EP0628725A2 - Pompe à engrenages - Google Patents

Pompe à engrenages Download PDF

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Publication number
EP0628725A2
EP0628725A2 EP94113865A EP94113865A EP0628725A2 EP 0628725 A2 EP0628725 A2 EP 0628725A2 EP 94113865 A EP94113865 A EP 94113865A EP 94113865 A EP94113865 A EP 94113865A EP 0628725 A2 EP0628725 A2 EP 0628725A2
Authority
EP
European Patent Office
Prior art keywords
bearing
bearing body
channel
gear pump
pump according
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.)
Withdrawn
Application number
EP94113865A
Other languages
German (de)
English (en)
Other versions
EP0628725A3 (fr
Inventor
Peter Blume
Roger Stehr
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.)
Maag Pump Systems AG
Original Assignee
Maag Pump Systems AG
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 Maag Pump Systems AG filed Critical Maag Pump Systems AG
Priority to EP94113865A priority Critical patent/EP0628725A3/fr
Publication of EP0628725A2 publication Critical patent/EP0628725A2/fr
Publication of EP0628725A3 publication Critical patent/EP0628725A3/fr
Withdrawn legal-status Critical Current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
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0046—Internal leakage control
    • 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
    • F04C15/0088—Lubrication

Definitions

  • the present invention relates to a gear pump according to the preamble of claim 1.
  • the rotor shaft is led out of the housing, for example for coupling to a drive unit, it is endeavored to keep the absolute pressure in the lubricating medium at the lowest possible level axially behind the slide bearing to be able to keep the sealing effort for the lead-out shaft as low as possible.
  • the flow resistance for the lubricant, from the area behind the slide bearing back to the suction area of the pump, is at least essentially decisive for the absolute pressure that must occur behind the slide bearing in order to ensure the backflow.
  • the known provision of return bores in the pump housing is disadvantageous insofar as this results in relatively high flow resistances, due to the long flow paths, when the lubricating medium exits the sliding bearing and the returned lubricating medium enters the main flow of the medium.
  • radial connections are provided from the bearing gap to the return bores, preferably in the form of millings in the end faces of the bearing body facing away from the delivery space. in the form of millings in the end faces of the bearing body facing away from the delivery chamber.
  • the bearing body on the suction side of the pump has a squeeze groove on its end face, and the channel opens into it. It is thereby achieved that the local underpressure present in the area of the squeeze groove on the low-pressure or suction side contributes to the further reduction of the pressure axially behind the slide bearing, in addition to the reduction due to reduced flow resistance.
  • the channel can be realized holistically in the bearing body by an axial bore or by an axially extending groove on the Outer surface of the bearing body, which then forms the channel with the inner surface of the housing-side receiving bore for the bearing body, or can be formed by an axial groove on the inner surface of the receiving bore receiving the bearing body and the outer surface of the bearing body, or by azimuthally aligned grooves on each Surface of the bearing body and the surface of the mounting hole for the bearing body on the housing.
  • both slide bearing can be formed according to the invention on a gear pump according to the invention, for example the bearing of a shaft led out of the housing, both rotor shafts are advantageously mounted according to the invention at least on one side.
  • the channel can of course be provided in each bearing body as described above or by a groove in one and / or other of the bearing body surfaces mentioned.
  • the number of return channels to be provided is reduced in a gear pump with two of the slide-bearing rotor shafts on the same side in that the at least one channel connects the slide bearing ends of both slide bearings to the suction side of the pump.
  • the slide bearing on the gear pump according to claim 1 is preferably the slide bearing of a shaft led out of the housing.
  • an adjusting element for the backflow resistance in the channel for example an axially directed adjusting screw on the housing side, by means of which the opening cross section of the channel is adjusted behind the slide bearing.
  • a bearing body for a gear pump according to the invention is specified in claim 9, with a preferred embodiment variant in claim 10.
  • FIG. 1a and 1b schematically show a first embodiment variant of a gear pump according to the invention.
  • Fig. 1b of the delivery chamber Prior to the viewed image plane of Fig. 1b of the delivery chamber is shown in broken lines 3 of the gear pump with a suction-side inlet 5 and n pressure side outlet 5 h at the registered rotational direction of the rotor gear wheels.
  • the shaft 1 of one of the rotors is slidably supported on at least one side in a bearing body 7, the latter of which is non-rotatably seated in the housing 9 of the gear pump in a known manner.
  • the shaft under consideration is not led out of the housing, and in addition the bearing body 7 is separated from the delivery chamber 3 by a housing section 9 a .
  • an axially extending channel is provided, in the embodiment according to FIG.
  • a groove 11 is embedded in the outer surface 7 a of the bearing body 7, which, together with the inner surface 9 i of the receiving bore in the housing 9 for the bearing body 7 forms the axial channel mentioned.
  • a milling 12 enables the radial flow from the bearing gap 14 to the axial channel.
  • the channel is continued in the housing section 9 a into the delivery chamber 3 in such a way that it connects the area 13 behind the bearing body 7 to the delivery chamber on the suction side.
  • the flow of the lubricant Delivery medium is indicated with S in Fig. 1a.
  • the lubricant flows axially in the bearing gap 14 outwards to the section 13, therein to the inlet of the channel 11 and from the latter axially through the channel 11 to the suction side in the delivery chamber, preferably in the area of the separating gear teeth.
  • the pressure difference between the mouth of the channel 11 and section 13 is particularly high due to the suction pressure.
  • the channel 11 is in the immediate vicinity of the bearing gap 14, the flow paths in the section 13 to the confluence of the channel 11 in this section are minimal. As shown in dashed lines at 11a, it is readily possible to provide more than one channel in the embodiment shown in FIG. 1.
  • the axially provided return channel is either, as shown at 21, by an axial groove on the inner surface 9 i of the bearing body 7 receiving bore formed in the housing 9, cooperating with the outer surface 7 a of the bearing body, or there are both in the outer surface 7 a of the bearing body 7 and, and aligned, on the inner surface 9 i of the bearing body receiving bore in the housing 9 each have a groove incorporated as shown in dashed lines.
  • a plurality of return channels can be provided, possibly combined with those of the embodiment shown in FIG. 1.
  • FIG. 3 an illustration analogous to FIG. 2, the return channel 31 is completely incorporated as an axial bore in the bearing body 7.
  • Several such channels can also be provided here be and / or combined with channels of the embodiment shown in FIGS. 2 and 1.
  • FIG. 4 shows a preferred embodiment of the gear pump according to the invention, the return channel or channels being formed in one or, in combination, in several embodiments according to FIGS. 1 to 3.
  • the end face 7 s of the bearing body 7 forms the boundary surface of the Delivery chamber 3 with the meshing gears, one of which is indicated at 17. This results in the possibility of completely working the return duct, in particular in the embodiment according to FIG. 1 or 3, into the relatively small bearing body 7.
  • the flow paths shortened according to the invention for the conveying medium which is fed back into the main conveying flow and branched off as a lubricating medium provide the possibility of designing the bearing in such a way that a relatively low absolute pressure is sufficient in area 13, behind the sliding bearing, in order to prevent the backflow guarantee.
  • FIG. 5 where the preferred embodiment according to FIG. 4 is shown a guided through the housing 9 to the outside shaft 1 a. Due to the reduced pressure in section 13, the requirements for the seal in a sealing section 19 between section 13 and the environment are significantly reduced.
  • an embodiment according to FIGS. 1 to 3 is also particularly suitable on a shaft that is passed through to the outside.
  • FIG. 6 which in turn is based on an embodiment according to FIG. 4 for a shaft which has not been carried out or FIG. 5 for a shaft which has not been carried through, this is, however, according to FIGS formed channel 61, shown here in the construction shown in FIG. 3, adjustable in terms of its flow cross-section by, as is shown schematically, by means of an adjusting screw 21 in the housing 9, the inlet opening facing the section 13 is adjusted in the channel 61.
  • FIG. 7 schematically shows a particularly preferred embodiment of a gear pump according to the invention. Again the same reference numbers are used.
  • grooves are incorporated in both bearing bodies 7, as is known, which together form the squeeze groove 23 on the low pressure side.
  • there is negative pressure in the pump operation compared to the suction pressure in the channel 5 n , which promotes the backflow of the conveying medium used as a lubricant through the channel 71 a or 71 b opening into the groove 23.
  • each of the plain bearings with the bodies 7 'and 7''each have a channel 71 a and 71 b, in a preferred embodiment by either Nuteinarbeitung in the surfaces 10' and 10 '', a common channel for both bearings 71 c provided or, as indicated by dashed lines at 71 d , the V-shape for receiving the bearing bodies in the area of their common surfaces 10 ′, 10 ′′ is excluded in the housing 9, so that the return duct 71 d shown has an essentially triangular cross section is formed for both camps.
  • At least the shaft that is passed through is preferably supported according to the invention, in order to relieve the bushing seal 19 according to FIG. 5, or all four shafts are supported as described.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP94113865A 1994-09-05 1994-09-05 Pompe à engrenages. Withdrawn EP0628725A3 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP94113865A EP0628725A3 (fr) 1994-09-05 1994-09-05 Pompe à engrenages.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP94113865A EP0628725A3 (fr) 1994-09-05 1994-09-05 Pompe à engrenages.

Publications (2)

Publication Number Publication Date
EP0628725A2 true EP0628725A2 (fr) 1994-12-14
EP0628725A3 EP0628725A3 (fr) 1995-03-15

Family

ID=8216255

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94113865A Withdrawn EP0628725A3 (fr) 1994-09-05 1994-09-05 Pompe à engrenages.

Country Status (1)

Country Link
EP (1) EP0628725A3 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998002662A1 (fr) * 1996-07-12 1998-01-22 Courtaulds Fibres (Holdings) Limited Commande de la lubrification et de la temperature des paliers d'une pompe
EP0864045A4 (fr) * 1995-12-01 1999-02-24 Micropump Inc Pompe a fluide a paliers presentant des canaux de graissage
WO2003050418A1 (fr) * 2001-12-12 2003-06-19 Kreyenborg Verwaltungen Und Beteiligungen Gmbh & Co. Kg Pompe de refoulement pour milieux fluides
WO2003054393A1 (fr) * 2001-12-12 2003-07-03 Kreyenborg Verwaltungen Und Beteiligungen Gmbh & Co. Kg Pompe d'alimentation

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB322778A (en) * 1928-07-12 1929-12-12 British Celanese Improvements in or relating to processes of pumping artificial silk spinning solutions
GB1181224A (en) * 1966-06-20 1970-02-11 Dowty Hydraulic Units Ltd Gearing and Lubricating Means Therefor
GB1554262A (en) * 1975-06-24 1979-10-17 Kayaba Industry Co Ltd Gear pump
JP2613051B2 (ja) * 1987-05-07 1997-05-21 カヤバ工業株式会社 ギヤポンプ

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0864045A4 (fr) * 1995-12-01 1999-02-24 Micropump Inc Pompe a fluide a paliers presentant des canaux de graissage
WO1998002662A1 (fr) * 1996-07-12 1998-01-22 Courtaulds Fibres (Holdings) Limited Commande de la lubrification et de la temperature des paliers d'une pompe
WO2003050418A1 (fr) * 2001-12-12 2003-06-19 Kreyenborg Verwaltungen Und Beteiligungen Gmbh & Co. Kg Pompe de refoulement pour milieux fluides
WO2003054393A1 (fr) * 2001-12-12 2003-07-03 Kreyenborg Verwaltungen Und Beteiligungen Gmbh & Co. Kg Pompe d'alimentation
US6802702B2 (en) 2001-12-12 2004-10-12 Kreyenborg Verwal Tungen Und Beteiligungen Gmbh & Co. Kg Feed pump for fluidic media having sleeve bearing lubrication
US7018186B2 (en) 2001-12-12 2006-03-28 Kreyenborg Verwaltungen Und Beteilgungen Gmbh & Co. Kg Feed pump

Also Published As

Publication number Publication date
EP0628725A3 (fr) 1995-03-15

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