US2240158A - Fluid distributing system - Google Patents

Description

April 29, 1941. D, R. HlLLls v 2,240,158

- FLUIUDISTRIBUMG SYSTEM Filed March 4, 1937- 5 sheets-Sheet 1 ATTORNEY l April 29, 1941.- D. R. HlLLls 2,240,158

FLUID DISTRlBUTING SYSTEM Filed March 4, 1937 5` Sheets-Sheet 2 Wy v.

151 Fig. 6. 14s Y 107' lNvENToR D. R. HlLLis FLUID DISTRIBUTING SYSTEM Filed March 4, 1957 '5 lsheets-sheet s INVENTOR A TORNEY v www vApril 29, 1.941.

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-April 29, 1941, D. R. mms 2,240,158 y FLUID DISTRIBUT'ING SYSTEM Filed March 4, 1937 5 Sheets-Sheet 4 Fig. 10

OOGOOO TORNEY yApril 29, 1941. D. R. HlLLxs Z4-@,158

FLUID DISTRIBUTING SYSTEM Filed March 44,v 1937 5 sheets-sheet 5 Figc 13. n

INVENTOR ATTORNEY Patented pr. 29, 1941 FLUID DESTRIBUTING SYSTEM David R. Hills, Detroit, Mich., assignor, by mesne assignments, toReconstruction Finance Corporation, Detroit, Mich., a Vcorporation of the United States Appleman March 4, 1937, serial No. ,129,041V

A17 claims. t, (crisi-,7)

The present inventionrelates to a fluid distrib- '5 uting system and more particularlyto a dualline non-reversible fluid distributing system.

In the art of distributing fluids, especially in the lubricating art, there are conditions which require that a larger amount of fluid be dispensed at one place than at another; that theinterval between ejections of fluidat one place be greater than at another place; that at one time one kind of fluid be supplied and that at another time;v

another kind of iiuid be supplied at the same place, or that at one place one kind of fluid be supplied while at another place another kind of fluid be supplied.

There are many old and well-known iiuid dis- :1 5

pensing systems, all of which either distribute or attempt to distribute but one type of fluid ata time. The majority of these systems depend upon springs either to actuate valves controlling the dispensing pistons or to actuate control valves in 20 one direction, such as the valves controlling Various passages and ports, and, consequently, they are not positive in their operation; thus great loss results, both in eiciency of operation and in replacement costs to the user.

Of the many types of fluid distributing systems now on the market, some are entirely operated by hydraulic pressure; in fact there are two wellknown types of the lattenone known as the dual-line system and the other as the single-line reversible system. l

In the dual-line system in vogue before my present invention, the fluid is pumped alternately rst through one line and then through the other, thus requiring the use of a flow-reversing Valve. When heavy greases are handled in such a valve, the wear and tear becomes more and more pronounced, depending upon the frequency of operation of the moving parts. Hence a valve or moving part of a systemthat is in continuous operation soon tends to wear out some of the parts and the replacement costs become a heavy burden to the owner of the system.

When the dual-line system is adapted for autolmatic Operation, this necessitates the use of an automatically operated flow-reversing valve, which, to date, in addition to the above, is still a very expensive device to manufacture. In' many factories the said dual-line system is not used because the initial cost of the automatic flow-reverser is out of proportion to the cost of the rest of the system and the replacement cost makes the total cost almost prohibitive.

In the single-line reversible system, the fluid is pumped through the line, rst in one direction and then in the reverse direction ofv flow, thus also necessitating the use of a reversing valve which is subject to substantially the same conditions of wear and tear, highinitial cost and high replacement cost.

Moreover it is hard to maintain sufcient pressure in a long line, when handling heavy grease,

to operate the flow-reversing Valve by the return flow of the said grease.

In my copending application, Serial Number 116,773, led December 19, 1936, I have disclosed a `single-line uniflow-recirculating system that has many features and advantages over the prior systems, but, like them, it is adapted to handle but one Vfluid at a time.V

It is, therefore, the main object of my` present ,invention tov provide a systemv that will selectively dispense either Of two uids from separate reseryvoirs througha connected feeder or connected ,.feeders.

Another object of ymy invention is to provide a fluid distributing system wherein two distinct fluids such asoil and grease may be pumped through two associated pipe-lines and through associated feeders in such a manner that either of the fluids may be dispensed by any of the associated feeders, yby quickly madel changes, at the selection of the workman, without the intermingling of the two fluids, bothV uids being driven under pressure by means of but one pressure Vcreating means.

Another object of my invention isthe provision in a dual-line system for distributing iiuids, of a hydraulic operator adapted to drive a hydraulic'ally operated pump, the latter pumping fluid from one reservoir through an associated pipe-line, while the other line is connected to pumping means whereby pressure is created in .said last mentioned pipe-line and is connected to and adapted to operate the said hydraulic operator.' Y

In my aiore-said copending application, the system therein described embodies the following advantages and features not found in any prior 'art known to me, viz: y Y Y1. `The said system, is a positive, hydraulically operated, vone-way lfluidArecirculatingrand distrib-uting system. Y V

2. The said system is adapted for automatic operation without the use ci expensive flow-reversing valves.

3. A means-for control-ling the volume'of fluid pumped is provided in my said system.

l1. The volume offluid being pumped through theV line tothe respective feeders in my ysaid-sys;-

tem determines the frequency of operation of the hydraulic operators of the respective feeders and consequently normally determines the frequency of operation of the dispensing valves.

5. Means is provided in my said system for insuring operation of the dispensing valves of my feeders where resistance at the outlet points is to be overcome, said means consisting of an adjustable now-impedance member which may be adjusted to cause pressure to be developed in the line to any amount that may reasonably be required toy overcome the resistance at the outlets from the dispensing valves.

6. Means for indicating flow of fluid returning from the pipe-line of said system is provided, and each such visual indication of flow of fluid indicates that one or more of the hydraulic operators of the respective feeders has moved.

7. Individual adjustment for controlling the frequency of operation of the hydraulic operator of each feeder and consequently controlling the frequency of operation of the dispensing valves may be provided for at each feeder of said systcm, if desired, and such means may also be used for individual indications of the movement of the hydraulic operator valve of each feeder, and individual indication of each dispensing valve may be provided for, either by means of an indicating rod projecting from the valve itself or any suitable indicating means may be provided at each point where fluid is to be distributed, if desired.

8. The said system will handle practically any type of fluid, but is especially adapted for the handling of either grease or oil. I

9. In said system it is possible to service one group of receptacles in one sector and to shut olf` the dispensing port outlets in any sector where their use is not desirable.

10. The feeders used in the said system are compact and inexpensive to manufacture and they may be made with a Wide variation of the number of outlets from one feeder.

11. Each measuring valve of the said system may be provided with adjustable means to control the quantity of fluid dispensed by it, wherever this is required.

It is an object of my present invention to provide a dual-line fluid-distributing system that will embody all or substantially all of the above enumerated features of my single-line-uniflow recirculating system and also embody each of the following features and advantages:

1. It will permit the selective dispensing of the fluid carried by either of the pipe-lines through the dispensing valve or valves of any feeder associated with the pipe-lines, by merely connecting the feeder branch pipe to the pipe-line carrying the fluid desired.

2. It will cause the fiuid pressure created by one pump to hydraulically operate another pump associated with a second reservoir and a second pipe line.

3. It will maintain a constant pressure upon the main piston in the hydraulic operator which controls the pump piston in the hydraulically operated pump, determined by the adjustment of the pressure control or flow-impedance valve member, so that the hydraulically operated pump will supply only the volume of Afluid or4 grease required by the dispensing valves operatively connected to the pipe leading from the hydraulically operated pump. This feature preserves the pump from undue wear and thus reduces replacement of thepump operating parts to a minimum, which, as previouslystated; is

' indicator a very important feature when heavy greases are to be handled.

4. While maintaining sufficient pressure in one line to insure the operation of the dispensing valves operatively connected to said rst line, it will maintain only sufficient pressure in the other line to operate the dispensing valves to which 'it may be operatively connected.

5. It will recirculate fluid in one line, dispensing some of the fluid wherever desired, while merely pumping the required amount of fluid through the other line to the dispensing valves operatively connected thereto.

6. It will permit all the dispensing valves of a feeder to be shut off by merely turning one valve without stopping the operation of other feeders in the system.

The novel features that I consider characteristicof my invention are set forth with particularity inthe appended claims. The invention itself, however, both as to its construction and its method of operation, together with additional objects and advantages thereof, will best be understood from the following description of a specific embodiment, when read in connection with the accompanying drawings, in which:

Fig. 1 is a schematic view of a layout of the entire system with the top portion of one reservoir being broken off and the pressure regulating valve being shown in section;

Fig. 2 is a view partially in elevation and partially in section, taken on the line 2-2 of Fig. 7 showing a portion of the hydraulic operator and associated mechanism for actuating the hydraulically operated pump;

Fig. 3 is a sectional view taken on the line 3-3 of Fig. 7;

Fig. 4 is a sectional view taken on the line 4-4 of Fig. 7;

l Fig. 5 is a sectional View taken on the line 5--5 0f Fig. 3;

Fig. 6 is a view similar to view 5 showing the operative parts in a different position;

Fig. 7 is a sectional view taken substantially on the line 'l--T of Fig. 2;

Fig. 8 is a view similar to Fig. 7 showing the operative parts in a different position;

Fig. 9 is a side elevation of a feeder used in this system;

Fig. 10 is a section through the feeder taken on the line l-Hl of Fig. 1l;

Fig. 11 is a sectional view of the feeder taken on the line H-H of Fig. 10 with a discharge pipe and control valve shown partly in section and partly in elevation;

Fig. 12 is another sectional view of the feeder taken on line IZ-IZ of Fig. 10;

Fig. 13 is a sectional view taken on a line l3-l3 of Fig. 11 showing the operative parts of the hydraulic operator which controls the operation of myfeeder used in this system;

Fig. 14 is a view similar to Fig. 13 showing the operative parts of the hydraulic operator in the opposite position;

Fig. 15 is a sectional view of my volume control valve taken on a line IBL-I5 of'Fig. 17;

Fig.A 16 is a sectional view of the volume control valve taken on the line I 6;!6 of Fig. 18;

Fig. 1'7 is a sectional-view ofthe said volume control valve of line H-H of Fig. 15 and Fig. 18'is `a sectional view of the said volume control valve takenoir the line Iii-I8 of Fig. 15.

