EP3049671A1

EP3049671A1 - Sealing ring for a hydraulic pump distributor

Info

Publication number: EP3049671A1
Application number: EP14796176.7A
Authority: EP
Inventors: Vianney Rabhi
Original assignee: Individual
Current assignee: Individual
Priority date: 2013-09-25
Filing date: 2014-09-22
Publication date: 2016-08-03
Anticipated expiration: 2034-09-22
Also published as: ES2670551T3; KR20160058901A; KR102254259B1; FR3011045B1; AU2014326490B2; CA2925485C; AU2014326490A1; JP2016539285A; WO2015044571A1; CN105593519B; JP6387088B2; CA2925485A1; FR3011045A1; EP3049671B1; CN105593519A

Abstract

A sealing ring for a hydraulic pump distributor (i) for a hydraulic distributor (2) of a hydraulic pump (44), comprising a continuous sealing ring (11) housed in a ring groove (16) arranged in a pump stator (3) of which the inlet/discharge ports (7) are each aligned with a distribution recess (21) passing through said ring (11) from one side to the other in the direction of the thickness of same, the latter comprising a circumferential contact boss (14) that has a line of circumferential contact (15) that can come into contact with a low-pressure sealing surface on the rotor side (13), said ring (11) also comprising a compression/decompression track (24), a ring sealing lip (39) that provides a seal between said ring (11) and the ring groove (16), and rotation-stop means (36).

Description

SEAL RING FOR DISTRIBUTOR

HYDRAULIC PUMP

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. Thus, when the rotor rotates, 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.

It is noted that 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.

In the case of axial piston hydraulic pumps, to be as tight as possible between them. the supply face and the distribution face are subjected to a force which tends to keep them in contact with each other. This effort results in particular from the reaction force that oppose a platinum force to the thrust of the hydraulic pistons, said platen may for example be an inclined plate or a plateau of rods.

Combined with the relative displacement of said faces, said reaction force results in friction losses which reduce the energy efficiency of the pumps thus designed. Note that in the particular case of axial piston hydraulic pumps, the supply face and the distribution face are each positioned on a flat circular surface.

In the case of radial piston radial piston hydraulic pumps, 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. According to this particular configuration, 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.

Obtaining the seal according to this strategy leads to major leaks occurring in the latter type of distributor, even if the friction losses generated by said distributor are potentially lower. In addition, unless the radial piston hydraulic pump is radially balanced with at least two suction ports and two diametrically opposed discharge ports, the pressure exerted by the hydraulic fluid on the section of the light subjected to the strongest pressure can subject said distributor to a potentially large radial force and which generates additional frictional losses not negligible. This disadvantage can be mitigated or practically eliminated if radial force balancing grooves are provided which counterbalance the radial force of the intake or discharge light subjected to the highest pressure. Such an arrangement is for example disclosed in the patent application relating to a motor-pump No. 1354562 dated May 22, 2013. belonging to the applicant.

Taking into account what has just been said, in the current state of the art, a distributor whose seal is high tends to generate high friction losses while conversely, a distributor with low friction losses is rather inclined to have significant hydraulic fluid leaks.

It should be noted that the relative decrease in energy efficiency induced by hydraulic leaks and by friction beads occurring between the supply face and the distribution face of hydraulic pumps with axial or radial cylinders with rotating cylinders and in particular those with variable displacement it is all the more important that the pressure under which said pumps operate is high on the one hand, and that said pumps are used with partial displacement on the other hand.

It is therefore particularly important to reduce as much as possible said leaks and said losses while recovering the highest possible fraction of the energy released by the hydraulic fluid during its decompression.

It is to serve this set of objectives that the sealing ring for hydraulic pump distributor according to the invention provides that. compared with the prior art and when - according to a particular embodiment - it equips a distributor with cylindrical feed and distribution faces:

At the same friction losses, the leakage rates occurring at the level of the distributor between the suction ducts and the discharge ducts are reduced, as are the leakage rates occurring between said ducts and the internal casing which the pumps generally comprise. hydraulic; • Same level of tightness. the friction losses generated by said distributor are reduced.

Consequently, the sealing ring for a hydraulic pump distributor according to the invention makes it possible in particular:

"To contribute to the realization of high-efficiency, water-based hydraulic pumps and energy:" To allow the design and manufacture of hydraulic pumps or hydraulic motor-pumps that can favorably constitute, with other components, a hydraulic hybrid transmission with high efficiency energy for the propulsion of motor vehicles. In addition, the sealing ring for hydraulic pump distributor according to the invention 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 other features of the present invention have been described in the description and in the dependent claims directly or indirectly dependent on the main claim.

