CN111503142B - Water lubrication tail bearing with function partition structure - Google Patents

Water lubrication tail bearing with function partition structure Download PDF

Info

Publication number
CN111503142B
CN111503142B CN202010283458.8A CN202010283458A CN111503142B CN 111503142 B CN111503142 B CN 111503142B CN 202010283458 A CN202010283458 A CN 202010283458A CN 111503142 B CN111503142 B CN 111503142B
Authority
CN
China
Prior art keywords
lining
bearing
water
rubber lining
rubber
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.)
Active
Application number
CN202010283458.8A
Other languages
Chinese (zh)
Other versions
CN111503142A (en
Inventor
袁成清
张豪
谭祖胜
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.)
Wuhan University of Technology WUT
Original Assignee
Wuhan University of Technology WUT
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.)
Filing date
Publication date
Application filed by Wuhan University of Technology WUT filed Critical Wuhan University of Technology WUT
Priority to CN202010283458.8A priority Critical patent/CN111503142B/en
Publication of CN111503142A publication Critical patent/CN111503142A/en
Application granted granted Critical
Publication of CN111503142B publication Critical patent/CN111503142B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/02—Sliding-contact bearings
    • 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
    • B63H23/326—Water lubricated bearings
    • 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
    • F16C17/14—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load specially adapted for operating in water
    • 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
    • F16C17/24—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with devices affected by abnormal or undesired positions, e.g. for preventing overheating, for safety
    • F16C17/243—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with devices affected by abnormal or undesired positions, e.g. for preventing overheating, for safety related to temperature and heat, e.g. for preventing overheating
    • 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
    • F16C37/00—Cooling of bearings
    • 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
    • F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
    • F16C2208/10—Elastomers; Rubbers
    • 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
    • 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
    • F16N15/00—Lubrication with substances other than oil or grease; Lubrication characterised by the use of particular lubricants in particular apparatus or conditions
    • F16N15/04—Lubrication with substances other than oil or grease; Lubrication characterised by the use of particular lubricants in particular apparatus or conditions with water

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Ocean & Marine Engineering (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

The invention discloses a water-lubricated tail bearing with a function partition structure, which comprises a rubber lining, a high-modulus middle lining layer and an outermost alloy bushing, wherein the top and the bottom of the rubber lining are non-grooved areas, a notch is arranged at the center of the non-grooved area at the bottom of the rubber lining along the axial direction of the rubber lining, the rubber lining is grooved except the non-grooved area, and uniformly distributed water tanks are arranged on the inner surface of the grooved area of the rubber lining; the middle lining of high modulus presss from both sides between rubber lining and alloy bush, the middle lining bottom of high modulus is equipped with the breach complex axial arch of rubber lining, the protruding top of axial and rubber lining parallel and level, the protruding middle part of axial is equipped with a trapezoidal cross-section basin. The bearing has a simple structure, makes full use of the advantages of various materials and structures, can improve the bearing capacity and the lubricating performance of the bearing, meets the requirements of bearing cooling and silt discharge, and ensures that the comprehensive performance of the bearing is optimal.

