US3698838A - Automatic fluid supply and control means - Google Patents

Automatic fluid supply and control means Download PDF

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Publication number
US3698838A
US3698838A US114479A US3698838DA US3698838A US 3698838 A US3698838 A US 3698838A US 114479 A US114479 A US 114479A US 3698838D A US3698838D A US 3698838DA US 3698838 A US3698838 A US 3698838A
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United States
Prior art keywords
fluid
line
compressor
control means
receiver
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Expired - Lifetime
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US114479A
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English (en)
Inventor
John E Holdsworth
Dallas M Weir
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Ingersoll Rand Co
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Ingersoll Rand Co
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
    • F04C29/0014—Injection of a fluid in the working chamber for sealing, cooling and lubricating with control systems for the injection of the fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0207—Lubrication with lubrication control systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16N—LUBRICATING
    • F16N29/00—Special means in lubricating arrangements or systems providing for the indication or detection of undesired conditions; Use of devices responsive to conditions in lubricating arrangements or systems
    • F16N29/02—Special means in lubricating arrangements or systems providing for the indication or detection of undesired conditions; Use of devices responsive to conditions in lubricating arrangements or systems for influencing the supply of lubricant

Definitions

  • an automatically-operative sub-system for controlling oil supply from the receiver to the compressor.
  • the sub-system means include a flow-control valve signal-operative solely from fluid power, i.e., from receiver fluid pressure, to insure oil supply when the compressor starts up, and operative to insure oil supply cut-off when the compressor is halted.
  • This invention pertains to fluid supply and control means and in particular to such means automatically operative for cutting off the flow of fluid, suchas oil to an oil flooded air compressor, or like machine, when the machine is stopped, and operative to insure fluid supply to the machine at start-up.
  • Automatically-operative fluid supply and control means are known, of course, and typically they employ liquid flow control valves of either one of two types: the normally closed? or the normally open flow control valve.
  • the normally closed valve has a disadvantage in that a signal, comprising a component of fluid pressure, or the like, is required to hold the valve open, and-if the signal should be interrupted, from whatever cause, the valve will close. This would result in a disastrous lack of supply of cooling oil for the gas compressor if, for instance, the means are deployed to such use.
  • Thenormally open valve has a disadvantage in that, notoriously, and almost invariably, a spring is used to hold the valve open.
  • first fluidactuable valve means having means for interruptive interpositioning thereof in said supply line, selectively operative in a plurality of positions for conducting a flow of fluid therethrough in a first operative position, and for interdicting a fluid flow therethrough in a second operative position
  • control means coupled to said first valve means, having means for effecting a fluid through-connection thereof with said receiver and said compressor, automatically operative, in response to a start-up of said compressor, to dispose said first valve means in said first operative position solely by fluid power.
  • FIG. 1 is a schematic diagram of a gas compressor and compressed-gas receiver system with which an embodiment of the novel fluid supply and control means has been operatively through-connected;
  • FIG. 2 is an axial, cross-sectional view of the flowfcontrol valve of the FIG. 1 embodiment.
  • a compressed-gas system 10 theredepicted comprises a gas compressor 12 and a compressed-gas receiver 14.
  • a discharge line 16 conductsthe compressed-gas productto the receiver 14 from the compressor 12, by way of a check valve 18.
  • the receiver 14 confines a reservoir of compressor cooling and sealing oil 20 which is supplied to the compressor 12 by a fluid supply line 22.
  • the receiver has a compressed-gas output line 24, and a compressed-gas device supply line 25.
  • the fore-described compressed-gas system 10 is quite conventional for such'systems whichemploy an oil-flooded compressor, and it is proposed to represent compressor 12 herewith and herein as a compressor of that type.
  • the novel fluid supply and control means 26 here taught comprises a first, normally-open, flow-control valve 28 operatively and interruptively interpositioned in line 22, a second, normally-open, flow-control valve 30 similarly interpositioned in line24, first and second fluid-pressure pilot lines 32 and 34, respectively, and an orifice member 36, the latter restrictively interposed in line 24.
  • First flow-control valve 28, of our design, as FIG. 2 evidences, comprises a housing 38 which defines a chamber or cylinder 40 therewithin.
  • a pair of spaced apart ports 42 and 44 open at either ends externally of the housing 38 and internally on cylinder 40.
  • Port 42 is threaded to receive a first portion of line 22 thereat, for admittance of oil into the cylinder 40 from receiver 14, and port 44 is threaded to receive a second portion of line 22 thereat, for the conduct of oil from the cylinder 40 to the compressor 12.
  • the oil 20 is admissible from port 42 toport 44, via a land 46 formed in housing 38, when the land is not obstructed.
  • a piston 48 is movably disposed in the housing 38 for opening and for obstructing land 46.
  • Piston 48 is resiliently urged, by spring 50, normally to assume the position shown in full-line illustration in which land 46 is unobstructed.
  • a third port 52 is formed in housing 38 and opens externally of the housing and internally onto a large bearing surface 54 of piston 48. Port 52 is threaded thereat to receive a termination of line 32. Fluidpressure admitted via port 52 bears upon surface 54, and the fluid pressure of the oil 20 admitted via port 42 is operative upon the small bearing surface 56 at the other end of piston 48.
  • a check valving element 58 is slidably mounted on a housing-carried rod 60 to close off port 42 in the absence of oil pressure thereat; in the full-line illustration of element 58 it is proposed to suggest that oil pressure causes a coursing of oil through ports 42 and 44. In the absence of oil pressure, element 58 assumes the dashed-line positioning shown; in the presence of fluid pressure at port 52, piston 48 assumes the dashedline positioning shown. Port 62 simply provides for a bleeding-off of oil or gas which leaks past the O-ring seals disposed about piston 48.
  • valve 28 When the compressor 12 is operating normally, the valve 28 is in the open position, to conduct oil 20 from port 42 to port 44 the piston 48 being held by the spring 50, and by oil pressure on the small surface 56 of the piston. There is no pressure in the first pilot line 32 which is open to atmosphere through the connection of an end thereof with output line 24 and orifice member 36; valve 30 is closed at this time due to compressor operation.
  • the receiver 14 is under compressor gas discharge pressure, accordingly, oil 20 flows from the receiver 14 through line 22, through the valve 28 and into the gas compressor 12. In the gas compressor 12, the oil is mixedwith the gas being compressed and is discharged back to the receiver 14 by way of the compressor discharge line 16.
  • the pressure in the compressor discharge line 16 falls to atmospheric levels upstream of check valve 18. This causes the pressure in pilot line 34 to fall to atmospheric pressure. This allows the normally-open, second flow-control valve 30 to open and exhaust the pressure from the receiver 14 to atmosphere through the restrictive orifice member 36.
  • the orifice member 36 has a restrictive orifice so sized, in relation to the valve 30 that at all significant receiver pressures it will maintain a marked pressure differential thereacross. Accordingly, the pressure in pilot line 32 will be substantially equal to the pressure in the receiver 14.
  • the pressure in pilot line 32 acts on the large surface 54 of the piston 48.
  • the area of the large surface 54 of the piston 48 is configured to be at least 1% times greater than the area of the small surface 56 of the piston 48.
  • the pressure in pilot line 32 acting on the large surface 54 of the piston 48 thus overcomes both spring 50 and the oil pressure in line 22 acting on the small surface 56 of the piston 48, and the valve 28 closes, preventing the flow of oil into the compressor 12 with the consequences described before.
  • Our novel fluid supply and control means 26 accomplishes the following functions: l Automatically shuts off the oil flow to the compressor 12 solely on a fluidpower signal which only occurs when the compressor is shut down. (2 The valve 28 normally re-opens immediately afterv all pressure is relieved from the receiver 14. (3) In the event of spring failure normally to open the valve 28, or the build-up of gummy deposits on piston 48, the system oil pressure alone will force open the valve 28, allowing for normal flow, with subsequent start-up of the compressor 12.
  • first fluid actuable valve means having means for interruptive interpositioning thereof in said supply line, selectively operative in a plurality of positions for conducting a flow of fluid therethrough in a first operative position, and for interdicting a fluid flow therethrough in a second operative position; and control means coupled to said first valve means, having means for effecting a fluid through-connection thereof with said receiver and said compressor, automatically operative, in response to a start-up of said compressor, to dispose said first valve means in said first operative position solely by fluid power; wherein said control means is further automatically operative in response to shut down of said compressor, to dispose said first valve means in said second operative position solely by fluid power; and
  • said fluid through-connection effecting means, of said control means comprises a first fluid-pressure pilot line having opposite ends thereof coupled to and opening on said valve means and said output line, for accomodating a conduct of actuating fluid from said output line to said first valve means to effect a disposal of the latter in said second operative position, and a second fluid-pressure pilot line having one end thereof coupled to and opening on said discharge line; and further including second fluid actuable valve means, having means for interruptive interpositioning thereof in said output line, selectively operative in a plurality of positions for conducting a flow of fluid therethrough in a given operative position, and for interdictin g a fluid flow therethrough in another operative position; and
  • Fluid supply and control means for operative interpositioning in said output line to effect a maintenance of said actuating fluid, in said first fluid-pressure pilot line, at a pressure substantially equal to that of pressure of gas in said receiver.
  • Fluid supply and control means according to claim 1, wherein:
  • Fluid supply and control means according to claim 1, wherein:
  • Fluid supply and control means according to claim 6, wherein:
  • said first fluid actuable valve means comprises a housing having a cylinder defined therewithin, and first and second spaced-apart ports formed in said housing, each of said first and second ports opening on said cylinder and externally of said housing, and wall means movably disposed within said cylinder both for interrupting and for permitting fluid communication between said first and second ports, said first and second ports each having means for threadedly coupling a portion of said supply line thereto; and
  • said wall means is movably responsive to 5 pressure of fluid in said supply line, to provide fluid communication between said ports and to accomodate a conduct of fluid through said housing.
  • said wall means comprises a piston and means engaging surfaces of both said piston and said housing for urging said piston to a disposition which facilitates a fluid communication between said first and second ports.
  • Fluid supply and control means further including:
  • a third port formed in said housing, spaced from said first and second ports, and opening on said cylinder and externally of said housing, said third port having means for threadedly coupling one end of said first fluid-pressure pilot line thereto;
  • Fluid supply and control means according to claim 9, wherein:
  • Fluid supply and control means according to claim 10, wherein:
  • said one surface comprises an area greater than that of said other surface.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
US114479A 1971-02-11 1971-02-11 Automatic fluid supply and control means Expired - Lifetime US3698838A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US11447971A 1971-02-11 1971-02-11

Publications (1)

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US3698838A true US3698838A (en) 1972-10-17

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US114479A Expired - Lifetime US3698838A (en) 1971-02-11 1971-02-11 Automatic fluid supply and control means

Country Status (7)

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US (1) US3698838A (xx)
AU (1) AU450534B2 (xx)
BR (1) BR7200747D0 (xx)
CA (1) CA955144A (xx)
GB (1) GB1323780A (xx)
IT (1) IT943854B (xx)
ZA (1) ZA717691B (xx)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2343184A1 (fr) * 1976-03-03 1977-09-30 Hoerbiger Ventilwerke Ag Dispositif de commande pour l'injection d'huile dans un compresseur helicoide
EP0067949A2 (de) * 1981-06-05 1982-12-29 Bauer Schraubenverdichter Gmbh Ventilblock für das Steuern der Ölzufuhr eines Schraubenverdichters
US4583919A (en) * 1984-06-18 1986-04-22 Ingersoll-Rand Company Lubrication system for a compressor
US4605357A (en) * 1984-06-18 1986-08-12 Ingersoll-Rand Company Lubrication system for a compressor
US20030173155A1 (en) * 2002-03-14 2003-09-18 Jean-Louis Picouet Suction oil injection for rotary compressor
US20040057836A1 (en) * 2002-09-25 2004-03-25 Caterpillar Inc. Hydraulic pump circuit
US9358856B2 (en) 2013-10-03 2016-06-07 Ford Global Technologies, Llc System off configuration for climate control system
US9856866B2 (en) 2011-01-28 2018-01-02 Wabtec Holding Corp. Oil-free air compressor for rail vehicles

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60249691A (ja) * 1984-05-21 1985-12-10 ゼネラル　シグナル　コーポレーシヨン 回転ピストン真空ポンプ
DE4438827C2 (de) * 1993-10-19 1996-12-12 Mannesmann Ag Ansaugregler

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2343184A1 (fr) * 1976-03-03 1977-09-30 Hoerbiger Ventilwerke Ag Dispositif de commande pour l'injection d'huile dans un compresseur helicoide
EP0067949A2 (de) * 1981-06-05 1982-12-29 Bauer Schraubenverdichter Gmbh Ventilblock für das Steuern der Ölzufuhr eines Schraubenverdichters
EP0067949A3 (en) * 1981-06-05 1983-01-12 Bauer Schraubenverdichter Gmbh Valve block for controlling the oil supply of a screw compressor
US4583919A (en) * 1984-06-18 1986-04-22 Ingersoll-Rand Company Lubrication system for a compressor
US4605357A (en) * 1984-06-18 1986-08-12 Ingersoll-Rand Company Lubrication system for a compressor
US20030173155A1 (en) * 2002-03-14 2003-09-18 Jean-Louis Picouet Suction oil injection for rotary compressor
WO2003078807A2 (en) * 2002-03-14 2003-09-25 Vilter Manufacturing Corporation Suction oil injection for rotary compressor
WO2003078807A3 (en) * 2002-03-14 2004-01-15 Vilter Manufacturing Corp Suction oil injection for rotary compressor
US7011183B2 (en) 2002-03-14 2006-03-14 Vilter Manufacturing Llc Suction oil injection for rotary compressor
US20040057836A1 (en) * 2002-09-25 2004-03-25 Caterpillar Inc. Hydraulic pump circuit
US9856866B2 (en) 2011-01-28 2018-01-02 Wabtec Holding Corp. Oil-free air compressor for rail vehicles
US9358856B2 (en) 2013-10-03 2016-06-07 Ford Global Technologies, Llc System off configuration for climate control system

Also Published As

Publication number Publication date
BR7200747D0 (pt) 1973-05-17
IT943854B (it) 1973-04-10
GB1323780A (en) 1973-07-18
CA955144A (en) 1974-09-24
ZA717691B (en) 1972-08-30
AU450534B2 (en) 1974-07-11
AU3616471A (en) 1973-05-31

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