CA1119008A - Seal for articulated joint connecting a long leg of a drilling and/or production platform to the associated spud tank - Google Patents
Seal for articulated joint connecting a long leg of a drilling and/or production platform to the associated spud tankInfo
- Publication number
- CA1119008A CA1119008A CA000352799A CA352799A CA1119008A CA 1119008 A CA1119008 A CA 1119008A CA 000352799 A CA000352799 A CA 000352799A CA 352799 A CA352799 A CA 352799A CA 1119008 A CA1119008 A CA 1119008A
- Authority
- CA
- Canada
- Prior art keywords
- ring
- seal
- bearing
- articulated joint
- retainer
- 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.)
- Expired
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63B—SHIPS OR OTHER WATERBORNE VESSELS; EQUIPMENT FOR SHIPPING
- B63B35/00—Vessels or similar floating structures specially adapted for specific purposes and not otherwise provided for
- B63B35/44—Floating buildings, stores, drilling platforms, or workshops, e.g. carrying water-oil separating devices
- B63B35/4406—Articulated towers, i.e. substantially floating structures comprising a slender tower-like hull anchored relative to the marine bed by means of a single articulation, e.g. using an articulated bearing
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C11/00—Pivots; Pivotal connections
- F16C11/04—Pivotal connections
- F16C11/06—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints
- F16C11/0666—Sealing means between the socket and the inner member shaft
- F16C11/0676—Sealing means between the socket and the inner member shaft allowing operational relative movement of joint parts due to sliding between parts of the sealing means
-
- 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
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
- F16J15/3208—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip provided with tension elements, e.g. elastic 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2326/00—Articles relating to transporting
- F16C2326/30—Ships, e.g. propelling shafts and bearings therefor
Abstract
ABSTRACT OF THE DISCLOSURE
A seal for an articulated joint connecting a long leg of a drilling or production platform to the associated spud tank, whereby even though the seal according to the invention is subjected to wear it will reliably prevent ingress of sea water, over a very long period of time. The seal according to the invention also prevents ingress of sea water transport of a platform, during setting up of the platform, and of course during operation of the platform standing in a sea bed. The water pressure encountered at relatively great depths is utilized to compensate for wear in the seals, and the sealing means automatically eliminate any accumulation of sand or the like at bearing points.
A seal for an articulated joint connecting a long leg of a drilling or production platform to the associated spud tank, whereby even though the seal according to the invention is subjected to wear it will reliably prevent ingress of sea water, over a very long period of time. The seal according to the invention also prevents ingress of sea water transport of a platform, during setting up of the platform, and of course during operation of the platform standing in a sea bed. The water pressure encountered at relatively great depths is utilized to compensate for wear in the seals, and the sealing means automatically eliminate any accumulation of sand or the like at bearing points.
Description
This invention relates to a seal for the articulated joint connecting a long leg of a drilling and/or production platform to an associated spud tank resting on the sea bed with the articulated joint being constructed in the form of a convex-surface inner ring supported on a horizontal knuckle pin and a concave-surface outer ring seated in a bearing eye of the bearing casing connected to the spud tank.
The spud tanks of an off-shore platform may be located at a maximum depth of approximately 500 m below sea level. In constructing the articulated joint in the form of a spherical knuckle bearing of the type initial Iy referred to on each spud tanl<, it is necessary to seal the spherical knuckle bearings to protect them from external influences. It is important in designing the seal to positively prevent the ingress of sea water both during transport of the platform afloat, during setting-up of the platform as well as during operation of the platform standing on the sea bed, it being important that the relatively long service life of the drilling and/or production platforms should be matched by a relatively long service life of the seals. It should also be borne in mind that - since the spherical knuckle bearings perform sl ight motions in several directions - the seals will wear in the course of time, requiring a seal design that will maintain the necessary sealing affect in spite of such wear over a long period of time.
The object of the invention is therefore to provide a long-life seal which will in all cases, even under conditions of wear in the seals, reliably prevent the ingress of sea water.
According to the invention, this object is achieved in that a casing cover is fitted on each side to the lateral surfaces of the bearing eye with a seal ring interposed in each case, and in that each casing cover is formed with a surface suitable to accommodate a grooved-ring seal with two sealing lips, and in that grooved-ring seals are provided which are capable of being preloaded to a preset value by a pressure ring~and screws associated on each 3r' side with the centre part of the seal, and in that the pressure ring is slidably -1- ~
~11900~3 uided in an outer retainer contacting the sealing lips and mating surfaces of the casing covers and an inner retainer contacting the surface of the inner ring of the spherical knuckle bearing and mating surfaces of the casing covers~
and in that each pressure ring is formed with a flange and in that compression springs are provided between each flange and the outer retainer and the inner retainer. The seal according to the invention enables the necessary safety to be obtained against the ingress of sea water also at increased water pressure into the spherical knuckle bearing during towing to the site, during erection afloat and during setting down on the sea bed. As the off-shore platform is set down on the sea bed, the water pressure increases according to the depth of the sea. As a result of this pressure of the sea water, the pressure ring which is capable of sliding inwards ;is continuously kept applied against the grooved-ring seal with a certain force. This continuous-existing application onto and/or adjustment of the grooved-ring seal due to the water pressure of the sea water on the areas to be sealed automatically compensates for any wear of the grooved~ring seal on the surface of the spherical knuckle bearing inner ring in the course of time.
Further features of the invention provide for the inner seal retainers to be formed with a relatively keen outer edge each as well as a peripheral groove on the sides thereof facing the inner ring of the spherical knuckle bearing. The relativelY keen outer edge will cause any particles (e. g. sand) that may be deposited on the surface of the inner ring of the spherical knuckle bearing to be scraped off as the spherical knuckle bearing rings perform relative motions. Should this edge become blunt in the course of time, any sand or similar deposits would be trapped in the peripheral groove.
A typical embodiment of the invention is schematically shown in the accompanying drawings in which:
Figure 1 shows the articulated joint connecting a leg to the spud tanks in section, without seals; and Y' Figure 2 is a section through half of the articulated joint according 111900~3 o Figure l, but with seals and on a larger scale.
An off-shore rig in the form of a drilling and/or production platform for great depths (approximately 350 to S00 m) is formed with three raked steel legs which are articulatedly connected to the associated spud tank.
At its bottom end, each leg has a forked part la, lb with coaxial openings 2 to accommodate a horizontal hol low knuckle pin 3. Mounted non-rotating on the knuckle pin 3 in the area between the fork arms 1a, 1b, there is an inner ring 4 with a concave spherical outer surface. Spacers 6 are provided between the inner ring 4 and the mating inner shoulders 5 on the fork arms 1a, 1b. The inner ring 4 is surrounded by an outer ring 7 having a convex spherical surface and which is arranged in a cyl indrical bore 8 located in a bearing eye 9 located between the fork arms, the bearing eye 9 forming part of a column or simi lar member extending downwards in the spud tank. The outer ring 7 and the bearing eye 9 are formed with a width which is smaller than the width of the inner ring 4. The outer ring 7, the inner ring 4 and the knuckle pin 3 form a cardanic universal joint permitting the spud tank to turn both about the axis of the knuckle pin 3 and about the verti-cal axis.
Arranged on each side of the bearing eye 9 forming the bearing casing for the outer ring 7 there is a casing cover 11 centered in the bore of the bearing casing. The casing covers 11, apart from their protective function, are designed to fix the axial position of the outer ring 7 in the bearing eye. The casing covers 11 are attached to the lateral surfaces of the bearing eye 9 by means of screws 13 spaced uniformly over its circumference with a gasket 12 made of copper, bronze or a similar material interposed.
The screws 13 are to be tightened firmly enough to prevent sea water ~rom penetrating at these points into the spherical knuckle bearing. The heads of the screws 13 are tlush in socket recesses lO in the casing covers ll. The recesses 10 are closed for protection against the ingress of sea water by a cover 14. Cavities between the tightened-down screws 13 and the covers 14 11~9008 lay be filled by a sealing compound, such as tar or similar materials, or any other appropriate sealant.
