EP0328745B1 - Machine à engrenages internes - Google Patents

Machine à engrenages internes Download PDF

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Publication number
EP0328745B1
EP0328745B1 EP88118905A EP88118905A EP0328745B1 EP 0328745 B1 EP0328745 B1 EP 0328745B1 EP 88118905 A EP88118905 A EP 88118905A EP 88118905 A EP88118905 A EP 88118905A EP 0328745 B1 EP0328745 B1 EP 0328745B1
Authority
EP
European Patent Office
Prior art keywords
tooth
gear
internal
openings
machine according
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
EP88118905A
Other languages
German (de)
English (en)
Other versions
EP0328745A3 (en
EP0328745A2 (fr
Inventor
Reinhard Ing.-Grad. Pippes
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.)
Eckerle Rexroth GmbH and Co KG
Original Assignee
Otto Eckerle GmbH and Co KG
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 Otto Eckerle GmbH and Co KG filed Critical Otto Eckerle GmbH and Co KG
Publication of EP0328745A2 publication Critical patent/EP0328745A2/fr
Publication of EP0328745A3 publication Critical patent/EP0328745A3/de
Application granted granted Critical
Publication of EP0328745B1 publication Critical patent/EP0328745B1/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
    • 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
    • F04C2/101—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 with a crescent-shaped filler element, located between the inner and outer intermeshing members

Definitions

  • the invention relates to an internal gear machine, in particular an internal gear pump, with the features according to the preamble of patent claim 1.
  • the liquid in the pressure chamber is displaced from the tooth gaps of the two wheels by the increasing tooth engagement between the pinion and the ring gear and is thereby conveyed to the outlet.
  • This displacement process forces the liquid to flow axially and radially past the teeth entering the tooth gaps.
  • the gap between the teeth available for this purpose is already relatively small at the beginning of the tooth engagement, so that even before the flank contact there is a relatively large flow resistance, which increases even further when this gap further decreases and ultimately increases as the tooth engagement increases decreases the value zero. This high flow resistance manifests itself as a power loss.
  • Gear machines are known in which this power loss is reduced in that the ring gear has radial openings which connect the outer circumference of the ring gear to the inside thereof in the region of the tooth gaps and through which the delivery medium is conveyed to the outlet. Because of the breakthroughs that can Pumped medium, when the gaps between the teeth become smaller, also leave the tooth gap in the direction of the breakthroughs, so that no squeezing liquid can arise, especially shortly before full tooth engagement. A further improvement in this direction results in a known gear machine of the type specified at the outset (US Pat. No.
  • a gear machine with external teeth in which relief channels in the non-load-bearing tooth flanks run obliquely from the tooth head to the tooth base (GB-A 15 47 944).
  • the relief channels are connected to axial channels in the gear wheels, which lead to the inlet or outlet of the gear machine.
  • the formation of such axial channels in the gears and their connection to the individual relief channels is relatively complex.
  • the invention is therefore based on the object of providing an internal gear machine of the type specified which enables a further reduction in the losses caused by the gap flow described without a significant reduction in the strength of the ring gear.
  • the tooth head there are no openings through the teeth of the ring gear to the tooth head, but the remaining openings opening into the tooth gaps are moved into the non-load-bearing tooth flank in such a way that they create a connection between the tooth head and the tooth base.
  • the medium located between the tooth tips of the ring gear and the tooth feet of the pinion with less flow resistance can reach the area of the non-load-bearing tooth flank and break through there. Since the breakthrough leads through the ring gear to the outlet, there is no loss of delivery volume.
  • the tooth head is withdrawn relative to its circumferential surface which determines the tip circle diameter over the height of the tooth-head edge of each opening.
  • This local retraction of the tooth head on the one hand increases the inflow space for the liquid to the opening. This is particularly the case if the tooth tip is withdrawn in the mentioned area over the entire width of the tooth, because this means that a larger flow cross-section is also available for the fluid located axially away from the opening to promote the opening.
  • the retraction of the tooth head in the part in which the opening cuts through the tooth surface on the peripheral surface of the teeth prevents the resulting edge from removing the lubricating film of the tooth heads from the filler piece or from even having a milling effect on the filler piece. In both cases, a sustainable malfunction of the internal gear machine would occur soon.
  • the tooth tip can be withdrawn in the part of the opening mentioned either as a flat chamfer or in the form of a concave groove, but advantageously also in the form of a combination of the two.
  • the lubrication film formation on the filler is promoted in the region of the chamfer and in the transition between this and the flat peripheral surface of the tooth head, while the subsequent groove forms the flow cross-section for the amount of liquid that adheres to the Tooth ends located and must be promoted for breakthrough.
  • a single opening per tooth gap with a correspondingly larger cross section is more favorable.
  • the breakthroughs can be as simple holes, i.e. H. with a circular cross-sectional border.
  • a cross-sectional configuration of the openings is advantageous, according to which the cross-section, at least on the side of the opening penetrating the tooth flank, is straight and limited parallel to the flank line of the corresponding tooth. Because this also creates a straight line of intersection with the tooth flank in the area of the tooth head, which runs parallel to the tooth direction (flank line).
  • the height of the tip relief described above can be kept to a minimum
  • the flow cross section of the opening is larger, especially in the area of the tooth flank. This also shortens the flow path between the tooth ends and the opening.
  • the invention therefore proposes to construct the ring gear from two separate parts, the parting or connecting plane of which lies in the area of the openings.
  • the ring gear is expediently divided exactly in the plane of symmetry. This measure makes it possible to produce the two ring gear parts by sintering or by extrusion, the parts forming the openings can be molded directly. But even when the recesses forming the openings are machined, the separation gives an advantage because the side faces of the ring gear are much more easily accessible.
  • an internally toothed ring gear meshes with an externally toothed pinion 2.
  • the pressure chamber 4 is separated from the suction chamber 5 of the internal gear pump by a filler piece 3.
  • the filler 3 is supported on a rotatably mounted filler pin 6.
  • the ring gear 1 is mounted directly in a pot-shaped housing 7 and has radial openings 8, through which the pumped medium from the pressure chamber 4 can flow to the outlet, not shown.
  • the pot housing 7 is closed by a bearing cover 9.
  • two openings 8 arranged next to one another are provided for each tooth gap. From the illustration according to FIG. 2 it can be seen that in the area of the pressure chamber 4 the teeth 12 of the pinion 2 increasingly enter the tooth spaces 13 between the teeth 11 and in this way displace the liquid located in the tooth spaces 13 therefrom.
  • the openings 8 are arranged asymmetrically to the radial center plane of the tooth gaps 13 such that they penetrate the tooth flank 14 of the teeth 11 of the ring gear 1 rearward in the direction of rotation of the gear wheels 1, 2.
  • the diameter of the openings 8 is selected such that they grip the tooth base of both the load-bearing and the non-load-bearing flank of the teeth 11 and the tooth head in the region of the non-load-bearing flank 14.
  • the part of the tooth head 15 which is penetrated by the edge of the opening 8 is withdrawn in a manner which is particularly clear from FIG. 5.
  • a chamfer 16 extending over the entire tooth width, which in turn is followed by a groove 17 which is greater in height than the chamfer 16 and also extends over the entire tooth width.
  • the embodiment according to FIGS. 4 and 5 differs therefrom by a different cross-sectional shape of the openings 8 '. 4, the openings 8 'taper in their cross-section from the inside to the outside and, especially in the region of the non-load-bearing tooth flank 14, have a rectilinear limitation of their cross-section which runs parallel to the flank line of the teeth. This results in a correspondingly straight line of intersection 18 with the tooth head, which is aligned with the edge formed at the transition between the chamfer 16 and the groove 17.
  • the ring gear 1 ' is divided in its central plane, which is also the plane of symmetry of the openings 8', in order to make it easier to manufacture the described shape of the openings 8 ', as explained at the beginning .
  • the two halves of the ring gear 1 ' are by means only indicated, e.g. connected by a screw connection 19 made at several circumferential points through the teeth.
  • FIG. 1 shows the openings 8 are not aligned with their longitudinal axis radially to the center of the ring gear 1, but inclined to the corresponding radius at an acute angle.
  • the mouth of the openings 8 on the peripheral surface of the ring gear 1 is offset against the direction of rotation of the ring gear 1 with respect to the mouth on the tooth side.
  • the reason for this position of the breakthroughs 8 is the possibility offered thereby to keep the diameter of the breakthroughs larger and thus the flow resistance smaller.

Claims (9)

  1. Machine à engrenage interne, en particulier pompe à engrenage interne, comportant une couronne à denture interne (1, 1'), un pignon à denture externe (2) en prise avec la couronne, et une fourrure (3) agencée entre couronne et pignon, la couronne présentant des perçages (8, 8') qui conduisent largement radialement vers une sortie et qui relient la périphérie externe de la couronne a son côté interne dans la zone des creux de dent (13) et des sommets de dent, caractérisée en ce que les perçages (8, 8') qui débouchent dans les creux de dent (13) sont chaque fois décalés dans les flancs de dent (14) non porteurs qui délimitent les creux de dent d'un côté, au point qu'ils réalisent en même temps une liaison entre le pied de dent et le sommet de dent.
  2. Machine à engrenage interne suivant la revendication 1, caractérisée en ce que, sur la hauteur du bord, du côté du sommet de dent, de chaque perçage (8, 8'), le sommet de dent est diminué par rapport à sa surface périphérique (15) qui détermine le diamètre du cercle de sommet.
  3. Machine à engrenage interne suivant la revendication 2, caractérisée en ce que le sommet de dent est diminué en forme de chanfrein (16) sur toute la largeur de la dent.
  4. Machine à engrenage interne suivant l'une ou l'autre des revendications 2 et 3, caractérisée en ce que le sommet de dent est diminué en forme de gorge (17) sur toute la largeur de la dent.
  5. Machine à engrenage interne suivant l'une ou l'autre des revendications 3 et 4, caractérisée en ce que le chanfrein (16) s'étend sur une partie, partant de la surface périphérique (15) de la dent, de la hauteur du bord, du côté du sommet de dent, du perçage (8, 8') et en ce qu'il se raccorde là à la gorge (17).
  6. Machine à engrenage interne suivant l'une quelconque des revendications 1 à 5, caractérisée en ce que la section transversale du perçage (8') est délimitée de façon rectiligne au moins sur son côté qui pénêtre dans le flanc de dent (14) et en ce que le côté droit s'étend parallèlement à la ligne des flancs.
  7. Machine à engrenage interne suivant l'une quelconque des revendications 3 à 6, caractérisée en ce que le bord rectiligne (18), du côté du sommet de la dent, du perçage (8') est à fleur de l'arête du chanfrein (16) ou de la gorge (17).
  8. Machine à engrenage interne suivant l'une quelconque des revendications 1 à 7, caractérisée en ce que la couronne (1') est constituée de deux parties indépendantes dont le plan de séparation est situé dans la zone des perçages (8').
  9. Machine à engrenage interne suivant l'une quelconque des revendications 1 à 8, caractérisée en ce que l'axe des perçages (8, 8') s'étend de façon inclinée suivant un angle aigu par rapport au rayon correspondant de la couronne (1).
EP88118905A 1988-02-19 1988-11-12 Machine à engrenages internes Expired - Lifetime EP0328745B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3805186A DE3805186A1 (de) 1988-02-19 1988-02-19 Innenzahnradmaschine
DE3805186 1988-02-19

Publications (3)

Publication Number Publication Date
EP0328745A2 EP0328745A2 (fr) 1989-08-23
EP0328745A3 EP0328745A3 (en) 1990-03-07
EP0328745B1 true EP0328745B1 (fr) 1992-05-06

Family

ID=6347724

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88118905A Expired - Lifetime EP0328745B1 (fr) 1988-02-19 1988-11-12 Machine à engrenages internes

Country Status (4)

Country Link
US (1) US4934913A (fr)
EP (1) EP0328745B1 (fr)
JP (1) JPH0650113B2 (fr)
DE (2) DE3805186A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4104397C2 (de) * 1990-03-09 1993-12-16 Voith Gmbh J M Innenzahnradpumpe
CH682939A5 (de) * 1990-03-09 1993-12-15 Voith Gmbh J M Innenzahnradpumpe.
SI9300276A (en) * 1993-05-24 1994-12-31 Drago Cendak High-pressure gear mechanism
EP1396639A1 (fr) * 2002-09-03 2004-03-10 Techspace Aero S.A. Pompe volumétrique rotative à gerotor
US10443597B2 (en) 2016-01-12 2019-10-15 Hamilton Sundstrand Corporation Gears and gear pumps

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE296588C (fr) *
US751196A (en) * 1904-02-02 Rotary pump
US1496737A (en) * 1922-06-03 1924-06-03 Viking Pump Company Rotary pump, motor, or engine
US1739139A (en) * 1925-05-18 1929-12-10 Hiram H Haight Pump
US2601003A (en) * 1946-05-17 1952-06-17 Bendix Aviat Corp Gear pump
DE1245738B (de) * 1961-09-29 1967-07-27 Thomas Hindmarch Zahnradpumpe
US3448615A (en) * 1967-01-03 1969-06-10 American Meter Co Rotary meter,direct drive
CH483563A (de) * 1967-11-30 1969-12-31 Von Roll Ag Speiseeinrichtung für Hydroeinheiten
US3981646A (en) * 1973-03-15 1976-09-21 Lucas Aerospace Limited Gear pumps and motors
US4233005A (en) * 1978-01-18 1980-11-11 Lucas Industries Limited Hydraulic gear pump with recesses in non-working gear flanks
JPS54140309U (fr) * 1978-03-23 1979-09-29
GB1547944A (en) * 1978-04-05 1979-07-04 Rolls Royce Gear pumps or motors
DE2933493A1 (de) * 1979-08-18 1981-03-26 Daimler-Benz Aktiengesellschaft, 70567 Stuttgart Zahnradpumpe

Also Published As

Publication number Publication date
DE3805186A1 (de) 1989-08-31
JPH01267378A (ja) 1989-10-25
EP0328745A3 (en) 1990-03-07
DE3870853D1 (de) 1992-06-11
US4934913A (en) 1990-06-19
EP0328745A2 (fr) 1989-08-23
JPH0650113B2 (ja) 1994-06-29

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