EP0043899B1 - Zahnringpumpe - Google Patents

Zahnringpumpe Download PDF

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Publication number
EP0043899B1
EP0043899B1 EP81103438A EP81103438A EP0043899B1 EP 0043899 B1 EP0043899 B1 EP 0043899B1 EP 81103438 A EP81103438 A EP 81103438A EP 81103438 A EP81103438 A EP 81103438A EP 0043899 B1 EP0043899 B1 EP 0043899B1
Authority
EP
European Patent Office
Prior art keywords
teeth
annular gear
wheel
tooth
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
Application number
EP81103438A
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German (de)
English (en)
French (fr)
Other versions
EP0043899A1 (de
Inventor
Siegfried A. Dipl.-Ing. Eisenmann
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
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP0043899A1 publication Critical patent/EP0043899A1/de
Application granted granted Critical
Publication of EP0043899B1 publication Critical patent/EP0043899B1/de
Expired 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels

Definitions

  • the invention relates to a gerotor pump with a housing, an internally toothed ring gear with 8 to 16 teeth, which is rotatably mounted in the housing, and a pinion which meshes with the ring gear and is supported by a drive shaft and has one tooth less than the ring gear, with the seal between the suction chamber and the pressure chamber opposite the deepest tooth engagement by sliding the tooth tips of the pinion on the ring gear teeth and the deepest tooth engagement by contacting the driving tooth flanks of the pinion on the ring gear teeth, furthermore the tooth heads of the pinion in the tooth gaps of the ring gear go free and the theoretical tooth shape of the pinion is determined by rolling the pinion rolling circle on the ring gear rolling circle.
  • Such gerotor pumps have been known for a long time.
  • the multiple tooth engagement of the Eaton pump has the disadvantage that, depending on the manufacturing tolerance of the tooth flank shape, both on the ring gear and on the pinion of the real tooth engagement under Herz's pressure for torque transmission from the pinion to the ring gear in the circumferential direction is often far away from the point of deepest meshing. Because of the then changed angular position of the pressure point between the tooth flanks of the pinion and ring gear, a tooth force component is then created on the ring gear which tends to increase the center distance of the two wheels. The consequence of this is that the seal between the teeth deteriorates compared to the point of deepest tooth engagement, and because the tooth forces then increase, the higher the delivery pressure, the more so.
  • the invention has set itself the task of further developing the Eaton pump, as outlined in the preamble of claim 1, in such a way that the tooth surfaces of the pinion and ring gear, which are in meshing engagement with one another, slide less on one another and lie against one another over a large area, as a result of which the Herz's Pressure is reduced, that the delivery chambers between each pair of teeth of pinion and ring gear are large, that the essential disadvantage of the continuous volume change of the delivery chambers mentioned is at least largely eliminated and that the toothing voltage is less sensitive to warping compared to the known Eaton gearing. Furthermore, the invention is intended to achieve better smoothness and to reduce the risk of oil film stripping. Finally, a non-invasive area is to be created which avoids the drive engagement intermingling with the sealing engagement lying opposite it.
  • the invention encompasses the basic idea that the engagement ratios and other relationships set out above for the Eaton pump are substantially improved by dividing the ring gear tooth into two parts, namely a driving area and, at the point, the deepest tooth meshing area and another area of the tooth head, which only has the task of sealing at the point opposite the deepest tooth engagement.
  • the first step in accordance with the invention is that two Eaton ring gear teeth with curved tooth contours and halved by half a tooth pitch in the circumferential direction compared to the desired number of teeth are superimposed on one another and only those parts of the teeth that are left of the teeth of both are left standing Gears are covered.
  • each tooth contour arc of the original Eaton gears spanned two of the remaining teeth, which now have a triangular shape with convexly curved flanks.
  • the tooth arch thus defines the two tooth flanks facing away from each other of two adjacent teeth.
  • the tooth profile created in this way does not yet permit a permanent seal at the point opposite the deepest tooth engagement.
  • the toothing is now superimposed on a third Eaton toothing, the pitch of which is equal to half the pitch of the original full Eaton toothing.
  • the flat, curved tooth head profile of the Eaton toothing which is very advantageous for the seal at the point of deepest tooth engagement, is also present in the new toothing according to the invention. Because the tooth tips are cut off, the theoretical degree of coverage falls below the value one. In practice, however, this has no disruptive influence on the teeth according to the invention, as long as the ring gear has no less than eight teeth.
  • the pitch circle of the ring gear runs in the area of the “theoretical” tooth root of the ring gear and accordingly the pitch circle of the pinion runs in the area of the “theoretical” tooth tip of the pinion.
  • the requirement regarding the pitch circles does not have to be met exactly, but it should at least be met approximately.
