Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
  • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
  • F04B1/047—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the outer ends of the cylinders
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
  • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
  • F04B1/0404—Details or component parts
  • F04B1/0452—Distribution members, e.g. valves
  • F04B1/0465—Distribution members, e.g. valves plate-like
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
  • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
  • F04B1/10—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
  • F04B1/107—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders
  • F04B1/1071—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders with rotary cylinder blocks
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
  • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
  • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
  • F04B1/2014—Details or component parts
  • F04B1/2021—Details or component parts characterised by the contact area between cylinder barrel and valve plate
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
  • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
  • F04B1/26—Control
  • F04B1/30—Control of machines or pumps with rotary cylinder blocks
  • F04B1/303—Control of machines or pumps with rotary cylinder blocks by turning the valve plate
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
  • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
  • F05B2210/00—Working fluid
  • F05B2210/10—Kind or type
  • F05B2210/11—Kind or type liquid, i.e. incompressible
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
  • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10S417/00—Pumps

Definitions

• the present invention relates to a sealing ring for a hydraulic pump distributor.
• Axial or radial piston pumps with rotating cylinders and particularly those with variable displacement are most often constituted by a rotor in which hydraulic cylinders are arranged. In each of these cylinders, a hydraulic piston moves back and forth.
• Said rotor usually has a feed face maintained in contact with the most tight possible with a distribution face - also called ice or distribution plate - arranged on the surface of a stator, the latter may be part of a pump body.
• the supply face generally comprises orifices each connected to one of the hydraulic cylinders, while the distribution face comprises at least one suction port through which the hydraulic pistons can draw hydraulic fluid, and at least one light discharge means by which said pistons can repress said fluid, said orifices and said lights constituting a hydraulic distributor.
• said orifices are alternately connected to a suction duct by the suction lumen, then with a discharge duct by the discharge lumen. It follows from this that a flow of hydraulic fluid can be established between said ducts following the movements back and forth that the hydraulic pistons, each in its hydraulic cylinder.
• hydraulic fluid leaks inevitably occur between the supply face and the distribution face. As a result, a portion of the hydraulic fluid passes directly from the discharge pipe to the suction pipe or vice versa, while another part of said fluid passes directly from said pipes to an inner casing. that comprise in general said hydraulic pumps on the other hand. These leaks reduce the volumetric and energy efficiency of said pumps.
• said platen may for example be an inclined plate or a plateau of rods.
• the distributor is most often constituted by a distribution face positioned on the outer surface of a first cylinder integral with the stator, while the supply face is positioned on the inner surface of a second cylinder, which caps the first cylinder, and which is secured to the rotor.
• the sealing between said faces is preferentially obtained from a weak clearance left between the first and the second cylinder, the manufacture of the latter requiring high machining precision.
• sealing ring for hydraulic pump distributor provides that. compared with the prior art and when - according to a particular embodiment - it equips a distributor with cylindrical feed and distribution faces:
• the sealing ring for a hydraulic pump distributor according to the invention makes it possible in particular:
• the sealing ring for hydraulic pump distributor has a low cost, its manufacture does not involve any complex process or expensive material.
• Said ring is also designed to offer great strength and long life and can operate in the field of high hydraulic pressures.
• Said ring is also applicable to any hydraulic pump or hydraulic motor-pump with fixed or variable displacement, that said pump or motor-pump is in particular pallet, axial piston, radial piston, rotating cylinder or not and whatever the liquid, gaseous, or semi-liquid fluid that it operates.
• the sealing ring for a hydraulic pump distributor provided for a hydraulic distributor that may comprise a hydraulic pump, said distributor comprising at least one pump stator distribution face integral with a pump stator said distribution face having a surface of low-pressure sealing on the stator side of which open at least two intake-discharge ports arranged in the pump stator and which each communicate with at least one inlet-discharge duct of their own and which is also arranged at the said stator, said dispenser also comprising at least one rotor supply face of pump integral with a pump rotor, said supply face having a low-pressure sealing surface on the rotor side from which opens at least one orifice communicating with a supply duct arranged inside said rotor while the surface of the low-pressure seal on the stator side is positioned opposite the low-pressure sealing surface on the rotor side so that the supply orifice is alternately facing one or the other of the two inlet-discharge ports at the less once per pump rotor turn, includes:
• At least one circumferential contact boss arranged axially or radially on either side of the dispensing recess, said boss having a circumferential contact line that can come into contact with the low-pressure sealing surface on the rotor side;
• At least one compression-decompression track arranged on an angular sector of the ring rotor side face, said sector being positioned outside the portion of said face which is placed (radial distribution recess; • At least one ring sealing lip integral or not with the continuous sealing ring and which provides an axial or radial seal between said ring and the ring groove; At least one compression-decompression seal which seals between the stator-side face of the ring and the bottom and / or the axial or radial sides of the ring groove and this, at the angular zone defined by the angular sector on which is arranged the compression-decompression track;
• the sealing ring for hydraulic pump distributor comprises a ring groove which comprises a ring bearing face on its sides which are oriented perpendicularly to the low-pressure sealing surface on the stator side, said face of the ring. support cooperating with a shoulder support ring that includes the continuous seal ring.
• the sealing ring for a hydraulic pump distributor comprises a ring groove which has a ring sealing face on its sides which are oriented perpendicularly to the low-pressure sealing surface on the stator side, said face of the ring. sealing cooperating with a ring sealing shoulder that includes the continuous sealing ring.
• the sealing ring for hydraulic pump distributor comprises a ring sealing lip which is a flexible metal blade integral with the ring sealing shoulder.
• the sealing ring for a hydraulic pump distributor according to the present invention comprises a ring sealing lip which is positioned on, below or in the extension of the ring sealing shoulder.
• the sealing ring for a hydraulic pump distributor according to the present invention comprises a ring sealing lip which is constituted by a lateral seal made of flexible material held simultaneously in contact with the ring groove and with the face of the ring. ring side staior.
• the sealing ring for a hydraulic pump distributor comprises a compression-decompression seal which has at least one sectorial compression-decompression chamber which defines a closed and sealed volume with the stator side face of the ring and the bottom and / or the axial or radial sides of the ring groove.
• the sealing ring for a hydraulic pump distributor comprises a compression-decompression seal which comprises a cellular stiffening structure in which is arranged the compression-decompression sector cell, said honeycomb structure being made in a rigid material that can be directly or indirectly held in position relative to the continuous sealing ring by the rotational stop means, while said rigid material may in all or in part be coated with a flexible material that can enter into contact with the stator side of the ring face on the one hand, and / or with the bottom and / or the axial or radial sides of the ring groove on the other hand.
• the sealing ring for a hydraulic pump distributor comprises a honeycomb stiffening structure which is integrated with the stator-side face of the ring and which is made in the same piece of material as the continuous sealing ring.
• the sealing ring for a hydraulic pump distributor comprises a compression-decompression track which has at least one sectoral compression-compression-compression orifice through which a sectoral compression-decompression duct is opened, the latter connecting with the face of the ring on the rotor side.
• the closed and sealed volume defined by the sectoral cavity compressk> rK) ecornpression said sector orifice being positioned in such a way that the supply orifice is facing said sector orifice once per revolution of the pump rotor, said orifice sectorial then connecting the supply duct to said sealed volume via the sectoral duct compression-decompression.
• the seal ring for a hydraulic pump distributor according to the present invention comprises a side seal and a compression-decompression seal which form a single piece.
• the hydraulic pump distributor sealing ring according to the present invention comprises a ring sealing face which is positioned approximately perpendicular to the circumferential contact line.
• the hydraulic pump distributor sealing ring according to the present invention comprises a ring sealing face which is positioned approximately perpendicular to the circumferential contact line while the ring bearing face is further away from the bottom. the ring groove and the dispensing recess as said sealing face so that it is offset from the plumb of the circumferential contact line.
• the sealing ring for a hydraulic pump distributor comprises at least one of the axial faces of the ring groove which is formed by the axial face of a ring mounting ring which encloses the pump stator.
• the hydraulic pump distributor sealing ring comprises a pump stator distribution face and a pump rotor supply face which are cylindrical while at least one of the intake-discharge ports cooperates with at least one radial force compensation light arranged in the pump stalor, the latter light emerging from the pump stator distribution face and facing the pump rotor supply face, said compensation light being furthermore located - in said stator - diametrically opposite the inlet-discharge lumen with which it co-operates and being connected by a radial force compensation duct to the intake-return duct to which said light is connected. intake-discharge with which it cooperates.
• the sealing ring for a hydraulic pump distributor comprises a compensation light which opens out from the pump stator distribution face via a radial force compensation groove in which is housed at low axial clearance and / or tangential a radial force compensation sealing plate.
• the sealing ring for hydraulic pump distributor comprises a radial force compensation sealing plate which is traversed right through its thickness by a compensating recess which connects the conduit. of radial force compensation with the pump rotor supply face.
• the sealing ring for a hydraulic pump distributor according to the present invention comprises a radiai force compensation groove which comprises a plate bearing face on its sides which are oriented perpendicularly to the low-pressure sealing surface on the stator side, said bearing face cooperating with a plate support shoulder that comprises the radial force compensation sealing plate.
• the sealing ring for a hydraulic pump distributor according to the present invention comprises a radial force compensation groove which has a plate sealing face on its sides which are oriented perpendicular to the low-pressure sealing surface on the stator side. , said sealing face cooperating with a plate sealing shoulder that comprises the radial force compensation sealing plate.
• the sealing ring for a hydraulic pump distributor comprises a radiiai force compensation sealing plate which cooperates with a compensation plate sealing lip integral or not with said plate, said lip providing a tightness axial and / or radial and / or tangential between said plate and the radial force compensation groove.
• the sealing ring for a hydraulic pump distributor comprises a ring sealing lip which is constituted by a flexible seal of compensation of flexible material maintained simultaneously in contact with the radial force compensation groove and with the radial force compensation sealing plate,
• the sealing ring for a hydraulic pump distributor comprises a radiai force compensation sealing plate which comprises at least one compensating peripheral contact boss arranged at its periphery, said boss having a peripheral line of contact. compensation which can come into contact with the pump rotor supply face.
• the sealing ring for a hydraulic pump distributor comprises a plate sealing face which is positioned approximately vertically above the compensating peripheral contact line.
• the hydraulic pump distributor sealing ring comprises a plate sealing face which is positioned approximately perpendicular to the compensating peripheral contact line while the plate bearing face is further away. the bottom of the radial force compensation groove and the compensating recess that said sealing face so that it is offset from the plumb line of the peripheral compensation contact line.
• the sealing ring for a hydraulic pump distributor according to the present invention comprises a dispensing recess which comprises at least one connecting beam which interconnects the circumferential contact bosses, said beam thus defining on either side of its length. at least one sub-recess of distribution.
• the sealing ring for a hydraulic pump distributor according to the present invention comprises rotation stop means which consist of at least one ring rotation stopper pin inserted in a stator stopping pin hole. in the pump stator on the one hand, and introduced into a ring stopper hole through the continuous sealing ring in the direction of its thickness on the other hand.
• FIG. 1 is a three-dimensional phantom view of an axial piston hydraulic pump comprising a hydraulic distributor which receives the hydraulic pump distributor sealing ring according to the invention, the continuous sealing ring of which is generally planar and is intercalated between a pump stator distribution face and a pump rotor supply face which is also flat.
• FIG. 2 is a three-dimensional phantom view of a radial piston hydraulic pump comprising a hydraulic distributor which receives the sealing ring for a hydraulic pump distributor according to the invention, the continuous sealing ring of which is generally cylindrical in shape and is interposed between a pump stator distribution face and a pump cylindrical pump rotor supply face.
• FIGS. 3 and 4 are respectively a three-dimensional phantom view and an exploded three-dimensional view of a hydraulic distributor which receives the sealing ring for a hydraulic pump distributor according to the invention, the continuous sealing ring of which is generally cylindrical in shape, ring cooperating with four radial force compensatio lights placed axially on either side of two inlet-discharge ports.
• Figure 5 is a three-dimensional view of the continuous sealing ring when it is generally cylindrical, and two compression-decompression seals and four side seals consist of a single piece of continuous material flexible with which can cooperate said ring, this configuration may be the subject of a particular embodiment of the sealing ring for hydraulic pump distributor according to the invention.
• Figures 6 and 7 are respectively a side view and a schematic cross section of the continuous seal ring when it is generally cylindrical in shape and comprises - according to a particular embodiment of the Sealing ring for hydraulic pump distributor according to the invention - six sectorial compression-decompression cells and fifteen distribution sub-recesses.
• Figure 8 is a schematic cross section of a hydraulic distributor which receives the seal ring for hydraulic pump distributor according to the invention, said distributor comprising a pump stator provided with two inlet-discharge ports which cooperates with a rotor pump which has nine supply ports.
• Figure 9 is a three-dimensional sectional view of the continuous sealing ring of the hydraulic pump distributor sealing ring according to the invention, as well as lateral seals, the ring groove, and the stator of pump with which cooperates said continuous ring.
• Figure 10 is a partial schematic section along BB of the continuous sealing ring shown in Figure 8 as may be provided by the sealing ring for hydraulic pump distributor according to the invention, said section being made at a sub-level. -videly distribution.
• FIG. 11 is a partial diagrammatic section along CC of the continuous sealing ring shown in FIG. 8 as may be provided by the sealing ring for a hydraulic pump distributor according to the invention, said section showing in particular how a cell can be arranged. sector-specific compression-decompression and how it can be connected to the surface of the compression-decompression track by a sectoral conduit compression-decompression.
• Figures 12 and 3 illustrate in schematic section the operation of the continuous sealing ring such that it can be provided by the sealing ring for hydraulic pump distributor according to the invention when one of the two inlet ports- delivery of the pump stator with which said continuous ring cooperates is subjected to a high pressure.
• Figure 14 is a three-dimensional sectional view of the radial force compensation sealing plate that can comprise the sealing ring for hydraulic pump distributor according to the invention, as well as the flexible anointed compensation sealing, radial force compensation groove, and pump stator with which said plate cooperates.
• FIG. 15 is a diagrammatic section of the radial force compensation sealing plate such as may be provided by the sealing ring for a hydraulic pump distributor according to the invention, said section being made at the level of the compensation recess. that includes said plate.
• FIGS. 1 to 15 show the sealing ring for a hydraulic pump distributor 1.
• the sealing ring for a hydraulic pump distributor 1 is provided for a hydraulic distributor 2 that may comprise a hydraulic pump 44, said distributor 2 comprising at least one pump stator distribution face 5 integral with a pump stator 3, said distribution face 5 having a low-pressure sealing surface on the stator side 12 from which at least two admission ports open in the pump stator 3 and which each communicate with at least one inlet-discharge duct 8 which is their own and which is also arranged inside the stator 3, said distributor 2 also comprising at least one pump rotor supply face 6 integral with a pump rotor 4, said supply face 6 having a low-pressure sealing surface on the rotor side 13 of which opens at least one opening 9 communicating with a supply duct 10 arranged inside said rotor 4 while the low-pressure sealing surface on the stator side 12 is positioned facing the low-pressure sealing surface on the side rotor 13 so that the supply port 9 is alternately facing one or the other of the two inlet-d
• the sealing ring for a hydraulic pump distributor 1 comprises at least one continuous sealing ring 11 housed at low axial and / or radial clearance in a ring groove 16 provided in the stator of pump 3 inside the surface area delimited by the a low-pressure sealing surface on the stator side 12, said ring 11 having a stator side face of the ring 23 housed inside the ring groove 16.
• the continuous sealing ring 11 may advantageously have a low thickness and stiffness so as to be easily deformable and to adapt to its geometric environment even when the hydraulic pressure produced by the hydraulic pump 44 is relatively low.
• the sealing ring for a hydraulic pump distributor 1 comprises at least one circumferential contact boss 14 arranged axially or radially on either side of the 21, said boss 1 having a circumferential contact line 15 which can come into contact with the low-pressure sealing surface on the rotor side 13.
• circumferential contact boss 14 and / or the low-pressure sealing surface on the rotor side 13 can be nitrided, cemented and / or coated with DLC "Diamond-like-Carbon" or any other hard coating and / or low coefficient of friction.
• the sealing ring for a hydraulic pump distributor 1 also comprises at least one compression-decompression track 24 arranged on a certain angular sector of the rotor-side face of the ring 22, said sector being positioned outside the portion of said face 22 where is placed Radiai radiai distribution 21. Said track 24 is particularly visible in Figure 5.
• the sealing ring 1 furthermore comprises at least one ring sealing lip 39 which may or may not be integral with the continuous sealing ring 11 and which provides a seal axial or radial between said ring 11 and the ring groove 16.
• FIG. 11 shows that the sealing ring for a hydraulic pump distributor 1 comprises at least one compression-decompression seal 28 which provides a seal between the stator-side face of the ring 23 and the bottom and / or axial or radial sides of the ring groove 16 and this, at the angular 2one defined by the angular sector on which is arranged the compression-decompression track 24.
• the sealing ring for a hydraulic pump distributor 1 comprises rotational stop means 36 shown in FIGS. 4 and 5 which keep the continuous sealing ring 11 in a fixed angular position with respect to the pump stator 3.
• the sealing ring for hydraulic pump distributor 1 provides that the ring groove 16 may comprise - as illustrated in FIG. 9 - a ring bearing face 17 on its sides which are oriented perpendicular to the surface of the ring. low-pressure sealing on the stator side 12, said bearing face 17 cooperating with a ring bearing shoulder 19 that comprises the continuous sealing ring 11.
• the ring groove 16 may comprise a ring sealing face 18 on its sides which are oriented perpendicularly to the low-pressure sealing surface on the stator side 12, said sealing face 18 cooperating with a ring sealing shoulder 20 that comprises the continuous sealing ring 11.
• the ring sealing lip 39 may be a flexible metal strip integral with the ring sealing shoulder 20. Note that the ring sealing lip 39 can be positioned on, below or in the extension of the ring sealing shoulder 20.
• the ring sealing lip 39 may consist of a lateral seal 27 of flexible material held simultaneously in contact with the ring groove 16 and with the stator-side face of the ring 23, which is clearly shown in FIG.
• Said flexible material may for example be rubber or an elastomer, and may be reinforced with a more rigid material such as plastic, teflon, steel or any stiffening material or structure known to those skilled in the art
• the hydraulic pump distributor sealing ring provides that the compression-decompression seal 28 may have at least one compression-decompression sector cell 25 which defines a sealed and sealed volume. with the face of the ring on the stator side 23 and the bottom and / or the axial or radial sides of the ring groove 16, said cell 25 being of round, oval, oblong, square, rectangular or any geometry, without any limitation .
• the compression-decompression seal 28 may comprise a cellular stiffening structure 40 in which the sectoral compression-decompression cell 25 is arranged, said cellular structure 40 being made of a rigid material 42 and able to be directly or indirectly maintained. in position relative to the continuous sealing ring 11 by the rotational stop means 36.
• FIGS. 4, 5, 7, 8, 11, 12 and 13 show that the cellular stiffening structure 40 can be integrated with the face of the ring on the stator side 23 and be made in the same piece of material as the continuous sealing ring. 1.
• the sectoral compression-decompression cell or recesses 25 may be hollowed out in the stator-side face of the ring 23, for example by electrochemical machining, while the lateral seal 27 and the compression-decompression seal 28 may consist in particular of a flexible material 43 overmolded on the face of the stator side ring 23 and the cellular structure of stiffening 40, said seals then having to load only to achieve the best sealing possible between the continuous seal ring 11 and the ring groove 16 with which it cooperates.
• the compression-decompression track 24 may have at least one sectoral compression orifice.
• decompression 26 through which opens a compression-decompression sector duct 41 the latter connecting with the rotor-side face of the ring 22 the closed and sealed volume that defines the compression-decompression sector cell 25, said sector orifice 26 being positioned in such a manner that the supply port 9 is facing said sector orifice 26 once per revolution of the pump rotor 4, said sector orifice 26 then connecting the supply duct 10 to said sealed volume via the sectoral duct compression-decompression 1.
• the lateral seal 27 and the compression-decompression seal 28 may form only one piece which may be made of various rigid and flexible materials so as to be locally resistant to deformation, and so be locally or uniformly armed and or reinforced by any means known to those skilled in the art
• the side seal 27 and / or the compression-decompression seal 28 may for example comprise a metal core 55 of rigid material 42. It is drowned that the ring sealing face 18 can be positioned approximately perpendicular to the circumferential contact line 15, whereas a slight offset between said face 18 and said line 15 allows - as suggested in FIG. the pressure in the ring groove 16 plate said line 15 on the pump rotor supply face 6 to achieve a good seal between said line 15 and said feed face 6 while generating little effort to contact between these last two and therefore, little friction losses
• FIG. 10 also illustrates that the ring sealing face 18 can be positioned approximately perpendicular to the circumferential contact line 15 while the ring bearing face 17 can be further away from the bottom of the ring groove 16 and the distribution prover 21 as said sealing face 18 so that it is offset with respect to the plumb with the circumferential contact line 15.
• At least one of the axial faces of the ring groove 16 can be formed by the axial face of a ring mounting ring 34 which encloses the pump stator 3.
• said ring 34 for mounting the continuous sealing ring 11 and / or the compression-decompression seal 28 and / or the seal side 27 on the pump stator 3.
• said mounting ring 34 may be mounted on the pump stator 3, in particular by rubbing, gluing, screwing, crimping, rolling or welding and that it may comprise at least one solid seal or viscous lodged between him and the pump stator 3.
• the pump stator distribution face 5 and the pump rotor supply face 6 may be cylindrical while at least one of the intake-discharge ports 7 cooperates with at least a radial force compensation light 30 arranged in the pump stator 3, the latter light 30 opening out from the pump stator distribution face 5 and facing the pump rotor supply face 6.
• compensation 30 being further located - in said stator 3 - diametrically opposite to the intake-discharge port 7 with which it cooperates and being connected by a radial force compensation duct 31 to the intake-discharge duct 8 to which said intake-discharge port 7 is connected. with which she cooperates.
• the surface exposed by said pressure compensating light 30 is substantially equivalent to the surface exposed by the same pressure to the inlet-discharge port 7 with which it co-operates so that said pressure generates only a small amount of pressure. or no radial force on the pump stator 3 and the pump rotor 4.
• the compensation light 30 can be arranged inside the surface area delimited by the lowermost sealing surface. stator side pressure 12 while it can face the low-pressure sealing surface rotor side 13.
• the compensation light 30 can lead to the distribution face of stator pump 5 via a radial force compensation groove 29 in which is housed at low backlash and / or tangential radial force compensation sealing plate 32 which is made of steel, for example.
• FIG. 15 shows that the radial force compensation sealing plate 32 can be traversed right through in the direction of its thickness by a compensating recess 48 which links the radial force compensation duct 31 with the pump rotor supply face 6.
• the compensating evacuation 48 may consist of a hole of small section preserving the radial force compensation sealing plate 32 the best possible rigidity, said hole serving only to propagate to the the pump rotor supply face 6 the pressure prevailing in the radial force compensation duct 31 to which said plate 32 is connected.
