CN114291209A - Adjustable-stiffness transverse damper, mooring device, system and method - Google Patents
Adjustable-stiffness transverse damper, mooring device, system and method Download PDFInfo
- Publication number
- CN114291209A CN114291209A CN202111682017.6A CN202111682017A CN114291209A CN 114291209 A CN114291209 A CN 114291209A CN 202111682017 A CN202111682017 A CN 202111682017A CN 114291209 A CN114291209 A CN 114291209A
- Authority
- CN
- China
- Prior art keywords
- spring
- motor
- damper
- mooring
- rigid arm
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000000034 method Methods 0.000 title claims abstract description 21
- 230000005284 excitation Effects 0.000 claims description 25
- 230000007246 mechanism Effects 0.000 claims description 17
- 238000012544 monitoring process Methods 0.000 claims description 14
- 230000000694 effects Effects 0.000 abstract description 6
- 230000009467 reduction Effects 0.000 abstract description 4
- 229910000831 Steel Inorganic materials 0.000 description 14
- 239000010959 steel Substances 0.000 description 14
- 230000033001 locomotion Effects 0.000 description 13
- 230000009471 action Effects 0.000 description 10
- 238000010586 diagram Methods 0.000 description 10
- 230000008569 process Effects 0.000 description 6
- 238000005096 rolling process Methods 0.000 description 6
- 238000013016 damping Methods 0.000 description 5
- 230000009286 beneficial effect Effects 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 230000002411 adverse Effects 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 238000009826 distribution Methods 0.000 description 2
- 230000005484 gravity Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 238000005260 corrosion Methods 0.000 description 1
- 230000007797 corrosion Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000011150 reinforced concrete Substances 0.000 description 1
- 239000013535 sea water Substances 0.000 description 1
- 230000008054 signal transmission Effects 0.000 description 1
- 230000000087 stabilizing effect Effects 0.000 description 1
- 238000003860 storage Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Images
Abstract
The invention relates to a stiffness-adjustable transverse damper, a mooring device, a system and a method, comprising: the damper is provided with a mass block, and the mass block can move along the extension direction of the damper; the motor is arranged on the damper and is respectively positioned on two opposite sides of the mass block, the motor is connected with the mass block through a spring, and the motor can adjust the number of effective turns between the motor and the mass block. The rigidity-adjustable transverse damper, the mooring device, the mooring system and the method can adjust the rigidity of the spring between the motor and the mass block, further adjust the natural frequency of the whole rigidity-adjustable transverse damper, can achieve a good vibration reduction effect aiming at waves with different frequencies, can be arranged outside the mooring rigid arm, and can be applied to any form of mooring rigid arm.
Description
Technical Field
The invention relates to the technical field of vibration reduction of marine oil and gas platforms of ships and ocean engineering, in particular to a transverse damper with adjustable rigidity, a mooring device, a mooring system and a mooring method.
Background
At present, a Floating Production Storage and Offloading (FPSO) soft rigid arm single-point mooring device is an offshore mooring and oil-gas transmission facility with a complex structure and high manufacturing cost, the environment and the working condition are quite severe, the device needs to bear the actions of wind waves, water flow, seawater corrosion, mechanical disturbance and the like, and sometimes needs to be subjected to accidental impacts such as earthquakes, tsunamis, typhoons, ice impacts or ship impacts, and the safety degree of the structure is always a great concern in the field of offshore oil production engineering.
The mooring rigid arm on the soft rigid arm single-point mooring device often can generate larger rolling and pitching in the mooring process, the overlarge swinging is not beneficial to the stable state of the FPSO ship, the larger movement displacement causes the structure to be subjected to the increase of the alternating stress peak value, and the strength and the fatigue life of the structure are also adversely affected.
In the related art, a Tuned Liquid Damper (TLD) is generally adopted to damp a mooring rigid arm. However, the TLD has a vibration damping and anti-rolling effect only for a single frequency, has a poor vibration damping effect for waves with different frequencies, and cannot damp all sea conditions, and the TLD has a single application form, has a high requirement on the size of a box body only for a rectangular box body mooring rigid arm, and cannot be applied to a bottle-shaped or other forms of mooring rigid arms.