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 continuous sealing ring housed at low backlash and / or radial clearance in a ring groove formed in the pump stator within the surface area defined by the low-pressure sealing surface on the stator side, said ring having a stator-side ring face housed inside the ring groove, and a rotor-side ring face that is flush with the low-pressure sealing surface on the stator side, while the inlet-discharge ports open at said sealing surface via said groove, said ring being axially or radially wider than said openings so as to cover them and having approximately axially or radially aligned with the latter, at least one through-distribution recess the continuous sealing ring from one side to the other in the direction of its thickness, said recess being able to put in communication one of the two lights intake-discharge with the supply port when the latter is approximately opposite said light;

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;

"Rotational stop means which keep the continuous sealing ring in a fixed angular position relative to the pump stator. The sealing ring for hydraulic pump distributor according to the present invention 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 according to the present invention 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 according to the present invention 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 according to the present invention 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 according to the present invention 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 according to the present invention 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 according to the present invention 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 according to the present invention 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 according to the present invention 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 according to the present invention 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 according to the present invention 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 according to the present invention 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 according to the present invention 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 according to the present invention 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 according to the present invention comprises a plate sealing face which is positioned approximately vertically above the compensating peripheral contact line.

The hydraulic pump distributor sealing ring according to the present invention 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. the following description with reference to the accompanying drawings, given by way of non-limiting examples will better understand the invention, the features it has, and the benefits it is likely to provide:

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. DESCRIPTION OF THE INVENTION

FIGS. 1 to 15 show the sealing ring for a hydraulic pump distributor 1. The sealing ring for a hydraulic pump distributor 1 according to the invention 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-discharge ports 7 at least once per revolution of the pump rotor 4.

It can be seen in FIGS. 1 to 13 that 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. and a rotor side ring face 22 which is flush with the low sealing surface - Stator side pressure 12, while the inlet-discharge ports 7 open at said sealing surface 12 through said groove 6, said ring 11 being axially or radially wider than said lights 7 so covering them el having, approximately axially or radially aligned with the latter, at least one dispensing recess 21 passing through the continuous sealing ring 11 from one end to the other in the direction of its thickness, said recess 21 being able to put in communication the one of the two intake-discharge lights 7 with the supply port 9 when the latter is approximately opposite said light 7, the same recess distr ibution 21 can put only one light in communication with said orifice 9.

Note that 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.

Also, as particularly illustrated in FIGS. 9 and 10, the sealing ring for a hydraulic pump distributor 1 according to the invention 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.

It is noted that advantageously, the 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.

As can be seen clearly in FIG. 9, the sealing ring 1 according to the invention 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.

In particular, 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.

Finally, 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 according to the invention 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.

It can still be seen in FIG. 9 that 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.

As shown in FIG. 9, 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

As shown in FIG. 11, the hydraulic pump distributor sealing ring according to the invention 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. while said rigid material 42 may in all or part be coated with a flexible material 43 which can come into contact with the ring face next stator 23 on the one hand, and / or with the bottom and / or the axial or radial sides of the ring groove 16 on the other hand. 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. In this case, 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. According to a particular embodiment of the sealing ring for a hydraulic pump distributor 1 according to the invention shown in FIGS. 5 to 8 and in FIG. 11, 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.

Note that in this case, the pressure to which the hydraulic fluid contained in the feed pipe 10 is immediately propagated to the closed and sealed volume that defines the sectoral cell compression-decompression 25. Taking this into account, Said sector compression-decompression chamber 25 on which said pressure is exerted is advantageously greater than the area of the feed opening section 9 so that the compression-decompression track 2 is naturally found plated. by said pressure on the low-pressure sealing surface on the rotor side 13 to which it faces, this result producing the desired sealing between said track 24 and said surface 13.

It will be noted - particularly in FIGS. 4 and 5 - that 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 As such, as shown in Figures 10 and 11, 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.

According to a particular embodiment of the sealing ring for a hydraulic pump distributor 1 according to the invention shown in FIG. 4, 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.

Note that 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.

It can be seen in FIGS. 3 and 4 that 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.

It should be noted that 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. It is further noted that 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. As illustrated particularly in Figures 4, 14 and 15, 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.

It is noted that 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.

Still in FIG. 1, it can be seen that 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.

It is noted that 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. According to the particular embodiment of the sealing ring for a hydraulic pump distributor 1 according to the invention shown in FIGS. 1 and 15, 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.

It is noted that advantageously, the 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. Also, 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.This configuration is clearly exposed in Figure 15.

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.

As shown in Figures 3 to 10 and 1 and 13, 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.

It should be noted in FIGS. 4 and 5 that 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. Note that 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.

OPERATION OF THE INVENTION:

From the foregoing description and in connection with FIGS. 1 to 15, the operation of the sealing ring for a hydraulic pump distributor 1 according to the present invention is understood. To illustrate the operation of said ring 1, the configuration shown in FIGS. 2 to 15, which has been applied to a hydraulic pump 44, of which the hydraulic pump pistons 53 and the hydraulic pump cylinders 54 are arranged radially in the pump rotor 4 as shown in Figure 2. It is specified that according to this non-limiting embodiment, said pump 44 pumps oil.

According to this non-limiting embodiment of the sealing ring 1 according to the invention, 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. As is clearly illustrated in FIGS. 8, 1 and 13, 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. FIGS. 3 to 10 and 12 and 13 show that the distribution recesses 21 pass through the continuous sealing ring 11 from one end to the other in the direction of its thickness and are separated from each other in the circumferential direction by a compression-decompression track 24 on the surface of which open several sectoral compression-decompression ducts 41 via a sectoral orifice of compression-decompression 26 own. According to this non-constructive example of embodiment, the circumferential contact bosses 14 arranged axially on either side of the distribution recesses 21 are connected in the axial direction by connecting beams 56 which separate the distribution sub-recesses 57.

It will be noted - particularly in FIGS. 8, 12 and 13 - that 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.

It is clearly seen in FIGS. 5, 7, 8, 12 and 13 that 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. For the sake of clarity, in said figures, said continuous piece is shown separated from the continuous sealing ring 11. In practice, 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 .

As can be seen in FIGS. 4 and 5, 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.

It is easy to deduce from FIG. 4 that the continuous sealing ring 11 thus configured with its compression-decompression seals 28 and its lateral sealing joints 27 could be mounted on the pump stator 3 by virtue of the ring mounting ring 34.

It can also be seen in FIGS. 3 and 4 that the pump stator 3 has four radiai axial force compensation slots 30 placed axially on either side of the inlet-discharge ports 7. According to this particular configuration of the bushing of FIG. Sealing for hydraulic pump distributor 1 according to the invention, 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. It is noted that the total area are exposed to pressure 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. Thus, 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. It can be seen that, like the continuous sealing ring 11 which ensures the best possible seal between the inlet-discharge ports 7 and the pump rotor supply face 6, 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.

As such, 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. 15 which is a diagrammatic section thereof show that, in the case taken here to illustrate the operation of the sealing ring i according to the invention, 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.

It can be specified here that 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.

To do this, 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

To properly describe the operation of the sealing ring 1 according to the invention, it should be noted that 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.

Thus, when the hydraulic pump 44 with radial pistons - of the type shown in FIG. 2 · is operating, its pump rotor 4 rotates around the pump stator 3. The pump stator distribution face 5 is positioned facing the face of the pump. pump rotor supply 6 while the discharge inlet ports 7 are approximately aligned with the nine supply port ports 9 which each feed a hydraulic pump cylinder 54 via its own supply duct 10. It can be seen in FIGS. 12 and 13 that the pressure that prevails in the upwardly located inlet-discharge lumen 7 and that we will tentatively call "upper lumen 7" does not propagate to the intake-discharge lumen. placed at the bottom in said Figures 12 and 13 and that we will call temporarily "light 7 below" and this, thanks to the continuous seal ring 11 and in particular the compression-decompression seal 28 which prohibits the oil to pass tangentially between the stator-side face of the ring 23 and the bottom of the ring groove 16.

If, as shown in FIG. 12, it is in the upper lumen 7 that 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.

As a result of this asymmetry of thrust, 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. Note that 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. In this respect, it should be noted that, as shown in FIG. 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. It should be noted that 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. It is seen in Figure 10 between the sealing surface of ring 18 that has the ring groove 16 and ^the shoulder sealing ring 20 that has the ring 11 continues to seal the sealing is effected of on the one hand by the ring sealing lip 39 which remains in contact - given its elasticity - with the seal sealing face 18, and on the other hand, by the lateral sealing gasket 27. Thus, said lip 39 avoids that said seal 27 is extruded even under very high pressure - for example two thousand bars - while it ensures a perfect seal. It has been seen in FIG. 12 that, due to the deformation of the continuous sealing ring 1, at the level of the inner lumen 7, 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.

Consequently, the seal between said lower lumen 7 and the pump rotor supply face 6 is no longer achieved only by the small clearance of a few microns or tens of microns left between the low-pressure sealing surface quoted. stator 12 and the low-pressure sealing surface on the rotor side 1. Said weak game is obtained in particular thanks to a high machining accuracy of said surfaces 12, 13 while the leak rates passing between them remain low given the low pressure - here, ten bars according to the example chosen - prevailing in the light 7 lower. The energy loss related to said leakage rates is negligible.

It will be understood that 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.

It has been noticed - particularly in FIGS. 8, 12 and 13 - the sectoral compression-decompression cells 25 which ensure a good seal between the supply orifices 9 and the compression-decompression track 24 after said orifices 9 have left the sector. angular occupied by the upper light 7. Said cells 25 are also visible in three dimensions in FIG. 5, and in schematic section in FIG.

Indeed, according to the example taken here to illustrate the operation of the sealing ring 1 according to the invention, 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.

When - because of the rotation of the pump rotor 4 - the supply port 9 leaves the upper lumen 7 to engage the compression-decompression track 24, said orifice 9 which previously put said upper lumen 7 in connection with the corresponding hydraulic pump cylinder 54 via its own feed duct 10 is closed by said track 24. The mechanism of the hydraulic pump 44 increasing the volume of the hydraulic pump cylinder 54, the oil contained therein relaxes and begins to mechanically yield to said pump 44 the energy stored during the compression of said oil.

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.

It is therefore found in the configuration shown in Figure 11 which has the immediate effect of propagating the pressure in the hydraulic pump cylinder 54 to said closed and sealed volume whose radial section is substantially larger than that of the orifice 9. The resulting radial radial section S2 is shown in FIG. S2 was determined during the design of the continuous sealing ring 11 on the basis of a compromise between sealing and friction losses.

Or made of the differential radial section § £, 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.

Also, it is understood that as and when the feed port 9 is advanced on the compression-decompression track 24, the volume of the hydraulic pump cylinder 54 increases without the amount of oil increasing. This is imposed by the mechanism of the hydraulic pump 44. This effectively results in an expansion of said oil and a recovery of energy that had been previously stored during the compression of the latter.

When said supply port 9 encounters the sectoral compression-decompression orifice 26 following, the same principle of plating of the compression-decompression track 24 on the low-pressure sealing surface on the rotor side 13 takes place, but a lower pressure, and so on until said supply port 9 reaches the lower lumen 7.

Note that according to the non-limiting embodiment of embodiment of the sealing ring 1 according to the invention illustrated in FIGS. 8, 12 and 13, 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. To increase the number of sectoral compression-decompression ports 26 and therefore the number of sectorial compression-decompression orifice 26, it is noted that one can provide oblong axial supply ports 9, which can be separated in staggered rows in at least two rows, the latter configuration can also be applied - at as a non-limitative exemption - to sectoral compression-decompression ports 26.

Furthermore, 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. In practice, 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. II It should be understood that the foregoing description has been given by way of example only and does not in any way limit the scope of the invention of which one would not go out by replacing the execution details described by any other equivalent.

Claims

1. Sealing ring for a hydraulic pump distributor (1) 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 nozzle (5) having a low-pressure sealing surface on the stator side (12) from which at least two intake-discharge ports (7) arranged in the pump stator (3) and which each communicate with at least one inlet-discharge duct (8) of 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 rotor-side low-pressure sealing surface (13) from which least one orifice (9) communicating with a conduit supply (10) arranged inside said rotor (4) while the low-pressure sealing surface on the stator side (12) is positioned opposite the low-pressure sealing surface on the rotor side (3) so the supply opening (9) is alternately facing one or the other of the two inlet-discharge ports (7) at least once per revolution of the pump rotor (4), characterized in that what she understands:

