EP0475109B1 - Pompe à engrenages internes pour fluide hydraulique - Google Patents

Pompe à engrenages internes pour fluide hydraulique Download PDF

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Publication number
EP0475109B1
EP0475109B1 EP91113737A EP91113737A EP0475109B1 EP 0475109 B1 EP0475109 B1 EP 0475109B1 EP 91113737 A EP91113737 A EP 91113737A EP 91113737 A EP91113737 A EP 91113737A EP 0475109 B1 EP0475109 B1 EP 0475109B1
Authority
EP
European Patent Office
Prior art keywords
eccentric
chamber
inlet
pump
radius
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
EP91113737A
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German (de)
English (en)
Other versions
EP0475109A1 (fr
Inventor
Siegfried Hertell
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.)
Barmag Luk Automobiltechnik GmbH and Co KG
Original Assignee
Barmag Luk Automobiltechnik GmbH and Co KG
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 Barmag Luk Automobiltechnik GmbH and Co KG filed Critical Barmag Luk Automobiltechnik GmbH and Co KG
Priority to AT9191113737T priority Critical patent/ATE104747T1/de
Publication of EP0475109A1 publication Critical patent/EP0475109A1/fr
Application granted granted Critical
Publication of EP0475109B1 publication Critical patent/EP0475109B1/fr
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
    • 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

