29, 1963Panhard & Levassor EtsMachines of the piston-pump type
US3138038 *Jan 31, 1962Jun 23, 1964Daimler Benz AgFuel-injection adjusting device
US3822683 *Dec 11, 1972Jul 9, 1974Caterpillar Tractor CoRoller bearing retaining clip
US3991723 *Apr 28, 1975Nov 16, 1976Curtiss-Wright CorporationFuel injection system for rotary internal combustion engine
US4197787 *Aug 29, 1977Apr 15, 1980The United States Of America As Represented By The Secretary Of The NavyPump piston with flexible member
US4671743 *May 12, 1983Jun 9, 1987Hydrowatt Systems LimtedPiston pump
US5655501 *May 9, 1996Aug 12, 1997Caterpillar Inc.Rate shaping plunger/piston assembly for a hydraulically actuated fuel injector
US6347614May 9, 2000Feb 19, 2002Lawrence W. EversMechanical fuel injection system
US6953016Jan 23, 2004Oct 11, 2005Ina-Schaeffler KgTappet in a valve train of an internal combustion engine
US7318416Apr 7, 2005Jan 15, 2008Stewart Howard CLiquid fuel pump
US20040177822 *Jan 23, 2004Sep 16, 2004Henning KarbsteinTappet in a valve train of an internal combustion engine
US20150136051 *Nov 15, 2013May 21, 2015Delphi Technologies, Inc.Camshaft and follower geometry
DE1273902B *May 8, 1963Jul 25, 1968Kloeckner Humboldt Deutz AgAnordnung einer als Einsteckpumpe ausgebildeten Brennstoffeinspritzpumpe an einer Brennkraftmaschine
DE4006367A1 *Mar 1, 1990Sep 5, 1991Kloeckner Humboldt Deutz AgIC engine fuel injection pump - has adjustable fuel injection timing and has hollow RAM with internal hydraulic piston
U.S. Classification123/496, 92/129, 123/446
International ClassificationF02M59/38, F02M59/00
Cooperative ClassificationF02M59/00, F02M59/38, F02M2700/1317
European ClassificationF02M59/00, F02M59/38