WO2018172059A1 - Machine à engrenages intérieurs - Google Patents

Machine à engrenages intérieurs Download PDF

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Publication number
WO2018172059A1
WO2018172059A1 PCT/EP2018/055418 EP2018055418W WO2018172059A1 WO 2018172059 A1 WO2018172059 A1 WO 2018172059A1 EP 2018055418 W EP2018055418 W EP 2018055418W WO 2018172059 A1 WO2018172059 A1 WO 2018172059A1
Authority
WO
WIPO (PCT)
Prior art keywords
filler
pinion
pressure
internal gear
yoke
Prior art date
Application number
PCT/EP2018/055418
Other languages
German (de)
English (en)
Inventor
Steffen SCHÖNTHALER
Original Assignee
Voith Patent 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 Voith Patent Gmbh filed Critical Voith Patent Gmbh
Publication of WO2018172059A1 publication Critical patent/WO2018172059A1/fr

Links

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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • F04C15/0019—Radial sealing elements specially adapted for intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/04—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for reversible machines or pumps
    • 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 a reversible gear machine with a filler.
  • gear machines can be operated as a pump or generator.
  • an internal gear machine is known. Such machines can be used as a gear pump.
  • a longitudinally divided filler is provided.
  • the filler is symmetrical with respect to a radially extending plane of symmetry.
  • operation of the internal gear pump is reversible, i.
  • the pump can deliver in both directions.
  • the filler is multi-part, divided in the circumferential direction, constructed. In the description it is mentioned that the filler could also be constructed in one piece. However, a one-piece filler is not disclosed.
  • a gear pump with a filling piece which has two legs.
  • the two legs are connected by a bridge and include an internal volume.
  • the pressure in the inner volume is established by a circumferentially formed opening to the pressure or suction area by pressure equalization.
  • the filler is not symmetrical.
  • the filler used in gear pumps are also referred to as sickle.
  • multi-part compensation elements are used for volumetric efficiency increase of internal gear pumps. These components function independently of each other and are usually used in asymmetric design.
  • the filler pieces are often symmetrical, but usually constructed in several parts.
  • the disadvantage of this construction is the susceptibility to negative pressures, causing a collapse can result or system vibrations, in particular a tendency to vibration.
  • such multi-section pumps exhibit inertia in the pressure buildup and depressurization due to the movable parts and / or the freedom of movement between the spline components.
  • Another disadvantage is that tilting is possible through tolerances and a movement play. Compared to a one-piece patch result from a multi-part higher manufacturing costs.
  • the object of the invention is to provide a filler for an internal gear machine and an internal gear machine, with a more stable operation can be achieved.
  • the filler comprises an inner side and an outer side.
  • the inner side is connected to the outside via a first yoke and a second yoke, wherein an internal volume is enclosed by the filler.
  • the filler is inflatable.
  • the volume of the enclosed inner volume is adjustable by a pressure prevailing in the inner volume or the pressure ratio of inner volume and the pressure acting on the outside of the filler.
  • the connections between the first and second yoke and the inside are made hydraulically tight. Furthermore, the connections between the first and second yoke and the outside are made hydraulically tight.
  • the internal volume is limited and completed.
  • the inside is spaced from the outside by a distance.
  • the filler is formed symmetrically symmetrical to a the inside and the outside intersecting plane of symmetry.
  • the filler is provided for installation within a cavity formed by an internally toothed ring gear and an externally toothed pinion.
  • the inside is provided for a radially inwardly from the outside arrangement with respect to the radial direction of the pinion.
  • the inside is designed for a partial abutment on the external toothing of the pinion.
  • the outside is disposed radially outward from the inside with respect to the radial direction of the pinion.
  • the outside is designed for a concern with the internal toothing of the ring gear.
  • the filler is provided with at least one supply opening for pressure equalization, preferably with the pressure side.
  • the pressure in the inner volume automatically adapts to this pressure prevailing on the pressure side.
  • the dynamics of the pressure change of the internal volume can be predetermined.
  • the sealing effect can be increased compared to the suction side and pressure side. This reduces the leakage losses.
  • At least one supply opening is formed in the inside and / or the outside in the filler. In a particularly preferred embodiment, the formed at least one supply opening in the inside. This is easier to manufacture.
  • supply opening is provided on the outside.
  • the supply opening is designed to intersect the plane of symmetry in the filler.
  • depressions of the control geometry are aligned in the circumferential direction.
  • a control geometry assigned to the supply opening is provided, wherein the control geometry in at least one of the walls comprises at least one formed depression.
  • the control geometry interacts with the supply opening.
  • the supply opening is disposed within one of the recesses of the control geometry.
  • the inside and the outside are curved to provide a spring elasticity.
  • the inner side and / or the outer side may be configured in the shape of a leaf spring.
  • the filler is integrally formed.
  • a bulge of the inner volume is formed in a transition region between a yoke and the inside or outside. When installed, the transition area forms an entry phase and exit phase depending on the operating mode.
  • a geometry for providing an optimized pressure surface effect is achieved. Due to the internal pressure, the filler has the tendency to expand in all directions. This could result in unwanted deformations. By the bulges a preferred deformation can be achieved. An equal fitting geometry of the teeth can be achieved.
  • At least one yoke is preferably the first and the second yoke formed with a receiving geometry for receiving a storage.
  • the object underlying the invention is achieved by an internal gear machine with a filling piece according to the invention.
  • the internal gear machine for the reversing operation has an externally toothed pinion.
  • the externally toothed pinion meshes with an internally toothed ring gear.
  • pinion and ring gear By pinion and ring gear a crescent-shaped cavity is formed.
  • a filler is arranged in the crescent-shaped cavity. Through the centers of pinion and ring gear runs a plane of symmetry.
  • At least one axial disc is provided, wherein the axial disc is provided with a pressure supply bore penetrating the axial disc.
  • This pressure supply hole opens in the inner volume of the filler. This can ensure that the axial disc is acted upon on the side remote from the pinion and ring gear with fluid from the internal volume. As a result, the axial disc is pressed in the direction of pinion and ring gear. As a result, leakage losses can be reduced.
  • the filler is mounted under tension between two fixing pins arranged in the cavity.
  • the filler can be mounted under a predetermined bias and on the other hand, the assembly is particularly simple.
  • FIG. 3 shows another illustration of the filling piece from FIG. 2
  • Fig. 7 further embodiment of a filler
  • Fig. 8 section through an internal gear machine with an axial disc
  • FIG. 1 shows a section through an internal gear machine 1.
  • the venezffyradmaschinel can be operated as a pump or generator.
  • the illustrated internal gear machine 1 is designed for reversible operation.
  • the gear machine has a housing 2.
  • a pinion 3 is rotatable about a center 5 and a ring gear 4 rotatable about a Center 6 stored.
  • the pinion 3 meshes with the ring gear 4, wherein the axes of rotation of pinion 3 and ring gear 4 are spaced from each other and arranged parallel to each other.
  • a sickle-shaped extending in the axial direction cavity 7 is formed in the cavity 7, a filler 14 between two provided as a bearing 22 fixing pins 23 is arranged.
  • the filler 14 has an inner side 15 and an outer side 16.
  • the inner side 15 is connected to the outer side 16 on one side via a first yoke 17 and on the opposite side via a second yoke 18.
  • the outer side 16 is arranged to the inner side 15 in the radial direction 36 with a distance.
  • the first yoke 17 is arranged in the circumferential direction 37 to the second yoke 18 at a distance.
  • the teeth of the pinion 3 come into contact with the inner side 15, so that the cavities formed between the teeth are sealed in the radial direction 36 by the inner side 15 of the filler 14.
  • the outside 16 of the filler 14 is in touching contact with the teeth of the ring gear 4, so that the cavities formed between the teeth of the ring gear 4 are sealed by the outside 16.
  • the filler 14 By means of these sealed by the filler 14 cavities hydraulic medium, preferably a liquid such as oil, transported from the suction side 13 to the pressure side 12.
  • the filler 14 is arranged symmetrically to a plane of symmetry 8.
  • the plane of symmetry 8 extends through the middle point 15 of the axis of rotation of the pinion 3 and through the center 6 of the axis of rotation of the ring gear 4.
  • the plane of symmetry 8 coincides with the plane of symmetry 8a of the filler 14.
  • FIG. 4 An interpretation of an axial disc 25, as shown in detail in Fig. 4, can be seen. From the axial disc 25 is a pressure supply hole 24, which opens into the interior volume 19 can be seen. In the Axialthrough a Axialdruckfeld with control geometry 26 is formed. A first and a second fluid connection 9, 10 can be seen. With reference to Figures 2 and 3, the filler 14 will be described in more detail.
  • the filler 14 is provided with a supply port 20 through which a hydraulic connection is provided from the interior volume 19 to the outside.
  • the supply opening 20 is formed in the radial direction.
  • This supply opening 20 is formed in the illustrated embodiment in the inner side 15.
  • a control geometry 21 is formed, which cooperates with the supply opening 20. In the embodiment shown, the control geometry is also formed in the inner side 15.
  • control geometry 21 The extent in the circumferential direction of the control geometry 21 is designed so that it is ensured that a direct connection with the suction side 13 and the pressure side 12 does not occur during operation of the internal gear 1 and a connection of the control geometry 21 only with the between inside 15 and the teeth the pinion formed cavities is possible and about a pressure compensation takes place.
  • the extension of the control geometry in the circumferential direction is selected so that a connection of the control geometry 21 is possible only with the cavities formed by the teeth of the ring gear 4 and the outer side 16 and in turn a direct connection with the suction side 13 or pressure side 12 of the internal gear machine 1 in normal operation is not possible.
  • the control geometry 21 is formed symmetrically to the plane of symmetry 8a of the filler 14 and the supply opening 20, the symmetry plane 8a cutting, arranged.
  • the filler 14 is symmetrical to allow 4-Qadranten operation.
  • the filler 14 is integrally formed in the illustrated embodiment.
  • the inner volume 19 is enclosed in the radial and in the circumferential direction and forms a pressure chamber. Due to this closed configuration, the inner volume 19 with pressure be charged. By pressurization, puffing can be achieved. It is an elastic deformation of the filler 14th
  • the yoke 17, 18 is formed with a transition region 30, which is referred to as the entry and exit phase.
  • the inside 15 and the outside 16 are formed with a resilient geometry 34, 35.
  • the inner side 15 and the outer side 16 have the shape of a leaf spring.
  • the filler 14 was formed with bulges 32.
  • the bulges 32 have an Anpressgeometrie 33, wherein the angles of the inner surfaces of the bulge 32 in the transition region 30 are designed so that the forces generated by an internal pressure and in correlation with the fixing pins 23 contribute to a radial sealing effect. Due to the symmetrical design this is possible in the complete 4-quadrant range of a motor and generator operation.
  • a pressure equalization of the inner volume 19 of the filler 14 with the pressure side for an increased sealing effect is realized by means of a radial opening in the form of a supply opening 20.
  • This can be located on the side of the pinion 3 or the ring gear 4 and interacts with a control geometry 21, here in the form of control grooves.
  • the control geometry 21 can be varied by its design and geometry.
  • the axial disc 25 is controlled.
  • the axial disc 25 is supplied by an axial pressure supply bore 24 in the region of the inner volume 19 of the filler 14.
  • the axial disk is subjected to pressure on the side facing away from the pinion 3 and ring gear 4 and thus printed as an axial conclusion in the direction of pinion 3 and ring gear 4.
  • the filler 14 is designed by the structure so that it by the radially applied supply opening 20 with control geometry 21 on the Hohlrad- and Pinion gear is supplied with oil pressure and by the internal pressure caused by the radial forces can inflate.
  • This assumes that the filler 14 has a closed contour / cavity at least towards the suction side 13 and pressure side 12.
  • the swelling creates a radial sealing effect that automatically increases with increasing operating pressure.
  • the axial sealing takes place via the axial disc 25 and the opposite bearing cap. But it could also be provided on both sides Axialimpeden 25.
  • the geometric structure is designed so that the filler 14 is biased in the unpressurized state by utilizing the inherent resilience of the material.
  • the inner side 15 and the outer side 16 are similar to the cross section of a leaf spring, installed between the ring gear 4 and the pinion 3. Due to the distance of the fixing pins 23 used as a bearing 22, a predetermined bias can be specified in the assembled state. In addition, it is possible to increase the contact pressure by a further spring element.
  • FIG. 4 shows an axial disk 25.
  • Axial pressure fields with control geometry 26 are formed in the axial disk.
  • Dashed lines indicate kidney-shaped pockets 46 are formed on the back.
  • the kidney-shaped pockets 46 are axially defined by kidney-shaped axial piston 48, shown in phantom.
  • the kidney-shaped axial piston 48 are received in the kidney-shaped pockets 46 of the axial disc 25.
  • a seal 49 shown in phantom, provided. By the seal 49 ensures that the volume of the kidney-shaped pockets 46 is completed. If the kidney-shaped pockets 46 are then pressurized, the axial piston 48 is thereby pressed axially out of the axial disc 25 and thus out of the kidney-shaped pocket 46.
  • a support of the axial disc 25 is achieved against the housing 2 or the bearing cap.
  • a supply bore 42 shown in dashed lines, formed in the axial disc 25.
  • the supply bore 42 is connected to the pressure supply bore 24.
  • the supply bore 42 is connected to a transverse bore 41, shown in phantom.
  • the transverse bore 41 is in turn connected via a respective inflow 44 with the kidney-shaped pockets.
  • a speed controller 27 is provided.
  • Fixierbohrept 28 are formed so that the axial disc 25 can be mounted axially displaceable on the fixing pins 23.
  • FIGS. 5 and 6 show alternative embodiments of filler pieces 14.
  • the filling piece 14 shown in FIG. 5 has on both sides a curvature formed in the direction of the inner volume for receiving the fixing pins 23. It is a supply opening 20 in the axial center and also formed in the middle with respect to the circumferential direction 37 of the inner side 15 of the filler 14.
  • the supply opening is arranged in the radial direction of the filler. Instead of only one supply opening could be arranged offset in the axial direction arranged supply openings.
  • the supply opening 20 is assigned a control geometry 21.
  • FIG. 5 shows a control geometry which is formed by depressions.
  • depressions are arranged at a distance in the axial direction 38 and extend in the circumferential direction 37.
  • the dynamics of the swelling behavior or the dynamics of a pressure compensation of the inner volume 19 are also determined by the control geometry 21.
  • the depressions are tapered in the circumferential direction 37.
  • a plurality of cavities formed by the inner side 15 and the teeth of the pinion are interconnected.
  • the control geometry 21 recesses, which are configured in the circumferential direction 37 angular.
  • the control geometry comprises a plurality of depressions, which are arranged parallel to each other and spaced apart in the axial direction 38.
  • the control geometry 21 is always formed on the side facing away from the inner volume 19 side of the inner side 15 or the outer side 16.
  • FIG 7 an alternative contour of a filler 14 is shown in section.
  • the first and the second yoke are formed with an outer curvature.
  • Such a filler 14 may be supported by a bearing 22 provided in the inner volume.
  • such a filler 14 can be mounted by a arranged outside the filler and adapted to the outer contour of the filler 14 in the region of the first 17 and second yoke 18 storage 22 and also stored biased.
  • connection hole 42 is formed within the axial disc 25.
  • connection hole 42 is provided with a shutter 43.
  • the connecting hole 42 is caulked by a ball. Opening the connection hole is not provided.
  • the transverse bore is caulked by a closure 43.

Landscapes

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

Abstract

L'invention concerne une machine à engrenages intérieurs (1) pour le fonctionnement réversible avec un pignon (3) à denture extérieure. La machine à engrenages intérieurs comprend une couronne (4) à denture intérieure, la couronne (4) s'engageant avec le pignon (3). Le pignon (3) et la couronne (4) permettent de former un espace creux (7) en forme de faucille. Une pièce de remplissage (14) est disposée dans l'espace creux (7) formé par la couronne (4) et le pignon (3). La pièce de remplissage (14) comprend un côté intérieur (15) et un côté extérieur (16). Le côté intérieur (15) est relié au côté extérieur (16) par l'intermédiaire d'une première culasse (17) et par l'intermédiaire d'une deuxième culasse (18), la pièce de remplissage (14) renfermant un volume intérieur (20).
PCT/EP2018/055418 2017-03-22 2018-03-06 Machine à engrenages intérieurs WO2018172059A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017106140.1 2017-03-22
DE102017106140.1A DE102017106140A1 (de) 2017-03-22 2017-03-22 Innenzahnradmaschine

Publications (1)

Publication Number Publication Date
WO2018172059A1 true WO2018172059A1 (fr) 2018-09-27

Family

ID=61691449

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2018/055418 WO2018172059A1 (fr) 2017-03-22 2018-03-06 Machine à engrenages intérieurs

Country Status (2)

Country Link
DE (1) DE102017106140A1 (fr)
WO (1) WO2018172059A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020110217A1 (de) 2020-04-14 2021-10-14 Hydraulik Nord Technologies GmbH Innenzahnradmaschine

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2100525A2 (fr) * 1970-01-30 1972-03-24 Zahnradfabrik Friedrichshafen Pompe a engrenage a rotation inversable et sens de debit constant
JPS50141203U (fr) * 1974-05-08 1975-11-20
WO2001002730A1 (fr) 1999-07-06 2001-01-11 Voith Turbo Gmbh & Co. Kg Machine a engrenage interne destinee au fonctionnement reversible dans un circuit hydraulique ferme
DE9321656U1 (de) * 1993-11-13 2003-03-13 Eckerle Industrie-Elektronik GmbH, 76316 Malsch Reversierbare Innenzahnradmaschine (Pumpe oder Motor)
DE102008053318A1 (de) * 2008-10-27 2010-04-29 Trw Automotive Gmbh Reversibel betreibbare Zahnradmaschine, sowie Fahrzeuglenksystem und Verfahren zur Steuerung eines Fahrzeuglenksystems
DE102012207259A1 (de) 2012-05-02 2013-11-07 Robert Bosch Gmbh Innenzahnradpumpe

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE528637C (de) * 1928-02-09 1931-07-03 Edmond Moglia Drehkolbenpumpe oder -verdichter
DE1403924A1 (de) * 1961-01-24 1968-11-28 Oilenergetic Establishment Fuellstueck fuer Innenlaeuferzahnradmaschinen
DE1653818A1 (de) * 1967-02-28 1971-06-09 Daimler Benz Ag Innenverzahnte Zahnradpumpe,insbesondere fuer die Druckmittelversorgung von selbsttaetig schaltenden Kraftfahrzeuggetrieben

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2100525A2 (fr) * 1970-01-30 1972-03-24 Zahnradfabrik Friedrichshafen Pompe a engrenage a rotation inversable et sens de debit constant
JPS50141203U (fr) * 1974-05-08 1975-11-20
DE9321656U1 (de) * 1993-11-13 2003-03-13 Eckerle Industrie-Elektronik GmbH, 76316 Malsch Reversierbare Innenzahnradmaschine (Pumpe oder Motor)
WO2001002730A1 (fr) 1999-07-06 2001-01-11 Voith Turbo Gmbh & Co. Kg Machine a engrenage interne destinee au fonctionnement reversible dans un circuit hydraulique ferme
DE102008053318A1 (de) * 2008-10-27 2010-04-29 Trw Automotive Gmbh Reversibel betreibbare Zahnradmaschine, sowie Fahrzeuglenksystem und Verfahren zur Steuerung eines Fahrzeuglenksystems
DE102012207259A1 (de) 2012-05-02 2013-11-07 Robert Bosch Gmbh Innenzahnradpumpe

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020110217A1 (de) 2020-04-14 2021-10-14 Hydraulik Nord Technologies GmbH Innenzahnradmaschine
WO2021209222A1 (fr) 2020-04-14 2021-10-21 Hydraulik Nord Technologies GmbH Machine à engrenages intérieurs
US11905956B2 (en) 2020-04-14 2024-02-20 Hydraulik Nord Technologies GmbH Internal gear machine with switching valves

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