US3064759A

US3064759A - Two-fluid signaling lubricating system

Info

Publication number: US3064759A
Application number: US69655A
Authority: US
Inventors: George H Acker
Original assignee: Eaton Manufacturing Co
Current assignee: Cleveland Gear Co
Priority date: 1960-11-16
Filing date: 1960-11-16
Publication date: 1962-11-20
Anticipated expiration: 1979-11-20
Also published as: GB938034A

Description

Nov. 20, 1962 e. H. AC KER TWO-FLUID SIGNALING LUBRICATING SYSTEM 5 Sheets-Sheet l Filed Nov. 16. 1960 'GEORGE H. ACKER ATTORNEYS Nov. 20, 1962 e. H. ACKER 3,064,759

TWO-FLUID SIGNALING LUBRICATING SYSTEM Filed NOV. 16. 1960 5 Sheets-Sheet 2 ii A FIG 6 FIG l9 NVENTOR GEORGE H. ACKER TTORNEYS Nov. 20, 1962 G. H. ACKER TWO-FLUID SIGNALING LUBRICATING SYSTEM 5 Sheets-Sheet 3 Filed NOV. 16, 1960 Q i m INVENTOR.

GEORGE H. ACKER ATTORNEYS v Nov. 20,1962 G. H. ACKER 3,064,759

TWO-FLUID SIGNALING LUBRICATING SYSTEM Filed Nov. 16, 1960 5 Sheets$het 4 TO BEARNG A TO BEARING B FIG l6 TO BEARINGA T0 BEARING B FIG I? INVENTOR.

' GEORGE H. ACKER 1 "I y w"?! ATTORNEYS Nov. 20, 1962 G. H. ACKER TWO-FLUID SIGNALING LUBRICATING SYSTEM 5 Sheets-Sheet 5 Filed Nov. 16, 1960 32 o If FIG 20 INVENTOR.

GEORGE H. ACKER ATTORNEYS United States Patent Ofiice 3,064,759 Patented Nov. 20, 1962 7 TWO-FLUID SIGN LIIIG LUBRICATING SYSTEM This invention relates generally, as indicated, to a twofluid signaling lubricating system and more particularly to a lubricating valve and system providing high lubricating pressures for lubricants automatically to lubricate extensive mill equipment.

In past practice, lubricants such as grease have been purchased in 400 1b. drums, and the lubricant reservoirs of the individual lubricating systems in a particular mill or plant filled from such drums. Some companies have found it possible to reduce their lubricating costs by buying the lubricant in bulk lots of 10,000 to 20,000 lbs., delivered directly from the lubricant manufactory in tanks holding such amounts, and transferred by suitable pumps from such truck-transported tanks to similar tanks located within the mill. There is economy in the bulk purchase of the lubricant itself; the cost of moving the 400 lb. drums around the mill is eliminated, loss through residual grease left in the 400 lb. drums is eliminated, and hazard of lubricant contamination is minimized. From such a bulk central storage tank, the lubricant is pumped through a header passing near all of the lubricating system control units serving the particular mill and valved branch lines from this header permit renewing the lubricant supply in the individual lubricant system reservoirs without exposure to external contamination.

In accordance with the present invention this lubricant distribution header is placed under a constant high pressure and the multiplicity of lubricating systems in such mill are operated from this high pressure header directly. This eliminates the requirement for grease storage reservoirs and pumps normally employed to operate each of the individual lubricating systems.

It is then a principal object of the present invention to provide a lubricating system facilitating bulk purchase of the lubricant at a price advantage and considerably reducing the in-plant handling costs of such lubricant.

For a variety of reasons, line breakage in a line leading to any particular bearing to be lubricated or blockage of such line may occasionally occur. Accordingly, a system providing a signal indicating the occurrence of and location of such breakage or blockage as closely as possible is to be highly desired. Furthermore, a system which will by-pass any such breakage or blockage so that all of the other bearings served by the lubricating system will be lubricated in the normal manner is also obviously desirable.

In such lubricating system, metering of requisite amounts of lubricant to the bearings is customarily accomplished by displacement resulting from movement of pistons in cylinders under differential pressures. High pressures are usually necessary to accomplish this, and high differential pressures present a hazard of by-passing lubricant around the displacement pistons, destroying the accuracy of metering. It is therefore advisable to provide relatively equal at-rest residual pressures in such a system.

It is accordingly a further important object of the present invention to provide such a lubricating system capable of metering lubricant to the bearings under high pressures and yet closely balanced at-rest residual pressures.

7 It is yet another important object to provide a lubricating system having a localized signal of line breakage or blockage.

A further important object is the provision of a lubricating system wherein the lubricant will by-pass all but the valve having the blocked or broken line.

Another object is to provide a two-fluid lubricating system which will have low residual substantially identical at-rest pressures for each fluid, substantially eliminating valve leakage past piston lands.

It is yet another object to provide a lubricating system which may be very extensive and yet which can be programmed to operate automatically.

Other objects and advantages of the present invention will become apparent as the following description proceeds.

To the accomplishment of the foregoing and related ends, the invention, then, comprises the features hereinafter fully described and particularly pointed out in the claims, the following description and the annexed drawings setting forth in detail certain illustrative embodiments of the invention, these being indicative, however, of but a few of the various Ways in which the principles of the invention may be employed.

In said annexed drawings:

FIG. 1 is a diagrammatic fragmentary layout of a lubricating system in accordance with the present invention;

FIG. 2 is a top plan view of a manifold lubricating valve which may preferably be employed with the present invention;

FIG. 3 is a front elevation of such manifold valve as viewed from the bottom of FIG. 2;

FIG. 4 is an end elevation of such manifold valve as seen from the left of FIG. 2;

FIG. 5 is a vertical section of the inlet end block of such valve taken substantially on the line 5-5 of FIG. 2;

FIG. 6 is a vertical section of such inlet end block taken on the line 66 of FIG. 5;

FIG. 7 is a vertical section of the outlet end block of such valve taken substantially on the line 77 of FIG. 2;

FIG. 8 is a vertical section of such outlet end block taken substantially on the line 8-8 of FIG. 7;

FIG. 9 is a vertical section taken on the line 9-9 of FIG. 2 of one of the valves in such manifold;

FIG. 10 is a horizontal section of such valve taken on the line 1010 of FIG. 9;

FIG. 11 is a horizontal section of such valve taken on the line 1111 of FIG. 9;

FIG. 12 is a vertical fragmentary section of such valve taken on the line 1212 of FIG. 10;

FIG. 13 is a vertical section of such valve taken on the line 1313 of FIG. 10;

FIG. 14 is a vertical section of such valve taken on the line 1414 of FIG. 9;

FIG. 15 is a vertical section of such valve taken on the line 15-15 of FIG. 9;

FIG. 16 is an enlarged section identical to that of FIG. 9 illustrating more clearly the details of such valve;

FIG. 17 is a sectional view similar to FIG. 16 illustrating such valve in its alternate position;

FIG. 18 is a fragmentary section taken substantially on the line 13-18 of FIG. 2 illustrating the details of the low pressure cut-off valve mounted on the bearing outlets of each of the valves in such manifold;

FIG. 19 is a fragmentary diagrammatic view of an alternative form of lubricating system in accordance with the present invention; and

FIG. 20 is a wiring diagram of the rudiments of an electrical system that may be employed to operate a lubricating system in accordance with the present invention.

The System-FIGURE I Referring now to the annexed drawing and more par ticularly to FIG. 1, the lubricating systeiri illustratedfis designed for time-clock programmed operation, and for employment where lubricant is continuously supplied un= der high pressure, e.g., 2,000 psi, from some central source or alternatively as hereinafter described from conveniently positioned pumps and reservoirs such as those commonly employed in present lubrication practice.

In FIG. 1, a lubricant supply line 1 is teed oil as shown at 2 from the pressure header 3. The pressure header 3 containing the required grease or oil may extend throughout the mill from the aforementioned central supply and a pump as shown or several pumps may be employed to raise and maintain a pressure therein of, for example, 2,000 psi. Such lubricant supply line 1 is provided with a shut-off valve 4 and continues through to the first valve manifold 5 and then as shown at 6 to a further valve manifold 7 and to other and further valve manifolds as indie'ated at 8. Whereas only three have been illustrated in FIG; 1, it will readily be understood that as many valve manifolds may be employed in such system as required to lubricate the particular mill or equipment. Such lubricant supply line is plugged as shown at 9 at the end of the last valve manifold 8 in such system. The shut-off valve 4 may be controlled by a solenoid of conventional type or preferably, as illustrated, by an air motor 10, such motor being supplied with air pressure through line l l, such'air pressure being controlled by solenoid operated air valve 12. Air for operation of the motor 10 may be provided by header 13 or from any convenient source of air under pressure. In operation of the system, the air motor operated shut-off valve 4 will normally be closed.

Also provided is a fluid reservoir 15 for a fluid such as ordinary hydraulic fluid. An air operated pump 16 as, for example, a conventional bell type pump may be provided to pump the fluid from the reservoir 15 at high pressure to a fluid supply line 17 through which all of the

valve manifolds

5, 7, 8 etc. are connected in series as in the case of the lubricant supply line .1. A normally closed solenoid valve 18 is provided in air supply line 13 controlling the operation of pump 16. Whereas an air operated pump is illustrated, it will readily be appreciated that an electric motor driven pump may equally well be employed and, if such is the case, a conventional motor starter would then be employed in place of valve 18.

Ahead of the first valve manifold 5 an accumulator 20 is provided interconnecting the lubricant supply line 1 and the fluid supply line 17. This accumulator consists of a closed end cylinder in which a closely fitting axially free-sliding piston 21 is inserted. One end of the accumulator cylinder is teed into the lubricant supply line 1 and the other end of the accumulator is teed into the fluid supply line 17.

A fluid return line 23 is provided between the fluid supply line 17 and the fluid reservoir 15. A shut-off valve 24, normally open, may be controlled by air motor 25. The air motor 25 is connected to air line 26 which is controlled from the solenoid operated air valve 18 controlling the fluid pump 16. However, a solenoid operated valve may'optionally be provided energized by the same electric circuit as that shown. Between the shut-off valve 24 in the return line 23 and the fluid reservoir 15 a pressurelimiting check valve 27 opening, for example, at 700 psi. is provided,.having the effect of limiting the relief of the pressure in the fluid supply line to that pressure level.

When a time clock 30 or other .programming'means makes an energizing electrical contact within controlcenter 31, the lubricant shut-off valve 4 is opened through solenoid valve 12 and also the fluid pump motor 16 is started, while the fluid relief shut-off valve 24 is closed. The accumulator 20 will be partially filled with lubricant atths point and it may receive additional lubricant from the inflow resulting when the shut-off valve 4 is opened.

4 The fluid pump 16 will build fluid pressure higher than the 2,000 psi. lubricant pressure, and will force the lubricant from the accumulator 20 back into the supply line 1. When the lubricant has been displaced and the accumulator piston 21 cannot move further, the fluid pressure will rise as required until it reaches a magnitude of approximately 3,000 psi. at the valve manifolds. Ahigh pressure switch 32 installed in the fluid outlet of the last manifold 8 at the distal end of the system will make an electric contact to energize a reset relay 33 when such 3,000 psi. pressure is obtained at that point. This will normally indicate completion of the lubricating cycle causing the shutoff valve 4 to close, the fluid pump 16 to stop, and the relief cut-off valve 24 to open.

