EP0802327A1 - Zahnradpumpe - Google Patents

Zahnradpumpe Download PDF

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Publication number
EP0802327A1
EP0802327A1 EP97440038A EP97440038A EP0802327A1 EP 0802327 A1 EP0802327 A1 EP 0802327A1 EP 97440038 A EP97440038 A EP 97440038A EP 97440038 A EP97440038 A EP 97440038A EP 0802327 A1 EP0802327 A1 EP 0802327A1
Authority
EP
European Patent Office
Prior art keywords
pressure chamber
piston
gear pump
diameter
head
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.)
Granted
Application number
EP97440038A
Other languages
English (en)
French (fr)
Other versions
EP0802327B1 (de
Inventor
Clément Kiefer
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.)
Pierburg Pump Technology France SARL
Original Assignee
Europeenne De Mecanique Sa Ste
Europeenne De Mecanique Sa Ste
SOC EUROP DE MECANIQUE SA
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 Europeenne De Mecanique Sa Ste, Europeenne De Mecanique Sa Ste, SOC EUROP DE MECANIQUE SA filed Critical Europeenne De Mecanique Sa Ste
Publication of EP0802327A1 publication Critical patent/EP0802327A1/de
Application granted granted Critical
Publication of EP0802327B1 publication Critical patent/EP0802327B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F04C14/265—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels being obtained by displacing a lateral sealing face

Definitions

  • the present invention relates to a gear pump, preferably an external gear pump, comprising a pump body in which rest at least two opposite, meshing toothed wheels, one of which is connected to a drive, a hollow cylinder, fixed to one of the side walls of the gear pump and disposed in front of an opening in this side wall, a hollow cylinder in which rests a piston movable in the axial direction of the toothed wheels, the piston head of which, at rest, comes against the front face of the cogwheels under the effect of an elastic element.
  • the face of the gearwheels will be called the face of the gear, perpendicular to the axis of the gear, facing the aforementioned piston.
  • gear pumps are suitable for many hydraulic drives. In particular, they are often used as lubricating oil pumps in internal combustion engines.
  • the oil pressure produced by the gear pump cools the piston heads, lubricates and cools the piston slide track, main bearings and connecting rod bearings as well as the rocker arms and feeds the camshaft bearings.
  • the entrainment and the delivery of the liquid results from the fact that it penetrates into the free spaces between the toothed wheels meshing with each other, moves, in the direction of rotation, outside, along the wall of the pump body. , to penetrate the pressure zone and is expelled from the beams towards the pressure chamber by the mutual meshing of the teeth.
  • Gear pumps operating on the volumetric principle have the property that the delivery and pressure of the liquid increases proportionally as the speed of rotation increases. Consequently, in the absence of regulation, the permissible permanent operating pressure - for economical use and a sufficient service life - is exceeded.
  • this regulation technique is disadvantageously accompanied by a significant power dissipation from the gear pump, which can reach, for example, around 1300 W for a delivery of 10 liters / minute; when the flow rate increases, the power dissipation decreases only relatively little.
  • An object of the present invention is to configure the gear pump described at the outset so as to achieve a substantial reduction in power dissipation and to prevent foaming.
  • Another object of the invention is to reduce the friction forces between the meshing wheels and the overpressure reducing device.
  • the elastic element may consist of a helical spring inserted between the rear face of the piston head and the internal face of the cover of the hollow cylinder.
  • the face of the piston head which faces the toothed wheel has a hollowed-out central part, the diameter of which is slightly less than the diameter of the bottom of the gaiters while the total diameter of the piston head is slightly greater than the diameter of the head circle of the gear wheel.
  • the piston is lightened and its inertia decreases.
  • the force of the support spring can be considerably reduced, which not only reduces the forces of friction between the piston head and the front face of the toothed wheel but still allows a much quieter operation of the pump.
  • the rear face of the piston on which the effect of the spring is exerted and which constitutes a back-pressure chamber is simply connected to the pressure chamber of the pump by a conduit d 'power can, in particular, pass through the piston head or pass through the wall of the pump body.
  • the back-pressure chamber is also provided with a second return conduit towards the suction chamber.
  • This return pipe to the suction chamber is fitted with a calibrated valve.
  • the back-pressure chamber is provided with a conduit leading towards the outside of the pump, in particular a conduit allowing the return to a reservoir of the fluid transported by the pump.
  • a diameter of the return duct is provided which is greater than the diameter of the supply duct of the back-pressure chamber.
  • the liquid is discharged in such a way that the liquid penetrates, suction side, in the suction chamber (2) of the pump, in the free spaces of the gear wheels (4, 5) in engagement, arranged in the pump body (3); it moves, from the outside, along the wall of the pump body, in the direction of rotation of the wheels, in the direction of the discharge side of the pump and is expelled from the teeth by the mutual meshing of the teeth. Since each entry, before complete emptying, is closed by the corresponding tooth of the opposite toothed wheel, this results here in what is called a crushing liquid which is derived in the pressure chamber (6) through bores not shown in order to avoid loss of energy and a bumpy running of the toothed wheels.
  • the toothed wheels one of which, for example the wheel (4) is connected to a drive element (20), not shown in FIGS. 1 and 2, turns with a very small clearance in the radial and axial direction between them and the pump body.
  • a through hole (8) arranged coaxially with the toothed wheel, a hole the surface of which is similar to the surface of the head circle of the teeth of the gear wheel.
  • a hollow cylinder (9) integral with the wall (7) of the pump body.
  • the cylinder (9) and the wall (7) may consist of two separate integral parts.
  • the cylinder body and the wall (7) came from one piece and the bottom of the displacement is closed by a cover.
  • the inside diameter of the hollow cylinder coincides with the diameter of the through hole.
  • a piston (10) which, in the embodiment illustrated in Figures 1 and 2, has the shape of a hollow cylinder whose piston head (11) flat, at rest, comes against the front face of the toothed wheel. Since the surface of the piston head is similar to the surface of the head circle of the teeth of the toothed wheel, the front face of the latter is completely covered by the piston head.
  • a cylindrical helical pressure spring (12) whose spring force presses, in the axial direction and against the front face of the toothed wheel, the piston head which completely covers this front face of the toothed wheel.
  • the piston When, in operation, a predetermined discharge is exceeded, the piston is, despite the force of the helical pressure spring, pushed inside the hollow cylinder, so that a slot opens between the piston head and the face front of the toothed wheel, that the excess discharge can flow, by means of this bypass, directly to the suction side, to the suction chamber of the gear pump, and that there is a drop in pressure.
  • the power dissipation decreases significantly and a smaller amount of liquid must be drawn into the circuit. Only the quantity of liquid which is actually useful is sucked up.
  • the use of the gear pump produced with a movable piston according to the invention reduces the power dissipation to 960 W. It also prevents the liquid from foaming.
  • the diameter of the piston (11) is slightly greater than the bore of the pump body (3) in which rests the gear (4) facing it.
  • the cylinder abuts against the edge of this bore. If the gear is not flush, but in very slight withdrawal, this results in very little play which advantageously reduces the frictional forces.
  • the piston head has a hollowed-out central zone E, the diameter of which is slightly less than the diameter of the wheel, at the bottom of the crossbeams. There is therefore no contact or friction between the central part of the piston and the central part of the gears or pinions.
  • the spring should provide a force of around 30 daN.
  • the spring only has to provide a force of the order of 5 daN. Spring size and therefore its price is significantly reduced and its assembly is also greatly facilitated.
  • the back pressure chamber (14) is connected to the suction chamber by a suction return duct (19) whose diameter is greater than the diameter of the duct d suction (13).
  • the return duct (19) is closed by a ball valve, comprising a sealing ball (15), on which pushes a valve spring (16), a stop (18) forming a plug.
  • This embodiment allows oil-tight circulation from the outside between the pressure chamber (6), the back-pressure chamber (14) and the suction chamber (2): it is a sealed internal circuit. This embodiment is particularly suitable for a pump placed outside a crankcase.
  • the back pressure chamber (14) is connected to the outside by a return duct (17).
  • This conduit (17) is itself closable by means of a calibrated valve comprising a ball (15), a valve spring (16) and a stop (18).
  • This embodiment having an open circuit between pressure chamber (6) - back pressure chamber (14) and outlet of the conduit (17), is particularly suitable for a pump placed in the fluid reservoir, for example at the inside of a crankcase.
  • the use of the additional calibrated valve limits the back pressure and thus facilitates the movement and the release of the piston, which allows more frank regulation.
  • the valve spring is chosen so that the valve opens at the desired control pressure.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
EP97440038A 1996-04-17 1997-04-16 Zahnradpumpe Expired - Lifetime EP0802327B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9605052 1996-04-17
FR9605052A FR2747743A1 (fr) 1996-04-17 1996-04-17 Pompe a engrenages

Publications (2)

Publication Number Publication Date
EP0802327A1 true EP0802327A1 (de) 1997-10-22
EP0802327B1 EP0802327B1 (de) 2000-06-28

Family

ID=9491465

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97440038A Expired - Lifetime EP0802327B1 (de) 1996-04-17 1997-04-16 Zahnradpumpe

Country Status (5)

Country Link
EP (1) EP0802327B1 (de)
AT (1) ATE194212T1 (de)
DE (1) DE69702368T2 (de)
ES (1) ES2147429T3 (de)
FR (1) FR2747743A1 (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001092673A2 (en) * 2000-06-01 2001-12-06 Pancanadian Petroleum Limited Fluid displacement apparatus and method
US6454010B1 (en) 2000-06-01 2002-09-24 Pan Canadian Petroleum Limited Well production apparatus and method
AT503856B1 (de) * 2006-06-30 2008-01-15 Tcg Unitech Systemtechnik Gmbh Zahnradpumpe mit veränderbarem fördervolumen
EP2203624A2 (de) * 2007-10-01 2010-07-07 Raymond C. Davis Erdölpumpe

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CZ2017330A3 (cs) * 2017-06-08 2018-11-21 Emil Brabec Pístové čerpadlo pro kapaliny, zvláště pro viskóznější a pastovitá média
RU210819U1 (ru) * 2022-01-07 2022-05-05 Акционерное общество "Ремдизель" Масляный насос двигателя внутреннего сгорания

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2437791A (en) * 1943-06-26 1948-03-16 Borg Warner Pump with unloading bushing
GB1188977A (en) * 1966-06-24 1970-04-22 Werner Schindler Rotary Positive Diplacement Pump.

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2437791A (en) * 1943-06-26 1948-03-16 Borg Warner Pump with unloading bushing
GB1188977A (en) * 1966-06-24 1970-04-22 Werner Schindler Rotary Positive Diplacement Pump.

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001092673A2 (en) * 2000-06-01 2001-12-06 Pancanadian Petroleum Limited Fluid displacement apparatus and method
WO2001092673A3 (en) * 2000-06-01 2002-04-04 Pancanadian Petroleum Fluid displacement apparatus and method
US6454010B1 (en) 2000-06-01 2002-09-24 Pan Canadian Petroleum Limited Well production apparatus and method
AT503856B1 (de) * 2006-06-30 2008-01-15 Tcg Unitech Systemtechnik Gmbh Zahnradpumpe mit veränderbarem fördervolumen
EP2203624A2 (de) * 2007-10-01 2010-07-07 Raymond C. Davis Erdölpumpe
EP2203624A4 (de) * 2007-10-01 2011-08-17 Raymond C Davis Erdölpumpe

Also Published As

Publication number Publication date
FR2747743A1 (fr) 1997-10-24
EP0802327B1 (de) 2000-06-28
ES2147429T3 (es) 2000-09-01
ATE194212T1 (de) 2000-07-15
DE69702368T2 (de) 2001-03-29
DE69702368D1 (de) 2000-08-03

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