KR102254259B1 - Sealing ring for a hydraulic pump distributor - Google Patents

Abstract

The hydraulic pump distributor sealing ring (1) for the hydraulic distributor (2) of the hydraulic pump (44) includes a continuous sealing ring (11) received in a ring groove (16) formed in the pump stator (3), the pump stator The inlet-transfer ports 7 formed in are respectively aligned with the distribution openings 21 passing through the ring 11 in the thickness direction, which rings are circumferentially capable of contacting the rotor-side low pressure sealing surface 13 It comprises a circumferential-contact boss (14) with a directional contact line (15), the ring (11) between the compression-decompression track (24), the ring (11) and the ring groove (16). It further comprises a ring sealing lip 39 providing sealing, and anti-rotation means 36.

Description

SEALING RING FOR A HYDRAULIC PUMP DISTRIBUTOR}

The subject of the invention is a sealing ring for a hydraulic pump distributor.

Rotary cylinder axial-piston or radial-piston hydraulic pumps, in particular pumps with variable cylinder capacity, usually consist of a rotor in which hydraulic cylinders are formed. In each of the cylinders, a hydraulic piston performs a reciprocating motion.

The rotor typically comprises a feed face formed on the surface of the stator-often also known as a distribution plate-which maintains the most sealable contact with the distribution face, wherein the stator is the pump body Can form part of.

The supply surface generally includes an orifice each connected to one of the hydraulic cylinders, while the distribution surface includes at least one inlet port through which the hydraulic piston can introduce hydraulic fluid, and the The piston comprises at least one delivery port through which the fluid can be delivered, and the orifice and the port constitute a hydraulic distributor.

Thus, when the rotor rotates, the orifice is communicated with the inlet duct by the inlet port and then alternately communicates with the delivery duct through the delivery port. As a result, a flow of hydraulic fluid may be established between the ducts due to the reciprocating motion that the hydraulic piston can perform in each hydraulic cylinder.

It is noted that leakage of hydraulic fluid inevitably occurs between the supply side and the distribution side. As a result, a portion of the hydraulic fluid passes directly from the delivery duct to the inlet duct on the one hand or vice versa, and on the other hand, a portion of the fluid passes from the duct to the inner housing which is generally contained Pass directly. This leakage reduces the volume and energy efficiency of the pump.

In the case where the hydraulic pump is of the type having an axial piston, in order to be as sealed to each other as possible, the supply and distribution surfaces are loaded so that these supply and distribution surfaces tend to keep in contact with each other. This load is in particular due to the reaction force generated by the thrust plate in response to the thrust of the hydraulic piston, for example the plate may be a swashplate or a yoke.

In combination with the relative movement of the faces, the reaction force causes frictional losses, reducing the energy efficiency of the pump designed in this way. It should be noted that in the specific case of the axial-piston hydraulic pump, the supply and distribution surfaces are respectively located on a planar circular surface.

In the case of a rotary cylinder radial-piston hydraulic pump, the distributor typically consists of a distributing face located on the outer surface of the first cylinder fixed to the stator, while the feed face fitted over the first cylinder and fixed to the rotor. It is located on the inner surface of the second cylinder. With this particular configuration, the sealing between the faces is preferably obtained by the small clearance left between the first and second cylinders, requiring extreme precision in machining these cylinders during manufacture.

Acquiring a seal using this strategy results in significant leakage in this latter type of dispenser, although the friction losses produced by the dispenser are potentially lower. Furthermore, unless the radial-piston hydraulic pump is radially balanced with at least two inlet ports and two delivery ports arranged opposite each other, the pressure exerted by the hydraulic fluid on the cross section of the higher pressure port is It can be attributed to the distributor what could be a potentially high radial load that could lead to non-negligible additional frictional losses.

This drawback can be reduced, if not actually eliminated, if it offsets the radial load of the inlet or delivery port under higher pressure by providing grooves that equalize the radial-load. Such an arrangement is disclosed, for example, in Patent Application No. 1354562 relating to a pump motor, filed May 22, 2013 in the name of the present applicant.

As always, in the state of the art, distributors with high sealing levels tend to generate high friction losses, while conversely, distributors with low friction losses tend to exhibit significant leakage of hydraulic fluid.

The relative decrease in energy efficiency caused by hydraulic leakage and friction losses occurring between the supply and distribution surfaces of rotary cylinder radial-piston or axial-piston hydraulic pumps, in particular pumps with variable cylinder capacity, is, on the one hand, It is understood that the higher the pressure at which the pump operates, and on the other hand the pump is used with partial cylinder capacity.

It is thus of particular importance to reduce the leakage and the losses as much as possible while at the same time recovering the highest possible amount of energy released by the hydraulic fluid when it is decompressed.

In order to fulfill this object, the sealing ring for a hydraulic pump distributor according to the present invention, according to one specific embodiment, provides the following, compared to the prior art, when equipped with a distributor having a cylindrical supply side and a distribution side:

동일한 마찰 손실에서, 상기 입구 덕트와 상기 전달 덕트 사이에 상기 분배기에서 일어나는 누설 흐름이 감소되고, 상기 입구 덕트와, 유압 펌프가 일반적으로 포함하는 상기 내부 하우징 사이에 일어나는 누설 흐름도 또한 감소된다;

At the same frictional loss, the leakage flow occurring in the distributor between the inlet duct and the delivery duct is reduced, and the leakage flow occurring between the inlet duct and the inner housing generally included in a hydraulic pump is also reduced;

동일한 밀봉 레벨에서, 상기 분배기에 의해 생성되는 마찰 손실이 더 낮아진다.

At the same sealing level, the friction loss produced by the distributor is lower.

As a result, the sealing ring for the hydraulic pump distributor according to the invention, in particular,

높은 용적과 에너지 효율을 나타내는 유압 펌프를 생성하는데 기여할 수 있고;

Can contribute to creating a hydraulic pump that exhibits high volume and energy efficiency;

다른 부품들과 함께, 자동차를 추진하도록 의도된 높은 에너지 효율의 유압 하이브리드 트랜스미션(hydraulic hybrid transmission)을 유리하게 구성할 수 있는 유압 펌프 또는 유압 모터-펌프를 설계하고 제조할 수 있다.

Together with other parts, it is possible to design and manufacture hydraulic pumps or hydraulic motor-pumps that can advantageously constitute a high energy efficient hydraulic hybrid transmission intended to propel automobiles.

Furthermore, the sealing ring for a hydraulic pump distributor according to the invention provides a low cost manufacturing method that does not require complicated methods or expensive materials.

The ring is also designed to provide high robustness and longevity and can be used in high hydraulic applications.

Said ring is also in particular, whether the pump or pump-motor is of the vane, axial piston, radial piston, rotary or non-rotating cylinder type, and the fluid operating in the pump or pump-motor is liquid, gas or Regardless of whether it is semi-liquid, it can be applied to any hydraulic pump or hydraulic pump-motor with fixed or variable cylinder capacity.

A sealing ring for a hydraulic pump distributor designed for a hydraulic distributor that a hydraulic pump may contain, the distributor comprising at least one pump stator dispensing face fixed to the pump stator, the distributing face having a stator-side low pressure sealing surface (stator-side low pressure sealing surface), at least two inlet-transfer ports formed in the pump stator from the stator-side low pressure sealing surface are opened, and each inlet-transfer port is specified to this inlet-transfer port. In communication with at least one inlet-transfer duct formed in the stator, the distributor also comprising at least one pump rotor feed face fixed to the pump rotor, the feed face having a rotor-side low pressure sealing surface And at least one orifice in communication with a supply duct formed in the rotor from the rotor-side low pressure sealing surface is opened, while the stator-side low pressure sealing surface is positioned toward the rotor-side low pressure sealing surface to be supplied. The orifice alternately faces one or the other of the two inlet-transfer ports at least once per revolution of the pump rotor, and the sealing ring,

