EP0534836B1 - Hydraulikzahnradmaschine mit einem schwebendem Körper - Google Patents

Hydraulikzahnradmaschine mit einem schwebendem Körper Download PDF

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Publication number
EP0534836B1
EP0534836B1 EP92402597A EP92402597A EP0534836B1 EP 0534836 B1 EP0534836 B1 EP 0534836B1 EP 92402597 A EP92402597 A EP 92402597A EP 92402597 A EP92402597 A EP 92402597A EP 0534836 B1 EP0534836 B1 EP 0534836B1
Authority
EP
European Patent Office
Prior art keywords
flanges
machine according
pinions
casing
lobes
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
EP92402597A
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English (en)
French (fr)
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EP0534836A1 (de
Inventor
Roger Laumont
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.)
Hydroperfect International Inc
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Hydroperfect International Inc
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 Hydroperfect International Inc filed Critical Hydroperfect International Inc
Publication of EP0534836A1 publication Critical patent/EP0534836A1/de
Application granted granted Critical
Publication of EP0534836B1 publication Critical patent/EP0534836B1/de
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
    • 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

Definitions

  • the present invention relates to hydraulic gear machines intended to be used either as pumps or as motors.
  • devices of the type comprising a set of two cooperating toothed wheels arranged to rotate between two flanges, forming a bearing, mounted movable in translation in corresponding recesses made in a body. central and delimited by two opposite covers or housings fixed in leaktight manner to the latter, each flange being substantially balanced in pressure by the arrangement between this flange and the adjacent cover with a suitable seal system.
  • Such devices are known from FR-A-2 215 103 and give satisfaction by making it possible to obtain excellent mechanical and volumetric yields for an acceptable cost price in consideration of the performances obtained.
  • the known devices do not maintain the same efficiency as a function of the working temperature, which is due to the variations in viscosity of the working fluid as well as to the differential expansions existing between the different parts and, more particularly, between the fixed and mobile parts, the pump bodies are often made of aluminum as well as the flanges while the pinions are made of steel.
  • the invention aims to remedy the drawbacks observed by creating a new hydraulic machine, all the moving parts of which can float relative to the fixed parts, regardless of the operating temperature and the speed of rotation of the moving parts, while also making compensation pressures generated which according to the invention are differential pressures maintain a constant compensation of the clearances.
  • Such an embodiment does not provide support for said flanges which closely corresponds to the pressures prevailing in the machine.
  • GB-A-853,550 used to state the preamble of appended claim 1 relates to an arrangement in which the housing delimits annular chambers extending partially around the pinions. Such an arrangement does not allow axial compensation by the flanges or bearings because it is not possible to prevent leaks on the lateral sides of the pinions.
  • the flanges supporting the pinions delimit lobes with the same radius of curvature as that of the circular cavities of the middle casing containing the flanges which are mounted floating inside this median casing and hydraulic pressure means apply the flanges lobes against said center casing.
  • Fig. 1 is a longitudinal sectional elevation of an embodiment of the machine according to the invention.
  • Fig. 2 is a sectional view along line II-II of FIG. 1.
  • Fig. 3 is a section seen along line III-III of FIG. 1.
  • Fig. 4 is a plan view, partly in section, along the line IV-IV of FIG. 1.
  • Fig. 5 is a section seen along the line V-V of FIG. 1 or Va-Va in fig. 4.
  • Fig. 6 is a section seen along line VI-VI of FIG. 1.
  • the illustrated embodiment of the machine is described as a pump for supplying pressurized liquid.
  • the same machine could be used as a motor, its constituent elements being reversible as is usual in the technique of pumps or hydraulic motors of the gear type.
  • the hydraulic machine is described with reference to a machine with a single set of gears but it could, in a similar manner, include several sets of gears, in particular two sets of gears whose teeth would be offset from one game to another.
  • the machine comprises a front casing 1 or cover and a rear casing 2 or cover connected to each other by a median casing 3 inside which is disposed, in accordance in the invention, a floating body 4 constituted by flanges for supporting shafts and pinions described below.
  • the median casing 3 is centered with respect to the anterior 1 and posterior casings 2 by means of pins 5.
  • the anterior 1 and posterior casings 2 are fixed to the median casing 3 by bolts 6.
  • Seals 7, 8 are interposed between the front casing 1 and the central casing 3, and respectively, between the rear casing 2 and the central casing 3 (fig. 1).
  • the front casing 1 has a gasket 9 and a bearing 10 in which is mounted an input shaft 11a connected via a coupling 21 to an input shaft 11 extending within the housing median 3 to a housing 12 of the rear casing 2.
  • the shaft 11 supports and drives a primary pinion 13 disposed between a front flange 14 and a rear flange 15 forming part of the floating body 4.
  • the flanges 14 and 15 also support a secondary shaft 16 on which is fixed a pinion 17 in engagement with the primary pinion 13.
  • Both the shaft 11 and the shaft 16 are supported by the flanges 14 and 15 by means of bearings or bearings 18, 18 a and 19, 19 a whose width is slightly smaller than the thickness of said flanges 14, 15 and in which the shafts 11 and 16 can slide at the same time as they rotate.
  • bearings When the above bearings are constituted by smooth rings, they preferably include lubrication grooves 20 advantageously constituted in the manner described and shown in French patent 1,554,858.
  • the coupling 21 causes the part of the shaft 11, which is carried by the bearings 18, 18 a , to undergo the same bending stresses as the shaft 16, which equalizes the working mode of the two trees considered.
  • the pinions 13 and 17 are mounted on the shafts 11 and 16 in order to be able to slide axially thereon.
  • the flanges 14, 15 each have substantially the shape of the number 8.
  • the interior of the median casing 3 delimits two circular cavities 22, 23 which communicate with each other by a median circular cavity 24.
  • the radius of curvature of the circular cavities 22, 23 is the same as that of the periphery of the teeth of the primary pinions 13 and secondary 17 which are engaged with each other.
  • the central cavity 24 communicates, on the one hand, with the intake duct 25 for the fluid to be pumped and, on the other hand, with a discharge duct 26 for this same fluid (see FIGS. 2 and 5).
  • the intake duct 25 is of larger section than the discharge duct 26.
  • Each flange 14 and 15 has, at its peripheral part, a lobe 27, respectively 28, of the same radius as the corresponding cavity 22, respectively 23, to bear against the respective wall of each of the two above cavities.
  • the outer wall of the front flanges 14 and rear 15 has low-cut parts 29, 30 respectively, that is to say parts of smaller diameter than the lobes 27, 28 so as to provide spaces 31, 32 communicating as well as this is shown in particular in figs. 2 and 6 with the discharge pipe 26.
  • Pads 33, 34 are arranged in the flanges 14, 15 to project into the spaces 31, 32.
  • the studs 33, 34 are mounted in housings 35 communicating with the spaces 31, 32 so that the pressure which reigns in these spaces is applied on either side of said studs which are also pushed by springs 36, slightly constrained , of so that they exert a push only tending to keep the lobes 27, 28 of the flanges in abutment against the wall of the circular cavities 22, 23.
  • each flange 14 and 15 has a front wall or face 37 facing the pinions 13 and 17 and a rear wall or face 38 facing, for the flange 14, towards the front casing 1 and, for the flange 15, to the rear housing 2.
  • the front wall 37 comprises annular segments 39, 40 (FIGS. 2 and 5) extending from the bore containing the bearing 18 or 18 a to the bottom of the teeth 41 and 42 of the primary gears 13 and secondary 17.
  • the segments 39, 40 constitute bearing surfaces for the solid parts of the pinions 13, 17.
  • the annular segments 39, 40 are connected to plates 43, 44 of substantially trapezoidal shape and, at their other end, they are interconnected by a partition 45 separating the intake duct 25 from the discharge duct 26.
  • Fig. 5 shows that the partition 45 advantageously has a substantially diamond-shaped shape.
  • Fig. 2 shows that the dimension of the partition 45 and also its shape are determined to correspond to the measurement occupied by at least one of the gable ends 13, 17 so that there can never be direct communication between the intake duct 25 and the discharge conduit 26 when the pinions rotate.
  • the part of the front wall 37 which should not bear against the lateral face of the pinions is milled to provide a chamber 46 (fig. 5), respectively 47 (fig. 1), on each side of the primary 13 and secondary 17 pinions.
  • each flange has a groove 48 having substantially the shape of the letter W, and in which is disposed a seal 49 terminating at its two ends by retaining shoes 50, 51 (fig. 6).
  • the seal 49 is provided with an anti-extrusion packing 52.
  • the seal 49 has bosses 53 to delimit notches 53a and allow the fluid, being in the circular cavities 22, 23 and coming against the rear wall 38 of each flange, to push the seal against the front casing 1 and, respectively, the rear casing 2, while exerting pressure on the rear face of each flange.
  • the size of the groove 48 and of the seal 49, the shoes 50 of which are disposed in the lobes 27, 28, is determined so that the surface on which the pressure of the fluid coming from the discharge conduit 26 is greater to that on which this pressure is exerted on the front face of each flange.
  • the seal 49 located in the rear face of each flange, exerts itself a slight pressure so that the flanges are held in abutment against the lateral faces of the pinions when the pump is is not in action and that the pressure in the discharge duct 26 tends to equalize with the pressure in the intake duct 25.
  • the floating body 4 is independent of stresses due to possible differential expansions, it is made so that the sum of the thicknesses of the flanges 14, 15 and the pinions 13, 17 is slightly less than the width of the middle casing 3, the centering the floating body being provided by the seals 49 and the differential pressure which pushes the flanges 14, 15 towards each other against the lateral faces of the pinions 13 and 17.
  • the lobes 27 and 28 preferably extend over an arc of a circle less than 90 °, the flanges 14 and 15 being prevented from tilting by the studs 33, 34 which hold said lobes 27 and 28 against the wall of the cavities circular 22, 23, which also makes it possible to compensate for any differential expansions which may occur between the flanges 14, 15 and the middle casing 3.
  • Fig. 6 shows that the rear face of the flanges 14 and 15 delimits channels 54, 55 communicating the intake duct 25 through the cavity 24 with one end of the lubrication grooves 20 of the bearings 18, 18 a and 19, 19 a .
  • fig. 5 shows a recess 56 made in the front face of the flanges 14 and 15 between the plates 43, 44 and the partition 45.
  • the recess 56 places the cavity 24 under low pressure in communication with the lubrication grooves 20, so that the hydraulic fluid circulates in said grooves from the recess 56 to the channel 54 or 55, or vice versa, according to the direction of rotation of the shafts 1 and 16.
  • each recess 56 reduces the surface on which the pinions rub.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Gear Transmission (AREA)
  • Lubricants (AREA)
  • Hydraulic Motors (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Claims (15)

  1. Hydraulische Zahnradmaschine mit wenigstens einem Satz aus Zwei miteinander zusammenwirkenden Zahnritzeln, die zwischen zwei translatorisch beweglichen Flanschen in Hohlräumen drehbar angeordnet sind, die in einem auf seinen beiden sich gegenüberliegenden Seiten durch ein vorderes und ein hinteres Gehäuse verschlossenen mittleren Gehäuse ausgebildet sind, wobei sich jeder Flansch durch die Anordnung eines Dichtungssystems zwischen diesem Flansch und dem benachbarten Gehäuse in einem ungefähren Druckgleichgewicht befindet,
    dadurch gekennzeichnet, daß die die Zahnritzel (13, 17) tragenden Flansche (14, 15) Vorsprünge (27, 28) von gleichem Krümmungsradius wie die kreisrunden Hohlräume (22, 23) des mittleren Gehäuses (3) begrenzen, das die genannten Flansche enthält, die innerhalb dieses mittleren Gehäuses (3) schwimmend angeordnet sind, und daß hydraulische Druckeinrichtungen (26) die Vorsprünge der Flansche (14, 15) an das mittlere Gehäuse (3) anpressen.
  2. Maschine nach Anspruch 1,
    dadurch gekennzeichnet, daß die Vorsprünge an das mittlere Gehäuse (3) durch einen Differenzdruck angepreßt sind, der zwischen der Rück- und der Vorderseite der Flansche (14, 15) ausgeübt wird, wobei der Druck sich aus dem Verbinden von Kammern (46, 47), die auf der den Zahnritzeln (13, 17) zugewandten Vorderseite jedes Flansches begrenzt sind, mit Abschnitten der Rückseite (38) der Flansche, die durch einen Einstich (48) begrenzt sind, und durch Verbinden der genannten Kammern und der Abschnitte der Rückseite mit einer Druckleitung (26) ergibt, in der ein hoher Druck erzeugt wird.
  3. Machine nach einem der Ansprüche 1 und 2,
    dadurch gekennzeichnet, daß die Flansche (14, 15) jenseits der Vorsprünge zurückgesetzte Abschnitte (29, 30) begrenzen, die Räume (31, 32) bilden, welche die Kammern (46, 47) der Vorderseiten der Flansche mit deren Rückseiten verbinden.
  4. Maschine nach einem der Ansprüche 1 bis 3,
    dadurch gekennzeichnet, daß sich die Vorsprünge (27, 28) der Flansche über einen Kreisbogen kleiner als 90° erstrecken.
  5. Maschine nach einem der Ansprüche 1 bis 4,
    gekennzeichnet durch in die Flansche (14, 15) eingesetzte Klötze (33), die von Federn (36) zur Anlage an der Wand der kreisrunden Hohlräume (22, 23) angepreßt sind, wobei die Anlage der Vorsprünge (27, 28) an dem ihnen entsprechenden Abschnitt dieser Hohlräume aufrechterhalten wird.
  6. Maschine nach einem der Ansprüche 1 bis 5,
    dadurch gekennzeichnet, daß im Einstich (48) der Rückseite der Flansche (14, 15) eine Dichtung (49) angeordnet ist, die Ansätze (53) und Rasten (53a) zum Begrenzen von Durchlässen für das aus der Druckleitung (26) kommende Fluid aufweist.
  7. Maschine nach Anspruch 6,
    dadurch gekennzeichnet, daß die Dichtung (49) eine elastische Längskraft auf das ihr gegenüberliegende Gehäuse (1, 2) ausübt.
  8. Maschine nach einem der Ansprüche 1 bis 7,
    dadurch gekennzeichnet, daß die Vorderseite der Flansche (14, 15) kreisbogenförmige Segmente (39, 40) begrenzt, die durch Scheiben (43, 44) verlängert und miteinander durch eine Trennwand (45) verbunden sind, die mit den genannten kreisbogenförmigen Segmenten und den Scheiben, die Anlageflächen für die Stirnfläche der Zahnritzel bilden, in einer Ebene angeordnet ist.
  9. Maschine nach Anspruch 8,
    dadurch gekennzeichnet, daß sich die kreisbogenförmigen Segmente (39, 40) bis zum Zahngrund (41, 42) der Zahnritzel (13, 17) erstrecken.
  10. Maschine nach Anspruch 8,
    dadurch gekennzeichnet, daß die die kreisbogenförmigen Segmente verbindende Trennwand (45) so gestaltet ist, daß sie wenigstens einer Zahnlücke (41, 42) der Zahnritzel (13, 17) entspricht, wobei sie jede direkte Verbindung zwischen der Einlaßleitung (25) und der Druckleitung (26) verhindert.
  11. Maschine nach einem der Ansprüche 1 bis 10,
    dadurch gekennzeichnet, daß die die Zahnritzel (13, 17) tragenden Wellen (11, 16) in den Flanschen (14, 15) durch Lagerschalen oder Lager (18, 18a, 19, 19a) von kleinerer Breite als die Dicke der genannten Flansche gelagert sind.
  12. Maschine nach einem der Ansprüche 1 bis 11,
    dadurch gekennzeichnet, daß die Rückseite der Flansche (14, 15) Kanäle (54, 55) aufweist, welche die Einlaßleitung (25) mit Schmiernuten (20) der Lagerschalen (18, 18a, 19, 19a) verbinden.
  13. Maschine nach einem der Ansprüche 1 bis 12,
    dadurch gekennzeichnet, daß eine (11) der Wellen der Zahnritzel mit einer Eingangswelle (11a) durch eine Kupplung in der Weise verbunden ist, daß die Hauptwelle (11) und die Nebenwelle (16) denselben Biegebeanspruchungen unterworfen sind.
  14. Maschine nach Anspruch 11,
    dadurch gekennzeichnet, daß die Wellen (11, 16) in den Flanschen (14, 15) axial verschieblich gelagert sind.
  15. Maschine nach einem der Ansprüche 1 bis 14,
    gekennzeichnet durch eine in die Vorderseite der Flansche zwischen jeder Scheibe (43, 44) und der Trennwand (45) eingearbeitete Ausnehmung (56) zur Erzeugung einer Umwälzung zwischen den Kanälen (54, 55) und dieser Ausnehmung über die Schmiernuten (20) der Lagerschalen und zur Reduzierung der Reibungsfläche der Zahnritzel.
EP92402597A 1991-09-24 1992-09-22 Hydraulikzahnradmaschine mit einem schwebendem Körper Expired - Lifetime EP0534836B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9111745 1991-09-24
FR9111745A FR2681647B1 (fr) 1991-09-24 1991-09-24 Machine hydraulique du type a engrenage a corps flottant.

Publications (2)

Publication Number Publication Date
EP0534836A1 EP0534836A1 (de) 1993-03-31
EP0534836B1 true EP0534836B1 (de) 1995-12-06

Family

ID=9417235

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92402597A Expired - Lifetime EP0534836B1 (de) 1991-09-24 1992-09-22 Hydraulikzahnradmaschine mit einem schwebendem Körper

Country Status (9)

Country Link
US (1) US5240393A (de)
EP (1) EP0534836B1 (de)
JP (1) JP2660139B2 (de)
KR (1) KR0148493B1 (de)
AT (1) ATE131255T1 (de)
CA (1) CA2078956C (de)
DE (1) DE69206564T2 (de)
ES (1) ES2081591T3 (de)
FR (1) FR2681647B1 (de)

Families Citing this family (8)

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ES2229228T3 (es) * 1994-07-14 2005-04-16 Casappa S.P.A. Bomba de engranajes.
US6158983A (en) * 1997-04-24 2000-12-12 Trw Inc. Pump having muffler for attenuating noise
US5961309A (en) * 1997-04-24 1999-10-05 Trw Inc. Gear pump with noise attenuation
DE10024884A1 (de) * 2000-05-19 2001-11-22 Bosch Gmbh Robert Zahnradförderpumpe
JP4606842B2 (ja) * 2004-11-01 2011-01-05 カヤバ工業株式会社 ギアポンプ・モータ
KR101032691B1 (ko) * 2009-04-17 2011-05-06 (주)디지탈옵틱 신속한 혈구분리가 가능한 질병진단용 바이오센서
CN105889060A (zh) * 2016-06-16 2016-08-24 江苏国瑞液压机械有限公司 一种两开式轴向间隙补偿高压齿轮泵
KR102325671B1 (ko) 2019-11-08 2021-11-12 박기민 공압조향수단을 구비한 자주형 농기계

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US2691945A (en) * 1950-08-30 1954-10-19 Borg Warner Pressure loaded gear pump
GB853550A (en) * 1956-06-30 1960-11-09 Bosch Gmbh Robert Improvements in machines for example pumps or motors, with hydraulic pressure areas
US3376824A (en) * 1965-07-01 1968-04-09 Turolla Marco Gear pump
AT260030B (de) * 1966-02-08 1968-02-12 Naradi Narodni Podnik Hochdruckzahnrad-Pumpe oder -Motor mit kompensiertem Stirn- und Radialspiel der Zahnräder
GB1311868A (en) * 1969-10-30 1973-03-28 Dewandre Co Ltd C Gear pumps
JPS551286B2 (de) * 1971-11-30 1980-01-12
FR2215103A5 (de) * 1973-01-23 1974-08-19 Hydroperfect Int
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GB1565684A (en) * 1975-10-17 1980-04-23 Kayaba Industry Co Ltd Pressure loaded gear pump
DE2855567A1 (de) * 1978-12-22 1980-06-26 Duesterloh Gmbh Nachstelleinrichtung fuer eine sperrfluegel- oder zahnradmaschine
JPS55100612A (en) * 1979-01-29 1980-07-31 Furukawa Electric Co Ltd Laminated paper for electric insulation
DE3404959A1 (de) * 1984-02-11 1985-08-14 Robert Bosch Gmbh, 7000 Stuttgart Zahnradmaschine (pumpe oder motor)
CN1007369B (zh) * 1987-04-18 1990-03-28 程安强 浮动轴式齿轮泵，齿轮马达

Also Published As

Publication number Publication date
ATE131255T1 (de) 1995-12-15
FR2681647A1 (fr) 1993-03-26
CA2078956A1 (en) 1993-03-25
DE69206564T2 (de) 1996-06-05
JPH05296156A (ja) 1993-11-09
DE69206564D1 (de) 1996-01-18
CA2078956C (en) 1997-12-09
JP2660139B2 (ja) 1997-10-08
KR0148493B1 (ko) 1999-01-15
ES2081591T3 (es) 1996-03-16
KR930006326A (ko) 1993-04-21
FR2681647B1 (fr) 1995-05-12
EP0534836A1 (de) 1993-03-31
US5240393A (en) 1993-08-31

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