EP0579981B1 - Pompe à engrenages internes pour fluide hydraulique - Google Patents

Pompe à engrenages internes pour fluide hydraulique Download PDF

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Publication number
EP0579981B1
EP0579981B1 EP93110326A EP93110326A EP0579981B1 EP 0579981 B1 EP0579981 B1 EP 0579981B1 EP 93110326 A EP93110326 A EP 93110326A EP 93110326 A EP93110326 A EP 93110326A EP 0579981 B1 EP0579981 B1 EP 0579981B1
Authority
EP
European Patent Office
Prior art keywords
tooth
eccentric
pocket
wheel
internal gear
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
EP93110326A
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German (de)
English (en)
Other versions
EP0579981A1 (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.)
Magna Powertrain Hueckeswagen GmbH
Original Assignee
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 LuK Automobiltechnik GmbH and Co KG filed Critical LuK Automobiltechnik GmbH and Co KG
Publication of EP0579981A1 publication Critical patent/EP0579981A1/fr
Application granted granted Critical
Publication of EP0579981B1 publication Critical patent/EP0579981B1/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
    • 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels

Definitions

  • the invention relates to an internal gear pump according to the preamble of claim 1.
  • EP-A-0474001 contains no explicit teaching or other information in this regard. The representation is therefore considered to be random. Such a design proves to be wrong, since very high pressure peaks occur in the wing foot wells of the inner wheel, which at best are associated with an unpleasant noise, at worst with an impermissible load on the pump.
  • the invention has for its object to bring about a substantial reduction in noise.
  • This task is aimed in particular at pumps of the following type:
  • the outer wheel is mounted stationary and rotatably, the inner wheel is freely rotatable on an eccentric.
  • the eccentric sits eccentrically on the drive shaft, which is mounted concentrically to the outer wheel.
  • the dead space is the volume of the tooth cells that arise at a pair of teeth in engagement at the bottom dead center.
  • the gap with its narrow gap width extends in any case between the tip circle of the outer wheel and the pitch circle.
  • An increase in the gap width is provided between the pitch circle and the tip circle of the inner wheel.
  • the design of the outlet channels is also of particular importance.
  • the outlet channel is the connection channel between the respective tap and the Pressure chamber in which the oil from all cells is collected and passed on to consumers.
  • the outlet channels or outlet bores must be short, preferably shorter than 5 mm, before they open into the pressure chamber, in which the pressure can settle without resistance.
  • 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 stop laterally.
  • 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, whose central axis 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 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 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 in the adjacent end face of the Eccentric 11 is introduced in the area of 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 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 driving 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. 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 in the axial direction two outlet bores (outlet channels) 25.1 and 25.2 are adjacent to each other for each tooth gap.
  • the outlet bores are each arranged in parallel radial planes.
  • Each outlet bore opens into a pocket 38.
  • This pocket is introduced into the outer wheel 6 from the outer circumference of the outer wheel.
  • Each pocket is characterized by the fact that it has a larger cross section than the respective outlet bore 25.1 and 25.2, the diameter of which is as small as possible and forms a diameter step with the pocket.
  • the pocket is circular cylindrical like the outlet bore.
  • the pocket can also be designed as a groove which is milled into the outer circumference of the outer wheel in the circumferential direction or axially parallel, the bottom of the groove is wider than the diameter of the outlet bores 25.1 and 25.2, is flat and preferably intersects the outlet bores at a right angle.
  • a check valve is housed in each pocket 38 thus formed. It can be z. B. act as a spring tongue when the pocket 38 is designed as a groove. Such an embodiment is the subject of Fig. 4.
  • the pocket can also be designed as a groove which extends over the entire circumference of the outer wheel and whose width is greater than the diameter of the outlet bores 25.1 and 25.2.
  • the bottom of the groove of this circumferential groove is covered by an elastic valve ring, which covers all the outlet bores which open onto the bottom of the groove (see FIGS. 1, 2).
  • the valve ring is preferably cut in an axial plane and one end is held in place by a rivet while the other end is free to move.
  • 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 check valves 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.
  • 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.
  • Fig. 3 shows the formation of the teeth based on the detailed radial section of a tooth of the inner wheel, which engages between two adjacent teeth of the outer wheel at bottom dead center.
  • the tooth 39 of the inner wheel almost completely fills the tooth gap between the two teeth 40 of the outer wheel.
  • the left flank of tooth 39 is referred to as the driving flank 41.
  • the flank 41 transmits the torque to the inner wheel by contact with the corresponding counter flank of the external tooth. There is therefore no play between the driving flanks of the inner tooth 39 and the outer tooth 40.
  • the flank 42 which is not driving, does not form a further passage, as usual, but a narrow gap with the corresponding counter flank of the outer tooth 40.
  • the tooth root spaces 43 and 44 are connected to one another via this gap, which has the quality of a sealing gap.
  • 43 is the footwell of the outer wheel (outer footwell) and 44 the footwell of the inner wheel (inner footwell).
  • the gap width is 20 to 60 ⁇ m.
  • the tooth flank of the inner tooth 39 is withdrawn, so that the foot space 43, ie the outer cell 43, results over the width of the head and the non-driving flank 42 outside the pitch circle 45.
  • the inner footwell (inner cell) 44 is formed in that only the top flank of the outer tooth is withdrawn from the bottom of the tooth space.
  • the outer cell and inner cell have a width between 60 ⁇ m and 300 ⁇ m.
  • the outlet bore 25 is as short as is responsible for strength reasons, preferably shorter than 5 mm.
  • the outlet bore 25 opens into a pocket 38.
  • the pocket 38 is of circular cylindrical design.
  • the diameter of the pocket 38 is larger than the diameter of the outlet bore 25.
  • the diameter step between the pocket 38 and the outlet bore 25 is flat and designed as a valve seat.
  • a check valve 26 rests on this valve seat.
  • This check valve is designed as a circular cylindrical valve plate. It is loaded by a spring 46.
  • the spring 46 is supported on the outside on the spring holder 47.
  • the spring holder is attached to the outer circumference of the outer wheel. It is a bracket that spans the pocket 38.
  • the pocket 38 is designed as an axially parallel groove.
  • This groove is made in the outer circumference of the outer wheel.
  • two outlet bores 25.1 and 25.2 open.
  • the bottom of the groove is flat.
  • a spring plate is attached centrally as an outlet valve 26.
  • the two free ends of the spring plate rest resiliently on the outlet bores 25.1 and 25.2. 3 and 4 ensure that the outlet bores 25 have only a very small volume to have.
  • the volume is limited on the one hand by the required outlet cross-section and on the other hand by strength considerations. In this context, the volume of the outlet bores is minimized.
  • the outlet bore is understood to mean the channel section between the external tooth cell space and the check valve.
  • the bag represents part of the pressure space insofar as it also allows the pressure to spread without resistance.

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

Claims (4)

  1. Pompe à engrenages intérieurs pour liquides hydrauliques, dans laquelle chaque cellule de dent est respectivement pourvue d'un canal d'évacuation (25) et d'une soupape d'évacuation (26), et dans laquelle les cellules de dents sont très petites au point mort bas de la région d'engagement, caractérisée en ce que les dents du pignon intérieur (14) et du pignon extérieur (6) sont configurées de telle sorte qu'au point mort bas de la région d'engagement, les flancs non entraîneurs des dents (39, 40) qui se trouvent en prise forment un interstice d'une largeur de 20 à 60 µm.
  2. Pompe à engrenages intérieurs selon la revendication 1, caractérisée en ce que l'interstice s'élargit, radialement à l'extérieur du cercle primitif, à une largeur supérieure à 60 µm, mais inférieure à 300 µm.
  3. Pompe à engrenages intérieurs selon la revendication 1 ou 2, caractérisée en ce que chaque canal d'évacuation (25) possède une longueur inférieure à 5 mm entre la cellule de dent et la chambre de refoulement.
  4. Pompe à engrenages intérieurs selon une des revendications 1 à 3, caractérisée en ce que chaque canal d'évacuation (25) part radialement des entredents du pignon extérieur et débouche dans une poche respective (38), en ce que la poche (38) est pratiquée dans le pignon extérieur (6) à partir de la périphérie extérieure de ce dernier, et en ce qu'une soupape d'évacuation (26) sollicitée par ressort est montée dans chacune des poches (38).
EP93110326A 1992-06-29 1993-06-29 Pompe à engrenages internes pour fluide hydraulique Expired - Lifetime EP0579981B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4221326 1992-06-29
DE4221326 1992-06-29

Publications (2)

Publication Number Publication Date
EP0579981A1 EP0579981A1 (fr) 1994-01-26
EP0579981B1 true EP0579981B1 (fr) 1996-10-23

Family

ID=6462083

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93110326A Expired - Lifetime EP0579981B1 (fr) 1992-06-29 1993-06-29 Pompe à engrenages internes pour fluide hydraulique

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EP (1) EP0579981B1 (fr)
DE (1) DE59304256D1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1271052B (it) * 1993-11-18 1997-05-26 Pompa ad ingranaggi interni con sporgenze volumetriche
WO2016149246A1 (fr) 2015-03-16 2016-09-22 Saudi Arabian Oil Company Pompe type gérotor à paroi égale pour des applications de forage
DE102016121240A1 (de) 2016-11-07 2018-05-09 Nidec Gpm Gmbh Elektrische Gerotorpumpe und Herstellungsverfahren für dieselbe
US11371326B2 (en) 2020-06-01 2022-06-28 Saudi Arabian Oil Company Downhole pump with switched reluctance motor
US11499563B2 (en) 2020-08-24 2022-11-15 Saudi Arabian Oil Company Self-balancing thrust disk
US11920469B2 (en) 2020-09-08 2024-03-05 Saudi Arabian Oil Company Determining fluid parameters
US11644351B2 (en) 2021-03-19 2023-05-09 Saudi Arabian Oil Company Multiphase flow and salinity meter with dual opposite handed helical resonators
US11591899B2 (en) 2021-04-05 2023-02-28 Saudi Arabian Oil Company Wellbore density meter using a rotor and diffuser
US11913464B2 (en) 2021-04-15 2024-02-27 Saudi Arabian Oil Company Lubricating an electric submersible pump
US11994016B2 (en) 2021-12-09 2024-05-28 Saudi Arabian Oil Company Downhole phase separation in deviated wells

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB223257A (en) * 1923-04-16 1924-10-16 Hill Engineering Company Inc Improvements in rotors for rotary compressors and the like
US3139835A (en) * 1962-08-15 1964-07-07 Davey Compressor Co Rotary pump or motor
DE3444859A1 (de) * 1983-12-14 1985-06-27 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Rotationszellenpumpe fuer hydrauliksysteme
DE3869737D1 (de) * 1987-11-07 1992-05-07 Barmag Barmer Maschf Innenzahnradpumpe.
EP0474001B1 (fr) * 1990-09-01 1995-01-04 BARMAG LUK AUTOMOBILTECHNIK GMBH & CO.KG Pompe à engrenages internes pour fluide hydraulique

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Publication number Publication date
EP0579981A1 (fr) 1994-01-26
DE59304256D1 (de) 1996-11-28

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