CN113494525A - Thrust bearing - Google Patents
Thrust bearing Download PDFInfo
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- CN113494525A CN113494525A CN202110833050.8A CN202110833050A CN113494525A CN 113494525 A CN113494525 A CN 113494525A CN 202110833050 A CN202110833050 A CN 202110833050A CN 113494525 A CN113494525 A CN 113494525A
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- thrust bearing
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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
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/08—Elastic or yielding bearings or bearing supports, for exclusively rotary movement primarily for axial load, e.g. for vertically-arranged shafts
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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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
- F16F15/027—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means comprising control arrangements
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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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
- F16F15/027—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means comprising control arrangements
- F16F15/0275—Control of stiffness
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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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
- F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
- F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
- F16F9/22—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with one or more cylinders each having a single working space closed by a piston or plunger
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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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/3292—Sensor arrangements
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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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/36—Special sealings, including sealings or guides for piston-rods
- F16F9/362—Combination of sealing and guide arrangements for piston rods
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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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/43—Filling or drainage arrangements, e.g. for supply of gas
- F16F9/437—Drainage arrangements
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H23/00—Transmitting power from propulsion power plant to propulsive elements
- B63H23/32—Other parts
- B63H23/321—Bearings or seals specially adapted for propeller shafts
- B63H2023/325—Thrust bearings, i.e. axial bearings for propeller shafts
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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
- F16C2326/00—Articles relating to transporting
- F16C2326/30—Ships, e.g. propelling shafts and bearings therefor
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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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2230/00—Purpose; Design features
- F16F2230/06—Fluid filling or discharging
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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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2230/00—Purpose; Design features
- F16F2230/08—Sensor arrangement
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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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2230/00—Purpose; Design features
- F16F2230/30—Sealing arrangements
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Support Of The Bearing (AREA)
Abstract
The present application provides a thrust bearing. The thrust bearing comprises a box body and a thrust shaft rotatably arranged in the box body, the thrust shaft is provided with a thrust disc in the circumferential direction, one side of the box body corresponding to the thrust disc is provided with a thrust block, and the thrust block is positioned on a thrust bearing seat; hydraulic vibration damping devices which are hermetically connected with the box body are uniformly distributed in the circumferential direction of the other side of the thrust bearing seat, and each hydraulic vibration damping device comprises a hydraulic cylinder component, a displacement measuring assembly and a communicating valve block; the pressure regulating control device is electrically connected with the displacement sensor and used for regulating the pressure of hydraulic oil in the hydraulic cylinder component in real time according to the real-time detection distance of the displacement sensor so as to enable the thrust disc to be in a balance position. The vibration noise of large-scale boats and ships in the operation process can effectively be reduced to this application to through reasonable structural design, system layout, parameter setting, guaranteed still can effectively work in full operating mode scope, different application scenario, further promoted the universality.
Description
Technical Field
The application relates to the technical field of vibration noise control of large ship power mechanical equipment, in particular to a thrust bearing for damping a ship shafting.
Background
The main power of a large ship mainly comprises a diesel engine, a steam turbine, a motor and the like, and due to the influences of factors such as nonuniformity of power output, turbulence in water, ocean current and the like, the thrust borne by a shafting can generate periodic or aperiodic pulsation, so that the pulsation is transmitted to a ship body through a thrust bearing to generate vibration and noise.
In order to ensure the safety and comfort of the ship, the vibration and noise reduction of the shafting must be considered heavily, and the thrust bearing the pulsating thrust in the shafting is a key part for solving the problems of vibration and noise. For the vibration reduction design of the thrust bearing, schemes such as rubber vibration reduction, disc spring vibration reduction, hydraulic vibration reduction and the like exist. Among them, the rubber damping and disc spring damping schemes are not suitable for being applied to a propulsion system of a large ship because the problems of excessive axial deformation and large radial dimension of a thrust bearing can be caused when the thrust bearing bears large thrust. The hydraulic vibration reduction scheme can guarantee vibration reduction and noise reduction effects and can meet requirements for the size and the deformation of the thrust bearing, however, existing hydraulic vibration reduction measures in the prior art can only play a role in resonance conversion vibration reduction under a certain shafting working condition frequency range due to the fact that self structural scheme limits and hydraulic function purposes are different, application range is narrow, and requirements for vibration reduction and noise reduction of shafting full working conditions cannot be effectively met.
In view of the above problems, a thrust bearing hydraulic damping scheme with better universality and more reasonable structure and control is urgently needed, so that better measures are provided for damping and reducing noise of large ships, and the safety and comfort of the ships are further improved.
Disclosure of Invention
The application aims to provide a thrust bearing, can control the rigidity and the damping of a thrust bearing system through measures such as the volume of changing hydraulic oil, the drift diameter of a pipeline and the like according to different working conditions, and comprises a set of hydraulic vibration reduction device and a control system which are more reasonable in structure, so that the requirement of reducing vibration and noise of a large ship is ensured, and meanwhile, the thrust bearing adopting the set of hydraulic vibration reduction and the control device thereof is also ensured to be suitable for vibration reduction of a shafting full working condition range for use.
In order to achieve the purpose, the thrust bearing comprises a box body and a thrust shaft which is rotatably arranged in the box body, wherein a thrust disc is arranged on the thrust shaft in the circumferential direction, a thrust block is arranged on one side, corresponding to the thrust disc, of the box body, and the thrust block is positioned on a thrust bearing disc; a hydraulic vibration damping device which is hermetically connected with the box body is arranged at a position corresponding to the thrust block, and the hydraulic vibration damping device comprises a hydraulic cylinder component, a displacement measuring assembly and a communicating valve block; the hydraulic cylinder component is hermetically arranged on one side of the box body, a piston rod is arranged in the middle of the hydraulic cylinder component, and one end of the piston rod extends into the box body and is connected with the thrust block; hydraulic oil is filled in the hydraulic cylinder part to form a hydraulic oil cavity; the displacement measuring assembly comprises a guide rod and a displacement sensor; the guide rod is abutted against the other end of the piston rod in real time; the displacement sensor is abutted with one end of the guide rod, which is far away from the piston rod; the communication valve block is provided with a first connecting end, a second connecting end and a third connecting end; the first connecting end is communicated with the box body and the hydraulic oil cavity; the second connecting end is communicated with the container group; the third link is connected to the pressure regulating control device, the pressure regulating control device with displacement sensor electric connection for according to displacement sensor's real-time detection distance is adjusted in real time the pressure of hydraulic oil intracavity hydraulic oil, so that the thrust disc is in balanced position.
The further improvement of this application lies in, the thrust piece is followed the circumference of thrust shaft is equipped with a plurality ofly, and each thrust piece passes through the reference column and holds the equipment of pushing away the seat, hold the seat of pushing away through the location uide pin with the box carries out the assembly of axial slidingtype, hold the opposite side that pushes away the seat with the tip looks butt of piston rod.
The application is further improved in that the joint surface of the thrust bearing seat and the box body is also provided with a wear-resistant vibration damping layer.
The application is further improved in that the hydraulic cylinder component further comprises a hydraulic cylinder sleeve, a guide sleeve and a hydraulic cylinder cover; the hydraulic cylinder sleeve is arranged corresponding to the piston rod and is connected with the box body in a sealing way; the guide sleeve is connected with one side, facing the box body, of the hydraulic cylinder sleeve in a sealing mode; the piston rod is fixed in the guide sleeve and arranged along the axial direction of the thrust shaft; the hydraulic cylinder cover is connected with one side of the hydraulic cylinder sleeve, which is far away from the guide sleeve, in a sealing way; the hydraulic cylinder sleeve, the piston rod and the hydraulic cylinder cover are arranged in an enclosing mode to form the hydraulic oil cavity.
In a further development of the application, the hydraulic cylinder part further comprises a support ring and a sealing ring; the support ring is arranged between the piston rod and the guide sleeve and is arranged around the axial direction of the piston rod; the sealing ring is arranged among the piston rod, the hydraulic cylinder cover and the hydraulic cylinder sleeve and surrounds the axial direction of the piston rod.
The application is further improved in that the communication valve block is communicated with the hydraulic oil cavity through a hydraulic oil pipe; the hydraulic cylinder cover is provided with an oil pipe mounting hole, and the hydraulic oil pipe is connected with the oil pipe mounting hole of the hydraulic cylinder cover.
The application is further improved in that the displacement measuring assembly comprises a guide seat, a guide rod and a disc spring; the guide seat is mounted to the hydraulic cylinder cover; a baffle ring is arranged in the middle of the guide rod and can be arranged in the guide seat in a sliding manner; two ends of the guide rod respectively extend out of the guide seat; the displacement sensor is provided with a displacement sensor probe, one end of the guide rod is abutted with the displacement sensor probe, and the other end of the guide rod is abutted with the piston rod; the disc spring is arranged in the guide seat and is abutted against the baffle ring, so that the guide rod is kept in abutting contact with the piston head of the hydraulic cylinder part in real time.
In a further development of the application, the displacement measuring assembly further comprises a sensor support and a fastening guide stud; the sensor mount is mounted to the hydraulic cylinder head; the displacement sensor is fixed on the sensor bracket; the fastening guide stud is detachably arranged at one end, facing the displacement sensor, of the guide seat, and the fastening guide stud is sleeved on the outer side of the guide rod and is abutted to the disc spring.
The further improvement of this application lies in, hydraulic cylinder cover, the intercommunication valve piece or still be equipped with discharge valve on the container group.
The further improvement of this application lies in, hydraulic damping device is equipped with a plurality ofly, and is a plurality of hydraulic damping device follows thrust shaft's circumference evenly sets up.
In a further development of the present application, the thrust bearing further comprises a damping valve block; the damping valve block is provided with a plurality of hydraulic damping units with different apertures, which are arranged in parallel, and each hydraulic damping unit comprises a stop valve and a damping hole pipe.
In a further development of the application, the container group comprises a plurality of hydraulic volume units arranged in parallel, each hydraulic volume unit comprising a shut-off valve and a hydraulic container.
The application provides a pair of thrust bearing can make the thrust disc of thrust axle be in balanced position, can effectively reduce the vibration noise of large-scale boats and ships in operation process to through reasonable structural design, system arrangement, parameter setting has guaranteed still can effectively work in full operating mode scope, different application occasions, has further promoted the universality.
Drawings
FIG. 1 is a schematic view of a thrust bearing body with a hydraulic cylinder assembly according to the present application.
FIG. 2 is a side view schematic of a thrust bearing body with a hydraulic cylinder assembly according to the present application.
FIG. 3 is a schematic diagram of the hydraulic cylinder component structure of the present application.
FIG. 4 is a schematic diagram of the hydraulic damping system of the present application.
Fig. 5 is a schematic diagram of the pressure regulating control device of the present application.
FIG. 6 is a schematic diagram of the hydraulic damping and control system assembly of the present application.
Fig. 7 is a basic schematic diagram of the hydraulic damping of the present application.
Description of reference numerals:
1 is a thrust shaft, 2 is a displacement measuring component, 2-1 is a sensor bracket, 2-2 is a displacement sensor, 2-3 is a fastening guide stud, 2-4 is a guide seat, 2-5 is a disc spring, 2-6 is a sealing ring, 2-7 is a guide rod, 3 hydraulic cylinder parts, 3-1 piston rods, 3-2 is a guide sleeve, 3-3 is a support ring, 3-4 is a sealing ring, 3-5 is a hydraulic cylinder sleeve, 3-6 is a hydraulic cylinder cover, 4 is a box body, 5 is a communicating valve block, 6 is a positioning guide pin, 7 is a wear-resistant vibration damping layer, 8 is a thrust bearing seat, 9 is a positioning column, 10 is a thrust block, 11 is a thrust disc, 12 is a spherical cushion block, 13 is a support bearing, 14 is a sealing component, 15 is a hydraulic oil pipe, 16 is an exhaust valve, 17 is a damping valve block, 17-1 is stop valves A-D (from top to bottom), 17-2 are damping hole pipes E-H (from top to bottom), 18 is a container group, 18-1 are stop valves I-M (from top to bottom), 18-2 are hydraulic containers N-R (from top to bottom), 19 is a piston position PID controller, 20 is a first overflow valve, 21 is an oil tank, 22 is a manual pump, 23 is an electric pump, 24 is a check valve, 25 is a second overflow valve, 26 is an accumulator, 27 is a first pressure sensor, 28 is an adjustable throttle, 29 is a servo valve, and 30 is a second pressure sensor.
Detailed Description
The preferred embodiments of the present application will be described in full hereinafter with reference to the accompanying drawings, making the technical contents thereof clearer and easier to understand. The present application is capable of embodiments in many different forms and is not intended to be limited to the embodiments shown herein.
Referring to fig. 1-4, the present application provides a thrust bearing including a hydraulic damping device and a pressure regulating control device. The thrust bearing can bear high thrust, has the effect of overall vibration reduction of all-directional vibration transmitted to the thrust bearing device of the shafting, has compact size and structure, and is suitable for application in ship shafting with large, medium and small thrust. The thrust bearing meets the requirements of vibration reduction and noise reduction of large ships, ensures that the thrust bearing adopting the hydraulic vibration reduction and control device is suitable for vibration reduction in the full working condition range, and provides a more excellent scheme for the vibration reduction and noise reduction design of the thrust bearing.
With reference to fig. 1 to 3, a specific structure of the thrust bearing body will be described. The thrust bearing body serves the purpose of structure indication, only the damping structure is arranged at the main machine end of the body to realize the thrust transmission and damping functions of the forward working condition, and the damping structure is not arranged at the stern shaft end of the body to realize the thrust transmission function of the reverse working condition. It can be understood that a vibration damping structure can be arranged at the end of the stern shaft to realize the functions of thrust transmission and vibration damping under the working condition of backing.
The thrust bearing body mainly comprises a thrust shaft 1, a displacement measuring assembly 2, a hydraulic cylinder component 3, a box body 4, a communicating valve block 5, a positioning guide pin 6, a wear-resistant vibration damping layer 7, a thrust bearing seat 8, a positioning column 9, a thrust block 10, a thrust disc 11, a spherical cushion block 12, a supporting bearing 13, a sealing assembly 14, a hydraulic oil pipe 15 and an exhaust valve 16. The displacement measurement component 2 comprises a sensor support 2-1, a displacement sensor 2-2, a fastening guide stud 2-3, a guide seat 2-4, a disc spring 2-5, a sealing ring 2-6 and a guide rod 2-7. The hydraulic cylinder part 3 comprises a piston rod 3-1, a guide sleeve 3-2, a support ring 3-3, a sealing ring 3-4, a hydraulic cylinder sleeve 3-5 and a hydraulic cylinder cover 3-6.
The two sides of the thrust shaft 1 are provided with flanges, the left side is a thrust bearing main machine end flange used for being connected with an output flange of a main machine, and the right side is a thrust bearing stern shaft end flange used for being connected with an input end flange of a stern shaft, so that the output power of the main machine is transmitted to a stern shaft propeller. The middle section of the thrust shaft 1 is provided with a thrust disc 11, a thrust block 10 is in contact with the thrust disc, the thrust block is positioned on a thrust bearing disc, a plurality of thrust blocks 10 arranged in the circumferential direction are arranged on one side of a thrust bearing seat 8 through corresponding spherical cushion blocks 12 and positioning columns 9, the thrust bearing seat 8 is arranged in a box body 4 through positioning guide pins 6, the other side of the thrust bearing seat 8 is in contact with the right side of a piston rod 3-1 in a hydraulic cylinder part 3, and a sealed space formed by the left side of the piston rod 3-1, a hydraulic cylinder sleeve 3-5 and a hydraulic cylinder cover 3-6 is filled with hydraulic oil to form a hydraulic oil cavity, namely the hydraulic oil cavity is filled with the hydraulic oil in the hydraulic cylinder part 3; the pressure regulating control device regulates the pressure of hydraulic oil in the hydraulic oil cavity in real time to enable the thrust disc 11 to be in a balance position; the hydraulic cylinder components 3 are fixed on the box body 4 through bolts, the hydraulic cylinder components are circumferentially and uniformly distributed on the box body 4 by taking the axis of the thrust shaft 1 as the center, the hydraulic cylinder components 3 are mutually connected in series through a hydraulic oil pipe 15 and a communication valve block 5, and the box body 4 is connected with a ship body through the mounting foot parts of the left wing and the right wing of the box body axis. The thrust shaft 1 is supported and positioned in the radial direction by a support bearing 13 mounted in the casing 4, and the rotating thrust shaft 1 and the casing 1 are sealed by seal assemblies 14 mounted at both ends of the casing 4.
When the thrust bearing is in working condition of forward driving, the propeller transmits the generated thrust to a flange disc at the stern shaft end of the thrust shaft 1 and then to the thrust disc 11, and then the thrust disc 11 transmits the thrust to the left thrust block 10, the spherical cushion block 12, the thrust bearing seat 8, the hydraulic cylinder component 3 and the box body 4 in sequence, and finally the thrust is transmitted to the ship body through the two-wing mounting machine feet by the box body 4, so that the ship body is pushed to advance.
When the thrust bearing works under a backing working condition, the propeller transmits generated pulling force to a stern shaft end flange disc of the thrust shaft 1 and then to the thrust disc 11, then the pulling force is transmitted to the thrust block 10 on the other side, the spherical cushion block 12, the thrust bearing seat 8 and the box body 4 in sequence by the thrust disc 11, and finally the pulling force is transmitted to the ship body through the two-wing installation machine feet by the box body 4, so that the ship body is pushed to back.
As the thrust bearing seat 8 at one side of the hydraulic oil cylinder 4 has the axial sliding structural characteristic, the outer circumferential surface of the thrust bearing seat 8 is provided with the wear-resistant vibration damping layer 7 made of high polymer material, so that the problems of friction and abrasion between metals and large axial movement friction force are solved. The circumference of the thrust bearing seat 8 is provided with a positioning guide pin 6 which guides the axial movement of the thrust bearing seat to the left and right and is used for preventing the thrust bearing seat 8 from rotating in the circumferential direction during normal work.
The piston rod 3-1 is placed in the hydraulic cylinder sleeve 3-5 and the guide sleeve 3-2 through the support ring 3-3, the guide sleeve 3-2 and the support ring 3-3 made of high-molecular wear-resistant vibration damping materials are arranged due to the fact that the piston rod 3-1 is long in structural length, accurate and reliable axial movement of the piston rod 3-1 in the hydraulic cylinder component 3 is facilitated, the guide sleeve 3-2 is installed on the hydraulic cylinder sleeve 3-5 through bolts, axial limiting is conducted on the piston rod 3-1 through the hydraulic cylinder cover 3-6 and the guide sleeve 3-2, and damage to the hydraulic cylinder component 3 and a thrust bearing body due to failure of a hydraulic system is prevented. The sealing rings 3-4 are used to prevent leakage of hydraulic oil.
The hydraulic cylinder covers 3-6 are provided with exhaust valves 16, which are convenient for quick discharge of gas when hydraulic oil enters into each hydraulic cylinder 3.
The hydraulic cylinder parts 3 are connected in series with each other through the hydraulic oil pipes 15 and the communicating valve block 5, so that the uniform distribution of hydraulic oil pressure in the hydraulic cylinder parts 3 is ensured, the synchronous movement of the piston rods 3-1 is ensured, and the exhaust valve 16 is arranged on the communicating valve block 5, so that the rapid discharge of gas is facilitated when hydraulic oil enters the communicating valve block 5.
The communicating valve block 5 is provided with a first connecting end, a second connecting end and a third connecting end; the first connecting end is communicated with the box body 4 and the hydraulic oil cavity; the second connection end is in communication with the container group 18; the third connecting end is connected to a pressure regulating control device, the pressure regulating control device is electrically connected with the displacement sensor 2-2 and is used for regulating the pressure of hydraulic oil in the hydraulic oil cavity in real time according to the real-time detection distance of the displacement sensor 2-2 so that the thrust disc 11 is in a balance position.
The thrust blocks 10 are arranged along the circumferential direction of the thrust shaft 1, each thrust block 10 is assembled with a thrust bearing seat 8 through a positioning column, the thrust bearing seat 8 is assembled with the box body 4 in an axially sliding mode through a positioning guide pin 6, and the other side of the thrust bearing seat 8 is abutted to the end portion of the piston rod 3-1.
The shell of a displacement sensor 2-2 in a displacement measuring assembly 2 is fixed on a sensor support 2-1, the sensor support 2-1 is fixed on a hydraulic cylinder cover 3-6, a telescopic probe of the displacement sensor 2-2 is contacted with one side of a guide rod 2-7, the guide rod 2-7 is arranged in a guide seat 2-4 and a fastening guide stud 2-3 to ensure that the guide rod 2-7 can accurately move along the axial direction, the fastening guide stud 2-3 is arranged on the guide seat 2-4 through threads, the guide seat 2-4 is arranged on the hydraulic cylinder cover 3-6 through threads, one end of a disc spring 2-5 arranged in the guide seat 2-4 is contacted with the end face of the fastening guide stud 2-3, and the other end is contacted with a retaining ring of the guide rod 2-7 to ensure that the other side of the guide rod 2-7 is axially and tightly contacted with the end face of a piston rod 3-1, therefore, the axial displacement of the piston rod 3-1 is transmitted to the displacement sensor in real time through the guide rod, and the sealing ring 2-6 is used for preventing hydraulic oil from leaking into the guide seat 2-4.
The real-time position of the piston rod 3-1 is measured through the displacement measuring assembly 2, hydraulic oil charging and discharging operations in each hydraulic cylinder component 3 are achieved through an external oil circuit interface communicated with the valve block 5, and then displacement of each piston rod 3-1 in the hydraulic cylinder 3 is controlled, and the piston rod 3-1 can work within a designated position range in the hydraulic cylinder component 3 when the thrust bearing is under different thrust working conditions.
Referring to fig. 3 to 4, the specific structure and the operation principle of the hydraulic damping device will be described.
The hydraulic vibration damping device mainly comprises a hydraulic cylinder component 3, a communicating valve block 5, a hydraulic oil pipe 15, an exhaust valve 16, a damping valve block 17, stop valves A-D (from top to bottom) 17-1, damping hole pipes E-H (from top to bottom) 17-2, a container group 18, stop valves I-M (from top to bottom) 18-1 and hydraulic containers N-R (from top to bottom) 18-2. The damping valve block 17 is provided with a plurality of hydraulic damping units with different apertures, which are arranged in parallel, each hydraulic damping unit comprises a stop valve 17-1 and a damping hole pipe 17-2, and the variable damping function of the system is realized through the combination arrangement of the different hydraulic damping units. The container group 18 comprises a plurality of hydraulic volume units which are arranged in parallel, each hydraulic volume unit comprises a stop valve 18-1 and a hydraulic container 18-2, and the variable stiffness function is realized through the combination arrangement of different volume units.
FIG. 7 is a basic principle diagram of hydraulic damping, having a total of n cross-sectional areas A0The small oil cylinder is supported on the bearing and pushing seat and is connected to the V-shaped oil cylinder through a pipeline1The total volume of the oil tank, the oil cylinder, the pipeline and the oil tank is V. The displacement measuring assembly 2 is subjected to the liquid pressure P) under a thrust force F ═ a0Under the action of P, the hydraulic cylinder component 3 is communicated with the oil tank 4, and the total volume V changes as follows due to the equivalent transmission of the hydraulic pressure:
in the formula, β represents a compression set coefficient, and β is 1/E.
q is a volume deformation coefficient under the action of oil pressure in consideration of an oil tank and the like.
Then under the effect of thrust F, the displacement s of hydro-cylinder is:
the corresponding stiffness K is then:
wherein: e is the liquid rigidity, q is the deformation coefficient, n is the number of hydraulic cylinders, A0Is the cylinder area and V is the total liquid volume.
From the above formula, it can be seen that, under the condition that the average bulk modulus E of the hydraulic oil is basically unchanged, only the total area nA of the oil cylinder is reduced0Or by increasing the tank volume V1To increase the total volume V, the stiffness K can be adjusted to a sufficiently small value.
According to the natural frequency f of a shafting:
wherein: k is the shafting rigidity, and m is the shafting quality.
After the natural frequency of the shafting is reduced, the longitudinal vibration transmission of the shafting can be reduced, and the effect of vibration reduction of the shafting is achieved.
By opening and closing the stop valves I-M (from top to bottom) 18-1, whether the hydraulic containers N-R (from top to bottom) 18-2 with different volumes are connected to the oil circuit or not can be controlled. The hydraulic system is connected into the oil circuit in a combined mode through a plurality of hydraulic oil with different volumes, so that the total volume of the hydraulic oil in the oil circuit is changed, and the aim of adjusting the rigidity of the hydraulic system to an expected value range can be achieved.
To facilitate the evacuation of the gas from the hydraulic tank N-R (from top to bottom) 18-2 during the loading of hydraulic oil, a separate vent valve 16 is mounted on the hydraulic tank N-R (from top to bottom) 18-2.
Meanwhile, the relationship between the liquid viscosity damping coefficient and the pipeline area is as follows:
wherein: r is the fluid viscosity damping coefficient, μ is the hydrodynamic viscosity, l is the length of the pipeline, A0Is the area of the cylinder, A1Is the pipe area.
Through the opening and closing of the stop valves A-D (from top to bottom) 17-1, whether the damping hole pipes E-H (from top to bottom) 17-2 with different diameters in the oil circuit are connected into the oil circuit or not can be controlled, the damping hole pipes with different diameters are connected into the oil circuit in a combined mode, accordingly, the viscous damping in the oil circuit is changed, and the aim of adjusting the damping of the hydraulic system to the expected value range can be achieved.
Through the switching of stop valve, rigidity and damping that can hydraulic oil among the dynamic control hydraulic system, consequently can adapt to different application scenes and operating mode, and can realize various thrust level thrust bearing damping uses, and this set of hydraulic damping system application scope is wider, and the universality is stronger.
Referring to fig. 5 to 6, the oil passage arrangement and the control principle of the pressure-regulating control device will be described.
The pressure regulating control device mainly comprises a displacement measuring assembly 2, a hydraulic cylinder component 3, a communicating valve block 5, a hydraulic oil pipe 15, an exhaust valve 16, a piston position PID controller 19, a first overflow valve 20, an oil tank 21, a manual pump 22, an electric pump 23, a one-way valve 24, a second overflow valve 25, an energy accumulator 26, a first pressure sensor 27, an adjustable throttle valve 28, a servo valve 29 and a second pressure sensor 30.
Hydraulic oil in the oil circuit of the pressure regulating control device is sucked from the oil tank 21 by the electric pump 23, sequentially passes through the one-way valve 24, the adjustable throttle valve 28, the servo valve 29, the communicating valve block 5 and the hydraulic oil pipe 15, and enters each hydraulic cylinder component 3 to be filled with oil and pressurized; the hydraulic oil in the hydraulic cylinder part 3 is discharged to the oil tank 21 for oil discharge and pressure reduction through the servo valve 29 and the adjustable throttle valve 28. When the thrust bearing operates, the thrust transmitted to the piston rod 3-1 changes along with the change of the thrust of the stern shaft, the piston rod 3-1 dynamically moves along the axis, the position measuring component 2 collects the position of the piston rod 3-1 in real time and transmits a position signal to the piston position PID controller 19, after the position signal is processed and calculated, the piston position PID controller 19 controls the servo valve 29 to charge and discharge oil to the hydraulic cylinder component 3, and the position of the piston rod 3-1 is controlled to be in a set working range, so that the closed-loop control of the piston position is realized.
The first overflow valve 20 in the oil path of the pressure regulating control device is used for controlling the pressure of the vibration damping system to work within a specified range, and the pressure of the vibration damping system caused by the conditions of thrust sudden increase and the like is prevented from exceeding the upper limit of the working pressure of the system. And a second overflow valve 25 in the oil circuit of the pressure regulating control device is used for controlling the pressure in the oil-filled loop to work within a specified range and preventing the pressure of the oil-filled loop from exceeding the specified upper limit of the oil-filled pressure. The accumulator 26 is used for stabilizing and controlling the working pressure of the system and can be used as a pressure source, the manual pump 22 is used for emergency operation of oil supply of a pressure regulating control device under the condition that the control loop is out of power, and the adjustable throttle valve 28 is used for regulating the flow and back pressure of the oil charging and discharging loop, so that the servo valve 29 works in a better control range, and the closed-loop control response and stability of the piston position are improved. The first pressure sensor 27 is used for monitoring oil pressure of an oil supply loop, the second pressure sensor 30 is used for monitoring oil pressure of a damping system, thrust borne by the thrust bearing can be converted according to the total area of the oil cylinder, and real-time display of the thrust is achieved.
The application provides a take hydraulic pressure damping and controlling means's thrust bearing, structural design is more reasonable, and control is more accurate, can adjust the rigidity and the damping of liquid simultaneously, guarantees to normally work under great operating mode within range and different application scenes. The requirements of vibration reduction and noise reduction of the large ship can be met, and the requirement of universality of the thrust bearing can be met. The safety and the comfort in the operation process of the large ship are ensured, and meanwhile, the maneuverability of the large ship is also ensured. The thrust bearing of this set of hydraulic damping scheme application scope is wider, provides a more excellent scheme for thrust bearing's damping design.
Furthermore, the volume of the hydraulic oil cavity can be adjusted according to the practical application condition by adjusting the balance position of the piston head and selecting the proper size of the hydraulic oil cavity so as to adjust the size of the axial clearance of the thrust bearing.
Furthermore, the electric pump and the manual pump can work independently, and the system can be operated safely and reliably.
Furthermore, an oil-filled energy accumulator is arranged in an oil supply oil path of the pressure regulating control device, a certain amount of hydraulic oil higher than the oil pressure of the vibration reduction system is stored in the oil-filled energy accumulator, and when the control device needs to fill oil into the hydraulic oil cavity of the hydraulic cylinder component, the hydraulic oil stored in the energy accumulator can be filled into the hydraulic cylinder component through a servo valve, so that the oil-filled effect is achieved by replacing an electric pump. The electric pump is restarted when the pressure in the oil-filled circuit is lower than a prescribed value. The oil-filled accumulator can prevent the electric pump or the manual pump from working for a long time.
The application provides a take hydraulic pressure damping and controlling means's thrust bearing can effectively reduce the vibration noise of large-scale boats and ships at the operation in-process to through reasonable structural design, system layout, parameter setting, guaranteed still can effectively work in full operating mode scope, different application occasions, further promoted the universality.
The above description is only the preferred embodiments of the present application to make it clear for those skilled in the art how to practice the present application, and these embodiments do not limit the scope of the present application. It will be apparent to those skilled in the art that various modifications and enhancements can be made without departing from the principles of the application, and such modifications and enhancements are intended to be included within the scope of the application.
Claims (12)
1. A thrust bearing is characterized by comprising a box body and a thrust shaft rotatably arranged in the box body, wherein the thrust shaft is provided with a thrust disc in the circumferential direction, one side of the box body corresponding to the thrust disc is provided with a thrust block, and the thrust block is positioned on a thrust disc; the thrust piece correspond the position be equipped with box sealing connection's hydraulic damping device, hydraulic damping device includes:
the hydraulic cylinder component is hermetically arranged on one side of the box body, a piston rod is arranged in the middle of the hydraulic cylinder component, and one end of the piston rod extends into the box body and is connected with the thrust block; hydraulic oil is filled in the hydraulic cylinder part to form a hydraulic oil cavity;
the displacement measurement assembly comprises a guide rod and a displacement sensor; the guide rod is abutted against the other end of the piston rod in real time; the displacement sensor is abutted with one end of the guide rod, which is far away from the piston rod; and
the communication valve block is provided with a first connecting end, a second connecting end and a third connecting end; the first connecting end is communicated with the box body and the hydraulic oil cavity; the second connecting end is communicated with the container group; the third link is connected to the pressure regulating control device, the pressure regulating control device with displacement sensor electric connection for according to displacement sensor's real-time detection distance is adjusted in real time the pressure of hydraulic oil intracavity hydraulic oil, so that the thrust disc is in balanced position.
2. The thrust bearing of claim 1, wherein a plurality of thrust blocks are provided along a circumferential direction of the thrust shaft, each thrust block is assembled with a thrust bearing seat through a positioning column, the thrust bearing seat is axially slidably assembled with the housing through a positioning guide pin, and the other side of the thrust bearing seat abuts against an end of the piston rod.
3. The thrust bearing of claim 2, wherein the contact surface of said thrust bearing and said housing is further provided with a wear-resistant damping layer.
4. The thrust bearing of claim 1, wherein said hydraulic cylinder component further comprises:
the hydraulic cylinder sleeve is arranged corresponding to the piston rod and is connected with the box body in a sealing mode;
the guide sleeve is connected with one side, facing the box body, of the hydraulic cylinder sleeve in a sealing mode; the piston rod is fixed in the guide sleeve and arranged along the axial direction of the thrust shaft; and
the hydraulic cylinder cover is connected with one side of the hydraulic cylinder sleeve, which is far away from the guide sleeve, in a sealing way; the hydraulic cylinder sleeve, the piston rod and the hydraulic cylinder cover are arranged in an enclosing mode to form the hydraulic oil cavity.
5. The thrust bearing of claim 4, wherein said hydraulic cylinder component further comprises:
the support ring is arranged between the piston rod and the guide sleeve and is arranged around the axial direction of the piston rod; and
and the sealing ring is arranged among the piston rod, the hydraulic cylinder cover and the hydraulic cylinder sleeve and surrounds the axial direction of the piston rod.
6. The thrust bearing of claim 4, wherein said communication valve block communicates with said hydraulic oil chamber through a hydraulic oil line; the hydraulic cylinder cover is provided with an oil pipe mounting hole, and the hydraulic oil pipe is connected with the oil pipe mounting hole of the hydraulic cylinder cover.
7. The thrust bearing of claim 4, wherein the displacement measurement assembly comprises:
a guide seat mounted to the hydraulic cylinder head;
the middle part of the guide rod is provided with a baffle ring which can be arranged in the guide seat in a sliding way; two ends of the guide rod respectively extend out of the guide seat; the displacement sensor is provided with a displacement sensor probe, one end of the guide rod is abutted with the displacement sensor probe, and the other end of the guide rod is abutted with the piston rod; and
and the disc spring is arranged in the guide seat and is abutted against the baffle ring so that the guide rod is kept in abutment against the piston head of the hydraulic cylinder part in real time.
8. The thrust bearing of claim 7, wherein the displacement measurement assembly further comprises:
a sensor mount mounted to the hydraulic cylinder head; the displacement sensor is fixed on the sensor bracket; and
and the fastening guide stud is detachably arranged at one end of the guide seat facing the displacement sensor, and the fastening guide stud is sleeved on the outer side of the guide rod and is abutted to the disc spring.
9. The thrust bearing of claim 4, wherein an exhaust valve is further provided on said hydraulic cylinder head, said communication valve block, or said container group.
10. The thrust bearing of claim 1, wherein said hydraulic damping means is provided in plurality, and a plurality of said hydraulic damping means are uniformly arranged in a circumferential direction of said thrust shaft.
11. The thrust bearing of claim 1, wherein the thrust bearing further comprises a damping valve block; the damping valve block is provided with a plurality of hydraulic damping units with different apertures, which are arranged in parallel, and each hydraulic damping unit comprises a stop valve and a damping hole pipe.
12. The thrust bearing of claim 1, wherein the set of containers comprises a plurality of hydraulic volume units arranged in parallel, each hydraulic volume unit comprising a shut-off valve and a hydraulic container.
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| CN202110833050.8A CN113494525B (en) | 2021-07-22 | 2021-07-22 | Thrust bearing |
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| CN114084330A (en) * | 2021-12-13 | 2022-02-25 | 中国船舶重工集团公司第七0四研究所 | Water-tight box of shaft type oil distributor |
| CN114572373A (en) * | 2022-03-21 | 2022-06-03 | 浙江海洋大学 | High-stability ship propulsion device based on hydraulic thrust bearing |
| CN115489709A (en) * | 2022-10-08 | 2022-12-20 | 中国舰船研究设计中心 | A thrust bearing vibration isolation structure |
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