Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
  • F16K41/00—Spindle sealings
  • F16K41/02—Spindle sealings with stuffing-box ; Sealing rings
  • F16K41/023—Spindle sealings with stuffing-box ; Sealing rings for spindles which only rotate, i.e. non-rising spindles
  • F16K41/026—Spindle sealings with stuffing-box ; Sealing rings for spindles which only rotate, i.e. non-rising spindles for rotating valves
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
  • F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
  • F16K5/06—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary with plugs having spherical surfaces; Packings therefor
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
  • F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
  • F16K5/06—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary with plugs having spherical surfaces; Packings therefor
  • F16K5/0663—Packings
  • F16K5/0694—Spindle sealings

Definitions

• the present invention relates to a sealing ring made of deformable material with a radially inwardly facing inner sealing surface and a radially outwardly facing outer sealing surface and a sealing system with a first component with a bore, a second component which is arranged in the bore, and a sealing ring of the type mentioned.
• Seals for sealing annular gaps are required in technology, in particular in mechanical engineering, in a wide variety of geometrical and usage forms. A wide variety of designs of such seals - also known as prepared standard components, even standardized - are consequently known in the prior art.
• One of the simplest forms of known annular seals is a rubber O-ring.
• the so-called shaft sealing ring for example, a sealing element with a metal ring as the outer seat and a sealing lip made of rubber pointing radially inwards, is much more complicated in construction.
• Shaft sealing rings of this type are used, for example, to seal a transmission housing from which a rotating shaft is guided.
• the metal ring sits in the bore of the housing through which the shaft is guided, and the sealing lip bears against a circular cylindrical surface of the shaft that is as smooth-walled as possible.
• the contact area between the sealing lip and the shaft surface is reduced to a ring line around the shaft - in that the sealing lip tapers radially inwards to a geometrically sharp edge.
• This configuration allows high speeds of the shaft, for example gear oil, which is located inside the housing and which exits the housing. should be prevented by the seal forms a lubricating film under the sealing lip.
• Dynamic pressure As is known, conditions in the area of the contact surface ensure that the oil does not penetrate outside under the sealing lip.
• the plain bearings are regularly in the immediate vicinity of the seal. Since the plain bearings are often exposed to wear due to the relative movement of the two components, direct contact between the two components can nevertheless occur after a certain operating time, which makes the relative movement of the two components with respect to one another more difficult.
• felt rings are known for sealing annular gaps around a component which is not only rotating but also translationally moved through the bore.
• the effect of known sealing rings is often not sufficient, so that undesirable leakage can occur.
• the invention has for its object to provide a seal and a sealing system, the sealing effect is improved.
• a sealing ring made of deformable, preferably elastically deformable material, e.g. made of a polymer, two sealing surfaces, one of which faces radially inwards and one radially outwards. These sealing surfaces are then usually, e.g. in a suitably designed sealing groove in the area of the gap against complementary sealing surfaces of the components.
• the sealing ring is characterized by at least one pressure surface which is designed as a wall of a cavity in the sealing ring.
• the at least one pressure surface is essentially at least radially opposite at least one of the sealing surfaces, so that a fluid which is in the cavity under pressure against the pressure surface presses the at least one sealing surface outwards and therefore, with suitable installation, against a complementary sealing surface of a component.
• This increased pressure of a sealing surface of the sealing ring according to the invention improves the sealing effect considerably. This is particularly advantageous in the case of annular gaps which are to be sealed against a fluid under pressure.
• the pressure of the fluid can be used according to the invention by installing the sealing ring according to the invention in such a way that a fluid opening leading out of the cavity allows the fluid to penetrate into the cavity and there its pressure on the pressure surface and thereby exerted on the radially opposite sealing surface.
• the cavity in the sealing ring is preferably designed in the form of a groove which is formed in an axial outer surface of the sealing ring on the circumference of the sealing ring.
• the radial boundary surfaces of the groove then lie, particularly in the case of a circular-cylindrical tubular seal ring, its two seal surfaces (one pointing outwards and one pointing inwards) and press when pressure is applied. supply of the groove by a fluid under pressure, the sealing surfaces from the cross section of the sealing ring to the outside, ie radially outwards or radially inwards.
• the sealing system comprises a first component with a bore, a second component which is arranged in the bore and a sealing ring for sealing the gap between the first and the second component against an at least temporarily pressurized fluid.
• a roller bearing for receiving axial forces acting on the second component is further arranged between the two components between the first and the second component.
• the roller bearing can either be arranged on the sealed side in the area of the gap between the two components or on the non-sealed side of this gap. In the latter case, the materials of the rolling bearing components must be selected so that there is resistance to the fluid.
• roller bearing absorbs the forces absorbed by the slide bearing in the prior art and can therefore substantially relieve the load or even make it unnecessary.
• the wear of the plain bearing is greatly reduced or avoided entirely.
• the rolling bearing itself is almost wear-free even under high loads due to high forces and long relative high speeds that occur between the two components.
• a sealing system is particularly advantageous in which a slide bearing, in particular an axial-radial slide bearing, is combined with a roller bearing on the sealed side on the pressure side of the seal. This results in a particularly advantageous sealing and absorption of the forces between the two components.
