EP0791129B1 - Kolbenpumpe - Google Patents

Kolbenpumpe Download PDF

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Publication number
EP0791129B1
EP0791129B1 EP95939324A EP95939324A EP0791129B1 EP 0791129 B1 EP0791129 B1 EP 0791129B1 EP 95939324 A EP95939324 A EP 95939324A EP 95939324 A EP95939324 A EP 95939324A EP 0791129 B1 EP0791129 B1 EP 0791129B1
Authority
EP
European Patent Office
Prior art keywords
piston
injection
cylinder
pump
rod
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
EP95939324A
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English (en)
French (fr)
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EP0791129A1 (de
Inventor
Michel Chatelain
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Individual
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Individual
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Publication date
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams

Definitions

  • the present invention relates to a piston pump intended for supply two independent liquid circuits, in particular the circuit injection system and the lubrication system of a internal combustion.
  • a pump according to the closest prior art is known from US-A-2 980 023. It is more particularly a shaft pump crossing.
  • the injection and lubrication functions are provided in such a way conventional by two separate devices.
  • the fuel supply of each cylinder, or injection is provided by a so-called “injection” pump.
  • this pump has a plurality of pistons driven by a camshaft and returned by springs. The recall by springs notoriously limit the maximum speed of the pump, absorbs a lot of power, a lot of noise and heating.
  • injection and lubrication are provided by two separate bodies, which increases the total cost, and especially limits accessibility.
  • the invention overcomes these drawbacks.
  • the invention proposes to provide a pump ensuring jointly the oil pump functions for the lubrication of a engine and injection pump for the fuel supply of the same engine.
  • the oil pump body and the injection pump body are arranged perpendicular to each other on the outside of the same fuel-filled crankcase that serves as a housing for the eccentric shaft which controls them together and with the same eccentric.
  • the oil pump pistons are returned with compression springs while driving the pump pistons to injection is of the desmodromic type by means of a half-ring terminated at its ends by two internal, flat bearing elements, perpendicular to the movement of the piston and intended to be in contact with the eccentric.
  • To each internal bearing corresponds a rod: for a side, it is the pump piston and for the other, it is a guide which ensures a perfect guidance of the monobloc assembly constituted by the half-ring and the two rods.
  • the casing which receives all the pump bodies is in two parts: the first part constitutes the body of the housing and it serves as housing essentially to the eccentric and to the half-rings of the pistons of injection pump.
  • the injection pistons are mounted at an angle since the opening and the position of the pistons is given by the housing injection piston guides in the housing. In contrast, the position of injection cylinders on the crankcase is given by the piston and from the guide.
  • the hole in the housing around the injection piston has a very large clearance important to facilitate assembly and to allow the return of fuel not injected at the end of injection. This return takes place between the cylinder and the cylinder cover and through cross slots under the cylinder towards the hole in the housing around the piston.
  • the cylinder covers are secured to the cylinders by two screws which are also used to make them turn slightly on themselves when the pump is set on the test bench, to have an injection start angularly identical on all pistons. This adjustment is made with the slightly unlocked cylinder head to release the cylinders which are tight without seal and the cylinder covers which are sealed with two seals toric.
  • the cylinder head is a distribution part common to all cylinders injection. This arrangement ensures better rigidity and stability of all.
  • each piston corresponds to a chamber conical which receives the ball valve with its return spring. The ball has its seat directly in the cylinder.
  • two exits are machined to communicate with two injectors not shown which will in turn supply fuel to an engine cylinder or a explosion chamber. This arrangement is remarkable and the distribution is equal in volume on the two injectors with the same calibration of injection pressure.
  • the flow rate of the injection pump is variable while the engine. This variation in flow is obtained by an inclined ramp in piston head. This inclined ramp closes an orifice on the cylinder of the piston. By rotating the piston on itself, we change the position of this filling and as a result, more or less fuel.
  • the volume of fuel injected by a piston rise is between a closure, given by the inclined ramp which puts the pressurized volume, and an opening that leaks volume and which corresponds to the end of injection.
  • the end of injection is a point that remains always fixed.
  • the start of injection is a point that varies with the boom tilted; the more the closure is advanced in the rise of the piston, the more the the greater the flow, the more the closure is moved back in the rise of the piston the smaller the flow.
  • This variation in flow is given by the rotation of the piston on its axis to change the position of the inclined ramp by relative to the light on the pump cylinder.
  • This light controls by one end the start of injection and by the other end the end of injection.
  • the rotation control of the pump piston on its axis is obtained by a needle which is welded on the half-ring of each piston.
  • This needle is perfectly parallel at constant distance from the axis piston. This needle meshes with the rack which controls simultaneously all the pistons.
  • the piston stroke of the injection pump is fixed and the variation in flow is given by varying the stroke of the piston the injection start point, as is the case with many pumps injection.
  • the stroke of the oil pump pistons is the same as that of the pistons of the injection pump, but the flow is constant for a speed given.
  • Injection pump flow variation is done by a regulator electronic which prevents motor runaway.
  • the regulator which is placed on the side of the pump, in turn controls the rack which in turn controls the rotation of the pistons to make vary the flow.
  • a speed regulator is fixed electronic.
  • This regulator is placed behind the rack and they are connected between them by a finger which is part of the rack and which is housed in the regulator.
  • the rack finger is perpendicular to the back of the rack and it is located in the middle of the back of the rack.
  • This part of the stroke used for the injection is located on both sides other than the mid-stroke of the injection piston in the period when the speed linear is the largest.
  • the rest of the race causes leaks which return to the housing by the light and the notches made on the injection pump piston cylinder.
  • the free volume between the cylinder and the cylinder cover also participates in the fuel return circuit towards the casing and it is the role of the cylinder cover.
  • the injection device itself is of the drawer type.
  • the head of piston is cylindrical and hollow.
  • the central hole connects the room compression with a radial hole which opens with the stroke of the piston in a light on the cylinder.
  • On the piston head there is a ramp inclined which regulates the start of injection with regard to the same light on the cylinder.
  • the end of injection is a fixed and identical point on all the cylinders and pistons.
  • the start of injection is a moving point which varies with the position of the ramp inclined at the piston head.
  • the pump Once the pump has been adjusted to the bench, it can be mounted directly at the end of the crankshaft on the engine.
  • Figure 1 is a perspective view of the eccentric shaft fitted with injection pump pistons.
  • Figure 2 is a side view of an injection pump piston.
  • Figure 3 is a top view of the same piston.
  • Figure 4 is an enlarged detail of the head of the piston rod.
  • Figure 5 is a general section along a plane perpendicular to the eccentric shaft.
  • the invention as briefly shown in Figure 1, combines an oil pump and an injection pump used especially in a diesel engine, the number of pistons of this pump not being limited.
  • This set includes a through shaft (10) with eccentrics, a set of pistons (20) of oil pump of cylindrical shape with valves, and a set of pistons (30) of injection pump having in the general form of a half-ring (31), bearing at its ends a coaxial piston rod (32) and a guide (33).
  • This set is trapped in a housing (15) not shown in Figure 1.
  • the pistons (20) of oil pump slide inside cylinders (21) of oil pump oil fixed by a cylinder head (22) not shown in this figure.
  • the injection pump piston guides slide inside the same housing (15).
  • the injection pump piston rods (32) slide, in their end part, in a piston cylinder (35) surrounded by a cylinder cover (36) and surmounted by a cylinder head (37) not shown.
  • FIG. 5 the different parts are better identified in the state assembled.
  • the eccentric shaft (10) (11) comprising as shown (1) an eccentric (11).
  • On one side of this eccentric supports a piston (20) of oil pump of a form hollow cylindrical, shown here in the position closest to the axis (12) rotation.
  • This piston can slide inside a cylinder of piston (21), the sending being generated by the movement of the eccentric (11) and the return (in this maximum figure) is ensured by a spring (23).
  • the chamber of this piston communicates with a cylinder head (22) equipped with valves not shown ensuring the passage of the oil according to the arrows referenced.
  • the injection pump piston (30) moves in one direction perpendicular to the piston (20) of the oil pump.
  • This piston (30) is composed of three distinct portions, namely a piston rod (32), a half-ring (31) for driving and connecting, and a guide (33).
  • the rod piston (32) moves inside a piston cylinder (35) to compress a quantity of fuel and send it to the cylinder head (37) and up to the injector through a ball valve (38).
  • This piston rod (32) is pierced with an axial hole (40) connected in the axis of the half-ring (31) by a radial hole (42) which opens onto the diameter of the piston and which controls the end of injection when it opens on the light (45) of the cylinder.
  • the cylinder (35) is sealed with a cylinder cover (36). They are made integral by a screw (46). This screw (46) is used to change the cylinder position on the test bench and cylinder head (37) unlocked to obtain angularly the start of identical injection on all pistons to any one position of the rack.
  • the cylinder cover (36) used to contain leaks at the end of injection towards the housing according to arrow F.
  • the piston guide (33) is placed in the extension of the piston rod (32) on the other side of the eccentric shaft (10).
  • This guide (33) is slidably mounted inside the casing (15).
  • the guide (33) and the rod (32) are connected by a half-ring (31) whose internal shape cooperates with the eccentric (11).
  • the eccentric (11) rotates
  • the most eccentric part (13) of the shaft rotation axis (12) sometimes pushes the rod (32) to ensure the compression movement and sending the piston, sometimes pushes the guide (32) to ensure the recall of the piston.
  • This advantageous form makes it possible to dispense with the use a return spring.
  • the half-ring (31) carries on its outer face (50) a parallel axis (51) to the axis of movement of the piston and is moved away from the external face (50) of the half-ring (31) by two arms (52,53).
  • This axis (51) is intended to be translated by a hollow (55) on the rack (56) driven by a speed regulator (57).
  • a speed regulator 57
  • the action of this rack (56) allows to rotate the piston (30) about its axis of alternating movement.
  • the different pistons (30) placed along the eccentric shaft (11) are driven simultaneously by this speed regulator (57) and by the rack (56).
  • the eccentric shaft (11) rotates on itself, causing a longitudinal reciprocating movement of the piston (20) oil pump which thus ensures its function.
  • the injection pump piston (30) also describes reciprocating motion longitudinal which allows it to create fuel compression at level of the compression chamber which is under the ball valve placed on the cylinder (35).
  • the head (41) of the piston rod (32) is opposite the light (45) located on the piston cylinder (35). So the whole housing, the space between the cylinder cover (36) and the cylinder (35), the light (45) of the cylinder and the interior (40) of the piston rod, are in communication, so at low pressure.
  • the piston rod (32) begins to move the inside of the cylinder (35) and the head (41) of the rod leaves the light (45) of the piston cylinder (35). From that moment, the fuel trapped in the interior (40) of the piston rod and below the valve (38) is compressed.
  • the flow rate is adjusted by rotating the piston rod (32) to inside the cylinder (35). This rotation is obtained by the action of the rack (56) on the half-ring (31) which causes the pivoting.
  • an inclined ramp (47) is disposed at the head (41) of the rod (32) of piston. Depending on the angle of the piston (30) relative to the cylinder (35), and therefore in light (45), the instant of facing the ramp (47) and the light (45) will be variable. This allows the flow and advance to be adjusted injection.
  • this set allows to have two pumps with only one drive, which reduces mass and cost of such an achievement.
  • such a pump not using return springs for its injection function allows speeds significantly higher than all existing pumps currently, with less noise, less heating and less dissipated power.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (9)

  1. Eine aus zwei Kolbenpumpen bestehende Vorrichtung, die zwei voneinander unabhängige Flüssigkreisläufe bedienen soll, im Besonderen den Brennstoffeinspritzkreislauf und den Ölkreislauf für Verbrennungsmotoren, mit der Eigenheit, dass
    er nur ein einziges Vergasergehäuse (15) braucht, in dem die Pumpenkörper verankert sind;
    eine einzige Exzenterantriebswelle (10)(11) zur Steuerung der beiden Pumpen;
    ein Satz von Ölpumpenkolben (20), wobei jeder Pumpenkolben (20) während der Bewegung mit dem Exzenter zusammenspielt, indem er ihn von der Welle (10) entfernt, eine Feder (23) sorgt für den Rückzug;
    ein Satz von Einspritzpumpenkolben (30), deren Bewegung vertikal zur Bewegung der Pumpenkolben verläuft, wobei jeder Einspritzpumpenkolben (30) beim Schub und am Rückzug mit einem Exzenter (11) mitbeteiligt ist mittels eines halbkreisförmigen Ringstückes(31), dessen Öffnung in Richtung des entsprechenden Pumpenkolbens (20) orientiert ist, und die Extremitäten besagten Ringstückes (31) mit entsprechend einer Kolbenführung (33) und einer Kolbenstange (32) versehen sind, wobei die Führung und die Stange aneinandergereiht sind; jede Kolbenstange (32) gleitet in einem Zylinder (35), der mit einer Öffnung (45) versehen ist, welche den Beginn des Einspritzens mit einem Ende der Kolbenstange (32) in Form einer schrägen Rampe (47) und das Ende des Einspritzens mit einem auf der Kolbenstange (32) angebrachten Loch (42) anzeigt.
  2. Vorrichtung nach Forderung 1, mit der Eigenheit, dass diesselbe zusätzlich mit einem Einspritzzylinderkopfblock (37) ausgestattet ist, der alle Zylinder (35) durch Sperrung auf dem Vergaserblock (15) verbindet.
  3. Vorrichtung nach einer der Forderungen 1 und 2, mit der Eigenheit, dass jeder Zylinder (35) im Inneren einer Zylinderabdeckung (36) beweglich ist, deren Lage im Verhältnis zum Zylinder (35) durch eine Schraube (46) verstellbar ist.
  4. Vorrichtung nach einer der Forderungen von 1 bis 3, mit der Eigenheit, dass der Einspritzzylinderkopfblock (37) dem Zylinder (35) gegenüber mit einem Verdichtungsraum ausgestattet ist, der das Ventil (38) und seine Feder (39) enthält und der auf den Ausgangspunkt (28) zweier Einspritzdüsen mündet.
  5. Vorrichtung nach einer der Forderungen 1 bis 4, mit der Eigenheit, dass die Steuerung des Durchflusses der Einspritzpumpe durch die Drehung der Kolben (30) um ihre Achse erreicht wird ; diese Drehung wird von der Rückseite der halbkreisförmigen Ringe gesteuert, auf denen zwei mit einer Rille versehene Arme (52, 53) eine parallel zur Kolbenachse aufgeschweisste Nadel (51) erhalten, mit der Fähigkeit, mit einer parallel zur Exzenterwelle (11) liegenden Zahnstange zusammenzuarbeiten.
  6. Vorrichtung nach einer der Forderungen 1 bis 5, mit der Eigenheit, dass der Vergaser (15) mit einem auf dem restlichen Vergaserkörper (15) befestigten Deckel (16) versehen ist, der über eine Gleitschiene für die Zahnstange verfügt, wie auch über eine Öffnung, die den Zapfen (55) der Zahnstange aufnehmen kann.
  7. Vorrichtung nach einer der Forderungen 1 bis 6, mit der Eigenheit, dass der Zapfen der Zahnstange durch einen auf dem Deckel (16) des Vergasers (15) befestigten Geschwindigkeitsregler (57) gesteuert wird.
  8. Vorrichtung nach einer der Forderungen 1 bis 7, mit der Eigenheit, dass die schräge Rampe (47) der Kolbenstange, das auf der Kolbenstange (32) befindliche Loch (42) und die Zylinderöffnung (45) so angelegt sind, dass die Brennstoffeinspritzung jeweils beidseitig beim halben Kolbenhub stattfindet, wenn die Lineargeschwindigkeit am grössten ist.
  9. Vorrichtung nach einer der Forderungen 1 bis 8, mit der Eigenheit, dass eines der Enden der Exzenterwelle (10) direkt mit der Kurbelwelle verbunden werden kann, während das andere Ende an eine Antriebsscheibe anschliessbar ist, die eine zusätzliche Ausrüstung antreiben kann, wie etwa eine Wasserpumpe oder eine Wechselstromlichtmaschine.
EP95939324A 1994-11-07 1995-11-06 Kolbenpumpe Expired - Lifetime EP0791129B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR9413507 1994-11-07
FR9413507A FR2726606B1 (fr) 1994-11-07 1994-11-07 Pompe a pistons
PCT/FR1995/001452 WO1996014496A1 (fr) 1994-11-07 1995-11-06 Pompe a pistons

Publications (2)

Publication Number Publication Date
EP0791129A1 EP0791129A1 (de) 1997-08-27
EP0791129B1 true EP0791129B1 (de) 1998-09-02

Family

ID=9468696

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95939324A Expired - Lifetime EP0791129B1 (de) 1994-11-07 1995-11-06 Kolbenpumpe

Country Status (6)

Country Link
US (1) US6109894A (de)
EP (1) EP0791129B1 (de)
CN (1) CN1171833A (de)
DE (1) DE69504531D1 (de)
FR (1) FR2726606B1 (de)
WO (1) WO1996014496A1 (de)

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FR2797658B1 (fr) 1999-08-18 2002-08-23 Snecma Aube de turbine a profil ameliore
DE10010945B4 (de) * 2000-03-06 2004-07-22 Robert Bosch Gmbh Pumpe zur Versorgung eines Kraftstoffeinspritzsystems und einer hydraulischen Ventilsteuerung für Brennkraftmaschinen
US6461117B2 (en) * 2001-02-27 2002-10-08 International Truck Intellectual Property Company, L.L.C. Reversible volume oil pump
ITMI20040032A1 (it) * 2004-01-14 2004-04-14 Piaggio & C Spa Gruppo pompa carburante a portata variabile
US7134846B2 (en) * 2004-05-28 2006-11-14 Stanadyne Corporation Radial piston pump with eccentrically driven rolling actuation ring
US20060127228A1 (en) * 2004-12-09 2006-06-15 Steve Rohring High pressure open discharge pump system
US8182246B1 (en) 2004-12-09 2012-05-22 Steve Rohring High pressure open discharge pump system
CN100445519C (zh) * 2006-09-22 2008-12-24 郑国璋 多种燃料柴油机机油增压泵
US20080115770A1 (en) * 2006-11-16 2008-05-22 Merchant Jack A Pump with torque reversal avoidance feature and engine system using same
AT503752B1 (de) * 2007-05-10 2008-10-15 Avl List Gmbh Brennkraftmaschine
US8506267B2 (en) * 2007-09-10 2013-08-13 Schlumberger Technology Corporation Pump assembly
US8113805B2 (en) * 2007-09-26 2012-02-14 Torad Engineering, Llc Rotary fluid-displacement assembly
EP2184491A1 (de) * 2008-11-07 2010-05-12 Delphi Technologies Holding S.à.r.l. Pumpenkopf für eine Brennstoffpumpenanordnung
CN102840128A (zh) * 2012-09-10 2012-12-26 浙江大学 一种新型柱塞泵装置
EP3350447B1 (de) 2015-09-14 2020-03-25 Torad Engineering, LLC Mehrflügliges laufrad
CN105545549A (zh) * 2016-01-28 2016-05-04 全椒县全动机械有限公司 一种带输油泵的双轴平衡单缸柴油机
CN107387387B (zh) * 2017-08-30 2020-01-14 王湫锂 用于调量注入泵的低压变容流量调节方法及其调节机构
DE102019106531A1 (de) * 2019-03-14 2020-09-17 Baier & Köppel GmbH & Co. KG Schmierstoffpumpe mit automatisch ankoppelnder Pumpeinheit und Verfahren zum Ankoppeln einer Pumpeinheit an eine Schmierstoffpumpe
CN110425405A (zh) * 2019-08-22 2019-11-08 江苏中科朗润智能科技有限公司 一种正反转高压油泵
CN112761842A (zh) * 2020-12-29 2021-05-07 余姚市舒春机械有限公司 一种电喷柴油机一体式燃油泵

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FR677993A (fr) * 1928-08-13 1930-03-17 Commande pour organes distributeurs animés d'un mouvement alternatif d'amplitude constante
US2059758A (en) * 1932-10-11 1936-11-03 Stearns Frank Ballon Fuel pump for internal combustion engines
US2697403A (en) * 1949-06-06 1954-12-21 Melba L Benedek Hydraulic pump or motor
US2980023A (en) * 1957-10-07 1961-04-18 Holley Carburetor Co Fluid pumps
US3385221A (en) * 1967-03-07 1968-05-28 Caterpillar Tractor Co Multi-plunger engine fuel oil pump
IT1086329B (it) * 1977-05-26 1985-05-28 Riva Calzoni Spa Dispositivo di aggancio dei pistoni al rotore in un motore idraulico a pistoni radiali
DE3700599C2 (de) * 1987-01-10 1997-12-04 Hugo Dipl Ing Fiedler Einspritzvorrichtung für Dieselmotoren
NL9301011A (nl) * 1993-06-11 1995-01-02 Applied Power Inc Radiale-plunjerpomp.

Also Published As

Publication number Publication date
WO1996014496A1 (fr) 1996-05-17
FR2726606B1 (fr) 1996-12-06
DE69504531D1 (de) 1998-10-08
CN1171833A (zh) 1998-01-28
EP0791129A1 (de) 1997-08-27
US6109894A (en) 2000-08-29
FR2726606A1 (fr) 1996-05-10

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