US3741685A

US3741685A - Fluid or fuel injection pump assembly

Info

Publication number: US3741685A
Application number: US00198677A
Authority: US
Inventors: A Simko
Original assignee: Ford Motor Co
Current assignee: Ford Motor Co
Priority date: 1971-11-15
Filing date: 1971-11-15
Publication date: 1973-06-26
Anticipated expiration: 1990-06-26
Also published as: CA972644A; JPS4858218A; DE2255350A1; GB1368526A; JPS5214807B2

Abstract

A fluid injection pump assembly, particulary adaptable for use as a fuel injection pump for an internal combustion engine having a plurality of cylinders. The pump assembly includes a plurality of reciprocable pumping means, one for each cylinder of the internal combustion engine. Means are coupled to certain of the reciprocable pumping means, preferably alternate ones, and these means are responsive to a predetermined external condition that controls the amount of fuel or liquid pumped by the pump for arresting the reciprocation of certain of the reciprocable pumping means. In an internal combustion engine fuel delivery is cut off to certain of the cylinders, for example, every other cylinder, during periods of idle or low load conditions on the internal combustion engine.

Description

[ FLUID OR FUEL INJECTION PUMP ASSEMBLY [75] Inventor: Aladar O. Simko, Dearbom Heights,

Mich.

[73] Assignee: Ford Motor Company, Dearbom,

Mich.

22 Filed: Nov. 15,1971 21 Appl, No.: 198,677

[52] US. Cl. 417/214, 123/198 F, 417/216, 92/24, 123/139 AZ [51] Int. CL. F0411 49/00, FlSb 15/26, F02rn 63/02 [58] Field of Search 417/212, 214, 216,

417/426; 92/22, 24, 27;-l23/139 B, 139 AC,

- 139 AZ, 198 F [56] References Cited UNITED STATES PATENTS 1,967,101 7/1934 Rassbach et al 123/198 F 2,875,742 3/1959 Dolza 3,240,197 3/1966 Mock 3,319,568 5/1967 Repko 2,713,328 7/1955 Driskel et a1. 1,973,146 9/1934 Gill 417/426 [451 ,lue 26,1973

FOREIGN PATENTS OR APPLICATIONS 602,199 5/1948 Great Britain 417/214 Primary Examiner-C. J. Husar s i tan .E4m r -L9nar mith 2 a a Attorney-John R. Faulkner and Keith L. Zerschling [57 ABSTRACT A fluid injection pump assembly, particulary adaptable for use as a fuel injection pump for an internal combustion engine having a plurality of cylinders. The pump assembly includes a plurality of reciprocable pumping means, one for each cylinder of the internal combustion engine. Means are coupled to certain of the reciprocable pumping means, preferably alternate ones, and these means are responsive to a predetermined external condition that controls the amount of fuel or liquid pumped by the pump for arresting the reciprocation of certain of the reciprocable pumping means. In an internal combustion engine fuel delivery is cut off to certain of the cylinders, for example, every other cylinder, during periods of idle or low load conditions on the internal combustion engine.

7 Claims,8 Drawing Figures PAIENIEDJUIIZB 1973 3 .741. 685

. SHEEI1UF4 'INVENTOR AZADAE O. GYM/(O ATTORNFYS PAIENIEDauuzs I975 SNEEI 3 0F 4 F'IG.3

FIG-5.4

BDC

TDC

I IDLE SPRING STOP IQOORPM IDLE CONTROL CURB STOP POS.

PRIME START INVENTOR 41/10/12 0. J/M/m FLUID OR FUEL INJECTION PUMP ASSEMBLY BACKGROUND OF THE INVENTION- This invention relates to a fluid injection pump assembly and, more particularly, to such an assembly that is particularly adapted to pump fuel to an internal combustion engine in which certain ones of the pumping mechanisms or means are arrested, or rendered inoper-. ative, during certain modes of engine operation, for example, at idle or low load modes of operation of the internal combustion engine.

There is disclosed in U.S. Pat. No. 3,319,568 a fuel injection pump assembly which may be used to pump fuel for injection into the cylinders of an internal combustion engine. This pump has a plurality of pumping means in the form of reciprocating type pistons or plungers each of which is axially movable in a bore or barrel. A discharge passage is connected to one end of each of these pumping means, pistons or plungers, for delivering fuel to a delivery valve. Each of these delivery valves may in turn be connected to a fuel injection nozzle for a cylinder of an internal combustion engine. Fuel under pressure is supplied to the end of the pumping means, piston or plunger through a spill port, and the pistons'or plungers are driven by a drive plate having an angled drive surface. The amount of fuel supplied to the pumping chamber at the end of the pump ing means, pistons or plungers may be controlled by means of a rotatable metering valve having a helix positioned thereon. This metering valve is rotated by the drive shaft of the pumping assembly which, in turn, is rotated by the internal combustion engine. External control means are employed for moving this valve metering helix axially with respect to its rotatable axis and this external control means may include a linkage connected to the accelerator pedal of the vehicle.

Thus, the amount of fuel pumped by each of the reciprocable pumping means, pistons or plungers, and, hence, the amount of fuel delivered to each cylinder,

is controlled by the position of the accelerator pedal of the vehicle. Means are also shown in this patent to control the amount and timing of the fuel injected to the cylinders as a function of engine speed.