Definitions

  • the invention relates to a gear pump according to the preamble of claim 1.
  • This pump is known from DE-OS 34 48 253 (PP-1372).
  • the inner wheel is mounted in the recess of a rotor.
  • the rotor in turn is rotatably supported in the space formed by the outer wheel and fills it.
  • the known pump has a circular cylindrical inlet space located in an end wall and a channel system arranged in the rotor, which meshes with the circular cylindrical insert space and is in permanent communication.
  • annular inlet space is covered by the rotating wheel so that the engagement zone on the pressure side has no connection to the inlet.
  • the solution according to claim 5 avoids that the rotating forces arising from the rotation of the inner wheel and the pressure zone have an effect on the drive shaft and lead to bending of the shaft and tilting of the inner wheel.
  • the solution according to claim 6 and / or 7 achieves good cooling and lubrication of the eccentric, which is subjected to heat and wear due to the sliding bearings inside and outside.
  • a further intensification of the cooling can be achieved by the measure according to claim 8.
  • the invention has the advantage that the delivery characteristic of the pump initially rises rapidly with increasing speed, then remains constant and then drops again.
  • a characteristic curve is particularly suitable in automotive hydraulics.
  • the pump housing is formed by the pump casing 1 and the end plates 2 and 3, which are stacked on top of one another.
  • the housing shell 1 has a circular cylindrical interior, in the cylindrical inner shell of which a circumferential groove 4 is pierced.
  • the outer wheel 6 is fastened on the webs 5 which remain to the side.
  • the entire package consisting of housing shell 1, end plates 2 and 3 and outer wheel 6 is held together by a screw 7.
  • the screw connection 7 penetrates the outer wheel in the region of the tooth heads with holes 8.
  • the outer wheel has internal teeth.
  • the interior of the pump is thus circumscribed by the internal toothing with tip circle 9 of the outer wheel.
  • a pin 10 is firmly inserted at one end.
  • the other end of the pin 10 projects into the interior of the pump.
  • an eccentric 11 is freely rotatable.
  • the axial width of the eccentric corresponds essentially to the axial width of the housing shell 1 and the outer wheel 6.
  • the eccentric has a circular cylindrical outer circumference, the central axis of which is indicated at 12 and which rotates with the eccentricity E about the axis 13 of the pin 10.
  • the inner wheel 14 is freely rotatably mounted on the eccentric 11.
  • the inner wheel 14 has external teeth.
  • the eccentricity E of the eccentric and the external toothing of the inner wheel are dimensioned and the toothings are designed so that the external toothing of the inner wheel meshes with the internal toothing of the outer wheel. Therefore, the top circles 9 and 15 of the toothing intersect in the circumferential intersection points 21 and 22. On the inner circumference of the top circle 9 of the outer wheel, this results on the one hand on the side of the axis 13, between the intersection points 21 and 22 which has the eccentricity E, the circumferential engagement area and, on the other hand, on the side of the axis 13 which faces away from the eccentricity, the circumferential inner sickle space 23 of the pump.
  • the teeth are designed so that the teeth of the outer and inner wheel between the intersections 21 and 22 of the tip circles 9 and 15 are in sealing engagement with their flanks. There are therefore several tooth cells between the intersection points 21 and 22 in the engagement area, which are sealed by touching their flanks to one another and to the inner crescent space 23 facing away from the eccentricity.
  • the drive shaft 16 is used to drive the pump.
  • the drive shaft 16 is rotatably mounted concentrically to the central axis 13 of the pin 10 in the other end plate 2 and its end is essentially flush with the inside of the pump chamber.
  • the shaft 16 forms an end face on which a coupling tab 17 is attached eccentrically. This coupling tab 17 protrudes axially into a driving pocket 18 which is introduced into the adjacent end face of the eccentric 11 in the area of the eccentricity.
  • the pump has an essentially radial inlet channel 19 in the end plate 3.
  • the inlet channel opens into a distribution space 20 which concentrically surrounds the pin 10.
  • the distributor chamber is designed as a circular cylindrical recess in the end face of the end plate, which delimits the pump chamber. Their radius is smaller than the radius Fi of the root circle of the inner wheel.
  • a further circular cylindrical recess is made concentrically with the axis 13.
  • This recess serves as the inlet chamber 28.
  • the distributor chamber 20 and the inlet chamber 28 are through channels which axially penetrate the eccentric, connected with each other. These channels are preferably designed as grooves of the inner bore of the eccentric and serve to lubricate the slide bearing of the eccentric on the pin 10 and also to cool the eccentric 11.
  • the drive pocket 18 serves as such a channel, which therefore axially penetrates the eccentric 11 and with it outer edge revolves on a radius that is slightly larger than the radius of the shaft. It is particularly advantageous that this channel lies on the side of the eccentric axis in which the eccentricity is also directed.
  • Corresponding channels can also be created in the inner bore of the eccentric, so that a symmetrical distribution of the oil and at the same time hydrodynamic support of the eccentric is effected by the oil flow flowing in these channels 29 and in the driving pocket 18.
  • These oil flows also have the function of cooling the eccentric. This cooling function is particularly important because the eccentric is rotatably supported in its inner bore and serves as a rotatable bearing for the inner wheel on its outer casing.
  • Another measure for cooling which can be used additionally or alternatively, is also that on the side of the ring channels, i.e. the inlet chamber 28 and / or the distributor chamber 20, the eccentric is somewhat thinner than the inner wheel or the width of the housing shell 1.
  • an annular surface is formed on the end face of the eccentric, which is filled with oil and in which there is a constant oil flow .
  • this embodiment of the eccentric is shown by lines 34, 35, which indicate the end faces of the eccentric.
  • the outer radius R of the inlet chamber 28, based on the axis 13 of the pin 10, has to be kept within certain limits according to the invention, which will be discussed later.
  • the dimensioning of the outer radius R of the inlet chamber 28 is such that the root circle Fi of the inner wheel or the circular area circumscribed by this root circle covers the inlet chamber 28 with the exception of a crescent-shaped inlet surface 27.
  • the inlet surface is also partially covered by the sides of the teeth of the inner wheel.
  • the inlet surface 27 runs on the side of the interior facing away from the eccentricity.
  • the dimensioning according to the invention of the outer radius R of the inlet chamber 28 on the one hand and the root circle Fi of the inner wheel on the other hand ensures that the crescent-shaped inlet surface 27 is never covered by one of the closed tooth cells of the engagement area. This avoids a dead travel of these tooth cells in the pressure range and improves the hydraulic efficiency.
  • the outlet channel 24 is located radially in the housing shell 1 and is connected to the circumferential groove 4 of the housing shell. This circumferential groove is limited on the inside by the outer circumference of the outer wheel and forms an outer chamber.
  • the outer wheel has at least one outlet bore 25 in the region of each tooth gap.
  • Fig. 1 it is shown that two outlet bores 25.1 and 25.2 are adjacent to each other in the axial direction per tooth gap.
  • the outlet bores are each arranged in parallel radial planes.
  • Each radial plane is covered by an elastic valve ring 26.1 and 26.2, which covers all the outlet bores of a normal plane and is cut through in an axial plane.
  • One end is e.g. held by a rivet, the other end is free to move.
  • These valve rings 26.1, 26.2 serve as check valves for each of the outlet bores.
  • the drive shaft 16 is driven with the direction of rotation 31.
  • the clutch tab 17 engages in the driving pocket 18 of the eccentric and takes the eccentric with it.
  • the inner wheel 14 executes a wobbling movement in the interior of the pump, whereby it rotates in the direction of rotation 32 due to the engagement of its toothing with the toothing of the outer wheel. It forms with the toothing of the outer wheel in the engagement area between the intersections 21, 22 of the two tip circles, a plurality of tooth cells, which continuously enlarge and reduce. In the trailing area, the cells enlarge until they open and come into contact with the inner sickle space 23 filled with oil. The cells shrink on the leading side of the inner wheel. So here the oil is put under pressure. If the pressure in a cell exceeds the system pressure prevailing in the circumferential groove 4, the valve rings 26.1 and 26.2 are lifted there from the outlet bores 25.1, 25.2 due to the pressure difference, so that the oil can be expelled from the cell.
  • the outer diameter of the inlet chamber 28 is now dimensioned such that the cells on the pressure side have no connection with the inlet chamber 28. Rather, the inlet chamber is in the pressure area from the end face of the inner wheel, i.e. covered by the area enclosed by the root circle and the tooth heads. Therefore, the width of the crescent-shaped inlet surface 27, which is delimited on the outside by the circumferential surface of the inlet chamber 28 and on the inside by the root circle of the inner wheel, may only be one division greater than the width of the crescent-shaped interior 23, which is delimited by the two root circles. The width of these crescent-shaped spaces and the division is measured in each case as a central angle about the central axis 13 of the pump.
  • the pump can preferably also be used as a suction-restricted pump.
  • the inlet duct 19 has a throttle 33.
  • This throttle only a limited amount of oil can be drawn in.
  • This time-limited suction quantity is only sufficient to completely fill the pump up to a certain speed.
  • the pump delivery rate is therefore proportional to the speed only up to this speed. If the speed increases, there is no further increase in the delivery rate. Therefore, increasing the speed is not associated with increased power consumption.
  • the pump is therefore particularly suitable for consumers in motor vehicles who have an oil requirement that is not dependent on the strongly fluctuating engine speed.
  • the inlet surface 27 can also be dimensioned so small that the throttling required for a suction throttle control takes place there. As a result, the seal 36 in the region between the pump shaft 16 and the housing end wall 2 can be relieved of pressure forces.
  • the radius of the distributor space 20 can be dimensioned in the same way as the radius of the inlet chamber 28.
  • the pump is filled both via the distributor space and via the inlet chamber. This results in a conveying characteristic curve which initially increases steeply with the speed in the case of suction throttling, but then remains constant regardless of the speed.
  • Such a characteristic curve is suitable in automotive hydraulics wherever constant hydraulic forces have to be applied which are independent of the engine speed and speed of the vehicle.
  • the radius of the distribution space can also be dimensioned such that the distribution space is not connected to the pressure cells formed by the teeth.
  • the pump is filled exclusively via the inlet chamber 28.
  • there is a delivery characteristic curve which initially increases steeply with the speed when the pump is throttled, then kinks and remains essentially constant over a speed range and then again with the Speed drops.
  • Such a characteristic curve is installed in the area of motor vehicle hydraulics wherever only reduced hydraulic forces are to be applied at high vehicle speed or engine speed, as is the case, for. B. is the case with the steering aid.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Claims (9)

