CN211501307U - Double-wedge antifriction bearing bush upper rudder bearing - Google Patents

Abstract

The utility model discloses a double-wedge antifriction bearing bush upper rudder bearing, including rudder bearing body and rudder bearing frame, be provided with outer loop double wedge oil groove and inner ring double wedge oil groove in the quotation of axial bearing bush, outer loop double wedge oil groove and inner ring double wedge oil groove are the arc wall, each section inside, outer loop double wedge oil groove mutual interval sets up and be in on the same circumference outer loop double wedge oil groove depth increase from the groove intermediate position to groove both ends and form the wedge oil groove continuously, be provided with the outer loop oilhole in the middle of this outer loop double wedge oil groove, inner ring double wedge oil groove depth increase from the groove intermediate position to groove both ends also form the wedge oil groove continuously, be provided with the inner ring oilhole in the middle of this inner ring double wedge oil groove, the inner ring oilhole is linked together with radial bearing bush oil feed nozzle; radial bearing shell oil grooves are formed in the radial bearing shells, the radial bearing shell oil grooves located on the same circumference are arranged at intervals, and the radial bearing shell oil grooves on the two adjacent circumferences are arranged in a staggered mode. The rudder bearing on the double-wedge antifriction bearing bush can form a stable lubricating oil film, so that dry friction is effectively avoided.

Description

Double-wedge antifriction bearing bush upper rudder bearing

Technical Field

The utility model relates to a rudderstock rudder bearing in the boats and ships rudder system especially relates to the improvement that is used for rudder bearing structure on large-tonnage boats and ships plane friction formula.

Background

The rudder bearing is an important device in the rudder system of the ship, and the rudder bearing bears the axial and radial loads from the rudder stock and the rudder blade so as to ensure that the rudder blade rotates left and right along with the rudder stock, thereby forcing the ship to change the course or keep straight sailing. Usually the rudder stock is supported by two rudder bearings; the upper rudder bearing is positioned at the upper end of the rudder stock.

The existing upper rudder bearing mainly comprises a rudder bearing frame fixedly arranged on a rudder stock and a rudder bearing body for slidably supporting the rudder bearing frame, wherein a window communicated with the outside is arranged in the middle of the rudder bearing body, watertight packing is filled between an inner hole in the lower part of the window of the rudder body and the rudder stock, and a packing gland is arranged above the watertight packing. Between the rudder carrier and the rudder carrier body, a planar sliding bearing shell is provided, by means of which the rudder carrier and its rudder stock are rotatably supported on the upper end face of the rudder carrier body, so that essentially the rudder carrier is an axial sliding bearing for supporting the rudder stock and maintaining the rotation.

Along with the continuous emergence of large-tonnage freight ships, the weight of parts for controlling ship rudder systems is increased. The upper rudder bearing product manufactured according to the existing ship industry standard 'plane friction watertight upper rudder bearing' has a plurality of defects when being applied to large-tonnage ships. Firstly, the existing upper stern bearing structure is deviated from supporting the axial force of the rudder bearing, the radial support of a rudder stock is neglected, the weight of a huge rudder system part such as the rudder stock is completely supported on the sliding surface of an axial bearing bush, on one hand, due to the increase of the axial force and the deterioration of the lubrication condition of the axial sliding surface, dry friction between the sliding surfaces is easily formed, the rotation load of the rudder stock is increased, the flexibility is reduced, the abrasion is serious, the service life is shortened, and even the gluing of the bearing bush and the rudder bearing body is formed. On the other hand, due to the vibration of the rudder stock and the shaking of the center of the rudder stock, the unbalance load of the axial bearing bush is formed, the local overload of the sliding surface is formed, the lubricating oil film is damaged, the galling and the corrosion between the axial bearing bush and the rudder body are caused, the sliding surface of the bearing bush is formed into small blocks which are peeled off to generate cavitation corrosion damage, and the stability of the operation of the rudder bearing is directly influenced and the service life of the rudder bearing is directly prolonged.

Chinese utility model patent ZL201820763504.2 discloses a rudder bearing on "multidirectional lubricated flat-grinding formula", it is through the friction disc between rudder bearing body and gland, and the axle sleeve between rudderstock and the rudder bearing main part bears axial force and radial force respectively, the atress situation of going up the rudder bearing has been improved effectively, still do not improve lubricated situation effectively, because lubricating oil hardly enters into on the friction glide plane of friction disc and axle sleeve, even lubricating oil enters into on above-mentioned axial and radial glide plane, lubrication inadequately also can appear, or hardly form the lubricating oil film, lead to the dry friction between the glide plane, produce to gnaw at revolute pair department and lose the damage, aggravate revolute the wearing and tearing of revolute pair, seriously influence the life of upper rudder bearing.

SUMMERY OF THE UTILITY MODEL

The above-mentioned not enough to prior art exists, the utility model aims to solve the technical problem that a rudder bearing on double wedge antifriction axle bush that can form stable lubricating oil film, effectively avoid dry friction is provided.

In order to solve the technical problem, the double-wedge antifriction bearing bush upper rudder bearing of the utility model comprises a rudder bearing body and a rudder bearing frame, wherein an axial bearing bush is arranged between the rudder bearing frame and the rudder bearing body, the axial bearing bush is of a disc-shaped structure, a radial bearing bush is arranged in a rudder stock hole of the rudder bearing body, the radial bearing bush is of a cylindrical structure, an outer ring double-wedge oil groove and an inner ring double-wedge oil groove are arranged on the disc surface of the axial bearing bush, the outer ring double-wedge oil groove and the inner ring double-wedge oil groove are both oil groove arc grooves, the outer ring double-wedge oil grooves of all sections are arranged at intervals and are positioned on the same circumference, and the inner ring double-wedge oil grooves of all sections are arranged at; the groove depth of the outer ring double-wedge oil groove is continuously increased from the middle position of the groove to the two ends of the groove to form a wedge-shaped oil groove, an outer ring oil hole is arranged in the middle of the outer ring double-wedge oil groove, and the outer ring oil hole is communicated with a radial bearing bush oil supply nozzle; the groove depth of the inner ring double-wedge oil groove is continuously increased from the middle position of the groove to the two ends of the groove to form a wedge-shaped oil groove, an inner ring oil hole is formed in the middle of the inner ring double-wedge oil groove, and the inner ring oil hole is communicated with a radial bearing bush oil supply nozzle; radial bearing shell oil grooves are formed in the radial bearing shells, the radial bearing shell oil grooves located on the same circumference are arranged at intervals, and the radial bearing shell oil grooves on two adjacent circumferences are arranged in a staggered mode.

After the structure is adopted, the axial bearing bush and the radial bearing bush are fixedly arranged on the rudder bearing body, the axial bearing bush bears the whole weight of rudder system devices such as a rudder stock and the like, the flexible rotation of the rudder stock is ensured, the radial bearing bush bears the radial force generated by the shaking and deflection of parts such as the rudder stock and the like, the contact stress concentration on the bearing sliding surface and the abnormal increase of local contact load are avoided, therefore, the axial bearing bush bears the pure axial force in the structure, the radial bearing bush bears the pure radial force, the structure not only enables the axial bearing and the radial bearing of the bearing to become stable and reliable, but also enables the comprehensive bearing capacity and the fatigue life of the bearing to be obviously improved. Because the disk surface of the axial bearing bush is provided with two circles of outer ring double-wedge oil grooves and inner ring double-wedge oil grooves, the outer ring double-wedge oil grooves or the inner ring double-wedge oil grooves on each section of the circumference are all triangular wedge oil grooves formed by continuously increasing from the middle position of the groove to the two ends of the groove, when the rudder stock swings in the positive direction or the negative direction, the lubricating oil on the disk surface of the axial bearing bush always decreases from the middle of the groove to the oil flow channel on one side and increases to the oil flow channel on the other side, so that the lubricating oil in the oil groove on the decreased side is squeezed to generate oil pressure, the oil pressure enables a gap to be generated between the sliding surface of the axial bearing bush and the rudder bearing frame to contain the lubricating oil to form an oil film, the oil groove on the increased side can generate negative pressure at the deep end of the groove to generate oil absorption effect, the oil pressure at the shallow, the continuous oil suction and pumping functions are formed, so that a stable and continuous lubricating oil film is generated, the two metal surfaces of the axial bearing bush and the rudder carrier are separated from each other, the dry friction generated by the direct contact of metal materials is avoided, the lubricating condition is effectively improved, and the friction damage of the sliding surface is greatly reduced. And because the radial bearing bush is provided with a plurality of radial oil grooves which are arranged at intervals, and two adjacent radial bearing bush oil grooves are arranged in a staggered manner, the uniform distribution of a lubricating oil film on the radial bearing bush is effectively improved, so that a uniform and thin oil film is formed on the sliding surface of the radial bearing bush and the rudder carrier rod, and the dry friction and the corrosion biting phenomenon on the sliding surface are avoided.

The utility model discloses a preferred embodiment, axial axle bush fixed mounting is on the rudder bearing body, and this axial axle bush place plane is mutually perpendicular with the central line of radial axle bush. The outer ring double-wedge oil groove and the inner ring double-wedge oil groove are positioned on two concentric circumferences. The central angle alpha of the outer ring double-wedge oil groove is = 80-100 degrees, and the central angle beta of the inner ring double-wedge oil groove is = 80-100 degrees. The outer ring double-wedge oil grooves and the inner ring double-wedge oil grooves which are respectively positioned on different circumferences are arranged on the axial bearing bush in a staggered mode. The structure is beneficial to generating a more uniform and stable lubricating oil film on the disc surface of the axial bearing bush, and a reliable lubricating working condition is formed.

The utility model discloses a preferred embodiment, radial axle bush oil groove distributes on 2-6 circumferences of radial axle bush internal face, and radial axle bush oil groove staggered arrangement on the adjacent twice circumference. The central angle gamma of the radial bearing shell oil groove is = 80-100 degrees. And an oil groove oil hole is formed in the radial bearing bush oil groove and communicated with the axial bearing bush oil supply nozzle. The method is favorable for forming a uniform and stable lubricating oil film on the sliding surfaces of the radial bearing bush and the rudder stock, and enhances the reliability of lubricating conditions.

The utility model discloses a further embodiment, rudder bearing frame, rudder bearing body, axial axle bush and radial axle bush all adopt the subdivision structure. Is convenient for manufacturing and installation.

Drawings

The present invention will be further explained with reference to the attached drawings and the following detailed description.

FIG. 1 is a schematic cross-sectional view of one embodiment of a rudder bearing on a double-wedge antifriction bearing shell according to the present invention;

FIG. 2 is a schematic structural view of the embodiment shown in FIG. 1 in the axial bearing disk surface direction;

FIG. 3 is a schematic cross-sectional view of the outer ring dual wedge oil groove of the configuration shown in FIG. 2;

FIG. 4 is a schematic cross-sectional view of the inner ring dual wedge oil groove of the configuration of FIG. 2;

FIG. 5 is a schematic cross-sectional view of the radial bearing shell of the embodiment of FIG. 1;

fig. 6 is a sectional view a-a of the structure shown in fig. 5.

In the figure, 1-rudder carrier, 2-axial bearing bush, 3-oil baffle, 4-rudder stock liner, 5-radial bearing bush, 6-rudder stock seal, 7-seal gland, 8-rudder stock, 9-axial bearing bush oil supply nozzle, 10-adjusting washer, 11-deck, 12-rudder carrier body, 13-radial bearing bush oil supply nozzle, 14-outer ring double wedge oil groove, 15-outer ring oil hole, 16-inner ring double wedge oil groove, 17-inner ring oil hole, 18-radial axial oil groove, 19-oil groove oil hole.

Detailed Description

As shown in figure 1, the rudder bearing on the double-wedge antifriction bearing bush is characterized in that a rudder bearing body 12 is arranged on a deck 11 through an adjusting washer 10, the adjusting washer 10 is a circular steel ring, the field installation and debugging of the rudder bearing can be realized through the adjusting washer 10, and the improvement of the installation efficiency is facilitated. The rudder carrier body 12 is of a split structure, and the two half bodies are fixedly connected with each other through hinged bolts and sleeved on the rudder stock 8. A radial bearing bush 5 is fixedly arranged on the hole wall of the central hole of the rudder stock body 12 through a sunk screw, and the radial bearing bush 5 also adopts a split structure. The rudder stock 8 is fixedly and tightly sleeved with a rudder stock lining 4, and the radial bearing bush 5 is slidably sleeved on the rudder stock lining 4, so that the structure is favorable for protecting the rudder stock 8 from being abraded.

A rudder stock seal 6 and a seal cover 7 are provided at the lower port of the rudder stock body 12, the rudder stock seal 6 is a common lip seal, and the seal cover 7 is mounted on the rudder stock body 12 by bolts. The sealing gland 7 also adopts a split structure, and two half bodies of the sealing gland 7 are connected through corresponding connecting bolts. The axial bearing bush 2 is fixedly arranged on the rudder bearing body 12, and the plane of the axial bearing bush 2 is vertical to the central line of the radial bearing bush 5.

The rotatable rudder carrier 1 is arranged above the rudder stock body 12, and the rudder carrier 1 adopts a split structure and is fixedly clamped on the rudder stock 8 through a hinged bolt. And a limit block is arranged on the rudder stock 8 on the rudder carrier 1. An axial bearing bush 2 is arranged between the rudder stock body 12 and the rudder carrier 1, the axial bearing bush 2 is fixedly connected to the rudder stock body 12 by means of a corresponding countersunk head screw, and the rudder carrier 1 is supported on the axial bearing bush 2 in a sliding manner. The oil baffle plate 3 is arranged on the periphery of the rudder carrier 1 to prevent external impurities and dust from falling into the sliding surface, thereby avoiding aggravating the abrasion to parts. The rudder bearing frame 1, the rudder bearing body 12, the axial bearing bush 2 and the radial bearing bush 5 all adopt split structures. The axial bearing bush 2 and the radial bearing bush 5 are made of nonmetal materials such as polytetrafluoroethylene, modified polyformaldehyde and nylon, and can also be made of bearing bush alloy, powder metallurgy and other materials.

In the axial bush 2 shown in fig. 2, a central circular hole is provided at the center of the disc-shaped axial bush 2. The disc surface of the axial bearing bush 2 is provided with 4 sections of outer ring double wedge oil grooves 14 and 4 sections of inner ring double wedge oil grooves 16, the outer ring double wedge oil grooves 14 and the inner ring double wedge oil grooves 16 are arc-shaped grooves, the central angle α =90 ° of each section of outer ring double wedge oil grooves 14, and the central angle β =90 ° of each section of inner ring double wedge oil grooves 16. The 4-segment outer ring double wedge oil groove 14 is positioned on the same circumference, and the 4-segment inner ring double wedge oil groove 16 is positioned on the other circumference, wherein the two circumferences are two concentric circles. The outer ring double wedge oil grooves 14 and the inner ring double wedge oil grooves 16 which are positioned on two different circumferences are respectively positioned in different circle center angle areas of the disc surface of the axial bearing bush 2, so that the outer ring double wedge oil grooves 14 and the inner ring double wedge oil grooves 16 are arranged in a staggered mode.

As shown in fig. 3, the groove depth of the outer ring double wedge oil groove 14 is gradually and continuously increased from the groove middle position to both ends of the groove to form a triangular wedge-shaped oil groove, an outer ring oil hole 15 is provided at the highest middle position of the outer ring double wedge oil groove 14, the outer ring oil hole 15 is communicated with the radial pad oil supply nipple 13 through an oil filling hole passage, and the radial pad oil supply nipple 13 is attached to the rudder carrier body 12. As shown in fig. 4, the groove depth of the inner ring double wedge oil groove 16 gradually and continuously increases from the groove middle position to the two ends of the groove to form a triangular wedge oil groove, an outer ring oil hole 17 is provided at the highest middle position of the inner ring double wedge oil groove 16, and the outer ring oil hole 17 is also communicated with the radial bearing oil supply nozzle 13 through an oil filling hole passage.

As shown in fig. 5 and 6, the radial bearing shell 5 is of a partial structure, and the radial bearing shell 5 is formed by combining two semi-radial bearing shells. The radial bearing bush 5 is fixedly arranged in a corresponding hole of the rudder bearing body 12 through a screw. Radial bearing bush oil grooves 18 are respectively arranged on 3 circles of the inner cylinder wall of the radial bearing bush 5, 4 sections of radial bearing bush oil grooves 18 are respectively arranged on each circle, an oil groove oil hole 19 is arranged in the middle of each radial bearing bush oil groove 18, the oil groove oil hole 19 is communicated with an axial bearing bush oil supply nozzle 9 through a pore channel, and the axial bearing bush oil supply nozzle 9 is installed on the rudder bearing body 12. The corresponding central angle γ =90 ° of each radial bearing shell oil groove 18. The radial bearing oil grooves 18 on two adjacent circles are respectively positioned on the corresponding cylindrical surfaces of different central angles to form a staggered arrangement structure.

The foregoing has outlined a preferred embodiment of the present invention but the invention is not limited thereto and various modifications and changes may be made without departing from the basic concept thereof. If the central angle of the outer ring double-wedge oil groove is not limited to 90 degrees, the central angle alpha of the outer ring double-wedge oil groove can be preferably 80-100 degrees, and the central angle of the inner ring double-wedge oil groove is also not limited to 90 degrees, and the central angle beta of the inner ring double-wedge oil groove can be preferably 80-100 degrees; the central angle of the radial bearing oil groove is not limited to 90 degrees, and the central angle gamma of the radial bearing oil groove can be preferably 80-100 degrees; radial axle bush oil groove can distribute on 2-6 circumferences of radial axle bush internal face, etc. and these alternations all fall into the utility model discloses an in the protection scope.

Claims (9)

1. The utility model provides a rudder bearing on double wedge antifriction bearing shell, includes rudder bearing body (12) and rudder bearing frame (1), is provided with axial axle bush (2) between rudder bearing frame (1) and rudder bearing body (12), and this axial axle bush (2) are discoid structure, installs radial axle bush (5) in the rudder stock hole of rudder bearing body (12), and this radial axle bush (5) are the tubular structure, its characterized in that: an outer ring double-wedge oil groove (14) and an inner ring double-wedge oil groove (16) are arranged on the disc surface of the axial bearing bush (2), the outer ring double-wedge oil groove (14) and the inner ring double-wedge oil groove (16) are arc-shaped grooves, the outer ring double-wedge oil grooves (14) of all sections are arranged at intervals and are positioned on the same circumference, and the inner ring double-wedge oil grooves (16) of all sections are arranged at intervals and are also positioned on the same circumference; the groove depth of the outer ring double-wedge oil groove (14) is continuously increased from the middle position of the groove to the two ends of the groove to form a wedge-shaped oil groove, an outer ring oil hole (15) is formed in the middle of the outer ring double-wedge oil groove (14), and the outer ring oil hole (15) is communicated with a radial bearing bush oil supply nozzle (13); the groove depth of the inner ring double-wedge oil groove (16) is continuously increased from the middle position of the groove to the two ends of the groove to form a wedge-shaped oil groove, an inner ring oil hole (17) is formed in the middle of the inner ring double-wedge oil groove (16), and the inner ring oil hole (17) is communicated with the radial bearing bush oil supply nozzle (13); radial bearing shell oil grooves (18) are formed in the radial bearing shell (5), the radial bearing shell oil grooves (18) located on the same circumference are arranged at intervals, and the radial bearing shell oil grooves (18) on the two adjacent circumferences are arranged in a staggered mode.

2. The double-wedge antifriction bearing shell upper rudder bearing of claim 1, wherein: the axial bearing bush (2) is fixedly arranged on the rudder bearing body (12), and the plane of the axial bearing bush (2) is vertical to the central line of the radial bearing bush (5).

3. The double-wedge antifriction bearing shell upper rudder bearing of claim 1, wherein: the outer ring double wedge oil groove (14) and the inner ring double wedge oil groove (16) are positioned on two concentric circumferences.

4. A double-wedge antifriction bearing shell upper rudder bearing according to claim 1, 2 or 3, characterised in that: the central angle alpha of the outer ring double wedge oil groove (14) is = 80-100 degrees, and the central angle beta of the inner ring double wedge oil groove (16) is = 80-100 degrees.

5. The double-wedge antifriction bearing shell upper rudder bearing of claim 4, wherein: the outer ring double-wedge oil grooves (14) and the inner ring double-wedge oil grooves (16) which are respectively positioned on different circumferences are arranged on the axial bearing bush (2) in a staggered mode.

6. The double-wedge antifriction bearing shell upper rudder bearing of claim 1, wherein: the radial bearing bush oil grooves (18) are distributed on 2-6 circles of the inner wall surface of the radial bearing bush (5), and the radial bearing bush oil grooves (18) on two adjacent circles are arranged in a staggered mode.

7. The double-wedge antifriction bearing shell upper rudder bearing of claim 6, wherein: the central angle gamma of the radial bearing shell oil groove (18) is = 80-100 degrees.

8. The double-wedge antifriction bearing shell upper rudder bearing according to claim 1 or 7, characterized in that: an oil groove oil hole (19) is formed in the radial bearing bush oil groove (18), and the oil groove oil hole (19) is communicated with the axial bearing bush oil supply nozzle (9).

9. The double-wedge antifriction bearing shell upper rudder bearing of claim 1, wherein: the rudder bearing frame (1), the rudder bearing body (12), the axial bearing bush (2) and the radial bearing bush (5) all adopt split structures.

Images