CN113187817A - Dynamic and static pressure dual-function bearing device of stern bearing and adjusting method - Google Patents
Dynamic and static pressure dual-function bearing device of stern bearing and adjusting method Download PDFInfo
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- CN113187817A CN113187817A CN202110606851.0A CN202110606851A CN113187817A CN 113187817 A CN113187817 A CN 113187817A CN 202110606851 A CN202110606851 A CN 202110606851A CN 113187817 A CN113187817 A CN 113187817A
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- 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
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
- F16C32/064—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being supplied under pressure
- F16C32/0644—Details of devices to control the supply of liquids to the bearings
- F16C32/0648—Details of devices to control the supply of liquids to the bearings by sensors or pressure-responsive control devices in or near the bearings
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- 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
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
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- 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
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
- F16C32/064—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being supplied under pressure
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- 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
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
- F16C32/064—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being supplied under pressure
- F16C32/0651—Details of the bearing area per se
- F16C32/0655—Details of the bearing area per se of supply openings
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- 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
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
- F16C32/064—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being supplied under pressure
- F16C32/0651—Details of the bearing area per se
- F16C32/0659—Details of the bearing area per se of pockets or grooves
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- 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
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0662—Details of hydrostatic bearings independent of fluid supply or direction of load
- F16C32/067—Details of hydrostatic bearings independent of fluid supply or direction of load of bearings adjustable for aligning, positioning, wear or play
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
- F16J15/3436—Pressing means
- F16J15/3452—Pressing means the pressing force resulting from the action of a spring
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
- F16J15/3464—Mounting of the seal
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
The invention relates to the technical field of ship stern shafts, in particular to a stern bearing dynamic and static pressure dual-function bearing device and an adjusting method, which comprises a mounting base, a stern bearing arranged on the mounting base, sealing devices respectively arranged at two end sides of the stern bearing, and a high-pressure oil supply system matched with the stern bearing, wherein the stern bearing comprises an upper bearing bush and a lower bearing bush which are matched with each other, an oil groove is arranged on the inner surface of the lower bearing bush, an oil hole communicated with the outside of the lower bearing bush is arranged in the oil groove, the high-pressure oil supply system comprises a high-pressure oil tank, a high-pressure oil pump, an oil supply pipeline and an oil return pipeline, the inlet end of the high-pressure oil pump is communicated with the high-pressure oil tank, the outlet end of the high-pressure oil pump is communicated with one end of the oil supply pipeline, the other end of the oil supply pipeline is communicated with the oil hole, one end of the oil return pipeline is arranged on the upper bearing bush and communicated with the inside of the upper bearing bush, and the other end of the oil return pipeline is communicated with the high-pressure oil tank, the invention greatly prolongs the service life of the shaft and the bearing, and the stern shaft has better stability and is not easy to damage.
Description
Technical Field
The invention relates to the technical field of ship stern shafts, in particular to a bearing device with dual functions of dynamic and static pressure of a stern bearing and an adjusting method.
Background
With the rapid development of economic globalization, international trade is increasingly close. Maritime transportation is the most important transportation mode in international trade, and takes over two thirds of the total transportation volume of international trade. The ship is a carrier for shipping, and its importance is self evident. The shafting is an important component of a ship propulsion system, and the bearing is a core component of the shafting. The stern bearing has bad working conditions and is easy to damage, not only needs to bear uneven cantilever load when the propeller rotates in water, but also can generate additional vibration during the operation of the propeller shaft. The failure of the stern bearing will affect the operation of the whole ship and increase the potential safety hazard of the ship. The stern bearing is difficult to inspect when the ship sails, and can be overhauled and maintained only when the ship enters a dock. The stern bearing docking maintenance not only affects the maintenance period, but also has expensive maintenance cost and affects the economic benefit of the ship.
At present, a dynamic pressure oil-lubricated white alloy bearing is mainly adopted by medium and large ships, because the bearing has the advantages of convenience in installation, high rotation precision, low manufacturing cost and the like, but the defects are obvious, such as: (1) when the stern shaft is started and stopped, the starting torque of the stern shaft is large, the stern bearing is easy to heat, and in addition, because the running speed of the stern shaft is too low, a pressure oil film cannot be quickly formed, the direct contact between the stern shaft and the surface of the stern bearing cannot be avoided, and the abrasion is caused. (2) When a ship enters and exits a wharf, the running speed of a stern shaft is low, a reliable oil film is difficult to form between the stern shaft and a stern bearing, and dry friction between the stern shaft and the stern bearing is large, so that the stern bearing is easy to wear; (3) during the operation of the stern shaft, the deviation of the shaft center is different along with different working conditions such as external load, rotating speed and the like, and the stability is easily influenced by external factors.
Therefore, in order to prolong the service life of the stern bearing, prolong the overhaul period of the stern bearing and improve the operating income of the ship, the invention designs the double-function bearing device capable of adjusting the dynamic and static pressures of the stern shaft.
Disclosure of Invention
Aiming at the defects in the prior art, the invention aims to provide a dynamic and static pressure dual-function bearing device of a stern bearing and an adjusting method.
In order to achieve the purpose, the invention provides the following technical scheme: a dynamic and static pressure double-function bearing device of a stern bearing comprises a mounting base, the stern bearing arranged on the mounting base, sealing devices respectively arranged at two end sides of the stern bearing, and a high-pressure oil supply system matched with the stern bearing,
the stern shaft is rotationally arranged in the stern bearing and penetrates through the two sealing devices,
the stern bearing comprises an upper bearing bush and a lower bearing bush which are matched with each other, an oil groove is arranged on the inner surface of the lower bearing bush, an oil hole communicated with the outer part of the lower bearing bush is arranged in the oil groove,
the high-pressure oil supply system comprises a high-pressure oil tank, a high-pressure oil pump, an oil supply pipeline and an oil return pipeline,
the inlet end of the high-pressure oil pump is communicated with the high-pressure oil tank, the outlet end of the high-pressure oil pump is communicated with one end of the oil supply pipeline, the other end of the oil supply pipeline is communicated with the oil hole,
one end of the oil return pipeline is arranged on the upper bearing bush and communicated with the interior of the upper bearing bush, and the other end of the oil return pipeline is communicated with the high-pressure oil tank.
Preferably, the sealing device comprises a movable ring, a stationary ring and a compression spring,
the dynamic ring and the static ring are sleeved on the stern shaft, the dynamic ring is in clearance fit with the stern shaft, the static ring is in interference fit with the stern shaft,
the compression spring is arranged between the dynamic ring and the static ring, the dynamic ring is pressed against the end side surface of the stern bearing through the elasticity of the compression spring,
the compression springs are uniformly arranged between the movable ring and the static ring in the circumferential direction.
Preferably, the oil groove is arranged on the inner surface of the lower bearing shell in a circumferential arc shape.
Preferably, a plurality of oil grooves are uniformly arranged on the inner surface of the lower bearing bush in the axial direction.
Preferably, a connecting groove is arranged on the inner surface of the lower bearing shell in a communicating manner between the plurality of oil grooves.
Preferably, the connecting groove is arranged on the inner surface of the lower bearing shell as an axial straight groove.
Preferably, the oil supply pipeline and/or the oil return pipeline are respectively provided with a pressure oil meter.
Preferably, the oil supply pipeline is provided with a safety valve and a maintenance valve.
Preferably, a pressure sensor is arranged between the stern bearing and the stern shaft.
In order to achieve the above purpose, the invention also provides the following technical scheme: a method for adjusting a dynamic and static pressure double-function bearing device of a stern bearing comprises the following steps:
(1) before the stern shaft is started, the high-pressure oil pump pumps high-pressure oil from the high-pressure oil tank and injects the high-pressure oil into an oil hole and oil groove of a lower bearing bush of the stern bearing;
(2) after the oil groove is filled with high-pressure oil, the high-pressure oil lifts the stern shaft in the stern bearing, so that the stern shaft is changed to be in a backward inclined state;
(3) after the stern shaft is lifted to the horizontal theoretical central line, the bearing load of the stern shaft is uniformly distributed along the axis;
(4) when the stern shaft is started, the stern shaft runs at a low speed, and a pressure oil film is formed between the shaft and the bearing bush;
(5) monitoring the oil film strength between the shaft and the bearing bush through a pressure sensor;
(6) when the oil film strength is smaller than a preset value, oil is continuously injected into the oil hole through the oil supply pipeline; otherwise, returning oil through an oil return pipeline;
(7) when the stern shaft rotates to a certain speed, the stern bearing becomes a hybrid bearing of dynamic and static pressure;
(8) and if the stern shaft and the stern bearing are in fault and need to be overhauled, opening the overhaul valve for overhauling.
Compared with the prior art, the invention has the beneficial effects that: compared with the conventional dynamic pressure bearing, the dynamic and static pressure bearing can inject high-pressure oil into an oil groove oil hole of a lower bearing bush of the stern bearing through a high-pressure oil pump, so that the stern shaft is lifted to a theoretical horizontal center line of a shaft system, the stern shaft and the bearing bush are separated by a pressure oil film, the pressure oil film is densely and uniformly distributed, the sliding resistance is only from fluid viscosity, and the dynamic and static pressure bearing is small in friction factor, high in reliability and long in service life.
In addition, the hydrostatic bearing has the function of homogenizing errors, the influence caused by inaccuracy in manufacturing is reduced, the temperature distribution of the bearing is uniform, and the problem of thermal expansion is not as serious as that of a hydrodynamic bearing. When the shaft carrier rotates to a certain speed, the bearing becomes a dynamic and static pressure mixed bearing, and the stability of the stern shaft becomes good.
Drawings
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is a schematic view of the internal structure of the lower bearing shell according to the present invention;
fig. 3 is a schematic structural diagram of the sealing device of the present invention.
In the figure: 1. a stern shaft; 2. mounting a base; 3. a high-pressure oil tank; 4. a high-pressure oil pump; 5. an oil supply conduit; 6. an oil return conduit; 7. a service valve; 8. a safety valve; 9. a stern bearing; 10. a sealing device; 11. a pressure oil gauge;
91. an upper bearing bush; 92. a lower bearing bush; 93. an oil sump; 94. an oil hole; 95. connecting grooves;
101. a moving ring; 102. a stationary ring; 103. compressing the spring.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
Referring to fig. 1 to 3, the present invention provides a technical solution: a dynamic and static pressure double-function bearing device of a stern bearing comprises a mounting base 2, a stern bearing 9 arranged on the mounting base 2, sealing devices 10 respectively arranged at two end sides of the stern bearing 9, and a high-pressure oil supply system matched with the stern bearing 9,
the stern shaft 1 is rotatably arranged in a stern bearing 9, the stern shaft 1 penetrates through two sealing devices 10,
the stern bearing 9 comprises an upper bearing bush 91 and a lower bearing bush 92 which are matched with each other, an oil groove 93 is arranged on the inner surface of the lower bearing bush 92, an oil hole 94 communicated with the outer part of the lower bearing bush 92 is arranged in the oil groove 93,
the high-pressure oil supply system comprises a high-pressure oil tank 3, a high-pressure oil pump 4, an oil supply pipeline 5 and an oil return pipeline 6,
the inlet end of the high-pressure oil pump 4 is communicated with the high-pressure oil tank 3, the outlet end of the high-pressure oil pump 4 is communicated with one end of the oil supply pipeline 5, the other end of the oil supply pipeline 5 is communicated with the oil hole 94,
one end of the oil return pipeline 6 is arranged on the upper bearing bush 91 and communicated with the inside of the upper bearing bush 91, and the other end of the oil return pipeline 6 is communicated with the high-pressure oil tank 3.
High-pressure oil pump 4 adopts the gear pump setting, high-pressure oil in the operation through the gear pump with high-pressure oil tank 3 is poured into in the axle bush 92 and is filled full oil groove 93, make high-pressure oil carry out the lifting to stern axle 1, make 1 lifting of stern axle to horizontal theoretical central line, make 9 year loads of stern bearing along axis evenly distributed, and when stern axle 1 starts, 1 low-speed operation of stern axle, form the pressure oil film between axle and the axle bush, when stern axle 1 moves the uniform velocity, the bearing becomes hybrid bearing of hybrid dynamic and static pressure this moment, stern axle 1's stability is better, not fragile, the life of axle and bearing has been improved greatly.
The sealing device 10 comprises a movable ring 101, a stationary ring 102 and compression springs 103, wherein the movable ring 101 and the stationary ring 102 are both sleeved on the stern shaft 1, the movable ring 101 is in clearance fit with the stern shaft 1, the stationary ring 102 is in interference fit with the stern shaft 1, the compression springs 103 are arranged between the movable ring 101 and the stationary ring 102, the movable ring 101 is pressed against the end side surface of the stern bearing 9 through the elasticity of the compression springs 103, and a plurality of compression springs 103 are uniformly arranged between the movable ring 101 and the stationary ring 102 in the circumferential direction;
the two sides of the stern bearing 9 are respectively provided with a sealing device 10, a static ring 102 (a support ring) of the sealing device 10 is in interference fit with the stern shaft 1, a movable ring 101 of the sealing device 10 is in clearance fit with the stern shaft 1, the movable ring 101 is abutted against the stern bearing 9 through the elastic action of a compression spring 103 to perform high-pressure oil sealing, and meanwhile, the elastic action of the movable ring 101 and the compression spring 103 is utilized to adjust the oil pressure in the stern bearing 9.
The inner surface of the lower bearing bush 92 is provided with a plurality of circumferential arc-shaped oil grooves 93, the inner surface of the lower bearing bush 92 is uniformly provided with a plurality of oil grooves 93 along the axial direction, connecting grooves 95 are communicated among the oil grooves 93 on the inner surface of the lower bearing bush 92, and the inner surface of the lower bearing bush 92 is provided with an axial straight groove 95;
the number of the oil grooves 93 is calculated and determined according to parameters such as the length of the stern bearing 9, the model weight of the stern shaft 1 and the like, three connecting grooves 95 are arranged in actual production, and the three connecting grooves 95 are respectively positioned at two end sides of the oil grooves 93 and at the middle end of the oil grooves 93;
the number of the oil holes 94 is set according to the speed of the oil supply efficiency in the oil groove 93, and generally, an oil hole 94 is respectively arranged in each oil groove 93, or an oil hole 94 is arranged in each adjacent oil groove 93.
The oil supply pipeline 5 and/or the oil return pipeline 6 are respectively provided with a pressure oil meter 11;
through the setting of pressure oil gauge, can the whole high pressure oil supply pipeline of straight tube carry out the oil pressure observation.
The oil supply pipeline 5 is provided with a safety valve 8 and an overhaul valve 7;
by arranging the safety valve 8, the condition that the system is damaged due to overhigh oil pressure in equipment failure is avoided;
through the arrangement of the maintenance valve 7, the operation is convenient and fast when the stern shaft 1 and the stern bearing 9 are in failure and need to be maintained.
A pressure sensor is arranged between the stern bearing 9 and the stern shaft 1;
the oil film strength between the shaft and the bearing bush can be monitored through the pressure sensor, when the oil film strength is smaller than a preset value, oil is continuously injected into the oil hole 94 through the oil supply pipeline 5, otherwise, oil is returned through the oil return pipeline 6, and therefore safe and stable operation of the stern shaft 1 in the operation process is guaranteed.
A method for adjusting a dynamic and static pressure double-function bearing device of a stern bearing 9 comprises the following steps:
(1) before the stern shaft 1 is started, the high-pressure oil pump 4 pumps high-pressure oil from the high-pressure oil tank 3 and injects the high-pressure oil into an oil hole 94 of a lower bearing bush 92 of the stern bearing 9 and an oil groove 93;
(2) after the oil groove 93 is filled with high-pressure oil, the high-pressure oil lifts the stern shaft 1 in the stern bearing 9, so that the state that the stern shaft 1 inclines backwards is changed;
(3) after the stern shaft 1 is lifted to the horizontal theoretical central line, the load of the stern bearing 9 is uniformly distributed along the axial line;
(4) when the stern shaft 1 is started, the stern shaft 1 runs at a low speed, and a pressure oil film is formed between the shaft and the bearing bush;
(5) monitoring the oil film strength between the shaft and the bearing bush through a pressure sensor;
(6) when the oil film strength is smaller than the preset value, oil is continuously injected into the oil hole 94 through the oil supply pipeline 5; otherwise, oil is returned through the oil return pipeline 6;
(7) when the stern shaft 1 runs to a certain speed, the stern bearing 9 becomes a hybrid bearing of dynamic and static pressure;
(8) if the stern shaft 1 and the stern bearing 9 are in fault and need to be overhauled, the overhaul valve 7 is opened for overhauling.
According to the technical scheme, a propeller is suspended behind a ship stern shaft 1, the stern shaft 1 is in a downward inclined state, high-pressure oil is injected into an oil hole 94 of an oil groove 92 of a lower bearing bush 92 of a stern bearing 9 through a high-pressure oil pump 4, so that the stern shaft 1 is lifted to a theoretical horizontal center line of a shafting, a reliable bearing oil film is established when the stern shaft 1 is started, stopped and runs at a low speed, the surface direct contact between the stern shaft 1 and the surface of the stern bearing 9 is avoided, the abrasion between the stern shaft 1 and the stern bearing 9 is reduced, and the abrasion reducing effect is difficult to realize in the running of a dynamic pressure bearing. Meanwhile, the starting torque of the stern shaft 1 is greatly reduced, and the bearing is not easy to heat. When the bearing of the stern shaft 1 runs to a certain speed, the stern bearing 9 becomes a hybrid dynamic and static pressure bearing, and the stability of the stern shaft 1 is good and is not easily influenced by the outside.
Although embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that changes, modifications, substitutions and alterations can be made in these embodiments without departing from the principles and spirit of the invention, the scope of which is defined in the appended claims and their equivalents.
Claims (10)
1. The utility model provides a difunctional bearing device of stern bearing hybrid which characterized in that: comprises a mounting base, a stern bearing arranged on the mounting base, sealing devices respectively arranged at two end sides of the stern bearing, and a high-pressure oil supply system matched with the stern bearing,
the stern shaft is rotationally arranged in the stern bearing and penetrates through the two sealing devices,
the stern bearing comprises an upper bearing bush and a lower bearing bush which are matched with each other, an oil groove is arranged on the inner surface of the lower bearing bush, an oil hole communicated with the outer part of the lower bearing bush is arranged in the oil groove,
the high-pressure oil supply system comprises a high-pressure oil tank, a high-pressure oil pump, an oil supply pipeline and an oil return pipeline,
the inlet end of the high-pressure oil pump is communicated with the high-pressure oil tank, the outlet end of the high-pressure oil pump is communicated with one end of the oil supply pipeline, the other end of the oil supply pipeline is communicated with the oil hole,
one end of the oil return pipeline is arranged on the upper bearing bush and communicated with the interior of the upper bearing bush, and the other end of the oil return pipeline is communicated with the high-pressure oil tank.
2. The dynamic and static pressure dual-function bearing device for the stern bearing of claim 1, wherein: the sealing device comprises a movable ring, a static ring and a compression spring,
the dynamic ring and the static ring are sleeved on the stern shaft, the dynamic ring is in clearance fit with the stern shaft, the static ring is in interference fit with the stern shaft,
the compression spring is arranged between the dynamic ring and the static ring, the dynamic ring is pressed against the end side surface of the stern bearing through the elasticity of the compression spring,
the compression springs are uniformly arranged between the movable ring and the static ring in the circumferential direction.
3. The dynamic and static pressure dual-function bearing device for the stern bearing of claim 1, wherein: the inner surface of the oil groove on the lower bearing bush is arranged in a circumferential arc shape.
4. A stern bearing hybrid dual function bearing device as claimed in claim 3, wherein: the oil groove is evenly provided with a plurality of in the inner surface of lower axle bush axial.
5. The stern bearing hybrid dual function bearing device as claimed in claim 4, wherein: and a connecting groove is formed in the inner surface of the lower bearing bush in a communicated manner between the oil grooves.
6. The stern bearing hybrid dual function bearing device as claimed in claim 5, wherein: the connecting groove is arranged on the inner surface of the lower bearing bush in an axial straight groove mode.
7. The dynamic and static pressure dual-function bearing device for the stern bearing of claim 1, wherein: and the oil supply pipeline and/or the oil return pipeline are respectively provided with a pressure oil meter.
8. The dynamic and static pressure dual-function bearing device for the stern bearing of claim 1, wherein: and the oil supply pipeline is provided with a safety valve and an overhaul valve.
9. The dynamic and static pressure dual-function bearing device for the stern bearing of claim 1, wherein: and a pressure sensor is arranged between the stern bearing and the stern shaft.
10. A method for adjusting a dynamic and static pressure double-function bearing device of a stern bearing is characterized by comprising the following steps: the method comprises the following steps:
(1) before the stern shaft is started, the high-pressure oil pump pumps high-pressure oil from the high-pressure oil tank and injects the high-pressure oil into an oil hole and oil groove of a lower bearing bush of the stern bearing;
(2) after the oil groove is filled with high-pressure oil, the high-pressure oil lifts the stern shaft in the stern bearing, so that the stern shaft is changed to be in a backward inclined state;
(3) after the stern shaft is lifted to the horizontal theoretical central line, the bearing load of the stern shaft is uniformly distributed along the axis;
(4) when the stern shaft is started, the stern shaft runs at a low speed, and a pressure oil film is formed between the shaft and the bearing bush;
(5) monitoring the oil film strength between the shaft and the bearing bush through a pressure sensor;
(6) when the oil film strength is smaller than a preset value, oil is continuously injected into the oil hole through the oil supply pipeline; otherwise, returning oil through an oil return pipeline;
(7) when the stern shaft rotates to a certain speed, the stern bearing becomes a hybrid bearing of dynamic and static pressure;
(8) and if the stern shaft and the stern bearing are in fault and need to be overhauled, opening the overhaul valve for overhauling.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110606851.0A CN113187817A (en) | 2021-06-01 | 2021-06-01 | Dynamic and static pressure dual-function bearing device of stern bearing and adjusting method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110606851.0A CN113187817A (en) | 2021-06-01 | 2021-06-01 | Dynamic and static pressure dual-function bearing device of stern bearing and adjusting method |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN113187817A true CN113187817A (en) | 2021-07-30 |
Family
ID=76986111
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110606851.0A Pending CN113187817A (en) | 2021-06-01 | 2021-06-01 | Dynamic and static pressure dual-function bearing device of stern bearing and adjusting method |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN113187817A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114457610A (en) * | 2022-03-23 | 2022-05-10 | 杭州美辰纸业技术有限公司 | Breast roll capable of avoiding transportation damage, bearing assembly and paper machine |
-
2021
- 2021-06-01 CN CN202110606851.0A patent/CN113187817A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114457610A (en) * | 2022-03-23 | 2022-05-10 | 杭州美辰纸业技术有限公司 | Breast roll capable of avoiding transportation damage, bearing assembly and paper machine |
| CN114457610B (en) * | 2022-03-23 | 2024-03-08 | 杭州美辰纸业技术有限公司 | Breast roll, bearing assembly and paper machine capable of avoiding transportation damage |
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