  • At least the pitch circle of the ring gear should run outside the circle around the center of the ring gear through the lower third of the tooth height of the ring gear. With larger numbers of teeth, the pitch circle of the ring gear can also lie somewhat outside the root circle of the ring gear. This is especially true for teeth over ten.
  • the pitch circle of the pinion must also be shifted inwards or outwards by the appropriate amount. This inward shifting of the pitch circles may be necessary if the number of teeth on the ring gear becomes small, e.g. with eight teeth.
  • the invention is characterized in that in a gerotor pump of the type outlined at the outset, the teeth of the ring gear have an approximate trapezoidal shape with convexly curved flanks and heads, and that the pitch circle of the ring gear runs outside the circle around the ring gear center through the lower third of the tooth height of the ring gear .
  • tooth shape is preferably completely symmetrical in the invention, as is generally customary, an asymmetrical tooth shape can also be used in principle. This applies in particular if the pump is only designed for a certain direction of rotation. In this case, then the two Eaton tooth contours, which define the two tooth flanks of the teeth, are not the same.
  • tooth gaps have to be deepened slightly, so that the tooth heads are clear and that no particularly precise machining is required at the base of the tooth gaps.
  • the tooth shape is preferably determined for the ring gear in such a way that the extent of the ring gear teeth and the extent of the ring gear tooth gaps in the circumferential direction on the circle through half the height of the ring gear teeth is approximately the same.
  • This condition has the further consequence that the theoretical tooth tip width of the ring gear teeth is approximately equal to two thirds of the theoretical width of the tooth gap on the other foot.
  • Such a design leads not only to a relatively large delivery volume measured by the pump diameter, but also to steep tooth flanks.
  • the tooth tip width (without the rounding to be explained later) of the ring gear is preferably 0.65 times to 0.7 times and the width of the tooth gap at the theoretical root circle of the ring gear (again without the rounding to be explained later) is 1.05- up to 1.1 times the theoretical tooth height of the ring gear.
  • a design has proven itself in which the tooth tip radius of curvature of the ring gear is approximately 2 to 2.4 times, better 2.2 to 2.3 times the theoretical tooth height of the ring gear.
  • the construction is also particularly favorable if the tooth flank radius of curvature of the ring gear is approximately 3.3 to 3.7 times, better 3.4 to 3.6 times the theoretical tooth height of the ring gear.
  • the radius of curvature of the tooth flank in this sense is the same as the radius of curvature of the original Eaton toothing by superimposing and displacing it by half a division of this original toothing.
  • the construction becomes particularly simple if the tooth tip curvature of the ring gear is a circular arc, the center of which lies on the radius line of the ring gear through the center of the tooth outside the tooth root circle and the tooth flanks of the ring gear run along circular arcs, the center points of which lie outside the tooth root circle.
  • the circular arcs instead of circular arcs, as explained above, other curves with a not exactly constant radius can occur here.
  • the circular arcs have the advantage of being easy to grasp theoretically because of their constant radius.
  • the tooth flanks of two adjacent teeth that face away from one another preferably lie on a common circular arc.
  • this condition is not essential, for example, two circular arcs with the same radius but different center points can be provided, which intersect on the line through the center of the ring gear and the center of the tooth gap between the two adjacent teeth.
  • the construction is significantly simplified if the edges between the tooth flanks and the tooth tips of the ring gear are each rounded off along an arc that continuously merges into both the arc defining the tooth flank and the arc defining the tooth tip and has a radius that in the Of the order of a third of the theoretical tooth height of the ring gear.
  • a measure of 0.3 times to 0.33 times the theoretical tooth height of the ring gear has proven itself here. If you make this radius too small, you will be forced to cut it out relatively deeply to avoid notching effects on the tooth root pinion.
  • the number of teeth of a gerotor pump according to the invention is limited by the requirement for a high pump output and thus the largest possible teeth.
  • the ring gear preferably has 9 to 15 teeth, more preferably 11 to 13 teeth.
  • a particularly favorable range is 10 to 12 teeth of the ring gear.
  • a number of 11 teeth on the ring gear is considered to be optimal in order to ensure a maximum delivery capacity of the pump for a given diameter.
  • the pump has a housing which has a first left end plate 18 and a right end plate 19.
  • An annular housing middle part 20 extends between the two end plates.
  • the three housing parts define between them a flat cylindrical cavity in which the ring gear 10 is slidably mounted with its outer peripheral surface on the inner peripheral surface of the housing part 20.
  • the pinion shaft 22 carrying the pinion 12 extends through a central bore of the right housing end part 20 and, as symbolically indicated by a wedge 23, is connected to the pinion 12 in a rotationally fixed manner.
  • the toothing of the pinion and ring gear are fully engaged, while below the tooth heads of the pinion and ring gear slide on each other.
  • the outlet opening 16 extends in the right housing end part 19, while the inlet opening 15 lies in the part of the housing end part 19 lying in front of the drawing plane in FIG. 5.
  • a connection channel runs from the drain or extension opening 16 through a connecting piece 24.
  • the three parts 18, 19 and 20 forming the housing are clamped together by screw bolts 25 distributed uniformly over the circumference.
  • the Eaton toothing contains the ring gear 1 of the Eaton pump according to FIG. 1.
  • each tooth 2 has essentially the shape of a segment of a circle.
  • the tooth base essentially coincides with the tooth root circle of the ring gear 1. Since the gearing shown in the example intended to comprise eleven teeth, has the ring gear 1, which is ultimately here only a theoretical tool for the invention construction 5 1/2 teeth 2.
  • the Eaton ring gear contour 1 shown hatched from the top left to the bottom right has an indefinite number of teeth.
  • the center of this ring gear is shown at 3.
  • the division T is shown only in the angular dimension. If you now limit the tooth outline of the ring gear contour 1 additionally by the same tooth contour 5, however, offset by half a tooth pitch, which is hatched in Fig. 2 from top right to bottom left, then only the equilateral triangles with convex flanks remain 6. teeth left, which are hatched both from top right to bottom left and from top left to bottom right.
  • a third ring gear contour 7 is superimposed on the tooth contour thus created, the division of which is equal to half the division t of the contours 1 and 5.
  • the ring gear contour 7 is hatched in FIG. 2 from top to bottom.
  • the greatest height of the teeth of the ring gear contour 7 is less than that of the ring gear contours 1 and 5, so that after overlaying all three ring gear contours, a tooth profile remains, which in FIG. 2 is from top left to bottom right, from top right to bottom left and vertically hatched from top to bottom.
  • the ring gear toothing according to the invention is obtained in principle, which is shown in its entirety in FIG. 3 with reference to the ring gear 10, the teeth 11 of which have the shape obtained according to FIG. 2.
  • the pinion 12 for the gearwheel set according to FIG. 3 is now obtained by rolling the root circle FH of the ring gear 10 onto the tip circle of the pinion 12. In this way, an enveloping figure is created which is exactly the same as the theoretical outline of the pinion 12.
  • the tooth flank construction can be designed optimally with regard to the gear mechanism, such as specific sliding, surface pressure and the like, on the one hand, but also with regard to the seal at the point of deepest tooth engagement, while the designer no longer has one for the formation of the tooth head certain flank construction is bound, but the tooth head curvature can also be chosen so that a practically pressure-free sliding of the tooth heads against each other is achieved compared to the point of deepest tooth engagement.
  • the conveying spaces 14 closed here practically do not change between each tooth gap of the pinion and the ring gear more, so that a violent squeezing of the delivery liquid from the delivery rooms 14 practically no longer occurs.
  • the conveying spaces between the teeth naturally change, but these spaces as a whole are practically constant over the angle of rotation, since they are not separated by tooth engagements.
  • the great length of the inlet and outlet openings, which the invention permits, is remarkable.
  • Each opening extends over about a third of the circumference. This allows high speeds.
  • the kidney-shaped inlets and outlets can be extended even further than the point of deepest tooth engagement by 6000 rpm or more.
  • the ring gear is said to have eleven teeth.
  • the pinion has ten teeth.
  • the diameter of the theoretical root circle FH of the ring gear 10 is selected, which, to give a numerical example, is assumed to be 66 mm.
  • the root circle of the ring gear is also its pitch circle; the tip circle KR of the pinion 12 whose pitch circle.
  • the theoretical tooth height H of the ring gear is 6 mm.
  • a pitch t of the ring gear is plotted from its center MH in the angular dimension and the bisector h of this pitch angle.
  • this radius rm was selected to be around 13.8 mm, ie 2.3 H.
  • the edges between the tip circle with the radius rm and the flank circles with the radius ro are rounded off.
  • a radius rk of 1.9 mm is selected in the exemplary embodiment, which continuously, ie with a common tangent, merges into the tooth flank arc and the tooth tip arc, as can be seen from FIG. 4.
  • the pinion 12 is constructed as an inner envelope figure, which is created by rolling from FH to KR or vice versa.
  • the resulting pinion tooth shape is shown in FIG. 4.
  • the pinion tooth head ZKR whose contour is formed by the tooth heads of the ring gear 10, by no means fills the tooth gap of the ring gear initially constructed, the base of which was formed by FH.
  • Gerotor pumps according to the invention are suitable for a wide variety of purposes.
  • they are suitable as lubricating oil pumps for motor vehicle piston engines, in which the pinion sits directly on the crankshaft and the ring gear in a housing fixed to the engine housing.
  • gear pumps according to the invention are insensitive to fluctuations in the center distance to such an extent that they can withstand the large displacements of the crankshaft of a cylinder internal combustion engine as measured by the dimensions of the relatively small pump.
  • gerotor pump according to the invention is not restricted to this purpose. It is also useful for a variety of other purposes, such as as a hydraulic pump.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)
EP81103438A 1980-07-10 1981-05-06 Zahnringpumpe Expired EP0043899B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19803026222 DE3026222A1 (de) 1980-07-10 1980-07-10 Zahnringpumpe
DE3026222 1980-07-10

Publications (2)

Publication Number Publication Date
EP0043899A1 EP0043899A1 (de) 1982-01-20
EP0043899B1 true EP0043899B1 (de) 1984-01-25

Family

ID=6106901

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81103438A Expired EP0043899B1 (de) 1980-07-10 1981-05-06 Zahnringpumpe

Country Status (8)

Country Link
US (2) US4398874A (ja)
EP (1) EP0043899B1 (ja)
JP (1) JPS5779290A (ja)
AU (1) AU546238B2 (ja)
BR (1) BR8104391A (ja)
CA (1) CA1168510A (ja)
DE (1) DE3026222A1 (ja)
MX (1) MX154462A (ja)

Families Citing this family (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3134668A1 (de) * 1980-07-10 1983-03-17 Siegfried Dipl.-Ing. 7960 Aulendorf Eisenmann Zahnringmotor
JPS5870014A (ja) * 1981-10-22 1983-04-26 Sumitomo Electric Ind Ltd オイルポンプ
DE3202179A1 (de) * 1982-01-25 1983-08-04 Schwäbische Hüttenwerke GmbH, 7080 Aalen Schalt- und/oder fuellpumpe fuer ein automatisches getriebe
DE3243067A1 (de) * 1982-11-22 1984-05-24 Schwäbische Hüttenwerke GmbH, 7080 Aalen Innenlaeuferzahnradoelpumpe fuer kraftfahrzeugverbrennungsmotoren
JPS6081391A (ja) * 1983-10-07 1985-05-09 三菱重工業株式会社 抄紙用エンドレス・ベルト
JPS618484A (ja) * 1984-06-22 1986-01-16 Mitsubishi Metal Corp 内接型ギヤポンプ
CN1007545B (zh) * 1985-08-24 1990-04-11 沈培基 摆线等距线齿轮传动副及其装置
US4760759A (en) * 1986-04-15 1988-08-02 Blake William L Geared ratio coupling
JPS63289634A (ja) * 1987-05-21 1988-11-28 Sony Corp グラフイツクスプリンタ
JPH0756268B2 (ja) * 1987-07-27 1995-06-14 株式会社ユニシアジェックス オイルポンプ
CH679062A5 (ja) * 1988-10-24 1991-12-13 Siegfried Eisenmann
CH676490A5 (ja) * 1988-10-24 1991-01-31 Hermann Haerle
JPH058165U (ja) * 1992-04-23 1993-02-05 ホソカワミクロン株式会社 熱交換器用導管
DE4311165C2 (de) * 1993-04-05 1995-02-02 Danfoss As Hydraulische Maschine
US5316457A (en) * 1993-05-11 1994-05-31 Suntec Industries Incorporated Gear pump with improved gear/shaft retention
DE4441522A1 (de) * 1994-11-22 1996-05-23 Schwaebische Huettenwerke Gmbh Schmiermittelpumpe
US5615579A (en) * 1995-06-02 1997-04-01 Shiow-Miin; Perng Gear structure for reduction gears
US5997262A (en) * 1997-04-10 1999-12-07 Walbro Corporation Screw pins for a gear rotor fuel pump assembly
JP4169724B2 (ja) 2003-07-17 2008-10-22 株式会社山田製作所 トロコイド型オイルポンプ
BE1016298A4 (nl) * 2004-11-04 2006-07-04 Wiele Michel Van De Nv Aandrijftandwiel voor het aandrijven van een grijperstang in een weefmachine.
JP2006152928A (ja) * 2004-11-30 2006-06-15 Hitachi Ltd 内接式歯車ポンプ
CA2596520C (en) * 2005-02-16 2013-10-08 Magna Powertrain Inc. Crescent gear pump with novel rotor set
KR101332995B1 (ko) 2009-11-16 2013-11-25 스미또모 덴꼬 쇼오께쯔 고오낑 가부시끼가이샤 펌프용 로터와 그것을 이용한 내접 기어 펌프
DE102011000880B3 (de) 2011-02-22 2012-07-12 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Verfahren zur Erzeugung der Zahnform von Innen- und Außenring einer Zahnringmaschine sowie damit erzeugter Zahnring
JP6027343B2 (ja) * 2012-06-01 2016-11-16 株式会社山田製作所 オイルポンプのロータ
CN106030152B (zh) * 2013-10-10 2018-11-30 澳商安博科技工业有限公司 工具机构和使用此工具机构的工具
DE102013111763B8 (de) 2013-10-25 2015-09-10 Universität Stuttgart Gerotormaschine, Gerotorsatz für eine Gerotormaschine und Verwendung eines Gerotorsatzes
DE102022130861A1 (de) 2022-11-22 2024-05-23 Klaus Stühmeier Fördereinrichtung für flüssiges oder gasförmiges Medium

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US892295A (en) * 1908-04-16 1908-06-30 George W Nuetz Rotary engine.
US1341846A (en) * 1918-04-22 1920-06-01 Ellick H Gollings Rotary power device
US1516591A (en) * 1923-04-30 1924-11-25 Hill Compressor & Pump Company Rotary pump
CH109955A (de) * 1924-02-22 1925-05-01 Hill Compressor & Pump Co Inc Zahnräder-Rotationsmaschine.
US2091317A (en) * 1934-10-13 1937-08-31 Myron F Hill Gear tooth curve
US2209201A (en) * 1937-08-28 1940-07-23 Myron F Hill Change speed gear
FR838270A (fr) * 1937-11-09 1939-03-02 Perfectionnements aux compteurs, pompes, compresseurs ou moteurs volumétriques pour tous fluides
AT291775B (de) * 1968-11-18 1971-07-26 Hohenzollern Huettenverwalt Hydraulische Zahnradmaschine
DE2024339C2 (de) * 1969-10-27 1983-02-03 Fürstlich Hohenzollernsche Hüttenverwaltung Laucherthal, 7480 Sigmaringen Zahnradverdrängermaschine für Flüssigkeiten, insbesondere Zahnradpumpe
DE2041483C3 (de) * 1970-08-20 1973-05-17 Hohenzollern Huettenverwalt Trochoidenzahnradpaarung
US3907470A (en) * 1971-08-19 1975-09-23 Hohenzollern Huettenverwalt Gear machine
DE2318753C2 (de) * 1973-04-13 1984-11-08 Eisenmann, Siegfried, Dipl.-Ing., 7960 Aulendorf Zahnradmaschine
SU606006A1 (ru) * 1976-01-20 1978-05-05 Erasov Fedor N Шестеренна гидромашина внутреннего зацеплени
DE2644531C2 (de) * 1976-10-01 1986-06-12 Fürstlich Hohenzollernsche Hüttenverwaltung Laucherthal, 7480 Sigmaringen Hydrostatische Zahnradmaschine mit einem Trochoidenzahnradpaar
DE2758376A1 (de) * 1977-12-28 1979-07-05 Schwaebische Huettenwerke Gmbh Kolbenkraft- oder -arbeitsmaschine mit innenlaeuferzahnradoelpumpe

Also Published As

Publication number Publication date
US4398874A (en) 1983-08-16
US4432712A (en) 1984-02-21
MX154462A (es) 1987-08-28
AU7266381A (en) 1982-02-18
BR8104391A (pt) 1982-03-30
JPS6257835B2 (ja) 1987-12-02
DE3026222C2 (ja) 1987-10-01
AU546238B2 (en) 1985-08-22
DE3026222A1 (de) 1982-02-04
EP0043899A1 (de) 1982-01-20
JPS5779290A (en) 1982-05-18
CA1168510A (en) 1984-06-05

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