US20090191075A1 - Positive displacement piston pump, for lubication - Google Patents

Positive displacement piston pump, for lubication Download PDF

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Publication number
US20090191075A1
US20090191075A1 US12/302,526 US30252607A US2009191075A1 US 20090191075 A1 US20090191075 A1 US 20090191075A1 US 30252607 A US30252607 A US 30252607A US 2009191075 A1 US2009191075 A1 US 2009191075A1
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US
United States
Prior art keywords
lubricant
positive displacement
piston pump
displacement piston
pump according
Prior art date
Legal status (The legal status 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 status listed.)
Abandoned
Application number
US12/302,526
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English (en)
Inventor
Andrea Di Foggia
Mariano Migliaccio
Ottavio Pennacchia
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
LA ME Srl
Original Assignee
LA ME Srl
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 LA ME Srl filed Critical LA ME Srl
Assigned to LA.ME. S.R.L. reassignment LA.ME. S.R.L. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DI FOGGIA, ANDREA, MIGLIACCIO, MARIANO, PENNACCHIA, OTTAVIO
Publication of US20090191075A1 publication Critical patent/US20090191075A1/en
Abandoned legal-status Critical Current

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Classifications

    • 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
    • F04B23/00—Pumping installations or systems
    • F04B23/02—Pumping installations or systems having reservoirs
    • F04B23/021—Pumping installations or systems having reservoirs the pump being immersed in the reservoir
    • F04B23/023—Pumping installations or systems having reservoirs the pump being immersed in the reservoir only the pump-part being immersed, the driving-part being outside the reservoir

Definitions

  • the device of the present invention is applicable, although not exclusively, to the field relating to the lubrication of mechanical components of reciprocating compressors and of small-sized internal combustion engines.
  • lubrication systems are required that are capable of handling even very modest lubricant flow rates and to supply them to the required points; moreover, said systems should have a simple mechanics, be realizable at low cost, and be able to utilise the motion provided by the machine on which they are mounted, without resorting to unduly complicated mechanisms (like additional small shafts, power takeoffs, etc.).
  • lubrication in small-sized piston engines and in reciprocating compressors is performed substantially either by splash lubrication, in case this method is considered satisfactory, or by employing gear pumps, in case the needs of a good lubrication are more pressing.
  • mechanically actuated usually by a cam
  • small-sized, positive displacement pumps have also been developed, as well as electromagnetically controlled valves, specifically for small internal combustion motors of motorcycles or scooters.
  • Splash lubrication which relies on the splashing and agitation caused by the very components to be lubricated (which are wetted by the oil generally contained inside an oil sump), has the advantage to be extremely economical and simple, provided it is able to insure a sufficient lubrication. Nevertheless, it has considerable drawbacks, like the need to maintain a constant lubricant level inside the oil sump in order to avoid seizure, the fact that the lubricant is not accurately supplied only to the points were it is really needed, the fact that it is impossible to supply the lubricant under pressure, the impossibility of using this kind of system in two-stroke engines with dry sump oil pumps, since in these applications the sump oil pump must work under dry conditions.
  • Lubrication under pressure has become the mostly used system because of its undoubted advantages linked to its utilisation, these advantages being, among others, the increase of the performance of the kinematical couples lubricated under pressure as compared with that obtainable without the contribution of the feed pressure.
  • the lubrication relying on gear pumps has the advantage of putting under pressure the lubrication circuit and of allowing to accurately reach the various points or areas to be lubricated, with the required oil flow rate and the correct (prescribed) pressure value.
  • the lubricant also has the not negligible task of cooling the surfaces which are in mutual contact.
  • cam-actuated positive displacement pumps has quickly become widespread, besides that of electromagnetic pumps, in the field of small-sized internal combustion engines and in the technical field of compressors, due to the possibility of feeding the lubricant under pressure, by controlling the flow rates, and therefore, taking advantage of the possibility of cooling down the various lubricated kinematical couples.
  • gear pumps lies in the increased costs involved in the production of high-quality mechanical components, like gearwheels for instance, and in the need to provide an adequate power takeoff (drive), so that the machine to be lubricated is more difficult to manufacture.
  • FIG. 1 shows the first embodiment of the needle-shaped positive displacement pump according to the present invention
  • FIGS. 2 a and 2 b are two orthogonal views of the second embodiment of the needle-shaped positive displacement pump according to the present invention.
  • FIGS. 3 a and 3 b are two orthogonal views of the third embodiment of needle shaped positive displacement pump according to the present invention.
  • FIG. 1 shows a schematic cross-section of a possible embodiment of the present invention, formed by:
  • A-version shown in FIG. 1 , is as follows:
  • the crank 7 by rotating around its own axis, gives rise to a relative motion—by means of the link rod 5 —between the piston 2 (which is hinged at the eccentric hole of the crank) and the cylinder body 1 .
  • This motion is the classical reciprocating motion of a conventional crank mechanism, whose stroke equals twice the distance between the axis of the crank 7 and the axis X of the eccentric hole of the crank 7 .
  • the piston 2 Starting from the bottom dead centre (BDC), the piston 2 , while moving upwards, generates a negative pressure inside the cylinder 1 , which is due to the fact that there is no fluid communication to the outside environment, because the suction inlet 10 remains closed (obstructed) by the piston 2 itself, while the delivery is controlled by the check valve 3 .
  • the piston 2 opens the suction inlet (suction opening) 10 obtained in the cylinder 1 , lubricant is sucked through the suction inlet 4 immersed in the lubricant (this system is self-starting or “self-priming” provided the negative pressure obtained inside the cylinder 1 insures the lifting of the liquid from the free, upper surface level, up to the suction opening 10 ).
  • the piston 2 Upon reaching the top dead centre (TDC), the piston 2 inverts its direction of motion; there will be a first phase of backflow of lubricant through the suction inlet, but then, after the piston 2 has closed this inlet 10 , the delivery phase starts, after the opening of the check valve 3 under the pressure force exerted by the compressed lubricant—on this check valve 3 —, which overcomes the closure force of the spring 11 of the valve 3 .
  • the lubricant first flows past the check valve 3 and then through a cavity obtained in the piston 2 , until it reaches a delivery region.
  • the plug 6 exerts a backing function (abutment) on the closure spring 11 of the check valve 3 .
  • the flow rate (delivery or capacity) of the pump of the invention can be modified by selecting an adequate cylinder bore or a suitable stroke (eccentricity of the hole on the crank).
  • FIG. 2 there is shown a further version (embodiment) of the small pump according to the present invention, that will be named “B-version”.
  • This system comprises:
  • FIG. 2 ( a and b )
  • the operation of the system illustrated in FIG. 2 ( a and b ) is basically the same as that of the device named “A-version”, with the only difference that the lubricant is now compressed inside a cylinder body 1 ′, which is substantially completely dipped (immersed) in the lubricant, while it is supplied to the delivery region through an additional element forming essentially a small hose 4 ′.
  • the operation is detailed in the following paragraph:
  • the crank 7 ′ while rotating around its axis, brings about a relative motion between the piston 2 ′ (hinged on the eccentric bore 9 ′ of the crank; X-axis) and the cylinder body 1 ′, the latter being hinged (at 15 ′) to the oil sump (not shown).
  • the resulting motion is a classical reciprocating motion of a conventional crank mechanism whose stroke is twice the distance existing between the axis of the crank 7 ′ and the axis X of the eccentric bore 9 ′ of the crank 7 ′.
  • the piston 2 ′ Starting from the BDC, the piston 2 ′, in the course of its upward motion, generates a negative pressure inside the cylinder 1 ′ which is due to the fact that there is no fluid communication to the outside because the suction inlet (analogous to 10 of FIG. 1 but not shown in FIGS. 2 a, 2 b ) is closed by the piston itself and the delivery is controlled by the check valve 3 ′.
  • the piston 2 ′ opens said suction inlet obtained in the cylinder 1 ′, lubricant is sucked through this suction inlet, which is immersed in the lubricant (this system, obviously, is always self-starting or “self priming”).
  • the piston 2 ′ Upon arriving at the TDC (top dead centre) the piston 2 ′ inverts its direction of motion; there will be a first phase of backflow through the suction inlet, and then the delivery phase will start after the piston 2 ′ has closed said inlet and the check valve 3 ′ has opened under the pressure force exerted—on this check valve 3 ′—by the compressed lubricant, this pressure force overcoming the closing force of the spring (not shown in FIG. 2 ) of the valve 3 ′.
  • This system may be equipped with a pressure-relief valve 8 ′.
  • the system includes:
  • C-version third embodiment
  • B-version second embodiment
  • the lubricant arrives at the delivery zone by passing through an additional, rigid duct 4 ′′.
  • the problem of connecting together the pumping zone with the delivery zone, which are in relative motion to each other, is solved by using a cylindrical rigid element 4 ′′ (rigid duct) that slides within the piston-bearing body 14 ′′.
  • the system may be equipped with a pressure-relief valve 8 ′′.
  • pivoting point (pivot pin) 15 ′′ is hinged to the oil sump (not shown).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Compressor (AREA)
US12/302,526 2006-05-31 2007-05-28 Positive displacement piston pump, for lubication Abandoned US20090191075A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
ITNA2006A000068 2006-05-31
IT000068A ITNA20060068A1 (it) 2006-05-31 2006-05-31 "pompa volumetrica alternativa a spillo per utilizzo in piccoli motori alternativi a combustione interna e in compressori volumetrici alternativi".
PCT/IT2007/000368 WO2007138633A1 (en) 2006-05-31 2007-05-28 Positive displacement piston pump, for lubrication

