CN111550522A - Ship propulsion shafting with high static and low dynamic stiffness oscillator periodic structure - Google Patents

Ship propulsion shafting with high static and low dynamic stiffness oscillator periodic structure Download PDF

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CN111550522A
CN111550522A CN202010427123.9A CN202010427123A CN111550522A CN 111550522 A CN111550522 A CN 111550522A CN 202010427123 A CN202010427123 A CN 202010427123A CN 111550522 A CN111550522 A CN 111550522A
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propulsion shafting
oscillator
stiffness
low dynamic
periodic structure
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CN111550522B (en
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杨志荣
王岩
于洪亮
王竟科
汝鹏
陈凤梅
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Jimei University
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Jimei University
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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
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
    • F16F15/1414—Masses driven by elastic elements
    • 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
    • B63H23/34—Propeller shafts; Paddle-wheel shafts; Attachment of propellers on 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
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • 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
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/16—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material
    • F16F15/167—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material having an inertia member, e.g. ring
    • 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
    • F16F2222/00—Special physical effects, e.g. nature of damping effects
    • F16F2222/08—Inertia
    • 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
    • F16F2222/00—Special physical effects, e.g. nature of damping effects
    • F16F2222/10—Adhesion
    • 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
    • F16F2238/00—Type of springs or dampers
    • F16F2238/02—Springs
    • F16F2238/026—Springs wound- or coil-like
    • 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
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T70/00—Maritime or waterways transport
    • Y02T70/10—Measures concerning design or construction of watercraft hulls

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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)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Ocean & Marine Engineering (AREA)
  • Vibration Prevention Devices (AREA)

Abstract

The invention provides a ship propulsion shafting with a high static stiffness oscillator periodic structure and a low dynamic stiffness oscillator periodic structure, and relates to the technical field of vibration reduction of ship propulsion shafting. The ship propulsion shafting with the high static and low dynamic stiffness vibrator periodic structure comprises a propulsion shafting, wherein a plurality of inner holes which are longitudinally and periodically arranged are arranged in the propulsion shafting, each inner hole comprises a high static and low dynamic stiffness mass vibrator, and when the mass vibrators are in static balance positions, a negative stiffness mechanism and a positive stiffness mechanism are connected in parallel and overlapped to form a high static and low dynamic stiffness mechanism. The mass vibrators with high static stiffness and low dynamic stiffness are periodically arranged in the ship propulsion shafting, so that low-frequency or ultralow-frequency longitudinal vibration band gap vibration reduction of the ship propulsion shafting can be realized, and the mass vibrators are arranged in the inner hole, so that the space is saved, the structure is compact, the stability is better, and the engineering application and popularization prospect is better.

Description

Ship propulsion shafting with high static and low dynamic stiffness oscillator periodic structure
Technical Field
The invention relates to the technical field of vibration reduction of a ship propulsion shafting, in particular to a ship propulsion shafting with a high static stiffness and low dynamic stiffness oscillator periodic structure.
Background
The propeller is the main propulsion device of the water surface ship, the ship sails in water, an uneven wake field is inevitably formed at the stern, the propeller rotates in the uneven wake field to generate pulsating thrust which is transmitted to the ship body through the propulsion shafting, the stern bearing, the middle bearing, the thrust bearing and the base thereof to cause the ship body to vibrate, and further underwater sound radiation is formed, the ship propulsion shafting is the main path for transmitting the exciting force generated when the propeller works to the shell, therefore, effective control measures are particularly important for the shafting vibration, the key point of low-frequency vibration noise control caused by the excitation of the stern of the ship is that the longitudinal vibration control is mainly to reduce the secondary pulsating exciting force transmitted to the ship body through the thrust bearing base, and the longitudinal force transmission path is the propeller, the transmission shaft and the thrust bearing, Thrust bearing base, between the hull, consequently can only keep apart or subduct the vibration source on this route, the vertical dead thrust of propulsion shafting is generally great, the isolator need bear great dead load, consequently, the vibration isolation has certain degree of difficulty, so the most dynamic vibration absorbers of installing of research of shafting longitudinal vibration control technique, still lack the effective measure to low frequency longitudinal vibration control, the low band gap characteristic of the low dynamic stiffness oscillator periodic structure of height quiet low is applied to and is promoted the shafting damping and have very big potentiality, can avoid traditional dynamic vibration absorption technique to the low frequency band or the poor not enough of super low frequency channel vibration absorption effect.
Disclosure of Invention
Technical problem to be solved
Aiming at the defects of the prior art, the invention provides a ship propulsion shafting with a periodic structure of high-static-low dynamic stiffness vibrators, and solves the problem that the low-frequency or ultralow-frequency longitudinal vibration of the ship propulsion shafting is difficult to control in the prior art.
(II) technical scheme
In order to achieve the purpose, the invention is realized by the following technical scheme: a ship propulsion shafting with a high static stiffness vibrator and low dynamic stiffness vibrator periodic structure comprises a propulsion shafting, wherein a plurality of inner holes which are longitudinally and periodically arranged are arranged in the propulsion shafting, mass vibrators are arranged in the inner holes, the top of one side of each mass vibrator is fixedly connected to one end of a first viscous damper, the bottom of the same side of each mass vibrator is fixedly connected to one end of a first linear spring, the top of the other side of each mass vibrator is fixedly connected to one end of a second viscous damper, the bottom of the same side of each mass vibrator is fixedly connected to one end of a second linear spring, the top end of each mass vibrator is fixedly connected with a first cam, a first roller is arranged at the top of each first cam, the first roller is rotatably connected to the middle position of a first rack, one side of the top of the first rack is fixedly connected to the bottom end of a third linear spring, and the other side of the top of the, the mass oscillator bottom fixedly connected with second cam, second cam bottom is provided with the second gyro wheel, the second gyro wheel rotates the intermediate position of connection at the second frame, second frame bottom one side fixed connection is on the top of fourth linear spring and second frame bottom opposite side fixed connection is on the top of fourth viscidity damper.
Preferably, the other ends of the first viscous damper and the first linear spring are fixedly connected to one side wall in the inner hole.
Preferably, the other ends of the second viscous damper and the second linear spring are fixedly connected to the other side wall in the inner hole.
Preferably, the top ends of the third linear spring and the third viscous damper are fixedly connected to the top side wall in the inner hole.
Preferably, the bottom ends of the fourth linear spring and the fourth viscous damper are fixedly connected to the bottom side wall in the inner hole.
Preferably, both sides of the first frame and the second frame are fixedly connected with sliding blocks, and the sliding blocks are connected with the inner wall of the inner hole in a sliding manner.
The working principle is as follows: a negative stiffness mechanism is formed by the first roller 9 and the first cam 8, and a positive stiffness mechanism is formed by the first linear spring 5 and the second linear spring 7 by the second roller 15 and the second cam 14; when the mass oscillator 3 is at a static balance position, the negative stiffness mechanism and the positive stiffness mechanism are connected in parallel and overlapped to form a high static stiffness mechanism and a low dynamic stiffness mechanism. Performing static analysis on the high static stiffness mechanism and the low dynamic stiffness mechanism (see figure 2); a mass oscillator 3 having a mass m; the damping coefficient c of the first viscous damper 4 and the second viscous damper 6hThe horizontal direction damper of (1); the first linear spring 5 and the second linear spring 7 have a stiffness khThe horizontal spring of (1); the first cam 8 and the second cam 14 are semicircular cams with the radius of R; the first roller 9 and the second roller 15 are round rollers with radius r; the third linear spring 12 and the fourth linear spring 17 have the rigidity kvA vertical spring of (a); the third viscous damper 13 and the fourth viscous damper 18 have a damping coefficient cvThe vertical direction damper of (1); when the system is in static equilibrium, the fourth linear spring 17 is compressed by an amount of1The amount of compression of the third linear spring 12 is2Considering the influence of gravity, then:
kv(1-2)＝mg (1)
the sum of the horizontal rigidities is 2khWhen x displacement occurs in the horizontal direction, the corresponding elastic restoring force is:
Figure BDA0002499117760000031
Figure BDA0002499117760000032
at this time, the process of the present invention,
Figure BDA0002499117760000033
if it is
Figure BDA0002499117760000034
The cam roller is disengagedFrom, the corresponding elastic restoring force is f 2khx. The elastic force is derived, and the dynamic stiffness displacement expression of the system is obtained as follows:
Figure BDA0002499117760000035
when the system is in a static equilibrium position,
Figure BDA0002499117760000041
when the structural parameters satisfy
Figure BDA0002499117760000042
The system has the characteristics of quasi-zero dynamic stiffness, namely high static stiffness and low dynamic stiffness; when the mass vibrators with ultralow natural frequency are arranged along the longitudinal cycle of the shafting, a propulsion shafting periodic structure is formed, and the periodic structure can show attenuation domain characteristics of elastic waves, namely band gap characteristics. When the frequency of the elastic wave falls within the band gap range, the propagation of the elastic wave is greatly attenuated, and the vibration reduction effect is obviously improved. Therefore, the periodic structure has the isolation capability for certain low-frequency band or ultra-low frequency elastic waves. When the propeller works in the uneven wake field, the propeller bears the action of longitudinal pulsation exciting force, the characteristic frequency of the longitudinal pulsation exciting force is low frequency or ultralow frequency, once the low-frequency longitudinal elastic wave falls into a longitudinal vibration suppression frequency band gap of the propulsion shafting, longitudinal vibration can be suppressed, and therefore control of longitudinal vibration of the propulsion shafting is achieved.
(III) advantageous effects
The invention provides a ship propulsion shafting with a high-static-low dynamic stiffness oscillator periodic structure. The method has the following beneficial effects:
1. according to the invention, the high static and low dynamic stiffness mechanism is formed by the first linear spring, the second linear spring, the first cam, the first roller, the second cam and the second roller, so that the mass vibrators have the characteristic of low frequency and are periodically arranged along the shafting to form a periodic structure of the propulsion shafting, and thus the low-frequency or ultralow-frequency longitudinal vibration band gap vibration reduction of the ship propulsion shafting can be realized by the vibrators with high static and low dynamic stiffness.
2. According to the invention, the mass oscillator is arranged in the inner hole of the ship propulsion shafting, so that the space can be saved, the structure is more compact, the stability is better, the adverse effect on the mass oscillator when the propulsion shafting rotates is greatly reduced, and the invention has better engineering application and popularization prospects.
Drawings
FIG. 1 is a schematic view of the overall structure of the present invention;
fig. 2 is a schematic structural diagram of a mass oscillator unit according to the present invention.
Wherein, 1, a propulsion shaft system; 2. an inner bore; 3. a mass oscillator; 4. a first viscous damper; 5. a first linear spring; 6. a second viscous damper; 7. a second linear spring; 8. a first cam; 9. a first roller; 10. a first frame; 11. a slider; 12. a third linear spring; 13. a third viscous damper; 14. a second cam; 15. a second roller; 16. a second frame; 17. a fourth linear spring; 18. a fourth viscous damper.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
Example (b):
as shown in fig. 1-2, an embodiment of the present invention provides a ship propulsion shafting with a periodic structure of high static stiffness and low dynamic stiffness vibrators, which includes a propulsion shafting 1, a plurality of inner holes 2 arranged longitudinally and periodically are arranged in the propulsion shafting 1, the inner holes 2 are all provided with mass vibrators 3, the mass vibrators 3 are arranged in the inner holes 2, so that more space can be saved, the structure of the propulsion shafting 1 is more compact, the stability is better, and adverse effects on the mass vibrators 3 during working and rotating of the propulsion shafting 1 can be greatly reduced, the top of one side of the mass vibrator 3 is fixedly connected to one end of a first viscous damper 4, the bottom of the same side of the mass vibrator 3 is fixedly connected to one end of a first linear spring 5, the top of the other side of the mass vibrator 3 is fixedly connected to one end of a second viscous damper 6, and the bottom of the same side of the mass vibrator 3 is fixedly connected to one, inertia force generated when the mass oscillator 3 vibrates can be borne through the first linear spring 5 and the second linear spring 7, a first cam 8 fixedly connected to the top end of the mass oscillator 3, a first roller 9 is arranged at the top of the first cam 8, the first roller 9 is rotatably connected to the middle position of the first frame 10, one side of the top of the first frame 10 is fixedly connected to the bottom end of the third linear spring 12 and the other side of the top of the first frame 10 is fixedly connected to the bottom end of the third viscous damper 13, a second cam 14 is fixedly connected to the bottom end of the mass oscillator 3, a second roller 15 is arranged at the bottom of the second cam 14, the second roller 15 is rotatably connected to the middle position of the second frame 16, one side of the bottom of the second frame 16 is fixedly connected to the top end of the fourth linear spring 17 and the other side of the bottom of the second frame 16 is fixedly connected to the top. The equal fixed connection of the other end of first viscidity attenuator 4 and first linear spring 5 is the lateral wall on one side in hole 2, the equal fixed connection of the other end of second viscidity attenuator 6 and second linear spring 7 is the another side lateral wall in hole 2, the equal fixed connection in top lateral wall in hole 2 in top of third linear spring 12 and third viscidity attenuator 13, the equal fixed connection in bottom lateral wall in hole 2 in bottom of fourth linear spring 17 and fourth viscidity attenuator 18, the equal fixedly connected with slider 11 in both sides of first frame 10 and second frame 16, be sliding connection between slider 11 and the inner wall of hole 2, slider 11 makes first frame 10 and second frame 16 can remove in hole 2, can restrict first frame 10 and second frame 16 again through the inner wall of hole 2 simultaneously and can only remove according to the direction of injecing. A negative stiffness mechanism is formed by the first roller 9 and the first cam 8, and a positive stiffness mechanism is formed by the first linear spring 5 and the second linear spring 7 by the second roller 15 and the second cam 14; when the mass oscillator 3 is in a static balance position, the negative stiffness mechanism and the positive stiffness mechanism are connected in parallel and overlapped to form a high static stiffness mechanism and a low dynamic stiffness mechanism, and the mass oscillator 3 has the characteristic of low frequency or ultralow frequency. When the mass vibrators 3 with the ultralow natural frequency are arranged along the longitudinal period of the propulsion shafting 1, a propulsion shafting periodic structure is formed, and the periodic structure can show the attenuation domain characteristic of elastic waves. When the frequency of the elastic wave falls within the band gap range, the propagation of the elastic wave is greatly attenuated, and the vibration reduction effect is obviously improved; when the propeller works in the uneven wake field, the propeller bears the action of low-frequency or ultralow-frequency longitudinal pulsation excitation force, once the low-frequency longitudinal elastic wave falls into a longitudinal vibration suppression frequency band gap of the propulsion shafting, longitudinal vibration can be suppressed, and therefore control of longitudinal vibration of the propulsion shafting is achieved.
Although embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that changes, modifications, substitutions and alterations can be made in these embodiments without departing from the principles and spirit of the invention, the scope of which is defined in the appended claims and their equivalents.

Claims (6)

1. The utility model provides a take boats and ships propulsion shafting of high quiet low dynamic stiffness oscillator periodic structure, includes propulsion shafting (1), its characterized in that: be provided with hole (2) that a plurality of longitudinal cycle was arranged in propulsion shafting (1), all be provided with mass oscillator (3) in hole (2), the top fixed connection of mass oscillator (3) one side is in the one end of first viscidity attenuator (4) and the bottom fixed connection of mass oscillator (3) homonymy the one end in first linear spring (5), the top fixed connection of mass oscillator (3) opposite side is in the one end of second viscidity attenuator (6) and the bottom fixed connection of mass oscillator (3) homonymy the one end in second linear spring (7), mass oscillator (3) top fixed connection has first cam (8), first cam (8) top is provided with first gyro wheel (9), first gyro wheel (9) rotate the intermediate position of connecting in first frame (10), first frame (10) top one side fixed connection is in the bottom of third linear spring (12) and first frame (10) top Opposite side fixed connection is in the bottom of third viscidity attenuator (13), quality oscillator (3) bottom fixedly connected with second cam (14), second cam (14) bottom is provided with second gyro wheel (15), second gyro wheel (15) rotate to be connected the intermediate position in second frame (16), second frame (16) bottom one side fixed connection is on the top of fourth linear spring (17) and second frame (16) bottom opposite side fixed connection is on the top of fourth viscidity attenuator (18).
2. The ship propulsion shafting with the high static stiffness and low dynamic stiffness oscillator periodic structure as claimed in claim 1, wherein: the other ends of the first viscous damper (4) and the first linear spring (5) are fixedly connected with one side wall in the inner hole (2).
3. The ship propulsion shafting with the high static stiffness and low dynamic stiffness oscillator periodic structure as claimed in claim 1, wherein: the other ends of the second viscous damper (6) and the second linear spring (7) are fixedly connected with the other side wall in the inner hole (2).
4. The ship propulsion shafting with the high static stiffness and low dynamic stiffness oscillator periodic structure as claimed in claim 1, wherein: the top ends of the third linear spring (12) and the third viscous damper (13) are fixedly connected to the top side wall in the inner hole (2).
5. The ship propulsion shafting with the high static stiffness and low dynamic stiffness oscillator periodic structure as claimed in claim 1, wherein: the bottom ends of the fourth linear spring (17) and the fourth viscous damper (18) are fixedly connected to the side wall of the bottom in the inner hole (2).
6. The ship propulsion shafting with the high static stiffness and low dynamic stiffness oscillator periodic structure as claimed in claim 1, wherein: the two sides of the first rack (10) and the second rack (16) are fixedly connected with sliding blocks (11), and the sliding blocks (11) are connected with the inner wall of the inner hole (2) in a sliding mode.
CN202010427123.9A 2020-05-19 2020-05-19 Ship propulsion shafting with high static and low dynamic stiffness oscillator periodic structure Expired - Fee Related CN111550522B (en)

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