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CN113494524A - Pressure regulating control device and thrust bearing - Google Patents

Pressure regulating control device and thrust bearing Download PDF

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Publication number
CN113494524A
CN113494524A CN202110833043.8A CN202110833043A CN113494524A CN 113494524 A CN113494524 A CN 113494524A CN 202110833043 A CN202110833043 A CN 202110833043A CN 113494524 A CN113494524 A CN 113494524A
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CN
China
Prior art keywords
control device
hydraulic oil
regulating control
pressure regulating
oil
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Granted
Application number
CN202110833043.8A
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Chinese (zh)
Other versions
CN113494524B (en
Inventor
李岳峰
李松山
程晓明
俞翔栋
何柳
刘逸斐
黄新源
孙丹婷
田江
陈悦
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711th Research Institute of CSIC
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Shanghai Marine Diesel Engine Research Institute
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Priority to CN202110833043.8A priority Critical patent/CN113494524B/en
Publication of CN113494524A publication Critical patent/CN113494524A/en
Application granted granted Critical
Publication of CN113494524B publication Critical patent/CN113494524B/en
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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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2230/00—Purpose; Design features
    • F16F2230/06—Fluid filling or discharging
    • 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
    • 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
    • F16F2230/18—Control arrangements
    • 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
    • F16F2230/22—Pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/20—Hydro energy

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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 application provides a pressure regulating control device and a thrust bearing. The pressure regulating control device is applied to a thrust bearing, and the thrust bearing comprises a hydraulic oil cylinder part and is communicated to the pressure regulating control device; the pressure regulating control device comprises an oil tank, a pressurization unit and a decompression unit; the pressurizing unit is used for filling hydraulic oil in the oil tank into the thrust bearing hydraulic oil cylinder part so as to increase the pressure of the hydraulic oil; the pressure reducing unit is used for discharging hydraulic oil in the hydraulic oil cylinder part into the oil tank so as to reduce the pressure of the hydraulic oil. This application can effectively reduce the vibration noise of large-scale boats and ships in the operation to through reasonable structural design, system arrangement, the damping parameter sets up, has guaranteed still can effectively work in full operating mode scope, different application occasions, has further promoted the universality.