At least one continuous sealing ring (11) housed at low axial and / or radial clearance in a ring groove (16) formed in the pump stator (3) inside the surface area which defines the surface of the low-pressure seal on the stator side (12), said ring (11) having a stator side ring tace (23) housed inside the ring groove (16). and a rotor side ring face (22) which is flush with the stator-side low-pressure sealing surface (12), while the intake-refueling ports (7) open at said sealing surface (12). by means of said groove (16), said ring (11) being axially or radially wider than said slots (7) so as to cover them and comprising, approximately axially or radially aligned with the latter, at least one recess of distribution (21) passing through the continuous sealing ring (11) from one side to the other in the direction of its thickness, said recess (21) being able to put in communication one of the two intake-refilling ports (7) with the supply port (9) when the latter is approximately opposite said light (7);

At least one circumferential contact boss (1) arranged axially or radially on either side of the dispensing recess (21), said boss (14) having a circumferential contact line (15) capable of coming into contact with the low-pressure sealing surface on the rotor side (13); ● At least one compresskMvdecompression track (24) arranged on a certain angular sector of the rotor side ring face (22). said sector being positioned outside the portion of said face (22) or is placed the radial distribution recess (21); ● At least one ring sealing lip (39) integral or not with the continuous sealing ring (11) and which carries an axial or radial seal between said ring (11) and the ring groove (16);

At least one compression-decompression seal (28) which seals between the stator-side face of the ring (23) and the bottom and / or the axial or radial sides of the ring groove (16) and this, at level of the angular zone defined by the angular sector on which the compression-decompression track (24) is arranged; ● Rotational stop means (36) which keep the ring continuous of étancnéité (11) in a fixed angular position relative to the pump stator (3).

2. sealing ring for hydraulic pump distributor according to claim 1, characterized in that (a ring groove (16) has a ring bearing face (17) on its sides which are oriented perpendicular to the surface of the low-pressure etancnéité side stator (12), said bearing face (17) cooperating with a bearing abutment ring (19) that comprises the continuous ring étancnéité (11).

Hydraulic pump distributor sealing ring according to Claim 1, characterized in that the ring groove (16) has a ring sealing face (18) on its sides yes are oriented perpendicularly to the low-pressure sealing surface on the stator side (12), said sealing lace (18) cooperating with a sealing impeded seal (20). ) that includes the continuous sealing ring (1).

4. Sealing ring for hydraulic pump distributor according to claim 3. characterized in that the ring sealing lip (39) is a flexible metal blade integral with the ring sealing shoulder (20).

5. ^Gasket for hydraulic pump dispenser according to claim 3, characterized in that the ring sealing lip (39) is positioned over, under or in the extension of the ring sealing shoulder ( 20).

6. Sealing ring for a hydraulic pump distributor according to claim 1, characterized in that the ring sealing lip (39) consists of a lateral seal (27) of flexible material held simultaneously in contact. with the ring groove (16) and with the stator side ring face (23).

Hydraulic pump distributor sealing ring according to Claim 1, characterized in that the compression-decompression seal (28) has at least one sectoral compression-decompression chamber (25) which defines a closed volume. and sealed with the stator side of the ring face (23) and the bottom and / or the axial or radial sides of the ring groove (16).

8. Sealing ring for a hydraulic pump distributor according to claim 7, characterized in that the compression-decompression seal (28) comprises a honeycomb structure (40) in which is arranged the sectoral cell of compression-decompression (25), said honeycomb structure (40) being made of a rigid material (42) and able to be directly or indirectly held in position relative to the continuous sealing ring (11) by the stop means in rotation (36), while said rigid material (42) may in all or in part be coated with a flexible material (43) which can come into contact with the face of the ring on the stator side (23) on the one hand, and / or with the bottom and / or the axial or radial sides of the ring groove (16) on the other hand.

9. Sealing ring for a hydraulic pump distributor according to claim 8, characterized in that the honeycomb stiffening structure

(40) is integrated in the stator side ring face (23) and is made of the same piece of material as the continuous sealing ring (11).

10. Sealing ring for a hydraulic pump distributor according to claim 7, characterized in that the compression-decompression track (24) has at least one compression-decompression sector orifice (26) through which a sectoral compression duct opens - Decompression (41) the latter connecting with the rotor-side face of the rotor (22) the closed and sealed volume that defines the sectoral compartment of compressiorv decompression (25), said sector orifice (26) being positioned in such a way that the supply port (9) is opposite 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 duct compression-decompression sector (41).

Hydraulic pump distributor sealing ring according to Claim 6, characterized in that the lateral seal (27) and the compression-decompression seal (28) form a single piece.

Hydraulic pump distributor sealing ring according to Claim 3, characterized in that the ring sealing face (18) is positioned approximately perpendicular to the circumferential contact line (15).