상기 고정자-측 저압 밀봉 표면에 의해 한정된 표면적 내 상기 펌프 고정자에 형성된 링 그루브에서 축방향 및/또는 방사방향으로 작은 양의 간격을 두고 수용된 적어도 하나의 연속적인 밀봉 링으로서, 상기 링은 상기 링 그루브 내에 수용된 고정자-측 링 면(stator-side ring face)과, 상기 고정자-측 저압 밀봉 표면과 동일 높이에 있는 회전자-측 링 면을 구비하는 반면, 상기 입구-전달 포트는 상기 그루브를 통해 상기 밀봉 표면으로 개방되고, 상기 링은 상기 포트보다 축방향으로 또는 방사방향으로 더 넓어서 상기 포트를 커버하며, 상기 포트와 축방향 또는 방사방향으로 대략 정렬되어, 두께 방향으로 상기 연속적인 밀봉 링을 통과하는 적어도 하나의 분배 개구(distribution opening)를 포함하고, 상기 개구는 공급 오리피스가 대략 상기 포트를 향하고 있을 때 상기 2개의 입구-전달 포트들 중 하나의 포트를 상기 공급 오리피스와 연통되게 배치할 수 있는, 상기 적어도 하나의 연속적인 밀봉 링;

At least one continuous sealing ring received at a small amount of space axially and/or radially in a ring groove formed in the pump stator within a surface area defined by the stator-side low pressure sealing surface, wherein the ring is the ring groove It has a stator-side ring face contained within and a rotor-side ring face flush with the stator-side low pressure sealing surface, while the inlet-transfer port is provided with the groove through the groove. Open to a sealing surface, the ring is axially or radially wider than the port to cover the port, approximately aligned with the port in an axial or radial direction, passing through the continuous sealing ring in the thickness direction And at least one distribution opening, the opening being capable of disposing one of the two inlet-transfer ports in communication with the supply orifice when the supply orifice is facing approximately the port. , The at least one continuous sealing ring;

상기 분배 개구의 각 측에 축방향으로 또는 방사방향으로 형성된 적어도 하나의 외주방향-접촉 보스(circumferential-contact boss)로서, 상기 보스는 상기 회전자-측 저압 밀봉 표면과 접촉할 수 있는 외주방향 접촉 라인을 구비하는, 상기 적어도 하나의 외주방향-접촉 보스;

At least one circumferential-contact boss formed axially or radially on each side of the dispensing opening, the boss being an circumferential contact capable of contacting the rotor-side low pressure sealing surface The at least one circumferential-contact boss having a line;

상기 회전자-측 링 면의 특정 각도 섹터(angular sector)에 형성된 적어도 하나의 압축-압축해제 트랙(compression-decompression track)으로서, 상기 섹터는 상기 방사방향 분배 개구가 위치된 상기 면의 부분의 외부에 위치된, 상기 적어도 하나의 압축-압축해제 트랙;

At least one compression-decompression track formed in a specific angular sector of the rotor-side ring face, the sector being outside of the portion of the face in which the radial distribution opening is located Located at the at least one compression-decompression track;

상기 연속적인 밀봉 링에 고정되거나 고정되지 않을 수 있고, 상기 링과 상기 링 그루브 사이에 축방향 또는 방사방향으로 밀봉을 수행하는 적어도 하나의 링 밀봉 립(ring sealing lip);

At least one ring sealing lip that may or may not be fixed to the continuous sealing ring and performs sealing in an axial or radial direction between the ring and the ring groove;

상기 고정자-측 링 면과 상기 링 그루브의 바텀(bottom) 및/또는 축방향 또는 방사방향 측면 사이에 밀봉을 수행하고 상기 압축-압축해제 트랙이 형성된 각도 섹터에 의해 한정된 각도 영역에서 밀봉을 수행하는 적어도 하나의 압축-압축해제 밀봉 가스킷(sealing gasket);

Performing sealing between the stator-side ring surface and the bottom and/or axial or radial side of the ring groove and sealing in an angular area defined by an angular sector in which the compression-decompression track is formed. At least one compression-release sealing gasket;

상기 펌프 고정자에 대해 고정된 각도 위치로 상기 연속적인 밀봉 링을 유지하는 회전-방지 수단을 포함한다.

Anti-rotation means for holding the continuous sealing ring in a fixed angular position relative to the pump stator.

The sealing ring for the hydraulic pump distributor according to the present invention comprises a ring groove comprising a ring bearing face on a side oriented perpendicular to the stator-side low pressure sealing surface, the support surface being the continuous It cooperates with the ring bearing shoulder that the sealing ring contains.

The sealing ring for the hydraulic pump distributor according to the present invention comprises a ring groove comprising a ring sealing surface on a side oriented perpendicular to the stator-side low pressure sealing surface, the sealing surface comprising the continuous sealing ring. Works with ring sealed shoulders.

The sealing ring for a hydraulic pump distributor according to the invention comprises a ring sealing lip, which is a flexible metal blade fixed to the ring sealing shoulder.

The sealing ring for a hydraulic pump distributor according to the invention comprises a ring sealing lip located on, below or in a continuation of the ring sealing shoulder.

The sealing ring for a hydraulic pump distributor according to the invention comprises a ring sealing lip consisting of a lateral sealing gasket made of a flexible material that holds in contact with the ring groove and the stator-side ring face simultaneously.

The sealing ring for the hydraulic pump distributor according to the invention, together with the stator-side ring face and the bottom and/or axial or radial side of the ring groove, defines a closed and sealed volume. And a compression-decompression sealing gasket having a sectorial compression-decompression cell cavity.

The sealing ring for the hydraulic pump distributor according to the present invention comprises a compression-release sealing gasket including a stiffening cellular structure in which the fan-shaped compression-release cell cavity is formed, and the partition structure is rigid. It is made of a rigid material and can be held in place relative to the continuous sealing ring by means of the anti-rotation means, either directly or indirectly, while the rigid material is on the one hand the stator-side ring face. And/or on the other hand a flexible material capable of contacting the bottom and/or axial or radial sides of the ring groove.

The sealing ring for the hydraulic pump distributor according to the invention comprises a rigid partitioned structure incorporated into the stator-side ring face and made of the same material as the continuous sealing ring.

The sealing ring for the hydraulic pump distributor according to the present invention comprises a compression-decompression track having at least one flat compression-decompression orifice through which the flat compression-decompression duct is opened, and the duct is the flat compression-compression Connecting the closed and sealed volume defined by a release cell cavity with the rotor-side ring face, the sector orifice positioned in such a way that the feed orifice faces the sector orifice once per rotation of the pump rotor , The sector orifice connects the supply duct to the sealed volume through the sector compression-release duct.

The sealing ring for a hydraulic pump distributor according to the invention comprises a lateral sealing gasket and a compression-release sealing gasket, forming only one single piece.

The sealing ring for the hydraulic pump distributor according to the invention comprises a ring sealing surface located approximately plumb with the circumferential contact line.

The sealing ring for the hydraulic pump distributor according to the invention comprises a ring sealing surface positioned approximately perpendicular to the circumferential contact line, while the ring sealing surface is further from the bottom of the ring groove and the dispensing opening than the sealing surface. At a distance, it is offset from perpendicular to the circumferential contact line.

The sealing ring for a hydraulic pump distributor according to the invention comprises at least one of the axial faces of the ring groove formed by the axial face of a ring mounting band that closely fits around the pump stator.

The sealing ring for the hydraulic pump distributor according to the invention comprises a cylindrical pump stator distribution surface and a pump rotor supply surface, while at least one of the inlet-transport ports is at least one radial load formed in the pump stator. Cooperating with a load-compensating port, the port opening from the pump stator dispensing surface and facing the pump rotor supply surface, the compensating port also opposite the cooperating inlet-transfer port-the stator In-placed and connected to the inlet-transfer duct by a radial-load compensation duct, to which the inlet-transfer port cooperating therewith is connected.

The sealing ring for the hydraulic pump distributor according to the invention is that the radial-load compensation sealing plate is opened from the pump stator distribution surface through a radial-load compensation groove received at a small amount of spacing in the axial and/or tangential direction. Includes a compensation port.

The sealing ring for the hydraulic pump distributor according to the present invention comprises a radial-load compensation sealing plate passing in the thickness direction through a compensation opening for arranging the radial-load compensation duct in communication with the pump rotor supply surface.

The sealing ring for the hydraulic pump distributor according to the present invention comprises a radial-load compensating groove comprising a plate support surface on a side oriented perpendicular to the stator-side low pressure sealing surface, and the support surface is the radial direction- It cooperates with the plate support shoulder that the load compensation sealing plate contains.

The sealing ring for the hydraulic pump distributor according to the present invention comprises a radial-load compensating groove comprising a plate sealing surface on a side oriented perpendicular to the stator-side low pressure sealing surface, the sealing surface being the radial- It cooperates with the plate sealing shoulder, which the load compensation sealing plate contains.

The sealing ring for the hydraulic pump distributor according to the present invention comprises a radial-load compensation sealing plate cooperating with a compensation-plate sealing lip that may or may not be fixed to the plate, the lip being the plate and the radial direction. -Sealing is carried out in the axial and/or radial and/or tangential directions between the load compensating grooves.

The sealing ring for a hydraulic pump distributor according to the present invention comprises a ring sealing lip consisting of a flexible compensation sealing gasket made of a flexible material that maintains contact simultaneously with the radial-load compensation groove and the radial-load compensation sealing plate. .

The sealing ring for the hydraulic pump distributor according to the present invention includes a radial-load compensation sealing plate including at least one compensation peripheral contact boss formed around, and the boss is capable of contacting the pump rotor supply surface. Compensating peripheral contact lines are provided.

The sealing ring for the hydraulic pump distributor according to the invention comprises a plate sealing surface located approximately perpendicular to the compensating peripheral contact line.

The sealing ring for the hydraulic pump distributor according to the present invention comprises a plate sealing surface positioned approximately perpendicular to the compensating peripheral contact line, whereas the plate supporting surface comprises the radial-load compensating groove and the compensating opening rather than the sealing surface. It is further from the bottom of the offset so that it is offset from the vertical with the surrounding contact line.

The sealing ring for the hydraulic pump distributor according to the present invention comprises a distribution opening comprising at least one connecting beam connecting the circumferential-contact bosses together, wherein the beam is at least one on both sides of the length. The distribution sub-opening is defined.

The sealing ring for the hydraulic pump distributor according to the present invention is plugged into a stator rotation-proofing pin hole formed in the pump stator on the one hand and on the other hand the continuous sealing ring in the thickness direction. And a rotation-preventing means consisting of at least one ring rotation-proofing pin inserted into the passing ring rotation-proofing pinhole.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention, its features, and the advantages it can provide will be better understood through the following detailed description with reference to the accompanying drawings, which are given as non-limiting examples:
1 is an axial direction comprising a hydraulic distributor employing a hydraulic pump distributor sealing ring according to the invention, wherein the continuous sealing ring is generally planar and disposed between the pump stator dispensing surface and the planar pump rotor supply surface. -3D virtual diagram of piston hydraulic pump;
Fig. 2 is a radial direction comprising a hydraulic distributor employing a hydraulic pump distributor sealing ring according to the present invention, wherein the continuous sealing ring is generally cylindrical in shape and is disposed between the pump stator dispensing surface and the cylindrically shaped pump rotor supply surface. -3D virtual diagram of piston hydraulic pump;
Figures 3 and 4 show, respectively, the continuous sealing ring is generally cylindrical in shape, the ring cooperating with four radial-load compensation ports located axially on each side of the two inlet-transfer ports. A three-dimensional virtual view and a three-dimensional exploded view of a hydraulic distributor employing the hydraulic pump distributor sealing ring according to the invention;
5 shows a continuous sealing ring when the sealing ring is of a wholly cylindrical shape, the configuration of which can form one specific embodiment of the hydraulic pump distributor sealing ring according to the present invention, and the same series, which can cooperate with the ring. Three-dimensional view of two compression-decompressing sealing gaskets and four lateral sealing gaskets made of a flexible material;
Figures 6 and 7 show, respectively, when the sealing ring is of a wholly cylindrical shape and the sealing ring-according to one specific embodiment of the hydraulic pump distributor sealing ring according to the invention-6 flat compression-decompression cell cavities and 15 A side view and a schematic cross-sectional view of a continuous sealing ring when it includes two dispensing sub-opens;
Fig. 8 is a view of a hydraulic distributor employing a hydraulic pump distributor sealing ring according to the invention, wherein the distributor comprises a pump stator having two inlet-transfer ports cooperating with a pump rotor having nine feed orifices. Schematic section;
Fig. 9 is a three-dimensional cross-sectional view of a continuous sealing ring of a hydraulic pump distributor sealing ring according to the present invention, a lateral sealing gasket, the ring groove and the pump stator, in which the continuous ring cooperates;
Fig. 10 is a partial schematic cross-sectional view of the BB of the continuous sealing ring shown in Fig. 8, which can be provided by the hydraulic pump distributor sealing ring according to the invention, the section taken in the dispensing sub-opening area. Cross-section;
Fig. 11 is a partial schematic cross-sectional view of the CC of the continuous sealing ring shown in Fig. 8, which can be provided by the hydraulic pump distributor sealing ring according to the invention, in particular in which the sectoral compression-decompression cell cavities will be arranged. A cross-sectional view showing how this cell cavity can be connected to the surface of the compression-decompression track by means of a flat compression-release duct;
12 and 13 show a continuous sealing ring that can be provided by the hydraulic pump distributor sealing ring according to the invention when one of the two inlet-transfer ports of the pump stator with which the continuous ring cooperates is subjected to high pressure. A schematic cross-sectional view showing how it operates;
14 shows a radially-load compensating sealing plate that the hydraulic pump distributor sealing ring according to the present invention may include, a flexible compensating sealing gasket, in which the plate cooperates, the radial-load compensating groove, and three of the pump stator. Dimensional section;
Fig. 15 is a schematic cross-sectional view of a radial-load compensating sealing plate that can be provided by a hydraulic pump distributor sealing ring according to the present invention, the cross-section taken in the compensation opening area contained in the plate.

1 to 15 show a hydraulic pump distributor sealing ring 1.

The hydraulic pump distributor sealing ring 1 according to the invention is intended for a hydraulic distributor 2 which a hydraulic pump 44 may contain, said distributor 2 being at least one fixed to the pump stator 3. It comprises a pump stator dispensing face (5), said distributing face (5) having a stator-side low pressure sealing surface (12) and at least two inlets formed in the pump stator (3) from this stator-side low pressure sealing surface. The delivery port 7 is opened, each inlet-delivery port being specific to this inlet-delivery port and communicating with at least one inlet-delivery duct (8) formed in the stator (3), and the distributor (2) is It also comprises at least one pump rotor feed face 6 fixed to the pump rotor 4, said feed face 6 having a rotor-side low pressure sealing surface 13, the rotor-side At least one orifice 9 in communication with the supply duct 10 formed in the rotor 4 from the low pressure sealing surface is opened, while the stator-side low pressure sealing surface 12 is a rotor-side low pressure sealing surface ( 13) so that the feed orifices 9 alternately face one or the other of the two inlet-transfer ports 7 at least once per revolution of the pump rotor 4.

1 to 13 show the hydraulic pump distributor sealing ring 1 axially and/or radially in a ring groove 16 formed in the pump stator 3 within the surface area defined by the stator-side low pressure sealing surface 12. It comprises at least one continuous sealing ring (11) received at a small amount of space, the ring (11) comprising a stator-side ring face (23) received in a ring groove (16), and the stator-side low pressure With the rotor-side ring surface 22 flush with the sealing surface 12, the inlet-transfer port 7 opens to the sealing surface 12 through the groove 16, and the The ring 11 is axially or radially wider than the port 7 to cover this port, which is roughly aligned with this port in the axial or radial direction and passes through a continuous sealing ring 11 in the thickness direction. At least one dispensing opening (21), the opening (21) connecting one of the two inlet-transfer ports (7) with the supply orifice (9) when the supply orifice is approximately facing the port (7). It is shown that only one port can be arranged in communication with the orifice 9, and one and the same dispensing opening 21 can be arranged in communication.

The continuous sealing ring 11 advantageously has a small thickness and small stiffness so that the sealing ring can be easily deformed and adapted to the geometrical environment even when the hydraulic pressure generated by the hydraulic pump 44 is relatively low. It is noted that there is.

Thus, in particular as shown in Figs. 9 and 10, the hydraulic pump distributor sealing ring 1 according to the invention is at least one circumferentially formed axially or radially on each side of the dispensing opening 21- A contact boss 14 is included, which has an circumferential contact line 15 capable of contacting the rotor-side low pressure sealing surface 13.

