US2440196A - Multiple fluid proportioning pump - Google Patents

Description

April 1948- I w. N. FENNEY 6 MULTIPLE FLUID PROPORTIONING PUMP Filed June 29, 1944- 2 Sheets-Sheet 1 i 30 l .l.

/5 35 I I r ATTORNE s pril 20, 1948. w. N. PM 2, 40,196

MULTIPLE FLUID- PROPORTIONING PUMP Tac fl. z l

Filed June 29, 1944 2 Sheets-Sheet 2 an .5. 35 24 I Patented Apr. 20, 1948 v 2,440,196 MULTIPLE FLUID PROPORTIONING PUMP William N. Fenney,

New York, N. Y., assignor to The Texas Company, New York, N. Y., a corporation of Delaware Application June 129, 1944, Serial No. 542,777 l6 Claims. (Cl. 103-7) This invention relates to improvements in pumping fluids and more particularly to a combination fluid pump. The invention is especially concerned with means forpumping fuels to be employed in an internal combustion engine.

It is an object of the invention to provide means for pumping a fluid varying in quantity and regulated in composition in accordance with the total quantity of fluid supplied ineach cycle of the pump. v

Another object of the invention is to provide a pump adapted to supply a fluid comprising a blend or combination or a plurality of fluids, the composition of said fluid being varied in accordance with the total quantity of fluid supplied in a cycle of the pump.

Other objects of the invention will in part be obvious and will in part appear hereinafter.

The pump of the present invention is of the plunger type in which a plunger is slidably and rotatably disposed in a pump cylinder and'ineludes means for causing the plunger to undergo reciprocating movement in the cylinder and means for varying the rotative position of the plunger. The pump includes a valve-controlled outlet port and, as distinguished from the ordinary pump of this type, with a plurality, preferably two, spaced fluid inlet ports in the wall of the cylinder, the particular positioning of the inlet ports being as described below. The pump plunger is generally cylindrical but in a portion of its length is so constructed as to control the opening of the inlet ports during. the plunger reciprocating movement by variation of the rotative position of the plunger in the cylinder. Thus the plunger is preferably formed throughout a portion of its length in the direction of the delivery chamber of the pump of reduced diameter to provide a helical shoulder terminating the truly cylindrical section of the plunger.

The inlet ports are so placed in relation to the helical shoulder of the plunger that they are uncovered for a selected period of the cycle of plunger reciprocating movement and'the respective fluids are permitted to enter the delivery chamber of the pump. In practicing theinvention it is preferred to adjust the size of the ports to vary the difference in pressures between the sources from which the fluids are supplied,

whereby the rates of injecting the separate fluids are adjusted and controlled. Thus, even where the fluids are maintained at the same pressure the rates of'fluid injection are affected by the sizes of the ports. Also, the separate fluids may be maintained at different pressures whether or not the ports are of diflerent sizes. Thus using two ports, the fluid supplied through one of the ports may be at a higher pressure than the pressure on the fluid entering from the other port. The port through which one fluid is fed into the delivery chamber is preferably controlled by a valve to prevent the flow oi fluid away from the cylinder of the pump. The other port is not so controlled arid therefore during the plunger movement excess fluid introduced into the delivery chamber is caused to flow away from the cylinder through this port.

The invention will be understood more fully by reference to the attached drawings in which:

Figure 1 is'a vertical, sectional view of a pump assembly illustrating the manner in which the principles of the invention may be incorporated in a pump of a generally conventional design;

Figures 2 to 5 are detailed views more or less diagram-matical in form which serve to illustrate the operation of the pump shown in Figure 1; Figure 6 is a detailed view also diagrammatical in form illustrating a modified pump plunger and pump body structure providing a rapid cutoff and release of pressure on the fluid in the pump cylinder;

Figure 7 is a graph showing the slope of the helical shoulder on the pump plunger of Figures 2 to 6 and also indicating the position or the pump plunger in several of the figures; and

Figure 8 is a graph illustrating the slope of the helical track on a modified pump plunger.

Referring to Figure 1, the pump body is shown at Ill and provides a support for the elements of the pump and a system of fluid conduits. A pump plunger i2 is slidably and rotatably disposed in a cylinder H in which it is caused to reciprocate in a conventional manner by means of a positively rotated cam causing upward movement and a spring causing downward movement, not shown. The upper end of the pump plunger and the side wall and top of the cylinder provide a delivery chamber IS in which the fluid to be supplied by the pump may be raised in pressure. The pump body is provided with two fluid conduits or channels l8 and 20 arranged to conduct any two desired fluids from storage vessels not shown into ports 22 and 24, which open'into the cylinder l4.

As will be described more fully hereinafter, when either or both of these ports are opened by the motion of the plunger, fluidenters the cylinder and is compressed during the upward movement of the plunger. When the pressure on the fluid in the delivery chamber reaches a previously selected value suiilcient to open a valve controlling the pressure of. the fluid in the passage leading from the chamber, shown as a check valve 26 which is held in place by a selected force exerted by a spring 28, the fluid'flows from the pump under a high pressure through a pipe 80.

As will be understood more fully as the description proceeds, rotation of the pump plunger i2 is effective to control both the composition and the quantity of the fluid supplied during any cycle of plunger reciprocating movement. The rotation of the pump plunger is accomplished by means of a pinion 32 and a rack 34. Movement of the rack may be controlled in any desired manner, not shown, and in the case where the pump -22 and 24 are shown disposed at an angle of 180 in the cylinder wall, which is a preferred arrangement when only two fluid ports are employed. Also for reasons given below, the port 24 is preferably of smaller diameter than port 22, The port 24 is controlled by a check valve 36 which is effective to prevent flow of fluid away from the pump cylinder.

rotative position shown in Figure 2 is that which will result in the delivery of'the smallest total quantity of fuel, and this fuel will be composed at least predominantly of the low quality fuel from port 22. If we assume the plunger in Figure 2 is moving downwardly on the-suction stroke of the plunger, then the port 24 has Just been opened to the delivery chamber, Depending upon the tension in the spring holding valve 36 on its seat, there may be no flow offuel through port or there may be a relatively low rate of flow. It will be seen that the force tending to open valve .38 results from the dif- As stated previously, the pump plunger I 2 is generally cylindrical but the upper portion of the plunger is formed so as to provide a helical shoulder 38'. As shown this shoulder extends entirely around the plunger, which is desirable where two ports disposed at 180 are employed and the helix is as shown. Thus the upper portion of the plunger is of reduced diameter so as to permit flow of fluid through a port when the port is opposite this portion. The general slope of the helix is illustrated in Figure '7. It will be seen from this figure that the portion of the helix shown in Figure 2 is the first half of the helix,be ginning at 0 and ending at 180. The position of the plunger in Figure 3 is that resulting from rptating the plunger 90 in a counter-clockwise direction, while the position of the plunger shown in Figures 4 and 5 is that taken by the plunger after 180 rotation from the position shown in Figure 2.

The pump may be operated in the following manner: With the arrangement shown in Figures 2 to 5, the fluid introduced through port 24 is the fluid desired to be supplied when the total quantity of fluid supplied by the pump is at the maximum. For example, when the pump is employed for supplying fuel to an internal combustion engine, this fluid would be preferably a high quality fuel, e. g., a high octane fuel in the case of an Otto cycle engine and a high octane fuel in the case of a Diesel engine. 0n the other hand, the fluid supplied through port 22 would be a low octane or low cetane fuel. Also, the pressure on the fluid entering through port 24 may be at a relatively low pressure whereas the pressure on the fluid entering through port 22 may be a relatively high pressure. Pressures of 15 pounds per ference in pressure between the delivery cham'- her and the source of fuelsupplying port 24 and adjustment of these pressures" in relation to the spring controlling the valve affects the rate of flow of fuel through port '24, As discussed above,

this rate is also affected by the sizeof the port.

Whether only a small amount or no fuel at all is introduced through port 24, as the, plunger continues its downward movement, port 22 is opened to the. delivery chamber and fuel, which may be under relatively high pressure, enters and fllls the chamber above the shoulder 38 of the plunger. The plunger stroke is preferably sufflciently long to bring the shoulder well below the port 22. On the upward movement of the plunger excess fuelis forced out of port 22 until this port has been covered by the cylindrical sec.- tion of the plunger. From this point on, the fuel in the delivery chamber is compressed until the pressure in the chamber reaches a selected value sutlicient to raise the valve 26'.

The rotative position of the plunger shown in Figure3 is that adapted to cause the pump to suppl a medium quantity of fluid composed of a mixture of the fuels from ports 22' and 24. In this case it will be seen that the plunger will have moved downwardly a substantial distance before port 24 is opened to the delivery chamber. Accordingly, the pressure in the delivery chamber will be low and a substantial flow of fuel through port 24 will have taken place before the port 22 is opened to the delivery chamber. Thus when the plunger has passed port 22, the delivery chamber will be filled with a mixture of the fuels from the two ports, and, while a portion of this mixture will be forced out of port 22 on the upward motion of the plunger, the fluid compressed and therefore supplied by the pump will be a mixture of two fuels.

The plunger setting shown in Figures 4 and 5 is designed to cause the pump to supply a maximum quantity of fuel in each cycle of reciprocating plunger movement and also to adjust the composition of this fuel so that itis composed predominantly oi the higher quality fuel issuing from port 24. Since the plunger will have moved down a maximum distance prior to opening port 24, the pressure in the delivery chamber willbe extremely low and therefore the high quality fuel will flow out of port 24 at a rapid rate and fill or substantially fill the chamber prior to the opening of port 22. In this case therefore, the fuel supplied by the pump will be substantial entirely a high quality fuel. 1

The pump illustrated in Figure 6 is similar to that described in Figures 1 to 5 but also includes square inch and 100 pounds per square inch may be cited as examples.

With these conditions existing, the pump means for accomplishing a rapid shutoff and reduction in pressure on the fluid in the delivery chamber. The cylinder is provided with a fluid exhaust port 40. The plunger l2 of this pump,

while similar in most respects to the plunger 12' oz fluid from the delivery ch'amber' n' to the exhaust port when the plunger is at the inner end of its stroke. Thus the plunger in the reduced diameter portion is provided with openings .42 and 44 which lead to a channel 46 in the plunger. The channel 46 leads to openings 48 and 50 which are disposed in a reduced section 52 of the plunger. It will be seen that when the plunger has reached the inner end of its stroke, the reduced section 52 will be opened to the port 40 and fluid from the delivery ch'ambertherefore can flow through the plunger and to the exhaust port. Since the pressure on the storage vessel to which the fluid passing through the port 40 is. preferably conducted may-be at a low pressure, at the point in the cycle of plunger movement wherethe section 52 is opened to the port 40 the pressure on the fluid in the delivery chamber is immediately reduced, which results in a rapid shutting of the valve 28.

Referring now to Figure 8, this figure illustrates a way in which the plunger shown in Figures 1 to 5 and the plunger shown in Figure 6 may be modified. Thus the slope of the helical shoulder may be varied so that the slope is relatively large at the beginning of the helix and becomes smaller toward the end. By using a plunger having a helical shoulder of this variable slope, it is possible-to keep one of the ports closed when the plunger is set in a rotative position to supply either a maximum or a minimum quantity of fuel on each cycle. A plunger modified as disclosed in Figure 8 when set in the same relative position as that shown in Figure 2 could be moved downwardly a suflicient distance to open port 22 without previously opening port 24 to the delivery chamber. Similarly, if the plunger is set in the position shown in Figure 4, the length of time during which the port 24 is opened to the delivery chamber before the port 22 is opened may be increased so as to insure that the fluid ciprocating movement.

fluid fed by the pump in a cycle oi plunger re- 2. A pump of the character described comprising a pump cylinder. a plunger slidably and rotatably disposed in said cylinder. means for causing said plunger to undergo reciprocating movement, means for varying the rotative position oi said plunger in said cylinder, said cylinder being provided with a plurality of inlet ports positioned in the wall thereof, at least one of said ports being positioned to be uncovered in a cycle of plunger reciprocating movement in any rotative position 01' said plunger, said plunger having means on its surface to control the'opening of said'ports during the plunger reciprocating movement by variation of the rotative position of said plunger, and separate conduit means for supplying a fluid to each of said inlet ports.

3. A pump of the character described comprising a pump cylinder, a plunger slidably and rotatably disposed in said cylinder, means for causing said plunger to undergo reciprocating movement, means for varying the rotative position of said plunger in said cylinder, said supplied by the pump is substantially entirely composed of the fluid flowing through port 24.

Although the present invention is particularly concerned with a means for pumping fuels for usevin an internal combustion engine, it will be understood that the pump is adapted for use in many other situations where it is desirable to supply a fluid varying in composition. it will also be understood that while in the specific description the ports have been shown as disposed at an angle of 180", the invention is not restricted to a pump with ports arranged in just this manner since they may be disposed at other angles and there may be more than two ports.

Obviously many modifications and variations of the invention, as hereinbefore set forth, may be made without departing from the spirit and scope thereof and therefore only such limitations should be imposed as are indicated in the appended claims. l

I claimf 1. A pump of the character described comprising a pump cylinder, a plunger slidably and rotatably disposed in said cylinder, means for causing said plunger to undergo reciprocating movement, means for varying the rotative position of said plunger in said cylinder, said cylinder being provided with a plurality of inlet ports positioned in the wall thereof, and means cooperative between said plunger and said ports and responsive to the rotative position of said plunger for both varying the relative proportions of separate fluids supplied from said plurality of inlet ports and also varying the total quantity of the composite cylinder being provided with two inlet ports positioned in the wall thereof, at least one of said ports being positioned to be uncovered in a cycle of plunger reciprocating movement in any rotative position of said plunger, said plunger having means on its surface to control the opening of said ports during the plunger reciprocating movement by variation of the rotative position of said plunger, separate conduits for supplying a fluid to each of said inlet ports, and a valve in one of said conduits to prevent flow of fluid away from said cylinder.

4. A pump of the character described comprising a pump cylinder, a plunger slidably and rotatably disposed in said cylinder, means for causing said plunger to undergo reciprocating movement, means for varying the rotative position of said plunger in said cylinder, said cylinder being provided with two inlet ports p0- sltioned in the wall thereof, at least one of said ports being positioned to be uncovered in a cycle of plunger reciprocating movement in any rotative position of said plunger, said plunger having means on its surface to vary both the point in the plunger reciprocating movement at which each port is uncovered and the period of the cycle during which each port remains uncovered by variation of the rotative position of said plunger, separate conduct means for supplying a fluidto each of said' inlet ports, and a valve in one of said conduits to prevent flow of fluid away from saidcylinder.

5. A pump of the character described comprising a cylinder provided with a valve-controlled outlet, port, a plunger slidably and rotatably disposed in said cylinder, said plunger and said cylinder forming a fluid delivery chamber, means for causing said plunger to undergo reciprocating movement, means for varying the rotative position of said plunger in said cylinder, said cylinder also being provided with two inlet ports positioned in spaced relation to be uncovered at different points in a cycle of plunger reciprocating movement, said plunger having a cylindrical section of substantially the diameter of said cylinder terminating in the direction of said delivery chamber in a helical line, whereby upon rotation of said plunger the cylindricalsection of said plunger covers a different portion of the wall of said cylinder and thereby is adapted to vary both the point in the cycle of plunger reciprocating movement at which each inlet port is opened to the delivery-chamber and the period of the cycle during which each inlet port remains open to'said delivery chamber, separate conduits for supplying a fluid to each of said inlet ports, and a valve in one of said conduits to prevent flow of fluid away from said cylinder.

6. A pump of the character described comprising a cylinder provided with a valve-controlled outlet port, a plunger slidably and rotatably disposed in said cylinder, said plunger and said cylinder forming a fluid delivery chamber, means for causing said plunger to undergo reciprocating movement, means for varying the rotative position of said plunger in said cylinder, said cylinder also being provided with two inlet ports positioned in spaced relation in the direction of the axis of the cylinder and around the circumference of the cylinder to be uncovered at different points of plunger reciprocating move ment, said plunger having a cylindrical section of substantially the diameter of said cylinder terminating in the direction of said deliverychamber in a helical line, said helical line having a varying slope which is relatively large at the beginning and decreases toward the end, whereby upon rotation of said plunger the cylindrical section of said plunger covers a different portion of the wall of said cylinder and thereby is adapted to vary both the point in the cycle of plunger reciprocating movement at which each inlet port is opened to the delivery chamber and the period of the cycle during which each inlet port remains open to said delivery chamber, separate conduits for supplying a fluid to each of said inlet ports. and a valve in one of said conduits to prevent flow of fluid away from said cylinder.

'7. A pumpof the character described comprising a cylinder provided with a valve-controlled outlet port, a plunger slidably and ,rotatably disposed in said cylinder, said plunger and said cylinder forming a fluid delivery chamber, means for causing said plunger to undergo reciprocating movement, means for varying the rotative position of said plunger in said cylinder, said cylinder also being provided with two inlet ports positioned in spaced relation to be uncovered at different points in a cycle of plunger reciprocating movement, said ports being of different sizes to control the rate of fluid flow into said fluid delivery chamber, said plunger havin a cylindrical section of substantially the diameter of said cylinder terminating in the direction of said delivery chamber in a helical line, whereby upon rotation of said plunger the cylindrical setion of said plunger covers a different portion of the wall of said cylinder and thereby is adapted to vary both the point in the cycle of plunger reciprocating movement at which each inlet port is opened to the delivery chamber and the period of the cycle during which each inlet port remains open to said delivery chamber, separate conduits for supplying a fluid to each of said inlet ports, and a valve in one of said conduits to prevent flow of fluid away from said cylinder.

8. A pump of the character described comprising a cylinder provided with a valve-controlled outlet port, a plunger slidably and rotatably disposed in said cylinder, said plunger and said cylinder forming a fluid delivery chamber, means for causing said plunger to undergo reciprocating movement, means for varying the rotative position of said plunger in said cylinder, said cylinder also being provided with two inlet ports psitioned in spaced relation to be uncovered at different points in a cycle of plunger reciprocating movement. said plunger having a cylindrical section of substantially the diameter of said cylinder terminating in the direction of said-delivery chamber in a helical line, whereby upon rotation of said plunger the cylindrical section of said plunger covers a different portion of the wall of said cylinder and thereby is adapted to vary both the point in the cycle of plunger reciprocating movement at which each inlet port is opened to the delivery chamber and the period of the cycle during which each inlet port remains open to said delivery chamber, a conduit for supplying a fluid to one of said inlet ports at a selected pressure, a separate conduit for supplying a fluid to the other of said inlet ports at a lower pressure, and a valve in said conduit supplying a fluid at a lower pressure to prevent flow of fluid away from said cylinder.

9. A pump of the character described comprising a pump cylinder provided with a valve-controlled outlet port at one end thereof, a generally cylindrical plunger slidably and rotatably disposed in said cylinder, said plunger and said cylinder forming a fluid delivery chamber, means for causing said plunger'to'undergo reciprocating movement, means for varying the rotative position of said plunger in said cylinder, said cylinder being also provided with two inlet ports positioned in space relation and at different distances from the end of said cylinder to be uncovered in a cycle of plunger reciprocating movement, said plunger being formed throughout a portion of its length in the direction of said delivery chamber of reduced diameter to provide a helical shoulder, whereby upon rotation of said plunger the cylindrical surface of said plunger covers a different portion of the wall of said cylinder and thereby is adapted to vary both the point in the cycle of plunger reciprocating movement at which each inlet port is opened to the delivery chamber and the period of the cycle during which each inlet port remains open to said delivery chamber, separate conduits for supplying a fluid to each of said inlet ports, and a valve in the conduit supplying fuel to the inlet port positioned closer to the outlet port to prevent flow of fluid away from said cylinder.

10; A pump of the character described com prising a pump cylinder provided with a valvecontrolled outlet port at one end thereof, a generally cylindrical plunger slidably and rotatably disposed in said cylinder, said plunger and said cylinder forming a fluid delivery chamber, means for causing said plunger to undergo reciprocating movement, means for varying the rotative position of said plunger in said cylinder, said cylinder being also provided with two inlet ports positioned in space relation and at different distances from the end of said cylinder to be uncovered in a cycle of plunger reciprocating movement, said plunger being formed throughout a portion of its length in the direction of said delivery chamber of reduced diameter to provide a helical shoulder, the slope of the helical shoulder being upward in the direction of the inlet port positioned closer to the outlet port, whereby upon rotation of said plunger the cylindrical surface of said plunger covers a different portion of the wall of said cylinder and thereby is adapted to vary both the point in the cycleof plunger reciprocating movement at which each inlet port is opened to the delivery chamber and the period of the cycle during which each inlet port remains open to said delivery chamber, separate conduits for supplying a fluid to each of said inlet ports, a valve in the conduit supplying fluid to the inlet port positioned closer to the outlet sure on the fluid entering the inlet port positioned further from the outlet port, and means for placing a lower pressure on the fluid entering the inlet port positioned closer to the outlet port. 1

11. A pump for supplying and proportioning a plurality of liquids comprising a casing having a delivery zone, separate inlets for a, plurality of liquids to said delivery zone, an outlet from said delivery zone, a pumping element for controlling the introduction through said separate inlets of a plurality of liquids into said delivery zone and for discharge of resulting composite liquid through said outlet, and means for both varying the volume of composite liquid discharged through said outlet on each cycle of said pump, and also concomitantly varying the relative proportions of the separate liquids in said composite liquid.

12. A pump according to claim-11, wherein said 'varying means-is constructed to terminate the supply of one liquid at. low volume delivery on eachcycle, and to terminate the supply of another liquid 'at. high volume delivery on each cycle.

13. A pump of the character described, comprising a cylinder having a delivery zone, a plurality of inlet passages for separate liquids opening into said cylinder, a discharge passage from said delivery zone, a reciprocating plungerwithin said cylinder controlling communication on each cycle of said plurality of inlet passages with said delivery zone to thereby supply a composite liquid thereto, and means for both varying the volume of composite liquid delivered through said discharge passage on each working stroke of said plunger, and also concomitantly varying the relative proportions of the separate liquids in said composite liquid.

14. A fuel pump for supplying and. proportioning two difierent liquid fuels to an internal combustion engine comprising a casing having a delivery zone,. an inlet for one liquid fuel to said delivery zone, a second inlet for a second liquid fuel of different character to said delivery zone, an outlet from said delivery zone adapted to be 10 connected to 'said internal combustion engine, pumping element within said casing controlling communication of both of said inlets with said delivery zone to supply a composite liquid fuel thereto and for discharging composite liquid fuel from said delivery zone through said outlet, and

means for both varying the volume of composite liquid fuel discharged from said delivery zone through said outlet on each cycle of the pump, and also concomitantly varying the relative proportions of the said difierent liquid fuels in said composite liquid fuel.

15. A fuel pump in accordance with claim 14, wherein said second inlet is adapted to be connected with a source of high octane liquid fuel, said first-mentioned inlet is adapted to be connected with a source of lower octane liquid fuel, and said varying means is constructed to increase the proportion of said high octane liquid fuel in the composite fuel discharged through said outlet on each cycle as the volume of said composite fuel is increased and vice versa.

16. A fuel pump in accordance with claim 14, wherein said second inlet is adapted to be connected with a source of high octane liquid fuel, said first-mentioned inlet is adapted to beconnected with a source of lower octane liquid fuel and said varying means is constructed for an intermediate range of pump delivery to increase the proportion of said high octane liquid fuel in 1 the composite fuel discharged through said outv let on each cycle as the volume of composite fuel so discharged on each cycle is increased and vice versa, and to terminate the supply of the lower octane fuel and discharge only high octane fuel at high pump delivery on each cycle and to terminate the supply of high octane fuel and dis- The following references are of record in the file of this patent:

' UNITED STATES PATENTS Number Name Date 1,119,323 Shaw Dec. 1, 1914 1,891,082 Dodson Dec. 13, 1932 1,917,690 Beeh July 11, 1933

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