Publications (1)

Publication Number Publication Date
US20090191075A1 true US20090191075A1 (en) 2009-07-30

Family

ID=38596340

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/302,526 Abandoned US20090191075A1 (en) 2006-05-31 2007-05-28 Positive displacement piston pump, for lubication

Country Status (5)

Country Link
US (1) US20090191075A1 (it)
EP (1) EP2032855A1 (it)
CA (1) CA2652914A1 (it)
IT (1) ITNA20060068A1 (it)
WO (1) WO2007138633A1 (it)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1858036A (en) * 1929-08-01 1932-05-10 Better Built Pumps Inc Pump
US4047845A (en) * 1975-12-22 1977-09-13 Auto Research Corporation Cyclic pump
US5894830A (en) * 1997-12-15 1999-04-20 Caterpillar Inc. Engine having a high pressure hydraulic system and low pressure lubricating system
US6364639B1 (en) * 1998-09-11 2002-04-02 Lincoln Industrial Corporation Pump

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB576549A (en) 1944-10-03 1946-04-09 Uni Gun Lubricating Equipment Improvements in or relating to reciprocating pumps

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1858036A (en) * 1929-08-01 1932-05-10 Better Built Pumps Inc Pump
US4047845A (en) * 1975-12-22 1977-09-13 Auto Research Corporation Cyclic pump
US5894830A (en) * 1997-12-15 1999-04-20 Caterpillar Inc. Engine having a high pressure hydraulic system and low pressure lubricating system
US6364639B1 (en) * 1998-09-11 2002-04-02 Lincoln Industrial Corporation Pump

Also Published As

Publication number Publication date
CA2652914A1 (en) 2007-12-06
WO2007138633A1 (en) 2007-12-06
ITNA20060068A1 (it) 2007-12-01
EP2032855A1 (en) 2009-03-11

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Legal Events

Date Code Title Description
AS Assignment

Owner name: LA.ME. S.R.L., ITALY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:DI FOGGIA, ANDREA;MIGLIACCIO, MARIANO;PENNACCHIA, OTTAVIO;REEL/FRAME:021895/0979

Effective date: 20070430

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION