EP0517014B1 - Pompe à engrenages pour huile de lubrification d'un moteur à combustion interne, en particulier pour véhicules - Google Patents

Pompe à engrenages pour huile de lubrification d'un moteur à combustion interne, en particulier pour véhicules Download PDF

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Publication number
EP0517014B1
EP0517014B1 EP92108169A EP92108169A EP0517014B1 EP 0517014 B1 EP0517014 B1 EP 0517014B1 EP 92108169 A EP92108169 A EP 92108169A EP 92108169 A EP92108169 A EP 92108169A EP 0517014 B1 EP0517014 B1 EP 0517014B1
Authority
EP
European Patent Office
Prior art keywords
pump
set forth
pump housing
crankshaft
outer rotor
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
EP92108169A
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German (de)
English (en)
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EP0517014A1 (fr
Inventor
Kurt Hoffmann
Franz Maucher
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.)
Schwaebische Huettenwerke Automotive GmbH
Original Assignee
Schwaebische Huettenwerke Automotive GmbH
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 Schwaebische Huettenwerke Automotive GmbH filed Critical Schwaebische Huettenwerke Automotive GmbH
Publication of EP0517014A1 publication Critical patent/EP0517014A1/fr
Application granted granted Critical
Publication of EP0517014B1 publication Critical patent/EP0517014B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • 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
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00

Definitions

  • the invention relates to a gear pump for oil for an internal combustion engine, in particular for motor vehicles, with the features which are listed in the preamble of claim 1, such oil pumps are known from DE-A-3 603 773 and US-A-4 827 881.
  • gear pumps are used in various technical areas.
  • gear pumps according to the preamble of claim 1 are increasingly used for internal combustion engines, in particular motor vehicle internal combustion engines, mostly for piston engines.
  • the crankshaft is extended at its free end in order to drive the inner rotor or the outer rotor.
  • the inner rotor or the driven outer rotor can be driven directly by the free end of the crankshaft.
  • embodiments are also known in which the inner rotor can be found on a separate bearing collar formed in the housing of the pump. The collar is penetrated by the crankshaft and driven by a driver.
  • the flow direction in a feed channel is approximately tangential to the central circumferential direction of the pump gearwheels in the so-called suction kidney region. Accordingly, the projection of the direction of flow in the feed channel at the beginning of the area in which it merges with the suction kidneys, i.e. in the area of the inlet opening of the working chamber, on a normal plane to the pump axis has a direction which is in line with the direction of movement of the teeth of the inner rotor or of the outer rotor this area coincides.
  • the feed channel which at the connection of the oil suction pipe can have the same circular cross section as the oil suction pipe, extends with a tapering circular cross section at the beginning of the suction kidney.
  • the oil supply duct runs partly in front of the end wall of the working chamber and partly over the circumferential surface of the Chamber of Labor.
  • the oil flow not only flows around the end face of the outer rotor, but also a part of the circumferential surface of the outer rotor.
  • the suction kidney ie the area of the opening of the working chamber, also extends over the end wall and its circumference.
  • suction kidney in which the oil flow no longer comes into contact with the peripheral surface of the outer rotor.
  • the arrangement of the suction kidneys is only provided in one end wall of the working chamber.
  • gear pumps or internal rotor gear pumps for oil for motor vehicle internal combustion engines are unanimously known from the prior art, which are provided as separate pumps and must also be driven separately.
  • the present invention is intended to solve the problem of remedying the disadvantages of the prior art and, in particular, of proposing a space-saving and simple solution for a gear pump for oil for internal combustion engines.
  • the gear pump is arranged in a drive wheel provided on the motor or in a deflection roller provided there.
  • the pump wheels provided for the actual pumping process or the pump wheel provided for this purpose are actuated via the Motor driven drive wheel or the existing deflection roller.
  • the camshaft or the crankshaft of the internal combustion engine can be used to drive the drive wheel.
  • a deflection roller present on the motor, which is used according to the invention for receiving the pump according to the invention, can be set in motion via a toothed belt, a chain or a pinion.
  • a compensation plate can be provided in the drive wheel, which is connected to the drive shaft.
  • the compensation plate should be arranged between the drive wheel and the pump wheels or the pump housing.
  • a guide device should be provided, which is designed, for example, in the form of a cylindrical pin. So that the existing compensation plate is in permanent contact has to the conveying pump wheels, a spring device is provided which biases the compensation plate against the pump wheels or presses against them. In this way, a constant delivery volume can be guaranteed regardless of the axial movement of the drive shaft. If this were not available, pressure fluctuations would result or the delivery pressure would even completely collapse at times.
  • one of the pump wheels could also be designed according to the function of the compensation plate.
  • the camshaft or crankshaft should be sealed off from the drive wheel by means of a seal, in particular an O-ring seal. This prevents oil losses.
  • An air gap should be provided between the camshaft or crankshaft and the pump housing and in particular the compensation plate, in which the drive shaft can rotate freely.
  • the pump according to the invention is provided in a deflection roller provided on the internal combustion engine, then at least the outer rotor should be firmly connected to the deflection roller.
  • the outer rotor can be pressed into the deflection roller.
  • the outer rotor meshes with the inner rotor and can interact with it in the manner of a so-called Eaton pump.
  • the inner rotor should be slidably mounted on the pump housing so that it can perform the required rotational movements.
  • the guide roller is held on the motor by means of a bearing pin.
  • the bearing pin is held or supported on the motor by a ball bearing.
  • Another bearing, in particular a needle bearing, is provided between the pump housing and the bearing pin.
  • This embodiment has the advantages that an outer rotor slide bearing is completely eliminated, since the bearing can be taken over by the roller bearing bearing pin via the deflection roller. With this, friction power reductions of approximately 50% can be achieved. In addition, the outer rotor is only braked on one side via an axial friction surface.
  • a seal is provided between the drive wheel or the deflection roller and the pump housing. Shaft seals are usually used for this.
  • the gear pump according to the invention is driven externally parasitically.
  • the force transmission takes place via the camshaft or the crankshaft to the drive wheel and from there via existing guide devices, for example cylindrical pins, to the outer rotor.
  • the power transmission is taken over by a drive shaft which is extended or provided especially for the pump.
  • the drive path is analogous, but in a slightly modified form, since no forces are transmitted via the bearing pin and the outer rotor can be firmly clamped into the drive wheel.
  • the gear pump for oil according to the invention for an internal combustion engine is generally identified by reference number 10.
  • an internal combustion engine is provided, to which the pump according to the invention is fastened by means of fastening means 32, for example screws, rivets or bolts.
  • the crankshaft 20 protrudes from the internal combustion engine 8, to which the drive wheel 12 is fastened by means of a screw 36.
  • a washer or a spring washer 26 can be provided between the screw 36 and the drive wheel 12.
  • the crankshaft 20 is sealed off from the drive wheel 12 via an O-ring seal 28.
  • teeth 30 are provided on the outer circumference of the drive wheel 12, via which teeth, for example, a toothed belt can be driven.
  • An air gap 38 is between the crankshaft 20 and one Pump housing 14 provided. In this way, the crankshaft 20 can rotate freely within the pump housing, which is firmly connected to the engine block.
  • a shaft seal 34 seals the pump housing 14 from the drive wheel 12.
  • a compensation plate 60 is provided to compensate for the axial movement of the crankshaft 20. This is provided between the drive wheel 12 and the outer rotor 18, the inner rotor 16 and the pump housing 14.
  • the inner rotor 16 is generally freely rotatable.
  • the compensation plate makes the movements of the crankshaft 20 coaxial with it.
  • the compensation plate is guided on guide devices 24, in the present case cylindrical pins 24, which is at least partially displaceably held in the adjacent components.
  • the outer rotor 18 is driven via said cylinder pins 24, with which the outer rotor 18 is connected in a rotationally fixed manner to the drive wheel 12.
  • the compensation plate 60 is permanently held in contact with the pump wheels 16, 18 by a spring device 22.
  • the outer rotor 18 meshes with the inner rotor 16 and interacts with it in the manner of an Eaton pump.
  • the crankshaft 20 drives the drive wheel 12, which in turn rotates the outer rotor 18 via the cylinder pins 24.
  • the inner rotor 18 could be provided with a ridge or a groove, which have a corresponding counterpart in the drive wheel 12.
  • the outer rotor 18 takes the inner rotor 16 with it through its toothing.
  • the cross section shown in FIG. 2 through the gear pump 10 shows the inlet or outlet opening 40, 42 through which the oil to be pumped is sucked in or pushed out.
  • the fastening parts 32 to recognize.
  • the crankshaft 20 or the screw 36 holding the drive wheel 12 is provided centrally.
  • the rotary movement is indicated by arrow 6 and runs in a clockwise direction.
  • FIG. 3 shows an analog representation of the features depicted in FIG. 2.
  • FIG. 4 shows the same features as the embodiment according to FIG. 1, the reference numerals from FIG. 1 being added to 100.
  • a camshaft 121 is provided, which is generally smaller in diameter than a crankshaft.
  • the oil to be conveyed is introduced or sucked into the pump according to the invention via an inlet opening 142 and is conveyed between the outer rotor 118 equipped with a varying inner diameter and the inner rotor 116 to the pressure or outlet opening 140.
  • the pressures that can be achieved are between 1 and 5 bar, but can be further influenced by constructive measures. Both the achievable pressure and the delivery rate depend on the speed. As a rule, the delivery pressure that can be achieved falls with decreasing speed. In contrast, the oil flow increases with speed.
  • the necessary amounts of oil can be achieved by different types of wheelsets.
  • the above-mentioned performance values of the pump according to the invention also result in remarkable reductions in the friction losses, so that there are outstanding advantages.
  • FIG. 5 shows a cross section through the embodiment according to FIG. 4.
  • the suction or pressure openings are indicated by the reference numerals 140, 142.
  • the embodiment 100 in question also conveys in the direction of arrow 106 in the clockwise direction.
  • FIG. 6 shows the same features as FIG. 5, but in a different sectional plane.
  • FIG. 7 shows the embodiment in which the pump according to the invention is driven by means of an existing deflecting roller 212 which is provided with external teeth 230.
  • the illustrated embodiment 200 has a pump housing 214, which can be made of aluminum.
  • An inner rotor 216 which advantageously consists of a sintered material, slides directly on the pump housing 214.
  • a bearing pin 254 Within the pump housing 214, a bearing pin 254, guided by a needle bearing 258, is guided.
  • the bearing pin 254 is rotatably supported on the motor block 208 via the pump housing 214 and a ball bearing 256 located between them.
  • the pump housing is connected to the motor block 208 via fastening means 232, namely a cylinder screw.
  • a seal 234 is arranged between the deflection roller 212 and the pump housing 214, a shaft sealing ring generally being used.
  • the outer rotor 218 is pressed into the deflection roller 212.
  • the suction opening is provided in the right half of FIG. 7, while the pressure opening can be seen in the left half of the section.
  • the friction losses compared to the known gear pumps are considerable, i.e. by about 60%.
  • the bearing of the deflection roller 212 over the roller-mounted bearing pin 254 results in a reduction of the required friction by 50%.
  • the lower axial friction surface which only engages on one side on the outer rotor and the positively changed relative speed between the inner rotor and the deflection pulley 212, result in further savings in friction, so that overall a 60% more favorable power consumption situation results than in the prior art.
  • Corresponding advantages can also arise for the embodiments 10, 100.
  • FIG 8 and 9 show cross sections through embodiment 200, from which the suction and pressure feeds and the associated compression and decompression spaces can be seen.
  • suction kidney shapes reference is made to the introduction to the description.

Claims (15)

  1. Pompe à engrenages pour huile d'un moteur à combustion interne, en particulier pour des véhicules automobiles, présentant les particularités suivantes :
    a) un carter de pompe monté sur le moteur;
    b) un rotor extérieur logé dans le carter de pompe;
    c) un rotor intérieur disposé dans le rotor extérieur et respectivement dans le carter de pompe;
    d) au moins une conduite d'aspiration et/ou au moins une conduite de refoulement dans le carter de pompe, et
    e) un mécanisme d'entraînement,
       caractérisée en ce qu'elle présente les particularités suivantes:
    f) la pompe (10, 100, 200) est disposée dans une roue de commande (12, 112) ou une poulie de renvoi (212) du moteur à combustion interne (8, 108, 208), et
    g) le rotor extérieur (18, 118, 218) et respectivement le rotor intérieur (16, 116, 216), par l'intermédiaire du rotor extérieur (18, 118, 218), sont entraînés par la roue de commande (12, 112) et respectivement par la poulie de renvoi (212) lesquelles sont entraînées par l'intermédiaire d'un arbre à cames (120) ou d'un vilebrequin (20) du moteur à combustion interne (8, 108).
  2. Pompe selon la revendication 1, caractérisée en ce que la poulie de renvoi (212) est entraînée par l'intermédiaire d'une courroie dentée ou d'une chaîne.
  3. Pompe selon la revendication 1, caractérisée en ce qu'elle comprend une plaque de compensation (60, 160) disposée de préférence entre la roue de commande (12, 112) et les roues de pompe et respectivement le carter de pompe (14, 114).
  4. Pompe selon la revendication 3, caractérisée en ce qu'elle comprend au moins un dispositif de guidage (24, 124) qui guide la plaque de compensation (60, 160) coaxialement pu rapport à l'arbre moteur et respectivement le vilebrequin (20, 120) et la bloque en rotation.
  5. Pompe selon la revendication 4, caractérisée en ce que le(s) dispositif(s) de guidage (24, 124) est/sont fixé(s) ou guidé(s) dans l'un des rotors extérieurs (18, 118) et/ou la roue de commande (12, 112).
  6. Pompe selon l'une des revendications 1 et/ou 3 à 5, caractérisée en ce que l'étanchéité entre l'arbre à cames et respectivement le vilebrequin (20, 120) et la roue de commande (12, 112) est assurée au moyen d'un joint d'étanchéité (28, 128), notamment un joint torique.
  7. Pompe selon l'une des revendications 1 et/ou 3 à 6, caractérisée en ce qu'elle comprend un élément de ressort (22, 122) qui met la plaque de compensation (60, 160) en précontrainte ou l'applique contre les roues de pompe (16, 116; 18, 118) et respectivement le carter de pompe (14, 114).
  8. Pompe selon l'une des revendications 3 à 7, caractérisée en ce qu'elle présente une fente (38, 138) entre l'arbre à cames et respectivement le vilebrequin (20, 120) et le carter de pompe (14, 114), et notamment la plaque de compensation (60, 160).
  9. Pompe selon l'une des revendication 1 ou 2, caractérisée en ce que le rotor extérieur (218) est solidarisé avec la poulie de renvoi (212) et notamment emmanché dans cette dernière.
  10. Pompe selon l'une des revendications 1, 2 et/ou 9, caractérisée en ce que le rotor intérieur (216) est monté de manière coulissante sur le carter de pompe (214).
  11. Pompe selon l'une des revendications 1, 2, 9 ou 10, caractérisée en ce que la poulie de renvoi (212) est fixée sur le moteur (208) par l'intermédiaire d'un axe de palier (254), notamment à roulement.
  12. Pompe selon la revendication 11, caractérisée en ce que l'axe de palier (254) est monté sur le moteur (208) par i'intermédiaire d'un roulement à billes (256).
  13. Pompe selon l'une des revendications 11 ou 12, caractérisée en ce qu'un palier supplémentaire notamment un roulement à aiguilles (258), est disposé entre le carter de pompe (214) et respectivement le rotor intérieur (216) et l'axe de palier (254).
  14. Pompe selon l'une des revendications 1, 2, 10 à 13, caractérisée en ce que l'axe de palier (254) est rendu étanche par rapport à la poulie de renvoi (212), en particulier par un joint torique (228).
  15. Pompe selon l'une des revendications 1 à 14, caractérisée en ce qu'entre le carter de pompe (14, 114, 214) et la roue de commande ou la poulie de renvoi (12, 112, 212) est disposé un joint d'étanchéité (134), de préférence une bague à lèvres avec ressort (34, 234).
EP92108169A 1991-06-07 1992-05-14 Pompe à engrenages pour huile de lubrification d'un moteur à combustion interne, en particulier pour véhicules Expired - Lifetime EP0517014B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE4118872 1991-06-07
DE4118872 1991-06-07
DE4123190 1991-07-12
DE4123190A DE4123190A1 (de) 1991-06-07 1991-07-12 Zahnradpumpe fuer oel fuer einen verbrennungsmotor, insbesondere fuer kraftfahrzeuge

Publications (2)

Publication Number Publication Date
EP0517014A1 EP0517014A1 (fr) 1992-12-09
EP0517014B1 true EP0517014B1 (fr) 1995-11-15

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EP92108169A Expired - Lifetime EP0517014B1 (fr) 1991-06-07 1992-05-14 Pompe à engrenages pour huile de lubrification d'un moteur à combustion interne, en particulier pour véhicules

Country Status (7)

Country Link
US (1) US5395217A (fr)
EP (1) EP0517014B1 (fr)
JP (1) JP3107646B2 (fr)
KR (1) KR100250191B1 (fr)
AT (1) ATE130402T1 (fr)
CA (1) CA2070477C (fr)
DE (2) DE4123190A1 (fr)

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Also Published As

Publication number Publication date
JP3107646B2 (ja) 2000-11-13
EP0517014A1 (fr) 1992-12-09
US5395217A (en) 1995-03-07
JPH05263771A (ja) 1993-10-12
DE4123190A1 (de) 1992-12-10
CA2070477C (fr) 2003-09-02
CA2070477A1 (fr) 1992-12-08
DE59204306D1 (de) 1995-12-21
KR100250191B1 (ko) 2000-04-01
KR930000802A (ko) 1993-01-15
ATE130402T1 (de) 1995-12-15

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