Description

Water lubrication tail bearing with function partition structure
Technical Field
The invention belongs to the field of ship machinery, relates to a water-lubricated tail bearing, and particularly relates to a water-lubricated tail bearing with a function partition structure, which can improve the bearing capacity, lubricating performance, cooling capacity and silt discharge capacity during operation by utilizing the advantages of various materials and structures.
Background
At present, the ship tail bearing mainly adopts an oil lubrication white alloy bearing, leaked lubricating oil can pollute a sailing water area, and the water lubrication bearing becomes a hot spot of current research along with the enhancement of environmental awareness of people and the strictness of environmental regulations. The water-lubricated tail bearing uses water as a lubricating medium, has rich lubricating water source and good safety, saves the consumption of lubricating oil and white alloy, and has good social benefit and economic benefit. However, the viscosity of water is low, the minimum film thickness of lubricating water is often only a few microns, and under the working conditions of low-speed heavy load and frequent start-stop, the water lubrication tail bearing is often in a mixed friction state, and a large amount of friction heat can further deteriorate the performance of the bearing, even burn out the lining. In addition, the problem that open water lubrication tail bearing commonly used at present can't avoid silt to pollute, when boats and ships navigation or business turn over harbour in inland river, a large amount of silt can enter into the bearing clearance, makes the frictional wear aggravation of inside lining. In order to enhance the cooling and heat dissipation and silt discharge capacity of the bearing, a certain amount of water tanks are usually provided on the inner liner of the bearing, but the water tanks reduce the bearing capacity of the bearing. Increasing the modulus of elasticity of the liner material can improve the bearing capacity of the bearing, but the bearing is not prone to dynamic pressure lubrication. These factors place higher demands on the material and structural properties of the water lubricated tail bearing.
In the research and development of the optimization of the bearing structure, researchers mainly focus on the aspects of the cross section shape of the water tank of the bearing, the arrangement mode of the water tank and the like. The cross section of the water tank can be divided into a trapezoid shape, a V shape, a U shape and the like, the influence of the water tanks with different cross section shapes on the performance of the bearing is different, and literature research shows that: the V-shaped groove has the largest flow field speed, but the lining has larger deformation, the trapezoidal groove has large bearing area, the lining has smaller deformation, but the flow performance is poorer, the performance of the U-shaped groove is between the V-shaped groove and the U-shaped groove, and the V-shaped groove is used for a negative pressure area of the bearing and the trapezoidal groove is used for a bearing area of the bearing, so that the advantages of the two grooves can be integrated, and the cooling performance and the bearing performance of the bearing reach satisfactory degrees. According to the distribution of the water tank in the circumferential direction of the bearing, the bearing can be divided into a partially-slotted bearing and a fully-slotted bearing, and researches show that: the friction coefficient of the half-slotted bearing is smaller than that of the full-slotted bearing, and the bearing capacity of the half-slotted bearing is larger than that of the full-slotted bearing, because the bearing area of the water lubrication bearing is mainly distributed on the lower half part of the bearing, the pressure distribution of a lubrication water film is discontinuous due to the arrangement of the water tank, and the lubrication state of the full-slotted bearing is worse under the same load. However, the temperature rise of the semi-slotted bearing is large, the temperature can rapidly rise to more than 60 ℃ under the working condition that cooling water is cut off, and the fully-slotted bearing can continuously run at 50 ℃. In addition, for the open type water lubrication bearing, the impurity particles in the cooling water can sink to the bottom of the bearing under the action of gravity, so that the friction and the abrasion of the half-slotted bearing are aggravated, the drainage capability of the full-slotted bearing is stronger, and the influence of the impurity particles is smaller. Therefore, the arrangement of the water tank improves the cooling performance and the impurity discharge capacity of the bearing by sacrificing a part of bearing capacity and tribological performance, and the comprehensive performance of the bearing can be optimized by optimizing the structure of the water tank.
In the development of bearing materials, naval brass or tin bronze is generally used for a bush, and the types of lining materials are various and mainly comprise rubber and modified substances thereof, high polymer materials and modified substances thereof and the like. Rubber and high-modulus plastic are the bearing materials which have better performance and are researched more enthusiastically. The rubber (such as nitrile rubber) has strong impact resistance and vibration absorption capacity, small elastic modulus, good adaptability to tail shaft misalignment caused by manufacturing errors, improper installation and hull deformation, is easier to form dynamic pressure lubrication in operation, but has small bearing capacity. High modulus plastics (such as ultra-high molecular weight polyethylene, polytetrafluoroethylene, polyurethane and the like) have high elastic modulus and strong bearing capacity, but are not beneficial to forming dynamic pressure lubrication on bearings. The thin rubber layer can be laid on the high-modulus plastic liner to form a composite structure, so that the advantages of the two materials are fully utilized, and the performance of the bearing is improved.
In conclusion, the structure and material optimization of the water lubrication tail bearing has very important significance for improving the performance of the water lubrication tail bearing, can effectively improve the bearing capacity, the lubricating performance, the cooling capacity and the silt discharge capacity during operation, prolongs the service time of the water lubrication tail bearing, and is beneficial to popularization and application of the water lubrication tail bearing.
Disclosure of Invention
The purpose of the invention is: the cross-sectional shape and the arrangement mode of the water-lubricated tail bearing water tank are optimized, the advantages of rubber and high-modulus plastics are fully utilized, the bearing capacity and the tribological performance of the bearing are improved, and meanwhile, the influence on the cooling heat dissipation capacity and the impurity discharge capacity is weakened as much as possible, so that the comprehensive performance and the reliability of the bearing are improved.
In order to achieve the purpose, the invention adopts the technical scheme that:
a water lubricated tail bearing with a function partition structure is characterized in that: including rubber inside lining, high modulus middle lining and outermost alloy bush, whole water lubricated tail bearing has the directionality, specifically is:
the top and the bottom of the rubber lining are non-grooved areas, a notch along the axial direction of the non-grooved area is arranged at the center of the non-grooved area at the bottom of the rubber lining, the rubber lining is grooved except the non-grooved area, and uniformly distributed water tanks are arranged on the inner surface of the grooved area of the rubber lining;
the middle lining of high modulus presss from both sides between rubber lining and alloy bush, the middle lining bottom of high modulus is equipped with the breach complex axial arch of rubber lining, the protruding top of axial and rubber lining parallel and level, the protruding middle part of axial is equipped with a trapezoidal cross-section basin.
Further, the ungrooved areas of the top and bottom of the rubber liner are symmetrically distributed on a vertical line passing through the axis center of the rubber liner.
Further, the total radian of the non-grooved area at the top of the rubber lining is 25-35 degrees.
Further, the total radian of the non-grooved area at the bottom of the rubber lining is 35-45 degrees.
Further, the water tank on the inner surface of the rubber lining is a water tank with a V-shaped section.
Further, the central angle of the alloy bushing's gap is no more than twice the water lubricated tail bearing angle of deflection.
Further, the thickness of the rubber lining is 1/2-2/3 of the thickness of the high modulus middle lining.
Further, the following steps: the rubber lining is made of thin nitrile rubber, and the high-modulus middle lining layer is made of ultra-high molecular weight polyethylene, polytetrafluoroethylene or polyurethane.
Further, the alloy bushing is made of corrosion-resistant navy brass or tin bronze.
Further, the rubber lining, the high-modulus middle lining layer and the alloy bushing are fixedly installed together by adopting bonding, interference fit or a connecting piece.
The rubber is used as the lining layer, so that a certain amount of water pockets are formed when the bearing is in mixed lubrication, the lubrication of the bearing is improved, meanwhile, the bearing is easy to form dynamic pressure lubrication due to the softer rubber lining, the vibration noise of the bearing during operation can be effectively reduced due to the excellent shock resistance of the rubber, and the working and living environments of crews are improved. The basin is not opened at rubber lining's top, can guarantee the intensity that can the lining does not influence the cooling heat dissipation ability of bearing again like this, the basin is not seted up in the certain limit of rubber lining bottom, be used for guaranteeing the continuous distribution of water film, the bearing capacity of reinforcing bearing, because the bottom of inside lining is main pressure-bearing area when boats and ships shut down, for the deflection of bearing this moment of reducing, rubber lining's bottom has set up a breach, be used for with the great high modulus intermediate layer cooperation of elastic modulus, thereby the bearing capacity of reinforcing bearing when boats and ships shut down, the central angle of breach generally is not more than the twice of bearing off normal angle, this is in order to let the minimum membrane thickness of bearing when operation be located rubber lining region, thereby reinforcing bearing forms the lubricated ability of dynamic pressure. The water tanks with certain number are uniformly arranged in other areas except the bottom and the top of the rubber lining layer and used for improving the cooling and heat dissipation capacity of the bearing, the cross section of each water tank is V-shaped, and the water tanks with the shapes can increase the speed of water flow and further enhance the heat dissipation of the bearing. The lining is in the middle of the high modulus in order to improve the intensity of the compound inside lining of multilayer, reduces the total deflection of lining, and the convex part in the middle of the high modulus lining bottom is the tail shaft that is used for supporting when boats and ships stop navigating, and trapezoidal basin has been seted up at the middle part of convex part simultaneously, and the effect of trapezoidal cross-section basin is the silt that deposits the bearing bottom under the action of gravity with the drainage, reduces the frictional wear who brings from this, sets up to trapezoidal because the bearing capacity of trapezoidal groove is strong. The outermost layer of the bearing is an alloy bushing which is generally made of alloy materials resistant to seawater corrosion, the inner surface of the alloy bushing is matched with the outer surface of the high-modulus middle lining layer to support the softer lining, and the outer surface of the alloy bushing is matched with a ship stern tube to play a role in fixing in the radial direction.
According to the technical scheme, when the high-modulus middle lining layer is applied to engineering, the axial protrusions of the high-modulus middle lining layer are arranged at the bottom of the bearing, the region bears the weight of a rotating shaft and a propeller when a ship is stopped, the minimum film thickness of the bearing during operation is located in the non-grooved region at the bottom of the rubber lining layer, the region nearby the region is the main bearing region during operation, the water tank is a straight tank penetrating through the bearing and is parallel to the axis of the bearing, cooling water flows in from one end of the bearing and flows out from the other end of the bearing, and a lubricating water film is distributed in a gap between the bearing.
Compared with the prior art, the invention has the following beneficial effects:
1) the thin rubber layer is used as the inner layer of the lining, the high-modulus plastic is used as the outer layer and the bottom of the inner layer of the lining, the shock resistance and vibration absorption performance of the rubber are utilized, noise and vibration in operation are reduced, the characteristic of small elastic modulus of the rubber is utilized, hydrodynamic lubrication is enabled to be easily achieved, and the characteristic of large elastic modulus of the high-modulus plastic is utilized to improve the bearing capacity of the bearing.
2) The top of the rubber lining is provided with no water tank, so that the rubber lining has higher strength; the bottom of the lining rubber lining is provided with no water tank, so that the bearing capacity of the bearing is enhanced, and the friction and the abrasion are reduced; v-shaped grooves are uniformly formed in other areas except the top and the bottom of the rubber lining, and the cooling and heat dissipation capacity of the bearing is enhanced.
3) A trapezoidal straight groove is formed in the middle of the protruding portion of the high-modulus middle lining layer, so that the discharge of silt impurities is facilitated, and meanwhile, the influence on the bearing capacity is weakened.
4) The minimum film thickness of the bearing during operation is enabled to appear in the non-grooved area at the bottom of the rubber lining, and the lubricating and cooling of the area are improved by utilizing the characteristic that the rubber is easy to deform and form a water pocket.
5) On the basis of considering the bearing capacity, the lubricating performance, the cooling capacity and the silt discharging capacity of the bearing, the comprehensive performance of the bearing is optimal, and the service time of the bearing is prolonged.
Drawings
FIG. 1 is a schematic view of a rubber innerliner in an embodiment of the invention;
FIG. 2 is a schematic representation of a high modulus middle liner made of ultra high molecular weight polyethylene in an embodiment of the present invention;
FIG. 3 is a schematic view of an alloy bushing of the present invention;
FIG. 4 is a schematic diagram of the general structure of a water lubricated tail bearing with a functionally zoned structure of the present invention;
1-alloy lining, 2-high modulus middle lining, 3-rubber lining, 4-axial bulge, 5-trapezoidal section water tank, 6-bottom non-grooved area, 7-V section water tank, 8-top non-grooved area and 9-notch.
Detailed Description
The embodiments of the present invention will be described in further detail with reference to the drawings and examples. The following examples are intended to illustrate the invention but are not intended to limit the scope of the invention.
The structure, principle and operation of the present invention will be further described with reference to the accompanying drawings, in which the present embodiment uses thin nitrile rubber as the rubber lining and ultra-high molecular weight polyethylene layer as the high modulus middle liner layer.
As shown in fig. 1 to 4, the present invention is a water lubricated tail bearing having a function partition structure, which utilizes the advantages of various materials and structures to improve the bearing capacity, lubricating performance, cooling capacity and silt discharging capacity during operation. The water lubrication tail bearing comprises an outer lining and an inner lining, wherein the outer lining is an alloy lining 1 and is used for being matched with a ship stern tube and the bearing inner lining to play a role in supporting the inner lining. The bearing lining is formed by compounding a rubber lining 3 and a high-modulus middle lining layer 2 made of ultra-high molecular weight polyethylene, and the lining with a composite structure is used for being matched with the rotating shaft, bearing the gravity of the bearing and the propeller, and is suitable for shafting misalignment caused by manufacturing deviation, improper installation and hull deformation.
The rubber lining 3 is composed of a top non-grooved area 8, a bottom non-grooved area 6 and grooved areas on two sides, the inner surface of the grooved area of the rubber lining 3 is provided with uniformly distributed V-shaped section water grooves 7, the middle part of the bottom non-grooved area 6 is provided with axially distributed notches 9, the thickness of a water film on the upper part of the rubber lining 3 during bearing operation is larger, cooling is better, non-grooving can increase the structural strength, the notches 9 on the lower part are matched with the axial protrusions 4 of the high-modulus middle lining layer 2, the bottom non-grooved area 6 is a main bearing area of a rotating shaft (positive and negative rotation), dynamic pressure lubrication is promoted by using the characteristic of easy deformation of rubber, the grooved areas on two sides are uniformly provided with the V-shaped section water grooves 7 to accelerate water flow, and cooling performance is improved. The bottom of the high-modulus middle lining layer 2 is provided with the axial bulge 4, and the gravity of the rotating shaft and the propeller is borne by the ultrahigh molecular weight polyethylene when the ship is stopped, so that the deformation of the lining is reduced. The central angle (i.e. the total arc) of the axial projections 4 should be less than twice the offset angle of the bearing during operation, in order to locate the minimum film thickness of the bearing in the bottom non-grooved region 6 of the rubber lining 3, thereby reducing frictional wear. Trapezoidal cross section basin 5 has been seted up to the intermediate position of axial bulge 4, uses trapezoidal cross section basin 5 to hold and excrete the silt impurity that subsides to the bearing bottom because of the action of gravity. The trapezoidal section water tank 5 has a trapezoidal cross section because the trapezoidal groove has a large bearing capacity, and the reduction of the bearing capacity caused by the grooving can be reduced.
During manufacturing, the bearing can be manufactured by dividing the alloy bushing 1, the high modulus middle lining layer 2 and the rubber lining 3 into three parts, and then combining the three parts into a whole by bonding or mechanical matching. When in use, the axial protrusions 4 of the high modulus middle lining layer 2 are arranged at the bottom of the bearing and then matched with a tail shaft of a ship, and then the ship can normally operate.
In the embodiment of the invention, the whole water lubrication tail bearing has directionality, namely, when the bearing is installed (horizontally installed), the axial bulge 4 is positioned at the bottommost part; the non-grooved areas at the top and the bottom of the rubber lining 3 are symmetrically distributed by a vertical line passing through the axis center of the rubber lining.
As a more preferable embodiment, the total radian of a top non-grooved area 8 of the rubber lining 3 is 25-35 degrees, the total radian of a bottom non-grooved area 6 of the rubber lining 3 is 35-45 degrees, and the thickness of the rubber lining 3 is 1/2-2/3 of the thickness of the high-modulus middle lining layer 2, so that the grooving processing cost is saved, the strength of the lining is ensured, the high-modulus middle lining layer 2 and the rubber lining 3 can respectively exert the material characteristics thereof, and the service performance of the whole water-lubricated tail bearing is improved.
The trapezoidal section water tank 5 and the V-shaped section water tank 7 of the embodiment of the invention are both straight water tanks along the axial direction of the water lubrication tail bearing.
Although not explicitly described, it is known from the prior art that the water tank of the present invention is an axially open water tank.
The above embodiments are merely illustrative of the present invention and are not to be construed as limiting the invention. Although the present invention has been described in detail with reference to the embodiments, it should be understood by those skilled in the art that various combinations, modifications or equivalents may be made to the technical solution of the present invention without departing from the spirit and scope of the technical solution of the present invention, and the technical solution of the present invention is covered by the claims of the present invention.

Claims (10)

1. A water lubricated tail bearing with a function partition structure is characterized in that: including rubber inside lining, high modulus middle lining and outermost alloy bush, whole water lubricated tail bearing has the directionality, specifically is:
the top and the bottom of the rubber lining are non-grooved areas, a notch along the axial direction of the non-grooved area is arranged at the center of the non-grooved area at the bottom of the rubber lining, the rubber lining is grooved except the non-grooved area, and uniformly distributed water tanks are arranged on the inner surface of the grooved area of the rubber lining;
the middle lining of high modulus presss from both sides between rubber lining and alloy bush, the middle lining bottom of high modulus is equipped with the breach complex axial arch of rubber lining, the protruding top of axial and rubber lining parallel and level, the protruding middle part of axial is equipped with a trapezoidal cross-section basin.
2. The water-lubricated tail bearing of claim 1, wherein: the non-grooved areas at the top and the bottom of the rubber lining are symmetrically distributed by a vertical line passing through the axis of the rubber lining.
3. The water-lubricated tail bearing of claim 2, wherein: the total radian of the non-grooved area at the top of the rubber lining is 25-35 degrees.
4. The water-lubricated tail bearing of claim 2, wherein: the total radian of the non-grooved area at the bottom of the rubber lining is 35-45 degrees.
5. The water-lubricated tail bearing of claim 1, wherein: the water tank on the inner surface of the rubber lining is a water tank with a V-shaped section.
6. The water-lubricated tail bearing of claim 1, wherein: the central angle of the notch of the alloy bushing is not more than twice of the deviation angle of the water-lubricated tail bearing.
7. The water-lubricated tail bearing of claim 1, wherein: the thickness of the rubber lining is 1/2-2/3 of the thickness of the high modulus middle lining.
8. The water lubricated tail bearing of any one of claims 1 to 7, wherein: the rubber lining is made of thin nitrile rubber, and the high-modulus middle lining layer is made of ultra-high molecular weight polyethylene, polytetrafluoroethylene or polyurethane.
9. The water lubricated tail bearing of any one of claims 1 to 7, wherein: the alloy bushing is made of corrosion-resistant navy brass or tin bronze.
10. The water lubricated tail bearing of any one of claims 1 to 7, wherein: the rubber lining, the high-modulus middle lining layer and the alloy bushing are fixedly arranged together by adopting bonding, interference fit or a connecting piece.
CN202010283458.8A 2020-04-13 2020-04-13 Water lubrication tail bearing with function partition structure Active CN111503142B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202010283458.8A CN111503142B (en) 2020-04-13 2020-04-13 Water lubrication tail bearing with function partition structure

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202010283458.8A CN111503142B (en) 2020-04-13 2020-04-13 Water lubrication tail bearing with function partition structure

Publications (2)

Publication Number Publication Date
CN111503142A CN111503142A (en) 2020-08-07
CN111503142B true CN111503142B (en) 2021-04-16

Family

ID=71872725

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202010283458.8A Active CN111503142B (en) 2020-04-13 2020-04-13 Water lubrication tail bearing with function partition structure

Country Status (1)

Country Link
CN (1) CN111503142B (en)

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4773771A (en) * 1987-11-09 1988-09-27 The B. F. Goodrich Company Bearing assembly
EP0635106B1 (en) * 1992-04-09 1996-03-13 neo-plastic Dr. Doetsch Diespeck GmbH Method of producing a sleeve-shaped friction bearing, and friction bearing produced by this method
CN101334069B (en) * 2008-08-06 2010-12-15 重庆奔腾科技发展有限公司 Water lubrication rubber alloy bearing
JP4848415B2 (en) * 2008-12-09 2011-12-28 三菱重工業株式会社 Manufacturing method of anticorrosion bearing
CN103821826B (en) * 2014-03-05 2016-02-24 华中科技大学 A kind of water lubricating rubber stern bearing and design method thereof
CN104728260B (en) * 2014-12-22 2018-03-23 广州市研理复合材料科技有限公司 A kind of multiple-layer laminated bullet moulds alloy from the manufacture method of liquid lubrication bearing
CN106142795A (en) * 2016-06-29 2016-11-23 中国科学院长春应用化学研究所 Deformation self adaptation macromolecule bearing composite material and preparation method and application

Also Published As

Publication number Publication date
CN111503142A (en) 2020-08-07

Similar Documents

Publication Publication Date Title
CN107166036B (en) A kind of low leakage helicla flute liquid film mechanical sealing end face structure
US7467796B2 (en) Bearing seal with flexible lip
CN106194989B (en) A kind of mixing channel water lubricated rubber bearing peculiar to vessel
CN106122482B (en) A kind of low leakage non-contacting mechanical seal end face structure
CN204961579U (en) Intermediate shaft bearing with keep off oily structure
CN109764063A (en) A kind of water lubriucated bearing of the ship longitudinal different rigidity of big damping
CN201110379Y (en) Combined oil seal for rotational shaft
KR20190077237A (en) Half thrust bearing
CN111503142B (en) Water lubrication tail bearing with function partition structure
CN113418703B (en) Water lubrication bearing capable of self-compensating static pressure, static pressure self-compensating system and engineering analysis method
CN2647749Y (en) Ship trailing axle system device using water lubricating
CN112460137A (en) Medium liquid self-cooling static pressure environment-friendly sliding bearing
CN114251365B (en) Method for improving bearing wear resistance of friction surface of bionic water-lubricated bearing
CN201277266Y (en) Bearing sealing ring and deep groove ball bearing
CN112610606B (en) Novel drag reduction water-lubricated bearing
CN114060108B (en) Water lubrication bearing of turbine type energy recovery integrated machine
CN102141151A (en) Novel static-ring structure of mechanical sealing device
JP7343940B2 (en) Bearings for ship propulsion shafts
CN210738902U (en) High-strength water-lubricated bearing
CN205978458U (en) Low non -contact mechanical seal terminal surface structure of leaking
CN109642606B (en) Thrust washer
US10648503B2 (en) Thrust bearing and bearing device
CN203335645U (en) Oil seal, vehicle rear axle with oil seal as well as vehicle
CN213839276U (en) Medium liquid self-cooling static pressure environment-friendly sliding bearing
CN113389806A (en) Sliding bearing and compressor with same

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant