EP0483029B1 - Hydraulischer Hochdruckerzeuger bzw.-Empfänger zur Leistungsübertragung - Google Patents

Hydraulischer Hochdruckerzeuger bzw.-Empfänger zur Leistungsübertragung Download PDF

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Publication number
EP0483029B1
EP0483029B1 EP91420376A EP91420376A EP0483029B1 EP 0483029 B1 EP0483029 B1 EP 0483029B1 EP 91420376 A EP91420376 A EP 91420376A EP 91420376 A EP91420376 A EP 91420376A EP 0483029 B1 EP0483029 B1 EP 0483029B1
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EP
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Prior art keywords
generator
receiver according
pinions
discs
envelope
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Expired - Lifetime
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EP91420376A
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English (en)
French (fr)
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EP0483029A1 (de
Inventor
Jean Malfit
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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
    • 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
    • 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
    • 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
    • F04C2/086—Carter

Definitions

  • the present invention refers to a hydraulic generator-receiver for power transmission.
  • EP 0165884 describes such an apparatus comprising two pinions 9, 10 coupled inside a stator, at least one of them being devoid of mechanical bearing, which stator also comprises at least one opening. inlet 40 and a discharge opening 40 for a pressurized liquid, while two flanges 21, 22 close the stator on either side of the two pinions 9, 10 on which they provide a lateral seal.
  • EP 0 262 189 has described such an apparatus, the drive pinion 9 of which alone is provided with mechanical bearings 123.
  • the stator comprises a flexible envelope 36 subjected externally to a centripetal pressure which enables it to ensure sealing on the tops of the teeth of the pinions 9, 10 with helical teeth located in the envelope 36.
  • Hydrostatic compensation forces on the flanges 21, 22 and on the envelope 36 come on the one hand from the pressure of the area 34 of permanent total pressure and on the other hand from the pressure prevailing in the hydrostatic balancing compensation sectors 38 and 60 respectively of the envelope and flanges. Said sectors are supplied by channels 43 and 23.
  • Two covers 54, 55 cover said flanges while a body 49 surrounds the envelope 36.
  • the internal hydraulic balancing is ensured by a hydraulic winding comprising rotor conduits in the pinions 9 and 10 and stator in the flanges 21 and 22 and the casing 36, the successive switching between the rotor and stator conduits being ensured by their scrolling ends one in front of the other on a switching circle 20. Balancing between the hollow of teeth is ensured by the permanent connection between the hollow of opposite teeth for an even number of teeth, and the hollow of opposite teeth with an offset of one demipas for an odd number of teeth via the conduits 23 of the flanges and of the channels formed in the pinions.
  • the rotor circuits in the pinions 9, 10 are constituted by groups of conduits 102 diametrically opposite on the switching circle 20 and parallel (or inclined to the value of the angle of the propeller) to the axis pinions 9, 10 and radial 101, joining the opposite conduits 102 of the ⁇ to form an H.
  • the stator circuits are constituted by the grooves 23, the connections 30 and the conduits 43.
  • the high pressure supply of the zone 34 of permanent total pressure is effected by a preferential valve system also allowing the decompression of this zone 34 when desired.
  • Seal anti-extrusion devices are incorporated in the hydrostatic compensation sectors 38 and 60 respectively delimited by the seals 37 and 45, the zone 34 being defined outside these seals and closed on the axis of the pinions 9 and 10 by the seals 58.
  • EP 0 262 189 entails risks of deformation of the plastic flanges 21 and 22 in the areas where they have the grooves 100 when in them the low pressure prevails, while the outside of the flanges is in permanent total high pressure from zone 34.
  • this embodiment has provided anti-extrusion seal devices also serving as reinforcement for plastic parts at the outlet orifices 40. These devices are not entirely satisfactory, lead to produce the outlet orifices 40 only in the flanges and covers and do not allow their production in the casing 36 and the body 49, which casing could be deformed by the action of the High Pressure.
  • the improvements which are the subject of the present invention aim to remedy these drawbacks and to allow the production of a generator-receiver which responds particularly well to the wishes of the practice.
  • each flange provision has been made to drown in each flange a reinforcing insert, one face of which is flush with its internal wall opposite each gear 9, 10.
  • the covers and the body have projections directed towards the interior of the device and suitable for penetrating into depressions of the flanges and of the casing respectively, said depressions being formed in the hydrostatic compensation sectors of the flanges and of the casing.
  • the projections of the covers and of the body have sections with oblique faces with respect to which said plastic parts are forced up.
  • the devices for supplying zone 34 and for returning leaks have been simplified.
  • the solution adopted consists in multiplying the number of satellites (pinions driven by the main pinion), each satellite always having four sectors (2 HP and 2 BP), and the main pinion a number of sectors depending on the number of satellites, the sectors always being either HP or BP and separated from each other by the zone 34 of value corresponding to the value of the "hydraulic bearings" in 6.
  • each of the flanges 21, 22 made of plastic material comprises a reinforcement piece produced in the form of an insert 207.
  • the plastic material of each flange is overmolded on the insert 207, the outer face of which is flush with the inner one of each flange.
  • the insert is made of a metallic material with a high coefficient of friction since it is in sliding contact with the pinions 9, 10.
  • the insert 207 has in profile in plan the shape of a face of glasses that is - say that it has two circular parts joined by a bi-concave junction 211 (fig. 2).
  • the bi-concave junction 211 can be entirely inserted into the plastic for the part concerning the friction concerning the teeth at the point of engagement 3: the friction on the faces of teeth is then carried out by the plastic and makes it possible to better compensate for the differences in width H between the teeth of the driving and driven pinions, of the order of a hundredth of a millimeter.
  • the insert 207 has grooves 210 (FIGS. 2 and 5) in which the plastic material constituting the flanges 21, 22 penetrates to form a bead in which is formed each cell 100 located on the switching circle 20 and connected by channel 23 to the connecting conduits 30.
  • Each circular part of the insert 207 has three radial tabs 209 facing outwards and arranged between the grooves 210 and corresponding to the hydraulic bearings (fig. 2).
  • recesses 205 facilitate the cooling of the plastic after the injection operation and give greater flexibility to the flanges 21, 22 (fig. 3 and 7). ).
  • grooves 215 are provided on the face of each insert 207 in contact with the pinions 9 and 10 to create fluid bearings.
  • the sectors which are adjacent to the meshing zone 3 of the pinions 9 and 10 have been referenced 60 ′ and 60 ′′. They roughly affect a shape with double curvature or in policeman's hat (fig. 8 ), the sector 60 '' being of shorter length than that of the sector 60 'due to the configuration of the balancing sectors of the flanges 21 and 22.
  • FIG. 6 Illustrated in fig. 6, 7 and 8 the manner in which the flanges 21 and 22 are anchored with respect to the covers 54, 55.
  • Each of them has projections 201 arranged symmetrically with respect to the engagement zone 3 of the pinions 9 and 10 (fig. 7) and extending in the balancing sectors 60 of the flanges 21, 22.
  • a projection 201 'shaped as an inverted policeman's cap, integral with each cover 54, 55 is arranged in one of the balancing sectors 60' located partly opposite the two pinions 9 and 10.
  • Another projection 201 '' in the sector 60 '' is provided on the covers 54, 55 opposite that 201 '. Its shape is similar to that of the latter, but it is more restricted in length due to the configuration of the balancing sectors on the flanges 21, 22.
  • the projections 201, 201 ', 201'' forcefully engage in the recesses of the flanges 21-22 so as to ensure a tightening at the joints 45, 45' and 45 '' and a play elsewhere, this engagement and this tightening is allowed by a tilt difference of the order of 5 ° between the respective faces which cooperate.
  • the ends of the stripped faces of the projections 201, 201 ', 201'' are hollowed out by pressure distribution grooves 202, 202', 202 '' respectively.
  • the protrusions considered of the covers constitute anti-extrusion devices for seals, which are force-fitted in the recesses of the flanges at the seals 45, 45 ', 45' '.
  • the envelope 36 comprises, in its part receiving the bosses 203 ′, a rectangular opening into which an element 49 a of the boss 203 (fig. 8) of the body 49 provided with the orifice 40 penetrates. This rectangular opening is permitted by the anchoring of the envelope 36 in the bosses 203 and 203 ′ of the body 49 of height slightly less than the width of the toothing and of width in relation to the module thereof. In this way, the orifices 40 can be produced in the body 49.
  • the finish of the projections 201, 201 ', 201' 'and the bosses 203, 203' as well as the faces of the covers 54, 55 and those inside of the adjoining body 49 is such that it presents a particularly high surface finish to receive the plastic parts of the flanges 21, 22 and of the casing 36 as well as the joints of the corresponding sectors 60, 60 ', 60' 'and 38, 38'.
  • This surface condition is obtained for example by a plastic overmolding or a coating of oven-baked epoxy paint.
  • the anti-extrusion joint effect of the projections and bosses is reinforced by a plastic border 0.3 to 0.5 mm high around the periphery of the joint housings on the flanges 21, 22 and on the casing 36. This border also absorbs differences in ribs.
  • Leaks are recovered by means of conduits 218 closed by a plug 219 and by a particular conduit 213 formed through the pinion 10 and parallel to the axis thereof.
  • the leaks recovered by these conduits are evacuated towards the low-pressure circuit by means of a piping connected in the hole 217 (fig. 1 and 8).
  • Food of zone 34 a permanent total high pressure zone, is produced by the orifice 216 from the high pressure generated or received.
  • the grooves 30, linked to the grooves 100 by the conduits 23, have a greater or lesser angular value depending on the operating conditions. In the example above, they are limited to the value of the diameter of the conduit. In reality, because of their respective positions in each of the flanges 21 and 22 relative to the inclination of the teeth, their value is equivalent to twice the diameter of the duct (when one is masked by a full of teeth, the the other is always in connection with the hollow of the tooth and vice versa).
  • These grooves 30 can be completed by a groove 212 halfway up the envelope 36, centered on the conduit 43, so that the groove 30 can always be made as short as possible, for example reduced to the diameter of the conduit 23. According to the priority direction of rotation, this groove 212 can be offset relative to the conduit 43 to promote faster pressurization on one side relative to the other side of the sector.
  • connecting conduit 23 can take the form referenced 214 on the generators-receivers of large displacement to favor the creation of the fluid bearings (fig. 17).
  • This arrangement requires the use of a spacer 221 on the driven pinion side, this and the bearing 123 on the driving pinion side then being inserted into the plastic of the flanges 21-22.
  • This plastic insertion makes it possible to make the bearing-flange assembly in one piece, to angularly separate the spacer 221 and the bearing 123 from the manifold 207 and to overcome the misalignment of the bearings bores.
  • the assembly pivots in a 36 '' envelope housed in the 49 '' body.
  • the orifices 40 HP-BP are either HP or BP, on the same side. Balancing is carried out in the same way as in the previous constructions.
  • the driving pinion cannot be balanced by the rotor conduits since the opposite sectors are not at the same pressure potential.
  • the driving pinion is balanced by means of the hydrostatic compensation sectors provided on the flanges.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Mechanical Operated Clutches (AREA)
  • General Details Of Gearings (AREA)

Claims (10)

  1. Hydraulischer Hochdruckerzeuger bzw. -empfänger mit einem Getriebe mit schraubenförmigen Zahnräder (9, 10), dessen inneres Gleichgewicht durch eine hydraulische Anordnung gesichert ist, die aus rotorischen und statorischen Leitungen besteht, und die hydraulische Lager und ein Eingreifen ohne Spiel erlauben und deren innere Dichte durch ein geschmeidiges System erhalten wird, das sich aus zwei Stirnwänden (21) und (22) zusammensetzt, die Rillen (100) und ein Gehäuse (36) mit hydrostatischen Ausgleichsektoren (60) und (38) haben, dadurch gekennzeichnet, daß die Stirnwände (21) und (22) auf einem Einsatz (207) mit einem guten Reibungskoeffizienten angeformt sind, dessen äußere Flächen mit den inneren Flächen jeder Stirnwand bündig sind, und die zwei kreisförmige Teile haben, die durch eine bikonkave Verbindung (211) verbunden sind, wobei der Einsatz Rinnen (210) aufweist, in denen jeweils plastisches Material angeordnet ist, das die Stirnwände zur Bildung eines Bandes durchdringt, in das eine Rille (100) angeordnet ist.
  2. Hydraulischer Hochdruckerzeuger bzw. -empfänger nach Anspruch 1, dadurch gekennzeichnet, daß die Deckel (54, 55) und die Körper (49) entsprechende Vorsprünge (201, 201', 201'') und Nocken (203, 203') aufweisen, die kraftschlüssig in entsprechende Aussparungen der Stirnflächen (21, 22) und des Gehäuses (36) eingreifen.
  3. Hydraulischer Hochdruckerzeuger bzw. -empfänger nach Anspruch 2, dadurch gekennzeichnet, daß die Vorsprünge (201, 201', 201'') und Nocken (203, 203') seitliche Flächen aufweisen, die mit einer Teilung von etwa 5° mit den entsprechenden Druckflächen zusammenwirken, die einen Kraftschluß der Stirnwände des Gehäuses im Hinblick auf die Deckel (54, 55) und die Körper (49) in Höhe der Dichtungen (45, 45', 45'') bis (37, 37') ergeben.
  4. Hydraulischer Hochdruckerzeuger bzw. -empfänger nach Anspruch 3, dadurch gekennzeichnet, daß die Vorsprünge (201, 201', 201'') und die Nocken (203, 203') mit einer Kunststoffhülle oder einem heißen Epoxy-Anstrich versehen sind.
  5. Hydraulischer Hochdruckerzeuger bzw. -empfänger nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der Rückfluß durch eine Unterdruckleitung (218) gesichert ist, von der ein Anschlußstück (217) des Deckels (55) abgezweigt ist, und daß die Versorgung der totalen permanenten hervorgebrachten oder erhaltenen Hochdruckzone (34) in eine Öffnung (216) des Deckels (55) abgezweigt wird.
  6. Hydraulischer Hochdruckerzeuger bzw. -empfänger nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß das Gleichgewicht der hydrostatischen Ausgleichssektoren durch eine Rille (212) im Gehäuse (36) in Höhe der Leitung (43) gegeben ist, daß die Rille exzentrisch zur Leitung (43) gemäß dem vorrangigen Drehsinn angeordnet ist und daß der vorrangige Typ der Funktion der Erzeuger oder Empfänger entspricht.
  7. Hydraulischer Hochdruckerzeuger bzw. -empfänger nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß das Führungszahnrad (10) mit einer Ausgleichsleitung (213) der Unterdruckkammer versehen ist, die auf der Achse des Zahnrades (10) angeordnet ist.
  8. Hydraulischer Hochdruckerzeuger bzw. -empfänger nach Anspruch 1, dadurch gekennzeichnet, daß der Einsatz (207) auf der Seite, die mit der Seite der Zahnräder (9, 10) in Verbindung steht, Ausgleichsrillen (215) aufweist, um die Bildung eines flüssigen Lagers zwischen der Fläche des Einsatzes (207) und der Fläche der Zahnräder (9 und 10) zu begünstigen.
  9. Hydraulischer Hochdruckerzeuger bzw. -empfänger nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß Dichtungen (58) in den Bohrungen der Deckel (54, 55) angeordnet sind, um den Einfluß der Druckzone (34) zu verringern, und daß die Rillen (100) in den Sektoren (60) sich vereinigen, um sich dem gleichen hydrostatischen Kompressionsdruck zu unterwerfen und dadurch in dieser Stellung eine geschmeidige plastische Verbindung zwischen den Querversteifungen (221) den Lagern (123) und dem Einsatz (207) gegenseitig zu bilden, wobei die Verbindung durch einen plastischen Teil der Stirnwände (21 und 22) gebildet ist.
  10. Hydraulische Hochdruckerzeuger bzw. -empfänger nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Zahl der Planetenräder n bei 1, 2, 3,....n und die Zahl der Zähne Z des Hauptzahnrades von der Zahl der Zähne z der Planetenräder in einem Verhältnis Z nz 2 
    Figure imgb0007
     abhängig ist, wenn n = 1 und Z = z ist und Z und z gerade und ungerade sind.
EP91420376A 1990-10-24 1991-10-23 Hydraulischer Hochdruckerzeuger bzw.-Empfänger zur Leistungsübertragung Expired - Lifetime EP0483029B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9013411 1990-10-24
FR9013411A FR2668548B1 (fr) 1990-10-24 1990-10-24 Generateur-recepteur hydraulique pour la transmission de puissance.

Publications (2)

Publication Number Publication Date
EP0483029A1 EP0483029A1 (de) 1992-04-29
EP0483029B1 true EP0483029B1 (de) 1995-06-21

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EP91420376A Expired - Lifetime EP0483029B1 (de) 1990-10-24 1991-10-23 Hydraulischer Hochdruckerzeuger bzw.-Empfänger zur Leistungsübertragung

Country Status (6)

Country Link
US (1) US5178528A (de)
EP (1) EP0483029B1 (de)
JP (1) JPH04262080A (de)
DE (1) DE69110614T2 (de)
ES (1) ES2073715T3 (de)
FR (1) FR2668548B1 (de)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2698413B1 (fr) * 1992-11-26 1995-01-27 Jean Malfit Générateur-récepteur hydraulique pour la transmission de puissance comportant un équilibrage hydraulique perfectionné.
DE19802443C1 (de) * 1998-01-23 1999-05-12 Luk Fahrzeug Hydraulik Pumpe
JP4977112B2 (ja) * 2008-11-17 2012-07-18 日立オートモティブシステムズ株式会社 ギヤポンプ
JP5441873B2 (ja) * 2010-12-01 2014-03-12 日立オートモティブシステムズ株式会社 外接歯車ポンプ
JP2016205170A (ja) * 2015-04-17 2016-12-08 セイコーエプソン株式会社 ギヤポンプおよびこれを備えた印刷装置
FR3067880B1 (fr) * 2017-06-15 2020-07-17 Moteurs Leroy-Somer Machine electrique tournante

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2966860A (en) * 1957-04-03 1961-01-03 Lobee Pump & Machinery Co Pump for corrosive fluids
US3057303A (en) * 1959-04-15 1962-10-09 Clark Equipment Co Pressure loaded gear pump
SE305986B (de) * 1966-05-27 1968-11-11 F Sneen
US3348492A (en) * 1966-12-05 1967-10-24 Borg Warner Reversible wear plate pump
US3363578A (en) * 1966-12-21 1968-01-16 Clark Equipment Co Gear pump and thrust plate therefor
FI62713C (fi) * 1979-10-22 1983-02-10 Valmet Oy Kugghjulspump och/eller -motor
SU941675A1 (ru) * 1980-12-25 1982-07-07 Кировоградский Завод Тракторных Гидроагрегатов Им.Хху Съезда Кпсс Шестеренна гидромашина
FR2564931B1 (fr) * 1984-05-22 1986-12-05 Malfit Jean Generateur recepteur hydraulique a haute pression pour la transmission de puissance
JPS61294178A (ja) * 1985-06-24 1986-12-24 Kawasaki Heavy Ind Ltd ねじポンプ
US4781552A (en) * 1985-11-27 1988-11-01 Jean Malfit High pressure hydraulic generator receiver for power transmission
EP0262189B1 (de) * 1986-04-01 1990-05-30 Jean Malfit Hydraulischer hochdruckerzeuger bzw.-empfänger zur leistungsübertragung
SU1386744A1 (ru) * 1986-06-23 1988-04-07 Белорусский Политехнический Институт Шестеренный насос

Also Published As

Publication number Publication date
FR2668548A1 (fr) 1992-04-30
US5178528A (en) 1993-01-12
DE69110614D1 (de) 1995-07-27
DE69110614T2 (de) 1996-02-22
FR2668548B1 (fr) 1993-01-08
ES2073715T3 (es) 1995-08-16
EP0483029A1 (de) 1992-04-29
JPH04262080A (ja) 1992-09-17

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