CA2165686A1 - Sealing arrangement for a spindle guided in an axially movable manner out of a housing - Google Patents
Sealing arrangement for a spindle guided in an axially movable manner out of a housingInfo
- Publication number
- CA2165686A1 CA2165686A1 CA002165686A CA2165686A CA2165686A1 CA 2165686 A1 CA2165686 A1 CA 2165686A1 CA 002165686 A CA002165686 A CA 002165686A CA 2165686 A CA2165686 A CA 2165686A CA 2165686 A1 CA2165686 A1 CA 2165686A1
- Authority
- CA
- Canada
- Prior art keywords
- annular
- casing
- diaphragm
- pressure
- transmission member
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
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
-
- 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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
-
- 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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/002—Sealings comprising at least two sealings in succession
- F16J15/004—Sealings comprising at least two sealings in succession forming of recuperation chamber for the leaking fluid
-
- 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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/002—Sealings comprising at least two sealings in succession
- F16J15/008—Sealings comprising at least two sealings in succession with provision to put out of action at least one sealing; One sealing sealing only on standstill; Emergency or servicing sealings
-
- 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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/46—Sealings with packing ring expanded or pressed into place by fluid pressure, e.g. inflatable packings
- F16J15/48—Sealings with packing ring expanded or pressed into place by fluid pressure, e.g. inflatable packings influenced by the pressure within the member to be sealed
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Architecture (AREA)
- Fluid Mechanics (AREA)
- Sealing Devices (AREA)
Abstract
Seal arrangement for a spindle (1) passing in an axially movable manner out of a casing (2) under the pressure of an operating medium, comprising a plurality of annular gland seal members (16, 18, 21, 23, 25, 27) located in an axial spacing one behind the other in an annular space (5) formed between spindle (1) and casing (2). The annular seal members (16, etc.) are under axial initial tension from the interior (40) of the casing by a pressure transmission member (6) loaded by the operating medium.
Description
216568(~
SE~L ARRANGEMENT FOR A SPINDLE PASSING IN AN AXIA~LY
MOVABLE M~NNER OUT OF A CASING
DESCRIPTION
The invention relates to a seal arrangement for a spindle passing in an axially movable mAnner out of a casing, a pressure line or the like, under the pressure of an operating medium, according to the preamble to Patent Claim 1.
Such a seal arrangement is known from DE 40 01 731 Al.
This known arrangement is characterised in that operation of the casing or the like under pressure need not be interrupted for servicing the external seal arrangement, i.e. for replacement of the outer group of annular seal members. The situation however is different with the seal arrangement in the interior of the casing. This may only be replaced after interruption of operation.
In addition, in the known seal arrangement, as with all other previous gland seals, the annular seal members are placed from the exterior axially under such a degree of initial tension that the innermost annular seal members in the casing deform radially sufficiently in order to achieve the necessary seal. This means 216~68~
that a large proportion of the axial force over the length of the seal arrangement is converted into unnecessarily high radial forces, which lead to permanent deformation in the outer annular seal members in the casing. In particular, high radial forces are exerted over the entire length of the seal arrangement on the spindle, with the result that the spindle becomes relatively stiff. In addition, wear on the annular seal members is unnecessarily increased.
The known gland seal arrangements are also characterised by a relatively great constructive length. Accordingly there is a risk that the seal arrangement, and particularly the annular seal members of the same, are exposed to additional stresses, which are constrained by distortion or bending of the spindle to the seal.
The known constructions also omit measures which would guarantee sufficient seal of the spindle even when it has a diameter changing over its length as a result of temperature influences. The changing diameter, upon axial movement of the spindle, causes a correspondingly changing radial load and a deformation of the individual annular seal members, which can lead to leakage after protracted use.
The purpose underlying the present invention is to provide a seal arrangement of the type already 3 21656~G
mentioned in which the annular seal members, internally in the casing and primarily responsible for the seal, are separately placed under initial tension, so that the axially outward initial tension and the overall constructive length of the arrangement can be considerably reduced without loss of the desired seal effect.
This purpose is fulfilled according to the invention in that the annular seal members are initially axially stressed from the interior of the casing by a pressure transmission member under load by the operating medium.
By means of this measure the annular seal members in the interior of the casing and primarily responsible for the axially movable spindle undergo a separate axial initial tension dependent on the pressure of the operating medium. The annular seal members in the interior of the casing are radially deformed to an increased degree by the loading from the interior of the casing, with a corresponding seal effect on the spindle at the point essential for this, i.e. as close as possible to the casing space which is under pressure. ~he axially outward portion of the seal arrangement is in this way relieved of stress to a considera~le extent. Accordingly, the axial outer initial tension on the annular seal members may also be reduced. The same applies to the constructive length of the seal arrangement, with the result that distortion or bending of the spindle upon axial movement of the same has hardly any further effect.
According to the invention, therefore, the m~ m seal effect is achieved in the direct vicinity of the operating medium under pressure. It is also of importance that the axial initial tension on the annular seal members inside the casing is load-dependent, i.e. dependent on the pressure of the operating medium in the interior of the casing. The annular seal members are thus not unnecessarily heavily loaded in dependence on the m~; mllm seal effect to be achieved, but respectively only as is necessary for operation. Thus the life-expectancy of the annular seal members may be considerably increased.
The pressure transmission member provided according to the invention preferably comprises a slide bush through which the spindle passes, and which is connected in a fluid-tight manner via a diaphragm within the inner side of the casing, particularly by welding. Thus a sufficiently large pressure transmission surface is provided.
The constructive design according to Claims 3 and 4 - aids the transmissian of the pressure of the operating medium to the s~ide bush through which the spindle passes, and thus to the annular seal members which are innermost in the casing.
216568(~
According to Claim 5, the wall thickness of the diaphragm of the pressure transmission member decreases radially in an outward direction, starting from the slide bush, in particular continuously. In this way, and in conjunction with one or a plurality of annular shafts according to Claim 4, upon axial movement of the slide bush, no bending movement is exerted thereon, or the slide bush and the diaphragm are movable precisely axially, i.e. parallel to the longitl~; n~l direction of the spindle. The measures according to Claim 5 lead to a particularly rigid design of the pressure transmission member in the transitional area between slide bush and diaphragm.
