CA1142206A - Self-aligning bearing - Google Patents
Self-aligning bearingInfo
- Publication number
- CA1142206A CA1142206A CA000353447A CA353447A CA1142206A CA 1142206 A CA1142206 A CA 1142206A CA 000353447 A CA000353447 A CA 000353447A CA 353447 A CA353447 A CA 353447A CA 1142206 A CA1142206 A CA 1142206A
- Authority
- CA
- Canada
- Prior art keywords
- bearing
- rotor
- axially directed
- pair
- strut members
- 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
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- Support Of The Bearing (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
In large turbine machines, it is critical to bearing performance that the turbine rotor remain aligned with the bearing surfaces. Misalignment can occur due to high thrust loads or thermal deformation. The object of the invention is to ensure correct rotor-bearing alignment under all operating conditions. The invention is a self-aligning bearing support structure capable of accommodating angular rotor misalignments. The bearing support structure includes a bearing casing which transfers axial loads or thrusts to the bearing standard through a yoke attached to the bearing casing and to the bearing standard by pairs of axially oriented flex struts. In combination with the axially oriented flex struts a transverse flex plate supports the bearing vertical load.
In large turbine machines, it is critical to bearing performance that the turbine rotor remain aligned with the bearing surfaces. Misalignment can occur due to high thrust loads or thermal deformation. The object of the invention is to ensure correct rotor-bearing alignment under all operating conditions. The invention is a self-aligning bearing support structure capable of accommodating angular rotor misalignments. The bearing support structure includes a bearing casing which transfers axial loads or thrusts to the bearing standard through a yoke attached to the bearing casing and to the bearing standard by pairs of axially oriented flex struts. In combination with the axially oriented flex struts a transverse flex plate supports the bearing vertical load.
Description
2 2 0 6 SELF-ALIGNING BEARING
Background of the Invention This invention relates to bearing supports for large, rotating shaft, turbomachines; and, in particular, is related to a self-al1gning journal-thrust bearing and bearing support.
Many kinds of machines have rotating shafts or rotors which ' can develop large axial thrust forces. Typically, a collar or runner on the shaft transmits the thrust load to a stationary thrust bearing.
One common type of thrust bearing is a tapered land thrust bearing, The bearing face is divided into several lands separated by radial oil supply grooves. These grooves have dams~at their outer ends and are supplied with oil under pressure to give controlled and pos~t~Ve oil feed to the lnlet edges of the lands. Each land is made with a fixed sloping bearing surface creating the hydrodynamic oil film wedge necessary to produce high thrust load carrying capability during operation. It is known that tapered land thrust bearings can with-.
stand very high l~oads when properly aligned. A small flat area at the trailing edge of each land is made parallel to the thrust runner to carry thrust loads~ when startlng or at low turnlng speeds, In a steam turbine, many thrust bearing fallures a~e related to misalign~qnt, often aggravated by high thrust loads due to water induction.~ Misalignment can occur when high thrust loads cause deformation and tilting of the stationary bearing pedestal or if the bearings suppor~ing the ~rotor move radially relative to each other due to dlfferential thermal expansion in the pedestals and foundations.
~:
; ~ 25 It is therefore~desirable to incorporate a self-aligning capabillty intQ a bearlng structure to allow the stationary thrust bearlng to conform to the orientatlon of the rotating thrust runner under operatl ng cond~tions. Equal or nearly equal loading on the various lands Qf the thrust bearing is thereby maintalned at all tlmes, - 1- 'q~
, . .
~ ~ .
l~Z~6 It 1s one object of the present invention to provide a bearing support structure capable of accommodat~ng angular rotor misalignments, It 1s another object of the invention to prov~de a bearing support structure which is very stiff in the axial and radial directions and reasonably flexible in a tilting mode to accom~odate angular misalignment in the rotor.
The novel features believed characteristic of the present invention are set forth in the appended claims. The invention itself~
however, together with further objects and advantages thereof? may best be understood with reference to the following descripticn taken in connection with the included drawings, Brief Descript~on of the Invention One application of the present invention to a large rotating~
shaft turbine machine occurs ~n a steam turbine. The turbine rotating shaft or rotor is formed with an enlarged thrust collar or wheel-llke portion perpend1cular to the axis of rotation whlch is called a thrust runner, The present invention is applied to a thrust-Journal bearing wherein axial movement or a resultant thrust in either axial direction of the rotor is transmitted to the thrust bearing, It is desirable and critical to ensure that the thrust runner surface be parallel to the thrust bearing face; i.e., the thrust runner surface must be in alignment with the thrust bearing face.
