Abstract: A sealing device is arranged in a groove between a first machine component and a second machine component. If the sealing device, comprising the sealing ring and the biasing element, is subjected to a hydraulic pressure from the high pressure side and/or should an axial motion of a machine component take place, the sealing ring pivots towards the low pressure side in such a fashion that an angle .alpha. is reduced and an angle .beta. is increased. Through this pivoting effect a sealing edge is formed. Thereby a wedge-shaped gap forms between the peripheral surface and the surface of the sealing ring lying across therefrom, the gap being open towards the low pressure side.

Abstract: A sealing means and sealing valve 10 for container openings is formed from a housing 11, 12 in which a seal 13 is arranged. The seal 13 closes a gap between the housing portions 11, 12. The housing portions 11, 12 exhibit bores 14, 14' and 15 through which a fluid can flow through the housing portions 11, 12, as long as the seal 13 opens up a gap. The seal 13 exhibits a sealing bead 20, which lies across from the spring-bead 22, 23, 24.

Abstract: A sealing arrangement for sealing a gap (11) between two concentric machine elements which can relatively move with respect to each other, the first machine element (3) having a smooth contact surface (5) and the second machine element (4) having a profiled section (6) which faces the contact surface (5) of the first machine element (3), accommodates a sealing ring (2). The profiled section (6) is bounded by a first flank (8) and a second flank (9). The sealing ring has a curved peripheral surface (7) and a radial surface (13), either of which may be completely exposed to the high pressure side. A sealing edge (10) of the sealing ring (2) is formed by the line of intersection of a conical surface (14) and the curved peripheral surface (7). The conical surface (14) merges into the radial surface (13).

Abstract: For sealing between two opposed surfaces of two machine elements (1, 2) a combination seal is provided to be fitted into an open groove (3) in one of the machine elements (2). The seal comprises an electomeric expansion ring (4, 5) at the bottom of the groove (3), an intermediate ring (6) made of a viscous-elastic material, e.g. PTFE and having a sealing surface (6b) to contact the mating machine element (2), and an elastomeric outer ring (8) fitted into a separate groove (7) in the sealing surface (6b) of the intermediate ring.

Abstract: In the case of conventional seal arrangements comprising a sealing ring (5) consisting of a tough-elastic plastic material and a rubber-elastic stressing ring (6), where one edge (53) of the sealing ring (5) is in contact with the circumference of a rod (1), the pressing force encountered at the edge is dependent, to a very high degree, on the fluid pressure because the fluid pressure acts upon the circumferential surface of the sealing ring (5) either directly or via the rubber-elastic stressing ring (6). The pressing force, which consequently rises considerably in the presence of high fluid pressure, leads to high frictional forces at the sealing edge (53), which increase even further in the course of operating time.

Abstract: A structure for sealing the gap between two concentric machine parts which are arranged to move relative to each other comprises a sealing ring which is made of a tough-elastic plastic material and which bears upon the contact surface of the second machine part by sealing edges arranged near its ends, the surface of the sealing ring facing the bottom of the groove being provided with an annular groove of substantially trapezoidal cross-section. The space bettween the sealing edges is connected with the bottom of the annular groove by one radial bore. A stressing ring of a rubber-elastic material is arranged in the annular groove, between the sealing ring and the bottom of the groove, which loads the sealing ring in the radial direction and which has an axial cross sectional length smaller than that of the sealing ring. The stressing ring is perfectly fixed by this arrangement relative to the sealing ring.

Abstract: A sealing ring structure comprises a sealing ring provided with sealing edges which are arranged adjacent its ends and are in contact with a second machine part, and a stressing ring embracing the sealing ring, loading it in the radial direction and being fitted into an annular recess in the sealing ring. The tightness of such a structure at high fluid pressures is improved by the fact that the stressing ring is accommodated in a trapezoidal annular groove in the sealing ring which communicates with the space between the sealing edges by radial bores. The stressing ring, which is fixed in the groove of the sealing ring, is shifted in operation in response to the prevailing pressures whereby the sealing edge on the high-pressure side is relieved from pressure while the contact pressure exerted upon the sealing edge on the low-pressure side is simultaneously increased.

