EP0474001B1 - Pompe à engrenages internes pour fluide hydraulique - Google Patents

Pompe à engrenages internes pour fluide hydraulique Download PDF

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Publication number
EP0474001B1
EP0474001B1 EP91113816A EP91113816A EP0474001B1 EP 0474001 B1 EP0474001 B1 EP 0474001B1 EP 91113816 A EP91113816 A EP 91113816A EP 91113816 A EP91113816 A EP 91113816A EP 0474001 B1 EP0474001 B1 EP 0474001B1
Authority
EP
European Patent Office
Prior art keywords
eccentric
pump
internal gear
recess
chamber
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
EP91113816A
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German (de)
English (en)
Other versions
EP0474001A1 (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
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Filing date
Publication date
Application filed by Barmag Luk Automobiltechnik GmbH and Co KG filed Critical Barmag Luk Automobiltechnik GmbH and Co KG
Publication of EP0474001A1 publication Critical patent/EP0474001A1/fr
Application granted granted Critical
Publication of EP0474001B1 publication Critical patent/EP0474001B1/fr
Anticipated expiration legal-status Critical
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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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C15/064—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps
    • F04C15/066—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps of the non-return type
    • F04C15/068—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps of the non-return type of the elastic type, e.g. reed valves
    • 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 GB-A-9359 / AD 1915.
  • 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.
  • the outer wheel with internal teeth is stationary and forms a closed interior.
  • the smaller inner wheel with external teeth is rotatable on a circular cylindrical eccentric that can be rotated around the pump axis and meshes with the outer wheel.
  • the inlet has an inlet chamber which communicates with the inlet channel on the one hand and with the inner crescent space of the pump on the other hand via connecting channels of the eccentric.
  • the inner wheel has a radial connecting channel in each tooth base.
  • an inlet space running around the eccentric is created, which is connected on the one hand directly or via axial channels arranged in the eccentric to the inlet channel and on the other hand only communicates with the filling space of the pump rotating around the eccentric.
  • the toothing of the pump is preferably designed so that in the engagement area between the intersections of the head circles, several pairs of teeth are in sealing engagement and form closed tooth cells. This area of engagement is in any case blocked by the configuration according to claim 1.
  • the solution according to claim 3 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 a deflection of the shaft and a tilting of the inner wheel.
  • the solution according to claim 4 achieves good cooling and lubrication of the eccentric, which is subjected to heat and wear due to the sliding bearings inside and outside.
  • 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 The inner wheel is dimensioned and the teeth are designed so that the outer toothing of the inner wheel meshes with the inner toothing of the outer wheel. Therefore, the top circles 9 and 15 of the toothing intersect in the circumferential intersections 21 and 22. On the inner circumference of the top circle 9 of the outer wheel, this results in between the intersections 21 and 22 on the one hand on the side of the axis 13, into which the eccentricity E points 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 or filling 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 journal 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 region 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 distribution space is designed as a circular cylindrical recess in the end face of the end plate, which limits the pump room. Their radius is smaller than the radius Fi of the root circle of the inner wheel, minus the eccentricity E.
  • a circular cylindrical recess is made concentrically to the central axis 12 of the eccentric.
  • This recess serves as the inlet chamber 28.
  • the distributor chamber 20 and the inlet chamber 28 are connected to one another by channels which penetrate the eccentric axially. 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. Several such channels can also be provided. From Fig.
  • the recess 28 is closed off from the inner circumference of the inner wheel by a rib 34 which remains.
  • This rib must extend essentially over the entire area of engagement extend. In other words, this means that the recess may only extend to the inner circumference of the inner wheel on the side of the eccentric bearing facing away from the eccentricity.
  • This opening area may only extend at most over the central angle, which is measured on the pump axis 13 and is not greater than the sum of the pitch angle and the central angle of the inner sickle space 23 (opening area) measured on the pump axis 13.
  • the rib 34 also has only a small connection opening 35 in the form of a groove made in the end face of the rib in the opening area. This groove lies on the diameter of the eccentric that intersects the pump axis and the eccentric axis, but on the side facing away from the eccentric axis.
  • the inner wheel is provided on the end face, which lies in the radial plane of the recess 28, with connecting grooves 36.
  • One connecting groove 36 connects each tooth base radially to the inner circumference.
  • the outlet channel 24 is located radially in the housing shell 2 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 through a rivet, for example held, 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 outer wheel 6 thereby executes a wobbling movement in the interior of the pump, wherein it rotates with the toothing of the outer wheel with the direction of rotation 32 as a result of the engagement of its toothing. 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. When 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 distribution space is connected to the recess 28 through the driver pocket 18 which penetrates the eccentric axially and / or through connecting channels 29.
  • the connecting channels 29 are designed as grooves in the inner circumference of the slide bearing of the eccentric. In the area of the slide bearing of the eccentric 11, this creates a good lubricating film, which is used both for lubrication and for hydrodynamic support.
  • the rotation of the eccentric with direction of rotation 31 rotates the inner wheel with direction of rotation 32.
  • the gear wheel therefore executes a relative movement to the eccentric and to the radial connecting opening 35 in the outer rib 34 of the eccentric.
  • An intermittent connection between the recess 28 and the inner sickle space (equal to the filling space) 23 of the pump is therefore produced via the connecting grooves 36 in the end face of the inner wheel.
  • the connection opening 35 and / or the connection grooves 36 are now dimensioned such that they only bring about a throttling connection.
  • the amount of oil entering the filling chamber 23 is limited by the speed-dependent time in which the connecting opening 35 and the connecting grooves 36 are each in alignment. The throttling at this point prevents the seal 37 from being exposed to a pressure difference.
  • the connecting opening 35 can also be larger than shown, so that in each case several of the connecting grooves of the inner wheel are aligned with the connecting opening 35 of the recess and there is therefore a constant connection between the recess 28 and the filling space 23.
  • the size of the connection opening 35 is so limited that it never covers one of the closed tooth cells of the engagement area S. This avoids a dead travel of these tooth cells in the pressure range and maintains or improves the hydraulic efficiency. Therefore, the width of the connecting opening 35 may only be one division greater than the width of the crescent-shaped interior 23, which is delimited by the two circles of the foot. The width of the crescent-shaped interior 23 of the opening 35 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.
  • By throttling the amount of oil admitted only a limited amount of oil can be drawn in per unit of time. This time-limited suction amount only extends to at a certain speed to completely fill the pump.
  • 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 throttling can - as already described - advantageously take place by a narrow dimensioning of the connecting opening 35 of the recess 28 and / or by a narrow dimensioning of the connecting grooves 36 in the end face of the inner wheel.
  • a throttle in the inlet channel 19 by means of which the amount of oil let through per unit of time is limited.
  • the throttling can alternatively or additionally also take place by means of a throttle which is installed in or in front of the inlet duct 19 (not shown).

Claims (5)

  1. Pompe à engrenages internes pour liquide hydraulique, dans laquelle le pignon externe (6) pourvu d'une denture intérieure est fixe et forme une chambre intérieure fermée, dans laquelle le pignon interne (14) plus petit pourvu d'une denture extérieure tourne sur un excentrique cylindro-circulaire tournant autour de l'axe de la pompe et engrène avec le pignon externe, dans laquelle l'aspiration comporte une chambre d'aspiration (28) qui communique d'une part avec le canal d'aspiration (19) et d'autre part avec la chambre intérieure (23) en forme de croissant de la pompe par l'intermédiaire de canaux de communication de l'excentrique (11) et dans laquelle le pignon interne (14) présente dans chaque fond de dent un canal de communication (36) radial, caractérisée par le fait que la chambre d'aspiration (28) est constituée par un évidement aménagé dans la face frontale de l'excentrique (11) qui comporte un orifice de communication (35) orienté radialement en direction de la surface périphérique intérieure du pignon interne (14), par le fait l'orifice de communication (35) s'étend sur un angle au centre mesuré au niveau de l'axe (13) de la pompe qui est inférieur à la somme de l'angle de division et de l'angle au centre mesuré au niveau de l'axe (13) de la pompe de la chambre intérieure (23) en forme de croissant qui tourne avec l'excentrique (11) et est définie par les cercles de tête du côté opposé à l'excentricité et par le fait que les canaux de communication (36) sont situés dans le plan de l'évidement.
  2. Pompe à engrenages internes selon la revendication 1, caractérisée par le fait que l'évidement (28) est relié de manière directe ou par l'intermédiaire de canaux de communication (18, 29) aménagés dans la direction axiale dans l'excentrique (11) à une chambre de répartition (20) cylindro-circulaire contigüe à surface frontale de l'excentrique (11), qui communique avec le canal d'aspiration (19) et dont le rayon est inférieur à la différence entre le rayon (FI) du cercle de pied du pignon interne et l'excentricité.
  3. Pompe selon l'une des revendications précédentes, caractérisé par le fait que l'excentrique (11) est monté tournant sur un tourillon (10) concentrique à l'axe de la pompe qui est monté fixe et en porte-à-faux dans le carter et par le fait que l'excentrique est rendu solidaire en rotation par un doigt d'entraînement (17) qui est lié à l'arbre de la pompe et pénètre dans un logement (18) de l'excentrique.
  4. Pompe selon l'une des revendications précédentes, caractérisé par le fait que l'évidement (28) et la chambre de répartition (20) sont formés chacun sur une face de l'excentrique et communiquent par des canaux (18, 29) parallèles à l'axe aménagés dans l'excentrique (11) et par le fait que, de préférence, les canaux (29) parallèles à l'axe sont aménagés dans le palier lisse de l'excentrique (11), sur le tourillon (10), et/ou dans le palier lisse du pignon interne (14), sur l'excentrique (11), sous la forme de rainures axiales.
  5. Pompe selon les revendications 3 et 4, caractérisée par le fait le logement (18) sert de canal parallèle à l'axe entre l'évidement (28) et la chambre de répartition (20).
EP91113816A 1990-09-01 1991-08-17 Pompe à engrenages internes pour fluide hydraulique Expired - Lifetime EP0474001B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4027825 1990-09-01
DE4027825 1990-09-01

Publications (2)

Publication Number Publication Date
EP0474001A1 EP0474001A1 (fr) 1992-03-11
EP0474001B1 true EP0474001B1 (fr) 1995-01-04

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EP91113816A Expired - Lifetime EP0474001B1 (fr) 1990-09-01 1991-08-17 Pompe à engrenages internes pour fluide hydraulique

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EP (1) EP0474001B1 (fr)
JP (1) JP3056292B2 (fr)
AT (1) ATE116719T1 (fr)
DE (1) DE59104131D1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0579981B1 (fr) * 1992-06-29 1996-10-23 LuK Automobiltechnik GmbH & Co. KG Pompe à engrenages internes pour fluide hydraulique
IT1271052B (it) * 1993-11-18 1997-05-26 Pompa ad ingranaggi interni con sporgenze volumetriche
DE102007022215A1 (de) * 2007-05-11 2008-11-13 Robert Bosch Gmbh Pumpenbaugruppe zur synchronen Druckbeaufschlagung von zwei Fluidsäulen
CN105422442A (zh) * 2015-12-31 2016-03-23 江苏驰翔精密齿轮股份有限公司 内啮合齿轮泵

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2834735A1 (de) * 1978-08-08 1980-02-14 Buehl Volks Raiffeisenbank Fluessigkeitspumpe, insbesondere fuer fluessigkeiten geringer viskositaet, wie wasser, alkohole u.a.
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
EP0474001A1 (fr) 1992-03-11
JP3056292B2 (ja) 2000-06-26
DE59104131D1 (de) 1995-02-16
JPH04234585A (ja) 1992-08-24
ATE116719T1 (de) 1995-01-15

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