At this point, the pressure differential between the fluid supply line '17 and the lubricant supply line 1 will have forced the pilot pistons of the valves as hereinafteride scribed toward the lubricant end of their cylinders and the metering pistons of these valves will have been forced toward the fluid end displacing lubricant to half of the bearings served by the system. With the fluid pump 16 stopped, the pressure throughout the fluid supply 17 will rather quickly. reduce to approximately 7-00 psi. The pilot pistons of the valves will also serve as very small accumulators, and as the fluid pressure in the system fails,

the entrapped air in the lubricant supply system beyond the cut-off valve 4 will tend to sustain the lubricant pressure temporarily, and as the fluid pressure falls the pilot pistons will be forced into their normal positions, causing displacement of lubricant to the other half of the interconnected bearings. Fluid willalso be displaced from the accumulator 20 as the fluid pressure drops, until fluid and lubricant pressures are equalized at that point. Completion of valve operation during this relieving cycle is insured by the relative size or flow resistance of the conduit between the accumulator and the lubricant supply line 1 to govern the rate of relief of lubricant pressure, or alternatively, closing of the cut-off valved may be delayed beyond stoppage of the pump 16 and opening. of valve 24.

While the system illustrated employs only a single accumulator, it will bejunderstood that a plurality of ac cumulators can be so located in an extensive lubricating system to offset the effect of high lubricant flow resistance hindering equalization of fluid and lubricant pressures in the system at rest. Discharge line check valves at the hearing points serve to maintain a 700 p.s.i. pressure in such discharge lines and thus equalize fluid and lubricant pressure, which is to be desired to minimize by-pass of fluid or-lubricant around the lands of the valve pistons.

When the fluid pressure at the remote or distal end of the fluid supply line 17 falls to a value slightly greater contact that will clear the electrical controls so that a new cycle of operation can be initiated in the system.

Without such contact being made, a new cycle cannot be started and the programming timer will then preferably make a warning indication.

A high-low pressure switch 35 is provided in the fluid supply line 17 ahead of the first valve manifold 5. This switch is set to make a contact at, for example, 3,500 psi. so that if a valve malfunctions and causes any of the high pressure by-pass valves in the manifold to open as hereinafter described, such switch will produce a high pressure contact energizing an alarm signal. This alarm signal may take the form of a signal light36 in a bank 37 of suc'n signal lights.

Similar switches

38 and 39 in the fluid supply line 17 may be provided for the respective manifolds 7 and 8, such switches energizing signal lamps 42' and 41 respectively upon the attainment of the.

such devices are provided between all manifolds, the'mal- 1 functioning one may be identified as that beyond which no high pressure indication is given.

It will be obvious that conventional limit switches can be installed in place of such high-low pressure switches to be operated by physical displacement of the manifold bypass valve members as hereinafter described to serve this same end. The making of the low pressure contact on the pressure switch located ahead of the first manifold may be set at a pressure below the 700 p.s.i. relief pressure as, for example, 650 p.s.i., and utilized directly to energize an alarm signalling a leak in either the fluid or lubricant supply lines since these pressures are equalized in the static condition through the accumulator.

Similar low pressure contacts on the high-low pressure switches 35, 38 and 39 in the fluid supply line may be employed to indicate remotely the malfunctioning manifold, since those manifolds on the pump side of the malfunctioning line will relieve quickly in those instances where the fluid relief is accomplished entirely through the fluid supply line, and relief beyond .the malfunctioning manifold will be delayed by the necessity of relieving through the restricted by-pass in the entering end block of the defective manifold. When the lubricating system is extensive, and operating cycles are relatively frequent, it is possible to increase the rate of relief by running a relief line 43 from the leaving end block of the last manifold back to the reservoir 15 through, for example, a 3,000 p.s.i. check valve 44. A by-pass in such optional line 43 must be provided between this 3,000 psi. pressure control valve 44 and the 700 p.s.i. valve 27. This by-pass line 45 may then be provided with a shut-off valve 46 actuated by an air motor 47 connected to air line 26 and operated in unison with the regular relief shut-off valve 24.

Particularly where such dual-end relief is provided, the low pressure contacts of high-low pressure switches 35, 38 and 39 in the fluid supply line between manifolds must all be required to make low pressure contact before the system may be recycled.

Instead of employing separate contacts on the high-low pressure switches 35, 38 and 39, a further low pressure switch 48 may be employed in fluid line 17 energizing warning light 49 when the pressure falls to 650 p.s.i. to indicate a broken main line. This switch may preferably be placed in front of the first manifold 5 as shown.

It will, of course, be realized that the indicated fluid pressures are exemplary only and that other fluid pressures could be employed. The only thing important is the difference in fluid pressures obtained between the fluid and lubricant supply lines.

The Valve Manifold An illustrative valve manifold is shown in FIGS. 2, 3 and 4 and the details of an individual valve are shown in FIGS. 5 through 18 inclusive. The valve manifold includes: an inlet end block 50 having a mounting plate 51 thereon; valves 5'2, 53, 54 and 55, all of which are identical in form; and outlet end block 56 also having a mounting plate 57 thereon. It is noted that all of the

blocks

50, 52, 53, 54, 55 and 56 are of the same rectangular shape and four aligned holes are provided in each for four

tie bolts

58, 59, 60 and 61 which pass through the end blocks and all intermediate valves to hold them in a compact assembly. Such tie bolts will be secured by nuts and washers as shown at the outlet end block 56 and gaskets 62 will be employed separating all of the segments of such an assembled manifold. The four tie bolts, of course, will pierce the gaskets 62, and three additional holes will be required to form continuations of the high pressure by-pass passages, the lubricant passage 1, and the fluid passage 17 through the manifold valves from one end block to the other. It is noted that since only those circular openings permitting passage from the ports of one valve block directly to those of the adjacent block are required in the gaskets, very little of the adjoining valve block surfaces are exposed to high hydraulic pressures,

and accordingly strains of no great severity will be imposed on the tie bolts when the manifold assembly is subjected to working pressures.

Each of the valves 52 through 55 inclusive is provided with two lubricant outlets as shown on :valve 52 at 64 and 65. Each such outlet is provided with a low pressure spring loaded cutoff 6-6 and 67 as are the outlets of the other valves in such manifold, such low pressure cutoffs being hereinafter described in more detail.

The passages and ports of the valves are drilled from a substantially rectangular steel block and where desired passages must be started from the outer surfaces of the valve block, but must be closed at such surface, it is the practice to accomplish this by laying a somewhat oversized soft steel ball in the external opening and spot welding it in place. The result is indicated by an internal hemisphere projecting into the passage.

The inlet end block is shown in more detail in FIGS. 5 and 6 and the outlet end block is shown in detail in FIGS. 7 and 8. The inlet end block has a through bore forming an inlet port 70 for the manifold for the lubricant line '1 and an inlet port 71 for connection of fluid line 17, both such ports 70 and 71 being preferably threaded to facilitate the connection of the supply lines thereto. Whereas the port 70 for the lubricant line leads directly through the block, the porting from the fluid connection 71 leads to the end of high pressure spring loaded by-pass piston 72. The pressure of spring 73' against such piston is backed up by means of nut 74 and the piston 72 extends through such nut exteriorly of the block as shown at 75. Accordingly, when fluid pressure on the end of the piston 72 exceeds the force of the spring 73 holding it in position, the piston 72 will move to the left permitting fluid to by-pass through passage 76 leading through the face of the block. The passage 76 continues through the manifold in the form of a high pressure Toy-pass line and the outlet end block 56 is drilled on its inner face to receive this high pressure by-pass line or passage as shown at 77 in FIG. 8. In the outlet end block 56, the high pressure by-pass passage 77 rejoins the fluid line and such fluid line is provided with a threaded outlet port 78 for a further extension of the fluid line 17. The fluid in the inlet end block will normally pass outwardly through port 79 through the manifold and into the fluid port 80 in the outlet block 56 and then outwardly through the fluid outlet port 78. The outlet end block 56 is also provided with lubricant outlet port 81 for continuation of the lubricant line 1. Each of the inlet and outlet end blocks is provided with four apertures as shown at 82 for accommodation of the four

tie bolts

58, 59, 60 and 61.

=Fluid will be forced through the high pressure by-pass line 76 only in the case of a malfunction or blockage in one of the valves 52 through 55 in the manifold, and return of the valves, as hereinafter described, beyond the one malfunctioning can be provided by relieving the fluid pressure at the far end of the last manifold. This can be accomplished by providing a .by-pass passage around the piston 72, such passage having a reduced diameter por' tion as shown at 83, with a one-way check valve in the form of a ball 84 loaded by spring 85 held-by plug 86, providing a one-way by-pass for fluid flow from the high pressure passage 76 to the entering fluid port 71.

The Valve The valve as disclosed in FIGS. 9 through 16 is shown in a normal or rest position. The fluid passages in the position shown are fluid filled under, for example, 700 p.s.i., the relieved presure, and the lubricant passages between operating cycles being substantially at that pressure.

Referring more particularly to FIGS. 9 and 16, at the start of an operating cycle, lubricant pressure is raised to 2,000 p.s.i. and fluid pressure to 3,000 p.s.i. Fluid enters inlet passage (FIG. 11) moving through passageway 91 and around ,the relieved portion 92 of pilot piston 93, through passage 94 and then across to passage 95 (FIGS. and 13) and through relieved portion 96 of the main or metering piston 97 and out port 98 to the next valve.

As shown perhaps more clearly in FIG. 16, the pilot piston 93 and the main piston 97 are horizontally mova ble' in respective cylindrical bores 99 and 100, the bore 99 being closed by

plugs

101 and 102 and the bore 100 being closed by plug 103 and adjustable indicator 104.

Both the pilot and main pistons are multi-land pistons and are provided with appropriate sliding seals where required as shown.

Lubricant enters the valve member through throughbore 105 aligned with the inlet port 70 and the outlet port 81 in the inlet and outlet end iblocks respectively. Such through-bore 105 is connected by passage 106 to the cylindrical bore 99 of the pilot piston 93 adjacent the plug 101 as seen more clearly in FIG. 16.

At the stime time that theepbmsuloal ghmMFWYMF At the same time that the fluid is traversing the path above indicated, fluid enters passageway 107 (FIG. 11) and acts on the right-hand end 108 of the pilot piston to force that piston to the left. Lubricant within the bore 99 of the pilot piston will be displaced by such piston movement back into the bore 105 which is a portion of the supply line 1 until the central annular relief 109 on the pilot piston 93, which connects with the lubricant supply through central longitudinally extending passage 110 in the pilot piston, uncovers the passage 111 leading to the left hand end of the main piston97.

This opposite position of the pilot piston is shown in FIG; 17.

The annular relieved portion 112 of the pilot piston 93 will then be in position to connect passage 113 leading from the right hand end of main piston 97 through the discharge passage 113 leading to bearing B. According-ly, the lubricant pressure in passage 111 permitted by movement of the pilot piston will provide a lubricant pressure on the left-hand end 115 of the main piston 97 forcing such piston to the right until its indicator stem 116 is checked by the adjusting screws in the indicator bonnet 117. The lubricant displaced by movement of the main piston to the right is forced into passage 113 and through the relieved portion 112 of the pilot piston 93 outwardly through passage 1-14 to bearing B.