Fig. 19 is a detail sectional view of one rof my dispensing` valves provided with one form o'f ll ...J

eratively connected feeders mayv dispense fluid from :the second pipe line. Each Vdispensing valve is provided with two able electric or other motive means for driving said pump is provided.

The pump discharges to a pipe line leading into a volume control valve, from whence the continuation of the pipe line is provided with a T connection forming two branch pipes. One

branch of the continuation of the pipe line leads;`

to another T connection providing fluid connection to a pressure gauge and to the inlet port of a hydraulic operator and a return pipe carries the operating iiuid back to the first mentioned reservoir.

The hydraulic operator operates a hydrau-v` lically operated pump associated therewith, which is preferably mounted on the housing of the first reservoir and the hydraulically operated pump, in turn, is connected to and I have-1' shown it as supporting a second reservoir from which the pump is adapted to pump a second fluid through a second pipe line connected thereto. v

The main pipe line continues from the rst mentioned T connection and returns to the first mentioned reservoir whereby a complete circuit is provided from the rst reservoir and through the pump, volume control valve, pipe lineV and associated members and back to said rst reservoir.

Each of my feeders is also provided with a hydraulic operator and the main pipe line has a direct fluid connection with each hydraulic operator of each feeder. Each feeder is provided with one or more dispensing valves.

The fluid passing through the main pipe line circuit operates the hydraulic operator of each feeder and some of it may be dispensed through the dispensing valves of any feeder by means of a short pipe connecting the main pipe to the feeder dispensing inlet port. The balance of the fluid in the main line returns to the first mentioned reservoir after passing through all connected hydraulic operators and operatively connected feeders, by way of a pressure regulating valve which may be adjusted to provide sufcient pressure in the line to insure the operation of any of the dispensing valves which are operatively connected to the first pipe line. Substantially the same pressure is maintained in the second pipe line as the same pressure is constantly maintained on the hydraulic operator operating the pump piston that forces liquid into the second pipe line.

The second pipe line of the dual-line system does not entirely complete the circuit from the second reservoir and back thereto, but connects the hydraulically operated pump with the feeder dispensing inlet port of such feeders in the main circuit as the workman desires to connect through short branch pipes. Fluid from the second reservoir may thus be pumped to the respective feeders connected to the second pipe line, whereby the dispensing valves of said opdischarge outlets, each of which is preferably connectedl to a distributing branch pipe leading to a receptacle or to a bearing although the discharge branch pipes from any one or more ldispensing valves may be suitably connected so as to' discharge from a common discharge pipe where thisfis desired.

IIhe numeral I representsany suitable body member which may be supported or provided with any suitable base 2, the body being provided with a suitable reservoir V3. Any nonpositive type of pump may be connected to the reservoir. By non-positive, I mean a pump which permits slippage so that when the volume control valve is adjusted to reduce the volume, the pump automatically pumps less fluid Without serious consequences resulting to the pump. I have illustrated a gear pump 4 connected with an electric motor 5 for driving the same.

Mounted on the pump 4 is a flow control valve 9, connected to the pump through a pipe line II through which all fluid from the pump must pass. The flow control valve is provided with a return pipe I3, leading back to the reservoir, for conveying leakage back to the reservoir as will hereafter be described. The continuation of the pipe line II connects the flow control valve, from its outlet port, with a T connection I5, from which the main pipe line, hereafter designated by the numeral I'I, and another pipe line, designated by the numeral I9, lead.

The pipe I9 is provided with a second T connection 2I, affording fluid connection to a pressure gauge 23 and to an inlet port 25 of a hydraulic operator 2I. Said hydraulic operator is provided with a discharge port 29 from which a continuation of the pipe line I9 leads to the reservoir 3, thus returning to the reservoir the operating fluid which passes through the hyd-raulic operator 21.

In Fig. 1, I have shown eight feeders connected tothe main pipe line I'I in such manner that the hydraulic operator (hereafter described) of each feeder will be operated by uid pressure, each of the feeders being designated by the numeral 35, although it is obvious that the number of feeders may be varied, each feeder having a hydraulic operator through which operating iiuid from the pipe line I I passes.

Each feeder 4is provided with an inlet port and an exhaust port, as will hereafter be described, permitting fluid to operate the hydraulic operator which controls the operation of the dispensing valves located in each of my feeders. Each feeder is also provided with a separate inlet port whereby fluid connection is made with the dispensing valves,

It win be noted in Fig. 1 that I have shown two branch pipes I 'Ia connected to the main pipe I'I, each ofwhich leads into an inlet port leading to the dispensing Valves of an associated feeder. f

In Fig. l, the hydraulically operated pump is illustrated and designated by the numeral 4I, said pump being supported upon the body I above the rst 'reservoir 3 and, in turn, the pump 4I has fluid connection, as will later be described, With a second reservoir 43, shown supported thereabove.

Leading from the pump 4I is a second feeder supply pipe line 45, and in the embodiment shown in Fig. 1, this pipe line is provided with ve connections 41 for communication with the fluid inlet ports leading toi the dispensing valves of a number of the associated'-feeders.` The end of the pipe line 45 also connects with a. feeder, in this instance being shown as the. lastA feeder of the main circuit. It is obvious that the respective types of branch pipes can be` substituted for each other so thateither uid supply line may be connected to the inlet vport leading to the dispensing valves of any feederV A shut-off valve 49 is provided adjacent the second inlet port of each feeder, whereby all the dispensing valves of each feeder may be turned onfand off at will.

The main circuit includes a pressure control valve 55 which preferably Valso is provided with a sight feed or visual indicator. This valve may be mounted in any suitable manner to permit return flow of fluid into the reservoir 3. For convenience, Iliave shown it mounted on an extension or bracket 56 supported on the body provided with a screw threaded aperture 51.

The pressure control Valve and sight feed indicator comprises a body member 5S, which, in this instance, is externally screw-threaded at its lower portion 6| to fit into the screw-threaded aperture 51. Said body member 59 is provided with a large cylindrical bore 65 in the base thereof projecting upwardly to a substantial degree and a transparent member S1, such as glass, is mounted therein in any suitable manner.

The lower end of the bore is suitably plugged by a pierced member as shown at 69 and another portion of pipe i1 is screwed thereinto and leads into the reservoir 3.

The top portion of the body member 59 is provided with a cylindrical bore 1| for a substantial distance and thereafter a smaller bore 13, preferably in axial alignment therewith, is pierced a substantial distance to form a cylindrical guide 13 for a reciprocating piston valve 15 which is mounted therein. At the base of the cylindrical passage 13, a return passage 11 connects to the pipe-line return port 19.

The piston valve is provided with a stem 8| cf reduced diameter and with a guide head 83,

the latter being mounted in the enlarged bore 1l.y

A pierced cap 85 is suitably secured to close the top of the member 59 and an adjustable screw member Si, having an elongated screw threaded siem Si) is threadably mounted in said cap. The base of the stem 55 is adapted to press upon a disk Si mounted in the bore 1|. Between said disk and said piston guide head 83 is a strong compression spring 93.

The piston bore 13 is provided With a passage 95 leading from a point substantially midway thereof and terminating in a nozzle 91 which discharges into the enlarged bore 65 of the visual indicator.

Thus it will be seen that some of the fluid in the main pipe l1 visibly returns to the reservoir 3 through this pressure control valve and that the screw S1 may be so adjusted as to require greater or less pressure, as the case may be, to force the piston valve- 15 upwardly so as to make an open connection between passages 11 and 95 whereby the returning fluid passes into and throughthe visual indicator from which it is drained into the reservoir 3.

As a result of the adjustment of said screw 31 the pressure in the line |1 may thus be controlled.

t is desirable to maintain sufcient pressure in the system to overcome all anticipated resistance, that of the fiuid flowing inthe lines, that of the hydraulic operator and hydraulically .operated pump,v that of the'hydraulic `operating units of -the measuring feeders and that of the measuring tons, and that encountered between the dispens- .ing cylinders and the bearings and particularly that of the bearings themselves.

It is immaterial whether the dispensing feeders are coupled to the working fiuid pipe line l1, which is usually an oil line, or to the other line, which is usually a grease line, or whether some are connected to one line and some to the other. Heavy grease usually requires about twice as much pressure as does oil when used in lubricating systems since it offers greater resistance to flow. Hence I have made the area of my operating piston in my hydraulic operator which handles the working fluid, twice the area of the pistonv in my hydraulically operated pump, which pumps the grease. Thus the grease is under substantially double the pressure that is on the oil.

If all the feeders are connected for discharging grease,oi1 under low pressure will actuate the hydraulic operators of the feeders (hereafter to be described) so as to reverse the inlet and outlet connections of the dispensing feeders, but there will be" insucient pressure in the grease line to actuate the dispensing pistons of the dispensing valves at the proper intervals unless some means is provided for either quickly building up or maintaining therequired pressure in the grease line.