• FIG. 14 shows that the radial force compensation groove 29 may comprise a plate bearing face 49 on its sides which are oriented perpendicularly to the low-pressure sealing surface on the stator side 12, said bearing face 49 cooperating with a plate bearing sponge 51 which comprises the radial force compensation sealing plate 32.
• FIG. 14 also shows that the radial force compensation groove 29 may comprise a plate sealing face 50 on its sides which are oriented perpendicular to the low-pressure sealing surface on the stator side 12, said sealing face 50 cooperating with a plate sealing sponge 52 that includes the radial force compensation sealing plate 32.
• the radial force compensation sealing plate 32 can cooperate with a compensation plate sealing lip 45 integral or not with said plate 32.
• said lip 45 providing axial sealing and / or radial and / or tangentially between said plate 32 and the radial force compensation groove 29 while said lip 45 may in particular be a flexible metal blade integral plate sealing shoulder 52 and / or be positioned on, in below or as an extension of the said spell 52.
• the ring sealing lip 39 may consist of a flexible sealing gasket 33 of flexible material held simultaneously in contact with the radial force compensation groove 29 and with the sealing plate of radiai force compensation 32 said flexible material may for example be rubber or an elastomer. and may be armed with a stiffer material such as plastic, teflon, steel or any material or stiffening structure known to those skilled in the art.
• the radiai force compensation sealing plate 32 may comprise at least one peripheral contact boss. compensation 46 arranged at its periphery, said boss 46 having a peripheral compensation contact line 47 able to come into contact with the pump rotor supply face 6.
• peripheral compensation contact boss 46 and / or the low-pressure sealing surface on the rotor side 13 with which it cooperates can be nitrided, cemented and / or coated with DLC "Diamond-like-Carbon" or any other hard coating and / or low coefficient of friction.
• the plate sealing face 50 can be positioned approximately perpendicular to the peripheral compensating contact line 47 while a slight offset between said face 50 and said line 47 allows the pressure in the throat of effort radiai plate 29 said compensation line 47 of the (ace pump 6 rotor power supplies to realize Give sealing between said line 47 and said supply surface 6 while generating little contact force between these last two and therefore, few losses by friction.
• FIG. 15 also shows that the plate sealing face 50 can be positioned approximately perpendicular to the peripheral compensating contact line 47 while the plate bearing face 49 is further away from the bottom of the throat of FIG. radial force compensation 29 and compensating recess 48 as said sealing face 50 so that it is offset from the plumb with the peripheral compensating contact line 47.
• the dispensing recess 1 may comprise at least one connecting beam 56 which connects the circumferential contact bosses 14, said beam 56 thus defining on either side of its length at least one distribution sub-recess 57, said beam 56 thus partially closing the intake-discharge port 7 which is approximately axially or radially aligned with said recess 21 without compromising the good circulation of a hydraulic fluid or any other fluid between said lumen 7 and the supply port 9 facing it.
• the rotational stop means 36 may consist of at least one ring rotation stop pin 35 plugged into a stator stop pin hole 37 provided in the stator of the stator. 3 on the one hand, and introduced into a ring stop pin hole 38 passing through the continuous sealing ring 11 in the direction of its thickness on the other hand.
• the ring rotation stop pin 35 can be freely mounted in the ring stop pin hole 38 and clamped in the stator stop pin hole. 37 or vice versa, said stop pin 35 being for example a metal cylinder or a tensioned elastic pin.
• the pump stator distribution face 5 and the pump rotor supply face 6 are cylindrical. Said ring 1 is therefore also of predominantly cylindrical shape.
• the hydraulic distributor 2 comprises, according to this example, two inlet-discharge ports 7. This justifies that the continuous sealing ring 11 has two distribution recesses 21 each radially aligned with the inlet-discharge lumen 7 with which it co-operates, as shown in FIGS. 3 to 8 and 12 and 13.
• FIG. 10 is a partial section along BB of the continuous sealing ring 1 shown in FIG. 8. Said section is made at a dispensing opening 21 and more particularly at a distribution sub-recess 57. Said section shows in particular the circumferential contact boss 14 arranged axially on either side of said recess 21. As shown in three dimensions in FIG. 9. said boss 14 has a circumferential contact line 15 intended to come into contact with the low-pressure sealing surface on the rotor side 13 so as to achieve with it the best possible seal.
• each compression-decompression sector duct 41 is connected to a sectoral compression-decompression chamber 25 which defines, with the bottom of the bagu groove 16, a sealed and sealed volume.
• FIG. 11 is a partial section along CC of the continuous sealing ring 11 shown in FIG. 8, which shows in detail how a sectoral compression-decompression cell 25 is arranged and how it is connected to the surface of your compression track -depression 24 by the compression-decompression sector duct 41 with which it cooperates.