  1. Pompe à engrenages intérieurs, pour fluide hydraulique, dans laquelle la roue extérieure dotée d'une denture intérieure est stationnaire et forme un volume intérieur fermé, la roue intérieure plus petite, dotée d'une denture extérieure, tourne sur un excentrique entraîné (11) excentriquement par rapport à la roue extérieure avec laquelle elle est en prise, la différence entre le nombre des dents de la roue extérieure (6) et de la roue intérieure (14) est d'au moins 2, et dans laquelle l'aspiration présente une chambre d'entrée cylindro-circulaire, concentrique à la roue extérieure, qui est agencée dans la paroi frontale et dont le rayon extérieur de cette chambre d'entrée est plus petit que la somme de l'excentricité et du rayon du cercle de pied de la roue intérieure et plus grand que la différence entre le rayon du cercle de pied de la roue intérieure et l'excentricité,
    caractérisée
    par le fait que la roue intérieure (14) recouvre partiellement la chambre d'entrée (28) et laisse libre une surface d'entrée tournante en forme de croissant (27), laquelle s'étend sur un angle au centre qui, mesuré sur l'axe de la pompe (13), est plus petit que la somme de l'angle de pas et de l'angle au centre, mesuré sur l'axe de pompe (13), de l'espace intérieur tournant en forme de croissant (23), lequel est défini, du côté éloigné de l'excentricité, par le cercle de tête.
  2. Pompe selon revendication 1,
    caractérisée
    par le fait que la denture est réalisée de manière que, dans la zone d'engrènement, entre les points d'intersection des cercles de tête, plusieurs paires de dents soient à chaque fois en engrènement étanche et forment des cellules à dents fermées, et par le fait qu'à chaque entredent est associé un canal de sortie (25) fermé par une soupape antiretour, plusieurs canaux de sortie étant affectés à chaque fois à un volume de refoulement.
  3. Pompe selon revendication 1 ou 2,
    caractérisée
    par le fait que l'excentrique (11) s'applique d'un côté contre la chambre d'entrée (28) et de l'autre côté contre une chambre répartitrice (20) cylindro-circulaire, laquelle est relié au canal d'aspiration et possède un rayon extérieur qui est plus petit que le rayon du cercre de pied de la roue intérieure et par le fait que la chambre répartitrice (20) et la chambre d'entrée (28) sont reliées par des canaux (19, 29, 30) parallèles à l'axe.
  4. Pompe selon revendication 3,
    caractérisée
    par le fait que l'excentrique est traversé par les canaux (19, 29, 30) parallèles à l'axe, lesquels se trouvent dans la région de l'excentricité.
  5. Pompe selon l'une des revendications 1 à 4,
    caractérisée
    par le fait que l'excentrique (11) est monté à rotation sur un tourillon (10) concentrique à l'axe (13) de la pompe et monté fixe, en porte à faux, dans le carter.
  6. Pompe selon revendications 4 et 5,
    caractérisée
    par le fait que les canaux (19, 29, 30) parallèles à l'axe sont aménagés sous forme de rainures axiales dans la portée de glissement de l'excentrique sur le tourillon et/ou dans la portée de glissement de la roue intérieure sur l'excentrique.
  7. Pompe selon revendication 5 ou 6.
    caractérisée
    par le fait que, du côté de la chambre d'entrée (28) et/ou du côté du chambre répartitrice (20), l'excentrique est plus étroit que la roue intérieure (14).
  8. Pompe selon revendication 5,
    caractérisée
    par le fait que l'excentrique est couplé à l'arbre d'entraînement par un entraîneur excentrique (17) de l'arbre d'entraînement, lequel entraîneur est en prise dans un évidement (18), et par le fait que l'évidement sert de canal entre chambre d'entrée (28) et chambre répartitrice (20).
  9. Pompe selon l'une des revendications précédentes,
    caractérisée
    par le fait que la chambre répartitrice (20) possède un rayon plus petit que le rayon du cercle de pied de la roue intérieure (14), déduction faite de l'excentricité (E) de l'excentrique (11).
EP91113737A 1990-08-20 1991-08-16 Pompe à engrenages internes pour fluide hydraulique Expired - Lifetime EP0475109B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT9191113737T ATE104747T1 (de) 1990-08-20 1991-08-16 Innenzahnradpumpe fuer hydraulikfluessigkeit.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE4026259 1990-08-20
DE4026259 1990-08-20
DE4028209 1990-09-06
DE4028209 1990-09-06

Publications (2)

Publication Number Publication Date
EP0475109A1 EP0475109A1 (fr) 1992-03-18
EP0475109B1 true EP0475109B1 (fr) 1994-04-20

Family

ID=25896045

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91113737A Expired - Lifetime EP0475109B1 (fr) 1990-08-20 1991-08-16 Pompe à engrenages internes pour fluide hydraulique

Country Status (3)

Country Link
EP (1) EP0475109B1 (fr)
JP (1) JP3011796B2 (fr)
DE (1) DE59101434D1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4412980C2 (de) * 1993-04-28 1999-05-06 Luk Automobiltech Gmbh & Co Kg Hydraulikpumpe
DE102015209836B3 (de) * 2015-05-28 2016-06-02 Eckerle Industrie-Elektronik Gmbh Innenzahnradpumpe
DE102016121237B4 (de) 2016-11-07 2020-03-12 Nidec Gpm Gmbh Hydraulische Gerotorpumpe und Herstellungsverfahren einer Gerotorpumpe
DE102016121240A1 (de) * 2016-11-07 2018-05-09 Nidec Gpm Gmbh Elektrische Gerotorpumpe und Herstellungsverfahren für dieselbe
DE102017104063B4 (de) 2017-02-27 2019-11-28 Nidec Gpm Gmbh Elektrische Gerotorpumpe mit Steuerspiegel

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1099560A (fr) * 1954-02-15 1955-09-07 Perfectionnements aux machines à engrenages conjugués et leurs applications
DE3005657A1 (de) * 1980-02-15 1981-08-20 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Zahnradpumpe
DE3444859A1 (de) * 1983-12-14 1985-06-27 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Rotationszellenpumpe fuer hydrauliksysteme
DE3504783A1 (de) * 1984-02-15 1985-10-24 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Zahnradpumpe mit innenverzahnung
GB2219631B (en) * 1988-06-09 1992-08-05 Concentric Pumps Ltd Improvements relating to gerotor pumps

Also Published As

Publication number Publication date
DE59101434D1 (de) 1994-05-26
EP0475109A1 (fr) 1992-03-18
JPH04255584A (ja) 1992-09-10
JP3011796B2 (ja) 2000-02-21

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