~The present invention is comprised of a bearing casing or bearing housing, an annular ring or yoke, axial strut members whlch act in pa~rs and a vertical flex plate. A first pair of axial strut members connect the bearing cas1ng to the yoke, A second pair of axial strut members connect the yoke to the bearing standard end wall.
The transverse flex plate is fixed to the floor of the bearing l~Z2~6 standard and is connected at its free end to the bearing casing.
The axial strut members may have rectangular crass-sections at their flexible portion. The first pair of axial s~ruts is oriented so that the mid-plane of the flexible portion lies in a vertical plane through the centerline af the rotor. The first pair of axial struts accommo-dates sideways angular misalignment. The second pair o~ axial struts is oriented so that the mid-plane of the flexible portion lies in a horizontal plane through the centerline of the rotor axis to accommo-date angular misalignment in the vertical plane. The transverse flex plate can twist and/or bend to accommodate any angular misalignment.
The bearing casing or housing is thus permitted to tilt ~:
vertically or horizontally which allows the bearing casing to follow?
to a limited extent, rotor angular misalignment in the horizont~l ~r vertical plane. Hence, the bearing self-aligns with the rotor $o thus satisfy~the object of the inventlon.
Brief DescriPtion of the Drawings FIGURE 1 is an isometric view partially sectioned and cut-away of a bearing standard, bearing support structure, a bearing casing and a portion of a turbine rotor.
FIGURE 2 is an elevation view of the bearing caslng and support.
FIGURE 3 is an elevation view of the bearing casing and bearing support showing rotor deflection frqm the horizontal plane.
FIGURE 4 is a plan view of the bearing casing and support means showing rotor deflection from the vertical plane.
Detailed Description of the Invention Figures 1 and 2 taken in combination show the construction of a bearing pedestal 11 in accordance with the present invention.
A baso plate or floor 13 supports the various bearing pedestal ~.
_3 llgLZ2[)6 elements, The bearing is partially enclosed by a bearing standard 17, a portion of which is shown in Figure 1. The bearing standard will provide support against thrust loadings transmltted by the bearing casing.
The bearing is used to support a rotor 21 a portion o~
which is shown in the drawing. The bearing functions to support the radial load of the rotor and axial thrust loads transmitted by the rotor in either direction. A thrust collar or runner 25 is for~ed on the rotor perpendicular to the axis of rotation for transmitting axjal thrust loads in either direction to the bearing casing 29. The bearing casing surrounds the rotor and is split along a horizontal iQint 31 for assembly purposes, The internal portion of the bearing casing lncludes stationary thrust bearing plates 33 for mainta~ning the axial pDsition of the rotor in either direction, Further, the bearing casing incl!Jdes a journal bearing 35. Thus the bearing casing shown is a combined journal and thrust bearing. While the present embodiment shows the thrust bearing surfaces straddling a single thrust runner and a journal bearing apart from that portion of the bearing, it is within the scope of the present invention to rearrange the bearing parts so as to 2~ include two thrust runners on the rotor at each end of the bear~nQ
casing which may have a journal bearing therebetween.
As is shown, perhaps more clearly in Figure 2, the bearing casing 29 may be for~ed with a pair of projections 41. These pro-iections provide attachment surfaces for one end of each of a pair of , 25 first axial flex struts 45. The "flex~ble" portions or areas of least cross-section of the flqx struts may have a rectangular cross-section so that the bend~ng stiffness is lower in the weak direction. The first pair of axial struts are also connected to a cross-member or yoke 47 which is positioned at one end of the bearing and which ls not !l ~
4~2~6 attached to the bearjng casing except through the f1rst pair of axlal struts. At rest, the yoke or r~ng central ax1s coincides approximately with the bearing casing central axis. The yoke need not be annular or even have a central aperture, The aperture merely allows the rotor to pass through the yoke whereas functionally the yoke could be a solid plate.
A second pair of axial struts 49 are provided approximately 90 away from the first pair of axial struts relative to their location on the yoke 47. Each axial strut is fixed to the Yoke at one lQ end and to the bearing standard 17 at the other end, Hence, the second pair of axial struts 49 transfer bearing loads to the bearing standard. The struts 49 may also be rectangular in cross-sect~on and are oriented to a110w bearing flexure from the horizontal plane.
Thus the first pair of axial struts 45 allows bending in the ~h~r1zontal plane (sideways) whereas the second pair of flex struts 49 allows bending ln the vertical plane (up and down).
The bearing casing is further supported by a trans~erse flex plate 51. The base of the flex plate is attached to the base plate 13. In the preferred embodiment o~ the invention the floxlble portlons of: flex struts 45 and 49 are centered ln the plane qf the ~i vertical transverse ~lex plate 51 so that the moment required to tilt the assembly is at a minimum. Stated in another way, the extended vertical plane of the flex plate cuts through the geometric center of the flexible portlon of the axial struts. Thus, in the preferred embodiment, in order to locate the flex1ble portlon of an axial strut (i.e., the dimension of reduced cross-section) extend the transverse plane to dissect the axlal struts. In addition, the flex plate ls located in a vertical plane which cuts approximately the mid-length of the journal bearing to minimke tiltlng due to radial loads.
1~4~Z~6 Figure 3 is similar to Figure 2 but shows the bearing casin~ tilting with respect to the X-X or horizontal axis. Since the flexure occurs out of the horizontal plane, axial struts 45 in the vertical plane will remain stiff and straight whereas axlal struts 49 (only one shown) will flex from the horizontal plane X-X.
In this case, the yoke 47 follows the movement of the bearing cas1ng 29 and flexure is taken up by the axial struts 49 and the vertical cross-wise flex plate 51. Vertical cross-wise flex plate ~1 will bend from the vertical planè Y-Y as shown in Figure 3.
Figure 4 is a plan view of the bearing structure with Y-Y
indicating a vertical plane. In the example shown, the rotor and bearing casing deflects from the vertical plane Y-Y due to rotor m~salignment. Note that axial struts 45 in the vertical plane will deflect from the vertical plane by bending whereas the axial struts 49 attached to the bearing standard 17 remain stiff and stra1ght.
This causes the yoke 47 to remain fixed relative to the bearing , . ~
standard. Flexure plate 51 will deflect by twisting as shown to ~i ~ accommodate bearing casing movement. It should be noted that in the ~ preferred embodiment shown in Figures 3 and 4, the axial Struts are ; 20 approximately located so that their flexure m~dpoints occur ~n the ; plane of the vertical support plate, ~ While there has been shown what is considered to be the preferred embodiment of the invention, other modifications may occur to those skilled in the art. Such modifications may include a rearrangement of the position of the thrust and journal bearing surfaces including thrust surfaces at either end of the bearing casing and the ~journal in-between. Also, the yoke need not actually be an annular structure if the rotor does not have to pass through ; the yoke. The bear1ng structure is also suitable for vertical shaft ~chines, ., I , . .
: ' ' ' ' . ! ;
''
Background of the Invention This invention relates to bearing supports for large, rotating shaft, turbomachines; and, in particular, is related to a self-al1gning journal-thrust bearing and bearing support.
Many kinds of machines have rotating shafts or rotors which ' can develop large axial thrust forces. Typically, a collar or runner on the shaft transmits the thrust load to a stationary thrust bearing.
One common type of thrust bearing is a tapered land thrust bearing, The bearing face is divided into several lands separated by radial oil supply grooves. These grooves have dams~at their outer ends and are supplied with oil under pressure to give controlled and pos~t~Ve oil feed to the lnlet edges of the lands. Each land is made with a fixed sloping bearing surface creating the hydrodynamic oil film wedge necessary to produce high thrust load carrying capability during operation. It is known that tapered land thrust bearings can with-.
stand very high l~oads when properly aligned. A small flat area at the trailing edge of each land is made parallel to the thrust runner to carry thrust loads~ when startlng or at low turnlng speeds, In a steam turbine, many thrust bearing fallures a~e related to misalign~qnt, often aggravated by high thrust loads due to water induction.~ Misalignment can occur when high thrust loads cause deformation and tilting of the stationary bearing pedestal or if the bearings suppor~ing the ~rotor move radially relative to each other due to dlfferential thermal expansion in the pedestals and foundations.
~:
; ~ 25 It is therefore~desirable to incorporate a self-aligning capabillty intQ a bearlng structure to allow the stationary thrust bearlng to conform to the orientatlon of the rotating thrust runner under operatl ng cond~tions. Equal or nearly equal loading on the various lands Qf the thrust bearing is thereby maintalned at all tlmes, - 1- 'q~
, . .
~ ~ .
l~Z~6 It 1s one object of the present invention to provide a bearing support structure capable of accommodat~ng angular rotor misalignments, It 1s another object of the invention to prov~de a bearing support structure which is very stiff in the axial and radial directions and reasonably flexible in a tilting mode to accom~odate angular misalignment in the rotor.
The novel features believed characteristic of the present invention are set forth in the appended claims. The invention itself~
however, together with further objects and advantages thereof? may best be understood with reference to the following descripticn taken in connection with the included drawings, Brief Descript~on of the Invention One application of the present invention to a large rotating~
shaft turbine machine occurs ~n a steam turbine. The turbine rotating shaft or rotor is formed with an enlarged thrust collar or wheel-llke portion perpend1cular to the axis of rotation whlch is called a thrust runner, The present invention is applied to a thrust-Journal bearing wherein axial movement or a resultant thrust in either axial direction of the rotor is transmitted to the thrust bearing, It is desirable and critical to ensure that the thrust runner surface be parallel to the thrust bearing face; i.e., the thrust runner surface must be in alignment with the thrust bearing face.
~The present invention is comprised of a bearing casing or bearing housing, an annular ring or yoke, axial strut members whlch act in pa~rs and a vertical flex plate. A first pair of axial strut members connect the bearing cas1ng to the yoke, A second pair of axial strut members connect the yoke to the bearing standard end wall.
The transverse flex plate is fixed to the floor of the bearing l~Z2~6 standard and is connected at its free end to the bearing casing.
The axial strut members may have rectangular crass-sections at their flexible portion. The first pair of axial s~ruts is oriented so that the mid-plane of the flexible portion lies in a vertical plane through the centerline af the rotor. The first pair of axial struts accommo-dates sideways angular misalignment. The second pair o~ axial struts is oriented so that the mid-plane of the flexible portion lies in a horizontal plane through the centerline of the rotor axis to accommo-date angular misalignment in the vertical plane. The transverse flex plate can twist and/or bend to accommodate any angular misalignment.
The bearing casing or housing is thus permitted to tilt ~:
vertically or horizontally which allows the bearing casing to follow?
to a limited extent, rotor angular misalignment in the horizont~l ~r vertical plane. Hence, the bearing self-aligns with the rotor $o thus satisfy~the object of the inventlon.
Brief DescriPtion of the Drawings FIGURE 1 is an isometric view partially sectioned and cut-away of a bearing standard, bearing support structure, a bearing casing and a portion of a turbine rotor.
FIGURE 2 is an elevation view of the bearing caslng and support.
FIGURE 3 is an elevation view of the bearing casing and bearing support showing rotor deflection frqm the horizontal plane.
FIGURE 4 is a plan view of the bearing casing and support means showing rotor deflection from the vertical plane.
Detailed Description of the Invention Figures 1 and 2 taken in combination show the construction of a bearing pedestal 11 in accordance with the present invention.
A baso plate or floor 13 supports the various bearing pedestal ~.
_3 llgLZ2[)6 elements, The bearing is partially enclosed by a bearing standard 17, a portion of which is shown in Figure 1. The bearing standard will provide support against thrust loadings transmltted by the bearing casing.
The bearing is used to support a rotor 21 a portion o~
which is shown in the drawing. The bearing functions to support the radial load of the rotor and axial thrust loads transmitted by the rotor in either direction. A thrust collar or runner 25 is for~ed on the rotor perpendicular to the axis of rotation for transmitting axjal thrust loads in either direction to the bearing casing 29. The bearing casing surrounds the rotor and is split along a horizontal iQint 31 for assembly purposes, The internal portion of the bearing casing lncludes stationary thrust bearing plates 33 for mainta~ning the axial pDsition of the rotor in either direction, Further, the bearing casing incl!Jdes a journal bearing 35. Thus the bearing casing shown is a combined journal and thrust bearing. While the present embodiment shows the thrust bearing surfaces straddling a single thrust runner and a journal bearing apart from that portion of the bearing, it is within the scope of the present invention to rearrange the bearing parts so as to 2~ include two thrust runners on the rotor at each end of the bear~nQ
casing which may have a journal bearing therebetween.
As is shown, perhaps more clearly in Figure 2, the bearing casing 29 may be for~ed with a pair of projections 41. These pro-iections provide attachment surfaces for one end of each of a pair of , 25 first axial flex struts 45. The "flex~ble" portions or areas of least cross-section of the flqx struts may have a rectangular cross-section so that the bend~ng stiffness is lower in the weak direction. The first pair of axial struts are also connected to a cross-member or yoke 47 which is positioned at one end of the bearing and which ls not !l ~
4~2~6 attached to the bearjng casing except through the f1rst pair of axlal struts. At rest, the yoke or r~ng central ax1s coincides approximately with the bearing casing central axis. The yoke need not be annular or even have a central aperture, The aperture merely allows the rotor to pass through the yoke whereas functionally the yoke could be a solid plate.
A second pair of axial struts 49 are provided approximately 90 away from the first pair of axial struts relative to their location on the yoke 47. Each axial strut is fixed to the Yoke at one lQ end and to the bearing standard 17 at the other end, Hence, the second pair of axial struts 49 transfer bearing loads to the bearing standard. The struts 49 may also be rectangular in cross-sect~on and are oriented to a110w bearing flexure from the horizontal plane.
Thus the first pair of axial struts 45 allows bending in the ~h~r1zontal plane (sideways) whereas the second pair of flex struts 49 allows bending ln the vertical plane (up and down).
The bearing casing is further supported by a trans~erse flex plate 51. The base of the flex plate is attached to the base plate 13. In the preferred embodiment o~ the invention the floxlble portlons of: flex struts 45 and 49 are centered ln the plane qf the ~i vertical transverse ~lex plate 51 so that the moment required to tilt the assembly is at a minimum. Stated in another way, the extended vertical plane of the flex plate cuts through the geometric center of the flexible portlon of the axial struts. Thus, in the preferred embodiment, in order to locate the flex1ble portlon of an axial strut (i.e., the dimension of reduced cross-section) extend the transverse plane to dissect the axlal struts. In addition, the flex plate ls located in a vertical plane which cuts approximately the mid-length of the journal bearing to minimke tiltlng due to radial loads.
1~4~Z~6 Figure 3 is similar to Figure 2 but shows the bearing casin~ tilting with respect to the X-X or horizontal axis. Since the flexure occurs out of the horizontal plane, axial struts 45 in the vertical plane will remain stiff and straight whereas axlal struts 49 (only one shown) will flex from the horizontal plane X-X.
In this case, the yoke 47 follows the movement of the bearing cas1ng 29 and flexure is taken up by the axial struts 49 and the vertical cross-wise flex plate 51. Vertical cross-wise flex plate ~1 will bend from the vertical planè Y-Y as shown in Figure 3.
Figure 4 is a plan view of the bearing structure with Y-Y
indicating a vertical plane. In the example shown, the rotor and bearing casing deflects from the vertical plane Y-Y due to rotor m~salignment. Note that axial struts 45 in the vertical plane will deflect from the vertical plane by bending whereas the axial struts 49 attached to the bearing standard 17 remain stiff and stra1ght.
This causes the yoke 47 to remain fixed relative to the bearing , . ~
standard. Flexure plate 51 will deflect by twisting as shown to ~i ~ accommodate bearing casing movement. It should be noted that in the ~ preferred embodiment shown in Figures 3 and 4, the axial Struts are ; 20 approximately located so that their flexure m~dpoints occur ~n the ; plane of the vertical support plate, ~ While there has been shown what is considered to be the preferred embodiment of the invention, other modifications may occur to those skilled in the art. Such modifications may include a rearrangement of the position of the thrust and journal bearing surfaces including thrust surfaces at either end of the bearing casing and the ~journal in-between. Also, the yoke need not actually be an annular structure if the rotor does not have to pass through ; the yoke. The bear1ng structure is also suitable for vertical shaft ~chines, ., I , . .
: ' ' ' ' . ! ;
''
Claims (9)
1. A self-aligning bearing structure for supporting a rotor comprising:
a bearing casing;
a yoke positioned at one end of the bearing casing and substantially aligned with the rotor axis or rotation;
a first pair of axially directed strut members connect-ing the bearing casing to the yoke; and, a second pair of axially directed strut members connecting the yoke to a support structure.
a bearing casing;
a yoke positioned at one end of the bearing casing and substantially aligned with the rotor axis or rotation;
a first pair of axially directed strut members connect-ing the bearing casing to the yoke; and, a second pair of axially directed strut members connecting the yoke to a support structure.