Hence I have provided the previously described pressure control means or back pressure valve 55. `By the adjustment of its screw 81 any desired isthe actuating fluid for the line |1 and when all the feeders are connected for discharging grease received from line 45. Screw 81 is thenadjusted until lthe gauge 23 records a pressure of about 550 pounds inthe oil line, at which time the operator knows that about 1100 pounds pressure is in the 4grease line. -He may inspect the bearings or other suitable -indicating means as illustrated in Figs. 19, 20 and 21 hereof to see that the discharge of Va measured quantity of grease is being delivered to each bearing at the proper intervals,

and if not he may `adjust the said screw 81 to obtain a Vsufficiently high pressure to assure proper operation.

Referring now to -the hydraulic operator 21 4which operates the pump 4|,` as shown in detail in Figs. 2, 3 and 5-8, inclusive, this operator comprises a casing ||J| provided with a large aperture or piston guidingfbore |03 extending therethrough and smaller,V valve receiving, apertures |05 and |01 ,drilledtherethrougn in spaced relation and preferably parallel thereto to provide a unit which iscompact and conveniently connectible. The

casing |0| is preferably a suitable casting commounted in any desired location.

In the present instance, the hydraulic operator forms a part of my system and for this reason is l preferably mounted as I have shown on the top of the body member the base and its pedestal portion being extended so as to cover the reservoir 3 Aand'to form a base portion and similar pedestal forthe pump` 4| which is operated by my said 1, hydraulic operator.

`'Iheimovable operatormember for translating the pressure of the working fluid into mechanical motion for doing useful work, which-in this instance is to operate my pump 4|, comprises a piston |09 slidably disposed in the piston guiding bore |03. The operator piston |09 comprises a substantially cylindrical body of a suitable diameter for sliding freely in the cylindrical aperture |93, and it is provided with a piston rod, or operating shaft which is connected, as by threading or welding, to one end thereof. The piston rod projects and connects with a mechanical element, which in this instance is the pump piston of pump 4| to be hereafter described.

The ends of the piston guiding cylinder |03 are provided with internal threads for operatively receiving a cylinder head plug |3 inone end thereof comprising a laterally projected shoulderY ||5 which may be of hexagonal or other suitable conformation for receiving a wrench. In the other end of the piston guiding bore |03, a cylinder head plug ||1 is threadably secured, which comprises an outwardly projecting sleeve H9 having an enlarged counter-bore |2| extended therein to provide a packing gland wherein packing material |22 is rmly compressed around the operator shaft |i| by means of a packing ring |23. For compressing the said packing which surrounds the rod the inner end of the packing ring |2Sis suitably tapered and a wide flange |25 is provided upon the outer end for engagement bya packing nut |21, which is internally threaded to be received upon external threads providedfupon the packing sleeve.

A fluid responsive piston valve |29 is slidably disposed in the valve receiving aperture |01 for controlling the application of iiuid pressures to reversely operate the working piston |09. The iiuid responsive valve |29 is of the dumb-bell piston type and comprises ilow restricting heads |3|, |33, |35 and |31 joined together in spaced relation by 'connectors |39, |4| 'and |43, which are of reduced cross-sectionV to permit the fluid to-flow freely therearound. The intermediate connector 46| is of larger diameterl than the other connectors to provide interlocking recesses |45 andl |41 which are disposed at the ends of the connector adjacent the heads |33 and |35 respectively. The valve bore |01 is provided with internal threads adjacent the opposite'ends thereof for receiving suitably threaded plugs |49, which are turned rmly therein to seal the ends of the aperture, and also to provide limiting stops for the valve. Projecting outwardly from the outer ends of the valve heads |3| and |31 are suitable stops |5| provided for abutting the adjacent plugs |49 to thereby limit the position of slidable valve |29 in spaced relation from the ends of the bore |01.

The piston controlling valve |29 is in turn operated by fluid pressures applied alternately to the ends thereof, in 'accordance with the movements of a piston driven valve |53 which is slidably disposedin the aperture |05. The piston driven valve |53 comprises flow restricting heads |55, and |51, .connected in spaced relation by a connector |59 of reduced cross-section to provide for the free flow of iiuid around it. At one end, the head |53 is joined through a connector I5 of reduced cross-section, to the inner end of a valve rod |63. The valve actuating rod |63 projects outwardly from. the end of the aperture |05 through a packing xture |65 which comprises a suitable packing gland and nut for providing a slidable seal around the rod, From the valve head |55, in the opposite end of the valve, a reduced connector |01 is joined to the inner end of a rod v|09 which projects from the opposite end of the bore |05 through a suitable packing xture |1|. Uponthe outer end of the stopvrod |69, an annular ring |13 may be firmly secured, in any suitable manner, as by threadable engagement thereon, by which the relative position of the connected valve may be readily ascertained when it is desired to adjust the adjustable stops hereafter to be described.

The valve rod |63 is provided with a pair of adjustable stops |15 and 11, see Fig. 1, secured in spaced relation thereon inany suitable manner. For driving the valve rod |63, the piston rod is provided with an actuator |19 which is secured adjustably thereon as by a clamping bolt 8|, see Fig. 2, on each sidefor drawing up a clamp |82. The upper portion of the actuator |19 vextends upwardly from thev piston rod adjacent the valve rod |63 between the stops |15 and |11 thereon. 'Ihus as the piston rod is slidably operated by its piston, the actuator |19 alternatively engages the stops on the valve rod to throw the valve |53 to its alternative positions after` any desired predetermined movement of the piston rod has been completed.

'In its operation, the piston driven valve |53 controls iiuid conducting means for reversely operating iiuid responsive valve |29, as will be subsequently set forth. I provide means for preventing the simultaneous movement of both of said valves. For this purpose, I provide av slidvable interlocking pin |83, which is slidably disposed in an aperture 85 which extends directly between the center points of the valve apertures |05 and |01 in the casing. The interlocking pin is provided with tapered or substantially rounded ends which are thus disposed for operatively engaging recesses |81 and |89, which areY provided in the driven valve |53 and also with interlocking recesses and |41 provided in the uid responsive valve |29, whereby the cammed surface of said recesses on any Valve that starts to move will force the locking pin in an opposite direction,and as the locking pin is longer than the'aperture |85 in which it is mounted, thepin will be forced into one of the rrecesses of the other valve so as to prevent simultaneous movement of said valves.

Working fluid enters the casing |9| under pressure in the line |9 through the port 25, said pipe being threadably connected tothe outer end of the inlet port 25 and as shown in Figs. 5 and 6, passes through a passage |95 into the valve bore |05, at substantially the middle thereof. Fluid pressure is thus continuouslyA applied in the space between the valve heads Vandl |51 of the valve |53. Said valve |53 is arranged to reciprocate through a distance which is slightly less than the distance between the heads. From the mid-point of the valve guiding bore 05, a passage |96 continuously connects, as shown in Figs. 2 and 3, into the mid-point of the valve guiding bore |91, whereby the line pressure is also continuously applied into the space between the heads v|33 and |35 of the uid responsive valve |29.

From the centrally charged space in the driven valve |53, high pressure uidis discharged through a passage |99 into the left hand end of the valve guiding bore |01, as shown in dotted lines in Fig. 5. Hence, driving the valve |53 to the right tends also to move the fluid responsive valve |29 in the same direction. The passage |99 connects into the valve vbore |05 at a point suitably disposed to the right of the center thereof controlled by the valve headl 51 for successive connection with inlet port pressures every time the driven valve |53is moved to the right.

When the driven valve |53 moves tothe left, its head |55 uncovers the port of a passage 29|, shown dotted in Figs. 5 and 6, which extends through the casing IBI and discharges fluid into the right hand end of thevalve guiding bore |31 and the fluid responsive valve |29 is thusmoved to the left, as shown in Fig. 6. The stopsV |5| on the ends of the fiuid responsive valve |29 serve to stop it in spaced relation from the end plugs |49 whereby the fluid can enter freely from either passage |99 or 23| to connect through the valve |29 to its alternative position.

The reciprocating motion thus imparted to the valve |29 discharges the high pressure working uid from the space between the heads |33 and |35 alternatively through passages 233 or `235 into the responsive right or left hand end of the piston guiding aperture |93, as shown in Fig. 7. The opening ports of the passages 253 and 235 are suitably disposed in bore |31 for control between movements of the valve heads '|33 and |35 respectively whereby movement of the fluid responsive valve |29 to the right, passes fluid through passage 235 to drive the piston |39 to the left and vice versa.

The passages 203 and 235 connecting to therends of the piston guiding bore |53 serve alternatively for intake and exhaust. As shown in Fig. '7, fluid is being discharged through passage 205 to move the piston |39 to the left. As this operation takes place, the uid previously charged into the cylinder at the left oi the piston |93, will now be exhausted through passage 203 into valve bore |51, from which it passes from an exhaust passage 231 into an exhaust passage 239 and out of outlet port 29 leading to a continuation of the branch pipe I9 which returns the operative iiuid to the reservoir 3. Above the exhaust passage 231, another exhaust passage 2|3 is interconnected between the valve ports |05 and |51 for handling fluid exhausted from the right hand end of bore |01 through passage 23| into bore .f

|35 around reduced portion |61 of the driven valve |53, as shown in Fig. 5` Equally spaced on the opposite side from the center, is an exhaust passage 2|5, connecting from the exhaust passage 259 into the valve bore |91 for connection with the passage 205 to receive uid exhausted by the return stroke of the piston |59, and an exhaust passage 2|1, corresponding to the'passage 2| 3, similarly connects bores 35 and |51 on the opposite side of the center.

As the piston |59 is thus operated from side t0 side, it in turn drives the valve |53 through the slack motion connectors |15 and |11. The motion of the drivenvalve |53 from end to end of its bore |35 applies fluid pressures to opposite ends of the fluid responsive valve |29 through the fluid conducting connections thus established and this in turn reciprocates the fluid responsive valve |29 in its bore to apply reversely operating fluid pressures from the inlet port 25 to in turn reversely operate the piston |39. Operating cycles comprising the above operations continue successively so long as suitable fluid pressures are applied in the inlet port 25.

Referring now to the hydraulically operated n' pump 4|, this comprises a casing 22| provided with a large aperture or piston guiding bore 223 extending therethrough and a smaller, valve receiving aperture 225 drilled through an offset portion 221 thereof. The casing 22| is preferably a suitable casting having a suitable base and, in this instance, I have shown the casing of both the hydraulic operator 21 and of the pump 4| as made from the same casting having a common elongated base |32 witha common pedestal portion |34.

Slidably disposed in the pump piston guiding bore 223 is a pump piston 223 which is connected to the `other end of the piston rod |I| in the same manner that piston |59 is connected thereto.

The ends of the piston guiding aperture 223 are plugged in the same manner that the ends of the piston guiding aperture |53 are plugged, and the ends of the valve receiving aperture 225 are suitably plugged after inserting a reciprocatable piston Valve 23|.

Substantially midway of the valve receiving aperture 225 is a fluid outlet port 233 to which is connected one end of the pipe line 45.

From the left end of bore 223 a passage 235 connects to the left end of the valve receiving bore 225 and from the right end of the bore 223 a passage 231 connects to the right end of the valve receiving bore 225.

Substantially midway of the bore 223 a fluid inlet passage 211|, see Fig. 4, connects the reservoir 43 to said bore whereby fluid in the reservoir may flow by gravity as well as by suction into the bore 223 from whence it is discharged through either passage 235 or 231 into passage 225, moving piston valve 23| to open port 233 to the passage in which fluid is then flowing and closing it to the other passage.

Referring now to the hydraulically operated feeders 35, each of which may be provided with one or more dispensing valves, one such feeder is shown in detail in Figs. 9-14 with modifying details shown in Figs. 19-21, inclusive. Each feeder comprises a metallic body or casing 25| for housing the multiple elements therein. For receiving iluid from the pipe line |1, I provide an inlet port 253 comprising a passage drilled longitudinally therein fromrone end. The inlet port 253 is provided with internal threads 255 adjacent its outer end for convenient connection with the end of the pipe line I1 which carries andsupplies the fluid under pressure for operating the hydraulic operator of my feeder.

For discharging the fluid to the continuation of the pipe line I1, after it has operated the hydraulic operator of the feeder in a manner to be subsequently described, I provide an exhaust port 259 by drilling a passage longitudinally into one end of the casing, preferably from the end opposite from the inlet port to facilitate connecting the device with the continuation of the pipe line |1. The outer end of the exhaust port 259 has internal threads 23| for convenient connection with the continuation of said pipe line l1.

Fluid dispensing ports 255 and 256 are provided, and, for convenience, they are arranged respectively in upper and lower horizontal rows disposed in the two opposite sides of the feeder casing 25| for dispensing fluid therefrom. Ports 255 are shown in cross-section in Fig. 12 and ports 235 are shown in cross-section in Fig. 1l. These ports are suitably internally threaded to facilitate connection with individual dispensing pipes 231, as shown in Fig. 1, usually extending separately to the various stations or bearings to be served, and each of these pipes may be provided with a stop cock 238, if desired.

For dispensing the fluid from the ports 255 and 235 automatically in response to unidirectional pressure applied by the fluid in` the-inlet port 253 of the feeder, I provide dispensing valves and a dispensing fluid inlet port and communicating passages to be hereafter described and a hydraulic operator for controlling the operation of said dispensing valves. My hydraulic operator, as used in the feeder, comprises a hollow piston 299 which is slidably disposed in Va cylindrical aperture or bore 21| extending axially through the casing, and which operates reciprocatively therein. The construction and o-perationof my hydraulic operator, both as used in the feeder and as used for operating the pump, is also disclosed and described in my co-pending application, Serial Number 113,873, entitled Hydraulic- Operator and filed December 2, 1936. The construction and operation of my feeder as used in this system is also disclosed and described in my co-pending application, Serial Number 114,323, entitled Multiple feeder for uni-flow system and filed December 5, 1936.

The opposite ends of the hollow piston 209 are closed by piston plugs 213 and the cylinder bore 21| by Cylinder plugs 215 which are threadably secured therein. To one of the piston plugs 213, an indicator rod 211 is connected, as by threading or welding, and it projects from the casing through the adjacent cylinder plug 215 which is suitably apertured and provided with a packing nut 219 for compressing suitable packing to provide a sliding shield around the rod in a manner that will be readily understood. As the hollow piston 269 reciprocates in the feeder casing 25|, the projected indicator rod 211 provides external indications of the continual operation of the device.

Slidablydisposed in the hollow piston is a piston valve 280 of the dumb-bell type comprising fluid flow restricting heads 23|, 283, 285, and 281, connecting by connecting rods 29|, 293, and 295, of reduced cross-section to permit uid to flow freely around.

Spacing stop pins 296 project from opposite ends of the piston valve 289. The middle connector 293, which is smaller in diameter than thel bore 291 within the piston, is larger than the other connectors in order to provide grooves 299 and 390 at opposite ends for the purpose of engaging the same with one end of an interlocking pin 30| which is slidably disposed in a suitable aperture extending through the side wall of the hollow piston 269 near its mid-point. The pin 36| is longer than the aperture in which it is slidably disposed. A camming plug 303, which is inserted through a suitable aperture in the base wall of the feeder when viewed as in Figs. 9 and 10, is provided with recesses 395 and 301 for engaging the outer end of the locking pin 30|. The camming plug 393 has an enlarged head 309 which is threaded for accurately seating it in an enlarged counter-bore 3|| which is internally threaded for receiving the same. A groove 3|0 is provided in the inner end of the camming plug 393 for receiving the outer end of the locking pin 39| and, in cooperation with the recesses, prevents rotation of the hollow piston.

The camming recesses 305 and 301 on the inner end of the camming plug 303 are spaced apart in an axial direction in the casing 25| and the distance between them is substantially equal to the distance which the hollow piston 269 is free to slide in the cylinder bore 21|. This distance is determined by the length of the hollow piston 269 and the projected positions of the inner ends of the cylinder plugs 215. During the slidable movements of the hollow piston 269 -in the casing, the interlocking pin 30| is -forced upwardly by a camming surface of one of the recesses of the camming plug 303 so that its other end engages in a groove in valve r28|) to hold the said slide valve 280 until the movement of the hollow piston is completed when the slide valve is released, and conversely, when the parts are in position for the slide .valve to shift, a cammed surface of one of its grooves causes the pin -to be depressed into either o-f the camming recesses of the camming plug and thus to prevent movement of the hollow piston 269 simultaneously therewith.

For admitting the high pressure fluid into opposite ends of the cylinder bore 21| to reversely work the hollow piston 289, I provide a passage 3|5 which leads from the inlet port 253 transversely through the side wall of the bore 21| substantially at the middle of the casing. Near its mid-point, the side wall of the hollow piston 269 is pierced by a passage 3|1 and a groove 3|9 is cut from the outer end axially in theouter surface of the piston whereby a continuous connection is provided to supply fluid pressure in the piston 269 in all positions thereof. The iluid pressure is thus applied around the middle connector 293 of the slide valve in the space in the piston between heads 283 and 285. From the middle of the piston 269 the uid is -passed through a port 320 and an axial passage 32| into the left hand end of the cylinder bore 21| thus shifting the piston 269 to the right, at which time the fluid in the right hand end of bore 21| (see Fig. 13) will be exhausted through a passage 325 and a port 323 into the hollow piston between valve heads 28| and 283 and thence through port 340 and ports 331 and 344 into exhaust port 259. Port 340 is adapted to connect with port 344 at all times, being provided with an extension in the form of a groove in theouter surface of the hollow piston 259. During this operation the slide valve stays in the same relative position to the piston 269, having its head 295 to the right of the port 320.

Pressure may now enter the hollow piston from inlet port 253 through ports 333 and 33| and Will shift the slide valve 280 to the left, exhausting uid from the left of the hollow piston through ports 335 and 331 which now register, the parts thereafter being in the position shown in Fig. 14. The head 283 of said `valve 230 is now at the left of a port 323. Fluid is then passed from the hollow piston through port 323 and ythrough an axial passage 325 into the right hand end of the cylindrical bore 21|, causing the hollow piston vtomove to the left, i. e., from the position shown in Fig. 14 to that shown in Fig. 13, at which time the iiuid in the left hand end of bore 21| will be exhausted through passage 32| and port 320 into the hollow .piston between valve heads 285 and 281 and thence through port 342 and ports 34| and 346 into exhaust port 259. Port 342 is adapted to connect with port 346 at all times, being provided with an extension in the form of a groove in the outer surface of the hollow piston 269. The hollow piston carries the slide valve 280 with it in the same relative position until the hollow piston completes its stroke to the left, whereupon the interlocking pin is released at one end and thereafter the slide valve 280 will be shifted to the right, as shown in Fig. 13 due to fluid under pressure entering the left end of said hollow piston 269 through ports 321 and 329 and will exhaust fluid from inside the right end of said hollow'piston throughv ports 339 and 34|, which then register.

During the movement of the sliding valve, the interlocking pin 39| will be forced into one of the recessesof the camming plug so as to prevent simultaneous movement of the hollow piston.

It will thus be seen that the application of iiuid pressure in the inlet port 253 causes pressures to be applied alternatively through the passages 32| or 325 for reversely moving the hollow piston under the control of the slidable valve 289 carried therein, and also the movement of the piston completes iiuid conducting connections for successively reversely operating the sliding valve.

It is obvious that as some fiuid in the line I1 is discharged through some of the feeders, the hydraulic operators more remote from the source of supply will operate somewhat slower than the more adjacent ones. Therefore it becomes necessary in some installations to vary the frequency of operation of the hydraulic operators of certain feeders and for this purpose I provide the indicator rods 211 with their associated parts 215 and 219 in different sizes so that more or less iiuid may be required in each end portion of the bore 21| in order to reciprocate the hydraulic operator and a similar indicator rod 211 may be attached to the reverse end of the hydraulic operator and similar adjustments may be made.

From the respective roWs of dispensing ports 255 and 256, measured quantities of iiuid are discharged alternatively and successively by the continued operation of the hydraulic operator. For this purpose, the side wall of the hollow piston 299 of my hydraulic operator is drilled to provide a passage 343 (Fig. l0) extending axially therethrough, and the ends of the passage are suitably yclosed as by metallic plugs 345 threaded or welded therein.

The uid dispensed from the elongated dispensing passage 343 in the piston to the respective dispensing ports 255 and 266 is measured and this is accomplished in measuring chambers 349. There are half as many dispensing chambers as there are ports 285 and 266, since each measuring chamber connects at each end thereof to a different dispensing port. A feeder may have one measuring chamber and two dispensing ports or any number of measuring chambers with twice as many dispensing ports.

Each measuring chamber 349 comprises a cylindrical bore drilled transversely through the casing 25| to slidably receive a measuring piston 35|. The ends of the measuring chambers 349 arey provided with counter-bores 352 which are threaded for receiving plugs 353, which may have wrench receiving apertures 355, as shown in Figs. 9, 10 and 11, or may be provided with other adjustable and/or indicating devices as will hereafter be described. Spacing pins 351 extend from opposite ends of each measuring piston 35| for abutting the end plugs 353 to stop the pistons in spaced relation therefrom in the usual manner.

For adjusting the degree of movement of the t measuring piston 35|, an adjustable threaded stop rod 359 may be threadably mounted in an adjusting plug 33|, as shown in Fig. 11, which may be conveniently installed in any of the chambers where it is desirable to provide for adjusting the measured quantities of fluid discharged therefrom. A wrench receiving portion 363 of square or other suitable conformation may be provided for installing or removing the adjustable plug 36 I.

A conduit` passage 365connects from one end of each measuring chamber 359 and extends toward the axis ofthe cylinder bore 21| for intersection with the side wall thereof. From the opposite end of each measuring chamber, a passage 361 extends to similarly intersect the walls of the cylinder bore 21|, but at a smaller angle from the chamber 349. The respective opposing passages 355 and 361 of each measuring chamber 349 thus connect into the cylindrical bore 21| from alternately opposed sides of each succeeding chamber 349, that is to say, that passage 365, which is directed toward the axis of the bore from one side of the first measuring chamber, is connected from the opposite end of the next measuring chamber, and so on, as may be seen in Figs. 10, 1l and 12. Throughout the length of the casing 25|, the measuring chambers 349 are thus provided with the end connecting passages 355 and 361 disposed on alternatively opposite sides of the casing.

As the piston 259 slides in the casing, it dispenses fluid from the elongated dispensing passage 343 into the ends of the measuring chambers 349 through passages 359 provided in the piston and disposed in alternatively opposite directions for connecting with the passages 335. By thisarrangement the measuring piston 35| in each measuring chamber is moved in the reverse direction, as compared with the adjacent pistons. As shown in Fig. 11, the measuring piston 35| has completed its movement to the right in the measuring chamber, and in so moving it discharged a predetermined quantity of fluid which had been previously charged in on the opposite side of the piston. The dispensed fluid passed out through an arcuate groove 31 I, cut in the peripheral outer surface of the right side of the piston for connecting with the inner end of a passage 313, through which the dispensed fluid passed out of the adjacent dispensing port 266.

In the next adjacent measuring chamber, as shown in Fig. 12, the uid under pressure also passed from the dispensing passage 343 by Way of passages 359 and 365 into the right end of the chamber 349, forcing the measuring piston 35| to the left end and dispensing the fluid previously charged therein through the passage 391 around arcuate groove 315 in the left side of the piston and thence by way of passage 311 out of the adjacent dispensing port 265. There are a total of eleven arcuate grooves 31| and 315 and a tota-l of eleven passages 359 located in the hollow piston 269, making a total of twenty-two passages, eleven of which are equidistantly and alternately disposed on each side of the hollow piston 259. One side of the piston will have five arcuate grooves and six passages 359 piercing it and the other side of the piston will have six arcuate grooves and five passages 339 piercing it. Y

There are ten passages 365, five in each side of the casing and ten passages 361, ve in each side of the casing. Each measuring chamber 349 communicates directly with one of each of said passages 355 and. 361, each one connecting one end of said chamber t0 the piston bore 21|. The passages 335 and 351 serve alternately as inlet and discharge passages to their respective measuring chambers. When iiuid enters a measuring chamber 349 from its associated passage 395, it discharges a measured quantity of fluid from the other or previously charged side of its piston 35| through its associated passage 391 which will then connect with an arcuate groove. When the hollow piston 269 shifts so as to permit pressure iluid to flow through a passage 359 to a passage 35,1, fluid will then enter the measuring chamber 349 through said passage 361 and its piston 35| will discharge iiuid from the previously charged side of the chamber through its associatedv passage 395.

Looking at Fig. 10, it will be seen that in the embodiment shown, six grooves 315 are indicated inv dotted lines, located on the far side of the piston, all but the extreme left one being shown in position to discharge through the far side outlet ports 295. In the same Fig. 10, it will also be noted that a portion of the bores of ve passages 339 are shown and they connect to the live passages 365, shown in dotted lines, which connect to the far side of the first, third, fifth, seventh and ninth measuring chambers 349, counting from the left. The seco-nd, fourth, sixth, eighth, and tenth measuring chambers are shown having passages 331 (shown in dotted; lines) which connect the far side of said measuring chambers with five of the six arcuate grooves 315 as shown.

There are twenty outlet or discharge ports 255 and 256, five ports 255 and five ports 253, a total of ten, being located on each side of the feeder, and there .are twenty casing discharge passages 313 and 3.11' connected thereto, but there are only ten measuring chambers. Hence, when fluid enters one side of a measuring chamber 349, as seen in Figs. 11 0r 12, the hollow piston valve 2159` is Vin yposition to close one of' its associated discharge passages and ports. only ten of the twenty discharge ports discharge at one time. In Fig. 10, five ports 265 are shown (in dotted lines) connected for discharging on the far side of the casing 'from the second, fourth, sixth, eighth and tenth measuring chambers 339, while the rst, third, fifth, seventh and ninth measuring chambers 349 are in position to discharge simultaneously therewith through the five discharge ports 253 that are located on the side vof thecasing shown in Fig. 9.

As there are twenty-two passages piercing the hollow piston 269, andas eleven of these are eduidistantly and alternately spaced on each side of said piston, twenty of them are, consequently,

'in position 'to register with the twenty passages 335 and 351 in either extreme position of the hollow piston 239, ten of the twenty passages 355 and 361 acting as inlet passages to their respectivemeasuring chambers at a time, being then in communication with ten of the eleven passages 339 so as to receive fluid under pressure, while the other ten of said passages 355 and 351 act as discharge passages from their respective measuiing chambers, being then in communication vwith 'ten of the eleven grooves 31| or 315. When the "hollow piston 239 shifts, opposite connections are made so that the reverse action takes place.'

In a given position of the piston 239, each of the dispensing pistons 35| shifts, but only onehalf of the dispensing ports Vare thus served. When the piston 259 is next moved to its alternative positionjby the reciprocating movements automatically induced and maintained by the pressure of the fluid entering the inlet port 253, the -other half of the dispensing ports are then served. This is accomplished by the movement of the piston in carrying its dispensing passages 'sesto inject num inte the ends of each measing chamber from which fluid was discharged by the previous operation. Simultaneously each It follows that arcuate groove 315 and 31| in the piston 269, except the one closest to one of the plugs 215 then abutting the end of the hollow piston, is connectedwith the adjacent measuring chamber 349 fortaking the fluid dispensed therefrom into `the adjacent dispensing port which was disconnected in the previous operation. The fluid to be dispensed enters the feeder through an inlet port 33|, as shown in Figs. 10-12. The dispensing fluid `inlet port 38| is internally threaded or otherwise adapted to receive an end of a branch pipe |1a or the end of the pipe 45 or a branch 41 thereof.

From the inner end of the dispensing uid inlet port 33|, an inlet passage 383 is drilled transverseiy to intersect a passage 335 which is drilled into the side wall of the casing from one end and substantially parallel to the axis thereof. The outer end of the axial passage 335 is closed 'by a suitable plug 331. From the inner end of the axial passage 385, a transverse passage 339 pierces the adjacent side of the cylindrical piston guiding bore 21| for delivering dispensing fluid thereto. y

To receive the dispensing fluid thus delivered into the piston guiding bore 21|, the hollow piston 239 is provided with a groove 39| which is cut in the outer peripheral surface of the piston 269 and which is suitably elongated to provide continuous lconnection with' the inner end of the transverse passage 389 through the entire stroke of the piston 269 as it reciprocates automatically, as previously described, in response to the pressure of the working fluid which is ap'- plied in the inlet port 253 of the casing.

The elongated iiuid dispensing passage 343 which extends -through the length of the hollow piston 239 is continuously supplied with dispensing uid under pressure from the fluid dispensing inlet port 38|, through a passage 393 drilled :from the bottom of the groove 39| in the piston and intersecting a passage 395 which intersects the elongated fluid dispensing passage 343. The elongated uid dispensing passage 333 thus rei oei-ves dispensing uid continuously and independently of the working iiuid which passes through the internal valve guiding bore 21| in the hollow piston 239 for reversely operating said hollow piston.

Wherever it is desired to have indi-cation of' the .operation of any individual dispensing valve, an indicator rod 499 may be provided on the dispensing pistons 35|, passing through the plugs 353 which maybe suitably apertured and packed, as shown in Fig. 19. When it is desired to have the indicator also control the amount of fluid to be discharged, the adjustable stop rod 359., as shown in Fig. 11, may be omitted, and capacity of the dispensing feeder may be regulated by the structure shown in- Figs. 20 and 21, wherein an indicator rod protecting sheath M1 of tubular conformation is provided, projecting outwardly from the cylinder plug through which the ind;- cator rod projects, and the sheath is provided with open side wall portions H9 through which the indicator rod 499 may be observed.

The tubular sheath M1 is provided with threads 92D to receive an adjustable stop plug 42| for engaging the outer end of the indicator rod 469 as it is projected from the dispensing cylinder 343. By adjusting the position of the stop plug 42| in the sheath, the degree of movement of the dispensing piston 35| may be conveniently varied and consequently the quantity of fluid discharged .maybe varied. A second threaded lock plug 423 is turned into the sheath for locking the stop plug 42 I.

Referring now to the volume control valve designated by the numeral 9 in Fig. 1, this is shown in detail in Figs. 15-18, inclusive. This volume control valve includes a base member 45| upon which is mounted a Valve body member 453 secured thereto in any suitable manner. The body member is longitudinally bored from top to bottom, as shown at 455 to receive a cylindrical valve member 451 which is adapted to be manually turned for adjustment therein. The upper portion of the cylindrical valve member 451 is reduced in diameter, as shown at 459, and projects above the upper portion of the member 453 to receive a handle member 46| which is secured thereto in any suitable manner.

The upper portion of the body member 453 is counter-bored, as shown at 463, and provided with suitable packing means 455 to prevent fluid from leaking out between the top of the cylindrical valve member 451 and the top of the valve cylinder. Said packing means surround the reduced portion 459 of the valve member 451 between its enlarged portion and the handle.

The valve body member is provided with an inlet port 461 and opposite the central portion of said port, the valve member 451 is provided with an annular groove 469. The valve body 453 is also provided with an outlet port 41| to the pipe line II .and opposite the central portion of said port, the valve 451 is provided with a groove 413 leading substantially three-fourths around said cylindrical valve 451, the groove varying in depth and in width gradually from one end thereof to the other, and tapering out to a ne line. At a point connecting the largest portion of the groove 413, the valve portion 451 is also provided with a groove 415, connecting to the groove 469, whereby fluid may pass through the inlet port 461 into the groove 469 down through the groove 415, into the groove 413 and thence out through the port 41| to the continuation of the pipe line II.

For entrapping any of the fluid that might leak out of saidvalve, I provide an additional outlet port 43| which connects to a pipe line I3 which leads back to a fluid reservoir 3 as shown in Fig. 1. I also provide a passage 483 in the valve body leading from the base of the reduced portion 459 of valve member 451 down to the base of said valve member and I provide a port 495 which connects said passage 483 to the outlet port 46|.

It will be seen that by turning the handle 46|, the valve portion 451 may be adjusted to control the volume of fluid passing to the valve outlet port 41 I.

Operation My system, when arranged as shown in Fig. 1, operates as follows:

Suppose that it is desired to distribute some oil to certain bearings where oil is preferable to grease for lubricating the same and in other bearings it is desired to dispense grease to the bearings. In order to accomplish this, I fill the reservoir 3 with oil and I fill the reservoir 43 with grease. The electric motor 5 is then connected for operation in the usual manner and it actuates the pump 4 which sucks in oil from the reservoir 3 and discharges it into the pipe II. The pipe II connects to the volume control valve 9, discharging oil thereinto and a continuation of said pipe I receives the oil discharged from said valve as fully illustrated in Figs. 15 to 18.

Turning to Fig. 15, the pipe is connected to the inlet port 461 of the volume control valve so that the oil passes through port 461 into the annular groove 469 on the cylindrical valve member 451, whence it passes down groove 415 which connects with the other semi-circular groove 413 and thence out of the valve through outlet port 41| into the continuation of the pipe line |I as shown in Fig. 1.

As previously described, the groove 413 passes substantially three-fourths the distance around the cylindrical valve member 451, the groove varying in depth and in width gradually from one end thereof to the other and tapering out to a iine line. Hence the handle 46| may be moved to turn the cylindrical member 451 to such position as to substantially lessen the volume of oil flowing from grooves 459 and 415 and through the groove 413 to the discharge Port 41|. Thus one may regulate the volume as desired.

Looking at Figs. 1, '7 and 8, it will be seen that the variation of the volume of oil passing through said valve tends to modify the speed of reciprocation of the hydraulic operator piston |69 in member 21 and consequently tends to vary the speed of reciprocation of the piston 229 in pump 4 I, depending upon the position of the dispensing valves in the feeders connected to the grease line. However, due to the fact that the pressure control valve 55 is set to maintain a constant pressure in the pipe line I1, the same constant pressure will be transmitted and maintained in the hydraulic operator 21. And, as this operator actuates the pump piston in the pump 4I, and, as said pump may only discharge fluid to the line 45 in such amount as the timing element of the hydraulic operators of the feeders permits, it will be seen that the variation of the volume of oil passing through the volume control valve is ineiectual in varying the speed of reciprocation of the hydraulic operator or of the pump piston when they are hooked up with the system as shown in Fig. 1. The main function of the iiow control valve is to vary the Volume of oil passing into the line I1 so as to vary the speed of reciprocation of the hydraulic operators of all of the feeders 35, hence it also modies the time element of the feeder pistons, since they cannot shift until after the shifting of their respective associated hollow valves or hydraulic operating members.

Thus it is seen that the flow control valve 9 may be adjusted to vary the volume of fluid passing into the line I1. This modies or varies the speed of reciprocation of the hydraulic operators of all of the feeder members 35.

In addition to this, the speed of reciprocation of each individual hydraulic operator may further be varied by changing the size of the indicator rod 211 and its associated parts or by the insertion of an additional indicator rod in the opposite plug 215 projecting from the plug 213 of the hollow piston.

It is thus evident that although the hollow piston must reciprocate a given distance in order to connect its respective valve ports and passages at each end of its stroke, a variation of the capacity of the chambers at each end of the bore 21| will necessarily vary the amount of fluid that is required to reciprocate the hollow piston.

Again looking rst at Fig. l5 and then at Fig. 1, it will be seen that such oil as tends to leak from the various circumferential grooves on the cylindrical member 451 either up or clown, in

vother T connection 2|.

Vaeanws the cylindrical chamber 455, is trapped and passes out through the passageways 48.3 and 485, into outlet port 48| which connects to return pipe I3 and returns such oil to the res;- ervoir 3.

'Ihe oil passing from discharge port 41|, of the volume control Valve 9, passes into the extension of the pipe line II, then passes into the T member I5 whence part of the oil passes to the main pipe-line I1 and part to the pipe linel9. The pipe-line or conduit |1 forms a circuit, together with pipe-line I, returning to reservoir 3, said circuit having feeder members interposed therein.

It is not essential that the volume control valve be located in the position shown in Fig. 1, as its real function is to control the flow of liquid through line I1 for controlling the speed of reciprocation of the hydraulic operator of each feeder, which determines the frequency of lubrication. Thus the volume control valve 9 may be inserted in the line |1 above the T member I5, in which case pipe will lead from the pump directly to the T member |5.

Said pipe-line I1 is connected to the inlet port 253, see Fig. 13, of each feeder. Hence it discharges oil under pressure into said feeder casing, through said inlet port, for operating the hollow piston or hydraulic operator and its inner control valve so as to `alternately place the respective feeding chambers in registry with the respective passages receiving the distributing fluid from the inlet `port 38|, see Fig. 10.

rThe oil operating the hollow piston, usually spoken of as the hydraulic operator of the feed- I er, and its control valve, is then discharged out of the exhaust port 259, see Figs. 13 and 14. It then passes to the continuation of pipe-line I1,

and so on through each operator and through the flow impedance member 55 and back to the reservoir 3. If no branch pipes |1a are open to the inlet port 38| of any feeder, no oil' will be discharged by the feeders, the oil then merely being used as an operating fluid to operate the operating members of each feeder, after which vit will be returned to the reservoir 3.

The oil passing through the T member I5 into the pipe line I9, then passes through an- Said T connection has one branch of pipe I9 leading therefromv and connected to the pressure gauge 23 (which will measure the pressure of the oil in said line in the usual manner). The T connection 25 has another branch of pipe I9 leading to the inlet port 25 of the hydraulic operator 21, schematically shown in Fig. 1, and clearly shown in Figs. 5' and 6.

Looking at Fig. 5, it will be seen that the oil entering the operator 21 (from the extension of the pipe I9 through inlet port 25) is constantly in communication with the central portion of the cylindrical valve chamber |05. In the position shown in Fig. 5, some of the oil passes around the hub `|55 of the valve member |53, between valve heads `|55 and |51 and through passage |99 (shown in dotted lines m Fig. 5), into the left end of valve bore |01, causing fluid responsive valve |29 with its equally spaced valve heads |3i, |33, |35, |31, to move to the right, as shown in said Fig. 5, and holding the same there until valve |53 shifts to the left.

During the movement of valve |29 to the right, the cam surface on the right of hub IIiI causes the cammed or rounded base portion of theintei-locking pin |83 to rise upwardly in its bore .|95 so Athat the'upper portion oi Vsaid Vpin. will 'be engagedin the groove |81 of valve |53, between the hub |59 and the valve lhead |55, thus preventing simultaneous movement of the two valves. After the movement is completed, gravitywill usually cause the pin |83 to return to the position shown in Fig. 5. But this is unimportant as the pin will always be in a position to prevent the valves from moving simul- The oil entering said inlet port 25 of the operator 21 and'coming into the central portion of the aperture |05, between Valve heads and |51, i's constantlyV adapted to flow into the passage I 96, as shown in Fig. 3, and from thence 'dotted lines in Fig. 5 and shown in full lines in Figs.`7 and 8.

'Ihe parts are then in the position shown in Fig. 7. Oil passing from said bore |01 into the passage 295 is then discharged into cylindrical bore |03, moving piston |09 to the left as shown in Fig. 8. This action causes the oil previously charged into the passage |03, to the left of piston |99, 'to be discharged into the passage 203 at which time the valve |29 is still in the position shown in Fig. 7, whereupon said oil passes into valve chamber |01 between valve heads |3I and |33. This portion of the valve bore |01. is then in communication with the passage 201, as shown in Fi'g. 5, from whence said oil is discharged from the passage 201 into the exhaust passage 299 and thence out of the operator exhaust port 29 to the continuation of the pipe I9, which returns the oil to the reservoir 3 as shown in Fig. 1.

As the operation of the hydraulic operator has previously been fully described, it is not thought that the description oi the reverse operation is necessary. Suffice it to say, that part of the oil is continuously adapted to be pumped into, and, when the device is in operation, will be pumped into the hydraulic operator 21, under pressure, entering the same through the inlet port 25, and will continuously maintain a pressure tending to `reciprocate the hydraulic operator piston |09, yfrom whence the oil used for operating said operatormember will be returned to the reservoir 3. l While part of the oil is thus reciprocating the operator piston |99, .for the purpose of driving `the pump piston in pump III, the portion of the oil'thatis being pumped into the circuit pipe-line I1 will Apass into the first feeder 35 connected thereto, and will operate its hydraulic operator and pass on to the continuation of the pipe-line |.1 and then enter the second feeder 35, operating its operator and so on through all the feeders.

A branch pipe I 1a is shown connecting pipeline I1 to the third feeders fluid-dispensing inlet port. Hence, if the dispensing pipe lines 261 of the'third feeder are connected to bearings which one desires to lubricate with oil, one opens the valve 09, permitting oil to enter the fluid-dispensing inlet port of the said third feeder 35.

Thus a portion of the oil will pass through the branch pipe |1a. into the feeder-dispensing inlet port of the third feeder and be dispensed from the measuring chambers in the manner previously described in the specification.

This will be in addition to the portion of the oil which passes through the hydraulic operator portion thereof. The same operation takes place with the sixth feeder 35.

However, if the bearings connected to the dispensing pipe-lines 261 are located on idle machines which do not require oil at the time, one may close the valve 49, in which case no oil or other iuid will be dispensed, and the oil in line |1 will simply pass through the hydraulic operator of the feeder.

As the oil returns in the line |1, that is, as it is about to complete its circuit, which is continuous in direction, it will pass through the flow impedance member 55 in a manner heretofore described and return to the reservoir 3 through the continuation of the pipe |1.

'Ihe operation of the individual feeders has heretofore been described, hence it is thought that it is sufficient to say that the oil passing through the pipe-line |1 enters each feeder through the inlet port 253, as shown in Fig. 13, and actuates the hydraulic operator and is exhausted to the continuation of the pipe line from the exhaust port 259.

Only fiuid that enters the feeder through the duid-dispensing port, namely the port 38|, as shown in Fig. 10, is adapted to be dispensed from the dispensing ports. Hence if the oil line |1 has a branch |`|a connecting it to a fluid dispensing inlet port 39| of any feeder and the valve 49 controlling said port is open, then that feeder will discharge oil out of its respective dispensing outlet ports. If the valve 49 is closed, no fiuid will enter the feeder-dispensing inlet port 38| and no fluid will be discharged from the dispensing ports of the feeder during the reciprocatory motion of the hydraulic operator.

As shown, in Fig. l, the first, second, fourth, fifth, seventh and'eighth feeders are also shown connected to the second pipe-line 45 through T connections 41. Valves 49 are provided and they control the entry of grease to the respective fluid-dispensing inlet-ports of the feeders, said grease being pumped from pump 4| into the pipe-line 45.

Turning new to Fig. 7, it will be seen that as the piston |99 moves to the left, it moves the pump piston 229 to the left.

As previously described, the grease reservoir 43 is continually in communication with the pump bore 223 through a passage 24|, as shown in Fig. 4. This passage 24| is located directly above the central portion of the bore 223 when looking at the views shown in Figs. '7 and 8. Hence as the piston 229, Fig. '7, moves to the left, it discharges grease previously charged in the left of the bore 223 out through the passage 235 and into the passage or valve guiding bore 225, moving the valve 23| from the left, as shown in Fig. 7, to the right, as shown in Fig. 8, and thence into the pipe line 45.

As the piston 229 passes to the left, it first closes the port 24|, creating a partial vacuum at the right side of the pump bore 223, so that, as the piston passes to the left, see Fig. 8, gravity as well as atmospheric pressure causes grease to fiow from the reservoir 43 into the pump cylinder 223 to fill the same.

When the pump piston 229 is moved in the opposite direction by the hydraulic operator pisvton |99, grease is discharged from the right hand side of the chamber 223, through the passage 231 and `into passage or valve guiding bore 225, (causing the valve 23| to move from the right, as shown in Fig. 8, to the left, as shown in Fig. '1) thus discharging additional grease into the pipeline 45.

The speed of reciprocation of the hydraulically operated piston |99 and of the pump piston 229 is primarily governed and controlled by the volume of grease (or other liquid) that is dispensed from the dispensing valves of the feeders connected to the pipe-line 45. This results from the fact that there is a constant pressure on the hydraulic operator piston which is transferred to the pump piston 229 by the piston rod and, unless liquid is consumed by the bearings or receptacles connected to the dispensing outlet ports of the dispensing valves operatively connected to line 45, the pump piston cannot move.

The grease being discharged into the line 45 from the pump 4| may enter each of the feeders connected therewith through their respective fluid dispensing inlet ports 33|, so called since they control the entry of the fluid to be dispensed therefrom. Hence, as shown in Fig. 1, the first, second, fourth, fifth, seventh and eighth feeders are adapted to receive grease if one desires to dispense grease therefrom.

For instance, if each of the dispensing pipe lines 251 of the first feeder is connected to ten bearings of a machine, which bearings are to be lubricated with grease, one opens the valve 49 of the connection to the first feeder. Then grease being pumped in the line 45 under pressure will enter the first feeder, passing through said valve 49 and through the fluid-dispensing inlet port 39|, as shown in Fig. 1.9, and will then pass through passages 383, 335, 389, 39|, 393 and 395, as shown in Figs. 11 and l2, into the elongated passage 343, from whence the grease is adapted to be discharged into the respective passages 399, thence into passages 365, thence to the measuring chambers 349, discharging the previously charged and measured portion from the measuring chambers through the passages 351, thence through the groove 31|, and thence through the passages 313 or 311, as the case may be, to the respective outlet ports 265 and 266 connecting to the dispensing pipes 261 and thence to the bearings.

Similarly each of the other feeders connected to the pipe 45 is adapted to dispense grease from its respective outlet ports. If certain of said ports are connected to bearings on a separate machine which is not then in operation, fluid flow to said respective bearings may be stopped by turning the cock-valve 263, as shown in Fig. l1, which is connected to the extension of each of the pipe lines 261.

It is thus seen that feeders three and six are connected in such manner as to discharge oil, if oil is owing in the line l1, because a branch pipe Ha is connected to the inlet port 38| of each of said feeders.

If grease is iiowing in line 45, the other six feeders are connected in such manner as to discharge grease, depending on the position of the valve 49.

If, however, the workman desire to dispense oil from the first feeder in the line, he merely has to disconnect the branch pipe with first valve 49, and close said valve, and put another T connection on the line I1 and connect a branch pipe I la, as shown connectedV to the third feeder, provide the said branch pipe lla with another valve 49, and connect the end of the pipe Ila. with the fluid-dispensing inletl port 38| Vof the first feeder. Y

Aside from the specific embodiment of the invention herein shown and described, it will be understood that numerous details of the construction may be altered or omitted. without departing from the spirit and scope. of theinvention as disclosed and claimed, and that I. do not desire to limit the invention to the exact Yconstruction herein set forth.

I claim:

1. In combination in a dual-line uniflow fluid dispensing system, a uid pump, a plurality of fluid dispensing feeders, each of said feeders comprising a series inlet, a series outlet, a .plu-

rality of dispensing outlets,A a second inlet, fluid responsive means responsive to fluid pressure for dispensing from said dispensing 4outlets fluid received through said second inlet, and a hydraulically operated member for controlling the supply of fluid from said second inlet, to said dispensing means; conduit means for continuously delivering fluid from said pump in one direction through the series inlets and the series outlets of said feeders for actuating said hydraulically operated members, and a second fluid delivery line for delivering a dierent fluid into selected ones of the second inlets of said feeders.

2. In combination in a uniflow fluid dispensing system, a slipping type of fluid pump, a plurality of fluid dispensing feeders, each of said feeders comprising a series inlet, a series outlet, a plurality of dispensing outlets, a second inlet, fluid responsive means for dispensing from said dispensing outlets, and a hydraulically operated member for controlling said dispensing means, clonduit means for delivering fluid from said pump through the series inlets and the series outlets of said feeders for actuating said hydraulically operated members, branch pipes connecting said conduit `to said second inlets of said feeders, and an adjustable volume controller interposed in said conduit means between said fluid pump and the feeders for regulating the fluid flow therein. Y

3. In combination in a uniilow fluid dispensing system, a fluid pump, a plurality of fluid dispensing feeders, each of said feeders comprisg ing a series inlet, a series outlet, a plurality of dispensing outlets, a second inlet, fluid responsive means for dispensing from said dispensing outlets fluid received in said second inlet, and a hydraulically operated member for controlling the supply of fluid from said second inlet to said fluid responsive dispensing means, conduit means for delivering fluid from said pump through the series inlet and series outlets of said feeders for operating said hydraulically operated members, a second fluid delivery line for delivering a different fluid into the second inlets of selected ones of said feeders in parallel relation, a second fluid pump for supplying fluid to said second fluid delivery line, a fluid pressure motor operatively connected for actuating said second fluid` pump, conduit means for applying fluid pressure from said first mentioned fluid pump to the fluid pressure motorfor driving said second fluid pump, and pressure controlling means aseach comprising, a series inlet, a series outlet, a plurality of dispensing outlets, a parallel connection inlet, fluid responsive means for dispensing from said dispensing outlets fluid received in said second inlet, and a hydraulically operated member for controlling the supply of fluid from said second inlet to said fluid responsive dispensing means, a source of pressure fluid, conduit means connected for delivering fluid from said source through the series inlets and outlets of said' feedersV in series connected relation forY operating said hydraulically operated members, a second source of different fluid, and a continuous delivery line lleading from said second source for delivering fluid to the parallel connection inlets of said feeders in parallel relation.

5. In combinationin a uniflow fluid dispensing system,v a slipping fluid pump, an electric niotor connected for driving said pump, a plurality of feeders, each of said feeders comprising fluid responsive means for dispensing fluid therefrom, conduit means for delivering fluid from said pump through said feeders inseries connected relation for actuating said fluid responsive means, and an `adjustable volume controller comprising flow restricting means in said conduit means between said pump and said feeders.

'6. In combination. in a uniflow fluid dispensing system, a slipping fluid pump, an electric motor connected for driving said pump, a plurality of feeders, each` of said feeders comprising fluid responsive means for dispensing fluid therefrom, conduit means for delivering fluid from said pump through said feeders in series connected relation for actuating saidv fluid responsive means, an adjustable volume controller in said conduit means Abetween said pump and said feeders, and an automatic pressure controller connected in said conduit means remotely from said pump beyond said feeders.

7. In combination in a uniflow fluid dispensing system, a gear pump, an electric motor connected for driving said gear pump, a plurality of feeders, each of said feeders comprising a series inlet, a series outlet, a plurality of dispensing outlets, a parallel connection inlet, iluid responsive means for dispensing fluid from said dispensing outlets and a hydraulically operated member for controlling the supply of fluid from said parallel connection inlet to said dispensing outlets, conduit means connected for delivering fluid from said pump through said feeders in series connected relation for operating said hydraulically operated members, an adjustable volume controller connected in said conduit means between said pump and said feeders, an automatic pressure-controller connected in said conduit means remotely from said pump beyond said. feeders, a second fluid delivery line connected for delivering a different fluid into the parallel connec- Ation inlets of said feeders to be dispensed theresociated with said conduit means remotely from system, a plurality of fluid dispensing feeders from, a second fluid pump connected for supplying fluid into said second line, a fluid pressure motor operatively connected for driving said sec- Tond fluid pump, and conduit means connected for lapplying fluid pressure from said gear pump te operate said fluid pressure motor.

8. In combination in a dual-line uniflow fluid dispensing system, a flrst uid pump, a plurality of feeders, each of said feeders comprising fluid responsive means for dispensing nuid therefrom, a second pump for supplying a different fluid, a fluid pressure motor responsive to fluid pressure from said first pump for driving said second pump,` and conduit means for supplying dispensing fluid to some of the feeders from one of the pumps and to the other feeders of the system from the other pump.

9. In combination in a dual-line uniflow fluid dispensing system, a ilrst fluid pump, a plurality of feeders, each of said feeders comprising fluid responsive means for dispensing fluid therefrom, a second pump for supplying a different fluid, a fluid pressure motor responsive to fluid pressure from said first pump for driving said second pump, a conduit means for supplying working fluid from said first pump through all of said feeders in series connected relation, conduits connected for supplying some of theV Working fluid to some of the feeders of the system to be dispensed, a fluid dispensingv supply line extending from said second pump, parallel connections extending from said dispensing supply line to respective ones of said feeders in parallel relation, and a manual valve in the dispensing fluid connection to each feeder.

10. In combination in a dual-line uniflow fluid dispensing system, a flrst fluid pump, a plurality of fluid dispensing feeders, each of said feeders comprising fluid pressure responsive means for dispensing fluid therefrom, a second pump for supplying a different fluid, a fluid pressure actuated motor responsive to fluid pressure from said first pump for driving sald second pump, conduit means connected for supplying fluid to said feeders from said pumps, means for separately adjusting the operation of said fluid pressure actuated motor to satisfy the demand for fluid from the second pump, and conduit means for supplying some of said feeders with fluid to be dispensed from the first pump and others of said feeders with fluid to be dispensed from the second pump.

11. In combination in a dual-line uniflow fluid dispensing system, a uniflow Working fluid pump having slippage fluid pumping means, a plurality of fluid dispensing feeders, each feeder comprising a working fluid inlet and a Working fluid outlet, conduit means for passing working fluid from said pump through said feeders in series connected relation, a dispensing fluid inlet in each of said feeders, a dispensing fluid line, a dispensing pump for supplying dispensing fluid under pressure in said line, parallel connections extending from said line into the dispensing fluid inlets of respective ones of said feeders, and branch feeders extending from said series connected conduit means for injecting the Working fluid into the remainder of said dispensing inlets.

12. In combination in a dual-line uniflow fluid dispensing system, a uniflovv Working fluid pump having slippage fluid pumping means, a plurality of fluid dispensing feeders, each feeder comprising a Working fluid inlet and a Working fluid outlet, conduit means for passing working fluid from said pump through said feeders in series connected relation, a dispensing fluid inlet in each of said feeders, a dispensing fluid line, a dispensing pump for supplying dispensing fluid under pressure in said line, parallel connections extending from said line into the dispensing fluid inlets of respective ones of said feeders, branch feeders extending from said series connected conduit means for injecting the working fluid CII for' operating said feeders and said fluid pressure motor.

13. In combination in a dual-line unilow fluid dispensing system, a uniflow Working fluid pump having slippage fluid pumping means,.a plurality of fluid dispensing feeders, each feeder comprising a working fluid inlet and a working fluid outlet, conduit means for passing Working fluid from said pump through said feeders in series connected relation, a dispensing fluid inlet in each of said feeders, a dispensing fluid line, adispensing pump for supplying dispensing` fluid under pressure in said line, parallel connections extending from said line into the dispensing fluid inlets of respective ones of said feeders, branch feeders extending from said series connected conduit means for injecting the Working fluid into the remainder of said dispensing inlets, a fluid pressure motor responsive to fluid pressure from the Working fluid pump and connected with said dispensing pump for operating the same, automatic pressure controlling means for maintaining a suitable pressure in said conduit means for' operating said feeders and said motor, and a volume controller for controlling the flow of fluid in said conduit means to regulate the operating speed of the feeders and the motor.

14. A fluid distributing system comprising a fluid pump, a plurality of fluid dispensing feeders, each of said fluid dispensing feeders having fluid responsive means for dispensing fluid therefrom, having hydraulically operated means for controlling said dispensing means and each of said feeders having two inlet ports, one for receiving working fluid and one for receiving dispensing fluid, a discharge port for discharging said Working fluid and a plurality of outlet ports for dispensing the dispensing fluid, conduit means connected to the Working fluid inlet port of each feeder for delivering Working fluid from said pump through said feeders in one direction for operating said hydraulically operated control means, a second fluid delivery line for delivering a dispensing fluid into the second inlet port of each of said feeders, and a second fluid pump connected for supplying fluid to said second fluid delivery line.

15. A fluid distributing system comprising a fluid pump, a plurality of fluid dispensing feeders, each of said fluid dispensing feeders having fluid responsive means for dispensing fluid therefrom, having hydraulically operated means for controlling said dispensing means and each of said feeders having two inlet ports, one for receiving working fluid and one for receiving dispensing fluid, a discharge port for discharging said working fluid and a plurality of outlet ports for dispensing the dispensing fluid, conduit means connected to the Working fluid inlet port of each feeder for delivering `Working fluid from said pump through said feeders in one direction for operating the said hydraulically operated control means, pressure controlling means connected with said conduit means in remotely disposed relation from said fluid pump for maintaining a suitable pressure, a second fluid delivery line connected for delivering a dispensing fluid into the second inlet port of each of said feeders, and a second fluid pump connected for supplying fluid to the second delivery line.

16. A fluid distributing system comprising a fluid pump, a pipe-line connected thereto, a fluid dispensing feeder having two inlet ports, the first of which is connected to said pipe-line, said feeder also having fluid responsive means for dispensing fluid therefrom, said iluld responsive means dispensing uid entering the feeder through the second inlet port, said feeder also having hydraulically operated means for controlling the supply of fluid from the second inleltl port to the fluid responsive dispensing means, said pump being adapted to deliver fluid in one direction under pressure to the said hydraulically operated controlling means of the feeder and for operating the same continuously, a second fluid delivery pipe-line for delivering a different fluid to the second inlet port of the feeder, and a second fluid pump for supplying fluid in one direction to the second delivery line.

17. In combination in a uniflow fluid dispensing system, a fluid pump, a fluid dispensing feeder comprising, a working fluid inlet, a working fluid outlet, a dispensing fluid inlet, a plurality of dispensing fluid outlets, fluid responsive means for dispensing from said dispensing fluid outlets fluid under pressure received in the dispensing fluid inlet and a hydraulically operated member for controlling the supply of fluid from the dispensing fluid inlet to said fluid responsive dispensing means, a conduit connecting said pump to said feeder whereby the Working fluid Will enter the feeder through said Working fluid inlet and actuate the hydraulically operated member and pass out of the feeder through said working fluid outlet, and means for supplying fluid under pressure to said dispensing fluid inlet.

DAVID R. HILLIS.

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