EP1701038A2 - Pompe à engrenages internes - Google Patents

Pompe à engrenages internes Download PDF

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Publication number
EP1701038A2
EP1701038A2 EP05026417A EP05026417A EP1701038A2 EP 1701038 A2 EP1701038 A2 EP 1701038A2 EP 05026417 A EP05026417 A EP 05026417A EP 05026417 A EP05026417 A EP 05026417A EP 1701038 A2 EP1701038 A2 EP 1701038A2
Authority
EP
European Patent Office
Prior art keywords
support
support ring
internal gear
web
ring
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.)
Granted
Application number
EP05026417A
Other languages
German (de)
English (en)
Other versions
EP1701038B1 (fr
EP1701038A3 (fr
Inventor
Reinhard Dipl.-Ing. Pippes (FH)
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.)
Eckerle Industrie Elektronik GmbH
Original Assignee
Eckerle Industrie Elektronik GmbH
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 Eckerle Industrie Elektronik GmbH filed Critical Eckerle Industrie Elektronik GmbH
Publication of EP1701038A2 publication Critical patent/EP1701038A2/fr
Publication of EP1701038A3 publication Critical patent/EP1701038A3/fr
Application granted granted Critical
Publication of EP1701038B1 publication Critical patent/EP1701038B1/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
    • F04C15/0003—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
    • F04C2/101—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 with a crescent-shaped filler element, located between the inner and outer intermeshing members

Definitions

  • the invention relates to an internal gear machine (pump or motor) with a multi-part housing, with two housed in the housing meshing gears, which is an externally toothed pinion and a pinion with the running, internally toothed ring gear, and with at least one between axial side surfaces the gear wheels and a housing part arranged sealing disc, which is pressed by a pressure on its side facing away from the gears and located on the high pressure side pressure field with high pressure on the side surfaces of the gears can be pressed, from which a located between the housing part and the sealing disc gap, and with one of the sealing of the gap serving around the pressure field circumferential seal which is supported on its side facing the gap by a circumferential support ring.
  • axial disks sealing plates In internal gear high pressure machines, ie formerly leopardradhochtulpumpen or réelleffyradhoch horrmotoren, also referred to as axial disks sealing plates are used, which avoid the operational and production-related gap between the end faces of the gears to the housing wall.
  • the seal is made by appropriate mold seals, which preferably consist of an elastomeric material.
  • the pressure field is located in the sealing washer or in the housing part.
  • the necessarily existing gap between the housing wall and the axial disc can lead to a so-called gap extrusion of these seals, up to their complete destruction.
  • support rings usually have a square or rectangular cross-section.
  • this design of the pressure field is extreme by machining costly, since only small diameter cutters can be used.
  • a piston ring with a separate seal can also be provided a sealing, triangular or trapezoidal molded rubber part, which is reinforced non-positively with an angled sheet metal part.
  • the support ring is designed with at least one extending in the axial direction and the seal inwardly engaging behind and positively supporting support web.
  • a particularly simple and cost-effective production of a seal receiving recess in the housing part or in the sealing washer can be achieved, or is the production of Recess in non-cutting shaping, such as casting, spraying and the like significantly simplified. Nevertheless, an advantageous support of the seal inwards towards the center of the pressure field can be achieved.
  • the preferably elastomeric seal and the support ring are particularly simple and inexpensive to produce separately, handled and assembled or disassembled.
  • the support bar is integrally connected to the support ring.
  • the support ring with support bar can be produced particularly inexpensively.
  • the support bar can be designed as a support ring web. Apart from the fact that a ring-shaped support bar can be made even more cost-effective, can be achieved with such a support bridge advantageous elasticity conditions.
  • the support web or a plurality of support webs delimit only a part of the pressure field, preferably in an area in which one or more axial pressure outputs lead into the pressure field, while another part of the by the preferably a semi-acicular outer contour having support ring limited pressure field without support web or support webs, that is designed without support web.
  • this area of the support ring can be designed without a support web which supports the seal inwardly.
  • Such a design without a support web or without support webs in this area also has the advantage that thereby the elasticity of the support ring is greater than in the provided with one or more support webs region of the support ring, thereby resulting in an improved investment of the support ring on the inner circumference of this receiving recess comes.
  • the support ring is divided by at least one transverse connecting web in at least two ring parts, of which at least one ring part without support web, that is formed without support web, while at least one other ring Part is designed with the preferably one or more axial pressure outputs surrounding and preferably a semi-crescent-shaped outer contour having support web.
  • the support ring Through the cross-connecting web, the support ring has a certain elasticity, but at the same time prevents compression of the support ring in this area. This is especially important for high dynamic pressure changes, to avoid a complete “disappearance" or detachment of the seal.
  • the cross-connecting web is designed as a bow, preferably as a circular arc. This allows even better compensation of a certain elasticity and the associated possibility of a tolerance compensation of both the pressure field and the support ring itself.
  • a designed with such a cross-connecting web support bar is particularly simple and inexpensive to produce.
  • the support ring when the support ring has a semi-crescent-shaped or crescent-shaped outer contour, it is advantageous if the support ring in the region of its sickle tip or optionally sickle tips has a reduced cross-sectional area, in particular a reduced width, compared to adjacent edge regions. As a result, sufficient elasticity can also be achieved in this area or these areas.
  • the support ring on its inner circumference inwardly projecting material accumulations, preferably rounded or semicircular knobs, which form Kraftangriffsstellen for Auswerferile a tool, preferably an injection mold for the production of the support ring.
  • a tool preferably an injection mold for the production of the support ring.
  • the support ring is designed as an angle support ring with an L-shaped cross-section. This can be used as a seal a particularly cost-effective and easy to assemble or disassemble O-ring direction with circular cross-section. Such an angular support ring can be produced in a particularly simple and cost-effective manner.
  • the internal gear pump 20 shown in Figures 1 to 3 has a housing 30 which is composed of an annular central part 31, which includes a pump chamber 32 radially, a first cover part 32, a bearing part 23 and a second cover part 34.
  • the bearing part 23 and the cover part 34 define the pump chamber 32 in the axial direction.
  • the middle part 31 engages over the bearing part 23 and the cover part 34 in the region of an outer recess 15.
  • the bearing part 23 has a through bore 36 into which a sliding bearing 37 is pressed. With the bore 36 is aligned a blind bore 38 of the cover part 34, in the likewise a sliding bearing 37 is pressed. In the two sliding bearings 37, a drive shaft 39 of the pump is mounted.
  • the cover part 33 has a bore 21 in which a radial shaft seal 22 is inserted. It is understood, however, that instead of the bearing part 23, if appropriate, only a second cover part can be used, which can then of course be provided with a bore for pressing in a sliding bearing for the drive shaft 39.
  • An externally toothed pinion 40 is fixed within the pumping chamber 32 on the drive shaft 39 or made in one piece therewith.
  • the pinion 40 is located within an internally toothed ring gear 41 whose axis is arranged eccentrically to the axis 27 of the pinion 40 and which is mounted on its outer periphery in the central part 31 of the housing 30.
  • center plane 42 mesh the two gears 40 and 41 with each other, between which, moreover, a crescent-shaped space 43 is.
  • This free space 43 is approximately half filled by a two-piece filler 44 which bears against the teeth of the pinion 40 and the ring gear 41. It is understood, however, that the invention can also be used in filler-less internal gear machines.
  • the filler 44 is rotatably mounted on axially extending bearing body 26 to axial bolts not shown in detail in the cover part 34 and in the bearing part 23.
  • the axial extent of the filler 44 is consistent with the axial extent of the two gears 40 and 41 match.
  • the pump of Figures 1 to 3 is constructed so that the pinion 40 in operation, as viewed in Figure 3, counterclockwise (arrow) must be driven.
  • the ring gear 41 then rotates counterclockwise.
  • hydraulic fluid migrates along with the tooth gaps on the filler 44 and enters the tooth engagement region of the two gears 40, 41.
  • the hydraulic fluid is displaced by not shown in detail radial bores of the ring gear 41 into the pressure channel 47.
  • hydraulic fluid is conveyed through axial pressure exits 77, 78, 79 in axial adjacent to the end faces 24, 25 of the gears 40, 41 sealing washers 55 through into an axial pressure outlet 48.
  • radial pressure channel 47 and axial pressure outlet 48 instead of the above-described embodiment with radial pressure channel 47 and axial pressure outlet 48, alternatively only one radial pressure channel or only one axial pressure outlet can be provided. It is further understood that the radial pressure channel 47 or the pressure outlet can form the working connection of the internal gear pump 20 and / or that the axial pressure outlet 48 can serve for the control of valves integrated in the cover part 34, not shown here.
  • a sealing plate 35 is arranged here, of a between her and the cover part 34 and the bearing part 23 existing pressure field 56 axially against the gears 20 and 21 is pressed.
  • Each sealing plate 35 closely surrounds the drive shaft 39 and the bearing body 26 of the filler 44 which extends in the axial direction through holes 57 of the sealing discs 55 and is thereby secured in position in a plane perpendicular to the axis 27 of the drive shaft 39 ,
  • a pressure field 56 is formed by a recess 45 in the cover part 34 or in the bearing part 23, wherein the recesses 45 are formed with grooves 58 and 61 merging into one another (FIGS. 6 and 7.
  • the pressure field 56 has, for example, from FIG , A semi-crescent shape and extends approximately from the pivot points where the filler pin 26 is connected to the filler 44, close to the center plane 42 zoom.
  • the limited by Ausappelungsr section 52 semi-crescent-shaped inner contour of the recesses 45 substantially corresponds to the semi-crescent-shaped outer contour 72 of a support ring 71, as shown in particular in FIG 8 is shown.
  • the recess 45 is sealed by a circumferential at its edges 52 sealing arrangement to a gap 70 between the sealing washer 55 and the cover member 34 and the bearing member 23 through.
  • the recess 45 In the area of the sealing arrangement, the recess 45 always has the same depth 53 and is bounded laterally by a recess 51 projecting here, as well as by its perpendicular edges 52.
  • the transition of the Ausappelungsgrundes 51 to the edges 52 is designed rounded.
  • an elastomeric seal 64 is inserted, which is designed here as a ring seal with a circular cross-section and accordingly having a diameter O-ring.
  • This seal 64 is supported outwardly at the edges 52 of the recess 45. So that the seal 64 does not migrate into the column 70 extending from the pressure field 56 or the recess 45 between the sealing disk 55 and the cover part 34 or the bearing part 23, the support ring 71 is provided. This is preferably made of plastic and runs around the pressure field 56, so surrounds this.
  • the support ring 71 has a semi-crescent-shaped outer contour (FIG. 8) and is here designed with two ring parts 86 and 87 which are divided off by a cross connection web 85.
  • the cross connecting web 85 is designed here with a circular arc 88.
  • the support ring 71 is formed on its entire circumference with a support and sealing web 84, which prevents a gap extrusion of the seal 64 in the gap 70.
  • the support and sealing web 84 has a rectangular shape and a height 96.
  • the support ring 71 In the ring part 87 of the support ring 71 this is designed only as a support and sealing web 84. In this area points the supporting and sealing web 84 has a rectangular cross section (FIG. 7). In contrast, the support web 71 has in its other ring part 86 designed as an annular web support web 75 which extends perpendicular to the support and sealing web 84 and from the axial side surfaces of the gears 40, 41 away ( Figures 4 and 6). , The support ring 71 is designed in this area with an axially extending and the seal 64 inwardly engages behind and positively supporting, annular support rib 75 which is integrally connected here with the support and sealing web 84.
  • the support bar 75 likewise has a semi-crescent-shaped outer contour (FIG. 8).
  • the height 99 of the support bar 75 is slightly smaller than the diameter or the height of the seal 64, so that the sealing function is not impaired, but at the same time sufficient support of the seal 64 is achieved inwardly, d. H. in a direction normal to the edges 52 of the recess 45 forming edge surfaces, or to the center of the pressure field 56 out.
  • the height 97 of the support web 75 is equal to or smaller than the depth 53 of the recess 45 and the pressure field 56.
  • the support and sealing web 84 preferably has a width 100 which is greater than the diameter or the width of the seal 64th in that the seal 64 is subjected to compressive forces essentially only or exclusively between the recess bottom 51 of the recess 45 and the opposing pressure surface 66 of the support and sealing web 84, wherein there is sufficient space for the purpose of lateral deformation possibility for the seal 64.
  • the transition between the seal to the 64th pointing pressing surface 66 of the sealing web 84 to the support surfaces 67 of the support web 65 for the seal 64 is rounded.
  • the support ring 71 is here completely continuous, d. H. closed trained. It is understood, however, that the support ring also "open" as in DE 43 45 273 C2, d. H. preferably can be designed with two overlapping ends.
  • the annular support web 75 encloses only a part 76 of the pressure field 56 in a region in which a plurality of axial pressure outputs, here in the form of the pressure channel 77 and the two control bores 78 and 79 in the sealing disk 55, into the pressure field 56 lead.
  • a plurality of axial pressure outputs here in the form of the pressure channel 77 and the two control bores 78 and 79 in the sealing disk 55, into the pressure field 56 lead.
  • highly dynamic flow processes with corresponding pressure peaks can occur during initial startup and / or during operation of the internal gear pump 20.
  • the support ring 75 running around the pressure exits 77, 78, 79 is provided to support the seal 64 inwards.
  • the support ring 71 is designed in a region which adjoins the sickle tip 74, without supporting web or support web free, so assumes there only the function of a support and sealing web to avoid a gap extrusion of the seal 64 to the outside through the gap 70th ,
  • the support ring 71 has a width 93 or a cross-sectional area, which in relation to the widths 92 and 93 or cross-sectional areas of the immediately adjacent edge portions 89, 90 of the support ring 71 is reduced to ensure sufficient elasticity of the support ring 71 in this area.
  • the support ring 71 has on its inner circumference 94 here eight inwardly projecting accumulations of material in the form of each semicircular knobs. These form force application points for ejector parts, not shown in detail, for example, an injection mold, which is used for the production of the support ring 71 made of plastic. As a result, any ejector marks do not hinder the sealing function of the support ring 71. It is understood, however, that the support ring 71 may also be made of metal.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP20050026417 2005-02-02 2005-12-03 Pompe à engrenages internes Expired - Lifetime EP1701038B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200510004657 DE102005004657A1 (de) 2005-02-02 2005-02-02 Innenzahnradmaschine

Publications (3)

Publication Number Publication Date
EP1701038A2 true EP1701038A2 (fr) 2006-09-13
EP1701038A3 EP1701038A3 (fr) 2010-09-22
EP1701038B1 EP1701038B1 (fr) 2012-03-07

Family

ID=36293427

Family Applications (1)

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EP20050026417 Expired - Lifetime EP1701038B1 (fr) 2005-02-02 2005-12-03 Pompe à engrenages internes

Country Status (2)

Country Link
EP (1) EP1701038B1 (fr)
DE (1) DE102005004657A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103370539A (zh) * 2011-01-06 2013-10-23 伊顿公司 半堵塞式星形齿轮转子及其组装方法
CN105980710A (zh) * 2014-03-06 2016-09-28 日本油泵株式会社 泵装置
CN106286287A (zh) * 2015-05-11 2017-01-04 比亚迪股份有限公司 叉车、内啮合齿轮泵及用于其的轴向补偿组件
US11680567B1 (en) 2020-02-27 2023-06-20 Parker-Hannifin Corporation Hydraulic gear pump with axial compensation

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009045227A1 (de) * 2009-10-01 2011-04-21 Robert Bosch Gmbh Innenzahnradpumpe für eine hydraulische Fahrzeugbremsanlage
DE102012213771B4 (de) * 2012-08-03 2025-04-24 Robert Bosch Gmbh Innenzahnradpumpe
DE102013201384A1 (de) * 2013-01-29 2014-07-31 Robert Bosch Gmbh Innenzahnradpumpe
DE102013204616B4 (de) 2013-03-15 2021-12-09 Robert Bosch Gmbh 2Innenzahnradpumpe
DE102015105933B4 (de) * 2015-04-17 2018-04-26 Schwäbische Hüttenwerke Automotive GmbH Pumpe
DE102018212497B4 (de) * 2018-07-26 2026-01-29 Eckerle Technologies GmbH Fluidfördereinrichtung
DE102019217049A1 (de) * 2019-11-06 2021-05-06 Robert Bosch Gmbh Innenzahnradmaschine mit hydrostatisch abgestütztem inneren Dichtungsteil am Füllstück

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4345273C2 (de) * 1993-07-03 1997-02-06 Eckerle Rexroth Gmbh Co Kg Hydraulische Zahnradmaschine (Pumpe oder Motor), insbesondere Innenzahnradmaschine
DK172177B1 (da) * 1995-11-27 1997-12-15 Danfoss As Aksial tætning
DE10059059A1 (de) * 2000-11-28 2002-05-29 Continental Teves Ag & Co Ohg Innenzahnradpumpe
DE102004016440B4 (de) * 2003-04-14 2014-02-13 Schaeffler Technologies AG & Co. KG Fördereinrichtung

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103370539A (zh) * 2011-01-06 2013-10-23 伊顿公司 半堵塞式星形齿轮转子及其组装方法
CN103370539B (zh) * 2011-01-06 2017-02-22 伊顿公司 半堵塞式星形齿轮转子及其组装方法
CN105980710A (zh) * 2014-03-06 2016-09-28 日本油泵株式会社 泵装置
CN106286287A (zh) * 2015-05-11 2017-01-04 比亚迪股份有限公司 叉车、内啮合齿轮泵及用于其的轴向补偿组件
US20180087505A1 (en) * 2015-05-11 2018-03-29 Byd Company Limited Forklift, internal gear pump, and axial compensation component thereof
EP3295030A4 (fr) * 2015-05-11 2018-10-31 BYD Company Limited Chariot élévateur à fourche, pompe à engrenages internes et composant de compensation axial associé
CN106286287B (zh) * 2015-05-11 2018-12-21 比亚迪股份有限公司 叉车、内啮合齿轮泵及用于其的轴向补偿组件
US11680567B1 (en) 2020-02-27 2023-06-20 Parker-Hannifin Corporation Hydraulic gear pump with axial compensation

Also Published As

Publication number Publication date
EP1701038B1 (fr) 2012-03-07
EP1701038A3 (fr) 2010-09-22
DE102005004657A1 (de) 2006-08-03

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