Referring to FIG. 10, it is noted that movement of the main piston 97, and thus the relieved portion 96, closes olf port 95 and uncovers port 118 thus interconnecting, through the relieved portion 96, port 98 and passage 118. Movement of the main piston 97 beyond this point is adjustable, since an adjustable stop is pro vided in the bonnet 117 for indicator stem 116, this adgistment regulating the volume displacement to hearing The movement of the pilot piston 93 to the left cuts off the fluid path from the entering port 90 around the relieved portion 92 of the pilot piston, and movement of the main piston to the right cuts off port 95 and thus the connection between port 95 and port 98 to the next valve. However, the left hand movement of the pilot piston 93 uncovers port 119 (FIGS. 11 and 17), so that fluid can flow from passageway 107 through the chamber 120 past the end of thenow shifted pilot piston 93 as shown in MG. 17. Movement of the main piston 97 to the right connects

ports

98 and 118, port 118 being connected-to port 119 through passage 121 as shown in FIG; 13 and in dotted lines in FIG. 15. This then enables fluid to take the alternate flow route indicated similarly to operate the next valve.

If, however, the discharge line leading to bearing B becomes plugged, displacement of the lubricant from the right ofithe main piston is prevented, but the pilot piston 93 nonethelessmoves to the left. As a result, both the

fluid'pa'ssages

94, 95 and 121, 113 are blocked. (Note 8 FIG. 13.) The resulting stoppage of the fluid with continued fluid pump operation causes the fluid pressure between the pump and the blocked valve to rise and at, say, 3,500 p.s.i., the high pressure by-pass fluid valve shown in FIG. 5 in the entering end block of the manifold is opened against its retarding spring 73, permitting such fluid to enter the high pressure by-pass line 76. In the valve, this by-pass line is in the form of a small diameter M through bore 122 aligned with the passage 76 in the ip inlet end block and the passage 77 in the outlet end block.

It will readily be seen that outward movement of the stem 75 of the high pressure bypass valve may be employed to actuate a limit switch to complete an electric alarm circuit as the pressure switch 35 energizes the alarm signal 36.

When thehigh pressure by-pass valve in the entering block of the manifold opens, fluid flows through the high pressure by-pass passage to the leaving end block 7 p where it reenters the fluid line. Since the main piston in that particular valve will still be in the rest position,

or at the left, the fluid will move through port 80 into outlet 98 and flow around the main piston relief from port 98 to port 95. The fluid will then move through passage 94 across the relieved portion 92 of the pilot piston 2 5' 93 which will still be at the right and pressure will then build at the right hand end of the pilot piston entering the chamber 120 of such valve through port 107. As the pilot piston 93 is forced to the left, it tends to close off communication between passage 94 and the port 107 through relieved portion 92. The length of the land at the extreme right of the pilot piston 93 should be such that before communication between passage 94 and port 107 is completely cut ofl it will have started to uncover port 119 which will assure complete leftward movement of the pilot piston, causing movement of the associated main piston to the right. Thus, it can be seen that with this valve it is possible to actuate such valve from either end of the manifold and accordingly all valves on either side of the malfunctioning valve will operate properly.

When the high fluid pressure has permeated the fluid system, and all valves have operated as described moving the pilot and main pistons to the positions shown in FIG.

17, the fluid pressure will be reduced or relieved to approximately 700 p.s.i. through operation of switch 32 thus lowering the fluid pressure. This makes the lubricant at 2,000 p.s.i. operative on the left hand ends of all the pilot pistons 93 substantially simultaneously. The pilot piston in the valve nearest the fluid source will move to the right as the fluid in chamber 120 displaced by such 5 movement is returned against 700 p.s.i. pressure to the reservoir 15.

The righthand movement of the pilot piston 93 will reconnect the lubricant pressure from passage to 113 as shown in FIG. 16 leading to the righthand end of the main piston 97, thus moving the main piston to the left and displacing lubricant from chamber 130 through pass-age 111 around the relieved portion 131 of the pilot piston 93 and out through passage 13 2 through the discharge connection 133 to hearing A, returning the valve 6 from the FIG. 17 to the FIG. 16 rest position. The

next valve in line then returns similarly, the fluid in chamher of such valve being relieved by fluid passage through outlet port 98, passageway 94, relieved portion 92, and inlet passage 90 of the first valve. All the valves 6 in the system are thus progressively returned.

75 position prevents return through the alternate route from 9 port 119 through port 118. Consequently, all valves following the malfunctioning one are held in their fluid high-pressure position and the fluid pressure beyond the malfunctioning valve remains high. The high-low pressure switches 35, 38 and 39 between manifolds in the fluid line can then be utilized to signal the location of the malfunctioning manifold.

Return of the valves beyond the malfunctioning one can be provided by relieving the fluid pressure at the far end of the last manifold as per line 43 in FIG. 1. Preferably, the passage including the restricted portion 83 and the one-way spring loaded check valve 84, 85 will be provided between the high pressure by-pass 76 and the fluid inlet 71 in each inlet end block of each manifold as shown in FIG. 5. Such construction then permits completion of operation of all of the valves by relieving fluid pressure beyond the malfunctioning valve by the one-way bypass relief valve in the inlet end block of the manifold and all of the pilot piston valves in the particular manifold will be relieved through this by-pass passage. Thus, the relieved by-

pass passage

76, 122 and 77 will provide the relief of pressure in the last valve in the manifold through port 98 and, since the main piston in that valve will be to the right as shown in FIG. 17, port 98 will be connected vw'th passages 118, 121 and 119' to the chamber 120, thus relieving the same. Valves beyond the malfunctioning manifolds will then be operated in the normal manner. The restricted passage 83 (FIG. may be sized to slow down the return of fluid by that route, and by such delay a signal of malfunction can be produced by means of the operating system with the high-low pressure switches being employed to locate the malfunctioning manifold from a remote point. It will, of course, be understood that such remote indication may not be required and in that case out-of-phase position of any valve indicator stem 116 will pinpoint a malfunctioning valve.

Referring now to FIGS. 2, 3, 4 and more particularly to FIG. 18, a low pressure cut-off mechanism 66 is provided for each of the bearing discharge outlets on each of the valves in the manifold. These low pressure cutoff mechanisms are brazed in place on the valve face, registering in the recess at the bearing discharge opening. These cut-ofi valves are each provided with plungers 140, such plungers extending transversely of outlet passages 141 and through spring housing 142. The plungers are provided with an annular shoulder 143 engaging spring 144 and a suitable seal 145 may be provided surrounding the plunger. Under normal lubricant pressures, the plunger will be held in the dotted line position shown at 146 clear of the discharge passage 141. When the pressure within such passage 141 drops below a nominal value, say 300 p.s.i., the pressure of spring 144 becomes greater than the lubricant pressure and the valve piston14t crosses the passage 141 and thereby blocks it as shown in the full line position in FIG. 18. It should be noted that the protruding low pressure cut-off valve stem 149 serves as an indicator of the position of that valve. In starting the system, this valve can be blocked open man ally to permit filling the lines and the discharge line pressure will then hold such valve open. In the event of discharge line failure, it will close and the position of the protruding stem will indicate the affected discharge line.

It is possible but improbable that a hearing may become so plugged with solids that lubricant penetration under the pressure provided i.e., 2,000 p.s.i., by such lubricating system is not possible. It is more probable that a loose connection in or rupture of a discharge line from the measuring valve to the hearing may prevent lubricant reaching the bearing. To permit a warning signal to be given in either eventuality, the lubricating system includes check valves 147 and 148 so that 700 p.s.i. flow resistance may be provided in the fitting employed to connect such discharge lines 149 to each bearing A, B, etc. lubrication opening (note FIG. 1). By this means, a

10 residual pressure to 700 p.s.i. is provided in the discharge lines and these low pressure cut-offs 66 are provided at each valve discharge outlet so that should the residual pressure in these lines fall below the nominal value of say 300 p.s.i., these valves will close off the discharge passage, automatically producing a blockage.

Referring particularly to FIGS. 10 and 14, it will be noted that the fluid inlet to the valve lines up with the fluid outlet 98 and both are in line with the

fluid passages

79 and 80 in the inlet and outlet end blocks in each manifold, respectively. Similarly, the lubricant passage is a throughbore lining up with the lubricant passages 70 and 81 in such inlet and outlets blocks. This is also true of the high pressure by-pass ports 122. Each of the valves is also provided with aligned apertures for accommodation of the

tie bolts

58, 59, 60 and 61 as are the inlet and outlet end blocks provided with apertures 82.

Alternative System Referring now to FIG. 19, there is illustrated an alternative lubricant system wherein a lubricant reservoir 15!) and electrically driven pump 151 are provided in place of the lubricant supply header as shown in FIG. 1. Electric motor 152 is employed to drive pump 151 to supply the requisite 2,000 p.s.i. pressure to the lubricant supply line 153 connecting the

valve manifolds

5, 7 and 8 in series in a manner identical to the connection of the lubricant supply line 1 to such manifolds in FIG. 1. In such case, the motor driven pump and control or starter takes the place of the solenoid operated shut-off valve 4 in FIG. 1. With this arrangement, no accumulator is positioned between the lubricant and fluid supply lines. The solenoid valve 154 is employed to open and close relief line 155, such relief line being provided with a 700 p.s.i. resistance check valve 156. Also, since the pump is electricially driven, a high-pressure relief line 157 is provided with a check valve 158 providing high-pressure relief at, for example, 4,000 p.s.i. leading back from the pump discharge to the reservoir. Thus with the shut ofi valve 154 open and the pump motor 152 turned off, a residual line pressure in the line 153 of 700 p.s.i. will be obtained. When the motor 152 is turned on the 4,000 p.s.i. relief valve 158 will lead back to the reservoir through line 157 should such excessive pressure be obtained. Control box 159 is provided controlling motor 152 and solenoid valve 154 through line 160 and a bank of signal lights and associated high-low pressure switches may be provided as shown at 37 in a manner identical to that shown in FIG. 1.

Pressure in the fluid supply line 162 may be provided through air driven pump 163 supplied by air through line 164. Air pressure in line 164 is controlled by solenoid operated valve 165 supplying air from header 166. An air motor 167 is employed to control shut-off valve 168 in relief line 169 with a 700 p.s.i. relief valve 170 also being provided. Such air motor 167 will also be controlled by solenoid valve 165 controlled from the control box 169. As in the FIG. 1 embodiment, a pressure switch 171 may be employed to indicate to the control center 159 the completion of the high pressure fluid cycle to stop operation of fluid pump 163 and open relief line valve 168 permitting the excess of lubricant pressure over the fluid pressure to return the valves to their rest position.

Referring now to the electrical diagram in FIG. 20, the various electrical components illustrated may be employed to control the FIG. 1 embodiment of the present system. Such components are wired between suitable mains and 181. In the control box 31, a timer motor 182 is controlled by a cut-out switch 183 and controls cycle switch 184 and signal switch 185 with clutch solenoid 186 engaging and disengaging the timer motor 182 which runs continuously. In operation, the timer will control the cycle switch 185 to energize control relay 187 if the proper reset contacts are closed as hereinafter described. Energization of relay 187 closes normally open contacts 188 to energize relay 189. This is a pilot circuit for starting both the lubricant and fluid systems. Energization of relay 189; closes both sets of contacts 190 and 191 with the closing of contacts 190 energizing solenoid valve 12 (FIG. 1). Energization of this solenoid valve controls air motor 10 to open shut-01f valve 4 in the lubricant supply line 1. The closing of contacts 191 energizes solenoid valve 18 starting the fluid pump 16 as well as operating

air motors

25 and 47 to close shut-ofi? valves 24 and 46 respectively. With such solenoids energized, the system is now in operation. 7

The high pressure switch 32 which is located in the fluid system line after the last manifold or in the last valve which is set for approximately 3,000 p.s.i. indicates completion of the fluid cycle and energizes reset relay 33 when such pressure is obtained at the end of the last manifold. Reset relay 33 closes normally open contacts 192 and opens normally closed contacts 193 deenergizing relay 187 opening both contacts 190 and 191 to deenergize solenoid valves 12 and 18 stopping both systems. Also the clutch will be engaged through solenoid 186 to start the time interval until the next cycle.

High pressure switch 35 energizes signal lamp 36 in the signal lamp bank 37 and low pressure or broken line switch 48, which is located in the fluid system aheadof the first manifold and set for-approximately 650 p.s.i. indicating a broken line, may be employed in either system to energize signal lamp 49. High pressure switch 38 is located between manifold-s and 7 and is set for approximately 3,500 p.s.i., indicating a malfunction of the succeeding manifold, and such switch energizes signal lamp 40; and finally high pressure switch 39 energizes signal lamp 41 in the same manner as switches 35 and 38. It is noted that each of the

switches

32,35, 48 and 38 and 39 is'provided with a set of contacts in series with control relay 194. Control relay 194 controls contacts 195 in the timing cycle and Warning circuit in series with relay 187. Such relay 194 prevents the system starting and will cause an alarm if not reset at the proper time. Thus, all of the switches 32, '35, 48, .38 and 39 must be properly set before the system can be placed in operation. The signal lamp 196 may be employed in series with control relay 187 to indicate when such relay is not energized through the cycle and signal switches 1-84 and 185. respectively. It will, of course, beunderstood that the illustrated circuit is employed with only three manifolds of valves and accordingly only the appurtenant signaling switches are indicated. If an extensive system is employed, additional switches will, of' course, be employed.

it will now be seen that there has been provided not only a valve structure but a centralized lubricating system capable of handling either grease or oil; of delivering such lubricant under pressure to all interconnected bearings in measured but adjustable amounts; of signaling bearing discharge line leakageror stoppage through system pressure change without interrupting operation of unaffected valves; and of giving visual indication of the precise point of operational failure.

Other modes of applying the principles of the invention may be employed, change being made as regards the details described, provided the features stated in any of the following claims or the equivalent of such be employed.

I, therefore, particularly point out and distinctly claim as my invention:

l. A centralized lubricating system comprising a lubricant supply line and a fluid control line, a plurality of lubricant metering valves serially interconnected in said lubricant supply line and said fluid line, means to place said lubricantsupply line at a substantially constant line pressure; means to raise the pressure in said fluid line above the pressure in said lubricant line to cause discharge of lubricant through said lubricant metering valves, and means to lower the fluid pressure in said fluid line below thepressure in said lubricant supply line again to cause discharge of lubricant through said lubricant valves.

2. In a centralized lubricating system, a source of lubricant under pressure, a plurality of metering valves connected to said source of lubricant under pressure, a hydraulic fluid'circuit connected to said metering valves, said metering valves each having two lubricant discharge outlets, and means to force lubricant through one said discharge outlet when the pressure of the hydraulic fluid exceeds the lubricant pressure, and means to force lubricant through the other said discharge outlet when such fluid pressure falls below such lubricant pressure. i

3. The system set forth in claim 2 including means to vary the fluid line pressure from substantially above such lubricant line pressure to substantially below such lubricant line pressure.

4. A centralized lubricating system comprising a lubricant supply line, means to pressurize said lubricant supply line, a plurality of metering valves connected in series in said lubricant supply line,two lubricant outlets in each said metering valves, a fluid control line connected parallel to said lubricant supply line and in series with said metering valves, said valves including means responsive to an excess of pressure in said fluid supply line over the pressure in said lubricant supply line to force a metered quantity of lubricant through one said lubricant outlet, and means responsive to an excess of pressurein said lubricant supply line over the pressure in said fluid supply line to force a metered amount of lubricant through the other said lubricant outlet.

5. A centralized lubricating system as set forth in claim 4 including means to create a pressure in said fluid control line substantially in excess of the pressure in said lubricant supply line, and means to relieve the pressure in said fluid control line whereby the pressure in said lubricant supply line will be substantially in excess of the pressure in said fluid control line.

6. A centralized lubricating system as set forth in claim 4 including means to create a pressure in said fluid control line substantially in excess of the pressure in said lubricant supply line, and means responsive to the attainment of such pressure in said fluid control line in the most remote portion of said system to relieve the pressure in said fluid control line whereby the pressure in said lubricant supply line will be substantially in excess of the pressure in said fluid control line. 7

7. A centralized lubricating system comprising a lubricant supply source, means to pressurize said lubricant supply, a plurality of metering valves connected to said including means responsive to an excessive pressure of said fluid over lubricant pressure to force a metered quantity of lubricant through one of said lubricant outlets in each said valve, and means responsive to an excessive pressure of said lubricant over fluid pressure to force a metered amount of lubricant through the other said lubricant outlet in each said valve.

8. A centralized lubricating system as set forth in claim 7 wherein said metering valves each include apilot piston and a main piston, means connecting one end of said pilot piston to said fluid pressure source, and means connecting theother end of said pilot piston to said lubricant pressure source; and means responsive to movement of said pilot piston to connect opposite ends of said main pistonwith said lubricant pressure source.

9. A centralized lubricating system as set forth in claim 7 8 including means responsive to reciprocation of said pilot 13 fold to the outlet side of said manifold, said fluid by-pass line connecting the fluid inlet of said manifold to the fluid outlet of said manifold.

11. A centralized lubricating system as set forth in claim wherein said by-pass line includes a pressure operated valve therein, and means to open said valve upon the attainment of a predetermined high pressure in said fluid supply.

12. A centralized lubricating system as set forth in claim 11 including a passage around said high pressure by-pass valve, said passage including a relief valve adapted to permit relief of such fluid through such by-pass passage.

13. A centralized lubricating system and the like comprising a metering valve having a main piston and a pilot piston, means connecting one end only of said pilot piston to a source of lubricant under pressure, means responsive to movement of said pilot piston toward said one end to connect said source of lubricant under presure to one end of said main piston, and means responsive to such movement of said pilot piston to port the opposite side of said main piston to a bearing and the like.

14. The system as set forth in claim 13 including fluid pressure means to move said pilot piston.

15. A system as set forth in claim 14 wherein said pilot piston includes means alternately to connect opposite ends of said main piston with said source of lubricant under pressure upon movement of said pilot piston.

16. A system as set forth in claim 15 wherein said pilot piston includes means alternately to connect the opposite ends of said main piston to separate bearing discharge lines upon reciprocation of said pilot piston.

17. A system as set forth in claim 14 wherein said fluid pressure means includes alternate fluid passages for said pilot piston in the extreme positions thereof, said passages being open and closed by movement of said main and pilot pistons.

18. A system as set forth in claim 17 wherein both said alternate passages will be closed when said main and pilot pistons are in an out-of-phase position, and fluid pressure by-pass means operative responsive to such out-of-phase position of said main and pilot pistons.

19. A metering valve as set forth in claim 13 including a valve housing for said metering valve, and fluid pressure passages therein adapted to operate said pilot piston, said fluid passages therein being positioned such that said valve can be manifolded.

20. A centralized lubricating system comprising a source of lubricant under pressure, a lubricant supply line leading therefrom; a plurality of lubricant metering valves connected to said lubricant supply line; a source of fluid under pressure, a fluid supply line leading therefrom, means connecting said fluid supply line to said metering valves; and means simultaneously to pressurize said lubricant and fluid supply lines at high yet different pressures to operate said metering valves to dispense lubricant therethrough, and means simultaneously to pressurize said lubricant and fluid supply lines with reversing differential pressures and equalize the pressures in said fluid and lubricant supply lines after all such valves have been operated.

21. A centralized lubricating system as set forth in claim 20 wherein each said valve includes two lubricant outlets, lubricant being discharged through one said outlet when said supply lines are pressurized and through the other said outlet when said fluid supply line is relieved.

22. A centralized lubricating system as set forth in claim 21 including manifolds of said valves, means adjacent each manifold adapted to indicate excessive pressure variance in said fluid supply line.

23. -A centralized lubricating system as set forth in 14 claim 22 including means at the distal end of said system to relieve said system in response to the obtaining of such high pressure in said fluid supply line at such distal end.

24. A centralized lubricating system as set forth in claim 23 including accumulator means interconnecting said lubricant and fluid supply lines to equalize the atrest pressure in said system.

25. A centralized lubricating system as set forth in claim 20 including pressure relief lines connected to said fluid and lubricant supply lines, shutoff valves in each said pressure relief line, and control means to close said shutoff valves when said fluid and lubricant supply lines are pressurized at such high yet dilferent pressures.

26. A centralized lubricating system as set forth in claim 25 including pump means operative thus to pressurize said lubricant and fluid supply lines, and means responsive to such pressure at the distal end of said system to turn ofl said pump means and open said shutofi valves.

27. A centralized lubricating system as set forth in claim 20 including a pressurized lubricant header, said lubricant supply line being connected thereto, a shutoff valve in said lubricant supply line, pump means to pressurize said fluid supply line, and means simultaneously to open said shutolf valve and energize said pump means thus to pressurize said lubricant and fluid supply lines.

28. A centralized lubricating system as set forth in claim 27 including means simultaneously to relieve the pressure in said fluid supply line and deenergize said pump means upon the attainment of a predetermined high pressure at the distal end of such system.

29. A centralized lubricating system as set forth in claim 28 including accumulator means interconnecting said lubricant and fluid supply lines to equalize the at rest pressure in said system.

30. A system as set forth in claim 2 wherein said lubricant discharge outlets are each provided with a line connected to a bearing structure or the like, and means responsive to line failure resulting in an abnormal decrease in pressure in said line to block said line and provide a visual signal at such line pin-pointing such line failure.

31. A centralized lubricating system comprising a lubricant supply line and a fluid supply line, a plurality of lubricant metering valves connected to said lubricant and fluid supply lines each having a lubricant discharge outlet; means simultaneously to pressurize said lubricant and fluid supply lines at high yet different pressures to operate said metering valves to dispense lubricant therethrough, said lubricant discharge outlets each being provided with a line connecting such outlets to a bearing structure or the like, and means responsive to said latter line failure resulting in an abnormal decrease in pressure in said latter line to block said line and provide a visual signal at such line pin-pointing such line failure.

32. A centralized lubricating system as set forth in claim 9 wherein each said valve includes alternate fluid passages therethrough, movement of said pilot piston and the resulting movement of said main piston closing one of said alternate passages and opening the other to permit fluid flow therethrough similarly to operate the next succeeding valve.

References Cited in the file of this patent UNITED STATES PATENTS 1,958,187 Dirkes May 8, 1934 2,038,287 Hawkes et al. Apr. 21, 1936 2,240,158 Hillis Apr. 29, 1941 2,719,603 Le Clair Oct. 4, 1955 2,973,058 Bricout Feb. 28, 1961