EP2154374B1 - Machine hydraulique à roue dentée - Google Patents

Machine hydraulique à roue dentée Download PDF

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Publication number
EP2154374B1
EP2154374B1 EP09009849.2A EP09009849A EP2154374B1 EP 2154374 B1 EP2154374 B1 EP 2154374B1 EP 09009849 A EP09009849 A EP 09009849A EP 2154374 B1 EP2154374 B1 EP 2154374B1
Authority
EP
European Patent Office
Prior art keywords
gear machine
sections
hydraulic gear
machine according
supporting element
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.)
Active
Application number
EP09009849.2A
Other languages
German (de)
English (en)
Other versions
EP2154374A3 (fr
EP2154374A2 (fr
Inventor
Sebastian Tetzlaff
Guido Bredenfeld
Ulrich Lendl
Stefan Cerny
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
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Publication of EP2154374A3 publication Critical patent/EP2154374A3/fr
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Publication of EP2154374B1 publication Critical patent/EP2154374B1/fr
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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
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or 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
    • 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
    • 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
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms

Definitions

  • the invention relates to a hydraulic gear machine according to the preamble of patent claim 1.
  • a gear machine shown with a housing in which two intermeshing and mounted in bearing bushes or bearing bodies gears are arranged, wherein the housing is closed with housing covers each end face.
  • a sealing groove with an axial field seal received therein is formed in the bearing body on the side facing the housing cover.
  • the axial field seal has a supported by a support ring elastic seal.
  • the support ring has two substantially L-shaped support portions which are interconnected via a plurality of connecting webs. Together, the L-shaped support sections form an approximately U-shaped cross section.
  • the outer walls of the support ring abut on the housing cover and on side walls of the seal groove approximately and the seal is substantially supported on inner walls of the support ring.
  • the disadvantage here is that the support ring has a high mechanical rigidity and thus unevenness or gaps can be compensated for example in the inner wall region of the seal only partially by the support ring, and there is a risk that the seal at high pressures between, for example, the inner wall of the seal groove and the Outside wall of the support ring moves, which can lead to damage and early wear of the seal.
  • the support member has in one embodiment, a U-shaped and in another a L-shaped cross-section.
  • a plurality of recesses can be distributed regularly over the longitudinal extension of the support element on a lateral boundary edge and on the U-shaped boundary edge on both lateral edges. Through the recesses, the contact surface of the support element is reduced to the inner walls of the sealing groove, whereby the surface pressure in this area between the support member and the inner wall is increased.
  • a disadvantage of this solution is also that the support element has a high mechanical rigidity in the contact area and thus can hardly compensate for unevenness, gaps, etc. in the inner wall region of the sealing groove, which can lead to the consequences explained above.
  • Object of the present invention is to provide a hydraulic gear machine, which has a simple structure, robust and a high sealing effect having Axialfelddichtung.
  • a hydraulic gear machine has a housing for receiving two intermeshing and bearing bushes mounted in gears.
  • the housing is closed at the front with a housing cover.
  • a sealing element is provided that is supported by a designed as an angle profile with an axial and a radial leg support member.
  • At least one of the legs has sections in the longitudinal extent at least a reduced cross section for Iokalen reduction of mechanical rigidity.
  • This solution has the advantage that the support element in areas where, for example, gaps or other seal critical areas occur, a reduced cross-section and thus has a lower mechanical rigidity. As a result, this can easily be adapted to the seal-critical areas by essentially elastic deformations. A rearward migration of the support element through the sealing element, which is explained in the upper prior art, is avoided.
  • the support element may preferably have a substantially L-shaped cross section.
  • the reduced cross section of the support member is formed by a chamfer of the axial leg of the support member in the adjacent region to the sealing element.
  • a bevel is on the one hand easy to manufacture and leads to the other to a higher elasticity of the axial leg, by the reduced cross-section.
  • the axial leg of the support element in the region of the reduced cross-section of the support element is trapezoidal.
  • the sealing element and the support member may be formed in approximately spectacle shape with two sections of the sliding bearing rotating ring sections, with a connecting the ring sections connecting web and two away from the sliding bearings angled end sections.
  • the reduced cross-sections can be arranged approximately in the transition region between end sections and ring sections and between ring sections and approximately half the extension length of a respective annular section, since, for example, gaps in the sealing area occur in these areas.
  • a tight fit of the sealing member and the support member is made possible when the sealing member is supported approximately at inner edges and stinking edges of the support member and the support member with outer edges substantially on the housing cover and partially abutting the slide bearings in approximately.
  • the sealing and the support element between a low pressure region and a high pressure region is arranged.
  • the gear machine may be an external gear machine.
  • FIG. 1 a designed as a gear machine 1 hydraulic machine is shown having a machine housing 2, which is closed by means of a bottom plate 4 and a cover plate 6, which are formed as a housing cover.
  • the cover plate 6 of the gear machine 1 is penetrated by a drive shaft 8, on which a first gear 10 is disposed within the machine housing 2.
  • the first gear 10 is engaged with a second gear 12 which is rotatably mounted on an axle 14.
  • the drive shaft 8 and the axis 14 are each rotatably mounted in two plain bearings 16, 18 and 20, 22, which are respectively received in bearing bushes or bearing bodies 24, 26, 28 and 30 respectively.
  • the bearing bodies 24 and 28 and the bearing bodies 26 and 30 are connected to each other via a bolt 32 and 34, respectively, and together form a bearing glasses.
  • FIG. 2 shows an enlarged section I of the gear machine 1 in the region of the axial field seal 36 from FIG. 1 , where the illustration is rotated 90 ° clockwise.
  • the axial field seal 36 has a seal member 38 supported by an L-shaped support member 40.
  • the support member 40 has - seen in cross section - while a substantially parallel to the bottom or cover plate 4, 6 from FIG. 1 extending radial leg 42 and one approximately parallel to a rotational axis of the drive shaft 8 from FIG. 1 extending axial leg 44, wherein the sealing element 38 is supported on the one hand on an inner and end edge 46, 48 of the axial leg 44 and on the other at an inner and front edge 50, 51 of the radial leg 42 substantially.
  • the sealing and supporting element 38, 40 are in each case in an end face 52 or 53, facing the bottom and cover plate 4, 6, of the respective bearing bodies 24, 28 and 26, 30, see also FIG. 1 , introduced sealing recess or sealing groove 54 added.
  • the seal groove 54 is the sliding bearing 16 to 22 (see also FIG. 1 ) and is open in the FIG. 2 bounded by these and by the bottom or top plate 4, 6.
  • the support member 40 is inserted into the sealing groove 54, so that a radial outer edge 56 of the radial leg 42, see FIG. 2 at the in FIG. 1 shown cover plate 4 and bottom plate 6 and with an axial outer edge 57 of the axial leg 44 on the slide bearings 16, 20 and 18, 22 approximately abuts.
  • FIG. 3 is a section taken along the line II-II FIG. 1 shown, with only the bearing body 24 and the sliding bearing 16 are shown in a rotated clockwise by 90 ° view.
  • the remaining bearing body 26 to 30 off FIG. 1 are correspondingly mirrored.
  • the sealing groove 54 is introduced into the bearing body 24, so that with the Axialfelddichtung 36 from FIG. 1 a high is separated from a low pressure region of the gear machine 1.
  • An annular groove portion 60 of the sealing groove 54 extends in sections around the slide bearing 16 and has a serious angled end portion 62, which is towards in the FIG. 1 shown adjacent bearing body 28 extends, and a second angled end portion 64 which extends radially away from the sliding bearing 16 through to in FIG. 1 illustrated machine housing 2 extends.
  • Issues to be sealed areas are essentially a bearing gap 66 in the sliding bearing 16 and the respectively formed by the angled end portions 62 and 64 together with the sliding bearing 16 corner regions 68 and 70.
  • the seal member 38 see FIG. 2 to avoid between the support member 40 and, for example, the bearing gap 66 or the corner regions 68, 70, the support member 40 in these areas a reduced cross-section, which in the following FIG. 4 is explained in more detail.
  • FIG. 4 the spectacle-shaped support member 40 is shown in a bottom view. There are the radial end and inner edges 48, 50 visible.
  • the peripheral shape of the support member 40 and in this FIG. 4 Not shown sealing element 38 substantially corresponds to the shape of the sealing groove 54 FIG. 3 at two juxtaposed bearing bodies 24, 28 and 26, 30 (see FIG. 1 and 3 ).
  • Two ring sections 72, 74 of the support member 40 thereby rotate around the plain bearings 16, 20 and 18, 22 (see FIG. 1 and 3 ).
  • a connecting bridge 75 connects the Ring portions 72, 74 and each extending between two of the bearing body 24, 28 and 26, 30. End portions 76, 78 bend radially on the ring portions 72, 74 respectively from the slide bearings 16, 20, 18 and 22 to the outside.
  • the support element 40 now has several areas with a reduced cross-section for locally reducing the mechanical rigidity and increasing the elasticity. Sections of reduced cross-section are located substantially where the support member 40 is located at problematic areas to be sealed, as in FIG FIG. 3 explained, is present.
  • the reduced cross-sectional areas are essentially first crease areas 80, 82 between the ring sections 72 and 74 and the end sections 76 and 78, second crease sections 84, 86 between the connecting web 75 and the ring sections 72, 74 and ring sections 88, 90 approximately at half the length of a stiffener
  • the reduced cross-sectional areas 80, 82, 84, 86, 88 and 90 are described in the following FIG. 5a shown in more detail.
  • FIG. 5a shows a section along the line III-III and FIG. 5b a section along the line IV-IV respectively from the FIG. 4
  • FIG. 5a shows the cross section in the reduced cross-sectional areas 80, 82, 84, 86, 88 and 90.
  • the cross section of the axial leg 44 here is approximately trapezoidal and has a reduced cross-sectional area compared to the substantially rectangular cross-section of the axial leg 44 of the FIG.
  • the inner edge 46 is in this case angled at an angle e, for example 30 °, which is the intersection angle between outer edge 57 and inner edge 46, so that the end edge 48 of the axial leg 44 is reduced.
  • the mechanical stiffness of the axial leg 44 in FIG. 5a thus decreases in the direction of the reduced front edge 48.
  • the radial leg 40 in both cross sections in FIGS. 5a and 5b approximately at right angles. To give an indication of the geometric cross - sectional dimensions of the reduced cross section in FIG. 5a in comparison to the unreduced cross section in FIG. 5b to get some values are referred to below.
  • the minimum width d1 of the axial leg 40 from FIG. 5a is about 0.2cm and the width d2 of the axial leg 40 from FIG. 5b in about 0.8cm.
  • the support member 40 can from the FIG. 4 better in the bearing gaps 66 of the sliding bearing 16 and in the corner regions 68 and 70, respectively FIG. 3 fit and nestle.
  • a rearward migration of the support member 40 of the sealing element 38 from FIG. 2 is not or hardly possible anymore.
  • the support member 40 is both stiff enough on the one hand to support the hydraulic load and on the other hand flexible enough to close gaps and prevent seal wear.
  • a hydraulic gear machine having a housing for receiving two intermeshing and bearing bushes mounted in gears.
  • the housing is closed at the front with housing covers.
  • a sealing element is provided, which is supported by a support member.
  • the support element has sections in the longitudinal direction at least a reduced cross section for Iokalen reducing the mechanical rigidity.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • General Details Of Gearings (AREA)
  • Gear Transmission (AREA)

Claims (11)

  1. Machine hydraulique à roue dentée comprenant un boîtier (2) pour recevoir deux roues dentées (10, 12) s'engrenant l'une dans l'autre et supportées dans des douilles-paliers (24, 26, 28, 30), lequel est fermé du côté frontal par un couvercle de boîtier (4, 6), un élément d'étanchéité (38) et un élément de support (40) supportant l'élément d'étanchéité (38), réalisé sous forme de profilé coudé avec une branche axiale (44) et une branche radiale (42), étant prévus, caractérisée en ce qu'au moins l'une des branches (42, 44) présente en partie dans l'étendue longitudinale au moins une section transversale réduite pour réduire localement la rigidité mécanique.
  2. Machine hydraulique à roue dentée selon la revendication 1, dans laquelle l'élément de support (40) présente une section transversale essentiellement en forme de L.
  3. Machine hydraulique à roue dentée selon la revendication 2, dans laquelle la section transversale réduite de l'élément de support (40) est réalisée par un biseautage de la branche axiale (44) de l'élément de support (40) dans la région adjacente à l'élément d'étanchéité (38).
  4. Machine hydraulique à roue dentée selon la revendication 2 ou 3, dans laquelle la branche axiale (44) de l'élément de support (40) est trapézoïdale dans la région de la section transversale réduite de l'élément de support (40).
  5. Machine hydraulique à roue dentée selon l'une quelconque des revendications précédentes, dans laquelle l'élément d'étanchéité (38) et l'élément de support (40) sont disposés dans un évidement d'étanchéité (54) réalisé dans la douille-palier (24, 26, 28, 30) ou dans une lunette de palier présentant deux douilles-paliers (24, 28 respectivement 26, 30).
  6. Machine hydraulique à roue dentée selon l'une quelconque des revendications précédentes, dans laquelle des paliers lisses (16, 18, 20, 22) sont prévus entre les douilles-paliers (24, 26, 28, 30) et les roues dentées supportées dans celles-ci.
  7. Machine hydraulique à roue dentée selon la revendication 6 ou 7, dans laquelle l'élément d'étanchéité (38) et l'élément de support (40) sont réalisés approximativement en forme de lunettes avec à chaque fois deux portions annulaires (72, 74) entourant en partie les paliers lisses (16, 18, 20, 22), avec une nervure de connexion (75) reliant les portions annulaires (72, 74) et avec deux portions d'extrémité (78, 80) coudées à l'écart des paliers lisses (16, 18, 20, 22).
  8. Machine hydraulique à roue dentée selon la revendication 7, dans laquelle les sections transversales réduites sont disposées approximativement dans la région de transition entre les portions d'extrémité (78, 80) et les portions annulaires (72) et entre les portions annulaires (72, 74) et la nervure de connexion (75) et approximativement à la moitié de la longueur d'étendue d'une portion annulaire respective (72, 74).
  9. Machine hydraulique à roue dentée selon l'une quelconque des revendications 6 à 8, dans laquelle l'élément d'étanchéité (38) s'appuie approximativement contre des arêtes intérieures (46, 50) et contre des arêtes frontales (48, 51) de l'élément de support (40) et l'élément de support (40) s'applique approximativement avec des arêtes extérieures (56, 57) essentiellement contre le couvercle de boîtier (4, 6) et en partie contre les paliers lisses (16, 18, 20, 22).
  10. Machine hydraulique à roue dentée selon l'une quelconque des revendications précédentes, dans laquelle l'élément d'étanchéité (38) et l'élément de support (40) sont disposés entre une région basse pression et une région haute pression.
  11. Machine hydraulique à roue dentée selon l'une quelconque des revendications précédentes, la machine à roue dentée (1) étant une machine à roue dentée extérieure.
EP09009849.2A 2008-08-12 2009-07-30 Machine hydraulique à roue dentée Active EP2154374B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102008038766.5A DE102008038766B4 (de) 2008-08-12 2008-08-12 Hydraulische Zahnradmaschine

Publications (3)

Publication Number Publication Date
EP2154374A2 EP2154374A2 (fr) 2010-02-17
EP2154374A3 EP2154374A3 (fr) 2014-08-13
EP2154374B1 true EP2154374B1 (fr) 2016-03-16

Family

ID=41381912

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09009849.2A Active EP2154374B1 (fr) 2008-08-12 2009-07-30 Machine hydraulique à roue dentée

Country Status (2)

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EP (1) EP2154374B1 (fr)
DE (1) DE102008038766B4 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011016810A1 (de) * 2011-04-12 2012-10-18 Robert Bosch Gmbh Zahnradwellenanordnung
DE102013202606A1 (de) 2013-02-19 2014-08-21 Robert Bosch Gmbh Zahnradmaschine mit einer Lagerhülse, die mehrere Vorsprünge aufweist.
DE102013202917A1 (de) 2013-02-22 2014-08-28 Robert Bosch Gmbh Zahnradmaschine mit erhöhter Partikelrobustheit
DE102013202918A1 (de) 2013-02-22 2014-08-28 Robert Bosch Gmbh Zahnradmaschine mit einem Stützkörper für eine Axialfelddichtung
DE102013218758A1 (de) 2013-09-19 2015-03-19 Robert Bosch Gmbh Zahnradmaschine mit nicht-zylindrischer Lagerbohrung
DE102014212255A1 (de) 2014-06-26 2015-12-31 Robert Bosch Gmbh Außenzahnradmaschine mit Lagerkörpern, die geradlinig gleitbeweglich aneinander abgestützt sind

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10104621B4 (de) 2001-02-02 2014-07-24 Robert Bosch Gmbh Axialfeldabdichtung einer Zahnradmaschine
DE10118055A1 (de) 2001-04-11 2002-10-17 Bosch Gmbh Robert Hydraulische Arbeitsmaschine

Also Published As

Publication number Publication date
EP2154374A3 (fr) 2014-08-13
DE102008038766A1 (de) 2010-02-18
EP2154374A2 (fr) 2010-02-17
DE102008038766B4 (de) 2019-10-10

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