Abstract: A sealing ring structure comprising a sealing ring made of a tough-elastic plastic material and a stressing ring made of a rubber-elastic material has the outer surface of the sealing ring designed as a conical surface and arranged in such a manner, relative to a groove accommodating the sealing ring and the stressing ring, that the stressing ring comes to occupy a position between this conical surface and the flank of the groove on the low-pressure side. The pressure fluid, which penetrates to the outside of the sealing ring through pressure-relieving grooves, urges the stressing ring into the wedge-shaped gap between the outer surface of the sealing ring and the end face of the groove. Consequently, the sealing ring is wedged in the groove and prevented from rotating relative to the machine part comprising the groove and to the stressing ring.

Abstract: In a sealing and wiper arrangement, a sealing ring (5), which may also serve a wiper function, and a stressing ring arrangement (6) are accommodated in a groove (4) of a first machine part (1). The stressing ring arrangement (6) is positioned between the sealing ring (5) and the base of the groove and urges the sealing ring against the surface of a second machine part (2) which is capable of a movement relative to the first machine part (1), in a direction perpendicular to the direction of the groove (4). The sealing ring (5) is in contact with a second machine part (2) by a wiper web (8) and an edge (11) provided on its high-pressure side. The edges (10, 11) provided on the sealing ring (5) are loaded independently of each other. This is achieved by giving the stressing ring arrangement (6) the form of two separate portions of a stressing ring. In one embodiment two completely separate stressing rings (61, 62) are provided. In another embodiment a Quad-ring (40) is provided.

Abstract: An arrangement for sealing that point at which the axially movable rod of a hydraulic device passes through its housing wall, comprises a sealing ring consisting of a tough-elastic plastic material or a harder elastomeric material and a stressing ring consisting of a softer elastomeric material, the two rings being accommodated jointly in a groove in the housing wall in such a manner that the sealing ring projecting from the groove is in contact with the axially moving rod, while the stressing ring seals the sealing ring against the circumferential face of the groove. The sealing ring is provided, on its inner surface facing the rod, with two axially offset annular sealing edges. The annular space between these two sealing edges is connected with the outer surface of the sealing ring by a channel. The channel opens at a point where it is covered by the stressing ring and which is located near the high-pressure end of the common contact face of the sealing ring and the stressing ring.

Abstract: In a sealing ring structure comprising a sealing ring (1) made of a tough-elastic plastic material and a stressing ring (11) made of a rubber-elastic material, the sealing ring (1) is provided with an annular recess (2) on its sealing surface which rests against the other machine component (14). The stressing ring (11) is arranged in the sealing ring (1) approximately centrically relative to the said recess so that the force of the stressing ring (11) is distributed over the two end portions of the sealing ring (1) defining the recess (2). Any dimensional deviations resulting from tolerances or temperature changes are compensated by smaller or greater deflection of the central portion of the sealing ring (1), without notable changes to the surface pressures encountered between the sealing ring (1) and the sealing surface (15) which are essential for the proper operation.

Abstract: In a double wiper arrangement, a wiper ring (5) and a stressing ring (6) are arranged in a groove (4) of a width which is only little larger than the width of the wiper ring (5). The stressing ring (6) loads the wiper ring (5) through a shoulder and an inclined circumferential surface (14) in such a manner that the wiper ring (5) is retained in contact with the flank (17) of the groove (4) on the high-pressure end and that a contact pressure is produced along a flat surface portion (7) which pressure diminishes at least nearly linearly along the said flat surface portion, starting from its inner end, but which is still defined at the outer end thereof.

Abstract: In packings for hydraulic pistons or piston rods with a packing ring comprised of a tough elastic synthetic material as the contact packing between a stationary machine part comprising an annular groove and a moving machine part comprising an initial slope and of a rubber clamping ring clamping the packing ring radially and providing a sealing action with respect to the annular groove in the stationary machine part, an annular surface is located between the end face of a step at the high pressure side and a conical surface adjoining the latter on the low pressure side, which annular surface forms an obtuse angle with the conical surface of such a value that when the packing travels in over the initial slope the resultant F.sub.res of the normal force F.sub.N and of the frictional force F.sub.R halves the sealing edge angle. When using conventional materials and conventional angles for the conical surface and the inlet slope, a value of 45.degree.

Abstract: A Sealing Ring Structure useful for pistons and piston rods has a sealing section and a stressing section for pressing a contact surface of the sealing section into engagement with a moving surface to be sealed. The sealing and stressing sections may be separate rings or may be layers of different material in an integral multilayer laminate. The contact surface of the sealing section is of small axial length compared with the overall length of the structure and is located between a recess in the sealing section on the high pressure side of the structure and an inclined surface of the sealing section which defines a wedge-like gap between the structure and the moving surface to be sealed which gap diverges towards the low pressure end of the structure.