In a concrete embodiment of the seal arrangement according to the invention, the slide bush of the pressure transmission member projects through the casing into the annular space accommodating the annular seal members, there being arranged in the outer end, or in the end of the slide bush projecting into the annular space, a radially outwardly projecting stop co-operating with the inner end or base of the annular space, said stop being particularly in the form of a stop ring which may be screwed on to the slide bush.
This stop ring limits the axial displacement of the slide bush of the pressure transmission member in the direction of the interior of the casing. In the opposite direction, the axial mo~ement of the slide bush is limited by the diaphragm connected thereto, 6 216558~i particularly integrally formed as one piece, or by a separate stop located on the outer periphery of the slide bush and co-operating with the inner side of the casing.
In order to enable replacement of the annular seal members in any optional position of the spindle, the measures according to Claims lO to 12 are provided. In this case, contrary to the prior art already mentioned, it is possible to replace all, i.e. even the ;nn~rmost annular seal members in the casing during operation in any optional spindle position or operational position.
The same also applies to other servicing operations on the seal arrangement, e.g. replacement of the spacer or the like. To this extent the seal arrangement according to the invention represents considerable progress compared to the previously known prior art.
The pressure medium chamber defined in more detail in Claims 13 and 14 shows whether servicing of the seal arrangement is necessary or not. Further, this reliably avoids the penetration of operating medium in an outward direction. This is above all important when the operating medium involves gases and fluids which are aggressive and injurious to health.
The measures according to Claims 15 et seq. are also of particular importance; according to these the annular seal members are radially movably mounted without this 7 2165681~
leading to any impairment in the seal effect.
Accordingly, distortions or bends in the spindle may be compensated for without difficulty. The same applies to the influence of an alteration in the diameter of the spindle caused ~y temperature factors.
An embodiment of a seal arrangement according to the invention will be explained in more detail in the following with reference to the annexed drawing. This shows one half of the abov~n~me~ embodiment in longitudinal Section, the spindle passing in an axially movable m~nner out of a casing 2 being identified ~y the reference numeral I. The internal space of the casing 2, under the pressure of an operating medium, is indicated by reference numeral 40. The seal arrangement shown comprises a so-called gland seal which is located within an annular space 5 formed between spindle 1 and casing 2. Seen from the exterior inwards, the gland seal has the following elements within the annular space 5:
- plate spring`s 29 - pressure ring 28 - axially and radially deformable annular seal member - axial face disc 24 - annular seal member 23 - axial face disc 22 - annular seal member 21 - spacer 19 with radial opening 20 - annular seal member i8 - axial face disc 17 - annular seal member 16 5 - axial face disc 31 - stripper rings 14 - seal ring disc 13.
The spacer 19 subdivides the annular seal members, 10 located one after the other with an axial spacing, into an axial inner group of annular seal mem.bers 16, 18 and an axial outer group of annular seal me-m-bers 21, 23, 24 and 27. The spacer 19 is connected in terms of fluid via a casing bore 32 with a closed, resiliently-15 expandable, in this case bellows shaped, pressuremedium chamber 34. Between the casing bore 32 and the pressure medium chamber 32 there is a connecting line 33. Axially outwardly, the annular space 5 is closed by a casing lid 3 extending around the spindle 1. ~or 20 this purpose the casing lid 3 is screwed on to the casing 2. The lid screw is indicated by reference numeral 4. The plate springs 29 exert an axial resilient initial tension on the annular seal members or gland rings 27, 25, 23, 21, 18 and 16, the effect on 25 the annular seal members 16, 18 inside the casing still being ml nl m~l. Accordingly, the axial initial tension of the annular seal members 16, 17 in the interior of the casing is exerted from the interior of the casing, via a pressure transmission member 6, which is loaded 216S68~
by the operating medium. This pressure transmission member comprises a slide bush 9, through which the spindle 1 passes, and which is connected in fluid ter-ms via a diaphragm 44 with the inner side o the casing 2, i.e. by welding. The corresponding annular weld seam is indicated by reference numeral 7. The diaphragm 44 is in annular disc form and has a portion 8 of increased resilience extend; ng over the circumference.
This portion 8 extends close to the outer circumference of the diaphragm 44 and is indicated by an annular recess. Fur~her, it may be seen that the wall thickness of the diaphragm 44, starting from the slide bush 9, continuously decreases in a radial outward direction, the wall thickness in the region of the recess 8 being at a ml n;~llm, By means of this construction, the transitional area between slide bush 9 and diaphragm 14 is sufficiently rigid. The deformation of the soft resilient recess 18 enables it to be ascertained that the slide bush with the diaphragm is substantially free of bending moment, and is axially movable in accordance with the pressure loading exerted by the operating medium in the interior of the casing 40. By means of the abo~enamed measures, the ease of running on the spindle 1 is not impaired by the slide bush 9, independently of its relative position.
As the drawing further shows, the slide bush 9 of the pressure transmission member 6 projects through the lo 216568~
casing 2 into the annular space 5 receiving the annular seal member 16 et seq., there being located at the outer end, i.e. the end of the slide bush 9 projecting into the annular space 5, radially outwardly projecting stop co-operating with the inner end or base of the annular space 5, said stop being in the form of a stop ring 10 which may be screwed on to the slide bush 9.
This stop ring limits the axial movement of the slide bush 9 in an inward direction, i.e. in the direction of arrow E.
In the opposite direction, i.e. in the direction of the ~arrow D, the axial movement of the slide bush 9 is limited by the membrane 44, which is integrally formed thereon as one piece, in co-operation with the associated inner side of the casing 2. It is also feasible to provide on the outer circumference o~ the slide bush 9 directly above the projection of the membrane 44, a separate annular stop, which limits the axial movement of the slide bush 9 from the outside inwards, and in turn in co-operation with the inner side of the casing 2 facing the diaphragm.
The space defined on the one hand by the pressure transmission member 6 and by the associated inner side of the casing 2 on the other side, in this case annular space 42, is connected in fluid terms via a leakage - hole 11 in the casing wall with the environment.
Accordingly, ambient pressure obtains in this space 42.
11 21656~
Accordingly, the pressure transmission member undergoes a pressure loading acting axially outwards due to the pressure of the operating medium obtaining in the inside of the casing 40. In this way the axial initial tension on the annular seal members 16, 18 on the inside of the casing, is effected from the interior of the casing, i.e. in the direction of arrow D.
A further important point is that on the inner or pressure-loaded side of the pressure transmission member 6, i.e. on the pressure-loaded side of the diaphragm 44 of the same, there is located a further diaphragm 36, extending around the spindle 1, and which between itself, the spindle 1 and the diaphragm 44, defines a space which commllnicates with the interior of the casing 40 under pressure ~ia an annular slot ~8 between diaphragm 36 and spindle 1 on the one hand and an opening located diametrically thereto, particularly a bore 39, on the other hand, with the interior of the casing 40. The diaphragm 36 is made of a heat-resistant steel plate in the manner of a plate spring, and is welded in a fluid-tight manner along its outer peripheral edge to the diaphragm 44 of the pressure - transmission member 6. The edge 37 of the diaphragm 36 2S exten~' ng about the spindle 1 is bent or curled outwards, in adaptation to the radius of the facing inner edge 45 of the slide bush 9, the outwardly bent or curled edge 37 being at a spacing from the facing inner edge 45 of the slide bush 9 under normal 12 216568~
operational conditions, as shown in the drawing, i.e.
when there is sufficient seal~g of the annular seal members 16 et seq.. Upon leakage or removal of the annular seal members 16 et seq. the outwardly bent or curled edge 37 of the diaphragm 36, deforming resiliently, is forced into the slot between spindle 1 and associated inner edge 45 of the slide bush 9, in such a way that a seal is produced between spindle 1 and slide bush 9 or pressure transmission member 6. As already mentioned abo~e, upon incorporation of the gland rings or annular seal members 16 et seq., the axially outer plate springs 29 apply a m;n;ml1m axial and deformation-constrained radial tension on the annular seal member 16 et seq., which ensure a m;n;mllm degree of seal of the spindle 1. Thus the gland seal is tight towards the exterior. By means of this procedure, the pressure transmission member ~ or its slide bush 9 is displaced inwards, i.e. in the direction of the arrow E, against the force of the resilient portion 8 of the diaphragm 44. The axial inward movement is limited by the stop ring 10. The system is then in a pressure-free state of equilibrium, as long as the stop ring 10 is ineffective. This means that there are effective, on the axially outermost annular seal member or gland ring 27, and on the innermost stripper ring 14 inside the casing, the same axial forces which are converted into radial tensions in accordance with the coefficient of the material.
Upon an increase in the pressure in the interior 40 of the casing 2, an axial force is exerted on the diaphragm 44 of the pressure transmission member 6.
This axial force is transmitted via the slide bush 9 and its outer end face 41 to the stripper rings and accordingly also to the annular seal members 16, 18 inside the casing. The pressure force arising at that paint is proportional to the pressure differential to be sealed off, always lying below the m; n;mllm pressure force constrained by the plate springs 29. The stripper rings 14 serve to ~eep solid components of the medium to the outside upon movement of the spindle 1, i.e in the direction of arrow D In the embodiment shown, the annular seal member 16 et seq. and the stripper rings 14 each have conical end faces. They are aligned with one another by means of these surfaces in such a way that, when under axial pressure, they are alternatively forced radially outwards and inwards, these radial movements being enabled by annular slots 46 or 46' between the gland ring seal members on the one hand and the spindle 1 on the casing 2 on the other hand (see Figure). Thus a good seal is achieved both in relation to the spindle 1 and also to the casing or annular space 5. Located between axially adjacent annular seal members there is respectively an axial face disc 15, 17, 22, 24, 26. The axial face discs 15, etc. enable or facilitate , depending on their inclination, a radial pressure dependent on direction and the relative movement of annular seal members or gland rings in the case of varying spindle diameters 14 216568~
and non-linearity of the flush alignment of the axes of spindle 1 and of annular space 5. Should however a leak occur in the region inside the casing of the seal arrangement, the leakage arising is diverted through the bore 20 in the spacer 19, casing bore 32 and pipe 33 into the already mentioned pressure medium chamber 34. Under normal conditions, the pressure medium chamber 34 is under initial ~echanical tension, i.e. a partial vacuum obtains in the chamber 34. Thus leakage amounts need not cause high pressures in order to expand the pressure medium chamber 34 in the direction of arrow A. Upon a specific leakage amount, an electrical contact 35 associated with the pressure medium 34 is closed, triggering a corresponding signal.
~he pressure medium chamber 34 may then be again pressurised, the leakage amount of the operating medium being mechanically forced again back into the system.
The time intervals between two leak signals may be interpreted as a measure of the flow of leakagei and of the necessity for servicing o~ the seal arrangement.
During this procedure, in any case, the external portion of the gland seal arrangement is still fluid-tight, so that no operating medium emerges into the environment in an uncontrolled m~nner. Exchange of defective annular seal members 16 and 18 inside the casing, or of strippers 14, may be carried out in any position on the spindle 1, with the aid of the already mentioned further diaphragm 36. Under normal operational conditions an annular slot 38 is formed 216~6~G
between the diaphragm 36 and the spindle 1. Close to the outer circumferential edge, the diaphragm 36 has a bore 39, whose cross-section is less than the free cross-section of the slot 38. When leakage amounts flow in the direction of the arrow D through the slot 38, solid matter is carried into the space 43 between diaphragm 36 and pressure transmission member 5 or its diaphragm 44, and is there separated. These solid materials or solid particles can however leave the space 43 again through the bore 39. If the leakage amounts are greater, the bore 39 is partially or entirely closed by the solid particles carried along, so that a pressure differential arises between the inner space of the casing 40 and the said diaphragm space 43. This causes an outward movement of the diaphragm 36, i.e. in the direction of arrow D. Thus the annular slot 38 reduces to an increasing degree, with the consequence that the said pressure differential is correspondingly increased. Finally, the outwardly bent or curled edge 37 of the diaphragm 36, in contact with the associated inner edge 45 of the slide bush 9, is forced into the slot between spindle 1 and the said inner edge 45. Thus a metallic seal of spindle 1 is achieved. In this position of the diaphragm 36, all annular seal members or gland rings 16 etc., together with stripper rings, spacer, etc., may be removed from the annular space 5 and replaced by new seal members. In this case operation of the arrangement need not be interrupted. The diaphragm 36 16 216568~
.,, is preferably so designed that it has two stable conditions, i.e. on the one hand the condition shown in the drawing with annular slot 38, and on the other hand the condition of purely metallic seal. In both conditions, the diaphragm 36 remains unaffected by external forces. From the last named condition, i.e.
the condition of metallic seal, the diaphragm 36 may be loosened axially inwardly, i.e. in the direction of arrow E, by movement of the spindle 1. Alternatively, 1~ the diaphragm 36 may also be pressure-loaded via the casing bore 32 and spacer 19. The corresponding design of the diaphragm 36 ~internal tension in the pressure-free condition), achievement of the two stable conditions is not a continuous process. In this lS embodiment the diaphragm 36 is bistable, i.e. held stable either in the open or in the sealing position.
This has the advantage that the two diaphragm positions are clearly defined.
All the features disclosed in the Application Documents are claimed as essential to the invention, insofar as they are new in comparison to prior art, individually or in combination.
17 21 6568g LIST OF REFERENCE N~MER~LS
1 Spindle 2 Casing 3 Lid 4 Connecting screw Annular space 6 Pressure transmission member 7 Annular weld seam 8 Resilient portion 9 Slide bush Stop ring 11 Leakage bore 12 Thread for screwing on stop ring 10 13 Annular seal disc 14 Stripper ring Axial face disc 16 Annular gland seal member 17 Axial face disc 18 Annular gland seal member 19 Spacer member Bore 21 Annular gland seal member 22 Axial face disc 23 Annular gland seal member 24 Axial face disc Annular gland seal member 18 21 6s6~6 26 Axial face disc 27 Annular gland seal member 28 Pressure ring 29 Plate springs Slot 31 Slot 32 Leakage bore 33 Fluid pipe 34 Pressure medium chamber Contact signal emitter 36 Diaphragm 37 Inner edge of diaphragm 36 38 Annular slot 39 Bore Inner space in casing 41 Outer end face of slide bush 9 42 Annular space 43 Space 44 Diaphragm of the pressure transmission member 6 Inner edge of the pressure transmission member or .
of the slide bush 9 46 Annular slot between annular gland seal member and spindle 46' Annular slot between annular gland seal member and casing
SE~L ARRANGEMENT FOR A SPINDLE PASSING IN AN AXIA~LY
MOVABLE M~NNER OUT OF A CASING
DESCRIPTION
The invention relates to a seal arrangement for a spindle passing in an axially movable mAnner out of a casing, a pressure line or the like, under the pressure of an operating medium, according to the preamble to Patent Claim 1.
Such a seal arrangement is known from DE 40 01 731 Al.
This known arrangement is characterised in that operation of the casing or the like under pressure need not be interrupted for servicing the external seal arrangement, i.e. for replacement of the outer group of annular seal members. The situation however is different with the seal arrangement in the interior of the casing. This may only be replaced after interruption of operation.
In addition, in the known seal arrangement, as with all other previous gland seals, the annular seal members are placed from the exterior axially under such a degree of initial tension that the innermost annular seal members in the casing deform radially sufficiently in order to achieve the necessary seal. This means 216~68~
that a large proportion of the axial force over the length of the seal arrangement is converted into unnecessarily high radial forces, which lead to permanent deformation in the outer annular seal members in the casing. In particular, high radial forces are exerted over the entire length of the seal arrangement on the spindle, with the result that the spindle becomes relatively stiff. In addition, wear on the annular seal members is unnecessarily increased.
The known gland seal arrangements are also characterised by a relatively great constructive length. Accordingly there is a risk that the seal arrangement, and particularly the annular seal members of the same, are exposed to additional stresses, which are constrained by distortion or bending of the spindle to the seal.
The known constructions also omit measures which would guarantee sufficient seal of the spindle even when it has a diameter changing over its length as a result of temperature influences. The changing diameter, upon axial movement of the spindle, causes a correspondingly changing radial load and a deformation of the individual annular seal members, which can lead to leakage after protracted use.
The purpose underlying the present invention is to provide a seal arrangement of the type already 3 21656~G
mentioned in which the annular seal members, internally in the casing and primarily responsible for the seal, are separately placed under initial tension, so that the axially outward initial tension and the overall constructive length of the arrangement can be considerably reduced without loss of the desired seal effect.
This purpose is fulfilled according to the invention in that the annular seal members are initially axially stressed from the interior of the casing by a pressure transmission member under load by the operating medium.
By means of this measure the annular seal members in the interior of the casing and primarily responsible for the axially movable spindle undergo a separate axial initial tension dependent on the pressure of the operating medium. The annular seal members in the interior of the casing are radially deformed to an increased degree by the loading from the interior of the casing, with a corresponding seal effect on the spindle at the point essential for this, i.e. as close as possible to the casing space which is under pressure. ~he axially outward portion of the seal arrangement is in this way relieved of stress to a considera~le extent. Accordingly, the axial outer initial tension on the annular seal members may also be reduced. The same applies to the constructive length of the seal arrangement, with the result that distortion or bending of the spindle upon axial movement of the same has hardly any further effect.
According to the invention, therefore, the m~ m seal effect is achieved in the direct vicinity of the operating medium under pressure. It is also of importance that the axial initial tension on the annular seal members inside the casing is load-dependent, i.e. dependent on the pressure of the operating medium in the interior of the casing. The annular seal members are thus not unnecessarily heavily loaded in dependence on the m~; mllm seal effect to be achieved, but respectively only as is necessary for operation. Thus the life-expectancy of the annular seal members may be considerably increased.
The pressure transmission member provided according to the invention preferably comprises a slide bush through which the spindle passes, and which is connected in a fluid-tight manner via a diaphragm within the inner side of the casing, particularly by welding. Thus a sufficiently large pressure transmission surface is provided.
The constructive design according to Claims 3 and 4 - aids the transmissian of the pressure of the operating medium to the s~ide bush through which the spindle passes, and thus to the annular seal members which are innermost in the casing.
216568(~
According to Claim 5, the wall thickness of the diaphragm of the pressure transmission member decreases radially in an outward direction, starting from the slide bush, in particular continuously. In this way, and in conjunction with one or a plurality of annular shafts according to Claim 4, upon axial movement of the slide bush, no bending movement is exerted thereon, or the slide bush and the diaphragm are movable precisely axially, i.e. parallel to the longitl~; n~l direction of the spindle. The measures according to Claim 5 lead to a particularly rigid design of the pressure transmission member in the transitional area between slide bush and diaphragm.
In a concrete embodiment of the seal arrangement according to the invention, the slide bush of the pressure transmission member projects through the casing into the annular space accommodating the annular seal members, there being arranged in the outer end, or in the end of the slide bush projecting into the annular space, a radially outwardly projecting stop co-operating with the inner end or base of the annular space, said stop being particularly in the form of a stop ring which may be screwed on to the slide bush.
This stop ring limits the axial displacement of the slide bush of the pressure transmission member in the direction of the interior of the casing. In the opposite direction, the axial mo~ement of the slide bush is limited by the diaphragm connected thereto, 6 216558~i particularly integrally formed as one piece, or by a separate stop located on the outer periphery of the slide bush and co-operating with the inner side of the casing.
In order to enable replacement of the annular seal members in any optional position of the spindle, the measures according to Claims lO to 12 are provided. In this case, contrary to the prior art already mentioned, it is possible to replace all, i.e. even the ;nn~rmost annular seal members in the casing during operation in any optional spindle position or operational position.
The same also applies to other servicing operations on the seal arrangement, e.g. replacement of the spacer or the like. To this extent the seal arrangement according to the invention represents considerable progress compared to the previously known prior art.
The pressure medium chamber defined in more detail in Claims 13 and 14 shows whether servicing of the seal arrangement is necessary or not. Further, this reliably avoids the penetration of operating medium in an outward direction. This is above all important when the operating medium involves gases and fluids which are aggressive and injurious to health.
The measures according to Claims 15 et seq. are also of particular importance; according to these the annular seal members are radially movably mounted without this 7 2165681~
leading to any impairment in the seal effect.
Accordingly, distortions or bends in the spindle may be compensated for without difficulty. The same applies to the influence of an alteration in the diameter of the spindle caused ~y temperature factors.
An embodiment of a seal arrangement according to the invention will be explained in more detail in the following with reference to the annexed drawing. This shows one half of the abov~n~me~ embodiment in longitudinal Section, the spindle passing in an axially movable m~nner out of a casing 2 being identified ~y the reference numeral I. The internal space of the casing 2, under the pressure of an operating medium, is indicated by reference numeral 40. The seal arrangement shown comprises a so-called gland seal which is located within an annular space 5 formed between spindle 1 and casing 2. Seen from the exterior inwards, the gland seal has the following elements within the annular space 5:
- plate spring`s 29 - pressure ring 28 - axially and radially deformable annular seal member - axial face disc 24 - annular seal member 23 - axial face disc 22 - annular seal member 21 - spacer 19 with radial opening 20 - annular seal member i8 - axial face disc 17 - annular seal member 16 5 - axial face disc 31 - stripper rings 14 - seal ring disc 13.
The spacer 19 subdivides the annular seal members, 10 located one after the other with an axial spacing, into an axial inner group of annular seal mem.bers 16, 18 and an axial outer group of annular seal me-m-bers 21, 23, 24 and 27. The spacer 19 is connected in terms of fluid via a casing bore 32 with a closed, resiliently-15 expandable, in this case bellows shaped, pressuremedium chamber 34. Between the casing bore 32 and the pressure medium chamber 32 there is a connecting line 33. Axially outwardly, the annular space 5 is closed by a casing lid 3 extending around the spindle 1. ~or 20 this purpose the casing lid 3 is screwed on to the casing 2. The lid screw is indicated by reference numeral 4. The plate springs 29 exert an axial resilient initial tension on the annular seal members or gland rings 27, 25, 23, 21, 18 and 16, the effect on 25 the annular seal members 16, 18 inside the casing still being ml nl m~l. Accordingly, the axial initial tension of the annular seal members 16, 17 in the interior of the casing is exerted from the interior of the casing, via a pressure transmission member 6, which is loaded 216S68~
by the operating medium. This pressure transmission member comprises a slide bush 9, through which the spindle 1 passes, and which is connected in fluid ter-ms via a diaphragm 44 with the inner side o the casing 2, i.e. by welding. The corresponding annular weld seam is indicated by reference numeral 7. The diaphragm 44 is in annular disc form and has a portion 8 of increased resilience extend; ng over the circumference.
This portion 8 extends close to the outer circumference of the diaphragm 44 and is indicated by an annular recess. Fur~her, it may be seen that the wall thickness of the diaphragm 44, starting from the slide bush 9, continuously decreases in a radial outward direction, the wall thickness in the region of the recess 8 being at a ml n;~llm, By means of this construction, the transitional area between slide bush 9 and diaphragm 14 is sufficiently rigid. The deformation of the soft resilient recess 18 enables it to be ascertained that the slide bush with the diaphragm is substantially free of bending moment, and is axially movable in accordance with the pressure loading exerted by the operating medium in the interior of the casing 40. By means of the abo~enamed measures, the ease of running on the spindle 1 is not impaired by the slide bush 9, independently of its relative position.
As the drawing further shows, the slide bush 9 of the pressure transmission member 6 projects through the lo 216568~
casing 2 into the annular space 5 receiving the annular seal member 16 et seq., there being located at the outer end, i.e. the end of the slide bush 9 projecting into the annular space 5, radially outwardly projecting stop co-operating with the inner end or base of the annular space 5, said stop being in the form of a stop ring 10 which may be screwed on to the slide bush 9.
This stop ring limits the axial movement of the slide bush 9 in an inward direction, i.e. in the direction of arrow E.
In the opposite direction, i.e. in the direction of the ~arrow D, the axial movement of the slide bush 9 is limited by the membrane 44, which is integrally formed thereon as one piece, in co-operation with the associated inner side of the casing 2. It is also feasible to provide on the outer circumference o~ the slide bush 9 directly above the projection of the membrane 44, a separate annular stop, which limits the axial movement of the slide bush 9 from the outside inwards, and in turn in co-operation with the inner side of the casing 2 facing the diaphragm.
The space defined on the one hand by the pressure transmission member 6 and by the associated inner side of the casing 2 on the other side, in this case annular space 42, is connected in fluid terms via a leakage - hole 11 in the casing wall with the environment.
Accordingly, ambient pressure obtains in this space 42.
11 21656~
Accordingly, the pressure transmission member undergoes a pressure loading acting axially outwards due to the pressure of the operating medium obtaining in the inside of the casing 40. In this way the axial initial tension on the annular seal members 16, 18 on the inside of the casing, is effected from the interior of the casing, i.e. in the direction of arrow D.
A further important point is that on the inner or pressure-loaded side of the pressure transmission member 6, i.e. on the pressure-loaded side of the diaphragm 44 of the same, there is located a further diaphragm 36, extending around the spindle 1, and which between itself, the spindle 1 and the diaphragm 44, defines a space which commllnicates with the interior of the casing 40 under pressure ~ia an annular slot ~8 between diaphragm 36 and spindle 1 on the one hand and an opening located diametrically thereto, particularly a bore 39, on the other hand, with the interior of the casing 40. The diaphragm 36 is made of a heat-resistant steel plate in the manner of a plate spring, and is welded in a fluid-tight manner along its outer peripheral edge to the diaphragm 44 of the pressure - transmission member 6. The edge 37 of the diaphragm 36 2S exten~' ng about the spindle 1 is bent or curled outwards, in adaptation to the radius of the facing inner edge 45 of the slide bush 9, the outwardly bent or curled edge 37 being at a spacing from the facing inner edge 45 of the slide bush 9 under normal 12 216568~
operational conditions, as shown in the drawing, i.e.
when there is sufficient seal~g of the annular seal members 16 et seq.. Upon leakage or removal of the annular seal members 16 et seq. the outwardly bent or curled edge 37 of the diaphragm 36, deforming resiliently, is forced into the slot between spindle 1 and associated inner edge 45 of the slide bush 9, in such a way that a seal is produced between spindle 1 and slide bush 9 or pressure transmission member 6. As already mentioned abo~e, upon incorporation of the gland rings or annular seal members 16 et seq., the axially outer plate springs 29 apply a m;n;ml1m axial and deformation-constrained radial tension on the annular seal member 16 et seq., which ensure a m;n;mllm degree of seal of the spindle 1. Thus the gland seal is tight towards the exterior. By means of this procedure, the pressure transmission member ~ or its slide bush 9 is displaced inwards, i.e. in the direction of the arrow E, against the force of the resilient portion 8 of the diaphragm 44. The axial inward movement is limited by the stop ring 10. The system is then in a pressure-free state of equilibrium, as long as the stop ring 10 is ineffective. This means that there are effective, on the axially outermost annular seal member or gland ring 27, and on the innermost stripper ring 14 inside the casing, the same axial forces which are converted into radial tensions in accordance with the coefficient of the material.
Upon an increase in the pressure in the interior 40 of the casing 2, an axial force is exerted on the diaphragm 44 of the pressure transmission member 6.
This axial force is transmitted via the slide bush 9 and its outer end face 41 to the stripper rings and accordingly also to the annular seal members 16, 18 inside the casing. The pressure force arising at that paint is proportional to the pressure differential to be sealed off, always lying below the m; n;mllm pressure force constrained by the plate springs 29. The stripper rings 14 serve to ~eep solid components of the medium to the outside upon movement of the spindle 1, i.e in the direction of arrow D In the embodiment shown, the annular seal member 16 et seq. and the stripper rings 14 each have conical end faces. They are aligned with one another by means of these surfaces in such a way that, when under axial pressure, they are alternatively forced radially outwards and inwards, these radial movements being enabled by annular slots 46 or 46' between the gland ring seal members on the one hand and the spindle 1 on the casing 2 on the other hand (see Figure). Thus a good seal is achieved both in relation to the spindle 1 and also to the casing or annular space 5. Located between axially adjacent annular seal members there is respectively an axial face disc 15, 17, 22, 24, 26. The axial face discs 15, etc. enable or facilitate , depending on their inclination, a radial pressure dependent on direction and the relative movement of annular seal members or gland rings in the case of varying spindle diameters 14 216568~
and non-linearity of the flush alignment of the axes of spindle 1 and of annular space 5. Should however a leak occur in the region inside the casing of the seal arrangement, the leakage arising is diverted through the bore 20 in the spacer 19, casing bore 32 and pipe 33 into the already mentioned pressure medium chamber 34. Under normal conditions, the pressure medium chamber 34 is under initial ~echanical tension, i.e. a partial vacuum obtains in the chamber 34. Thus leakage amounts need not cause high pressures in order to expand the pressure medium chamber 34 in the direction of arrow A. Upon a specific leakage amount, an electrical contact 35 associated with the pressure medium 34 is closed, triggering a corresponding signal.
~he pressure medium chamber 34 may then be again pressurised, the leakage amount of the operating medium being mechanically forced again back into the system.
The time intervals between two leak signals may be interpreted as a measure of the flow of leakagei and of the necessity for servicing o~ the seal arrangement.
During this procedure, in any case, the external portion of the gland seal arrangement is still fluid-tight, so that no operating medium emerges into the environment in an uncontrolled m~nner. Exchange of defective annular seal members 16 and 18 inside the casing, or of strippers 14, may be carried out in any position on the spindle 1, with the aid of the already mentioned further diaphragm 36. Under normal operational conditions an annular slot 38 is formed 216~6~G
between the diaphragm 36 and the spindle 1. Close to the outer circumferential edge, the diaphragm 36 has a bore 39, whose cross-section is less than the free cross-section of the slot 38. When leakage amounts flow in the direction of the arrow D through the slot 38, solid matter is carried into the space 43 between diaphragm 36 and pressure transmission member 5 or its diaphragm 44, and is there separated. These solid materials or solid particles can however leave the space 43 again through the bore 39. If the leakage amounts are greater, the bore 39 is partially or entirely closed by the solid particles carried along, so that a pressure differential arises between the inner space of the casing 40 and the said diaphragm space 43. This causes an outward movement of the diaphragm 36, i.e. in the direction of arrow D. Thus the annular slot 38 reduces to an increasing degree, with the consequence that the said pressure differential is correspondingly increased. Finally, the outwardly bent or curled edge 37 of the diaphragm 36, in contact with the associated inner edge 45 of the slide bush 9, is forced into the slot between spindle 1 and the said inner edge 45. Thus a metallic seal of spindle 1 is achieved. In this position of the diaphragm 36, all annular seal members or gland rings 16 etc., together with stripper rings, spacer, etc., may be removed from the annular space 5 and replaced by new seal members. In this case operation of the arrangement need not be interrupted. The diaphragm 36 16 216568~
.,, is preferably so designed that it has two stable conditions, i.e. on the one hand the condition shown in the drawing with annular slot 38, and on the other hand the condition of purely metallic seal. In both conditions, the diaphragm 36 remains unaffected by external forces. From the last named condition, i.e.
the condition of metallic seal, the diaphragm 36 may be loosened axially inwardly, i.e. in the direction of arrow E, by movement of the spindle 1. Alternatively, 1~ the diaphragm 36 may also be pressure-loaded via the casing bore 32 and spacer 19. The corresponding design of the diaphragm 36 ~internal tension in the pressure-free condition), achievement of the two stable conditions is not a continuous process. In this lS embodiment the diaphragm 36 is bistable, i.e. held stable either in the open or in the sealing position.
This has the advantage that the two diaphragm positions are clearly defined.
All the features disclosed in the Application Documents are claimed as essential to the invention, insofar as they are new in comparison to prior art, individually or in combination.
17 21 6568g LIST OF REFERENCE N~MER~LS
1 Spindle 2 Casing 3 Lid 4 Connecting screw Annular space 6 Pressure transmission member 7 Annular weld seam 8 Resilient portion 9 Slide bush Stop ring 11 Leakage bore 12 Thread for screwing on stop ring 10 13 Annular seal disc 14 Stripper ring Axial face disc 16 Annular gland seal member 17 Axial face disc 18 Annular gland seal member 19 Spacer member Bore 21 Annular gland seal member 22 Axial face disc 23 Annular gland seal member 24 Axial face disc Annular gland seal member 18 21 6s6~6 26 Axial face disc 27 Annular gland seal member 28 Pressure ring 29 Plate springs Slot 31 Slot 32 Leakage bore 33 Fluid pipe 34 Pressure medium chamber Contact signal emitter 36 Diaphragm 37 Inner edge of diaphragm 36 38 Annular slot 39 Bore Inner space in casing 41 Outer end face of slide bush 9 42 Annular space 43 Space 44 Diaphragm of the pressure transmission member 6 Inner edge of the pressure transmission member or .
of the slide bush 9 46 Annular slot between annular gland seal member and spindle 46' Annular slot between annular gland seal member and casing
Claims (18)
PROPERTY OF PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. Seal arrangement for a spindle (1) passing axially movably out of a casing (2) under the pressure of an operating medium, or out of a pressure pipe or the like, said seal arrangement comprising a plurality of annular gland seal members (16, 18, 21, 23, 25, 27), located at axial spacings one behind the other in an annular space (5) formed between spindle (1) and casing (2), said annular gland seal members being subdivided by a spacer (19) into an axially inner group of annular seal members (16, 18) and an axially outer group of annular seal members (21, 23, 25, 27), the spacer (19) being connected in fluid terms via a bore (32) formed in the casing (2) with a pressure medium chamber (34), and the annular seal members (16, 18, 21, 23, 25, 27) being initially tensioned in the axial direction, characterised in that the annular seal members (16, 18, 21, 23, 25, 27) are under a degree of initial axial tension from the interior (40) of the casing by means of a pressure transmission member (6) loaded by the operating medium.
2. Seal arrangement according to Claim 1, characterised in that the pressure transmission member (6) comprises a slide bush (g) through which the spindle (1) passes, and which is connected in fluid terms via a diaphragm (44) with the inner side of the casing (2), particularly by welding (annular weld seam 7).
3. Seal arrangement according to Claim 2, characterised in that the diaphragm (44) of the pressure transmission member (6) is in annular disc form and has a portion (8) of increased resilience extending over the circumference.
4. Seal arrangement according to Claim 3, characterised in that the portion (8) of increased resilience extends close to the outer circumference of the diaphragm (44) and comprises a weakened portion of material and/or one, or a plurality of, annular corrugation(s).
5. Seal arrangement according to one of Claims 2 to 4, characterised in that the wall thickness of the diaphragm (44) of the pressure transmission member (6), starting from the slide bush (9), decreases in a radially outward direction, especially continuously.
6. Seal arrangement according to Claim 5, characterised in that the diaphragm (44) of the pressure transmission member (6) has a minimum wall thickness in the region of its resilient portion (8).
7. Seal arrangement according to one of Claims 1 to 6, characterised in that the slide bush (9) of the pressure transmission member (6) projects through the casing (2) into the annular space (5) receiving the annular seal members (16, etc), there being located in the outer end or the end projecting into the annular space (5) of the slide bush (9), a radially outwardly projecting stop, co-operating with the end or base of the annular space (5) particularly in the form of a stop ring (10) which may be screwed onto the slide bush (9).
8. Seal arrangement according to one of Claims 1 to 7, characterised in that the space defined by the pressure transmission member (6) on the one hand and the associated inner side of the casing (2) on the other hand, particularly annular space (42), may be connected with the environment in fluid terms via a leakage bore (11) in the casing wall.
9. Seal arrangement according to Claim 7 or 8, characterised in that the axial movement of the slide bush (9) of the pressure transmission member (6) is restricted on the one hand, i.e. in the inward direction by the stop, particularly stop ring (10) located on the inner end, or on the end projecting into the annular space (5) receiving the annular seal members (16, etc.), and on the other hand, i.e. in the outward direction, by the diaphragm (44) connected to the slide bush (9) particularly integrally formed as one piece therewith, located for a separate stop located on the outer circumference of the slide bush (9), and co-operating with the inner side of the casing (2) facing the diaphragm (44).
10. Seal arrangement according to one of Claims 1 to 9, characterised in that there is located on the inner or pressure-loaded side of the pressure transmission member (6), particularly on the pressure-loaded side of the diaphragm (44) of the same, a further diaphragm (36) extending around the spindle (1), and which defines between itself, the spindle (1) and the pressure transmission member (6) or its diaphragm (44) a space (43) which communicates with the interior (40) of the casing which is under pressure via an annular slot (38) between the further diaphragm (36) and spindle (1) on the one hand and an opening located diametrically thereto, particularly a bore (39), on the other hand, with the interior (40) of the casing.
11. Seal arrangement according to Claim 10, characterised in that the further diaphragm (36) is formed in the manner of a plate spring, and is connected in a fluid-tight manner along its outer circumferential edge to the pressure transmission member (6) or its diaphragm (44) this being achieved in particular by welding.
12. Seal arrangement according to Claim 10 or 11 characterised in that the edge (37) of the further diaphragm (36) extending around the spindle (1) is bent outwards or curled in adaptation to the radius of the facing inner edge (45) of the pressure transmission member (6) or of the slide bush (9) of the same, the outwardly bent or curled edge (47) of the further diaphragm (36) under normal operational conditions, particularly when there is sufficient seal of the annular seal members (16, etc.), is at a spacing from the facing inner edge (45) of the pressure transmission member or its slide bush (9), whereas upon leakage or removal of the angular seal member (16, etc.), the outwardly bent or curled edge (37) of the further diaphragm (36), deforming resiliently, is forced into the slot between spindle (1) and associated inner edge (45) of the pressure transmission member or its slide bush (9) in such a way that a seal is obtained between spindle (1) and pressure transmission member (6) or its slide bush (9).
13. Seal arrangement according to one of Claims 1 to 12, characterised in that the pressure medium chamber (34), connected in fluid terms with the spacer (20), serves to receive leakage amounts of the operating medium, and is resilient and elastic, particularly bellows-like in form.
14 . Seal arrangement according to Claim 13, characterised in that the pressure medium chamber (34) has associated therewith a sensor, particularly an electrical contact (35), which emits a signal for excessive expansion of the pressure medium chamber (34), and thus unacceptable leakage.
15. Seal arrangement according to one of Claims 1 to 14, characterised in that the annular seal members (16, etc.) are supported via stripper rings (14) and if necessary an axial face disc (13) on the slide bush (9) of the pressure transmission member (6) or the outer end face (41) of the same.
16. Seal arrangement according to one of Claims 1 to 15, characterised in that the annular seal members (16, etc.) and if necessary also the stripper rings (14) each have conical end faces, and with these faces are aligned with one another in such a way that, under axial pressure, they are alternatively forced radially outwards and radially inwards.
17. Seal arrangement according to Claim 16, characterised in that an axial face disc (15, 17, 22, 24, 26) is located respectively between axially adjacent annular seal members (16, etc.).
18. Seal arrangement according to one of Claims 1 to 17, characterised in that the annular seal members (16, etc.) are held within the annular space (5) between spindle (1) and casing (2) by a lid (3), with interposed spring, particularly plate springs (29) and a pressure ring (28).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DEP4414174.2 | 1994-04-22 | ||
| DE4414174A DE4414174A1 (en) | 1994-04-22 | 1994-04-22 | Sealing arrangement for a spindle guided axially out of a housing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2165686A1 true CA2165686A1 (en) | 1995-11-02 |
Family
ID=6516225
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002165686A Abandoned CA2165686A1 (en) | 1994-04-22 | 1995-04-20 | Sealing arrangement for a spindle guided in an axially movable manner out of a housing |
Country Status (8)
| Country | Link |
|---|---|
| EP (1) | EP0705400A1 (en) |
| JP (1) | JPH08512396A (en) |
| KR (1) | KR960703215A (en) |
| CN (1) | CN1127545A (en) |
| BR (1) | BR9506215A (en) |
| CA (1) | CA2165686A1 (en) |
| DE (1) | DE4414174A1 (en) |
| WO (1) | WO1995029354A1 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB0004949D0 (en) | 2000-03-02 | 2000-04-19 | Needham David M | Fluid flow proportioning device |
| US8500740B2 (en) * | 2006-02-06 | 2013-08-06 | Conformis, Inc. | Patient-specific joint arthroplasty devices for ligament repair |
| EP1835206B1 (en) * | 2006-03-17 | 2011-04-06 | Carrara S.p.A. | A functional device, such as an on-off valve, provided with sealing means |
| CN108361435B (en) * | 2018-02-11 | 2019-07-19 | 江苏神通阀门股份有限公司 | A kind of application method of protective tooling that installing anti-fugacity filler |
| CN108167522B (en) * | 2018-02-11 | 2019-06-18 | 江苏神通阀门股份有限公司 | A kind of protective tooling for installing anti-fugacity filler |
| CN110195799B (en) * | 2019-06-18 | 2020-07-07 | 中国船舶科学研究中心（中国船舶重工集团公司第七0二研究所） | Automatic monitoring compensation and emergency device for valve rod sealing |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2484663A (en) * | 1946-11-01 | 1949-10-11 | Crane Co | Pressure sealed stuffing box |
| US3048412A (en) * | 1959-04-27 | 1962-08-07 | Union Oil Co | Shaft seal |
| CH652183A5 (en) * | 1981-08-24 | 1985-10-31 | Matkemi Ag | DEVICE WITH AN INTERIOR FOR A FLUID AND SEALANT AND USE OF THE DEVICE. |
| US4795171A (en) * | 1986-09-02 | 1989-01-03 | Federico Quevedo Del Rio | Self-pressurized shaft or closure seal |
| US4899899A (en) * | 1989-06-21 | 1990-02-13 | Triten Corporation | Pressure vessel |
-
1994
- 1994-04-22 DE DE4414174A patent/DE4414174A1/en not_active Withdrawn
-
1995
- 1995-04-20 BR BR9506215A patent/BR9506215A/en not_active Application Discontinuation
- 1995-04-20 EP EP95917344A patent/EP0705400A1/en not_active Withdrawn
- 1995-04-20 JP JP7527347A patent/JPH08512396A/en active Pending
- 1995-04-20 CA CA002165686A patent/CA2165686A1/en not_active Abandoned
- 1995-04-20 CN CN95190338A patent/CN1127545A/en active Pending
- 1995-04-20 KR KR1019950705835A patent/KR960703215A/en not_active Application Discontinuation
- 1995-04-20 WO PCT/EP1995/001487 patent/WO1995029354A1/en not_active Application Discontinuation
Also Published As
| Publication number | Publication date |
|---|---|
| DE4414174A1 (en) | 1995-10-26 |
| KR960703215A (en) | 1996-06-19 |
| CN1127545A (en) | 1996-07-24 |
| EP0705400A1 (en) | 1996-04-10 |
| BR9506215A (en) | 1997-09-30 |
| WO1995029354A1 (en) | 1995-11-02 |
| JPH08512396A (en) | 1996-12-24 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| FZDE | Dead |