EP0028349B1 - Machine hydrostatique à engrenages - Google Patents

Machine hydrostatique à engrenages Download PDF

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Publication number
EP0028349B1
EP0028349B1 EP80106401A EP80106401A EP0028349B1 EP 0028349 B1 EP0028349 B1 EP 0028349B1 EP 80106401 A EP80106401 A EP 80106401A EP 80106401 A EP80106401 A EP 80106401A EP 0028349 B1 EP0028349 B1 EP 0028349B1
Authority
EP
European Patent Office
Prior art keywords
gear
tooth
radius
range
profile
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
EP80106401A
Other languages
German (de)
English (en)
Other versions
EP0028349A1 (fr
Inventor
Bodo Dr.-Ing. Stich
Horst Fischer
Helmut Dipl.-Ing. Schulz
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.)
Bosch Rexroth AG
Original Assignee
Mannesmann Rexroth AG
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
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6084809&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0028349(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Mannesmann Rexroth AG filed Critical Mannesmann Rexroth AG
Priority to AT80106401T priority Critical patent/ATE4137T1/de
Publication of EP0028349A1 publication Critical patent/EP0028349A1/fr
Application granted granted Critical
Publication of EP0028349B1 publication Critical patent/EP0028349B1/fr
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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/1954—Eccentric driving shaft and axle
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19949—Teeth
    • Y10T74/19963—Spur
    • Y10T74/19972—Spur form