• the sealing system is developed in an advantageous manner in that an axial deep groove ball bearing is selected as the rolling bearing.
• the axial deep groove ball bearing is particularly suitable for regularly cramped conditions because it has a very compact shape.
• it is designed to absorb the forces that often occur predominantly in the longitudinal direction of the bore in the first component, that is to say the axial forces, between the first and second components.
• a further advantageous embodiment of the sealing system according to the invention comprises a first component with a bore, a second component which is arranged in the bore and a sealing ring of the type described above, which seals the gap between the two components against an at least temporarily pressurized fluid seals.
• the sealing ring according to the invention can be combined with a roller bearing, as described above. In this way, a particularly long-lasting and secure sealing of the gap between the first and second component is achieved.
• a simple and effective sealing is achieved with the sealing system according to the invention, in particular in the case of cylindrical jacket-shaped sealing gaps.
• sealing ring and sealing system for sealing the gap between an actuating pin of a ball valve and the housing of a ball valve.
• FIG. 1 shows a partially sectioned side view of an embodiment of the sealing system according to the invention
• Figure 2 is a partially sectioned front view of a second embodiment of the sealing system according to the invention.
• Figure 3 is a partially sectioned front view of a third embodiment of the sealing system according to the invention.
• Figure 1 shows a housing 2 with a bore 4, in which an actuating pin of a ball valve (not shown) is arranged.
• the gap between the actuating pin 6 and the housing 2 is sealed by a sealing ring 8 with an outer contour shaped like a circular cylinder.
• the sealing ring 8 has an inwardly facing inner sealing surface 10 and an outwardly facing outer sealing surface 12.
• the radially inwardly facing sealing surface 10 bears against a radially outwardly facing surface of the circular cylindrical actuating pin 6 and the radially outwardly facing sealing surface 12 against one radially inwardly facing surface 14 of a groove 16 in the housing 2, in which the sealing ring 8 is inserted.
• a cavity 14 is formed in the sealing ring 8.
• the cavity 14 is a groove in an axial outer surface 16 of the sealing ring 8.
• the groove 14 opens in the direction of a fluid 18 which is under pressure in the housing 2 and which passes through the gap 4 between the actuating pin 6 and the wall of the bore 4 penetrates to the sealing ring 8 and pressurizes the cavity 14 there.
• the cavity 14 has a wall 20 which is parabolic in cross-section.
• the wall 20 is radially opposite one of the sealing surfaces 10, 12, each with a "leg" of the parabola, and presses this, acted upon by the pressure of the fluid 18, against the complementary ones Sealing surfaces of the housing 2 and the actuating pin 6.
• the section 6a is positively connected to the ball (not shown) of the ball valve, which is arranged in the cavity 30 in the housing 2.
• the section 6b has a cylindrical surface 7, against which the sealing surface 10 of the seal 8 seals.
• a shoulder is formed which has a surface 40 lying perpendicular to the longitudinal direction of the actuating pin 6.
• a shoulder is also formed, which has a surface 41 lying parallel to surface 40.
• the surface 40 of the first shoulder is in contact with an annular slide bearing 50 which is arranged in the bore 4.
• the slide bearing 50 is designed as an axial-radial slide bearing and is supported in the area of a shoulder of the bore 4 on the cylindrical outer surface and the annular end face of this shoulder of the bore 4.
• the axial-radial slide bearing is designed to absorb axial forces which are directed radially outward in the flow channel 19 containing the fluid 18.
• the surface 40 of the first shoulder of the actuating pin faces away from the flow channel 19 of the fluid 18 and the annular end face of the shoulder of the bore 4 faces the flow channel 19.
• a first bearing shell 61 of an axial deep groove ball bearing 60 is supported on the surface 41 of the second shoulder of the actuating pin 6.
• the surface 41 faces away from the flow channel 19.
• a second bearing shell 62 of the axial deep groove ball bearing is supported on a housing section 3 of the housing 2.
• the balls of the deep groove ball bearing 60 are arranged between the first and second bearing shells 61, 62.
• the upper end portion of the section 6c of the actuating pin 6, as in the previously described embodiment, can be provided with shaped surfaces, such as, for example, square surfaces, in order to introduce a torque about the longitudinal axis of the actuating pin 6 into the actuating pin.
• the distances between the surfaces 40 and 41 of the actuating pin and the annular support surface in the shoulder of the bore 4 and the support surface on the housing section 3, which supports the second bearing shell 62, are selected such that axially outward forces from the actuating pin 6 into the housing section 3 are guided via the deep groove ball bearing 60 and the transmission of these forces via the slide bearing 50 is substantially or completely avoided. That is, the axial deep groove ball bearing 60 and the slide bearing 50 do not constitute an undetermined bearing since the slide bearing 50 has axial air.
• FIG. 3 is identical to the embodiment of FIG. 2 with regard to the sections 6a, 6b of the actuating pin 6, the slide bearing 50 and the seal 8.
• the housing 2 of the embodiment in FIG. 3 has a flattened portion 5 at the end of the bore 4 facing away from the flow channel 19.
• the flattened portion 5 lies perpendicular to the longitudinal axis of the bore 4.
• the annular surface 41 of the second shoulder of the actuating pin 6 projects beyond the flattened portion 5 of the housing 2.
• a plate 70 is arranged on the surface 41 and has an annular depression 71.
• the first bearing shell 61 is arranged in the annular depression 71.
• the deep groove ball bearing 60 protrudes axially beyond the annular depression 71.
• the second bearing shell 62 of the deep groove ball bearing 60 is arranged and supported in an annular depression 81 of a second plate 80.
• the second plate 80 is connected to a housing section 3.
• the torque required to actuate the actuating pin 6 can be made in the same way as in the previously mentioned embodiments via shaped surfaces which are in the end region of the Section 6c are arranged to be initiated.
• the torque required for actuation can be introduced via the plate 70, provided that it is connected to the actuating pin 6 in a torque-proof manner.

Landscapes

• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Taps Or Cocks (AREA)
• Sealing Devices (AREA)
• Details Of Valves (AREA)
• Sealing With Elastic Sealing Lips (AREA)
• Gasket Seals (AREA)

Applications Claiming Priority (3)

Publications (1)

Family

ID=7696748

Family Applications (1)

Country Status (8)

Families Citing this family (9)

Family Cites Families (18)

• 2001
  • 2001-08-28 DE DE10141927A patent/DE10141927A1/de not_active Ceased
• 2002
  • 2002-08-27 KR KR1020047002875A patent/KR100594821B1/ko not_active Expired - Fee Related
  • 2002-08-27 WO PCT/EP2002/009531 patent/WO2003020664A1/de active Application Filing
  • 2002-08-27 US US10/488,024 patent/US20050040607A1/en not_active Abandoned
  • 2002-08-27 BR BR0212127-1A patent/BR0212127A/pt not_active Application Discontinuation
  • 2002-08-27 JP JP2003524937A patent/JP4106022B2/ja not_active Expired - Fee Related
  • 2002-08-27 CN CNB028169409A patent/CN1280562C/zh not_active Expired - Fee Related
  • 2002-08-27 EP EP02767434A patent/EP1423348A1/de not_active Withdrawn

Non-Patent Citations (1)

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