EP0802327B1 - Zahnradpumpe - Google Patents

Zahnradpumpe Download PDF

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Publication number
EP0802327B1
EP0802327B1 EP97440038A EP97440038A EP0802327B1 EP 0802327 B1 EP0802327 B1 EP 0802327B1 EP 97440038 A EP97440038 A EP 97440038A EP 97440038 A EP97440038 A EP 97440038A EP 0802327 B1 EP0802327 B1 EP 0802327B1
Authority
EP
European Patent Office
Prior art keywords
piston
gear
chamber
gear pump
piston 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.)
Expired - Lifetime
Application number
EP97440038A
Other languages
English (en)
French (fr)
Other versions
EP0802327A1 (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
Pierburg SARL
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 Pierburg SARL filed Critical Pierburg SARL
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 pump gears, preferably a gear pump exterior, comprising a pump body in which rest at least two opposite toothed wheels, meshing, one of which is connected to a drive, a hollow cylinder, fixed to one of the side walls of the pump with gears and arranged in front of an opening in this wall lateral, hollow cylinder in which a piston rests movable in the axial direction of the gear wheels, the head of which piston, at rest, comes against the front face of the wheels toothed under the effect of an elastic element.
  • a pump gears preferably a gear pump exterior, comprising a pump body in which rest at least two opposite toothed wheels, meshing, one of which is connected to a drive, a hollow cylinder, fixed to one of the side walls of the pump with gears and arranged in front of an opening in this wall lateral, hollow cylinder in which a piston rests movable in the axial direction of the gear wheels, the head of which piston, at rest, comes against the front face of the wheels
  • the pumps gears are suitable for many drives hydraulic.
  • they are often used as lubricating oil pumps in engines with internal combustion.
  • the oil pressure produced by the gear pump cools piston heads, lubricates and cools the piston sliding track, the bearings main and connecting rod bearings as well as rocker arms and supplies the camshaft bearings.
  • the entrainment and the delivery of the liquid results from the fact let it penetrate into the gaps freed from the wheels toothed meshing with each other, moves, in the direction of rotation, outside, along the body wall of pump, to enter the pressure zone and is expelled from the entredents in the direction of the pressure by mutual meshing of teeth.
  • Gear pumps operating according to the volumetric principle have the property according to which the liquid discharge and pressure increase proportionally when the speed of rotation increases. Therefore, in the absence of regulation, the permissible permanent operating pressure - for a economical use and sufficient service life - is exceeded.
  • the permissible permanent operating pressure - for a economical use and sufficient service life - is exceeded.
  • An object of the present invention is to configure the gear pump described at the beginning so to obtain a significant reduction in the dissipation of power 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 can be consisting of a helical spring inserted between the face back of the piston head and the inner side of the cover of the hollow cylinder.
  • the face of the piston head which faces the gear wheel has a hollowed-out central part, the diameter of which is slightly less than the diameter of the bottom of the brackets while the total diameter of the piston head is slightly greater than the diameter of the gear wheel head circle.
  • the piston is lightened and its inertia decreases.
  • the force of the spring support can be considerably reduced, which does not only decreases the friction forces between the head piston and front face of toothed wheel but still allows a much quieter operation of the pump.
  • the rear face of the piston on which is exerted the effect of the spring and which constitutes a back-pressure chamber is simply connected to the pressure chamber of the pump by a supply duct which can, in particular, pass through the piston head or pass through the pump body wall.
  • the back pressure chamber is also with a second return pipe to the room suction.
  • This conduit back to the bedroom suction valve is fitted with a calibrated valve.
  • the back pressure chamber is fitted with a pipe leading to the outside of the pump, in particular a conduit allowing the return to a tank of the fluid transported by the pump.
  • the discharge of the liquid takes place 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) meshing, arranged in the pump body (3); he moves, from the outside, along the body wall pump, in the direction of rotation of the wheels, in the direction on the discharge side of the pump and is expelled from between the mutual meshing of the teeth.
  • a crushing liquid which is diverted into the pressure chamber (6) through bores not shown to avoid energy losses and a knocked gears step.
  • Cogwheels one of which, for example the wheel (4) is connected to a drive element (20), not shown in the figures 1 and 2, rotate with a very small backlash in the direction radial and axial between them and the pump body.
  • a hole passage (8) arranged coaxially with respect to the wheel toothed, hole whose surface is similar to the surface of the head circle of the teeth of the gear wheel.
  • a hollow cylinder is arranged coaxially (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) are come from one piece and the bottom of the cylinder is closed by a lid.
  • the inside diameter of the hollow cylinder coincides with the diameter of the through hole.
  • a piston (10) which, in the embodiment illustrated in FIGS. 1 and 2, presents the shape of a hollow cylinder whose piston head (11) flat, at rest, comes against the front face of the wheel toothed. Since the surface of the piston head is similar to the surface of the head circle of the teeth of the gear wheel, the front side of it is fully covered by the piston head.
  • a pressure spring is inserted helical cylindrical (12) whose spring force press, 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, it exceeds one determined delivery, the piston is, despite the force of the helical pressure spring, pushed inside the hollow cylinder, so that a slit opens between the head piston and the front face of the toothed wheel, that the excess backflow can flow, through this bypass, directly to the suction side, to the suction chamber of the gear pump, and that it produces a drop in pressure. Therefore, dissipation of power decreases significantly and an amount lower liquid must be entrained in the circuit. Only the quantity of liquid which is actually useful.
  • 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 very slight shrinkage, this results in very little play which advantageously reduces the friction forces.
  • the piston head has an area hollowed-out central unit 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 part center of the piston and the central part of the gears or gables.
  • the spring should provide an effort of around 30 daN.
  • the spring thanks to the back pressure established in chamber 14), the spring only has to provide an effort of the order of 5 daN. Spring size and therefore its price is significantly reduced and its mounting is also greatly facilitated.
  • the back pressure chamber (14) is connected to the chamber suction by a return suction duct (19) whose diameter is greater than the diameter of the duct 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 execution mode allows circulation, tight vis-à-vis the outside, oil between the pressure chamber (6), the back pressure chamber (14) and the suction chamber (2): these are a sealed internal circuit.
  • This execution mode is suitable particularly to a pump placed outside a Crankcase.
  • the back pressure chamber (14) is connected to the exterior 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), particularly suitable for a pump placed in the fluid reservoir, for example at inside a crankcase.
  • the use of the additional calibrated valve limits back pressure and thus facilitates movement and the release of the piston, which allows regulation more frank.
  • the valve spring is chosen in such a way so that the valve opens at the pressure of desired regulation.

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)

Claims (8)

  1. Getriebepumpe, umfassend einen Pumpenkörper (3), in dem zumindest zwei entgegenliegend gezahnte Räder (4, 5) angeordnet sind, die sich in Eingriff befinden, von denen eines mit einem Antrieb (20) verbunden ist, gekennzeichnet durch einen Hohlzylinder (9), der an einer der seitlichen Wände (7) der Getriebepumpe (1) fixiert ist und vor einer Öffnung (8) der seitlichen Wand (7) angeordnet ist, wobei in dem Hohlzylinder (9) ein Kolben (10) ruht, der sich in axialer Richtung der Zahnräder (4, 5) bewegen kann, wobei der Kolbenkopf (11) in Ruhestellung gegen die Vorderseite der Zahnräder (4, 5) anliegt, unter dem Effekt eines elastischen Elementes; und dadurch, daß der Kopf des Kolbens (11) die Vorderseite eines der Zahnräder (4, 5) vollständig abdeckt, daß die Mittelpunkte des Kolbenkopfes (11) und des Kopfkreises der Verzahnung des Zahnrades auf derselben Achse angeordnet sind, und dadurch, daß die Rückseite des Kolbens unter einem hydraulischen Druck steht, welcher in der Druckkammer (6) herrscht, mittels einer Versorgungsleitung (13) zwischen der Druckkammer (6) und der Rückseite, um eine Gegendruckkammer (14) zu bilden.
  2. Getriebepumpe nach Anspruch 1, dadurch gekennzeichnet, daß das elastische Element eine Spiralfeder (12) ist, die zwischen die Rückseite des Kolbenkopfes (11) und die Innenseite der Abdeckung des Hohlzylinders (9) eingefügt ist.
  3. Getriebepumpe nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet, daß der Kolbenkopf Seite an Seite vor dem Zahnrad einen mittleren ausgesparten Bereich E aufweist. dessen Durchmesser im wesentlichen gleich oder kleiner ist als der Durchmesser des Grundkreises des Zahnrades, und dadurch, daß der Außendurchmesser des Kolbenkopfes im wesentlichen gleich oder größer als der Kopfkreis des Zahnrades ist.
  4. Getriebepumpe nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die Gegendruckkammer (14) mit der Druckkammer (6) ausschließlich durch eine Versorgungsleitung verbunden ist, die durch den Kolbenkopf geht.
  5. Getriebepumpe nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die Gegendruckkammer (14) mit der Druckkammer (6) ausschließlich durch eine Versorgungsleitung verbunden ist, die durch eine Wand des Pumpenkörpers hindurchgeht.
  6. Getriebepumpe nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die Gegendruckkammer (14) mit einer Rückkehrleitung (19) versehen ist, die die Gegendruckkammer und die Belüftungskammer (2) verbindet, und dadurch, daß die Rückkehrleitung (19) mit einem geeichten Sperrventil (15, 16, 18) versehen ist.
  7. Getriebepumpe nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die Gegendruckkammer (14) mit einer Leitung (17) versehen ist, die die Gegendruckkammer (14) mit der Außenseite der Pumpe verbindet, und dadurch, daß diese Leitung nach außen führt und mit einem geeichten Sperrventil (15, 16, 18) versehen ist.
  8. Getriebepumpe nach einem der Ansprüche 6 oder 7, dadurch gekennzeichnet, daß die Rückkehrleitung (17, 19) einen Durchmesser aufweist, der größer ist als der Durchmesser der Versorgungsleitung (13).
EP97440038A 1996-04-17 1997-04-16 Zahnradpumpe Expired - Lifetime EP0802327B1 (de)

Applications Claiming Priority (2)

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

Publications (2)

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

Family

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Family Applications (1)

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

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

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2001263680A1 (en) * 2000-06-01 2001-12-11 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
US8225873B2 (en) * 2003-02-21 2012-07-24 Davis Raymond C Oil well pump apparatus
AT503856B1 (de) * 2006-06-30 2008-01-15 Tcg Unitech Systemtechnik Gmbh Zahnradpumpe mit veränderbarem fördervolumen
CZ307543B6 (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

Family Cites Families (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
CH476212A (de) * 1966-06-24 1969-07-31 Schindler Werner Verdrängungspumpe

Also Published As

Publication number Publication date
ES2147429T3 (es) 2000-09-01
DE69702368D1 (de) 2000-08-03
ATE194212T1 (de) 2000-07-15
DE69702368T2 (de) 2001-03-29
EP0802327A1 (de) 1997-10-22
FR2747743A1 (fr) 1997-10-24

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