Description

Pressure regulating control device and thrust bearing
Technical Field
The application relates to the technical field of vibration noise control of large ship power mechanical equipment, in particular to a pressure regulating control device for damping of a ship shafting and a thrust bearing.
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
An object of the application is to provide a pressure regulating control device and thrust bearing, can control thrust bearing system's rigidity and damping through measures such as the volume that changes hydraulic oil, the latus rectum of pipeline according to different operating modes to contained one set of more reasonable hydraulic damping device and control system of structure, when guaranteeing large-scale boats and ships vibration damping and fall the requirement of making an uproar, also guaranteed that the thrust bearing who adopts this set of hydraulic damping and control device is applicable to shafting full operating mode scope vibration damping and uses.
In order to achieve the purpose, the application provides a pressure regulating control device which is applied to a thrust bearing, wherein the thrust bearing comprises a hydraulic oil cylinder part communicated to the pressure regulating control device; the pressure regulating control device comprises an oil tank, a pressurization unit and a decompression unit; two ends of the pressurizing unit are respectively connected with the hydraulic oil cylinder part and the oil tank and used for filling hydraulic oil in the oil tank into the hydraulic oil cylinder part so as to increase the pressure of the hydraulic oil; and two ends of the pressure reducing unit are respectively connected with the hydraulic oil cylinder part and the oil tank and used for reducing the pressure of hydraulic oil by unloading the hydraulic oil in the hydraulic oil cylinder part into the oil tank.
A further development of the application is that the pressure reducing unit comprises a servo valve, an adjustable throttle valve.
The application is further improved in that the pressurization unit comprises an oil supply device, a second overflow valve, an accumulator, an adjustable throttle valve and a servo valve; the servo valve comprises a first interface, a second interface and a third interface; the first interface is communicated with the oil supply device, and the oil supply device is communicated with the oil tank; the second interface is communicated with the oil tank; the third interface is communicated with the hydraulic oil cylinder component; one end of the second overflow valve is connected to the oil tank, and the other end of the second overflow valve is connected between the first interface of the servo valve and the oil supply device; the accumulator is connected between the first port of the servo valve and the oil supply device.
A further development of the application is that the oil supply comprises an electric pump and a manual pump connected in parallel and operating independently of each other.
The application further improves and lies in, oil supply unit still is including locating the electric pump with the check valve of manual pump output.
The further improvement of this application lies in, the first interface of servo valve with between the oil supply unit, and the second interface of servo valve with still be equipped with adjustable choke valve between the oil tank.
The application is further improved in that pressure sensors are arranged between the first interface of the servo valve and the oil supply device and between the third interface of the servo valve and the hydraulic oil cylinder component.
The application is further improved in that a communication valve block is further arranged between the pressure regulating control device and the thrust bearing hydraulic oil cylinder component, 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 to the box body and the hydraulic oil cylinder part; the second connecting end is communicated to the container group; the third connecting end is connected to the pressure regulating control device.
The application is further improved in that the communication valve block is communicated with the hydraulic oil cylinder component 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 pressure regulating control device further comprises a piston position PID controller; and the piston position PID controller is electrically connected with the displacement sensor on the hydraulic oil cavity and is connected with an electrical interface of the servo valve.
The application also provides a thrust bearing, which comprises the pressure regulating control device.
The application provides a pair of pressure regulating controlling means and 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 the operation process to through reasonable structural design, systematic arrangement, parameter setting has guaranteed still can effectively work in full operating mode scope, different application scenario, 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.
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.
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.
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.
The pressure regulating control device is communicated to a hydraulic oil cylinder part 3 of the thrust bearing and used for regulating oil pressure of a hydraulic oil cavity in the hydraulic oil cylinder part 3, and the pressure regulating control device is divided into a pressurizing unit and a pressure reducing unit according to functional modules. The pressure reducing unit comprises a servo valve 29, an adjustable throttle valve 28. Two ends of the pressure reducing unit are respectively connected with the hydraulic oil cavity of the hydraulic oil cylinder component 3 and the oil tank 21, and the pressure reducing unit is used for discharging hydraulic oil in the hydraulic oil cylinder component 3 into the oil tank 21 so as to reduce the oil pressure of the hydraulic oil cavity. The pressurizing unit includes an oil supply device (manual pump 22 and electric pump 23), a second relief valve 25, an accumulator 26, an adjustable throttle valve 28, and a servo valve 29. Two ends of the pressurizing unit are respectively connected with the hydraulic oil cavity of the hydraulic oil cylinder component 3 and the oil tank 21, and the pressurizing unit is used for filling hydraulic oil in the oil tank 21 into the thrust bearing so as to increase the oil pressure of the hydraulic oil cavity. The axial force formed by the oil pressure of the hydraulic oil cavity acts on one side of the piston rod 3-1 and is transmitted to one side of the thrust disc 11 through the thrust bearing middle thrust bearing seat 8, the spherical cushion block 12 and the left thrust block 10, an interaction force is formed with propeller thrust transmitted to the other side of the thrust disc 11 through the stern shaft end, and the thrust disc 11 in the thrust bearing can be in a balance position by adjusting the axial force formed by the oil pressure of the hydraulic oil cavity in real time and balancing the dynamic propeller thrust.
Hydraulic oil in the oil circuit of the pressure regulating control device is sucked from an oil tank 21 by an electric pump 23, sequentially passes through a one-way valve 24, an adjustable throttle valve 28, a servo valve 29, a communication valve block 5 and a hydraulic oil pipe 15, and enters a hydraulic cylinder part 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 (11)

1. A pressure regulating control device is applied to a thrust bearing, wherein the thrust bearing comprises a hydraulic oil cylinder part communicated to the pressure regulating control device; the device is characterized in that the pressure regulating control device comprises an oil tank, a pressurization unit and a decompression unit;
two ends of the pressurizing unit are respectively connected with the hydraulic oil cylinder part and the oil tank and used for filling hydraulic oil in the oil tank into the thrust bearing hydraulic oil cylinder part so as to increase the pressure of the hydraulic oil;
and two ends of the pressure reducing unit are respectively connected with the hydraulic oil cylinder part and the oil tank and used for discharging hydraulic oil in the hydraulic oil cylinder part into the oil tank so as to reduce the pressure of the hydraulic oil.
2. The pressure regulating control device of claim 1, wherein the pressure reducing unit comprises a servo valve, an adjustable throttle valve.
3. The pressure regulating control device according to claim 1, wherein the pressure increasing unit includes an oil supply device, a second relief valve, an accumulator, an adjustable throttle valve, and a servo valve;
the servo valve comprises a first interface, a second interface and a third interface; the first interface is communicated with the oil supply device, and the oil supply device is communicated with the oil tank; the second interface is communicated with the oil tank; the third interface is communicated with the hydraulic oil cylinder component;
one end of the second overflow valve is connected to the oil tank, and the other end of the second overflow valve is connected between the first interface of the servo valve and the oil supply device;
the accumulator is connected between the first port of the servo valve and the oil supply device.
4. The pressure-regulating control device according to claim 3, wherein the oil supply means includes an electric pump and a manual pump connected in parallel and operated independently of each other.
5. The pressure regulating control device according to claim 4, wherein said oil supply means further comprises check valves provided at output ends of said electric pump and said manual pump.
6. The pressure regulating control device according to claim 3, wherein an adjustable throttle valve is further provided between the first port of the servo valve and the oil supply device, and between the second port of the servo valve and the oil tank.
7. The pressure regulating control device of claim 3, wherein pressure sensors are further provided between the first port of the servo valve and the oil supply device, and between the third port of the servo valve and the hydraulic cylinder component.
8. The pressure regulating control device according to claim 3, further comprising a communication valve block between the pressure regulating control device and the thrust bearing hydraulic oil cylinder component, wherein 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 to the hydraulic oil cylinder part; the second connecting end is communicated to the container group; the third connecting end is connected to the pressure regulating control device.
9. The pressure regulating control device according to claim 8, wherein the communication valve block is communicated with the hydraulic cylinder component 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.
10. The pressure regulating control device of claim 3, wherein said pressure regulating control device further comprises a piston position PID controller; and the piston position PID controller is electrically connected with a displacement sensor on the hydraulic oil cylinder part and is connected with an electrical interface of the servo valve.
11. A thrust bearing comprising the pressure regulating control device according to any one of claims 1 to 10.
CN202110833043.8A 2021-07-22 2021-07-22 Pressure regulating control device and thrust bearing Active CN113494524B (en)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1485773A (en) * 1973-11-16 1977-09-14 Mannesmann Ag Hydraulically loaded axial thrust bearing for a shaft provided with a thrust collar more particularly for ship transmission apparatus
CN102297753A (en) * 2011-07-19 2011-12-28 华中科技大学 Test bed for simulating longitudinal vibration of marine propulsion shafting
CN103353395A (en) * 2013-05-27 2013-10-16 武汉理工大学 Hydraulic loading device for large marine propulsion shafting test bed
CN112046721A (en) * 2020-09-23 2020-12-08 东台船用配件有限公司 Automatic displacement compensation thrust bearing
CN113107971A (en) * 2021-05-06 2021-07-13 东台市远洋船舶配件有限公司 Thrust bearing with vibration-damping piston

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1485773A (en) * 1973-11-16 1977-09-14 Mannesmann Ag Hydraulically loaded axial thrust bearing for a shaft provided with a thrust collar more particularly for ship transmission apparatus
CN102297753A (en) * 2011-07-19 2011-12-28 华中科技大学 Test bed for simulating longitudinal vibration of marine propulsion shafting
CN103353395A (en) * 2013-05-27 2013-10-16 武汉理工大学 Hydraulic loading device for large marine propulsion shafting test bed
CN112046721A (en) * 2020-09-23 2020-12-08 东台船用配件有限公司 Automatic displacement compensation thrust bearing
CN113107971A (en) * 2021-05-06 2021-07-13 东台市远洋船舶配件有限公司 Thrust bearing with vibration-damping piston

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