EP1328730B1 - Füllstücklose innenzahnradpumpe - Google Patents
Füllstücklose innenzahnradpumpe Download PDFInfo
- Publication number
- EP1328730B1 EP1328730B1 EP01978115A EP01978115A EP1328730B1 EP 1328730 B1 EP1328730 B1 EP 1328730B1 EP 01978115 A EP01978115 A EP 01978115A EP 01978115 A EP01978115 A EP 01978115A EP 1328730 B1 EP1328730 B1 EP 1328730B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- tooth
- circumferential surface
- pinion
- ring gear
- wheel
- 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
Links
Images
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
- 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 glall Clusterlose internal gear pump with the features according to the preamble of claim 1.
- Flush-free internal gear pumps or motors have a toothing of Pinion and ring gear whose teeth are engaged both in the mutual engagement Tooth gaps as well as, diametrically opposite, to each other lying tooth heads sealingly in mutual contact to thereby delimit a suction area from a pressure area. Since it is up in practice Reason unavoidable manufacturing tolerances and due to the particular in higher pressures occurring elastic deformations is not possible, the mentioned sealing contact in particular in the field of teeth achieve, in which the tooth heads are to abut each other Measures are taken to make this sealing contact at all To ensure operating conditions.
- bearing ring is arranged circumferentially.
- the bearing ring is relative to the housing about a pivot axis parallel to its axis pivotable.
- the pivot axis is such that the non-intrusive Hohlrad Scheme associated ring portion of the bearing ring through the pressure chamber acting on the ring gear pressure forces at least approximately radially to Pinion axis is moved, causing the tooth tips in the non-intrusive Hohlrad Scheme be held in mutual sealing contact (DE 196 51 683 A1).
- the object of the invention is an internal gear pump of the type mentioned to create, in which the sealing effect between the tooth tips improved and the Noise is reduced.
- tooth head withdrawal depends on the model size. It is therefore expediently, measured from the transition between the uncorrected circumferential or rounding surface and the tooth flank, the 0.02-0.1 times the gearing module m.
- the illustrated in Figs. 1 and 2 internal gear pump comprises a whole with 1 designated housing consisting of a cup-shaped housing part 11 and a attached to the front side housing cover 12 is constructed.
- cup-shaped housing part 11 is a pinion shaft 14 rotatably mounted on the one Pinion 2 is secured against rotation.
- the pinion 2 meshes with a ring gear 3, which in a bearing ring 4 is received and rotatably supported therein.
- the pinion 2 and the ring gear 3 as is apparent from Fig. 1, relative to each other with a Eccentricity e stored.
- the eccentricity e d. H.
- the distance between the Pinion axis and the ring gear corresponds to the theoretical Gearing geometry of pinion and ring gear and sets backlash-free or Sliding the gears ahead of each other.
- the teeth of the pinion 2 and the ring gear 3 mesh with each other in such a manner that on the left side in Fig. 1 in the region of the dividing line A, the teeth of the pinion 2 fully into the tooth gaps engage the ring gear 3 and abut the tooth flanks, while on the opposite, in Fig. 1 right side entirely from the tooth gaps of Ring gear 3 have leaked. Support in this non-invasive ring gear range E.
- ring gear 3 and pinion 2 each have one Involute toothing on, i. the tooth flanks have an involute contour.
- the number of teeth of the ring gear 3 differs from that of the pinion 2 to 1.
- the bearing ring 4 is in a housing bore 15 of the cup-shaped housing part eleventh recorded with a radial clearance of about 0.2 mm.
- the wall of the Housing bore 15 is partially penetrated by a bearing pin 16 which in the Bottom of the housing bore 15 is pressed firmly.
- With the over the wall of the Housing bore 15 protruding largely semi-cylindrical part of the Bearing pin 16 is this in an axially directed groove 17 of the bearing ring 4th added.
- the axial groove 17 is adapted to the shape of the bearing pin 16 and also partly cylindrical.
- the engaging in the axial groove 17 bearing pin 16 forms for the bearing ring 4 to a the axes of pinion 2 and ring gear 3 parallel pivot axis to which the bearing ring 4 in the context of the available radial clearance in the housing bore 15 is pivotable.
- this is Pivot axis in a quadrant of the bearing ring 4, located between the non-engaging ring gear E and the center of the pressure chamber D extends.
- the bearing ring 4 has at a location which is the vertex of the non-intrusive Hohlrad Schemes E is assigned, another axial groove 18 with a Rectangular cross-section on its outer circumference. This axial groove 18 is in the Bottom of the housing bore 15 associated with a receiving bore 19 in the one Hairpin spring 20 is held.
- the hairpin spring 20 protrudes into the axial groove 18 and loaded the bearing ring 4 radially so that the teeth of the ring gear 3 in the non-engaging Hohlrad Scheme E pressed with their tooth heads against each other become.
- This load direction largely corresponds to the direction of movement, the bearing ring 4 as a result of the pivoting movement about the pivot axis 16, 17th performs.
- the force of the hairpin spring 20 can be kept relatively low because it merely serves to provide the necessary sealing contact between the tooth tips in the non-intervention Hohlrad Scheme E during startup of the To ensure internal gear pump, d. H. at a time when in the pressure room D still no operating pressure is built up and therefore no pressure forces Act.
- the position and direction of the resultant R is largely predictable and substantially corresponds to that shown in Fig. 1.
- the pressure build-up in the pressure chamber D can be in a known manner by Vor Reichllschlitze to the Teeth of pinion 2 and / or ring gear 3 influence, so that z. B. over the Tooth gaps of the pressure chamber D across a largely equal pressure.
- the resultant R is pulled out perpendicular to that in FIG shown line that the vertex of the non-intrusive Hohlrad Schemes E with the pinion tooth connects at full engagement in a tooth gap of the ring gear.
- FIG. 3 differs from that according to FIGS Fig. 1, 2 essentially in that the ring gear 3 'in a known manner its outer circumference in the axial direction to a race 3 "widened to to keep the specific bearing pressure in the bearing ring 4 'low. Besides that is dispensed with a pressure spring 20. Regarding the axially widened tread the ring gear 3 ', on both sides over the side surfaces of ring gear and Pinion projects and the cross section of Figure 3 shows, however, for the The present invention has no meaning, reference is made to DE 198 15 421 A1.
- Fig. 4 is a section of the non-engagement ring gear E of both enlarged reproduced above embodiments. Shown are the Gears with the uncorrected tooth form and - for the ring gear - with the According to the invention corrected tooth shape.
- the teeth 22 and 33 of pinion 2 and Ring gear 3 are in a relative position in which they are in the arrow indicated direction of rotation have moved so far toward each other that their outer peripheral surfaces 23 and 34 at least partially opposite each other lie and rest against each other.
- the peripheral surfaces 23, 34 can be uncorrected Operagnelinder lake with the tip circle diameter of the respective teeth or with a smaller diameter (see THE TOOTH FORMS OF ZAHNR ⁇ DER H.
- the teeth 33 of the Ring gear 3 corrected according to the invention are taken back asymmetrically in the head area.
- a tooth centerline 40 which is also a tooth symmetry axis or symmetry plane at the same time the teeth 33 are taken back asymmetrically in the head area.
- the transition line 42 to the involute flank 35 closer to the Tooth base 44 is located as the transition 36 of the same tooth on the opposite lying side.
- the Return area 41 to a transition line 45 in the area of original circumferential surface 34 may extend into respect to the Tooth flank 35 is already beyond the center line 40.
- the redemption area can also run all the way to the opposite tooth flank, with the Transition line 45 coincide with the transition line 36 or even in the subsequent tooth flank may be, or shorter than shown, e.g. such that about half of the before the correction for the seal for Available peripheral surface 34 is maintained. In the former case is to make sure that the deviation of the return surface 41 from the not corrected peripheral surface 34 located in the beyond the center line 40 Section is small so as not to affect the sealing contact.
- the return surface 41 has a smooth in the embodiment shown steady course and can in all cases a cylindrical, in particular be circular cylindrical surface.
- the radius of this surface can basically be in wide limits are chosen, based only on the size of the gearing and are determined by which extension of the return surface 41 to the opposite tooth flank is desired. It goes without saying that occurring intersections (transition lines 42, 45) rounded or smoothed are to avoid any edges.
- the teeth 22 of the Pinion 2 corrected.
- the withdrawal of the tooth heads can in production by subsequent Grinding after the generation of the uncorrected gearing or a DIN gearing or already in the generation of the gearing by a corresponding tool profile done.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Description
- Fig. 1
- einen Querschnitt längs der Linie I-I in Fig. 2;
- Fig. 2
- einen Axialschnitt längs der Linie II-II in Fig. 1;
- Fig. 3
- einen zu Fig. 1 analogen Schnitt einer modifizierten Ausführungsform, und
- Fig. 4
- eine Darstellung des eingriffsfreien Hohlradbereichs beider vorstehender Ausführungsformen in stark vergrößertem Maßstab zur Verdeutlichung der erfindungsgemäßen Zahnkopf-Rücknahme.
Claims (6)
- Füllstücklose Innenzahlradpumpe mit einem Gehäuse (1), einem in dem Gehäuse umlaufenden innenverzahnten Hohlrad (3) und einem in dem Gehäuse drehbar gelagerten, mit dem Hohlrad kämmenden außenverzahnten Ritzel (2), dessen Zähne durch einen vollen Eingriff in Zahnlücken des Hohlrads, einerseits, und einen Dichtkontakt mit den Zahnköpfen des Hohlrads in einem dem Zahnlückeneingriff annähernd diametral gegenüberliegenden eingriffsfreien Hohlradbereich (E), andererseits, einen Saugraum (S) und einen Druckraum (D) der Verzahnung definieren, wobei die Verzahnung von Hohlrad und Ritzel eine Evolventen- oder Zykloidenverzahnung ist und die Zahnköpfe eine gerundete Umfangsfläche haben,
dadurch gekennzeichnet, dass die gerundete Umfangsfläche der Zahnköpfe von Hohlrad (3, 3') und/oder Ritzel (2) bezüglich einer Mittellinie (40) jedes Zahns (22, 33) asymmetrisch ist derart, dass der Übergang (42) zwischen der Zahnflanke (24, 35) und der Umfangsfläche bei dem Hohlrad auf der in Drehrichtung hinteren Zahnflanke (35) und bei dem Ritzel (2) auf der in Drehrichtung vorderen Zahnflanke (24) sich näher dem Zahnfuß befindet als auf der jeweils gegenüber liegenden Zahnflanke, wobei sich die asymmetrisch gerundete Umfangsfläche durchgehend zwischen den Zahnflanken jedes Zahns (22, 33) erstreckt. - Innenzahnradpumpe nach Anspruch 1, dadurch gekennzeichnet, dass sich die Umfangsfläche aus einer Rücknahmefläche (41) und einer nicht korrigierten Umfangsfläche (34) zusammengesetzt.
- Innenzahnradpumpe nach Anspruch 2, dadurch gekennzeichnet, dass der Übergang (42) zwischen der Rücknahmefläche (41) und der nicht korrigierten Umfangsfläche (34) in der Nähe der Zahn-Mittellinie (40) liegt.
- Innenzahnradpumpe nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass die Rücknahmefläche (41) und die nicht korrigierte Umfangsfläche (34) jeweils Kreiszylinderflachen sind.
- Innenzahnradpumpe nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass die Umfangsfläche eine Kreiszylinderfläche ist.
- Innenradpumpe nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass das Ausmaß (a) der Rücknahme des Zahnkopfes (in mm), gemessen von dem Übergang (36) zwischen der nicht korrigierten Umfangsfläche (34) und der Zahnflanke (35), 0,02m-0,1m beträgt (m=Verzahnungsmodul).
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10052779 | 2000-10-25 | ||
DE10052779A DE10052779A1 (de) | 2000-10-25 | 2000-10-25 | Füllstücklose Innenzahnradpumpe |
PCT/DE2001/003484 WO2002035097A1 (de) | 2000-10-25 | 2001-09-07 | Füllstücklose innenzahnradpumpe |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1328730A1 EP1328730A1 (de) | 2003-07-23 |
EP1328730B1 true EP1328730B1 (de) | 2004-10-20 |
Family
ID=7660943
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01978115A Expired - Lifetime EP1328730B1 (de) | 2000-10-25 | 2001-09-07 | Füllstücklose innenzahnradpumpe |
Country Status (4)
Country | Link |
---|---|
US (1) | US6893239B2 (de) |
EP (1) | EP1328730B1 (de) |
DE (2) | DE10052779A1 (de) |
WO (1) | WO2002035097A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102011100105A1 (de) | 2011-04-30 | 2012-10-31 | Robert Bosch Gmbh | Füllstücklose hydrostatischeInnenzahnradmaschine |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10302964A1 (de) * | 2003-01-25 | 2004-08-05 | Continental Teves Ag & Co. Ohg | Hochdruckinnenzahnradpumpe |
JP4319617B2 (ja) * | 2004-12-27 | 2009-08-26 | 株式会社山田製作所 | トロコイド型オイルポンプ |
US8242736B2 (en) * | 2008-04-03 | 2012-08-14 | Honda Motor Co., Ltd. | DC motor with directionally determined torque |
DE102012211225A1 (de) | 2012-06-29 | 2014-01-02 | Robert Bosch Gmbh | Rotationskolbenmaschine |
DE102012213236A1 (de) | 2012-07-27 | 2014-01-30 | Robert Bosch Gmbh | Rotationskolbenpumpe |
DE102012214243A1 (de) | 2012-08-10 | 2014-02-13 | Robert Bosch Gmbh | Innenzahnradpumpe |
US11549507B2 (en) * | 2021-06-11 | 2023-01-10 | Genesis Advanced Technology Inc. | Hypotrochoid positive-displacement machine |
US11965509B2 (en) | 2022-02-28 | 2024-04-23 | Genesis Advanced Technology Inc. | Energy transfer machine for corrosive fluids |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2389728A (en) * | 1943-10-14 | 1945-11-27 | Myron F Hill | Elliptical contour for rotor teeth |
GB1316934A (en) * | 1969-09-19 | 1973-05-16 | Hobourn Eaton Mfg Co Ltd | Rotary pumps and motors of the type incorporating inner and outer lobed members |
DD115184A1 (de) * | 1974-12-04 | 1975-09-12 | ||
EP0173778B1 (de) * | 1984-09-05 | 1990-03-07 | Hobourn Engineering Limited | Pumpen |
EP0362906B1 (de) | 1986-07-19 | 1991-09-04 | Barmag Ag | Innenzahnradpumpe |
JP2706475B2 (ja) * | 1988-07-15 | 1998-01-28 | 日立粉末冶金株式会社 | 内側噛み合い歯車ポンプ |
EP0736691B1 (de) * | 1995-04-04 | 1999-11-03 | Societe Techspace Aero | Innenzahnradpumpe mit radialen Zuführungsröhren |
DE19651683A1 (de) | 1996-12-12 | 1998-06-18 | Otto Eckerle | Füllstücklose Innenzahnradpumpe |
DE19815421A1 (de) | 1998-04-07 | 1999-10-14 | Eckerle Ind Elektronik Gmbh | Innenzahnradmaschine |
-
2000
- 2000-10-25 DE DE10052779A patent/DE10052779A1/de not_active Withdrawn
-
2001
- 2001-09-07 WO PCT/DE2001/003484 patent/WO2002035097A1/de active IP Right Grant
- 2001-09-07 DE DE50104246T patent/DE50104246D1/de not_active Expired - Lifetime
- 2001-09-07 EP EP01978115A patent/EP1328730B1/de not_active Expired - Lifetime
- 2001-09-07 US US10/415,225 patent/US6893239B2/en not_active Expired - Lifetime
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102011100105A1 (de) | 2011-04-30 | 2012-10-31 | Robert Bosch Gmbh | Füllstücklose hydrostatischeInnenzahnradmaschine |
Also Published As
Publication number | Publication date |
---|---|
EP1328730A1 (de) | 2003-07-23 |
US20040091379A1 (en) | 2004-05-13 |
WO2002035097A1 (de) | 2002-05-02 |
DE50104246D1 (de) | 2004-11-25 |
US6893239B2 (en) | 2005-05-17 |
DE10052779A1 (de) | 2002-05-08 |
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