The present invention represents a modification and improvement over the fuel injection pump assembly shown in U.S. Pat. No. 3,319,568 and described above.

SUMMARY OF THE INVENTION The present invention provides a means in a fluid injection pump assembly, particularly adapted for use as a fuel injection pump for an internal combustion engine, for cutting off or terminating the injection of fuel to certain of the cylinders of the engine, preferably alternate ones, during certain modes of engine operation, particularly when the engine is operating in the idle mode or the low load mode of operation.

Operation of an internal combustion engine in which fuel is injected in only certain ones of the cylinders, preferably every other one, at idle and at light loads has been found to reduce the amount of undesirable exhaust emissions by a considerable amount. This operation also improves fuel economy by a few percentage points. The deterioration in running smoothness of the engine occasioned thereby is minor and may be counteracted by design modifications such as softer engine mounts and a heavier flywheel.

More specifically, the invention provides in a fluid or fuel injection pump assembly that has a plurality of reciprocating pumping means, or pistons, or plungers, means for arresting or terminating the reciprocation of certain ones of these reciprocating means or plungers, preferably alternate ones. This means may comprise a detent which engages a groove in the certain ones of the reciprocating means or plungers when the engine is operating at idle or under light load conditions. This detent means may comprise a ball actuated by a shuttle or spool which in turn is operated by engine oil under pressure when the engine is operating at idle or under light loads.

The shuttle or spool may be actuated by the use of a solenoid operated valve which applies engine oil under pressure to one end of the shuttle or spool to move it into a position where it forces a ball into engagement with a depression or groove in the reciprocable pumping means or plunger. This solenoid may be energized from the electrical storage battery of a vehicle utilizing the present invention when the accelerator pedal is in the idle position or when it is in a position where the.

load on the internal combustion engine is very light, for

example, at positions where the vehicle is operating under forty miles per hour at road load.

Thus, the present invention provides for a means for terminating fuel injection to certain ones of the cylinders of an internal combustion engine, preferably alternate ones, when the engine is operating at idle or under light low loads. The invention also provides a fluid or fuel injection pump assembly for accomplishing this purpose.

An object of the present invention is the provision of a fluid or fuel injection pump assembly usable with an internal combustion engine which will result in the reduction of unwanted emissions in the exhaust gases of the engine.

A further object of the invention is the provision of a fluid or fuel injection pump assembly having a plurality of pumping means in which uncomplicated and reliable means are employed to terminate or cut off the delivery of fuel from certain of the pumping means or plungers during certain modes of operation.

Other objects and attendant advantages of the present invention may be more readily realized when the specification is considered in connection with the attached drawings.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a front elevational view of a fluid or fuel injection pump assembly of the present invention;

FIG. 2 is an enlarged cross sectional view of the pump assembly of the present invention;

' FIG. 3 is a schematic representation of the fluid or fuel injection pump assembly shown in FIG. 2;

FIG. 4 is a representation of the fluid or fuel metering means employed with the fluid or fuel injection pump assembly of the present invention;

FIG. 5 is a cross sectional view of a portion of the invention showing the control means thereof in one position;

FIG. 6 is a view similar to FIG. 5 but showing the control means of the present. invention in the other position; r

FIG. 7 is a schematic representation and circuit diagram of means for moving the control means shown in FIGS. 5 and 6 from one position to the other position; and

FIG. 8 is a schematic similar to a portion of FIG. 3 but showing another mode of control for the present invention.

DESCRIPTION OF THE PREFERRED EMBODIMENT Referring now to the drawings in which like reference numerals designate like parts throughout the several views thereof, there is shown in FIG. 1 an external view of the fluid or fuel injection pump assembly of the present invention which includes a housing 10 enclosing the actuating mechanism and pump plunger for the plunger type fuel injection pump of the present invention. This housing 10 has a number of fuel discharge outlets 11 that are each adapted to be connected by an external hose to an individual fuel injection nozzle.

The housing 10 includes a window 12 for observing the degree of injection advance; that is, for observing the timing of the pump to the engine, which will be described in more detail later. It also includes a window 14 adjacent an internal fuel reservoir to observe for air bubbles, etc. in the fuel for fuel vapor evaluation purposes. An externally controlled linkage 16 forms a part of the engine accelerator pedal linkage, and partially controls the discharge of fuel through outlets 11 in a manner to be described.

More specifically, as shown in FIG. 2, pump housing 10 has several sections bolted or otherwise secured together. These include a cover portion 20, a hollow upper housing portion 22 containing a flyweight governor mechanism, a central housing portion 26 containing the fuel pump plungers and fuel flow metering sleeve valve, and a lower housing portion 28 enclosing the drive shaft and pump drive plate assembly.

Lower housing portion 28 has a central bore 30 in which is rotatably mounted a tubular drive shaft 32 on side bearings 33. The drive for this shaft is not shown, but it would, in general, be driven by a geared take-off from the engine cam shaft. The upper part of shaft 32 is formed integral with a drive plate 34 of a known type of pump, having an angled drive surface 36. Plate 34 is rotatably mounted on thrust bearings 40.

A reciprocating-type piston or plunger 50 is axially movable in each of a plurality of bores or barrels 52 and the lower end 53 of each of these pistons or plungers 50 bears on the angled drive surface 36 of drive plate 34. The upper end of each bore or barrel S2 is intersected by crossbores 56 and 58 in housing portion 26, the number corresponding to the number of cylinders in the engine to which the fuel pump is connected. Bores 56 constitute discharge passages for fuel leading to delivery valves 59. Passages 58 constitute spill holes or ports connected to a central bore or fluid chamber 60 in housing section 26.

A fuel storage area 61 is provided on one side of pump housing portion 22, and is connected to chamber 60 by intersecting

passages

62 and 64. An external fuel transfer pump (not shown) would be connected to passage 62.

In general, the upper end of each plunger 50 is fed with fuel from the chamber 60 through its own spill hole 58 during the suction stroke of the plunger. During the plunger upstroke, fuel is displaced either back into chamber 60 or past the delivery valve 59. Fuel under pressure on the upper end of each plunger 50 forces the lower end 53 of each of these plungers or pistons into engagement with the angled drive surface 36 of drive plate 34.

Fuel delivery from the pump is controlled by proper phasing of a sleeve valve metering helix with respect to plunger displacement. The sleeve valve 70 has both axial and rotational movements to variably close or open spill ports 58. This sleeve valve 70 is of the spool type, and has upper and

lower lands

72 and 74 connected by a necked portion 76 of reduced diameter. The land diameters are such as to effectively seal the annular internal fuel reservoir defined between the lands so that axial movement of the sleeve valve 70 will control fuel flow into chamber 60 from passage 62, and also the passage of fuel into and out of spill ports 58. Lower land 74 as a raised circumferentially extending portion 78 in the shape of a helix that is integral with the valve and moves axially and rotatably with it, in a manner to be described, to progressively close or open spill ports 58.

The metering sleeve valve 70 surrounds an extension 82 of drive shaft 32, and can be moved both axially and rotatably with respect to it in the following manner. A tubular pump timing bushing is bolted to drive shaft 32, which is internally splined to the lower end of shaft 82. The two shafts are further connected by a pin 84 that is fixed to bushing 80 and projects through a slot 86 in shaft 82 to permit relative axial movement between them. Shaft 82 projects through an oil seal 87 and a thrust bearing 88, the thrust bearing being located axially in one direction by a retaining ring 90. Shaft 82 continues upwardly freely through metering valve 70, through a governor assembly 91, and into cover portion 20 through a journal bearing 92. The bearing is inserted in an aperture in a partition 93 in housing portion 22. The upper end of shaft 82 has a slotted pivotal connection at 94 to a lever 95 that is fixed to a rotatably mounted rod 96 forming a part of the vehicle accelerator pedal linkage.

Thrust bearing 88 and metering valve 70 are axially separated by an idle speed control spring 97 that surrounds shaft 82. The spring is seated at one end in a recess 98 in valve land 74 and at the other end against thrust bearing 88. The spring exerts a predetermined upward preload on land 74. The upper end of valve 70 is also recessed, and is slidably (see FIG. 3) splined to a reduced diameter sleeve member 100. The sleeve member is fixed to the lower race 102 of a thrust bearing 104 that slidably surrounds shaft 82.

Sleeve member has a cam follower slot 106 in which slides a drive pin 108 that is fixed to shaft 82. Slot 106 has an axially extending portion 110 and an inclined portion 1 12. Axial portion 110 permits relative axial movement between metering valve 70 and shaft 82, while inclined portion 112 forces the metering valve 70 to rotate relative to shaft 82 when the valve is moved axially. A second compression spring 114 surrounds shaft 82, and is seated between the lower end of sleeve member 100 and the bottom of recess 115 in upper land 72.

The thrust bearing 104, sleeve member 100, and valve 70 are moved axially downwardly by the mechanical flyweight governor assembly 91. This latter mechanism includes a cage or base plate 118 nonrotatably keyed to shaft 82. The cage has pairs of laterally spaced arms or ears 120, between which are pivotally mounted a pair of right angled speed responsive members 122.

The lower portion of each member 122 is formed as a weight 124, while the upper portion constitutes a lever 125 that abuts the upper race of bearing 104. Suitable screw adjusting devices 126 provide adjustment in a known manner. The governor operates to depress sleeve valve 70 downwardly relative to shaft 82 against the forces of

springs

97 and 114 upon outward movement of weights 124 under the effect of centrifugal force, in a manner that will become clearer later.

The preload of spring 114 maintains sleeve member 100 and metering valve 70 in their axially-most separated positions shown in FIGS. 2 and 3 below a predetermined speed of rotation of shaft 82 of, say, 2400 r.p.m., for example; that is, below the speed at which injection advance is desired, as will be explained more fully later.

Above 2400 r.p.m., centrifugal force acting on the governor weights overcomes the preload of spring 1 14, i

sembly indicated at 127. The pump drive plate thrust and

side bearings

70 and 33, and plungers 50, are lubricated by engine oil supplied through suitable intersecting passages 127 leading to these parts. I

The accelerator pedal control linkage is illustrated schematically in FIG. 3. It includes an accelerator pedal 128 pivotally mounted at 129, and pivotally connected near its center to an articulated linkage consisting of

links

130 and 131. These links are pivoted to each other, the opposite end of link 131 being fixed to rod 96 in FIG. 2. Suitable wide open throttle and

idle stops

132 and 133 are provided, as shown, with idle stop 133 including a pushbutton type microswitch 133' for purposes to be described later. A return spring 134 normally biases the pedal 128 to its idle position.

To prevent afterrunning of the engine-when the ignition is shut off, and to prevent overspeeding when desired, an additional external fuel shut-off linkage is provided. This consists of a power or manually movable knob 135 secured by a horizontally movable link 136 to a fuel shut-off lever 137. The lever, in its simplest form, is fixed for rotation with rod 96 as shown in FIG. 3, and rotates between fuel shut-off and wide-open throttle positions, as indicated. The fuel shut-off position would move the metering helix 78 downwardly to a position completely opening spill ports 58 so that no fuel would be discharged through passages 56.

FIG. 2 shows the parts of the fluid or fuel injection pump assembly of the present invention described thus far in the curb-stop or non-running position. The idle speed and injection advance springs 97 and 114 preload metering valve 70, sleeve member 100, and the governor members 122 to the positions shown. The accelerator pedal 128 (FIG. 3) is released to its idle position; therefore, no upward force is exerted on shaft 82 by this linkage. The metering helix 78 is positioned relative to the spill holes 58 at the point indicated in FIG. 4 so that slightly more than the normal amount of fuel required to provide idle operation of the engine would be injected past the delivery valves if the fuel pump were to be driven at this time. Consequently, the auxiliary fuel control shut-off knob 135 (FIG. 3) would be moved to the left to move shaft 82 and valve downwardly to a fuel shut-off position locating the spill holes 58 relative to helix 78 so that all of the fuel will spill back into chamber 60.

To start the engine, an amount of fuel far greater than the normal fuel load dispersion is desirable. The accelerator pedal 128 is depressed fully to its wideopen throttle position, which also corresponds to the prime-start position. This full depression of the pedal rotates lever clockwise to move shaft 82, governor mechanism 91, and metering valve 70 upwardly so that the bottom portion of the metering helix 78 now closes off spill holes 58 for almost the entire rotation of the metering valve as indicated in FIG. 4. Once the engine is cranked, therefore, substantially the entire output from the pump plunger bores 52 will be forced into discharge passages 56.

As soon as the engine is started, the operator releases the accelerator pedal 128 to its idle or rest position. This again returns shaft 82 downwardly towards its original curb-stop position, which schedules fuel discharge at a volume that will be greater than that needed to provide a selected engine idle speed of, say, 575 r.p.m. Simultaneously, however, the rotation of governor 91 at shaft speed now moves metering valve 70 further downwardly, and relative to shaft 82, against the force of spring 97 toward the idle speed position indicated in FIG. 4. The preload of spring 97 is chosen such that below a predetermined lower idle limit r.p.m., such as 400 r.p.m., for example, it will prevent the governor from moving. Between the idle speed limits of, say, 400-900 r.p.m., for example, the opposing forces provided by spring 97 and the downward movement of metering valve 70, due to centrifugal force acting on the governor, will cause the metering valve to reciprocate back and forth until it reaches an equilibrium position at the idle speed location chosen.

If the accelerator pedal is now again depressed, shaft 82 is raised, metering helix now covers more of the area of spill holes 58, and the shaft speed increases. When the shaft speed reaches the upper idle speed limit of 900 r.p.m., the metering helix 78 will have been moved downwardly by the governor enough to contact a stop 99 on thrust bearing 93. This now renders the governor 91 inoperative above 900 r.p.m. to prevent any further downward relative movement of sleeve 70 with respect to drive shaft 82 so long as the preload of spring 1M remains in effect. As stated previously, this preload is operative to maintain land 72 and sleeve 100 in the relative positions shown below a speed of 2400 r.p.m.

At 900 r.p.m. drive pin 108 will be positioned in the slot 106 of sleeve 100 at the junction between

portions

110 and 112. Further change in the axial position of metering helix 78 between 900 and 2400 r.p.m. is now, therefore, controlled entirely as a function of the movements of accelerator pedal 128. That is, depression of the pedal will rotate lever 95 clockwise to raise shaft 82, governor mechanism 91, and sleeve valve 70 proportionally. Load control is now a direct function of accelerator pedal position.

Above 2400 r.p.m., centrifugal force acting on governor weights 124 now is sufficient to overcome the preload of spring 114 and begin moving sleeve 100 into the upper end of sleeve valve 70, and downwardly relative to drive shaft 82. Since pin 109 must follow the curve of slot portion 112, the sleeve valve now is forced to rotate as well as move axially. This provides a change in the injection timing; that is, the helix 78 advances or rotates ahead relative to shaft 82 so that the fuel is now injected earlier. At a given speed of, say, 3400 r.p.m., pin 108 will have moved to the end of inclined slot portion 112, and further axial and circumferential movement of the sleeve valve relative to shaft 82 will terminate.

Deceleration control is obtained by releasing the accelerator pedal to its idle position. Shaft 82, the governor assembly 91, and helix 78 immediately move downwardly, and decrease the fuel output. Since the governor is operative, the high centrifugal force still acting on the governor weights at first maintains spring 114 compressed, and sleeve 100 almost entirely within land 72. However, as the speed decreases, the force of spring 114 will move valve 70 downwardly, so that at 2400 r.p.m., spring 114 will have moved valve 70 to its downwardmost position relative to shaft 82, and valve 70 will be in its downwardmost position against stop 99. The helix 78 will now completely uncover the area of spill holes 58, and thereby shut off all fuel flow to the nozzles. When the speed falls within the 400-900 r.p.m. idle speed range, spring 97 and the governor will again be operative to move the sleeve valve 70 and metering helix 78 to the idle speed position.

In the present invention, means are provided for arresting or stopping the reciprocating action of certain ones of the reciprocating type piston or plungers 50 that are movable in their respective bores or barrels 52. In the preferred embodiment of the invention, as shown in FIGS. 2, 5, and 6, this means is a detent means generally designated by the numeral 140. This detent means comprises a ball 142 operable in an aperture 144 positioned in the central housing portion 26 of the housing of the pump assembly. This ball 142 is adapted to engage a depression, preferably in the form of an annular groove 146, positioned in the outer periphery of certain ones of the pistons or plungers 50. As will be more fully explained subsequently, it is preferred that these balls 142 engage grooves 146 positioned in alternate ones of the pistons or plungers 50 for cutting off or terminating fuel injection to alternate cylinders of an internal combustion engine.

The ball 142 is actuated by a movable sleeve or spool 148 which is movable in a cylinder 150. The movable spool or sleeve 148 has a reduced central portion 152 and two

end portions

154 and 156 which are in sealing engagement in the cylinder 150.

The central portion 26 of the housing has a fluid passageway 158 communicating with the top of the enlarged portion 154 of the spool or sleeve 148, as shown in FIGS. 2, 5, and 6, and another'fluid passageway 160 communicating with the bottom of the other enlarged end 156 of the sleeve or spool 148. A rotatable valve means 162 is rotatably mounted in the central portion 26 of the housing. This rotatable valve means connects the fluid passage 158 to a source of fluid under pressure, which is connected to the line 163, when the valve means 162 is in the position shown in FIG. 6 and connects the fluid passageway 160 to the source of fluid under pressure when the valve means 162 is in the position shown in FIG. 5. For purposes of clarity, the valve means 162, as shown in FIGS. 5 and 6, is rotated through 90 with respect to its true position in the fluid 'or fuel injection pump assembly as shown in FIG. 2.

The valve means 162 may comprise a cylindrical portion 164 having a first fluid passage 166 and a second fluid passage 168 positioned therein, and each of these fluid passage means conveys fluid through approximately a right or angle in the cylindrical portion 164. The central portion 26 of the housing also has a return fluid passage means 170 which communicates at one end with the cylindrical portion 164 of the valve means 162 and at the other end with the interior of the lower portion 28 of the housing of the pump assembly.

When the fluid or fuel injection pump assembly of the present invention is used for injecting fuel into the cylinders of an internal combustion engine, the source of fluid under pressure connected to the line 163 may be engine oil under pressure. When the valve means 162 is in the position shown in FIG. 6, engine oil under pressure is supplied to the end of the enlarged portion 154 of the sleeve or spool 148 from the source of engine oil under pressure via line 163, passageway 166 in the cylindrical portion 164 of the valve means 162 and the fluid passageway 158. This positions the sleeve or spool 148 in the position in FIG. 6 where the reduced portion 152 of the spool or sleeve 148 is juxtaposed with respect to the ball 142. Consequently, the plunger or piston 50 may reciprocate in a conventional manner as it is driven by the drive plate 34. The other enlarged end portion 156 of the sleeve or spool 148 is in communication with the interior of the lower housing portion 28 via

passageways

160, 168, and 170.

On the other hand, when the cylindrical portion 164 of the valve means 162 is in the position shown in FIG. 5, engine oil under pressure is supplied to the end of the enlarged portion 156 of the spool or sleeve 148 via passageway 163, passageway 166 in the cylindrical portion 164 of the valve means 162, and the fluid passageway 160, thereby shifting or moving the spool or sleeve 148 upwardly into the position shown in FIGS. 2 and 5. This brings the outer surface of the enlarged end portion 156 into engagement with the ball 142, thereby forcing it to the left, as shown in FIGS. 5 and 6 and into the depression or groove 146 in the plunger or piston 50. This action locks the plunger or piston 50 into the position shown in FIGS. 2 and 5, thereby stopping or arresting the reciprocating action of the piston or plunger 50. Consequently, fluid or fuel is no longer pumped by this plunger or piston 50.

As shown in FIGS. 1, 2 and 7, each of the valve means 162 includes a radially extending shaft 171 having a pinion gear 172 formed on the end thereof opposite the cylindrical portion 164. Each pinion gear 172 is positioned in engagement with the teeth on a ring gear 174 which is supported for limited angular or rotatable movement about the central portion 26 of the housing of the fluid or fuel pump injection assembly of the present invention. This may be accomplished by mounting the gear 174 in a support member 176 which is affixed to the lower housing portion 28 of the assembly.

As shown in FIG. 7, the means for rotating the ring gear 174 by a limited angular amount comprises a sole noid 180 having an axially extending plunger 182 which is suitably coupled to a depending tang 184 on the ring gear 174. A spring biasing means in the form of a compression spring 186 is positioned between the main body portion of the solenoid 18 0 and the tang 184 afflxed to the ring gear 174. This spring 186 rotates the ring gear 174 and, hence, the pinion gears 172 attached to the valve means 162 so that the valve means 162 are positioned as shown in FIG. 6, when the solenoid 180 is unenergized. Thus, in this position, the fluid or fuel injection pump assembly of the present invention will operate in a normal manner as described above.

As shown in FIG. 7, the solenoid 180 is connected to a source of electrical energy, which may be in the form of a storage battery 188 employed in the automotive vehicle, through a pushbutton type switch which is the microswitch 133' shown in FIG. 3. When the switch 133 is closed, the solenoid 180 will be energized from the electrical storage battery 188 and the plunger 182 of the solenoid will be moved axially inwardly or to the left, as shown in FIGS. 1 and 7. This action rotates the ring gear 174 in a clockwise direction, as viewed in FIG. 1, thereby rotating each valve means 162 in a clockwise direction, as these valve means are viewed in FIGS. 5 and 6, and from the position shown in FIG. 6 to the position shown in FIG. 5.

As described above, when each valve means 162 is rotated from the position shown in FIG. 6 to the position shown in FIG. 5, fluid under pressure from the line 163 moves the spool or shuttle 148 upwardly into the position shown in FIG. 5. This action forces the ball 142 into the groove 146 in the plungers or pistons 50. As shown in these drawings, a valve means 162 is employed with every other or alternate plungers or pistons 50. As a result, the reciprocation of these plungers or pistons 50 is arrested thereby cutting off or arresting the injection of fuel to alternate cylinders of the internal combustion engine employing this invention.

Although a valve means 162 is shown in FIGS. 1 and 7 for alternate pistons or plungers 50, it can be readily appreciated by those skilled in the art that a single valve means 162 may be employed and that suitable conduits may be positioned in the central housing portion 26 to connect this single valve means 162 with each spool or sleeve 148 positioned to move the ball 142 into the groove or detent 146 of alternate pistons or plungers 50.

When the fuel injection pump assembly of the present invention is employed in an internal combustion en- 4 gine which has the control means shown in FIG. 3, the pushbutton switch, in the form'of microswitch 133', is positioned with respect to the accelerator linkage so that the link 131 engages and closes the microswitch 133' when the accelerator pedal 128 is in the idle or at rest position. 7

On the other hand, with respect to the embodiment shown in FIG. 8, the microswitch 133' is positioned adjacent a link I92 affixed pivotally to the intersection of the

links

131 and 130. This link is pivotally anchored at the other end to a vehicle body component. The microswitch 133' is positioned to be closed at a position of the accelerator pedal 128 that corresponds to low road load speeds of the automotive vehicle, for example, road load speeds of 40 miles per hour and below. As a result, the solenoid 180 is energized at these low road speeds and the valve means'l62 will be positioned as shown in FIG. 5, thereby arresting action of the plungers or pistons 50 having the valve means 162 associated with them. Consequently, in an internal combustion engine, injection of fuel is cut off to certain of the cylinders, preferably alternate cylinders at these road load speeds.

On the other hand, the microswitch 133 shown in FIG. 8 could be positioned in the same position as shown in FIG. 3, but could employ a large amount of hysteresis so that it would open only when the linkage is in a position where the link 131 corresponds to speeds above these low road load speeds, for example, 40 miles per hour and above.

Thus, in the operation of an automotive vehicle having an internal combustion engine which employs the fuel injection pump assembly of the present invention, the solenoid will be energized either at engine idle or at low engine loads. Consequently, the valve means 162 which are preferably coupled to operate on the plungers or pistons 50 connected to alternate cylinders of the engine are rotated into the position shown in FIG. 5, whereby the ball 142 will come into engagement with the depression or groove 146 of the piston or plunger 50. AS a result, fuel injection to alternate ones of the cylinders of the internal combustion engine will be cut off at this time, since the alternate pistons or plungers 50 are rendered incapable of pumping fuel for injection into these cylinders.

When the internal combustion engine is operated at speeds higher than engine idle in the embodiment shown in FIG. 3, or higher than low road speeds, as shown in FIG. 8, the microswitch 133 will be opened, thereby de-energizing the solenoid 180. As a result, the ring gear I74 will' be rotated so that the valve means 162 are rotated back into the position shown in FIG. 6. Consequently, engine oil under pressure will move the spool or sleeve 148 into the position shown in FIG. 6, thereby restoring normal pumping operations of each of the plungers 0r pistons 50 having the valve means 162 connected to them. Consequently, full fuel injection will be restored to all of the cylinders of the inter nal combustion engine utilizing the fluid or fuel injection pump assembly of the present invention.

I claim:

1. A fuel injection pump means for an internal combustion engine having a plurality of cylinders, comprising:

a plurality of reciprocable pumping means, one for each cylinder;

engine driven means coupled to said plurality of reciprocable pumping means for reciprocating said reciprocable pumping means; means operable for controlling the amount of fuel pumped by said plurality of reciprocable pumping means;

means coupled to certain of said reciprocable pumping means and responsive to a predetermined state of said means operable for controlling the amount of fuel pumped by said plurality of reciprocable pumping means for arresting the reciprocation of said certain of said reciprocable pumping means whereby fuel delivery is cut off from said certain of said reciprocable pumping means;

said means coupled to said certain of said reciprocable pumping means and responsive to a predetermined state of said means operable for controlling the amount of fuel pumped by said plurality of reciprocable pumping means comprising a detent means positioned adjacent each of said certain of said reciprocable pumping means and engagable in depressions positioned in said certain of said reciprocable pumping means, valve means movable be tween a first position and a second position,

a source of fluid under pressure coupled to said valve means, and

fluid operable means coupled to said valve means and to said detent means for engaging said detent means in said depression in said certain of said reciprocable pumping means when said valve means is in said first position and for disengaging said detent means from said depression in said depression in said certain of said reciprocable pumping means when said valve means is in said second position.

2. The combination of claim 1 in which said valve means is rotatably mounted in said fuel injection pump means, and further comprising an electromagnetic actuating means, and means coupling said valve means with said electromagnetic actuating means for rotating said valve means from one of said positions to the other of said positions when said electromagetic actuating means is energized.

3. The combination of claim 1 in which a valve means is provided for each of said detent means and each of said valve means is rotatably mounted in said fuel injection means for rotatable movement from said first position to said second position, and further comprising an electromagnetic actuating means and means coupled to each of said valve means and said electromagnetic actuating means for rotating each of said valve means from said second position to said first position when said electromagnetic actuating means is energized, and means for energizing said electromagnetic actuating means when said predetermined state of said means operable for controlling the amount of fuel pumped by said reciprocable pumping means is present.

4. The combination of claim 3 in which said predetermined state is a state in which the quantity of fuel pumped is low compared with the full quantity of fuel capable of being pumped by said plurality of reciprocable pumping means.

5. An injection pump assembly comprising, in combination:

a stationary housing having a central bore and a source of fluid under pressure connected to said bore;

a rotatable drive shaft mounted in said bore;

a plurality of reciprocable fluid pumping means;

means coupling said rotatable drive shaft and said plurality of reciprocable fluid pumping means for reciprocating said plurality of reciprocable fluid pumping means;

said plurality of reciprocable fluid pumping means each having a fluid discharge passage;

fluid metering means for metering the amount of fluid pumped by said plurality of reciprocable fluid pumping means;

external movable means coupled to said fluid metering means for varying the amount of fluid pumped by said plurality of fluid pumping means; and

means coupled to said external movable means and certain of said plurality of fluid pumping means for arresting the reciprocation of said certain of said plurality of fluid pumping means when said external movable means is in a predetermined position whereby pumping of fluid by said certain of said plurality of reciprocable fluid pumping means and discharge of fluid from the associated fluid discharge passage is terminated, each of said certain of said plurality of fluid pumping means having a groove positioned in the outer surface thereof;

said means for arresting the reciprocation of said certain of said plurality of fluid pumping means comprising a detent means positioned adjacent each of said certain of said plurality of fluid pumping means and movable into said groove when said external movable means is in said predetermined position,

fluid operable means coupled to said detent means for moving said detent into said groove when said external movable means is in said predetermined position,

a source of fluid under pressure, and

means coupling said source of fluid under pressure with said fluid operable means through said valve means,

said fluid operable means including means moving said detent means into said groove when said valve means is moved from said one position to said another position and actuating means coupled to said vvalve means and said external movable means for moving said valve means from said one position to said another position when said external movable means is in said predetermined position.

6. A fuel injection pump for an internal combustion engine having a plurality of cylinders comprising:

a stationary housing having a central bore and a source of fuel under pressure connected to said bore;

a rotatable shaft mounted in said bore;

a plurality of fuel pumping plungers mounted in said bore;

means coupling said rotatable drive shaft and said plurality of plungers for driving said plungers;

said plungers each having a fuel discharge passage communicating with one of the cylinders of the internal combustion engine and a fuel spill line connected to said bore;

a fuel metering valve member driven by said drive shaft slidably and rotatably mounted in said bore between said source and said fuel spill lines, said fuel metering valve member having fuel control portions thereon variably controlling the flow of fuel through said spill lines as a function of the axial and rotative movements of said metering member;

control means coupled to said fuel metering valve member for moving said fuel metering valve member in an axial direction; and

means coupled to said control means and to alternate ones of said fuel pumping plungers for arresting the reciprocable movement of said alternate ones of said plungers when said control means is in a predetermined position in the low speed range of the operation of the internal combustion engine whereby discharge of fuel from each fuel passage connected to said alternate ones of said plungers is terminated;

said means coupled to said control means and to alternate ones of said plungers including locking means positioned adjacent said alternate ones of said plungers movable into engagement with each of said alternate ones of said plungers, and

actuating means coupled to each of said locking means and to said control means for moving said locking means into engagement with each of said alternate ones of said plungers when said control means is in said predetermined position;

said control means comprising a throttle linkage for the internal combustion engine;

said actuating means including switch means operable between a closed and an open position, said switch means being positioned adjacent said throttle linkage for movement between one of said positions and the other of said positions when said throttle linkage moves into said predetermined position, and

means coupled to said switch means and said locking means and responsive to the movement of said switch means for moving said locking means into engagement with each of said alternate ones of said plungers.

7. The combination of claim 6 in which said actuating means further comprises fluid operable means coupled to said locking means, a source of fluid under pressure, valve means operable between a first and second position coupling said fluid operable means with said source of fluid under pressure, said valve means when in said first position applying fluid under pressure to said fluid operable means in a position to hold said locking means out of engagement with said alternate ones of said plungers and when in said second position applying under pressure to said fluid operable means in a position to hold said locking means in engagement with said alternate ones of said plungers, and electrically operable means coupled to said switch means and to each of said valve means for moving said valve means from said first position to said second position when said switch means is moved from said one of said positions to said other of said positions.

Claims

1. A fuel injection pump means for an internal combustion engine having a plurality of cylinders, comprising: a plurality of reciprocable pumping means, one for each cylinder; engine driven means coupled to said plurality of reciprocable pumping means for reciprocating said reciprocable pumping means; means operable for controlling the amount of fuel pumped by said plurality of reciprocable pumping means; means coupled to certain of said reciprocable pumping means and responsive to a predetermined state of said means operable for controlling the amount of fuel pumped by said plurality of reciprocable pumping means for arresting the reciprocation of said certain of said reciprocable pumping means whereby fuel delivery is cut off from said certain of said reciprocable pumping means; said means coupled to said certain of said reciprocable pumping means and responsive to a predetermined state of said means operable for controlling the amount of fuel pumped by said plurality of reciprocable pumping means comprising a detent means positioned adjacent each of said certain of said reciprocable pumping means and engagable in depressions positioned in said certain of said reciprocable pumping means, valve means movable between a first position and a second position, a source of fluid under pressure coupled to said valve means, and fluid operable means coupled to said valve means and to said detent means for engaging said detent means in said depression in said certain of said reciprocable pumping means when Said valve means is in said first position and for disengaging said detent means from said depression in said depression in said certain of said reciprocable pumping means when said valve means is in said second position.

5. An injection pump assembly comprising, in combination: a stationary housing having a central bore and a source of fluid under pressure connected to said bore; a rotatable drive shaft mounted in said bore; a plurality of reciprocable fluid pumping means; means coupling said rotatable drive shaft and said plurality of reciprocable fluid pumping means for reciprocating said plurality of reciprocable fluid pumping means; said plurality of reciprocable fluid pumping means each having a fluid discharge passage; fluid metering means for metering the amount of fluid pumped by said plurality of reciprocable fluid pumping means; external movable means coupled to said fluid metering means for varying the amount of fluid pumped by said plurality of fluid pumping means; and means coupled to said external movable means and certain of said plurality of fluid pumping means for arresting the reciprocation of said certain of said plurality of fluid pumping means when said external movable means is in a predetermined position whereby pumping of fluid by said certain of said plurality of reciprocable fluid pumping means and discharge of fluid from the associated fluid discharge passage is terminated, each of said certain of said plurality of fluid pumping means having a groove positioned in the outer surface thereof; said means for arresting the reciprocation of said certain of said plurality of fluid pumping means comprising a detent means positioned adjacent each of said certain of said plurality of fluid pumping means and movable into said groove when said external movable means is in said predetermined position, fluid operable means coupled to said detent means for moving said detent into said groove when said external movable means is in said predetermined position, a source of fluid under pressure, and means coupling said source of fluid under pressure with said fluid operable means through said valve means, said fluid operable means including means moving said detent means into said groove when said valve means is moved from said one position to said another position and actuating means coupled to said valve means and said external movable means for moving said valve means from said one position to said another position when said external movable means is in said predetermined position.

6. A fuel injection pump for an internal combustion engine having A plurality of cylinders comprising: a stationary housing having a central bore and a source of fuel under pressure connected to said bore; a rotatable shaft mounted in said bore; a plurality of fuel pumping plungers mounted in said bore; means coupling said rotatable drive shaft and said plurality of plungers for driving said plungers; said plungers each having a fuel discharge passage communicating with one of the cylinders of the internal combustion engine and a fuel spill line connected to said bore; a fuel metering valve member driven by said drive shaft slidably and rotatably mounted in said bore between said source and said fuel spill lines, said fuel metering valve member having fuel control portions thereon variably controlling the flow of fuel through said spill lines as a function of the axial and rotative movements of said metering member; control means coupled to said fuel metering valve member for moving said fuel metering valve member in an axial direction; and means coupled to said control means and to alternate ones of said fuel pumping plungers for arresting the reciprocable movement of said alternate ones of said plungers when said control means is in a predetermined position in the low speed range of the operation of the internal combustion engine whereby discharge of fuel from each fuel passage connected to said alternate ones of said plungers is terminated; said means coupled to said control means and to alternate ones of said plungers including locking means positioned adjacent said alternate ones of said plungers movable into engagement with each of said alternate ones of said plungers, and actuating means coupled to each of said locking means and to said control means for moving said locking means into engagement with each of said alternate ones of said plungers when said control means is in said predetermined position; said control means comprising a throttle linkage for the internal combustion engine; said actuating means including switch means operable between a closed and an open position, said switch means being positioned adjacent said throttle linkage for movement between one of said positions and the other of said positions when said throttle linkage moves into said predetermined position, and means coupled to said switch means and said locking means and responsive to the movement of said switch means for moving said locking means into engagement with each of said alternate ones of said plungers.