• the compression-decompression sectoral cells 25 are arranged in a rigidificatton honeycomb structure 40 integrated with the stator-side face 23, said structure 40 forming with a material flexible 43 overmolded on said structure ⁇ the compression-decompression seal 28, as shown in more detail in FIG. 11.
• FIGS. 4 and 5 show that according to the particular embodiment of the sealing ring 1 according to the invention taken here to illustrate the operation, the two compression-decompression seals 28 and the four lateral seals 27 consist in particular of the same continuous piece of flexible material 43.
• said continuous piece is shown separated from the continuous sealing ring 11.
• said The part may over-mold or glue the stator face ring face 23 and the honeycomb structural structure 40 integrated with said ring face 23.
• FIG. 11 shows that the flexible material 43 partially fills the sectoral compression-decompression cells 25 in such a way as to form a pocket in the said cells 25, and produces the best possible seal between the stator-side face of the ring 23 and the ring groove 16 .
• the continuous sealing ring 11 is held in a fixed angular position with respect to the pump stator 3 by the ring rotation stop pin 35 - here a simple metal cylinder - which crosses said ring 11 via the ring stop pin hole 38, said pin 35 being free in said hole 38 while it is locked in the stator stop pin hole 37.
• each intake-discharge light 7 cooperates with the two radial force compensation holes 30 which are arranged at its diametrical opposite in the pump stator 3, the latter lights 30 being connected by their radial force compensation duct 31 to the same intake-discharge duct 8 as the intake-discharge port 7 with which they cooperate, as clearly shown in FIG. 3.
• both said compensation lights 30 is substantially equivalent to the surface exposed at the same pressure intake-discharge light 7 with laquell e they cooperate.
• the pressure in the admitston-refouiement light 7 generates a radial force on the pump stator 3 and the pump rotor 4 weak, or even damaged.
• the compensation sealing plate of radial force 32 that has each radial force compensation light 30 also ensures the best possible seal between said light 30 and said supply fac 6.
• the radial force compensation sealing plate 32 comprises in particular a compensation plate sealing lip 45 which provides a seal between said plate 32 and the radial force compensation groove 29 with which it cooperates.
• FIG. 1 which is a three-dimensional section of said plate 32 and FIG.
• the lip of Compensation plate seal 45 is a thin metal plate arranged in the extension of the plate sealing shoulder 52 and which cooperates with a flexible sealing gasket 33 made of flexible material 43 such as rubber or an elastomer, said flexible material 43 being overmolded under the radial force compensation sealing plate 32 and in the extension of said shoulder 52, said flexible joint 33 being held simultaneously in contact with the radial force compensation groove 29 and with the lower part of the compensation plate sealing lip 45.
• the radial force compensation sealing plate 32 is relatively flexible and easily deformable so that the pressure can press the peripheral compensating contact line 47 on the low-pressure sealing surface on the rotor side. 13.
• an offset is provided between the plate sealing face 50 that has the radial force compensation groove 29 and the plumb with the compensating peripheral contact line 47 that comprises - immediately above said sealing face 50 - the radial force compensation sealing plate 32. It results fromdd offset a weak section on which the pressure is exerted, so that the radial force resulting from said section SI remains low. This tends to achieve a good seal between the peripheral compensating contact line 47 and the low-pressure sealing surface on the side rotor 13 while generating little contact force between said line 47 and said surface 13 and therefore little frictional losses
• the continuous seal ring 11 is of small thickness and as such, it is also relatively flexible and easily deformable. Furthermore, it should also be noted that the ring groove 16 is deep enough for said continuous ring 11 to be radially eccentric with respect to said groove 16 as shown in FIGS. 12 and 13. However, it is understood that in practice the deformations and eccentrations to which the continuous sealing ring 11 is subjected are of the order of a few microns to a few tens of microns and that FIGS. 12 and 13 which show said deformations and eccentrations strongly exaggerate the latter so that can understand the impact on the operation of the sealing ring 1 according to the invention.
• the highest pressure prevails ⁇ for example one thousand bars - while a lower pressure prevails in the lower lumen 7 - for example ten bars - said highest pressure exerts a local radial thrust on the side ring face stator 23 whose intensity is stronger than that exerted on said face 23 the lower pressure at the level of the light 7 Lower.
• the continuous sealing ring 11 deforms and presses against the low-pressure sealing surface on the rotor side 13 at the level of the upper lumen 7 while said continuous ring 11 remains at a distance a few microns or tens of microns of said surface 13 at the level of the lower lumen 7.
• the force corresponding to said radial thrust remains low because the pressure is exerted on the face of stator side ring 23 only on a small section SI of said face 23 as shown in Figure 10.
• Said section ⁇ was determined during the design of the continuous sealing ring 11 and results from the axial offset intentionally provided between the two ring sealing faces 18 that presents the ring groove 16 on either side of the continuous sealing ring 11 , and the plumb with the circumferential contact line 15 arranged immediately above each of said sealing faces 18 on the rotor-side face of the ring 22.
• the circumferential contacts 15 are axially located more inside the continuous sealing ring 11 than the ring sealing faces 18 with which they cooperate in order to produce the local radial thrust.
• the axial offset provided between the two ring sealing faces 18 and the plumb with the circumferential contact lines 15 and which determines the section ⁇ 1 makes the pressure prevailing in the Ring groove 16 effectively plates said lines 15 on the pump rotor supply face 6. This tends to seal between the said lines 15 and the feed face 6 while generating little contact force between the said lines. 15 and said face 6 and therefore, little friction losses.
• the contact pressure between the lines 15 and the pump rotor supply face 6 depends essentially on the width of the contact that the lines 15 produce with said face 6, said width also resulting from a voluntary choice made by means of of the design of the continuous sealing ring 11.
• the rotor side ring face 22 has remained at a distance of a few microns or tens of microns from the In the angular sector occupied by said lower lumen 7, the circumferential contact lines 15 do not therefore press on the pump rotor supply face 6 and perform no sealing.
• FIG. 13 shows the deformation of the continuous sealing ring 11 when it is in the upper lumen 7 that the weakest pressure prevails - for example ten bars - while it is in the lower lumen 7 that the highest pressure prevails - for example a thousand bars, the operation of the ring continues sealing 11 remaining unchanged.
• the hydraulic pump cylinders 54 draw oil under ten bars from the lower slot 7 to push it back under a thousand bars at the level of the upper light 7. Also, during the passage of any supply orifice 9 of the upper lumen 7 to the lower lumen 7 via the compression-decompression track 24, it is necessary to progressively relax the oil included in the hydraulic pump cylinder 54 and the supply ducts 10 which are connected to said supply port 9. During this expansion, the energy that has been stored by said oil during its compression - said oil being compressible - can be mechanically recovered by the hydraulic pump 44. This function is necessary to give said pump 44 a good energy efficiency.
• the feed orifice 9 continues to engage on the compression-decompression track 24 until it encounters a first sectoral pressure-decompression orifice 26 which connects said track 24 to the sealed and closed volume defined by the sectoral cell of FIG. compression-decompression 25 located immediately below said sector orifice 26.
• the compression-decompression track 24 is pressed by the pressure on the low-pressure sealing surface on the rotor side 13 from which opens the supply orifice 9. This constitutes a seal around the supply port 9 between the compression-decompression track 24 and the low-pressure sealing surface on the rotor side 13, with a plating force of said track 24 on said surface 13 which is all the more important that the pressure prevailing in the hydraulic pump cylinder 54 is high.
• the angular difference between two sectoral compression-decompression orifices 26 and the diameter of said orifices is calculated so that a same supply port 9 can not be simultaneously facing two said sectoral orifices 26.
• the geometry of the sectoral compression-decompression cells 25 shown in particular in FIG. 5 is non-limiting and may differ from one cell 25 to the other.
• the choice of said geometry must be guided by the need on the one hand, to produce the best possible seal between the compression-decompression track 24 and the low-pressure sealing surface on the rotor side 13 and other on the other hand, to generate the lowest possible friction between said track 24 and said surface 13.
• FIG. 11 shows the section ⁇ 1 resulting from the axial offset between the ring sealing faces 18 and the plumb with the circumferential contact lines 15, said offset being provided in the angular zone of the continuous sealing ring 11 It occupies the compression-decompression track 24 at the same distance as it is provided on the remainder of the circumference of the continuous sealing ring 11.
• Said section S1 makes it possible to complete the sealing in axial borders of said track 24.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Details And Applications Of Rotary Liquid Pumps (AREA)
• Rotary Pumps (AREA)
• Details Of Reciprocating Pumps (AREA)
• Reciprocating Pumps (AREA)
• Sealing With Elastic Sealing Lips (AREA)
• Sealing Devices (AREA)

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• 2013
  • 2013-09-25 FR FR1359250A patent/FR3011045B1/fr active Active
• 2014
  • 2014-09-22 WO PCT/FR2014/052352 patent/WO2015044571A1/fr active Application Filing
  • 2014-09-22 JP JP2016516863A patent/JP6387088B2/ja active Active
  • 2014-09-22 EP EP14796176.7A patent/EP3049671B1/de active Active
  • 2014-09-22 AU AU2014326490A patent/AU2014326490B2/en active Active
  • 2014-09-22 CN CN201480053212.4A patent/CN105593519B/zh active Active
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  • 2014-09-22 ES ES14796176.7T patent/ES2670551T3/es active Active
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