EP0789814B1 - Füllstücklose innenzahnradpumpe - Google Patents

Füllstücklose innenzahnradpumpe Download PDF

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Publication number
EP0789814B1
EP0789814B1 EP96932440A EP96932440A EP0789814B1 EP 0789814 B1 EP0789814 B1 EP 0789814B1 EP 96932440 A EP96932440 A EP 96932440A EP 96932440 A EP96932440 A EP 96932440A EP 0789814 B1 EP0789814 B1 EP 0789814B1
Authority
EP
European Patent Office
Prior art keywords
gear
annular gear
annular
internal
ring 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
EP96932440A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0789814A1 (de
Inventor
Otto Eckerle
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.)
Individual
Original Assignee
Individual
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
Priority claimed from DE19532226A external-priority patent/DE19532226C1/de
Application filed by Individual filed Critical Individual
Publication of EP0789814A1 publication Critical patent/EP0789814A1/de
Application granted granted Critical
Publication of EP0789814B1 publication Critical patent/EP0789814B1/de
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
    • 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
    • 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
    • F04C15/0007—Radial sealings for working fluid
    • F04C15/0019—Radial sealing elements specially adapted for intermeshing-engagement type machines or pumps, e.g. gear machines or pumps

Definitions

  • the invention relates to a filler-less internal gear pump with the features according to the preamble of Claim 1.
  • the invention is concerned with a design of the internal gear pump that leads to a leads to better sealing of the meshing teeth.
  • the groove guiding the hydraulic fluid, through which the Annular gap when the corresponding peripheral sections enter in the area of the groove hydraulic fluid is part-circular and overlaps on the front with the annular gap, whereby the hydraulic fluid in can flow in this direction.
  • the suction chamber connected relief groove similar design provided through which the annular gap in the peripheral sections, which reach the relief groove from the one in it prevailing pressure is relieved.
  • the eccentric bearing of the race relative to the ring gear making partial use of the existing one
  • the self-priming ability of the gear pump becomes an annular gap guaranteed or significantly improved.
  • the eccentricity is directed so that the center axis of the race is aligned is closer to the pinion axis than the ring gear axis. Due to this eccentricity, the spring elements biased unevenly, so that even in unpressurized Condition of the tooth heads of the pinion and ring gear are pressed tightly against each other.
  • Sealing surface formed e.g. can be ground, offer themselves as sealing elements metallic roles that result in a linear sealing contact. That’s why Circumferential sections with regard to their expansion in Circumferential direction and the resulting radial forces pretty much identifiable.
  • the object of the invention is based on the Basic ideas of the above-described construction of the known internal gear pump and while maintaining all related advantages a structurally simpler and to create functionally more effective design.
  • the radial open Breakthroughs of the ring gear expediently in a that Ring groove surrounding ring gear in the ring gear peripheral surface and / or in the inner race surface.
  • the circulation of the consisting of pinion, ring gear and race Running unit is accomplished by the fact that the Pinion driven ring gear with the race ring form-fitting is coupled. You can do this according to the entry described DE-C 44 21 255 on the peripheral surface of the Ring gear and / or on the inner surface of the race Driver elements can be provided that are form-fitting interlock. With the internal gear pump after the However, the present invention can be carried out separately Driver elements are dispensed with because of the Sealing elements located in the recording rooms themselves positive coupling of the ring gear with the race bring about.
  • FIGS. 1 to 4 Internal gear pump according to the invention each consist in essentially from one designated as a whole by 1 or 1 ' Housing, a running unit 2 or 2 'arranged therein, which consist of a race 3 or 3 ′ and a ring gear 4 or 4 'and a pinion 5 or 5', which on a shaft 6 or 6 'is rotatably attached.
  • the housing 1, 1 ' is made up of a central part 11 or 11' and two the front end of which is fastened housing covers 12, 13 or 12 ', 13' constructed, the inner surfaces of which each other form opposite housing walls.
  • the Housing cover 13 a suction channel 15, which consists of a first radial course bends axially and between in the suction chamber the teeth of the ring gear 4 and the pinion 5 opens.
  • the shaft 6 or 6 ' is rotatably supported in the housing covers 12, 13 or 12', 13 'by means of unspecified bearings.
  • the pinion 5 and the ring gear 4 are, as shown in FIG. 5, mounted relative to one another with an eccentricity e.
  • the eccentricity e ie the distance between the pinion axis MR and the ring gear axis M H , corresponds to the theoretical tooth geometry of the pinion and ring gear and requires play-free rolling or sliding of the toothings against one another.
  • the race 3 is received eccentrically in the housing middle part 11 relative to the ring gear 4, so that its axis of rotation is closer to the pinion axis M R than the ring gear axis MH by the amount of its radial play relative to the circumferential surface of the ring gear 4.
  • the resulting mode of operation of the running unit 2 corresponds to the mode of operation described in the aforementioned DE-C 44 21 255 and is explained in more detail below.
  • the ring gear 4 is in the race 3 with a radial clearance arranged, through which an annular gap 31 is formed.
  • the annular gap has exemplary embodiments according to FIGS. 1 to 4 a width of 0.1 mm on all sides, from which the the one-sided system of the Ring gear 4 on the race 3 a gap of a maximum of 0.2 mm Width results.
  • the ring gear 4 has in its Circumferential surface 42 approximately semicircular in cross section Axial grooves 43, which are opposite in the inner surface 33 of the race 3 appropriately designed axial grooves 32 are arranged. By the opposite Axial grooves 32, 43, receiving spaces 45 are created in which each have a sealing roller 44 with a circular cross section is included (Fig. 6).
  • the sealing rollers 44 consist in the discussed embodiment preferably from one high-strength plastic that can withstand temperatures of up to 180 ° C is stable.
  • the dimensions of the receiving spaces 45 and Sealing rollers 44 are selected so that the sealing rollers 44 slightly both radially and circumferentially are adjustable, the radial play only insofar must be sufficient to allow unimpeded movement of the To ensure sealing rollers 44 in both circumferential directions. This does not rule out that the sealing rollers 44 easily on Because of the axial grooves 32, 43 are in such a way that the Ring gear 4 on the race 3 partly also over the Supporting sealing rollers 44. As from FIGS.
  • the transition area is more clearly Axial grooves 32 and 43 to the annular gap 31, to the extent of deviates from the purely cylindrical cross-sectional design and widening the respective groove, beveled by one secure sealing line system of the sealing rollers 44 to the To get flanks of both axial grooves.
  • the ring gear 4 continues from the bottom of its Tooth gaps outgoing radial openings 24, which in an annular groove 25 (Fig. 2) in the peripheral surface of the ring gear 4 mouths.
  • annular groove 25 surrounding the ring gear 4, the Cross section from Fig. 2 emerges, the Axial grooves 43 and serves between the axial grooves 32, 43 created circumferential sections 34 of the annular gap 31 safe to fill and the recording rooms 45 with To apply flow medium.
  • the race has coaxial with the radial openings 24 3 also have radial openings 26, which in the Embodiment according to FIGS. 1, 2 on the pressure side in a housing recess 21 open (Fig. 1), the one hydrostatic bearing for the running unit 2 forms.
  • the Embodiment according to FIGS. 3, 4 serve the corresponding breakthroughs 26 'to promote the under Pressurized flow medium towards the Pressure channel 17 'and are therefore in their Cross section larger than in the embodiment according to FIG. 1, 2.
  • the teeth of the ring gear 4 and the pinion 5 are in the described embodiment involute gears, i.e. those where the contour of the Tooth flanks through involute curves, that of the tooth surfaces in the head and foot areas Arcs are formed.
  • the number of teeth and the geometry the teeth are selected so that in the area of Dividing line A-A (Fig. 5) the teeth of the pinion 5 fully in the Tooth gaps of the ring gear 4 engage or, diametrically opposite, entirely from the tooth gaps of the ring gear 4 have emerged and the tooth heads are on top of each other support sealingly. So that between pinion 5 and ring gear 4th bumpless, smooth running is guaranteed, it is expedient to round the tooth tips, i.e. the edges between the tip circle and the tooth flanks. It can be particularly advantageous to withdraw this to be asymmetrical with respect to the tooth center line, i.e. a larger radius of curvature on the inlet side choose as on the outlet side.
  • the prefill slot 10 itself from the suction field 16 'a certain distance in the sealing housing area extends so that when Entry of the race 3 'into this area still in one to a certain extent, filling the corresponding tooth gap of the ring gear 4 'through the radial opening 26'.
  • the pressure drop at the beginning of the Pressure chamber influenced. This influence depends on the Number of prefilling slots 10 and their cross-sectional size from. The mode of operation of control and pre-filling slots this type is well known and is therefore required here no further explanation.
  • the suction space On the suction side (left of the dividing line A-A in Fig. 5) the suction space is between the teeth of ring gear 4 and pinion 5 and thus also the part of the Annular gap 31 between the race 3 and ring gear 4 under the Suction pressure of the flow medium. Because in the Circumferential sections 34 of the annular gap 31 in this area There is largely equal pressure, the sealing rollers are located 44 in position IV (Fig. 8) approximately in the middle associated axial grooves 32 or 43, i.e. in the thereby formed recording spaces 45. When the Running unit 2 in the direction of rotation indicated by the arrow (Fig. 5) the receiving spaces 45 get out of the suction space, across the dividing line A-A, into position I (Fig. 6).
  • compression springs be provided due to the aforementioned eccentricity uneven between the race and the ring gear even when idle are biased.
  • These compression springs can be used with the Embodiment according to FIGS. 1 and 2 in the radial Breakthroughs 24 of the ring gear 4 can be arranged and themselves therein on the shoulder 27 provided there (FIG. 5) support.
  • the embodiment according to FIGS. 11 to 14 is one So-called tube pump, which is designed for high delivery pressures and is suitable. Their structure and mode of operation are correct with those of the embodiment according to FIGS. 3 and 4 agree and therefore do not require any further here Explanation. As far as matching construction parts Find mention, they are with the reference number of the Embodiment according to FIGS. 3 and 4, but with the Addition a denotes.
  • the pinion 5'a is integral with the shaft 6'a and stored on both sides in their own bearing disks 8 and 9.
  • the Running unit (pinion, ring gear, race) is together with the bearing disks 8, 9 in a tubular housing ll'a added, the front through housing cover 12'a and 13'a is closed. In the housing cover on the drive side 12'a accommodates a radial shaft seal 7.
  • the drive-side bearing disc 8 is sealed with their circumference on the inside wall of the housing and with their End faces on the housing cover 12'a or on the Running unit.
  • the one opposite the drive side Bearing plate 9 is both axially and radially pressure compensated for the required free mobility of the ring gear 4'a in the race 3'a not to hinder.
  • a pressure field 90 is formed, the via a bore 91 with the pressure space between the ring gear 4'a and the pinion 5'a is connected.
  • the print field 90 has approximately a crescent shape, as in FIG. 13 emerges. As a result, the bearing disc 9 is in sealing System held on the running unit.
  • the Bearing disk 9 on the radially the axially effective pressure field opposite radial surface two radial pressure fields 92 or 93, which are essentially circular in shape.
  • the Bearing disk 9 is thereby on one through the pressure field 90 prevented possible tilting and ensures both the front sealing of the running unit as well as the required radial mobility of the ring gear 4'a.
  • 4 has the ring gear in the embodiment described here 4'a no circumferential annular groove on its outer Peripheral surface on; the radial openings 24'a open directly into the outer peripheral surface.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP96932440A 1995-09-01 1996-08-09 Füllstücklose innenzahnradpumpe Expired - Lifetime EP0789814B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19532226A DE19532226C1 (de) 1994-06-17 1995-09-01 Füllstücklose Innenzahnradpumpe
DE19532226 1995-09-01
PCT/DE1996/001523 WO1997009533A1 (de) 1995-09-01 1996-08-09 Füllstücklose innenzahnradpumpe

Publications (2)

Publication Number Publication Date
EP0789814A1 EP0789814A1 (de) 1997-08-20
EP0789814B1 true EP0789814B1 (de) 1998-12-23

Family

ID=7770963

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96932440A Expired - Lifetime EP0789814B1 (de) 1995-09-01 1996-08-09 Füllstücklose innenzahnradpumpe

Country Status (8)

Country Link
US (1) US5890885A (da)
EP (1) EP0789814B1 (da)
JP (1) JPH10508359A (da)
CN (1) CN1164887A (da)
AT (1) ATE175005T1 (da)
DK (1) DK0789814T3 (da)
RU (1) RU2143589C1 (da)
WO (1) WO1997009533A1 (da)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19804133A1 (de) * 1998-02-03 1999-08-12 Voith Turbo Kg Sichellose Innenzahnradpumpe
DE19815421A1 (de) 1998-04-07 1999-10-14 Eckerle Ind Elektronik Gmbh Innenzahnradmaschine
DE20021586U1 (de) * 2000-12-21 2002-02-14 Andreas Stihl AG & Co., 71336 Waiblingen Getriebekopf
WO2003052272A1 (en) * 2001-12-13 2003-06-26 Performance Pumps, Llc. Improved gerotor pumps and methods of manufacture therefor
DE112013001156A5 (de) * 2012-02-27 2014-12-11 Magna Powertrain Bad Homburg GmbH Pumpenanordnung
RU2516754C1 (ru) * 2013-02-27 2014-05-20 Открытое акционерное общество "Уфимское моторостроительное производственное объединение" ОАО "УМПО" Российской Федерация Республика Башкортостан Шестеренчатый насос
JP6672850B2 (ja) * 2016-02-04 2020-03-25 株式会社ジェイテクト オイルポンプ
CN112013262B (zh) * 2020-08-28 2021-10-22 台州九谊机电有限公司 一种机油泵的转子结构
CN114017318A (zh) * 2021-11-18 2022-02-08 宁波威克斯液压有限公司 滚动式自调平衡器及含有其的高压内啮合齿轮泵

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB963736A (en) * 1959-08-12 1964-07-15 Merritt & Company Engineering Improvements in rotary fluid pumps of the n and n+1 type
US3680989A (en) * 1970-09-21 1972-08-01 Emerson Electric Co Hydraulic pump or motor
DE2300484A1 (de) * 1973-01-05 1974-07-18 Otto Eckerle Hochdruck-zahnradpumpe
DE4421255C1 (de) * 1994-06-17 1995-06-29 Otto Eckerle Füllstücklose Innenzahnradpumpe

Also Published As

Publication number Publication date
ATE175005T1 (de) 1999-01-15
RU2143589C1 (ru) 1999-12-27
DK0789814T3 (da) 1999-08-23
CN1164887A (zh) 1997-11-12
US5890885A (en) 1999-04-06
EP0789814A1 (de) 1997-08-20
WO1997009533A1 (de) 1997-03-13
JPH10508359A (ja) 1998-08-18

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