The circumferential-contact boss 14 and/or the rotor-side low pressure sealing surface 13 are coated with Diamond-Like-Carbon (DLC) and/or case-hardened and/or It is noted that it may be nitrided or have any other coating that is hard and/or has a low coefficient of friction.

The hydraulic pump distributor sealing ring (1) further comprises at least one compression-decompression track (24) formed in a specific angular sector of the rotor-side ring face (22), which sector has a radial distribution opening (21). Is located outside the portion of the face 22 on which it is located. The track 24 can be seen in particular in FIG. 5.

As can be clearly seen in Fig. 9, the sealing ring 1 according to the invention may or may not be fixed to the continuous sealing ring 11, and the shaft between the ring 11 and the ring groove 16 It further comprises at least one ring sealing lip 39 that performs sealing in a directional or radial direction.

11 shows in particular that the hydraulic pump distributor sealing ring 1 performs a sealing between the stator-side ring face 23 and the bottom and/or axial or radial side of the ring groove 16 and the compression-decompression track ( 24) is shown comprising at least one compression-decompression sealing gasket 28 that performs sealing in an angular region defined by the formed angular sector.

Finally, the hydraulic pump distributor sealing ring 1 is a rotation-preventing means for holding the continuous sealing ring 11 in a fixed angular position with respect to the pump stator 3, as shown in Figs. It includes (36).

The hydraulic pump distributor sealing ring 1 according to the invention has a ring support surface 17 on the side with the ring groove 16-as shown in FIG. 9-oriented perpendicularly to the stator-side low pressure sealing surface 12 The support surface 17 is provided with cooperating with the ring support shoulder 19 which the continuous sealing ring 11 comprises.

In FIG. 9 again, the ring groove 16 may comprise a ring sealing surface 18 on the side oriented perpendicularly to the stator-side low pressure sealing surface 12, which sealing surface 18 is a continuous sealing ring. It is noted that it cooperates with the ring sealing shoulder 20 that 11 contains.

As shown in FIG. 9, the ring sealing lip 39 may be a flexible metal blade fixed to the ring sealing shoulder 20.

It is noted that the ring sealing lip 39 can be located on, below or within the continuation of the ring sealing shoulder 20.

The ring sealing lip 39 may consist of a ring groove 16 and a lateral sealing gasket 27 made of a flexible material that maintains contact simultaneously with the stator-side ring face 23 as clearly shown in FIG. 10. have. The flexible material may be, for example, rubber or elastomer, and a more rigid material such as plastic, Teflon, steel or any stiffening known to those of ordinary skill in the art. It can be reinforced with a material or structure.

As shown in Fig. 11, in the hydraulic pump distributor sealing ring according to the present invention, the compression-decompression sealing gasket 28 is provided at the bottom and/or axial direction of the stator-side ring face 23 and the ring groove 16. Or with radial sides, at least one fan-shaped compression-decompression cell cavity 25 defining a closed and sealed volume, wherein the cell cavity 25 is circular, oval, oblong. ), square, rectangular, or any geometric cross-sectional shape including, but not limited to, shapes.

Compression-decompression sealing gasket 28 may include a rigid partitioned structure 40 in which a fan-shaped compression-decompression cell cavity 25 is formed, and the partitioned structure 40 is made of a rigid material 42. It is manufactured and can be held in place with respect to the continuous sealing ring 11 by means of direct or indirect anti-rotation means 36, while the rigid material 42 is on the one hand the stator-side ring face ( 23), and/or may be fully or partially coated with a flexible material 43 which may, on the other hand, contact the bottom and/or axial or radial sides of the ring groove 16.

4, 5, 7, 8, 11, 12 and 13 show that a rigid partitioned structure 40 can be incorporated into the stator-side ring face 23 and with a continuous sealing ring 11 It shows what is made of the same material. In this case, the flat compression-decompression cell cavities or cavities 25 can be hollowed in the stator-side ring face 23, for example using electrochemical machining, while lateral sealing. The gasket 27 and the compression-release sealing gasket 28 may in particular be made of a flexible material 43 overmolded on the stator-side ring face 23 and the rigid partitioned structure 40, which gasket is It only serves to provide the best possible seal between the successive sealing ring 11 and the cooperating ring groove 16.

According to one specific embodiment of the hydraulic pump distributor sealing ring 1 according to the invention shown in FIGS. 5 to 8 and 11, the compression-decompression track 24 has a flat compression-decompression duct 41. It may be provided with at least one open fan-shaped compression-release orifice 26, the duct having a closed and sealed volume defined by the fan-shaped compression-release cell cavity 25 on the rotor-side ring face 22. ) And the fan-shaped orifice 26 is positioned in such a way that the supply orifice 9 faces the fan-shaped orifice 26 once per rotation of the pump rotor 4, and the fan-shaped orifice 26 is supplied The duct 10 is connected to the sealed volume through a flat compression-release duct 41.

In this case, it is noted that the pressure received by the hydraulic fluid contained in the supply duct 10 directly diffuses into the closed and sealed volume defined by the sector compression-decompression cell cavity 25. Taking this into account, the area of the compression-decompression fan-shaped cell cavity 25 to which the pressure is applied is advantageously made larger than the cross-sectional area of the supply orifice 9, so that the compression-decompression track 24 is Naturally it is firmly pressed against the oriented rotor-side low pressure sealing surface 13, resulting in the desired seal between the track 24 and the surface 13.

-Particularly in Figs. 4 and 5-The lateral sealing gasket 27 and the compression-decompression sealing gasket 28 are resistant to local deformation and by any means known to those of ordinary skill in the art. It is noted that it can be formed from only one part which can be made of several rigid and flexible materials to be reinforced locally or evenly and/or reinforced.

In this respect, as shown in FIGS. 10 and 11, the lateral sealing gasket 27 and/or the compression-release sealing gasket 28 is made of, for example, a rigid material 42. core) 55 may be provided.

The ring sealing surface 18 can be positioned approximately perpendicular to the circumferential contact line 15, but by a small offset between the surface 18 and the line 15-as suggested in Fig. 10-the ring groove The pressure appearing in (16) firmly presses the line (15) to the pump rotor supply surface (6) to achieve an excellent sealing between the line (15) and the supply surface (6), and at the same time between the two surfaces. It is noted that it creates only a small amount of contact load and causes little friction loss.

FIG. 10 shows that the ring sealing surface 18 can be positioned approximately perpendicular to the circumferential contact line 15, while the ring sealing surface 17 has a ring groove 16 and a dispensing opening ( It further shows that it is further from the bottom of 21) so that it can be offset from the circumferential contact line 15 and perpendicular.

According to another specific embodiment of the hydraulic pump distributor sealing ring 1 according to the invention shown in FIG. 4, at least one of the axial faces of the ring groove 16 is tight around the pump stator 3. It can be formed by the axial side of the ring mounting band 34 to be fitted, by means of which the sealing ring 11 and/or the compression-release sealing gasket 28 and/or the lateral direction The sealing gasket 27 can be mounted on the pump stator 3.

The mounting band 34 is in particular the pump stator 3 by shrink-fitting, bonding, screwing, crimping, rolling or welding. It is noted that the mounting band may comprise at least one solid or viscous sealing gasket received between the band and the pump stator 3.

3 and 4, the pump stator distribution surface 5 and the pump rotor supply surface 6 may be cylindrical, while at least one of the inlet-transfer ports 7 is formed in the pump stator 3 Cooperates with the radial-load compensation port 30 of, the port 30 is open from the pump stator dispensing surface 5 and faces the pump rotor supply surface 6, and the compensation port 30 also cooperates. It is located on the opposite side of the inlet-transmission port 7-in the stator 3-and is connected to the inlet-transmission duct 8 by a radial-load compensation duct 31, to which the inlet-transmission duct is It is noted that the inlet-transfer port 7 cooperating with this is connected.

The surface area at which the compensation port 30 is exposed to pressure is almost the same as the surface area at which the cooperating inlet-transfer port 7 is exposed to the same pressure, so that the pump stator 3 and the pump rotor 4 are exposed to the same pressure by radial load. It is noted that no or little or no said pressure is produced in ). It is also noted that the compensating port 30 can be formed within a surface area that can face the rotor-side low pressure sealing surface 13 while the stator-side low pressure sealing surface 12 is defined.

In particular, as shown in Figs. 4, 14 and 15, the compensation port 30 is radial-the load compensation sealing plate 32 is received in the axial direction and / or tangentially with a small amount of space- It can be opened from the pump stator dispensing surface 5 via the load compensating groove 29, and the sealing plate 32 can be made of steel, for example.

15 shows that the radial-load compensation sealing plate 32 can pass in the thickness direction through a compensation opening 48 that arranges the radial-load compensation duct 31 in communication with the pump rotor supply surface 6 Shows that.

Compensation opening 48 can be composed of a hole of small cross-section that keeps the radial-load compensation sealing plate 32 as rigid as possible, the only function of the hole is the radial-load compensation duct to which the plate 32 is connected. It is noted that the pressure appearing at (31) is diffused to the pump rotor supply surface (6).

14 may include a plate support surface 49 on the side in which the radial-load compensating groove 29 is oriented perpendicular to the stator-side low pressure sealing surface 12, the support surface 49 being radial -Shows that the load compensating sealing plate 32 cooperates with the plate support shoulder 51 that it comprises.

14 may include a plate sealing surface 50 on the side in which the radial-load compensating groove 29 is oriented perpendicular to the stator-side low pressure sealing surface 12, the sealing surface 50 being radial -Further shows that the load compensating sealing plate 32 cooperates with the plate sealing shoulder 52 that it comprises.

14, the radial-load compensation sealing plate 32 may cooperate with the compensation-plate sealing lip 45, which may or may not be fixed to the plate 32, and the lip 45 Sealing is performed axially and/or radially and/or tangentially between the plate 32 and the radial-load compensating groove 29, while the lip 45 is in particular secured to the plate sealing shoulder 52. It can be seen that and/or may be a flexible metal blade positioned on, below or within a continuation of the shoulder 52.

The ring sealing lip 39 may consist of a radial-load compensating groove 29 and a flexible compensating sealing gasket 33 made of a flexible material that holds in contact with the radial-load compensating sealing plate 32 at the same time, For example, the flexible material may be a more rigid material, e.g. plastic, Teflon, steel, or rubber or elastomer reinforced with any stiffening material or structure known to those skilled in the art. It is noted.

According to a specific embodiment of the hydraulic pump distributor sealing ring 1 according to the invention shown in FIGS. 14 and 15, the radial-load compensating sealing plate 32 comprises at least one compensating peripheral contact boss 46 formed around it. ), and the boss 46 may have a compensating peripheral contact line 47 capable of contacting the pump rotor supply surface 6.

Advantageously, the compensating peripheral contact boss 46 and/or the cooperating rotor-side low pressure sealing surface 13 are coated with DLC (“diamond-like carbon”) and/or case-hardened and/or nitrided, or It is noted that it is possible to have any other coating that is hard and/or has a low coefficient of friction.

Further, the plate sealing surface 50 may be positioned approximately perpendicular to the compensation peripheral contact line 47, but due to a small offset between the surface 50 and the line 47, the radial-load compensation groove 29 ), the pressure present in the line 47 firmly presses the line 47 to the pump rotor feed side 6, creating a good seal between the line 47 and the feed side 6 while at the same time only small between the two sides. It creates a positive contact load, resulting in little frictional loss. This configuration is clearly presented in FIG. 15.

Figure 15 shows that the plate sealing surface 50 can be positioned approximately perpendicular to the compensation peripheral contact line 47, while the plate support surface 49 has a radial-load compensation groove 29 than the sealing surface 50. It further shows that it is further from the bottom of the compensating opening 48 and thus can be offset from the perpendicular to the compensating peripheral contact line 47.

3 to 10 and 12 and 13, the distribution opening 21 may include at least one connecting beam 56 connecting the circumferential-contact bosses 14 together, the The beam 56 defines at least one dispensing sub-opening 57 on either side of the length, the beam 56 being hydraulic fluid or any other between the port 7 and the supply orifice 9 facing it. It is possible to partially close the inlet-transfer port 7 aligned approximately axially or radially with the opening 21 without compromising the correct flow of fluid.

From Figs. 4 and 5 the anti-rotation means 36 is plugged into a stator anti-rotation pinhole 37 formed in the pump stator 3 on the one hand, and a continuous sealing ring 11 in the thickness direction on the other hand. It is noted that it may consist of at least one ring anti-rotation pin 35 inserted into the ring anti-rotation pinhole 38 passing through.

The ring anti-rotation pin 35 can be freely mounted in the ring anti-rotation pinhole 38 and can be tightly mounted in the stator anti-rotation pinhole 37 or vice versa, for example the rotation It is noted that the anti-pin 35 can be a metal cylinder or an elastic split pin.

How the invention works:

The manner in which the hydraulic pump distributor sealing ring 1 according to the present invention operates will be understood from the foregoing description in conjunction with FIGS. 1 to 15.

In order to illustrate the manner in which the ring 1 operates, the configuration shown in Figs. 2 to 15 is mainly selected, and as shown in Fig. 2, a hydraulic pump piston configured in a radial direction within the pump rotor 4 ( 53) and a hydraulic pump 44 equipped with a hydraulic pump cylinder 54. It should be emphasized that in this non-limiting exemplary embodiment, the pump 44 pumps oil.

According to this non-limiting exemplary embodiment of the sealing ring 1 according to the invention, the pump stator dispensing face 5 and the pump rotor feed face 6 are cylindrical. Thus, the ring 1 is also mainly cylindrical in shape. As clearly shown in FIGS. 8, 12 and 13, the hydraulic distributor 2 comprises two inlet-delivery ports 7 in this example. It comprises two dispensing openings 21 each radially aligned with a cooperating inlet-transfer port 7 as shown in FIGS. 3-8 and 12 and 13 with a continuous sealing ring 11. Justify what you do.

Fig. 10 is a partial cross-sectional view of the continuous sealing ring 11 shown in Fig. 8 on B-B. The cross section is taken at the dispensing opening 21, and more particularly, taken at the dispensing sub-opening 57. This cross section shows in particular an circumferential-contact boss 14 formed axially on each side of the opening 21. As shown in three dimensions in FIG. 9, the boss 14 has an circumferential contact line 15 designed to contact the rotor-side low pressure sealing surface 13 and create the best possible seal therewith.

In FIGS. 3 to 10 and 12 and 13 the dispensing opening 21 passes through a continuous sealing ring 11 in the thickness direction, is separated from each other in the circumferential direction by a compression-decompression track 24, and It can be seen that the four flat compression-decompression ducts 41 each open to the surface of this track through their own flat compression-release orifices 26. In this non-limiting embodiment, the circumferential-contact boss 14 formed axially on each side of the dispensing opening 21 is axially directed by a connecting beam 56 separating the dispensing sub-openings 57. Connected.

In particular in FIGS. 8, 12 and 13, each sector compression-decompression duct 41, together with the bottom of the ring groove 16, is a sectoral compression-decompression cell cavity 25 defining a closed and sealed volume. It is noted that it is connected to ). 11 shows how the fan-shaped compression-decompression cell cavities 25 are arranged and in which these cell cavities are connected to the surface of the compression-decompression track 24 by a cooperating fan-shaped compression-decompression duct 41. A partial cross-sectional view of the CC of the continuous sealing ring 11 shown in FIG. 8 showing the manner in detail.

5, 7, 8, 12 and 13, the fan-shaped compression-decompression cell cavity 25 is formed in the partitioned stiffening structure 40 incorporated in the stator-side ring surface 23, and the structure It can be clearly seen that 40 forms a compression-release sealing gasket 28 as detailed in FIG. 11, with a flexible material 43 overmolded over the structure.

4 and 5 are two compression-release sealing gaskets 28, according to a specific embodiment of the sealing ring 1 according to the invention contemplated herein to illustrate the manner in which the sealing ring operates. And four lateral sealing gaskets 27 are shown in particular made of one and the same continuous flexible material 43. For the sake of clarity, in the figure, the continuous material is shown separately from the continuous sealing ring 11. In practice, the continuous material may cover the stator-side ring surface 23 and the rigid partitioned structure 40 incorporated into the ring surface 23 by overmolding or bonding to the ring surface.

Figure 11 partially fills the flat compression-release cell cavity 25 so that the flexible material 43 pockets the cell cavity 25, and the stator-side ring face 23 and the ring groove 16 It is shown to produce the best possible seal between.

As can be seen in Figures 4 and 5, the continuous sealing ring 11 is pumped by means of a ring anti-rotation pin 35 passing through the ring 11 through a ring anti-rotation pinhole 38. It is held in a fixed angular position with respect to the stator (3)-in this case a simple metal cylinder-and the pin (35) is free in the hole (38), while the pin is blocked in the stator rotation-preventing pinhole (37). (blocked).

From Fig. 4 it is easy that a continuous sealing ring 11 consisting of a compression-release sealing gasket 28 and a lateral sealing gasket 27 can be mounted to the pump stator 3 by means of a ring mounting band 34. Can be inferred.

It is also noted from FIGS. 3 and 4 that the pump stator 3 has four radial-load compensation ports 30 positioned at an angle on each side of the inlet-transfer port 7. With this particular configuration of the hydraulic pump distributor sealing ring 1 according to the invention, each inlet-transfer port 7 has two radial-load compensation ports opposite this inlet-transfer port at the pump stator 3 ( 30), and the port 30 is the same inlet-transfer duct 8 as the inlet-transfer port 7 cooperating by a radial-load compensation duct 31, as clearly shown in FIG. It is noted that it is connected to.

It is noted that the total surface area of the two compensating ports 30 exposed to pressure is substantially equal to the surface area exposed to the same pressure by the cooperating inlet-transfer ports 7. Thus, the pressure present at the inlet-transfer port 7 creates a low value or even zero radial load on the pump stator 3 and the pump rotor 4.

In the manner of a continuous sealing ring 11 providing the best possible seal between the inlet-transfer port 7 and the pump rotor feed side 6, each radial-load compensation port 30 possesses the radial direction. It can be seen that the load compensating sealing plate 32 also provides the best possible seal between the port 30 and the feed face 6.

In this respect, the radial-load compensating sealing plate 32 in particular comprises a compensating-plate sealing lip 45 which provides a seal between the plate 32 and its cooperating radial-load compensating groove 29. do. Fig. 14, which is a three-dimensional cross-section through the plate 32, and Fig. 15, which is a schematic cross-section, shows, in the scenario considered here to illustrate how the sealing ring 1 according to the invention operates, the compensation-plate sealing lip 45 is a thin metal strip formed in the continuation of the plate sealing shoulder 52 and cooperating with a flexible compensation sealing gasket 33 made of a flexible material 43 such as rubber or elastomer, the flexible material 43 Potentially overmolded under the radial-load compensating sealing plate 32 and in the continuation of the shoulder 52, the flexible gasket 33 has a radial-load compensating groove 29 and compensating-plate sealing lip. It is shown to keep in contact with the lower part of 45 at the same time.

It can be emphasized here that the radial-load compensating sealing plate 32 is relatively flexible and easily deformable so that the pressure can press the compensating peripheral contact line 47 to the rotor-side low pressure sealing surface 13. have.

To do this, the plate sealing surface 50 represented by the radial-load compensating groove 29 is directly above the sealing surface 50 and the compensation peripheral contact line 47 contained by the radial-load compensating sealing plate 32 And is designed to be out of the vertical. This offset means that the cross-sectional area S1 to which pressure is applied is small, so that the radial load resulting from the cross-sectional area S1 is maintained at a small value. This achieves good sealing between the compensating peripheral contact line 47 and the rotor-side low pressure sealing surface 13, while at the same time creating little contact load in the contact between the line 47 and the surface 13, resulting in friction Little loss is caused.

In order to explain how the sealing ring 1 according to the invention operates in a suitable manner, it is noted that the continuous sealing ring 11 is of small thickness, and as a result, this sealing ring is also relatively flexible and easily deformable. It should be emphasized. Furthermore, it should also be emphasized that the ring groove 16 is sufficiently deep so that the continuous ring 11 can be eccentrically seated in the radial direction with respect to the groove 16 as shown in FIGS. 12 and 13. do. However, in practice, the deformation and eccentricity that the continuous sealing ring 11 receives is about several microns to several tens of microns, and Figs. 12 and 13 showing the deformation and eccentricity are the deformation and eccentricity. It should be understood that this is greatly exaggerated in order to be able to easily understand the influence of the sealing ring 1 according to the present invention.

Thus, when the radial-piston hydraulic pump 44 of the type shown in FIG. 2 is operating, the pump rotor 4 rotates around the pump stator 3. The pump stator dispensing face (5) is positioned towards the pump rotor feed face (6), while the inlet-delivery port (7) is roughly aligned with the nine feed orifices (9) and each orifice has its own feed duct (10). It is supplied to the hydraulic pump cylinder 54 through.

The pressure present in the inlet-outlet port 7 located at the highest height from FIGS. 12 and 13 and temporarily referred to as “upper port 7” is located below the lowest in FIGS. It is noted that it does not diffuse into the inlet-transfer port 7 referred to as "port 7", which due to the continuous sealing ring 11 and in particular due to the compression-decompression sealing gasket 28 causes the oil to be stator- This is because passing in the tangential direction between the side ring surface 23 and the bottom of the ring groove 16 is prevented.

As shown in Fig. 12, the upper port 7 has the highest pressure-for example 1000 bar-and the pressure appearing in the lower port 7 is lower pressure-for example 10 bar -, the further The high pressure applies a local radial thrust to the stator-side ring face 23 having a larger thrust magnitude than the thrust applied to the face 23 by the lower pressure appearing at the lower port 7.

As a result of this thrust imbalance, the continuous sealing ring 11 deforms and is firmly pressed against the rotor-side low pressure sealing surface 13 in the region of the upper port 7, while the continuous ring 11 In the region of (7), a distance of several microns or tens of microns is maintained in the direction away from the surface (13).

As shown in Fig. 10 , since pressure is applied to the stator-side ring surface 23 only over a small cross-sectional area S1 of the surface 23, the load corresponding to the radial thrust is maintained at a small value. It is noted. The cross-sectional area S1 was determined at the design stage of the continuous sealing ring 11, as a result of which the two ring sealing faces 18 and the ring groove 16 must be provided on both sides of the continuous sealing ring 11 , A fine axial offset is created between the vertical line and the circumferential contact line 15 formed directly above each of the sealing faces 18 on the rotor-side ring face 22. In this regard, as well shown in Fig. 10, the circumferential contact line 15 is located more axially toward the inside of the continuous sealing ring 11 than the cooperating ring sealing surface 18, so that the stator side ring surface It is understood to be shown in (23) to generate the desired local radial thrust.

Thus, the axial offset provided between the two ring sealing faces 18 and the circumferential contact line 15 and the vertical line and determining the cross-sectional area S1 is the pressure present in the ring groove 16 and the line 15 It means to effectively pressurize the pump rotor supply surface (6) firmly. This tends to create a seal between the line 15 and the supply surface 6 and at the same time generate little contact load at the contact between the line 15 and the surface 6, resulting in little frictional loss. There is this. The contact pressure at the contact between the line 15 and the pump rotor feed side 6 essentially depends on the contact width made by the side 6 and the line 15, the width also being a continuous seal It is understood that it depends on the elaborate choices made in the design of the ring 11.

The sealing between the ring sealing face 18 represented by the ring groove 16 from FIG. 10 and the ring sealing shoulder 20 represented by the continuous sealing ring 11, on the one hand, is, on the one hand,-due to the elasticity-the ring sealing face It can be seen that this is achieved by a ring sealing lip 39 that keeps contact with 18 and, on the other hand, by a lateral sealing gasket 27. Thus, by means of the lip 39 the sealing material 27 is not extruded even under very high pressure-for example 2000 bar-while the gasket provides a perfect sealing.

Due to the deformation of the continuous sealing ring 11 in the region of the lower port 7 in FIG. 12, the rotor-side ring face 22 is several microns away from the rotor-side low pressure sealing surface 13. Or it can be seen that it is kept at a distance of several tens of microns. The circumferential contact line 15 in the angular sector occupied by the lower port 7 does not press firmly against the pump rotor feed face 6 and thus does not provide a seal.

As a result, the seal between the lower port 7 and the pump rotor supply surface 6 is the number of microns or numbers remaining between the stator-side low pressure sealing surface 12 and the rotor-side low pressure sealing surface 13. It is only achieved through a small gap of ten microns. The small spacing is achieved in particular by machining the surfaces 12, 13 with high precision, while the leakage flow passing between the surfaces is the low pressure that appears in the lower port 7-10 bar in the example chosen here- Keeps small due to The energy losses associated with the leakage flow can thus be neglected.

13 shows the deformation of the continuous sealing ring 11 when the upper port 7 has a lower pressure, e.g. 10 bar, while the lower port 7 is in operation with the continuous sealing ring 11 It is understood that the mode has an upper pressure that remains unchanged, for example 1000 bar.

After the orifice 9 leaves the angular sector occupied by the upper port 7 there is a flat compression-decompression cell cavity 25 providing good sealing between the feed orifice 9 and the compression-decompression track 24. In particular, it is presented in FIGS. 8, 12 and 13. The cell cavity 25 can also be viewed in three dimensions in FIG. 5 and in a schematic cross-sectional view in FIG. 11.

In fact, according to the example considered here to illustrate how the sealing ring 1 according to the invention operates, the hydraulic pump cylinder 54 introduces oil at 10 bar from the lower port 7 and draws this oil from the upper side. In port 7 it transmits at 1000 bar. Thus, the hydraulic pump cylinder 54 connected to the feed orifice 9 when any feed orifice 9 transitions from the upper port 7 through the compression-decompression track 24 to the lower port 7 The oil contained in the and supply duct 10 needs to be continuously pressurized (expanded). During this expansion, when the oil is compressed-the oil is compressible-the energy stored by the oil can be mechanically restored by the hydraulic pump 44. This function is necessary to impart excellent energy efficiency to the pump 44.

-Due to the rotation of the pump rotor 4-when the feed orifice 9 leaves the upper port 7 and begins to follow the compression-decompression track 24, the upper port ( The orifice 9 arranged 7) in communication with the corresponding hydraulic pump cylinder 54 is closed by the track 24. When the mechanism of the hydraulic pump 44 increases the volume of the hydraulic pump cylinder 54, the oil contained therein expands, and the energy stored while compressing the oil is transferred to the pump 44 in a mechanical form. Start to do it.

In the first sector compression-decompression orifice 26 connecting the track 24 with a closed and sealed volume defined by a sector compression-decompression cell cavity 25 located immediately below the sector orifice 26. The feed orifice continues to start along the compression-decompression track 24 until the feed orifice 9 is strung.

Thus, this is a return to the configuration shown in FIG. 11 and this is the immediate effect of diffusing the pressure present in the hydraulic pump cylinder 54 into the closed and sealed volume with a radial cross section significantly larger than the cross section of the supply orifice 9. Provides. The differential radial cross-sectional area S2 resulting therefrom is shown in FIG. 11. It is understood that S2 was determined during the design phase of the continuous sealing ring 11 on the basis of a compromise between sealing effect and friction loss.

Due to the differential radial cross-sectional area S2 , the compression-decompression track 24 is firmly pressed against the rotor-side low-pressure sealing surface 13 on which the supply orifice 9 is opened by pressure. This constitutes a seal around the feed orifice 9 between the compression-decompression track 24 and the rotor-side low pressure sealing surface 13, and a load that presses the track 24 firmly against the surface 13. Is higher than the pressure present in the hydraulic pump cylinder 54.

Thus, as the supply orifice 9 progresses gradually along the compression-decompression track 24, the volume of the hydraulic pump cylinder 54 increases without increasing the amount of oil contained in the cylinder 54. It is understood to be. This is done by the mechanism of the hydraulic pump 44. As a result, the oil actually expands and the previously stored energy during compression is restored.

When the feed orifice 9 then comes to the flat compression-decompression orifice 26, the same principle occurs as the compression-decompression track 24 is firmly pressed against the rotor-side low pressure sealing surface 13. Only takes place at a lower pressure and continues to do so until the feed orifice 9 reaches the lower port 7.

According to a non-limiting embodiment of the sealing ring 1 according to the invention shown in FIGS. 8, 12 and 13, there is an angular offset between the two flat compression-release orifices 26 and the diameter of the orifices. It is noted that one and the same feed orifices 9 are calculated in such a way that they do not lie simultaneously towards the two said sector orifices 26. In order to increase the number of flat compression-decompression orifices 26, thereby increasing the number of flat compression-decompression orifices 26, axially, which can be separated in a staggered configuration over at least two rows. It is understood that it is possible to provide supply orifices 9 that are oblong, and this configuration can potentially also be applied to the sector compression-decompression orifice 26 as a non-limiting example.

Furthermore, in particular, the geometry of the fan-shaped compression-decompression cell cavity 25 shown in FIG. 5 is non-limiting and may be different for each cell cavity 25. In practice, the selection of the geometry is, on the one hand, in order to create the best possible seal between the compression-decompression track 24 and the rotor-side low pressure sealing surface 13, on the other hand, the track 24 In order to create the smallest possible amount of friction between the and the surface 13, it needs to be known by demand.

The cross-sectional area S1 resulting from the axial offset of the ring sealing surface 18 from the circumferential contact line 15 and the vertical can be seen in Fig. 11, and the compression-decompression track 24 is a continuous seal. The offset is provided in the angular section of the continuous sealing ring 11 occupied by the corresponding compression-decompression track as provided on the remaining periphery of the ring 11. Sealing at the axial margin of the track 24 can be improved by the cross-sectional area S1.

It is to be understood that the above description is provided by way of example only, and does not limit the field of the present invention in any way that does not exceed the limit when the details of the described embodiments are replaced with any other equivalents.

Claims (26)

A sealing ring for a hydraulic pump distributor (1) designed for a hydraulic distributor (2) that the hydraulic pump (44) may contain, the distributor (2) being at least one fixed to the pump stator (3). It comprises a pump stator distribution face (5), the distribution face (5) having a stator-side low pressure sealing surface (12), from the stator-side low pressure sealing surface to the pump stator (3). At least two inlet-transfer ports 7 formed are opened, each inlet-transmission port being specified in each inlet-transmission port and communicating with at least one inlet-transmission duct 8 formed in the stator 3, The distributor 2 further comprises at least one pump rotor feed face 6 fixed to the pump rotor 4, the feed face 6 being a rotor-side low pressure sealing surface ( 13), and at least one orifice 9 in communication with the supply duct 10 formed in the rotor 4 from the rotor-side low pressure sealing surface is opened, while the stator-side The low pressure sealing surface (12) is positioned facing the rotor-side low pressure sealing surface (13) so that the feed orifice (9) is at least once per revolution of the pump rotor (4) the two inlet-delivery ports (7). ) Facing one or the other alternately, the sealing ring,

At least one received with a small amount of spacing in the axial and/or radial direction in a ring groove 16 formed in the pump stator 3 within the surface area defined by the stator-side low pressure sealing surface 12 As a continuous sealing ring 11 of, the ring 11 comprises a stator-side ring face 23 received in the ring groove 16, the stator-side low pressure sealing surface 12 and With the rotor-side ring face 22 at the same level, the inlet-transfer port 7 opens through the groove 16 to the sealing surface 12, the ring 11 At least one is wider in the axial or radial direction than the port 7 to cover the port, and is aligned with the port in an axial or radial direction, and passes through the continuous sealing ring 11 in the thickness direction. A dispensing opening (21), the opening (21) allowing one of the two inlet-transfer ports (7) to communicate with the supply orifice (9) when the supply orifice faces the port (7). The at least one continuous sealing ring (11), which can be arranged;

At least one circumferential-contact boss (14) formed axially or radially on each side of the dispensing opening (21), the boss (14) being the rotor-side low pressure sealing surface (13). ) Said at least one circumferential-contact boss (14) having an circumferential contact line (15) capable of contacting;

At least one compression-decompression track (24) formed in a specific angular sector of the rotor-side ring face (22), the angular sector being the portion of the face (22) in which the radial distribution opening (21) is located The at least one compression-decompression track (24), located outside of the at least one;

At least one ring sealing lip that may or may not be fixed to the continuous sealing ring 11 and performs sealing in an axial or radial direction between the ring 11 and the ring groove 16 lip) 39;

Sealing between the stator-side ring face 23 and the bottom and/or axial or radial side of the ring groove 16, defined by an angular sector in which the compression-decompression track 24 is formed. At least one compression-release sealing gasket 28 for performing sealing in the angular region;

Sealing ring for a hydraulic pump distributor, characterized in that it comprises anti-rotation means (36) for holding the continuous sealing ring (11) in a fixed angular position with respect to the pump stator (3). The method of claim 1, wherein the ring groove (16) comprises a ring bearing face (17) on a side oriented perpendicular to the stator-side low pressure sealing surface (12), the ring bearing face ( 17) A sealing ring for a hydraulic pump distributor, characterized in that it cooperates with a ring bearing shoulder (19) included in the continuous sealing ring (11). The method of claim 2, wherein the ring groove (16) comprises a ring sealing surface (18) on a side oriented perpendicular to the stator-side low pressure sealing surface (12), the ring sealing surface (18) being the continuous Sealing ring for a hydraulic pump distributor, characterized in that it cooperates with a ring sealing shoulder (20), which is comprised of a special sealing ring (11). 4. Sealing ring according to claim 3, characterized in that the ring sealing lip (39) is a flexible metal blade fixed to the ring sealing shoulder (20). 4. Sealing ring according to claim 3, characterized in that the ring sealing lip (39) is located on, below, or within a continuation of the ring sealing shoulder (20). The method of claim 1, wherein the ring sealing lip (39) consists of a lateral sealing gasket (27) made of a flexible material that maintains contact simultaneously with the ring groove (16) and the stator-side ring face (23). Sealing rings for hydraulic pump distributors, characterized in that. The method of claim 1, wherein the compression-decompression sealing gasket (28) is closed, together with the stator-side ring face (23) and the bottom and/or axial or radial side of the ring groove (16) Sealing ring for a hydraulic pump distributor, characterized in that it has at least one flat compression-release cell cavity (25) defining a sealed volume. The method of claim 7, wherein the compression-decompression sealing gasket (28) comprises a stiffening cellular structure (40) in which the fan-shaped compression-decompression cell cavity (25) is formed, and the compartmental structure 40 is made of a rigid material 42 and can be held in place with respect to the continuous sealing ring 11, either directly or indirectly using the anti-rotation means 36, while The material 42 is a flexible material capable of contacting the stator-side ring face 23 on the one hand and/or the bottom and/or axial or radial sides of the ring groove 16 on the other hand. Sealing ring for a hydraulic pump distributor, characterized in that it can be completely or partially coated with the material (43). 9. A hydraulic pump distributor according to claim 8, characterized in that the rigid partitioned structure (40) is incorporated into the stator-side ring face (23) and is made of the same material as the continuous sealing ring (11). Sealing ring. 8. The method of claim 7, wherein the compression-decompression track (24) has at least one flat compression-decompression orifice (26) in which the flat compression-decompression duct (41) is open, the duct being the fan compression -Connecting the closed and sealed volume defined by the decompression cell cavity 25 with the rotor-side ring face 22, the sector orifice 26, the feed orifice 9 being the pump rotor (4) is positioned in such a way that it faces the fan-shaped orifice 26 once per revolution, and the fan-shaped orifice 26 allows the supply duct 10 to be sealed through the fan-shaped compression-decompression duct 41. Sealing ring for a hydraulic pump distributor, characterized in that it connects to the volume. 7. Sealing ring according to claim 6, characterized in that the lateral sealing gasket (27) and the compression-release sealing gasket (28) form only one single piece. 4. Sealing ring according to claim 3, characterized in that the ring sealing surface (18) is positioned vertically with the circumferential contact line (15). 4. The ring groove (16) according to claim 3, wherein the ring sealing surface (18) is located perpendicular to the circumferential contact line (15), while the ring support surface (17) is greater than the ring sealing surface (18). ) And further from the bottom of the dispensing opening (21) and offset from the circumferential contact line (15) and perpendicular to the seal ring. Hydraulic pressure 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 ring mounting band (34) that fits snugly around the pump stator (3). Sealing ring for pump distributor. The method according to claim 1, wherein the pump stator distribution surface (5) and the pump rotor supply surface (6) are cylindrical, while at least one of the inlet-transfer ports (7) is formed in the pump stator (3). Cooperating with at least one radial-load compensation port 30, the port 30 being opened from the pump stator distribution surface 5, facing the pump rotor supply surface 6, and the compensation port ( 30) is also located on the opposite side of the cooperating inlet-transmission port 7-in the stator 3-and is connected to the inlet-transmission duct 8 by a radial-load compensation duct 31 , A sealing ring for a hydraulic pump distributor, characterized in that the inlet-delivery port (7) cooperating therewith is connected to the inlet-delivery duct. 16. The method of claim 15, wherein the compensating port (30) is provided through a radial-load compensating groove (29) in which the radial-load compensating sealing plate (32) is received at a small amount of space in the axial and/or tangential direction Sealing ring for a hydraulic pump distributor, characterized in that it opens from the pump stator distribution surface (5). 17. The thickness of claim 16, wherein the radial-load compensation sealing plate (32) has a thickness compensation opening (48) that arranges the radial-load compensation duct (31) in communication with the pump rotor supply surface (6). Sealing ring for a hydraulic pump distributor, characterized in that penetrating in the direction. 18. The method of claim 17, wherein the radial-load compensating groove (29) comprises a plate support surface (49) on a side oriented perpendicular to the stator-side low pressure sealing surface (12), the support surface (49) Sealing ring for a hydraulic pump distributor, characterized in that it cooperates with a plate support shoulder (51) included in the radial-load compensating sealing plate (32). 19. The method of claim 18, wherein the radial-load compensating groove (29) comprises a plate sealing surface (50) on a side oriented perpendicular to the stator-side low pressure sealing surface (12), the sealing surface (50) Sealing ring for a hydraulic pump distributor, characterized in that it cooperates with a plate sealing shoulder (52) included in the radial-load compensating sealing plate (32). The method of claim 16, wherein the radial-load compensation sealing plate (32) cooperates with a compensation-plate sealing lip (45) which may or may not be fixed to the plate (32), and the lip (45) is Sealing ring for a hydraulic pump distributor, characterized in that sealing is carried out in an axial and/or radial and/or tangential direction between the plate (32) and the radial-load compensating groove (29). 21. A flexible compensation sealing gasket according to claim 20, wherein said ring sealing lip (39) is made of a flexible material that maintains contact simultaneously with said radial-load compensating groove (29) and said radial-load compensating sealing plate (32). Sealing ring for a hydraulic pump distributor, characterized in that consisting of (33). 20. The method of claim 19, wherein the radial-load compensating sealing plate (32) comprises at least one compensating peripheral contact boss (46) formed around, and the boss (46) comprises the pump rotor supply surface (6) Sealing ring for a hydraulic pump distributor, characterized in that it has a compensating peripheral contact line (47) capable of contacting with. 23. Sealing ring according to claim 22, characterized in that the plate sealing surface (50) is positioned vertically with the compensating peripheral contact line (47). 23. The method of claim 22, wherein the plate sealing surface (50) is positioned vertically with the compensating peripheral contact line (47), while the plate support surface (49) is more radially-loaded than the plate sealing surface (50). Sealing ring for a hydraulic pump distributor, characterized in that it is further from the compensation groove (29) and the bottom of the compensation opening (48) and is offset from the compensation peripheral contact line (47) and vertical. The method of claim 1, wherein the distribution opening (21) comprises at least one connecting beam (56) connecting the circumferential-contact bosses (14) together, wherein the beam (56) is at least one on both sides of the length. Sealing ring for a hydraulic pump distributor, characterized in that it defines a dispensing sub-opening (57) of. The method of claim 1, wherein the rotation-preventing means (36) is plugged into a stator rotation-proofing pin hole (37) formed in the pump stator (3) on the one hand, and in the thickness direction on the other hand. A hydraulic pump dispenser comprising at least one ring rotation-proofing pin (35) inserted into the ring rotation-preventing pinhole (38) passing through the continuous sealing ring (11). For sealing rings.

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