2. The bearing structure recited in claim 1 wherein each axially directed strut member has a rectangular cross section flexible portion, the cross section of the first pair of axially directed strut members being perpendicular to the cross section of the second pair of axially directed strut members.
3. The bearing structure recited in claim 2 wherein said first pair of axially directed strut members flex out of the vertical plane and the second pair of axially directed strut members flex out of the horizontal plane.
4. The bearing structure recited in claim 1 further comprising:
a base floor plate; and, a transverse flex plate mounted on the base floor plate and connected to the bearing casing, said flex plate being substantially perpendicular to the axially directed strut members and supporting the bearing casing.
a base floor plate; and, a transverse flex plate mounted on the base floor plate and connected to the bearing casing, said flex plate being substantially perpendicular to the axially directed strut members and supporting the bearing casing.
5. The bearing structure recited in claim 4 wherein each strut member has a reduced cross section flexible portion and the transverse flex plate is positioned approximately midway along the flexible portions of the strut members in the axial direction.
6. A bearing structure for supporting a rotor comprising:
a bearing casing surrounding a portion of said rotor;
a yoke positioned at one end of the bearing casing and substantially aligned with the rotor axis of rotation;
a first pair of axially directed strut members having a reduced cross section flexible portion which are flexible out of the vertical plane of the rotor connecting the bearing casing to the yoke;
a second pair of axially directed strut members having a reduced cross section flexible portion which are flexible out of the horizontal plane of the rotor connecting the yoke to a bearing standard mounted on a base floor plate;
and, a transverse flex plate supported by the bearing base floor plate and connected to the bearing casing.
a bearing casing surrounding a portion of said rotor;
a yoke positioned at one end of the bearing casing and substantially aligned with the rotor axis of rotation;
a first pair of axially directed strut members having a reduced cross section flexible portion which are flexible out of the vertical plane of the rotor connecting the bearing casing to the yoke;
a second pair of axially directed strut members having a reduced cross section flexible portion which are flexible out of the horizontal plane of the rotor connecting the yoke to a bearing standard mounted on a base floor plate;
and, a transverse flex plate supported by the bearing base floor plate and connected to the bearing casing.
7. The bearing structure recited in claim 6 wherein the bearing casing includes a journal bearing portion and said flex plate lies in a plane approximately perpendicular to the bearing casing and mid-way between the ends of the journal bearing.
8. A bearing support structure for a large rotating shaft machine comprising.
a bearing casing having an axial journal for accepting a rotor therethrough;
a substantially annular yoke positioned at one end of the bearing casing and substantially aligned with the rotor axis of rotation;
a bearing standard mounted on a base floor plate;
a first pair of axially directed strut members connect-ing the bearing casing to the yoke;
a second pair of axially directed strut members connecting the yoke to the bearing standard; and, a transverse flex plate mounted on the base floor plate and connected to the bearing casing supporting the bearing casing.
a bearing casing having an axial journal for accepting a rotor therethrough;
a substantially annular yoke positioned at one end of the bearing casing and substantially aligned with the rotor axis of rotation;
a bearing standard mounted on a base floor plate;
a first pair of axially directed strut members connect-ing the bearing casing to the yoke;
a second pair of axially directed strut members connecting the yoke to the bearing standard; and, a transverse flex plate mounted on the base floor plate and connected to the bearing casing supporting the bearing casing.
9. The bearing structure recited in claim 8 wherein each strut member has a reduced cross section flexible portion and the transverse flex plate lies in a vertical plane which intersects the midpoints of the flexible portions of the axially directed strut members.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000353447A CA1142206A (en) | 1980-06-05 | 1980-06-05 | Self-aligning bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000353447A CA1142206A (en) | 1980-06-05 | 1980-06-05 | Self-aligning bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1142206A true CA1142206A (en) | 1983-03-01 |
Family
ID=4117117
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000353447A Expired CA1142206A (en) | 1980-06-05 | 1980-06-05 | Self-aligning bearing |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1142206A (en) |
-
1980
- 1980-06-05 CA CA000353447A patent/CA1142206A/en not_active Expired
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |