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
  • 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
  • F04C15/0042—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
  • 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 relates to improvements made to a hydraulic generator-receiver according to French patent number 2,564,931.
• zone 34 a device for supplying zone 34 "hydraulic bearings" and intervals between sectors, by preferential valve ensuring supply and decompression for all operating cases, direction of rotation, generator or receiver, direction of pressure drop in the zone 34;
• each of the gears 9 and 10 has the same number of teeth, same toothing module, same helical angle oc, such that tg Mt apparent module 5, H tooth width 4, giving a half-step offset between the toothing profiles on the faces;
• FIG. 9 defined a sector-by-sector balancing (page 13, line 30, to page 14, line 20) and FIGS. 18 and 19, the different possibilities of making rotor and stator conduits ; these two provisions are included in the present invention.
• Sector-by-sector balancing consists in dividing the circumference of the pinion reduced by the value necessary for zone 34 at 6 and 3, for example an angular step at 6, and zero angular step at 3, or an angular step at 6, and an angular pitch in 3, in an even number 2 N of equal opposite sectors: - opposite to ⁇ if the number of teeth Z is even; - opposite ⁇ ⁇ an angular half step of teeth, if the number of teeth Z is odd, these equal opposite sectors being at the same pressure potential and in the same angular position on the two flanges 21 and 22 and on the casing 36 . Opposite sectors are equal, but two consecutive sectors can be unequal.
• Figure 1 is a perspective representation of the invention.
• the pinions 9 and 10 are balanced by the stator conduits formed by the cells 30 on the pitch circle, the conduits 23, the cells 100 on the switching circuit 20, and by the rotor conduits formed by the conduits 102 parallel to the axis of the pinion (or inclined to the value of the helix angle ⁇ ), opposite to ⁇ and the conduits 101 of diametrical connection between the conduits 102, the assembly ensuring an equipotential connection between sectors opposite to ⁇ if Z even, and at ⁇ ⁇ half an angular step of teeth if odd Z.
• the number of connections D is greater than N so as to provide, by the overlaps between the conduits 102 and the cells 100, a permanent connection between opposite sectors while ensuring sufficient sealing between successive sectors. This permanent connection is broken at points 6 and 3, zone 34 of permanent total pressure to ensure the creation at points 6 of "hydraulic bearings"
• FIG. 1 also shows the arrangement of the orifices 40 HP - BP, represented parallel to the axes of the pinions and of cylindrical shape. They can also adopt a shape derived from the shape of the fluidd vein generated or received and possibly inclined to the helix angle ⁇ .
• FIG. 2 is a sectional elevation II - II (FIG. 3), still in the case of taking up the clearances by compression of the envelope 36. It shows zone 34 and the arrangement of conduits 101 and 102 in the gables
• FIG. 20 shows the arrangement of the hydrostatic compensation sectors 60 on flanges 21 and 22 in the case of a symmetrical construction, that is to say with symmetry, with respect to the median plane perpendicular to the axes of the pinions 9 and 10.
• FIG. 3 shows a possibility of balancing by a conduit 103 constituted by bores, either through the body 49, or through the covers 54 or 55, or by a steel piping external to the apparatus and connecting two sectors opposite to ⁇ or to It also presents a realization of the conduits 101 from a bore produced by piercing a tooth recess with closure by a brazed plug 105.
• Figure 4 shows the arrangement of the hydrostatic compensation sectors 60 on flanges 21 and 22 in the case of an asymmetrical construction. This arrangement corresponds exactly to the pressures to be balanced in the sense that it takes account of the offset introduced by the helix angle ⁇ , that is to say an angular half pitch of toothing
• the flanges 21 and 22 are however always identical, but in position in the generator-receiver, they only have central symmetry with respect to the point 3 of meshing at mid-height of the pinions 9 and 10.
• Figures 3 and 4 show the hydrostatic compensation sectors 60 on flanges 21 and 22 located near point 3 cut by a certain value for the creation of zone 34 in 3 (mainly cipe an angular pitch of teeth); this in the case where the number of teeth Z is odd. In the case of even Z, these sectors close to point 3 will have a normal value if the zone 34 in 3 is equal to the zone 34 in 6, that is to say an angular pitch of toothing and will be increased if zone 34 adopted in 3 is weaker.
• FIG. 5 section V - V (FIG. 4) shows the conduits 101 and 102 in the pinions 9 and 10, with the conduits 101 being closed by the plug 105.
• This figure shows various possible construction variants:
• the seal housings 45 and 58 are molded in the flange 22.
• the envelope 36 is plastic, the hydrostatic compensation sectors on the envelope 36 are materialized by the clearance 38, the seal 37, the supply orifice 43 and the anti-extrusion device 107.
• the balancing between two opposite tooth recesses is clearly shown by the cells 30, the conduits 23, the stator cells 100 and the rotor conduits 101 and 102.
• FIG. 6 is an external developed view of the casing 36 which shows the hydrostatic balancing sectors 38 on the casing 36 and their supply via the orifice 43. On axis 3 corresponding to the point of engagement of pinions 9 and 10, the non-return
• zone 34 has been replaced by an orifice 43, zone 34 at 3 being eliminated and replaced by a sector of 'hydrostatic compensation at this point, because it is important to have the same pressure on the axis 3 inside and outside of the envelope 36.
• the role of the non-return 39 supplying the zone 34 will be fulfilled by a preferential valve device.
• section VII - VII ( Figure 2) is a section of the casing 36 which shows the detail of the hydrostatic compensation sectors 38 on veloppe 36 with anti-extrusion device 107 and supply via orifice 43.
• FIG. 8 is a panoramic representation of the stator circuits alveoli 30, conduits 23, alveoli 100, and rotor circuits conduits 101 and 102 in the case of an even number of teeth Z and symmetrical construction of the hydrostatic compensation sectors 60 on flanges 21 and 22.
• the upper representation shows the arrangement on the envelope 36, with the zone 34, the seals 37, the orifices 43.
• the form 108 is a form which extends the cells 30 towards the point 6, for hydrostatic balancing of the hollows of teeth at 6 and the creation of "hydraulic bearings" to replace the orifice 33. This arrangement makes it possible to better control the hydrostatic balancing at 6 according to the priority operations in generator or or receiver by varying the length of this shape 108.
• FIG. 9 is a panoramic representation of the stator and rotor circuits in the case of an odd number of teeth Z and symmetrical construction of the hydrostatic compensation sectors 60 on flanges
• FIG. 10 is a panoramic representation of the stator and rotor circuits in the case of an odd number of teeth Z and asymmetrical construction of the hydrostatic compensation sectors 60 on flanges 21 and 22. It requires an offset of half an angular step dd toothing of the alveoli 100 and an inclination conduits 102 at the helix angle ⁇ . It allows a more maintained balancing of the tooth hollows, the alveoli 30 being able to be angularly larger. The channels are tilted.
• FIG. 11 is a panoramic representation of the stator and rotor circuits in the case of an odd number of teeth Z, and asymmetrical construction of the hydrostatic compensation sectors 60 on flanges 21 and 22.
• This construction avoids the offset of an angular half step of toothing of the alveoli 100 between the flanges 21 and 22, and thereby preserving the conduits 102 parallel to the axis of the pinions 9 and 10.
• the shift of is then achieved by a spiral shape of a quarter angular pitch of the link conduit 23 between the cells 30 and the cells 100.
• Intermediate variants are possible depending on the construction facilities they provide.
• FIGS. 12, 13, 14 and 15, according to section II - II show various alternative embodiments of the flange clearance take-up assembly 21 and 22, envelope 36.
• Figure 12 according to section II - II: Plastic flanges 21 and 22 and hard cover 36 with plastic lining 48.
• Seal housings by molding in the covers 54 and 55 or in the flanges 21 and 22, and in the plastic trim 48 or in the body 9.
• Figure 13 according to section II - II: Plastic flanges 21 and 22 and hard or plastic envelope 36.
• Hard flanges 21 and 22, with plastic trim 109, and plastic cover 36 are Hard flanges 21 and 22, with plastic trim 109, and plastic cover 36.
• Seal housings by molding in the covers 54 and 55 or in the plastic lining 109 and in the body 49 or in the casing 36.
• Figure 15 according to section II - II: Flanges 21 and 22 hard or plastic, and envelope 36 plastic
• FIG. 4 shows the return of leakage towards the low sector pressure produced from the bore of the flanges 21 and. 22 by a conduit 110 fitted with a non-return 111 and opening out through a conduit 112 in a hydrostatic compensation sector 60 BP - HP, the assembly being closed by a stopper plug 113.
• Each flange 21 and 22 will be equipped with four of these non-return devices for all operating cases, direction of rotation, generator and receiver, ie two devices per bore. These devices can be considerably simplified, in particular in the plastic flanges 21 and 22, the non-return 111 being able to be produced by a metal washer located on the inlet of the discharge duct in the hydrostatic compensation sector 60.
• FIG. 17, section XVII - XVII shows the new device for pressurizing and decompressing zone 34, replacing the non-return valve 39 in 3 and the orifice 33 in 6 removed, zone 34 being the area of total permanent pressure generated.
• the supply and decompression of the zone 34 is made either by the conduit 114 or by the conduits 117 and 118 the selection being made by a preferential valve 116 opening into the conduit 115 leading to the zone 34.
• This device is closed by the plug 119.
• This figure shows the orifice 40 HP-BP inclined at the helix angle ⁇ ,
• the angle of inclination ⁇ , 120 may for units rotating at high speed of rotation (take values of the order of 45 °, in particular when using chevron teeth. Under these conditions, the HP conduits - BP are brought back perpendicular to the pinion axes, and positioned as on generators and receivers with gears with straight teeth.
• Figures 18 half-section II - II and 19 (partial section through a conduit 101) show an embodiment of the pinions 9 and 10 in two parts:
• a central core 121 produced with the half-conduits 102 on the switching circle 20, and the conduits 101 drilled through this core;
• a ring gear 122 produced with the other part of the conduits 102 on the switching circle 20.
• This ring will either be machined and assembled by brazing 106 on the core 121, or produced by sintering with anchors on the core 121 at the level of the switching circle 20.
• FIG. 20, section II - II is a variant of the protection of the pinion driving 9 against the external stresses transmitted by the power take-off: shocks, parasitic or internal forces resulting from possible imbalances of the hydrostatic compensations.
• the pinion 9 is supported at the covers 54 and 55 by two needle bearings 123 which position this pinion 9 relative to the body 49, to the covers 54 and 55, the other components of the generator-receiver coigur, pinion 10, flanges 21 and 22, envelope 36 balancing normally with respect to this positioning of the pinion 9 in the same way as in the preceding situations.
• This device is a variant of the power take-off protective gear 52 of the pinion 9. It will also allow, in association with hydrostatic compensation devices, a correction of certain minor imbalances resulting from the operation and from other imbalances such as those resulting from the compressibility of the hydraulic fluid in the case of an even number of teeth Z.
• General rules of construction will also allow, in association with hydrostatic compensation devices, a correction of certain minor imbalances resulting from the operation
• Pressure adopted the higher the higher the power to be transmitted. Choose the highest possible pressure, compatible towards low powers, with the sizing requirements of dry tors N, and towards high powers with the admissible mechanical stresses in the gears which are of the order of three, four times the hydraulic pressure. These pressure values can vary from 100 to 800 bars.
• Fluid flow speed hydraulic is the axial component of the speed of movement in the hollow of the tooth: only, this axial overlap is to be taken into account, the tangential component is canceled by the speed of rotation of the pinion. Everything happens as if the generation (or reception) were ensured by a tooth-piston moving at constant speed in a hollow tooth cylinder, this speed being Z times the width of teeth H for a time corresponding to one revolution of pinion, the direction being axial.
• Choice of the apparent modulus Mt, 5 Calculation of Mt for the power transmission as a function of the pressure adopted, the speed of rotation w, the number of teeth Z, and the width H, 4 of teeth.
• Choice of the propeller tilt angle ⁇ Calculation from tg
• Choice of the diameter of the output shaft d Calculation from the maximum torque to be transmitted, and the maximum stress allowed.
• the step in value 3 with an angular toothing pitch, zone 34, is distinct from the sectors located near point 3.
• the bearing in 3 has an angular toothing pitch, zone 34, amputated by half an angular toothing pitch, the sectors located on either side of point 3.
• Sectors N on either side of zone 34 in 3 will therefore have a value:
• the values underlined solid lines are those which make it possible to obtain the same pressure inside and outside of the envelope 36 on the axis 3
• the values underlined lines dotted lines lead to possible constructions as a receiver, but with a lower pressure value outside than inside the envelope 36 on axis 3
• Body 49 obtained by molding, aluminum-based alloy, cast iron or steel. Possible molding of the seal housings.
• Lids 54 and 55 obtained by molding, aluminum-based alloy, cast iron or steel. Possible molding of the seal housings.
• Flanges 21 and 22 are
• plastic or composite materials produced by molding with seal housings. - made of hard materials, lead aluminum alloy, with good friction characteristics

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

Applications Claiming Priority (4)

Publications (2)

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ID=26225150

Family Applications (1)

Country Status (4)

Families Citing this family (14)

Family Cites Families (22)

• 1987
  • 1987-04-01 JP JP62502215A patent/JP2813347B2/ja not_active Expired - Lifetime
  • 1987-04-01 EP EP87902113A patent/EP0262189B1/de not_active Expired - Lifetime
  • 1987-04-01 WO PCT/FR1987/000103 patent/WO1987005975A1/fr active IP Right Grant
• 1990
  • 1990-05-14 US US07/529,738 patent/US5028221A/en not_active Expired - Fee Related

Non-Patent Citations (1)

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