EP0614510B1 - Machine a engrenages - Google Patents

Machine a engrenages Download PDF

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Publication number
EP0614510B1
EP0614510B1 EP92923390A EP92923390A EP0614510B1 EP 0614510 B1 EP0614510 B1 EP 0614510B1 EP 92923390 A EP92923390 A EP 92923390A EP 92923390 A EP92923390 A EP 92923390A EP 0614510 B1 EP0614510 B1 EP 0614510B1
Authority
EP
European Patent Office
Prior art keywords
tooth
region
involute
machine according
geared machine
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
EP92923390A
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German (de)
English (en)
Other versions
EP0614510A1 (fr
Inventor
Horst Weidhaas
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.)
John S Barnes GmbH
Original Assignee
John S Barnes 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 John S Barnes GmbH filed Critical John S Barnes GmbH
Publication of EP0614510A1 publication Critical patent/EP0614510A1/fr
Application granted granted Critical
Publication of EP0614510B1 publication Critical patent/EP0614510B1/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
    • 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
    • Y10T74/19949—Teeth
    • Y10T74/19963—Spur
    • Y10T74/19972—Spur form

Definitions

  • the invention relates to a gear machine with at least two meshing gears according to the preamble of claim 1.
  • gear machine refers to both gear pumps and motors that have at least one pair of meshing gears (e.g. FR-A-2368622 or FR-A-2151943). With the two meshing gears, both an external toothing and an internal toothing can be provided.
  • an externally toothed spur gear referred to as an outer gear meshes with an internally toothed spur gear referred to as a ring gear.
  • the tooth flanks of the meshing wheels are provided with different curve sections and thus create a so-called cyclovent toothing.
  • a common involute is provided in the central region of the tooth flank, which continues toward the head region of the tooth in an arc region which merges tangentially into a subsequent straight section. This then immediately cuts the top surface of the tooth. Overall, this creates a straight line of engagement at the pitch point in the area of the involute ensured. Due to the design of the tooth flank of the tooth, in the operation of the gear machine, even in the event of manufacturing errors or in the event of load-related deformations of the individual teeth that are in engagement with one another, engagement shocks can be avoided. This results in the machine running very quietly.
  • An embodiment of the gear machine is particularly preferred in which the arc region is designed as a circular arc, the radius of curvature of which corresponds to the radius of curvature of the involute region immediately adjacent to the arc region, the involute and the arc region preferably merging tangentially.
  • This configuration results in a very uniform power transmission from a gear connected to a drive to the driven gear. The vibration excitation of the two meshing gears is reduced to a minimum.
  • An embodiment of the gear machine is particularly preferred in which the distances of the transition between the straight area and the arc area or the arc area and the involute measured from the end face of the tooth head are approximately in a ratio of 1: 2. Because of this configuration, a particularly uniform power transmission results near the head of a tooth, so that vibration excitation, which leads to noise within the gear machine, is also minimal.
  • an embodiment of the gear machine is particularly preferred in which the tooth flank in the region of the tooth base is designed in the form of a cycloid-like curve, in particular a cycloid, which directly adjoins the involute provided in the central region of the tooth flank in order to avoid an undercut.
  • the right tooth flanks 7 and 9 have in the area of the tooth tip 10 an involute 13 extending from the end face 11 of the tooth tip, which extends from the tooth tip over the central area of the tooth flank to the foot area 15.
  • a conventional undercut 17 is provided in the foot area itself, an edge 19 being clearly visible in the transition area between the involute 13 and the undercut 17. The undercut serves to prevent an entry shock when a new tooth of another gear assigned to the gear 1 enters.
  • FIG. 1 shows that the left tooth flanks 21 have a modified profile compared to known flanks 7 and 9.
  • An involute 25 is again provided in the central region of the tooth flank, to which an arc region 27 adjoins in the upper section facing the tooth tip 10, which in turn continues into a straight section 29.
  • the straight section 29 continues directly up to the end face 11 of the gear wheels 3 and 5, so that an edge 31, which forms a negative cutting edge, is formed here alone — outside of the active tooth flank.
  • the involute 25 in the foot region 15 of tooth 3 or 5 is continuously transitioned.
  • a cycloid 33 adjoins the involute 25, which results in an extension of the active tooth flank.
  • cycloids are used to address a cycloid-like curve which therefore deviates from a drochoid and is preferably designed as a cycloid in order to achieve a particularly smooth transition.
  • the course of the left flank 21 is shown even more clearly from the enlarged illustration of an individual tooth, for example tooth 5, shown in FIG.
  • the transition between the central region designed as involute 25 and the circular arc 27 is marked with x1.
  • the transition point between the arc region 27 and the straight section 29 is indicated in FIG. 2 by x2.
  • the transition between the involute and the subsequent cycloid 33 is marked with x3.
  • FIG. 2 a few auxiliary lines are also shown in broken lines, which are explained in more detail below:
  • an imaginary, first straight line G1 is drawn which intersects the tooth flank at the point x1.
  • a second imaginary straight line G2 runs parallel to the end face 11 and intersects the tooth flank at the point x2.
  • the distance between the end face 11 and the straight line G1 is identified by L y1 , the distance between the end face 11 and the straight line G2 by L y2 .
  • the tangent T to the straight line section 29 is drawn in the region of the edge 31 which intersects the end face 11 at an angle ⁇ .
  • the curvature of the arc region 27 is clearly recognizable by the auxiliary line G3.
  • This is preferably designed as a circular arc, the radius of curvature of the circular arc being selected to be as large as the radius of curvature of the involute 25 before it reaches the transition x1.
  • the flank sections 25 and 27 are formed tangentially merging into one another, so that there is a particularly soft transition between the different tooth flank regions at point x1.
  • the curve bend 27 also merges seamlessly into the straight section 29, since the two flank sections at point x2 are tangent to each other.
  • the angle ⁇ of the tangent T to the straight line section 29 in the region of the edge 31 is chosen to be as large as possible. It is in the range of approximately 45 ° and can vary by approximately + 5 ° to 10 °.
  • the center of the tooth M is shown by a dashed line.
  • the distance from the edge 31 to the center of the tooth is identified by L x1 , the distance from the corresponding edge 32 of the right tooth flank 9 by L x2 .
  • L x1 is smaller than the distance L x2 , that is to say that the tooth edge 31 springs back with respect to the edge 32, which is known in the prior art. In this way 25 entry shocks are avoided during operation of the gear machine using the tooth flank described here.
  • the radii of curvature of the cycloids 33 and that of the involutes 25 are preferably selected to be approximately the same size in the region of the transition x3. Practically identical radii of curvature have proven particularly useful.
  • the active tooth flank 21 is extended far into the region of the tooth base 15. This means that during operation of the gear machine, the forces to be transmitted can be transmitted over a very large tooth flank area, so that the gear machine runs very smoothly.
  • the radius of the circle tangent to the tooth flank in the area x2 is chosen so large that the imaginary one The center of this circle lies within the tooth.
  • the circle tangent to the tooth flank in the area x3 has a larger radius which is chosen so large that the imaginary center of this circle comes to lie outside the tooth.
  • the shape of the cycloid 33 is chosen so that when a new tooth enters, an engagement shock with the edge 31 is avoided, but on the other hand a very early power transmission is possible.
  • the tooth profile is composed of several different curve sections, which are selected so that a straight line of engagement is formed at the pitch point in the area of the involute, which, based on the pitch point, merges into a curved line of engagement in the area of the cycloid .
  • FIG. 3 shows two gears 40 and 50 of a gear machine.
  • An external toothing is shown here as an example.
  • Reference numerals in the figures 1 and 2 have already been used, are reused in Figure 3. The description of the associated parts can be omitted here. While FIGS. 1 and 2 show teeth which have the flank according to the invention on one side and a known flank on the other side, in FIG. 3 all teeth of the two gear wheels 40 and 50 are equipped on both sides with the flanks according to the invention.
  • a tooth 51 is in engagement between two teeth 41 and 43. Because the involute of the central tooth flank 25 is continued in the region of the tooth tip 10 of the tooth 43 by a curved curve 27 or by a straight section 29, the edge 31 jumps of the tooth 43 so far back that an engagement shock is reliably avoided in the region of the tooth base 15 of the tooth 53 adjacent to the tooth 51.
  • an undercut as is shown, for example, in FIG. 1, is avoided in the region of the tooth base at tooth 53. Rather, its central flank area, or its involute 25, is continued by a cycloid 33, against which the active flank 25 of tooth 43 is almost still in contact.
  • the gear 50 has a further tooth 55 to the left of the tooth 51, which almost touches the tooth 41 of the gear 40.
  • a fluid enclosed in the interdental space 61 increases comes under pressure and exits under high pressure through the remaining gap 63 between the head 10 of the tooth 41 and the foot 15 of the tooth 55.
  • the fluid or oil under high pressure has proven to be extraordinarily strong. This reduces friction between tooth 41 and tooth 55 to a minimum.
  • noise reduction is optimal, since head interferences largely be avoided.
  • a further reduction in noise occurs in that the lubrication is not penetrated by the lubricating film build-up when the teeth 41 and 55 converge, even in the further course of the involutes of the teeth 41 and 55.
  • edge 31 strikes the cycloid 33 of an adjacent tooth, but that this edge 31 can be used as a cutting edge, so that a very good radial run-in is obtained while maintaining the advantages of the Cyclovent teeth is guaranteed.
  • the edge 31 can serve as a cutting edge and remove material from the machine or pump housing.
  • this edge 31 can act on a filler piece customary in pumps with internal teeth and there ensure a good radial run-in.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Gears, Cams (AREA)
  • Retarders (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Gear Transmission (AREA)

Claims (12)

  1. Machine à engrenages comportant au moins deux roues dentées engrénants, dont le profil denté se compose de différentes formes de profil, caractérisée en ce que les flancs (21) des différentes dents (3, 5 ; 40, 50), correspondent dans la zone médiane à une développante (25) suivie d'une zone courbe (27) rejoignant de façon tangentielle un segment de droite (29) qui coupe directement la surface frontale (11) de la dent, pour avoir une ligne d'attaque droite.au point de roulement dans la zone de la développante.
  2. Machine à engrenages selon la revendication 1, caractérisée en ce que la zone courbe (27) est de préférence en arc de cercle.
  3. Machine à engrenages selon la revendication 1 ou 2, caractérisée en ce qu'on réalise un passage en douceur entre la développante (25) de la zone médiane et la zone courbe (27) par un rayon de courbure de la zone courbe qui est sensiblement égal au rayon de courbure de la développante avec la jonction de la zone courbe, et en ce que la développante et la zone courbe se rejoignent de préférence tangentiellement.
  4. Machine à engrenages selon l'une des revendications 1 à 3, caractérisée en ce que la développante (25) rejoint tangentiellement la zone courbe (27) et le rayon de courbure de la zone courbe est identique à celui de la zone directement adjacente de la développante de la zone médiane.
  5. Machine à engrenages selon l'une des revendications 1 à 4, caractérisées en ce qu'une droite (G1), imaginaire parallèle à la surface frontale (11) d'une dent (3, 5), coupant le passage entre la développante (25) et la zone courbe (27), est distante de la distance (Ly) par rapport à la surface frontale, cette distance étant sensiblement double de la distance d'une seconde droite (G2), fictive, parallèle à la surface de tête, et qui coupe le passage entre l'arc de cercle (27) et le segment de droite (29).
  6. Machine à engrenages selon la revendication 5, caractérisée en ce que le rapport des distances des droites fictives et de la surface de tête est compris entre 40:60 et 60:40 de préférence entre 55:45 jusqu'à 45:55 et est il notamment égal à 50:50.
  7. Machine à engrenages selon l'une des revendications 1 à 6, caractérisée en ce que les flancs (21) des différentes dents (3, 5) présentent dans la zone (15) du pied de la dent, un tracé cycloïdale de préférence un tracé correspondant à une cycloïde (33).
  8. Machine à engrenages selon l'une des revendications 1 à 7, caractérisée en ce que le rayon de courbure de la cycloïde (33) correspond sensiblement au rayon de courbure de la zone adjacente de la développante (25).
  9. Machine à engrenages selon la revendication 8, caractérisée en ce que le rayon de courbure de cycloïde (33) est égal à celui de la zone directement adjacente de la développante (25).
  10. Machine à engrenages selon la revendication 8 ou 9, caractérisée en ce que la cycloide (33) rejoint tangentiellement la courbe conduisant à la zone du pied de la dent voisine.
  11. Machine à engrenages selon la revendication 1 à 10, caractérisée en ce que la forme de dent de la zone de tête, supérieure de dent (25, 27, 29) est liée à la forme inférieure de la dent (25, 33, 23).
  12. Machine à engrenages selon l'une des revendications 1 à 11, caractérisée en ce que les roues dentées conviennent pour une denture intérieure ou une denture extérieure.
EP92923390A 1991-11-27 1992-11-12 Machine a engrenages Expired - Lifetime EP0614510B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4138913 1991-11-27
DE4138913A DE4138913C1 (fr) 1991-11-27 1991-11-27
PCT/EP1992/002592 WO1993011357A1 (fr) 1991-11-27 1992-11-12 Machine a engrenages

Publications (2)

Publication Number Publication Date
EP0614510A1 EP0614510A1 (fr) 1994-09-14
EP0614510B1 true EP0614510B1 (fr) 1996-01-24

Family

ID=6445651

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92923390A Expired - Lifetime EP0614510B1 (fr) 1991-11-27 1992-11-12 Machine a engrenages

Country Status (7)

Country Link
US (1) US5454702A (fr)
EP (1) EP0614510B1 (fr)
JP (1) JPH07501375A (fr)
AT (1) ATE133472T1 (fr)
DE (2) DE4138913C1 (fr)
ES (1) ES2082520T3 (fr)
WO (1) WO1993011357A1 (fr)

Families Citing this family (26)

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DE19615849B4 (de) * 1996-04-20 2004-07-08 Bosch Rexroth Ag Innenzahnradmaschine (Hydropumpe oder Hydromotor)
JPH1089443A (ja) * 1996-09-13 1998-04-07 Akitoshi Kitano 楕円形歯車
JP3358494B2 (ja) * 1997-05-20 2002-12-16 トヨタ自動車株式会社 歯車および歯車の歯面修整方法
US6164944A (en) * 1999-03-21 2000-12-26 Damilerchrysler Corporation Random error generation of tooth index to eliminate pump noise
US7665380B2 (en) * 2000-02-29 2010-02-23 Kabushiki Kaisha Toyota Chuo Kenkyusho Hypoid gear design method
US6814409B2 (en) 2001-04-12 2004-11-09 A-Dec, Inc. Hydraulic drive system
DE10125067A1 (de) * 2001-05-23 2002-12-12 Bosch Gmbh Robert Tellerrad
NL1020562C2 (nl) * 2002-05-08 2003-11-11 Norma B V Kroonwiel.
DE10302964A1 (de) * 2003-01-25 2004-08-05 Continental Teves Ag & Co. Ohg Hochdruckinnenzahnradpumpe
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
US8312785B2 (en) * 2008-06-20 2012-11-20 Graco Minnesota Inc. Involute gear teeth for fluid metering device
DE102009039648B3 (de) * 2009-08-28 2011-02-24 Keiper Gmbh & Co. Kg Beschlag für einen Fahrzeugsitz und Fahrzeugsitz
JP5632158B2 (ja) * 2009-12-24 2014-11-26 ポリプラスチックス株式会社 騒音予測方法
DE102010021771A1 (de) * 2010-05-27 2011-12-01 Schottel Gmbh Kegelzahnrad eines Kegelgetriebes
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
CN103671820B (zh) * 2012-09-21 2017-12-12 恩普乐股份有限公司 齿轮及其制造方法
ITMI20122168A1 (it) * 2012-12-18 2014-06-19 Mario Antonio Morselli Macchina idraulica a ingranaggi e relativa ruota dentata
US8863602B2 (en) * 2013-01-09 2014-10-21 Weidong Gao Oil field pump unit hybrid gear reducer
JP6188131B2 (ja) * 2013-06-14 2017-08-30 株式会社エンプラス 歯車
WO2015193809A1 (fr) * 2014-06-17 2015-12-23 Mario Antonio Morselli Engrenage denté transmetteur de couple monodirectionnel
DE102014221456A1 (de) * 2014-10-22 2016-04-28 Zf Friedrichshafen Ag Zahnradpaarung eines Getriebes
DE102016207093B4 (de) * 2016-04-26 2019-01-31 Eckerle Industrie-Elektronik Gmbh Zahnradfluidmaschine
IT201800005956A1 (it) * 2018-06-01 2019-12-01 Macchina volumetrica ad ingranaggi con denti elicoidali
JP7354914B2 (ja) * 2020-04-16 2023-10-03 トヨタ自動車株式会社 駆動装置
DE102021206054A1 (de) * 2020-06-17 2021-12-23 Sms Group Gmbh Getriebe für einen Walzwerksantrieb, Walzwerksantrieb mit einem Getriebe sowie die Verwendung des Getriebes als Walzwerksgetriebe
US11707792B2 (en) * 2020-09-28 2023-07-25 GM Global Technology Operations LLC Scattered topography rolling of powered metal gears

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Also Published As

Publication number Publication date
JPH07501375A (ja) 1995-02-09
ES2082520T3 (es) 1996-03-16
ATE133472T1 (de) 1996-02-15
DE4138913C1 (fr) 1993-06-09
EP0614510A1 (fr) 1994-09-14
DE59205192D1 (de) 1996-03-07
US5454702A (en) 1995-10-03
WO1993011357A1 (fr) 1993-06-10

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