Definitions

  • the invention relates to a hydrostatic gear machine with an internally toothed ring gear and an inner toothed wheel surrounded by and meshing with the ring gear, the tooth flanks of one of the toothed wheels viewed from the side being at least partially formed as circular arcs, the shape of the effective tooth flanks of the other wheel is determined by the rolling on the teeth of the first wheel and the odd number of teeth in the producing ring gear is in the range from 11 to 17 or in the producing inner wheel the even number of teeth is in the range 8 to 14, the tooth height is approximately equal to the tooth thickness is on the rolling cylinder, the tooth flank radii merge tangentially into one another and into the top or bottom circle of the gear wheel and the tooth flank, seen in cross-section, is largely convex or concave or approximately equally curved concave-convex.
  • a gear machine of the aforementioned type is known from DE-A-2 758 376.
  • Special gears of the aforementioned type are predominantly manufactured in two stages today, namely pre-profiling with a gear tool having relatively large dimensional deviations in the first stage and improving the shape and surface quality of the gearing produced by shape grinding in the second stage. If the degree of overlap of the toothing of the two meshing gears is relatively large, then the center distances of the two gears must be very precise in order to avoid interference with teeth and mechanically caused noises due to manufacturing-related dimensions. To reduce the degree of coverage, the tooth tip area is often shortened, but this results in an additional, harmful dead volume.
  • the present invention has for its object to provide a tooth profile that has optimal conditions in terms of delivery capacity, flow rate pulsation, tooth mesh frequency, noise behavior, space requirements and dead volume and enables economical, easily reproducible and easily verifiable production.
  • This object is achieved according to the invention by the features in the characterizing part of claim 1 or 5.
  • the tooth flank consists of at least three circular arcs that merge into one another.
  • a tooth profile can be obtained for the counter wheel, which is also made up of at least three circular arcs with very good approximation and can therefore also be produced relatively easily.
  • a gear machine with a correspondingly designed gear fulfills in particular the requirements for small flow fluctuations, the smallest possible dead volume, the greatest possible delivery capacity, the smallest possible space requirement and small leakage quantities by arranging a filler piece on a relatively large central angle, so that as many tooth heads as possible face the filler piece directly.
  • an internal gear 3 with ten teeth 4 is rotatably mounted about an axis 5.
  • the teeth 2 and 4 mesh with each other in the manner shown.
  • the teeth 2 and 4 are designed as shown in FIGS. 3 and 2 on a larger scale.
  • the ring gear 1 is the generating wheel. From the diameter of the pitch circle 6, the width or thickness swH (measured in each case on the circumference of the pitch circle 6) for each tooth and thus also the tooth height hH results from the predetermined number of teeth the tooth thickness is the same.
  • the ratio of the tip circle radius raH to the radius of the pitch circle 6 is approximately 0.9.
  • the pressure angle b at the pitch point C is 35 ° if the axes 5 and 8 of the two wheels 3 or 1 and the pitch point C lie in a line, and the ratio of the tip circle radius raH to the flank radius r2H in the area of the pitch circle 0.7.
  • the tooth flank radii merge tangentially into one another and into the top or bottom circle.
  • the ratio of the tip circle radius raH to one of the two other flank radii r1H and r3H and to the tooth height hH is 35, 20 and 3.75.
  • the ratio of the flank radius r2H to one of the two other flank radii r1H and r3H is 50 and 30, respectively, and the ratio of the two flank radii r3H and r1H is 1.7.
  • the flank shape of the ring gear 2 is convexly curved as seen from the side.
  • the toothing of the internal gear 3, which has ten teeth and whose pitch circle is designated by 9, is produced by the teeth 2 of the toothing of the ring gear 1, as follows:
  • the ratio of the tip circle radius raR to one of the four flank radii rlR, r2R, r3R and r4R is 20 or 0.1 or 35 or 0.1.
  • the ratio of the pitch circle radii of the ring gear 1 and the inner wheel 3 is 1.3.
  • the tooth height hR is approximately equal to the tooth thickness swR measured on the pitch circle of the inner wheel.
  • flanks of the teeth 4 of the inner wheel 3 When viewed from the side, the flanks of the teeth 4 of the inner wheel 3 also form three or four arcs that merge into one another and tangentially into the top or bottom circle. In cross-section, the flank of the tooth 4 can be both concave (if it is determined by three radii) and, in approximately equal parts, convex-concave (if it is determined by four radii).
  • flanks of the teeth 2 of the ring gear 1 and / or of the teeth 4 of the internal gear 3 are radially displaced towards the center by a few 1/100 mm.
  • Advantageous diameters of the pitch circle for the ring gear are between 35 mm to 200 mm.
  • a filler 7 is provided in a known manner in the free space between the ring gear 1 and the inner gear 3.
  • the center of the ring gear 1 is designated 8.
  • a gear rotor can also be formed.
  • the number of teeth of the generating internal gear is 10 and the ratio of the tip circle radius raR to the three flank radii r1 R, r2R and r3R is 20, 0.1 and 35, respectively.
  • the ratio of the flank radius r2R to one of the two remaining flank radii r1R and r3R is 200 and 325 respectively for the internal gear and the ratio of the two flank radii r3R and ri R is 0.6.
  • the shape of the flanks of the internal gear is either concave in the main part or approximately concave-convex in equal parts.
  • the tip circle radius raR to the pitch circle radius raR to the pitch circle radius rwR is 1.175.
  • the counter flank on the ring gear generated with such an internal gear is also, with very good approximation, a circular arc flank consisting of three circular arcs with different radii. The flank runs predominantly. Part convex.
  • the tip circle radius raH relates to the three flank radii r1 H, r2H and r3H as 35, 0.7 and 20.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Gears, Cams (AREA)

Claims (8)

1. Machine hydraulique à engrenage qui comprend une roue creuse ou une « couronne à denture intérieure et une roue dentée intérieure entourée par ladite couronne et dont la denture extérieure engrène avec celle de cette dernière, les flancs des dents de l'une de ces deux roues dentées présentant vus de côté, au moins partiellement, la forme d'un arc de cercle, la forme des flancs effectifs de l'autre roue étant déterminée par le roulement contre les dents de la première, l'arrangement étant tel que lorsque c'est la couronne qui est la roue génératrice, le nombre impair des dents, se situe entre 11 et 17, tandis que quand c'est la roue intérieure qui est la roue génératrice, le nombre pair des dents est compris entre 8 et 14, la hauteur des dents étant approximativement égale à l'épaisseur sur le cylindre de roulement, les rayons des flancs des dents se raccordant tangentiellement entre eux et au rayon de tête ou de pied de la roue dentée, les flancs des dents, vus en coupe ayant, en majeure partie, une forme convexe ou concave ou bien en parties égales une courbure concave et convexe caractérisée en ce que :
a) l'angle d'engrènement au point de roulement ou de contact est compris entre 30° et 40°, et
b) le rapport entre le rayon du cercle de tête raH et les trois rayons rl H, r2H, r3H des flancs de dent est compris respectivement entre 30 et 40, 0,55 et 0,9 et 15 à 25.
2. Machine à engrenage selon la revendication 1 dans laquelle le rapport entre le rayon raH du cercle de tête et le rayon rwH du cercle de roulement de la couronne dentée est d'environ 0,9, caractérisé en ce que le rapport entre le second rayon de flanc r2H d'une part, et le premier et le troisième rayons de flanc r1 H et r3H d'autre part, est respectivement compris entre 40 et 60 et entre 25 et 35, tandis que le rapport entre le rayon du troisième flanc et celui du premier flanc est compris entre 1,5 et 2 cependant que le rapport entre le rayon du cercle de tête sur la hauteur des dents est compris entre 3,5 et 4.
3. Machine à engrenage selon la revendication 1 ou 2 à la roue intérieure de laquelle la différence des dents de la roue génératrice sur les dents de la roue générée se situe entre 3 et 5, le rapport des rayons des cercles de roulement rwH et rwR de la roue génératrice et de la roue générée étant compris entre 1,2 et 1,4, la hauteur HR des dents étant approximativement égale à l'épaisseur des dents sur le cylindre de roulement, cependant que les rayons des flancs des dents se jettent tangentiellement l'un dans l'autre et dans les cercles de tête et de pied de la roue dentée, caractérisée en ce que, pour la roue dentée intérieure engendrée, le rapport du rayon du cercle de tête sur l'un des trois rayons de flanc r1 R, r2R. r3R est compris respectivement entre 15 et 25, 0,075 et 0,125 et 30 et 40.
4. Machine à engrenage selon la revendication 3, caractérisée en ce que le rapport du rayon du cercle de tête sur un tel quatrième rayon de flanc r4R est compris entre 0,075 et 0,125.
5. Machine à engrenage hydraulique qui comprend une couronne 1 à denture intérieure et une roue dentée intérieure 3 à denture extérieure entourée par ladite couronne et engrenant avec elle, les flancs des dents de l'une des deux roues dentées présentant, vus de côté, au moins en partie, la forme d'un arc de cercle cependant que la forme des flancs effectifs des dents de l'autre roue sont déterminés par le roulement contre les dents de la première roue et où, dans le cas d'une roue dentée intérieure génératrice, le nombre pair des dents est compris entre 8 et 14, la hauteur hR des dents étant approximativement égale à leur épaisseur sWR sur le cylindre de roulement, tandis que les rayons des flancs des dents se jettent tangentiellement les uns dans les autres et dans les cercles de tête et de pied de la roue dentée, les flancs des dents vus en coupe ayant, soit en majeure partie, une forme concave soit en parties égales, une courbure concave et convexe caractérisée par les particularités suivantes de la roue dentée intérieure génératrice :
a) l'angle d'attaque ou d'engrènement au point de roulement ou de contact est situé entre 30° et 40°,
b) le rapport du rayon du cercle de tête raR sur les trois rayons rl R, r2R, r3R des flancs des dents est compris respectivement entre 15 et 25, 0,09 et 0,125 et 30 à 40.
6. Machine à engrenage selon la revendication 5 dans laquelle le rapport du rayon raR du cercle de tête sur le rayon du cercle de roulement rwR de la roue intérieure est compris entre 1,1 et 1,25 caractérisée en ce que le rapport du second rayon de flanc r2R sur le premier r1 R et le troisième r3R est cmpris entre 150 et 250 et entre 275 et 375 et en ce que le rapport du troisième rayon de flanc sur le premier est compris entre 0,4 et 0,8 tandis que le rapport du rayon du cercle de tête raR sur la hauteur des dents est compris entre 3,5 et 4.
7. Machine à engrenage selon la revendication 5 ou 6 ayant une couronne engendrée où la différence des dents de la roue génératrice sur les dents de la roue dentée est comprise entre 3 et 5, le rapport des rayons des cercles de roulement de la roue génératrice et de la roue générée étant compris entre 0,7 et 0,85 et où la hauteur hH des dents est approximativement égale à l'épaisseur des dents sur le cylindre de roulement, cependant que les rayons des flancs des dents se jettent tangentiellement l'un dans l'autre et dans les cercles de tête et de pied de la roue dentée, caractérisée en ce que, dans la couronne engendrée, le rapport du rayon, du cercle de tête raH sur l'un des trois rayons de flanc rlH, r2H, r3H est respectivement compris entre 30 et 40, entre 0,55 et 0,9 et entre 15 et 25.
8. Machine à engrenage selon l'une quelconque des revendications précédentes caractérisée en ce que les flancs des dents sont décalés par rapport à leur position sans jeu, de quelques centièmes de millimètres en direction du pied de la dent correspondante.
EP80106401A 1979-10-31 1980-10-21 Machine hydrostatique à engrenages Expired EP0028349B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT80106401T ATE4137T1 (de) 1979-10-31 1980-10-21 Hydrostatische zahnradmaschine.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2943948 1979-10-31
DE19792943948 DE2943948A1 (de) 1979-10-31 1979-10-31 Hydrostatische zahnradmaschine

Publications (2)

Publication Number Publication Date
EP0028349A1 EP0028349A1 (fr) 1981-05-13
EP0028349B1 true EP0028349B1 (fr) 1983-07-13

Family

ID=6084809

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80106401A Expired EP0028349B1 (fr) 1979-10-31 1980-10-21 Machine hydrostatique à engrenages

Country Status (5)

Country Link
US (1) US4386892A (fr)
EP (1) EP0028349B1 (fr)
JP (1) JPS5675989A (fr)
AT (1) ATE4137T1 (fr)
DE (1) DE2943948A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3416400C2 (de) * 1984-05-03 1993-10-07 Schwaebische Huettenwerke Gmbh Kraftfahrzeugölpumpe
CH676490A5 (fr) * 1988-10-24 1991-01-31 Hermann Haerle
JP2654373B2 (ja) * 1995-03-14 1997-09-17 東京焼結金属株式会社 内接歯車式流体装置
US6089841A (en) * 1998-06-26 2000-07-18 General Motors Corporation Crescent gear pump
GB0412723D0 (en) * 2004-06-08 2004-07-07 Newton Alan R Offset drive direct ratio gear coupling
DE602007012824D1 (de) * 2007-03-16 2011-04-14 Yamada Mfg Co Ltd Innenzahnradpumpe
JP2018083579A (ja) * 2016-11-25 2018-05-31 トヨタ紡織株式会社 減速装置

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191216508A (en) * 1912-07-15 1913-06-05 Jens Nielsen Improvements in and relating to Rotary Pumps, Engines and Machines.
US2091317A (en) * 1934-10-13 1937-08-31 Myron F Hill Gear tooth curve
DE1266134B (de) 1960-09-26 1968-04-11 Otto Eckerle Zahnradpumpe
AT292464B (de) 1968-11-18 1971-08-25 Hohenzollern Huettenverwalt Hydraulische Zahnradmaschine
DE2024339C2 (de) * 1969-10-27 1983-02-03 Fürstlich Hohenzollernsche Hüttenverwaltung Laucherthal, 7480 Sigmaringen Zahnradverdrängermaschine für Flüssigkeiten, insbesondere Zahnradpumpe
DE2318753C2 (de) * 1973-04-13 1984-11-08 Eisenmann, Siegfried, Dipl.-Ing., 7960 Aulendorf Zahnradmaschine
US3907470A (en) * 1971-08-19 1975-09-23 Hohenzollern Huettenverwalt Gear machine
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
JPS5675989A (en) 1981-06-23
EP0028349A1 (fr) 1981-05-13
ATE4137T1 (de) 1983-07-15
JPH0238798B2 (fr) 1990-08-31
US4386892A (en) 1983-06-07
DE2943948A1 (de) 1981-05-27
DE2943948C2 (fr) 1988-02-04

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