GB1564826A - Creation of Inventions and Patents with Artificial Intelligence

GB1564826A – Bearing assemply
– Google Patents

GB1564826A – Bearing assemply
– Google Patents
Bearing assemply

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Publication number
GB1564826A

GB1564826A
GB39498/76A
GB3949876A
GB1564826A
GB 1564826 A
GB1564826 A
GB 1564826A
GB 39498/76 A
GB39498/76 A
GB 39498/76A
GB 3949876 A
GB3949876 A
GB 3949876A
GB 1564826 A
GB1564826 A
GB 1564826A
Authority
GB
United Kingdom
Prior art keywords
ring
oil
bush
shaft
chamber
Prior art date
1975-09-26
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

Application number
GB39498/76A
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)

Individual

Original Assignee
Individual
Priority date (The priority date 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 date listed.)
1975-09-26
Filing date
1976-09-23
Publication date
1980-04-16

1976-09-23
Application filed by Individual
filed
Critical
Individual

1980-04-16
Publication of GB1564826A
publication
Critical
patent/GB1564826A/en

Status
Expired
legal-status
Critical
Current

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Classifications

B—PERFORMING OPERATIONS; TRANSPORTING

B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT

B63H—MARINE PROPULSION OR STEERING

B63H23/00—Transmitting power from propulsion power plant to propulsive elements

B63H23/32—Other parts

B63H23/321—Bearings or seals specially adapted for propeller shafts

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

F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof

F16C33/02—Parts of sliding-contact bearings

F16C33/04—Brasses; Bushes; Linings

F16C33/06—Sliding surface mainly made of metal

F16C33/10—Construction relative to lubrication

F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant

F16C33/1045—Details of supply of the liquid to the 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

F16N—LUBRICATING

F16N7/00—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated

F16N7/14—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated the lubricant being conveyed from the reservoir by mechanical means

F16N7/16—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated the lubricant being conveyed from the reservoir by mechanical means the oil being carried up by a lifting device

F16N7/20—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated the lubricant being conveyed from the reservoir by mechanical means the oil being carried up by a lifting device with one or more members moving around the shaft to be lubricated

F16N7/22—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated the lubricant being conveyed from the reservoir by mechanical means the oil being carried up by a lifting device with one or more members moving around the shaft to be lubricated shaped as rings

B—PERFORMING OPERATIONS; TRANSPORTING

B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT

B63H—MARINE PROPULSION OR STEERING

B63H23/00—Transmitting power from propulsion power plant to propulsive elements

B63H23/32—Other parts

B63H23/321—Bearings or seals specially adapted for propeller shafts

B63H2023/322—Intermediate propeller shaft bearings, e.g. with provisions for shaft alignment

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

Description

(54) BEARING ASSEMBLY
(71) I, CHRISTIAN BERGMAN, of 22 Segebergerstrasse, 2061 Nahe, German
Federal Republic, a citizen of the German
Federal Republic, do hereby declare the invention, for which I pray that a patent may be granted to me, and the method by which it is to be performed, to be particularly described in and by the following statement: The present invention relates to a bearing assembly, and has particular reference to an arrangement for automatically supplying a shaft bearing with lubricant.
Journal bearing for journalling ship’s propeller shafts have to function reliably under harsh operating conditions. These requirements can only be met if a trouble-free supply of lubricant necessary for the maintenance of the fluid friction is delivered under all possible operating conditions, i.e. with motion of the sea, vibration, variable tilting of the longitudinal axis of the ship and, in the case of number of revolutions, from about 1 to a nominal speed of about 200 revolutions per minute. In particular, in order to deal with the case of the extremely low revolutions, which occur during the towing of ships fitted with fixed propellers due to the flow of water against the propeller, it is usual to lubricate such bearings by separate lubrication from a lubricant supply circuit located outside the bearing, it being necessary to provide an efficiently operating oil-return circuit. Since, in such systems, the oil reservoir is usually located close to the main engines but, on the other hand, the propeller shaft must be located deep down in the hull of the ship, there remains, particularly in the case of ships having their sterns lying lower in the water, little or no fall for the free return of the oil. Lubrication of this kind can therefore only be utilised, with reasonable cost and with safety of operation, in cases where the location of the bearing in the ship is favourable. Where such conditions do not apply, the supply of lubricant is dealt with throughout an additional circuit with an electrically driven pump. In this connection, known emergency systems are used to ensure operation is maintained, for example, by automatically switching of the pump to an emergency current supply in the event of cutting-out of the normal current supply or by switching on a second pump in the event of failure of the normal pump. Obviously, all these measures, though necessary, are associated with a high expenditure.
According to the present invention there is
provided a bearing assembly comprising a bearing bush for journalling a shaft, an oil collecting and dispensing ring, which extends around one end portion of the bush and through a trough for lubricant and which is adapted to be mounted on such shaft to rotate therewith, the ring being provided with a plurality of lubricant chambers, which are each provided in a side thereof defined by a wall of the ring facing the other end portion of the bush with at least one opening for the ingress and egress of lubricant and which are each closed at the remaining sides thereof, and a lubricant stripper block bearing under its own weight on the outer circumferential surface of the ring by means of a substantially planar bearing surface and having two stripper flanks inclined relative to each other and to the axis of the bush, the stripper flanks including an angle of at least 30 therebetween with the vertex of the angle being directed towards said other end portion of the bush.
In the usual construction of a journal bqar- ing with a fixed oil ring, the latter is usually located in a groove between two bushes and is constructed as an annular disc with smooth parallel sides which dip into an oil bath in the lower part of the bearing housing. When the shaft rotates, the oil wetting the sides and outer circumference of the ring is thus fed to a region above the shaft and is stripped off by a stripper, which is arranged at the uppermost point and which has the form of an edge at the bearing cap or a mounted “rider”.
Distinct disadvantages are associated with this construction: a) the volume of lubricating oil supplied at
low revolutions is dependent on viscosity
and temperature. Hence, the oil flows
straight back into the bearing sump
before it can be directed over the stripper
into the bearing, at a time when an in
creased feed for cooling is required.
b) With a fixed adjustment of the play of
the stripper, the same quantity of lubri
cating oil is passed on during low supply
volumes as during large supply volumes,
i.e. a smaller proportion is stripped off.
According to von Stribeck’s investigations (c.f. G. Vogelpohl “Safe-operating Journal
Bearing”), the friction value is dependent in a characteristic manner on the speed of sliding within the lubrication groove of the bearing.
Immediately the shaft starts to move and when low revolutions prevail, there occurs, due to the partial solid-body friction, a very high value of static friction accompanied by a drastic increase in the temperature in the lubrication groove. If insufficient oil is fed to the lubrication groove, the so-called transition rotational speed deviates from the theoretical range to higher revolutions (i.e. the region of pure fluid friction, in which the bearing operates safely, is curtailed), the unstable region of mixed friction becoming larger.
Bearing assemblies embodying the present invention may minimise the transitional rotational speed in the case of a bearing assembly having a fixed oil ring to such an extent that its application in the supporting of ships’ propeller shafts is made possible.
The advantage that may be obtained from bearing assemblies embodying the invention consists in that the providing of the bush with
a sufficient quantity of lubricant for the formation of a hydrodynamic lubricant-film independently of direction of rotation and without the aid of a separate lubrication is ensured
with an angle of turning of the shaft of less
than 1800.
Preferably said wall of the ring facing the
other end portion of the bush is provided with
an extension which extends radially inwardly
of a wall of the ring facing the outer circum
ference of the bush and defining a side of
each chamber adjacent such circumference.
For preference, the extension is interrupted
by a plurality of a radial slots.
With this arrangement, lubricant supplied to
the outer contours of the ring by adhesion is prevented from running back into the trough
at low rotational speeds or when the shaft is
stationary but, by a dripping-off process, also
contributes to the lubrication of the shaft.
In one convenient arrangement, the ring
comprises two radially spaced apart walls extending in the longitudinal direction of the
bush and around said one end portion of the bush and an insert member provided with a plurality of radial dividing elements arranged
between said two walls to partially define the
lubricant chambers, the insert member being
inserted between the walls from the ends there
of facing said other end portion of the bush.
Expediently, the insert member which may comprise thermoplastics material, is resiliently retained between the two radially spaced apart walls.
Preferably the insert member comprises wall portions remote from said ends of the two radially spaced apart walls, each wall portion partially defining a respective one of the chambers and each provided with a fold extending towards said ends of the two radially spaced apart walls to facilitate expansion and contraction of the insert member drcumferentially of the ring.
The insert member may comprise spaced flange portions adjacent said ends of the two radially spaced apart walls, the spacings between the flange portions providing the chamber openings and the flange portions extending radially inwardly of the inner one of the two radially spaced apart walls.
With the measures set forth so far, a sufficient supply of lubricant is guaranteed in the very low to middle range of revolutions. It fails, however, at higher revolutions, since filing of the chambers of the fixed ring can scarcely occur due to the shortness of their transit time through the trough and centrifugal force causes only partial emptying of the chambers. In this range, the supply of lubricant is ensured in a known manner by stripping off lubricant adhering to the outer surfaces of the ring, the lubricant being stripped off at the top of the ring. The stripper is constructed as a sliding stripper block floating on the cylindrical outer surface of the ring and having an approximately planar sliding surface. The advantage that may be obtained thereby consists in that the quantity of lubricant stripped off remains approximately constant independently of variatiou in the viscosity of the lubricant caused by temperature fluctuation, since, for example, with lowering of the viscosity due to increased temperature- i.e. reduced supply of the lubricant-the gap between the stripper block and the fixed ring is reduced, due to which the percentage amount of the quantity of stripped-off lubricant supplied to the shaft increases.
Embodiments of the present invention will now be more particularly described by way of example with reference to the accompanying drawings, in which:
Fig. 1 is a partly sectioned perspective view of a bearing assembly according to a first embodiment of the invention; and
Fig. 2 is a partly sectioned perspective – view of the oil ring of a bearing assembly according to a second embodiment of the invention.
Referring now to the drawings, there is shown in Fig. 1 a shaft 2, which passes through a bearing housing 1 having external seals 15 and a bush 13 and which carries a fixed oil ring 3. The ring 3 is fixedly attached to the shaft 2 and is arranged between one of the seals 15 and the bush 13, the cross-section of the ring being in the form of a ‘P’ supported on the shaft 2. An annular space 31 of the fixed oil ring, which space is disposed at a distance from the outer surface of the shaft and is concentric with the axis the shaft, is divided by radial dividing elements 39 into chambers 37, which are separate from one another and which are defined by a rim 38 laterally overhanging the bush 13. A side wall 34 of the chamber lying opposite to a side wall 33 connected to support pieces 32 has a number of openings 341 corresponding to the number of the chamber 37, the openings 341 having a vertical height corresponding to that of the chambers 37 and each being equidistant from the two adjacent elements 39. The side wall 34 is continued to form a drip rim 343, which is directed towards the shaft 2, slightly overlaps the bottom of the chambers 37, rotates above the outer surface 14 of the bush, and is interrupted by a plurality of radial cutouts 344. At the top of the bearing housing 1, there is located a stripper block 4 supported in a vertically yielding manner and having a sliding surface 41 floating on the outer surface 35 of the fixed oil ring 3. The sliding surface 41 is in the form of an isoscelles triangle with its apex pointing in the direction of the longitudinal axis of the shaft 2 and towards the bush 13.
In the interests of economical manufacture of the fixed oil ring, the cross-section of the ring can have the form of an ‘F’, as shown by the ring 50 in Fig. 2, which is supported with its limb 52 on the shaft 2 between an outer seal 15 and the bush and which overlaps the latter by its limb 56. Insert members 58, preferably of a flexible plastics material and manufactured by, for example, injection moulding, are inserted in a laterally open
U-shaped annular space 51 of the ring and are attached to one another and to the ring by glueing. As is apparent from Fig. 2, the insert members 58 form, by means comprising radial dividing elements 59, a plurality of chambers 57 which are separated from one another and which are closed apart from openings 541 facing the open side of the annular space 51 of the ring. An expansion fold 531 is arranged on a side wall 53 of each chamber 57 lying opposite to the openings 541, the folds permitting the insert member 58 to be adapted to the respective radius of curvature determined by the diameter of the annular space 51 of the ring and also enabling modification of the length of the chambers 57 to an integral sub – multiple of the circumference of the annular space 51. A drip rim 543 in the form of a flange portion corresponding to the drip rim 343 in Fig. 1, is attached to the element 59. The mode of operation of the bearing assembly hereinbefore described is as follows:
A portion of the circumference of the oil ring 3, which portion is located under the shaft 2, dips into an oil supply housed in the lower portion of the bearing housing so that the oil flows into the chambers 37 via the respective lateral openings 341 when below the oil level. During the course of the cycle of movement around the shaft of a chamber 37 located at the bottom of itz circumferential path, the chamber passes out of the oil supply with progressive rotation of the shaft. Due to increasing inclination of the chamber, the volume of oil contained therein collects in the rear part of the chamber in relation to the opening 341 and a part of the volume of oil flows back through the opening in consequence of the reduced holding capacity of this part of the chamber as compared with the whole of the chamber. On passing through the horizontal mid-section plane of the shaft 2, when the chamber is inclined at about 90 , the residual oil contained in the chamber (about a third of the original quantity when full) begins to run off, due to the “over-perpendicular” inclination of the chamber 37, after the shaft 2 has rotated through an angle of about 110′ The running-off of the oil continues until the chamber reaches the top of its path of rotation. Due to adhesion to the side wall 34, oil collects on the part of the drip rim 343 lying
below the opening 341 and provided with
cut-outs 344 for preventing the run-back of
oil into the oil reservoir, is passed on to the
upper half of the outer surface 14 of the bush 13, and is conducted by known means in the outer surface, such as grooves opening into guide channels leading to oil wells 131 located in the bearing surface of the bush 13. When the fixed oil ring 3 dips into the oil supply, an additional quantity of oil is, by adhesion to the outer surface 35 of the ring, also delivered to a region above the shaft 2, where it is stripped-off by the stripper block 4 at the top of the bearing housing 1 and conducted to the oil wells 131 via the side wall 34 and drip rim 343. At higher rotational speeds of the shaft 2, the latter oil supply takes over the lubrication of the journal bearing on its own, since filling of the chambers 37 no longer occurs due to the brevity of their passage through the oil supply.
WHAT I CLAIM IS:- 1. A bearing assembly, comprising a bearing bush for journalling a shaft, an oil collecting and dispensing ring, which extends around one end portion of the bush and through a trough for lubricant and which is adapted to be mounted on such shaft to rotate therewith, the ring being provided with a plurality of lubricant chambers, which are each provided in a side thereof defined by a wall of the ring facing the other end portion of the bush with at least one opening for the ingress and egress of lubricant and which are each closed at the remaining sides thereof, and a lubricant stripper block bearing under its own
**WARNING** end of DESC field may overlap start of CLMS **.

Claims (11)

**WARNING** start of CLMS field may overlap end of DESC **. seals 15 and the bush 13, the cross-section of the ring being in the form of a ‘P’ supported on the shaft 2. An annular space 31 of the fixed oil ring, which space is disposed at a distance from the outer surface of the shaft and is concentric with the axis the shaft, is divided by radial dividing elements 39 into chambers 37, which are separate from one another and which are defined by a rim 38 laterally overhanging the bush 13. A side wall 34 of the chamber lying opposite to a side wall 33 connected to support pieces 32 has a number of openings 341 corresponding to the number of the chamber 37, the openings 341 having a vertical height corresponding to that of the chambers 37 and each being equidistant from the two adjacent elements 39. The side wall 34 is continued to form a drip rim 343, which is directed towards the shaft 2, slightly overlaps the bottom of the chambers 37, rotates above the outer surface 14 of the bush, and is interrupted by a plurality of radial cutouts 344. At the top of the bearing housing 1, there is located a stripper block 4 supported in a vertically yielding manner and having a sliding surface 41 floating on the outer surface 35 of the fixed oil ring 3. The sliding surface 41 is in the form of an isoscelles triangle with its apex pointing in the direction of the longitudinal axis of the shaft 2 and towards the bush 13. In the interests of economical manufacture of the fixed oil ring, the cross-section of the ring can have the form of an ‘F’, as shown by the ring 50 in Fig. 2, which is supported with its limb 52 on the shaft 2 between an outer seal 15 and the bush and which overlaps the latter by its limb 56. Insert members 58, preferably of a flexible plastics material and manufactured by, for example, injection moulding, are inserted in a laterally open U-shaped annular space 51 of the ring and are attached to one another and to the ring by glueing. As is apparent from Fig. 2, the insert members 58 form, by means comprising radial dividing elements 59, a plurality of chambers 57 which are separated from one another and which are closed apart from openings 541 facing the open side of the annular space 51 of the ring. An expansion fold 531 is arranged on a side wall 53 of each chamber 57 lying opposite to the openings 541, the folds permitting the insert member 58 to be adapted to the respective radius of curvature determined by the diameter of the annular space 51 of the ring and also enabling modification of the length of the chambers 57 to an integral sub – multiple of the circumference of the annular space 51. A drip rim 543 in the form of a flange portion corresponding to the drip rim 343 in Fig. 1, is attached to the element 59. The mode of operation of the bearing assembly hereinbefore described is as follows: A portion of the circumference of the oil ring 3, which portion is located under the shaft 2, dips into an oil supply housed in the lower portion of the bearing housing so that the oil flows into the chambers 37 via the respective lateral openings 341 when below the oil level. During the course of the cycle of movement around the shaft of a chamber 37 located at the bottom of itz circumferential path, the chamber passes out of the oil supply with progressive rotation of the shaft. Due to increasing inclination of the chamber, the volume of oil contained therein collects in the rear part of the chamber in relation to the opening 341 and a part of the volume of oil flows back through the opening in consequence of the reduced holding capacity of this part of the chamber as compared with the whole of the chamber. On passing through the horizontal mid-section plane of the shaft 2, when the chamber is inclined at about 90 , the residual oil contained in the chamber (about a third of the original quantity when full) begins to run off, due to the “over-perpendicular” inclination of the chamber 37, after the shaft 2 has rotated through an angle of about 110′ The running-off of the oil continues until the chamber reaches the top of its path of rotation. Due to adhesion to the side wall 34, oil collects on the part of the drip rim 343 lying below the opening 341 and provided with cut-outs 344 for preventing the run-back of oil into the oil reservoir, is passed on to the upper half of the outer surface 14 of the bush 13, and is conducted by known means in the outer surface, such as grooves opening into guide channels leading to oil wells 131 located in the bearing surface of the bush 13. When the fixed oil ring 3 dips into the oil supply, an additional quantity of oil is, by adhesion to the outer surface 35 of the ring, also delivered to a region above the shaft 2, where it is stripped-off by the stripper block 4 at the top of the bearing housing 1 and conducted to the oil wells 131 via the side wall 34 and drip rim 343. At higher rotational speeds of the shaft 2, the latter oil supply takes over the lubrication of the journal bearing on its own, since filling of the chambers 37 no longer occurs due to the brevity of their passage through the oil supply. WHAT I CLAIM IS:-

1. A bearing assembly, comprising a bearing bush for journalling a shaft, an oil collecting and dispensing ring, which extends around one end portion of the bush and through a trough for lubricant and which is adapted to be mounted on such shaft to rotate therewith, the ring being provided with a plurality of lubricant chambers, which are each provided in a side thereof defined by a wall of the ring facing the other end portion of the bush with at least one opening for the ingress and egress of lubricant and which are each closed at the remaining sides thereof, and a lubricant stripper block bearing under its own
weight on the outer circumferential surface of the ring by means of a substantially planar bearing surface and having two stripper flanks inclined relative to each other and to the axis of the bush, the stripper flanks including an angle of at least 30 therebetween with the vertex of the angle being directed towards said other end portion of the bush.

2. An assembly as claimed in claim 1, wherein said wall of the ring facing the other end portion of the bush is provided with an extension which extends radially inwardly of a wall of the ring facing the outer circumference of the bush and defining a side of each chamber adjacent such circumference.

3. An assembly as claimed in claim 2, wherein the extension is interrupted by a pluralitv of a radial slots.

4. An assembly as claimed in claim 1, wherein the ring comprises two radially spaced apart walls extending in the longitudinal direction of the bush and around said one end portion of the bush and an insert member provided with a plurality of radial dividing elements arranged between said two walls to partially define the lubricant chambers, the insert member being inserted between the walls from the ends thereof facing said other end portion of the bush.

5. An assembly as claimed in claim 4, wherein the insert member is resiliently retained between the two radially spaced apart walls.

6. An assembly as claimed in either claim 4 or claim 5, wherein the insert member comprises plastics material.

7. An assembly as claimed in any one of claims 4 to 6, wherein the insert member comprises wall portions remote from said ends of the two radially spaced apart walls, each wall portion partially defining a respective one of the chambers and each provided with a fold extending towards said ends of the two radially spaced apart walls to facilitate expansion and contraction of the insert member circumferentially of the ring.

8. An assembly as claimed in any one of claims 4 to 7, wherein the insert member comprises spaced flange portions adjacent said ends of the two radially spaced apart walls, the spacings between the flange portions providing the chamber openings and the flange portions extending radially inwardly of the inner one of the two radially spaced apart walls.

9. An assembly as claimed in any one of the preceding claims, wherein the shaft is adapted to carry a propeller.

10. A bearing assembly substantially as hreinbefore described with reference to Fig. 1 of the accompanying drawings.

11. A bearing assembly substantially as hereinbefore described with reference to Fig. 2 of the accompanying drawings.

GB39498/76A
1975-09-26
1976-09-23
Bearing assemply

Expired

GB1564826A
(en)

Applications Claiming Priority (1)

Application Number
Priority Date
Filing Date
Title

DE2542947A

DE2542947C3
(en)

1975-09-26
1975-09-26

Solid lubricating ring designed as a hollow ring to supply a plain bearing with lubricant

Publications (1)

Publication Number
Publication Date

GB1564826A
true

GB1564826A
(en)

1980-04-16

Family
ID=5957507
Family Applications (1)

Application Number
Title
Priority Date
Filing Date

GB39498/76A
Expired

GB1564826A
(en)

1975-09-26
1976-09-23
Bearing assemply

Country Status (2)

Country
Link

DE
(1)

DE2542947C3
(en)

GB
(1)

GB1564826A
(en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party

Publication number
Priority date
Publication date
Assignee
Title

US4591024A
(en)

1984-03-19
1986-05-27
Dresser Industries, Inc.
Lube oil ring pump

DE19546974B4
(en)

1995-12-15
2011-08-11
Renk AG, 86159

radial bearings

DE10100470B4
(en)

2001-01-08
2008-02-28
A. Friedr. Flender Ag

Device for supplying a sliding bearing with oil

1975

1975-09-26
DE
DE2542947A
patent/DE2542947C3/en
not_active
Expired

1976

1976-09-23
GB
GB39498/76A
patent/GB1564826A/en
not_active
Expired

Also Published As

Publication number
Publication date

DE2542947C3
(en)

1979-05-17

DE2542947A1
(en)

1977-03-31

DE2542947B2
(en)

1978-09-21

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