WO1981000276A1 - Pompe de mesure d'un lubrifiant - Google Patents

Pompe de mesure d'un lubrifiant Download PDF

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Publication number
WO1981000276A1
WO1981000276A1 PCT/US1979/000494 US7900494W WO8100276A1 WO 1981000276 A1 WO1981000276 A1 WO 1981000276A1 US 7900494 W US7900494 W US 7900494W WO 8100276 A1 WO8100276 A1 WO 8100276A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
chamber
casing
fluid
shaft
Prior art date
Application number
PCT/US1979/000494
Other languages
English (en)
Inventor
P Staebler
A Goloff
G Grim
Original Assignee
P Staebler
A Goloff
G Grim
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by P Staebler, A Goloff, G Grim filed Critical P Staebler
Priority to PCT/US1979/000494 priority Critical patent/WO1981000276A1/fr
Publication of WO1981000276A1 publication Critical patent/WO1981000276A1/fr

Links

Classifications

    • 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
    • F16N13/00—Lubricating-pumps
    • F16N13/22—Lubricating-pumps with distributing equipment

Definitions

  • This invention relates to a pump for metering fluids and more particularly to a pump for metering minute quantities of lubricant to components of engines, machine tools or the like.
  • the quantity of lubricant necessary may be minute, but the lubricant needs to be steadily delivered.
  • components which need only minute quantities of constantly supplied lubricant are, for example, the valve guides or the cylinder liners in diesel engines, seals of rotary engines, and moving parts in machine tools. Supplying lubricant in excess of need is wasteful, but supplying lubricant less than needed creates undesirable consequences.
  • a lubricant metering pump which includes a first member, a second member, inlet means for communicating fluid to the pump, outlet means for communicating fluid exteriorly of the pump, and chamber means for metering the flow of fluid from said inlet means to said outlet means.
  • the chamber means is defined radially between said first and second members.
  • the pump is improved by providing adjustment means for precisely adjusting the fluid flow from said inlet means to said outlet means.
  • Figure 1 is an end view of a first pump embodiment of the present invention
  • Figure 2 is a side view of a second pump embodiment of the present invention.
  • Figure 3 is a cross-sectional view, taken along line III-III of Figure 2;
  • Figure 4 is a side view of a third pump embodiment of the present invention.
  • Figure 5 is a view similar to Figure 3, but including an alternative feature of the present invention.
  • Figure 1 illustrates a first embodiment of the present invention as a pump 10 for metering fluid.
  • the pump 10 includes a first member which may be a shaft 12 having a cylindrical outer surface 14 defined thereon.
  • the shaft 12 may be rotated about its axis by any one of a variety of conventional input means which is not herein illustrated.
  • the shaft 12, when rotating, preferably does not carry a load for the engine, machine tool or the like with which the pump 10 is usefully combined.
  • the means for rotating the shaft 12 may rotate the shaft over a range of speeds, but more preferably rotates the shaft 12 in a rotational direction 20 at a substantially constant speed.
  • the pump 10 includes a second member which may be a resiliently deformable casing 22 having an inner surface 24 defined thereon, the surface 24 being spaced outwardly from the shaft surface 14.
  • the first and second members define a chamber 28 radially between the surfaces 24 and 14 thereof.
  • the chamber 28 is defined by a variable dimension 29, as further discussed hereinafter.
  • the shaft surface 14 and the casing surface 24 are normally concentric.
  • the chamber 28 extends longitudinally and may be open at its ends (as is illustrated in Figure 1) or may be closed, such as by conventional seals or the like.
  • chamber 28 is open or closed at ends thereof is primarily dependent upon convenience in the particular application thereof.
  • the pump 10 includes an inlet means 30 for communicating fluid to the chamber 28, and an outlet means 32 for communicating fluid exteriorly from the chamber 28 and pump 10.
  • An adjustment means 34 is provided for selectively varying the size of radial dii ⁇ ension 29 to control fluid flow through outlet means 32, as described more fully hereinafter.
  • the inlet means 30 communicates fluid from the casing 22 into the chamber 28 and may include a bore 42 extending into the casing 22 and communicating with a slot 44 formed in the casing to terminate at surface 24 thereof.
  • a fluid source (not illustrated), which may be any one of a variety of conventional fluid supply sources, such as a standard engine oil pump, an auxiliary pump, or any other applicable fluid pumping source, communicates the working fluid to the bore 42.
  • the slot 44 preferably extends longitudinally along the casing surface 24 a predetermined distance, and terminates short of the casing surface 24 length.
  • the outlet means 32 communicates fluid from the chamber 28 to the exterior of the pump 10, and may comprise a slot 48 formed in the casing to terminate at surface 24.
  • the slot 48 preferably extends longitudinally along the casing surface 24 a predetermined distance and terminates short of the casing surface 24 length.
  • the slot 48 is preferably about the same length as the slot 44.
  • the variable radial dimension 29 is defined as adjacent to slot 48 for explanation purposes herein.
  • the outlet means 32 communicates the fluid exteriorly to a fluid actuated device (not illustrated) of an engine, machine tool or the like, and may simply include a bore 50 within casing 22, the bore 50 communicating with the slot 48.
  • the slot 44 may be diametrically opposed from the slot 48; however, it is preferred that slot 44 be circumferentially spaced on the upstream side of slot 48 to subtend an angle of about 225° to about 270° therefrom.
  • the pump embodiment 10 includes the adjustment means 34 for selectively varying the radial dimension 29.
  • Radial dimension 29 will normally be on the order of .0001" (.0002 cm).
  • the adjustment means 34 is shown in the form of a deforming means for deforming the casing 22 to change the normal circular configuration of the casing surface 24.
  • the casing 22 of pump embodiment 10 is formed of a material which is sufficiently resiliently deformable to selectively vary the radial dimension 29 when a deforming load is applied to the casing 22. Such variation is, for example, on the order of 0.00001" (0.00025 mm).
  • the particular degree of deformation of the casing 22 varies depending upon the modulus of elasticity of the material from which the casing 22 is formed and the thickness of the casing 22; for example, deformation in the order of 0.0001" (0.002cm) when the material for casing 22 is steel and the casing 22 is of a thickness of about 0.25" (6.4 mm) provides a sufficient change of radial dimension 29 to insure the desired range of fluid flow through outlet means 32.
  • the deforming means may be a clamp member 54 having a pair of arms 56,58 each engaging the casing 22, the arms 56,58 being compressible upon the casing 22 by a differential screw member 60.
  • Clamp member 54 includes a protrusion 62 carried by one of the arms, such as by arm 58, the protrusion 62 preferably being aligned radially with the slot 48 and axially . extending therebeneath.
  • the other arm 56 has a yoke-shaped surface 59 engaging the casing 22 on the diametrically opposite side from protrusion 62.
  • the screw member 60 may include two sets of threads 66,68, wherein one set of threads 68, associated with the arm 58 which carries protrusion 62, may be of a slightly smaller pitch than that of threads 66.
  • the pump 10 receives fluid into bore 42 and hence into the slot 44.
  • the shaft 12 rotates in the direction of arrow 20
  • the fluid is distributed from slot 44 and flows substantially circumferentially within chamber 28 in the direction of rotation.
  • the casing surface 24 and the shaft surface 14 are normally substantially concentric, and thus the radial dimension 29 will be equal throughout the circumferential length of chamber 28 prior to deformation of the casing 22.
  • the dimension 29 decreases towards a minimum radial clearance between the casing and shaft surfaces 24,14.
  • a second pump embodiment 70 includes a first member or shaft 72, with a first portion 73 having a frusto-conically shaped outer surface 74 defined thereon.
  • a second member or casing is disposed radially outwardly from the first member and has a frusto-conically shaped inner surface 84 defined thereon arid disposed radially outwardly of the surface 74 to define a chamber 88 therebetween.
  • the chamber 88 has a radial dimension 89.
  • a second, driving portion 75 of the shaft 72 has a key 90 formed on an end thereof which detachably engages a slot 91, formed on an opposed end of the first portion 73 of the shaft in driving relationship therewith.
  • Second portion 75 can be suitably connected to a standard drive input to thus rotate shaft portion 73 through key and slot connection
  • the pump embodiment 70 also includes an inlet means 30a for communicating fluid to the pump 70, and an outlet means 32a for communicating fluid exteriorly of the pump.
  • the inlet means 30a and the outlet means 32a of the pump embodiment 70 function substantially the same as the previously described inlet means 30 and outlet means 32 for the pump embodiment 10.
  • the shaft surface 74 of pump 70 varies from surface 14 of the pump 10 embodiment in being conical, the casing surface 84 also being conical.
  • the shaft and casing surfaces 74,84 are substantially coaxial and have similar, relatively small cone angles, preferably of about 5° , and are positioned one with respect to the other to define the radial dimension 89 of chamber 88 which is substantially constant in dimension throughout the axial and circumferential lengths thereof.
  • the pump embodiment 70 includes an adjustment means 92 which functions similarly to the adjustment means 34 described for pump 10, except that radial dimension 89 is varied by moving surfaces 74 and 84 axially (rather than radially) relative each other.
  • the adjustment means 92 differs from the adjustment means 34 of pump 10 by displacing the shaft surface 74 axially with respect to the casing surface 84 rather than the deforming described for pump embodiment 10.
  • the displacing may be accomplished by reciprocally mounting shaft 73 wherein a thrust bearing 96 is secured on an end 98 of the first shaft portion 73 and has an end of a threaded screw 100 engaged therewith.
  • the screw 100 is threadably mounted on a stationary bracket 102.
  • a pair of thrust bearings 104 are mounted on shaft portion 75 and a biasing means 107 shown in the form of a compression coil spring 108, is mounted on the shaft portion 75 and between the thrust bearings 104.
  • selective rotation of screw 100 will, in turn, displace shaft portion 73 axially, to vary the radial dimension 89, against the opposed biasing force of spring 108.
  • the screw 100 may be rounded at one end 101 thereof and the thrust bearing 96 correspondingly formed to closely receive screw end 101 to prevent thrust bearing 96 from falling off.
  • a third pump embodiment 110 is illustrated by Figure 4 and includes a first member, such as a shaft 112 having a cylindrical outer surface 114 defined thereon.
  • the shaft 112 is rotated about a longitudinal axis 116 thereof by conventional input means (not shown).
  • a second member is disposedradially outwardly of the first member and may be a stationary casing 122 having a cylindrical inner surface 124 which is disposed radially outwardly of surface 114 to normally define an annular chamber 128 therebetween.
  • Chamber 128. has a radial dimension which can be varied, as described hereinafter.
  • the pump 110 further includes inlet means 30b for communicating fluid into the chamber 128, and outlet means (not shown) for communicating fluid from the chamber 128 to the exterior of pump 110, the inlet means 30b and the outlet means, which may be constructed similarly to outlet means 32a in Figure 3, functioning substantially in the same manner as those of the previously described pump embodiments.
  • the pump embodiment 110 further includes an adjustment means 134, which functions in a manner similar to the adjustment means 34 of pump 10.
  • the adjustment means 134 for selectively adjusting the size of the radial dimension 129 of the chamber 118 adjacent to outlet means 32a is by moving the casing 122 radially and into eccentric relationship to the shaft axis 116.
  • the pump embodiment 110 permits sensitive adjustments in the flow of fluid therefrom between minimum and maximum levels.
  • the pump embodiment 110 may be mounted on stationary brackets 140,142 secured on a base 144.
  • the adjustment means 134 may comprise a screw actuator, or nut, 146 interposed between the base 144 and the casing 122.
  • the actuator 146 is threadably mounted between a stud 148 engaged with the casing 122 and a stud 149 engaged with the base 144.
  • the actuator 146 has differential screw threads
  • FIG. 5 illustrates the addition of an optional directing means 150 of the pump embodiment 70 for directing fluid from the chamber 88 into the outlet means 32a.
  • the directing means 150 may also be used in the pump embodiments 10 and 110.
  • the directing means 150 may include a scraper member 156 radially protruding into chamber 88 to contact the shaft surface 74 at a one end 157 of scraper member 156, while being carried by the casing 82 at its other end 158.
  • a biasing member 160 Interposed behind end 158 of scraper member 156 and within casing 82 is a biasing member 160, such as a compression coil spring for continuously maintaining end 157 in contact with shaft surface 74.
  • the scraper member 156 is located adjacent to the outlet means 32a and on the downstream side thereof. Scraper member 156 preferably extends longitudinally substantially along the full length of casing surface 84.
  • Embodiments of the present invention find particular application in combination with engines to pump lubricating oil to working components of such engines.
  • embodiments of the present invention may also be utilized in combination with machine tools or other types of conventional apparatus requiring lubrication.
  • the pumps 10, 70 and 110 after having been assembled during manufacture, may be calibrated for the desired lubricant flow therefrom by selectively adjusting the respective screw members 60, 100, 146 of the respective adjustment means 34,92,134. Such calibration may be performed upon a calibration stand using a standardized fluid.
  • circumferential fluid flow in sleeve-type bearings is directly proportional to the tangential velocity of a rotating member and to a minimum fluid film thickness between the rotating member and its sleeve. Accordingly, once a pump designed in accordance with the present invention has been calibrated to a particular position for the casing and shaft surfaces, then the flow of lubricant will be dependent upon the clearance therebetween, and substantially determined thereby when the shaft is rotating at a constant speed.
  • the adjustment means 34,92 or 134 may be simply readjusted to bring the surfaces into another position.
  • a shaft has a diameter of about 0.5" (1.27 cm), that the shaft is turning at about 500 rpm, that the shaft and casing surfaces have been adjusted to have a radial dimension of about 0.0001" (0.0002 cm) therebetween, and that the surfaces are about 1" (2.54 cm) in length.
  • the fluid is delivered to the inlet at about 50 lbs/in 2 (345 Pa).
  • the pump embodiments 10,70 or 110 will deliver about 0.02 cubic inches of fluid per minute (0.32 ml/min).
  • the directing means 150 is included in embodiments of the present invention, most of the fluid circulating circumferentially within the pump is directed into the outlet means and thence from the pump. Thus, where the directing means is included in the above example, the fluid delivery will be about
  • the directing means tends to affect the radial dimension of the chamber, and hence should be in place during the calibration adjustments.
  • substantially all the fluid circumferentially flowing is directed into the outlet means, and hence the casing surfaces need not entirely surround (in cross-section) the shaft surfaces.
  • the pump of this invention provides that calibrated ranges of fluid flows may be metered therefrom, the calibration being substantially precise even with fairly liberal manufacturing tolerances for components thereof, and provides for convenient subsequent adjustments in flow therefrom.
  • Other aspects, objects, and advantages of this invention can be obtained from a study of the drawings, the disclosure and the appended claims.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

Un facteur cle dans la lubrification satisfaisante de composants de systemes mecaniques est d'assurer une alimentation uniforme en lubrifiant, independamment de la quantite desiree. Une pompe (10, 70, 110) est prevu pour mesurer de petites quantites d'huile de lubrification de composant de moteur, de machine outil, ou autre. La pompe comprend un axe rotatif (12, 72, 112) et un corps (22, 82, 122) delimitant entre eux une chambre (28, 88, 128). Le debit d'huile de lubrification provenant de la pompe est ajuste de maniere selective en reponse a la variation selective d'une dimension radiale (29, 89, 129) de la chambre.
PCT/US1979/000494 1979-07-12 1979-07-12 Pompe de mesure d'un lubrifiant WO1981000276A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/US1979/000494 WO1981000276A1 (fr) 1979-07-12 1979-07-12 Pompe de mesure d'un lubrifiant

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
PCT/US1979/000494 WO1981000276A1 (fr) 1979-07-12 1979-07-12 Pompe de mesure d'un lubrifiant
WOUS79/00494 1979-07-12

Publications (1)

Publication Number Publication Date
WO1981000276A1 true WO1981000276A1 (fr) 1981-02-05

Family

ID=22147631

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1979/000494 WO1981000276A1 (fr) 1979-07-12 1979-07-12 Pompe de mesure d'un lubrifiant

Country Status (1)

Country Link
WO (1) WO1981000276A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2751849A (en) * 1954-11-01 1956-06-26 Farmingdale Corp Pump
US2777394A (en) * 1954-10-27 1957-01-15 Farmingdale Corp Pump for viscous fluids
US3669561A (en) * 1970-10-09 1972-06-13 Honeywell Inc Hydrodynamic pump
US3794449A (en) * 1971-08-31 1974-02-26 Philips Corp Viscosity pump

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2777394A (en) * 1954-10-27 1957-01-15 Farmingdale Corp Pump for viscous fluids
US2751849A (en) * 1954-11-01 1956-06-26 Farmingdale Corp Pump
US3669561A (en) * 1970-10-09 1972-06-13 Honeywell Inc Hydrodynamic pump
US3794449A (en) * 1971-08-31 1974-02-26 Philips Corp Viscosity pump

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