Hydraulic pump distributor sealing ring according to claims 2 and 3, characterized in that the ring sealing face (18) is positioned approximately perpendicular to the circumferential contact line (15) while the ring bearing face (17) is further away from the bottom of the ring groove (16) and the dispensing recess (21) than said sealing face (18) so that it is offset by relative to the line of the circumferential contact line (15).

Sealing ring for a hydraulic pump distributor according to claim 1, characterized in that at least one of the axial faces of the ring groove (16) is formed by the axial face of a mounting ring of ring (34) which encloses the pump stator (3).

Hydraulic pump distributor sealing ring according to Claim 1, characterized in that the pump stator distribution face (5) and the pump rotor supply face (6) are cylindrical while the at least one of the inlet-discharge ports (7) cooperates with at least one radial force compensation slot (30) arranged in the pump stator (3), this latter slot (30) opening out from the distribution face pump stator (S) and facing the pump rotor supply face (6), said compensating light (30) being further located - in said stator (3) - diametrically opposite the inlet-discharge lumen (7) with which eHe cooperates and is connected by a radial force compensation duct (31) to the intake-discharge duct (8) to which said intake-discharge lumen (7) is connected (7). ) with which she cooperates.

Hydraulic pump distributor sealing ring according to Claim 15, characterized in that the compensating opening (30) opens out of the pump stator distribution face (5) via a radial force compensation groove ( 29) in which is housed a low axial play and / or tangential a radial force compensation sealing plate (32).

17. Sealing ring for hydraulic pump distributor according to claim 16, characterized in that the radial force compensation sealing plate (32) is traversed right through in the direction of its thickness by a recess of compensation (48) which relates the radiai force compensation conduit (31) to the pump rotor supply face (6).

Sealing ring for a hydraulic pump distributor according to Claim 16, characterized in that the radial force compensation groove (29) has a plate bearing face (49) on its sides which are oriented perpendicularly to the low-pressure sealing surface on the side stator (12), said bearing face (49) cooperating with a plate bearing sponge (51) that comprises the radial force compensation sealing plate (32).

Sealing ring for a hydraulic pump distributor according to claim 16, characterized in that the radial force compensation groove (29) has a plate sealing face (50) on its sides which are oriented perpendicularly to the stator-side low-pressure sealing surface (12), said sealing face (50) cooperating with a plate-sealing impedance (52) which comprises the radial force compensation sealing plate (32) .

Sealing ring for a hydraulic pump distributor according to claim 16, characterized in that the radial force compensation sealing plate (32) cooperates with a compensation plate sealing lip (45) integral with or not of said plate (32), said lip

(45) providing axial and / or radial and / or tangential sealing between said plate (32) and the radial force compensation groove (29).

Sealing ring for a hydraulic pump distributor according to claim 20, characterized in that the ring sealing lip (39) consists of a flexible sealing gasket (33) made of flexible material and held simultaneously. in contact with the radial force compensation groove (29) and with the radial force compensation sealing plate (32).

22. Sealing ring for a hydraulic pump distributor according to claims 16 and 17, characterized in that the radial force compensation sealing plate (32) comprises at least one compensating peripheral contact boss (46) arranged in its periphery, said boss

(46) having a compensating peripheral contact line (47) engageable with the pump rotor supply face (6).

23. Sealing ring for a hydraulic pump distributor according to claims 19 and 22, characterized in that the plate sealing face (50) is positioned approximately vertically in line with the peripheral compensation contact line (47). .

Sealing ring for a hydraulic pump distributor according to claims 18, 19 and 22, characterized in that the plate sealing face (50) is positioned approximately vertically in line with the peripheral compensation contact line ( 47) while the plate bearing face (49) is further away from the bottom of the radial force compensation groove (29) and the compensating cavity (48) than said sealing face (50) so that it is offset with respect to the line of the peripheral compensation contact line (47).

25. Sealing ring for a hydraulic pump distributor according to claim 1, characterized in that the dispensing recess (21) comprises at least one connecting beam (56) which interconnects the circumferential contact bosses (14). said beam (56) thus defining on either side of its length at least one distribution sub-recess (57).

26. Sealing ring for hydraulic pump distributor according to claim 1, characterized in that the rotational stop means (36) consist of at least one ring rotation stop pin (35) inserted in a stator stopping pin hole (37) provided in the pump stator (3) on the one hand, and introduced into a ring stopping pin hole (38) passing through the continuous sealing ring (11). ) in the direction of its thickness on the other hand