In addition, internal seals are provided in order to prevent the leakage, in particular, of sea water between the casing covers 11 and the convex surface of the inner ring 4 into the interior of the bearing. The internal seals are provided on both sides and are of identical construction.
Therefore, only one of the internal seals is described in the following.
Each internal seal is formed with a grooved=ring seal 15 having two sealing lips extending all round. By means of the side faces of the groove, the seal 15 extends over a flange 26 of the casing cover 11, and the sealing lips are designed to contact the appropriately shaped outer surfaces of the casing cover 11 and the surface of the inner ring 4 of the spherical knuckle bearing. The grooved-ring seal 15 is protected by an outer retainer 16~ an inner retainer 17 and a pressure ring 18 arranged between said rings against external influences. The inner retainer 17 bears on the inner ring 4 of the spherical knuckle bearing and is formed with a cylindrical outer ring surface. Slid on to the inner retainer 17 is the pressure ring 1`8 which, by means of screws 19, is attached to the flange 26. The screws 19 are tighten-ed only just enough to ensure that during towing of the floating drilling and/or production piatform or similar operations when a high water pressure is not yet acting on the seal, adequate sealing action is provided. The heads of the screws 19 are arranged in mating socket recesses in the pressure ring 18; the recesses are closed on the outside with a cover 20 each. The remaining cavity may be filled wjth an elastic sealant.
Between the pressure ring 18 and the casing cover 11, there is the outer retainer 16 which is guided by means of a corresponding obl ique outer surface on the mating oblique surface of the casing cover 11. The outer retainer and the inner retainer are formed with corresponding inner side faces which can be applied against the sealing lips. The pressure ring 18 is formed with a flange 22 on the outside which, when the seal is new, is at 1~19(:~08 reset distances from to the outer retainer 16 and the inner retainer 17.
Th~ outer and inner retainers are formed with socket recesses in which are housed compression springs 22 which, at their other end bear on the flange 22. Consequently, the pressure ring 18 is guided by the outer retainer and the inner retainer and axially slidable to the inside to some degree.
Sealing of the pressure ring 18 against the outer retainer 1~ and the inner retain0r 17 is effected by O-rings 23 which are arranged in mating ring grooves in the outer and inner retainers. The inner retainer 17 is formed on its outside facing the inner ring 4 with a keen edge and, on its side facing the spherical knuckle bearing inner ring 4 with a peripheral groove 25.
The casing covers 11, the pressure rings 18, the outer i-etainers 16, the inner retainers 17 and the compression springs 22 are made of sea-water-resistant materials, such as suitably stainless steel, bronze, copper or similar materials.
Since the preload of the screws 19 is designed to take into account only the water pressure existing during towing at sea or similar operations, the water pressure acting on the pressure ring outer surface at greater water depth will compress the seal to a greater degree whereby simultanouesly the screws 19 are relieved. As the sealing ring lips wear in the area of the spherical knuckle bearing inner ring 4, the permanently existing water pressure acting on the pressure ring outer surface wi l l provide automatic readjustment or matching of the sealing lips to the spherical knuckle bearing inner ring outer surface. In this process, an axial movement of the pressure ring 18 towards the inside may take place until the flange 22 of the pressure ring 18 contacts the outer retainer and inner retainer respectively.
: ,
The spud tanks of an off-shore platform may be located at a maximum depth of approximately 500 m below sea level. In constructing the articulated joint in the form of a spherical knuckle bearing of the type initial Iy referred to on each spud tanl<, it is necessary to seal the spherical knuckle bearings to protect them from external influences. It is important in designing the seal to positively prevent the ingress of sea water both during transport of the platform afloat, during setting-up of the platform as well as during operation of the platform standing on the sea bed, it being important that the relatively long service life of the drilling and/or production platforms should be matched by a relatively long service life of the seals. It should also be borne in mind that - since the spherical knuckle bearings perform sl ight motions in several directions - the seals will wear in the course of time, requiring a seal design that will maintain the necessary sealing affect in spite of such wear over a long period of time.
The object of the invention is therefore to provide a long-life seal which will in all cases, even under conditions of wear in the seals, reliably prevent the ingress of sea water.
According to the invention, this object is achieved in that a casing cover is fitted on each side to the lateral surfaces of the bearing eye with a seal ring interposed in each case, and in that each casing cover is formed with a surface suitable to accommodate a grooved-ring seal with two sealing lips, and in that grooved-ring seals are provided which are capable of being preloaded to a preset value by a pressure ring~and screws associated on each 3r' side with the centre part of the seal, and in that the pressure ring is slidably -1- ~
~11900~3 uided in an outer retainer contacting the sealing lips and mating surfaces of the casing covers and an inner retainer contacting the surface of the inner ring of the spherical knuckle bearing and mating surfaces of the casing covers~
and in that each pressure ring is formed with a flange and in that compression springs are provided between each flange and the outer retainer and the inner retainer. The seal according to the invention enables the necessary safety to be obtained against the ingress of sea water also at increased water pressure into the spherical knuckle bearing during towing to the site, during erection afloat and during setting down on the sea bed. As the off-shore platform is set down on the sea bed, the water pressure increases according to the depth of the sea. As a result of this pressure of the sea water, the pressure ring which is capable of sliding inwards ;is continuously kept applied against the grooved-ring seal with a certain force. This continuous-existing application onto and/or adjustment of the grooved-ring seal due to the water pressure of the sea water on the areas to be sealed automatically compensates for any wear of the grooved~ring seal on the surface of the spherical knuckle bearing inner ring in the course of time.
Further features of the invention provide for the inner seal retainers to be formed with a relatively keen outer edge each as well as a peripheral groove on the sides thereof facing the inner ring of the spherical knuckle bearing. The relativelY keen outer edge will cause any particles (e. g. sand) that may be deposited on the surface of the inner ring of the spherical knuckle bearing to be scraped off as the spherical knuckle bearing rings perform relative motions. Should this edge become blunt in the course of time, any sand or similar deposits would be trapped in the peripheral groove.
A typical embodiment of the invention is schematically shown in the accompanying drawings in which:
Figure 1 shows the articulated joint connecting a leg to the spud tanks in section, without seals; and Y' Figure 2 is a section through half of the articulated joint according 111900~3 o Figure l, but with seals and on a larger scale.
An off-shore rig in the form of a drilling and/or production platform for great depths (approximately 350 to S00 m) is formed with three raked steel legs which are articulatedly connected to the associated spud tank.
At its bottom end, each leg has a forked part la, lb with coaxial openings 2 to accommodate a horizontal hol low knuckle pin 3. Mounted non-rotating on the knuckle pin 3 in the area between the fork arms 1a, 1b, there is an inner ring 4 with a concave spherical outer surface. Spacers 6 are provided between the inner ring 4 and the mating inner shoulders 5 on the fork arms 1a, 1b. The inner ring 4 is surrounded by an outer ring 7 having a convex spherical surface and which is arranged in a cyl indrical bore 8 located in a bearing eye 9 located between the fork arms, the bearing eye 9 forming part of a column or simi lar member extending downwards in the spud tank. The outer ring 7 and the bearing eye 9 are formed with a width which is smaller than the width of the inner ring 4. The outer ring 7, the inner ring 4 and the knuckle pin 3 form a cardanic universal joint permitting the spud tank to turn both about the axis of the knuckle pin 3 and about the verti-cal axis.
Arranged on each side of the bearing eye 9 forming the bearing casing for the outer ring 7 there is a casing cover 11 centered in the bore of the bearing casing. The casing covers 11, apart from their protective function, are designed to fix the axial position of the outer ring 7 in the bearing eye. The casing covers 11 are attached to the lateral surfaces of the bearing eye 9 by means of screws 13 spaced uniformly over its circumference with a gasket 12 made of copper, bronze or a similar material interposed.
The screws 13 are to be tightened firmly enough to prevent sea water ~rom penetrating at these points into the spherical knuckle bearing. The heads of the screws 13 are tlush in socket recesses lO in the casing covers ll. The recesses 10 are closed for protection against the ingress of sea water by a cover 14. Cavities between the tightened-down screws 13 and the covers 14 11~9008 lay be filled by a sealing compound, such as tar or similar materials, or any other appropriate sealant.
In addition, internal seals are provided in order to prevent the leakage, in particular, of sea water between the casing covers 11 and the convex surface of the inner ring 4 into the interior of the bearing. The internal seals are provided on both sides and are of identical construction.
Therefore, only one of the internal seals is described in the following.
Each internal seal is formed with a grooved=ring seal 15 having two sealing lips extending all round. By means of the side faces of the groove, the seal 15 extends over a flange 26 of the casing cover 11, and the sealing lips are designed to contact the appropriately shaped outer surfaces of the casing cover 11 and the surface of the inner ring 4 of the spherical knuckle bearing. The grooved-ring seal 15 is protected by an outer retainer 16~ an inner retainer 17 and a pressure ring 18 arranged between said rings against external influences. The inner retainer 17 bears on the inner ring 4 of the spherical knuckle bearing and is formed with a cylindrical outer ring surface. Slid on to the inner retainer 17 is the pressure ring 1`8 which, by means of screws 19, is attached to the flange 26. The screws 19 are tighten-ed only just enough to ensure that during towing of the floating drilling and/or production piatform or similar operations when a high water pressure is not yet acting on the seal, adequate sealing action is provided. The heads of the screws 19 are arranged in mating socket recesses in the pressure ring 18; the recesses are closed on the outside with a cover 20 each. The remaining cavity may be filled wjth an elastic sealant.
Between the pressure ring 18 and the casing cover 11, there is the outer retainer 16 which is guided by means of a corresponding obl ique outer surface on the mating oblique surface of the casing cover 11. The outer retainer and the inner retainer are formed with corresponding inner side faces which can be applied against the sealing lips. The pressure ring 18 is formed with a flange 22 on the outside which, when the seal is new, is at 1~19(:~08 reset distances from to the outer retainer 16 and the inner retainer 17.
Th~ outer and inner retainers are formed with socket recesses in which are housed compression springs 22 which, at their other end bear on the flange 22. Consequently, the pressure ring 18 is guided by the outer retainer and the inner retainer and axially slidable to the inside to some degree.
Sealing of the pressure ring 18 against the outer retainer 1~ and the inner retain0r 17 is effected by O-rings 23 which are arranged in mating ring grooves in the outer and inner retainers. The inner retainer 17 is formed on its outside facing the inner ring 4 with a keen edge and, on its side facing the spherical knuckle bearing inner ring 4 with a peripheral groove 25.
The casing covers 11, the pressure rings 18, the outer i-etainers 16, the inner retainers 17 and the compression springs 22 are made of sea-water-resistant materials, such as suitably stainless steel, bronze, copper or similar materials.
Since the preload of the screws 19 is designed to take into account only the water pressure existing during towing at sea or similar operations, the water pressure acting on the pressure ring outer surface at greater water depth will compress the seal to a greater degree whereby simultanouesly the screws 19 are relieved. As the sealing ring lips wear in the area of the spherical knuckle bearing inner ring 4, the permanently existing water pressure acting on the pressure ring outer surface wi l l provide automatic readjustment or matching of the sealing lips to the spherical knuckle bearing inner ring outer surface. In this process, an axial movement of the pressure ring 18 towards the inside may take place until the flange 22 of the pressure ring 18 contacts the outer retainer and inner retainer respectively.
: ,
Claims (2)
1. A seal for an articulated joint connecting a long leg of a drilling and/or production platform to an associated spud tank designed to be stood on the sea bed with the articulated joint being constructed in the Form of a convex-shaped inner ring supported on a horizontal knuckle pin and a concave-shaped outer ring seated in a bearing eye of a bearing casing connect-ed to the spud tank, characterized in that a casing cover is attached on both sides to the sides of the bearing eye each with a sealing ring interposed and in that each casing cover is formed with a surface suitable to accept a grooved-ring seal having two sealing lips, and in that grooved-ring seals are provided which are capable of being preloaded via a pressure ring each and screws allied to the centre part of the seal to a predetermined value, and in that the pressure rings are slidably guided in an outer retainer contacting the sealing lip and a corresponding surface of the casing cover and an inner retainer contacting the surface of the inner ring of the spherical knuckle bearing and a corresponding surface of the casing cover, and in that each pressure ring is formed with a flange, and in that compression springs are provided between each flange and the outer retainer and the inner retainer.
2. A seal as in claim 1, characterized in that the inner retainers are each formed with a relatively keen outer edge and each with a peripheral groove on their side facing the inner ring of the spherical knuckle bearing.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DEP2922575.0 | 1979-06-02 | ||
| DE19792922575 DE2922575A1 (en) | 1979-06-02 | 1979-06-02 | SEALING FOR AN ARTICULATED CONNECTION OF A LONG LEG OF A DRILLING AND / OR PRODUCTION PLATFORM TO THE ASSOCIATED BASE BODY |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1119008A true CA1119008A (en) | 1982-03-02 |
Family
ID=6072377
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000352799A Expired CA1119008A (en) | 1979-06-02 | 1980-05-27 | Seal for articulated joint connecting a long leg of a drilling and/or production platform to the associated spud tank |
Country Status (7)
| Country | Link |
|---|---|
| JP (1) | JPS5628920A (en) |
| CA (1) | CA1119008A (en) |
| DE (1) | DE2922575A1 (en) |
| FR (1) | FR2458011A1 (en) |
| GB (1) | GB2055990A (en) |
| NL (1) | NL8003211A (en) |
| NO (1) | NO801624L (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104141793A (en) * | 2014-07-29 | 2014-11-12 | 中国船舶重工集团公司第七0四研究所 | Bay sealing device with angular displacement compensation function |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105485158A (en) * | 2015-10-13 | 2016-04-13 | 常州市武进顶峰铜业有限公司 | Self-lubricating bearing |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR1480754A (en) * | 1965-05-24 | 1967-05-12 | Ball joint, in particular for steering linkages and axle guiding members of motor vehicles | |
| FR1519891A (en) * | 1967-02-24 | 1968-04-05 | Entpr D Equipements Mecaniques | Improvements to structures such as platforms for underwater work |
| GB1565648A (en) * | 1975-09-02 | 1980-04-23 | Massey Ferguson Services Nv | Joints |
| US4034996A (en) * | 1975-10-08 | 1977-07-12 | Saitamakiki Co., Ltd. | Ball joint for torque rod |
-
1979
- 1979-06-02 DE DE19792922575 patent/DE2922575A1/en not_active Ceased
-
1980
- 1980-05-27 CA CA000352799A patent/CA1119008A/en not_active Expired
- 1980-05-28 FR FR8011774A patent/FR2458011A1/en not_active Withdrawn
- 1980-05-30 NO NO801624A patent/NO801624L/en unknown
- 1980-05-30 JP JP7264880A patent/JPS5628920A/en active Pending
- 1980-06-02 NL NL8003211A patent/NL8003211A/en not_active Application Discontinuation
- 1980-06-02 GB GB8018013A patent/GB2055990A/en not_active Withdrawn
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104141793A (en) * | 2014-07-29 | 2014-11-12 | 中国船舶重工集团公司第七0四研究所 | Bay sealing device with angular displacement compensation function |
Also Published As
| Publication number | Publication date |
|---|---|
| NO801624L (en) | 1980-12-03 |
| JPS5628920A (en) | 1981-03-23 |
| NL8003211A (en) | 1980-12-04 |
| GB2055990A (en) | 1981-03-11 |
| DE2922575A1 (en) | 1980-12-11 |
| FR2458011A1 (en) | 1980-12-26 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |