EP0600807B1 - Hydraulischer Hochdruckerzeuger bzw.-Empfänger zur Leistungsübertragung - Google Patents

Hydraulischer Hochdruckerzeuger bzw.-Empfänger zur Leistungsübertragung Download PDF

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Publication number
EP0600807B1
EP0600807B1 EP93420471A EP93420471A EP0600807B1 EP 0600807 B1 EP0600807 B1 EP 0600807B1 EP 93420471 A EP93420471 A EP 93420471A EP 93420471 A EP93420471 A EP 93420471A EP 0600807 B1 EP0600807 B1 EP 0600807B1
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EP
European Patent Office
Prior art keywords
force
balancing
high pressure
hydrostatic
sectors
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Expired - Lifetime
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EP93420471A
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English (en)
French (fr)
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EP0600807A1 (de
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Jean Malfit
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    • 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
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • 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
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps

Definitions

  • the present invention refers to improvements made to a hydraulic generator-receiver for the transmission of power of the kind described in European patents 165 884, 262 189 and 483 029.
  • an apparatus comprising two pinion gears with helical teeth coupled inside a stator, at least one of them being devoid of mechanical bearing.
  • the stator is established in the form of a flexible envelope which moreover comprises at least one inlet opening for a liquid at low pressure and a discharge opening for a liquid at high pressure.
  • the stator further comprises two identical flexible flanges and turned one relative to the other cooperating with the casing and enclosing the two pinions with which they provide lateral sealing by their identical inner face.
  • the flexible casing is subjected externally to a centripetal pressure which enables it to seal the tops of the teeth of pinions with helical teeth situated in the casing.
  • the hydrostatic compensation forces on the flanges and on the casing originate on the one hand from the pressure of a permanent total pressure zone and on the other hand from the pressure prevailing in balancing hydrostatic compensation sectors, respectively of envelope and flanges.
  • the sectors are fed by channels. Rigid covers cover the flanges, while an equally rigid body surrounds the casing.
  • the internal hydraulic balancing is ensured by a hydraulic winding comprising rotor ducts in the pinions and stator in the flanges and the casing. Successive switches between the rotor and stator conduits are ensured by their ends running past one another on a switching circle. Balancing between the tooth hollows is ensured by the permanent connection between the opposite tooth hollows for an even number of teeth and the opposite tooth hollows with an offset of 1 2 not for an odd number of teeth via the flange conduits and the channels formed in the pinions. Of course, this connection does not exist in the engagement zone and in the zones diametrically opposite to this engagement zone with respect to the pinions and in which hydraulic diametrically opposed bearings are created.
  • the winding connects the pairs of opposite teeth so as to obtain the same hydraulic pressure in the hollow of teeth for diametrically opposite angular positions and to create two opposite forces on the pinions in order to cause their engagement without play in the mesh area.
  • EP 483 029 For large displacements, the solution described in EP 483 029 consists in multiplying the number of satellite pinions driven by a main pinion, the latter having a number of sectors depending on the number of satellites, each satellite always having four sectors, two HP sectors and two BP sectors.
  • EP 0165884, EP 0262189 and EP 0483029 do not provide satisfactory axial balancing of the driving pinion. Indeed, if the action of the radial hydraulic bearings ensures the radial balance, the axial balancing of the pinion leading by the hydrostatic compensations on the flanges at the point of engagement only ensures a local balancing of the axial component in this point causing greater local wear of the flange subjected to the axial component of the driving pinion and therefore a precarious endurance resistance.
  • the axial general balancing of the driving pinion is not ensured due to the axial components, at each end of the assembly formed by each of the high pressure balancing sectors and by the two adjacent elements of the zone always at high pressure, resulting from hydrostatic compensations on the flanges.
  • the tangential force FT is defined on the basis of the transmitted power and the speed of rotation, the forces FR and FA being deduced therefrom via FN and FX and the angle ⁇ of real pressure and the angle ⁇ which is the complement of the helix angle ⁇ defined in EP 0 262 189.
  • This force acts from point 305 to point 306 diametrically opposite or vice versa depending on the direction of rotation.
  • the MFA torque is balanced by the reactions of the bearings of the driving pinion.
  • the improvements which are the subject of the present invention aim to remedy these drawbacks and to allow axial and tangential hydrostatic balancing of the driving pinion.
  • the value of the surface of the zone is always varied at high pressure, so that an application of the high pressure is produced on a surface of one of the flanges, either larger or smaller, the other flange not being influenced by this surface variation, while in order to perform tangential balancing, the surface of the sectors of the envelope adjacent to the point of meshing is varied detriment to the area still under high pressure.
  • Fig. 1 illustrates the decomposition of the normal force FN into FR and FX perpendicular to FR at the point of engagement of the pinions 9 and 10.
  • Fig. 2 is a section developed along the original cylinder of the driving pinion. We have included in I-I the section plane of fig. 1.
  • Fig. 3 and 4 are sections developed according to the primitive cylinders of the driving pinions respectively and driven in gear position, illustrating the direction of the axial component of imbalance of the driving pinion, according to the clockwise (SH) and counterclockwise (SIH) directions respectively ) of the driving gear.
  • Fig. 5 illustrates the balance according to the direction of rotation of the forces and unbalance couples of the pinion driving a generator-receiver to a single driven pinion.
  • Fig. 6 is a longitudinal section of an apparatus according to the invention.
  • Fig. 7 is a cross section of an apparatus according to the invention produced along a plane passing through the point of engagement of the pinions.
  • Fig. 8 is a section along VIII-VIII (fig. 6) with an axial balancing device. There is shown in VI-VI the section plane of FIG. 6 and in VII-VII that of fig. 7.
  • Fig. 9 is a variant of the axial balancing device of FIG. 8.
  • Fig. 10 is a partial developed section of the envelope and of the body in the case of hydrostatic balancing on this envelope of the tangential component FT.
  • Fig. 11 is a partial section corresponding to FIG. 8 and 9, but illustrating the modifications of the flanges corresponding to the actual balancing on the envelope of the tangential component FT.
  • Fig. 12 is a section along XII-XII (fig. 10). There is shown in X-X the section plane of FIG. 10.
  • Fig. 13 to 16 illustrate the equilibrium polygon of the tangential components FT, of the torque vectors MFA and the axial components FA to be balanced in the case respectively of a receiver generator with chevron toothing and with 2, 3, 4 satellite pinions, and according to the direction of rotation.
  • Fig. 17 is a variant of the axial balancing device illustrated in FIG. 8 and comparable to the variant of FIG. 9.
  • the hydrostatic balancing of the force FR by the hydraulic bearings in zones 6 is obtained by a theoretical value of 1 ⁇ 2 angular pitch of toothing, ie ⁇ / Z. This value is sufficient to balance the mechanical and hydrostatic radial forces in the engagement zone 3.
  • the overpressure in the hollow of the tooth resulting from the irregularities of flow happens to be a natural functional safety, but if this was too high, it can be evacuated by a non-return towards zone 34, (zone in high pressure) or towards high pressure as provided in EP 0 165 884.
  • the hydrostatic balancing of the force FA must allow reversibility, that is to say the change of direction of rotation in generator or receiver of the apparatus according to the invention.
  • the best solution for a device with a single driven sprocket is to adopt for the two sprockets a herringbone toothing thanks to which the axial forces FA naturally balance between the two 1 2 helical teeth of opposite inclination of said herringbone toothing.
  • the extension 301 is in the general form of a polygon surrounded by a 45 "joint deflection.
  • the axial balancing of the driving pinion 9 is carried out according to one of the two solutions above and the moment vectors of the resulting couples cancel each other out.
  • the additional rebalancing force is equal to the axial force FA per pair of pinions 9, 10 multiplied by the number of satellites n.
  • the axial force FA is directed downwards, so that the opposing force -FA must be directed upwards and in any case in the opposite direction to FA.
  • the hydrostatic balancing of the tangential force FT is carried out by means illustrated in FIG. 10, 11 and 12.
  • the aforementioned means consist first of all, as shown in FIG. 10, to delete the zone 34 between the sectors 38 ′ and 38 adjacent to the point of engagement 3 of the pinions at the level of the spokes 305 and 306 of the pinion 9 perpendicular to the axis 6-6.
  • the seals 37 'and 37 provided in the embodiment of fig. 9 of European patent 0483029 are replaced by a single joint 304 provided with a middle branch 304 a . This middle branch is located along departments 305 and 306 illustrated in fig. 11, as explained below.
  • the above modification requires deleting the part of the zone 34 between the sectors 60 ', 60 respectively 60 ", 60 of the flanges 21, 22 (fig. 11) at the level of the spokes 305 and 306, so that for each of the said rays, radial portions 45a, 45'a of the joints 45 and 45 '(fig. 8) and the radial portions 45 a and 45 "has seals 45 and 45' symmetrical to the previous relative to the geometric axis 6-6 are eliminated without affecting the axial balancing in any way.
  • the sectors 60 ′, 60 and 60 ′′, 60 are surrounded by joints 302 and 303 in one piece which each have, respectively, along the spokes 305 and 306 a branch 302 a , respectively 303 a which separates the sectors considered .
  • the branch 304 has seal 304 on the casing 36 materializing the end of the part of the zone 34 incorporated into the sectors 38 ′ for balancing the force FT, is located at 1 4 angular pitch pitch of the axis of the "hydraulic bearing" or ⁇ 2Z . Therefore, the FT component is balanced by this additional sector 38 'which is at high pressure for a value slightly higher than ⁇ Z + ⁇ .
  • the value ⁇ Z + ⁇ incorporated into sectors 38 'on the side of the driving pinion 9 must be calculated to balance FT, taking into account the offset introduced by the width of the joint.
  • the values on the flanges 21, 22 must correspond to the values on the casing 36 to ensure sealing on the faces.
  • the tangential force FT is balanced under the same conditions as for a helical toothing, the only difference being that the joint 304 then has, like the sectors 38 and 38 ', a herringbone shape.
  • a pinion driving 9 '' and three satellite pinions 10 '' have been illustrated in a body 49 ''.
  • the polygon of forces FT is closed, as is the polygon of the torque vectors M FA under the same conditions.
  • the additional axial component on the pinion 9 '' is in this case equal to three times FA per pair of pinions 9 '' - 10 ''.
  • a generator-receiver with a single driven satellite gear and helical teeth will only be used if this solution has certain economic advantages, since it is less rational than the previous two in terms of function.
  • Axial balancing will be necessary, balancing the tangential force will depend on the conditions of use.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Rotary Pumps (AREA)
  • Gear Transmission (AREA)

Claims (7)

  1. Hydraulischer Hochdruckerzeuger bzw. -empfänger mit schraubenförmigen Zahnrädern, bestehend aus einem Führungszahnrad und mindestens einem geführten Zahnrad, das mit einem mechanischen Lager versehen und stets im Gleichgewicht ist, wbei das innere Gleichgewicht durch eine hydraulische Anordnung gesichert ist und so hydraulische Lager und ein Eingreifen ohne Spiel gewährleistet sind und wobei die innere Dichte durch ein geschmeidiges System erhalten wird, das sich aus zwei Stirnwänden (21, 22) und einem Gehäuse (36) zum hydrostatischen Ausgleich mit Hilfe von hydrostatischen Ausgleichssektoren (60-38) zusammensetzt, dadurch gekennzeichnet, daß das Gleichgewicht der axialen Kräfte (FA) des Führungszahnrades (9) dadurch bewirkt ist, daß der Wert der Oberfläche des Bereichs (34) mit ständigem Hochdruck derart verändert ist, daß diese Veränderung ein Anlegen eines hohen Druckes auf einer der Oberflächen einer der Stirnwände (21, 22) bewirkt, wobei diese Veränderung des Wertes der Bereichs (34) mit ständigem Hochdruck, sei sie größer oder kleiner, keine Auswirkungen auf die andere Stirnwand (22) oder (21) hat und wobei zum ins Gleichgewicht-Bringen der tangentialen Kraft (FT) des Führungszahnrades (9) die Oberfläche des Abschnittes des Gehäuses (36), die dem Eingriffspunkt (3) zugeordnet ist, auf Kosten des Bereichs (34) mit ständigem Hochdruck verändert ist.
  2. Hydraulischer Hochdruckerzeuger bzw. -empfänger nach Anspruch 1, dadurch gekennzeichnet, daß das axiale hydrostatische Gleichgewicht des Führungszahnrades (9) durch Erzeugen einer Gegenkraft (-FA) zur axialen Kraft (FA) bewirkt ist, wobei eine Vergrößerung der Oberfläche des Bereichs (34) mit ständigem Hochdruck auf den Stirnwänden (21, 22) um einen Wert ΔS = FA / HP in dem Abschnitt des Bereichs (34), der den hydrostatischen Ausgleichssektoren (60') und (60) benachbart ist, (der diametral entgegengesetzt ist zu 60'), wobei die so bewirkte Kraft nur auf der Seite der Ausgleichssektoren (60') und (60) mit niegrigem Druck auftritt und so die Umkehrbarkeit der Anordnung gewährleistet.
  3. Hydraulischer Hochdruckerzeuger bzw. -empfänger gemäß Anspruch 1, dadurch gekennzeichnet, daß das axiale hydrostatische Gleichgewicht des Führungszahnrades (9) durch eine Gegenkraft (-FA) zu zu der axialen Kraft (FA) bewirkt wird durch eine Verringerung des Bereichs (34) mit hohem ständigen Druck auf den Stirnwäden (21, 22) durch Vergrößerung einer Ausnehmung (301) des hydrostatischen Ausgleichsektors (60") um eine Oberfläche ΔS, wobei diese zusätzliche Fläche ΔS = FA / HP eine Kraft erzeugt, die sich nur auf der Seite des Ausgleichssektors (60") mit hohem Druck ergibt, und so die Umkehrbarkeit des Systems gewährleistet.
  4. Hydraulischer Hochdruckerzeuger bzw. -empfänger nach Anspruch 1, dadurch gekennzeichnet, daß das hydrostatische Gleichgewicht der auf das Führungszahnrad (9) wirkenden tangentialen Kraft (FT) durch Bildung einer der tangentialen Komponente (FT) entgegengesetzten gleichen Kraft bewirkt ist, wobei diese durch eine Vergrößerung des Abschnittes (38) des Gehäuses (36) an der Seite des Führungszahnrades (9) und der hydrostatischen Ausgleichssektoren (60') und (60") auf den Stirnwänden (21, 22) bewirkt wird, in dem die Vergrößerung durch Veränderung der Dichtungen (304) des Gehäuses (36) und der Dichtungen (302) und (303) der Stirnwände erhalten ist, so daß ein teilweiser Ausgleich für eine Drehrichtung im Uhrzeigersinn (SH) und im Gegenuhrzeigersinn (SIH) und ein vollständiger Ausgleich für eine Drehrichtung im Uhrzeigersinn (SH) oder im Gegenuhrzeigersinn (SIH) auf Grund der Dicke der Dichtungen (302, 303, 304) in ihren radialen Abschnitten (302a, 303a und 304a) erhalten ist.
  5. Hydraulischer Hochdruckerzeuger bzw. -empfänger nach Anspruch 1, dadurch gekennzeichnet, daß das hydrostatische Gleichgewicht bei Hochdruckerzeugern bzw. -empfängern mit mehreren geführten Satellitenzahnrädern (10) dadurch erhalten ist, daß die Gegenkraft (-FA), die das Führungszahnrad (9) in Gleichgewicht bringt, gleich der axialen Kraft der gekuppelten führendengeführten Zahnräder (9-10) multipliziert mit der Zahl der Satellitenräder ist.
  6. Hydraulischer Hochdruckerzeuger bzw. -empfänger nach Anspruch 4, dadurch gekennzeichnet, daß die Verzahnung der Zahnräder zick-zack-förmig schraubenförmig verlaufend (Pfeilverzahnung) ausgebildet ist.
  7. Hydraulischer Hochdruckerzeuger bzw. -empfänger nach Anspruch 1, dadurch gekennzeichnet, daß das axiale hydrostatische Gleichgewicht des Führungszahnrades (9) durch eine Gegenkraft (-FA) zu der axialen Kraftkomponente (FA) erhalten ist durch eine Verringerung des Bereichs (34) mit ständigem hohen Druck auf den Stirnwänden (21, 22) durch Einführen einer Verminderung ΔD des Durchmessers D, der Oberfläche ΔS, der Oberfläche der entsprechenden hydrostatischen Ausgleichssektoren (60" und 60), wobei diese Veränderungen der Oberfläche ΔS = FA / HP eine Kraft bewirkt, die sich nur auf der Seite des Ausgleichsabschnittes (60") mit hohem Druck ergibt und so die Umkehrbarkeit des Systems gewährleistet.
EP93420471A 1992-11-26 1993-11-25 Hydraulischer Hochdruckerzeuger bzw.-Empfänger zur Leistungsübertragung Expired - Lifetime EP0600807B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9214676A FR2698413B1 (fr) 1992-11-26 1992-11-26 Générateur-récepteur hydraulique pour la transmission de puissance comportant un équilibrage hydraulique perfectionné.
FR9214676 1992-11-26

Publications (2)

Publication Number Publication Date
EP0600807A1 EP0600807A1 (de) 1994-06-08
EP0600807B1 true EP0600807B1 (de) 1996-07-03

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EP93420471A Expired - Lifetime EP0600807B1 (de) 1992-11-26 1993-11-25 Hydraulischer Hochdruckerzeuger bzw.-Empfänger zur Leistungsübertragung

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US (1) US5447421A (de)
EP (1) EP0600807B1 (de)
JP (1) JPH06200879A (de)
DE (1) DE69303463T2 (de)
FR (1) FR2698413B1 (de)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009012916A1 (de) * 2009-03-12 2010-09-16 Robert Bosch Gmbh Hydraulische Zahnradmaschine
US9366250B1 (en) * 2013-06-27 2016-06-14 Sumitomo Precision Products Co., Ltd. Hydraulic device
CN108571445B (zh) * 2018-04-16 2019-08-13 宁波布赫懋鑫液压技术有限公司 一种具有轴向补偿功能的内啮合齿轮泵
CN110206727A (zh) * 2019-07-02 2019-09-06 潘国陶 一种端面补偿机构及使用该机构的变速器
DE102019121005A1 (de) * 2019-08-02 2021-02-04 Volkswagen Aktiengesellschaft Pumpe umfassend magnetokalorisches Material

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4781552A (en) * 1985-11-27 1988-11-01 Jean Malfit High pressure hydraulic generator receiver for power transmission
WO1987005975A1 (fr) * 1986-04-01 1987-10-08 Jean Malfit Generateur-recepteur hydraulique a haute pression pour la transmission de puissance
FR2668548B1 (fr) * 1990-10-24 1993-01-08 Malfit Jean Generateur-recepteur hydraulique pour la transmission de puissance.

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Publication number Publication date
DE69303463T2 (de) 1997-02-13
US5447421A (en) 1995-09-05
DE69303463D1 (de) 1996-08-08
EP0600807A1 (de) 1994-06-08
FR2698413A1 (fr) 1994-05-27
JPH06200879A (ja) 1994-07-19
FR2698413B1 (fr) 1995-01-27

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