Therefore, there is a need to design a new stiffness-adjustable lateral damper to overcome the above problems.
Disclosure of Invention
Embodiments of the present invention provide a stiffness-adjustable lateral damper, a mooring apparatus, a system, and a method, to solve the problem that TLD in the related art cannot damp all sea conditions and cannot be applied to a bottle-shaped or other form of mooring rigid arm.
In a first aspect, there is provided an adjustable stiffness transverse damper comprising: the damper is provided with a mass block, and the mass block can move along the extension direction of the damper; the motor is arranged on the damper and is respectively positioned on two opposite sides of the mass block, the motor is connected with the mass block through a spring, and the motor can adjust the number of effective turns between the motor and the mass block.
In some embodiments, one end of the spring is fixed with the mass block, and the other end of the spring penetrates through the motor; the motor is internally provided with a driving mechanism, and the driving mechanism can push the spring along the extension direction of the spring, so that the effective number of turns of the spring between the motor and the mass block is increased or reduced.
In some embodiments, the driving mechanism includes a rotating body connected to a rotating shaft of the motor, the rotating body being provided with a spiral groove that extends spirally in an axial direction of the rotating body; the spring part is accommodated in the spiral groove, so that the spring is wound on the rotating body.
In a second aspect, there is provided a soft rigid arm single point mooring, comprising: the adjustable-rigidity transverse damper comprises a mooring tower and a mooring rigid arm arranged on the mooring tower, wherein the mooring rigid arm is provided with the adjustable-rigidity transverse damper.
In some embodiments, the soft rigid arm single point mooring further comprises: the wave period monitoring sensor is used for monitoring the external wave excitation load frequency; and the calculating module is connected with the wave period monitoring sensor and used for calculating the effective number of turns of the spring between the motor and the mass block according to the wave excitation load frequency and sending the effective number of turns to the motor.
In some embodiments, the calculation module is further configured to determine a natural frequency of the adjustable stiffness lateral damper based on the wave excitation load frequency, determine a spring stiffness based on the natural frequency, and determine an effective number of turns of the spring based on the spring stiffness.
In a third aspect, a method for using the soft rigid arm single-point mooring device is provided, which includes the following steps: calculating the effective number of turns of a spring between the motor and the mass block according to the external wave excitation load frequency; and enabling the motor to push the spring to move along the extending direction of the damper according to the effective number of turns.
In some embodiments, the calculating the effective number of turns of the spring between the motor and the mass according to the external wave excitation load frequency includes: determining the natural frequency of the transverse damper with adjustable rigidity according to the external wave excitation load frequency; determining a spring rate from the natural frequency; and determining the effective number of turns of the spring according to the spring stiffness.
In some embodiments, the adjustable stiffness transverse damper has a natural frequency greater than or equal to the wave excitation load frequency.
In a fourth aspect, there is provided a mooring system comprising: the mooring rigid arm of the soft rigid arm single-point mooring device is connected with the ship.
The technical scheme provided by the invention has the beneficial effects that:
the embodiment of the invention provides an adjustable-stiffness transverse damper, a mooring device, a system and a method.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the description of the embodiments will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without creative efforts.
FIG. 1 is a schematic structural diagram of a lateral damper with adjustable stiffness in a first state according to an embodiment of the present invention;
FIG. 2 is a structural diagram of a lateral damper with adjustable stiffness in a second state according to an embodiment of the present invention;
FIG. 3 is a schematic front view of a mooring system according to an embodiment of the present invention;
FIG. 4 is a schematic top view of a mooring system according to an embodiment of the present invention;
fig. 5 is a schematic structural diagram of a right side elevation of a mooring rigid arm provided in the embodiment of the present invention;
fig. 6 is a schematic structural diagram of a left side elevation of a mooring rigid arm provided in the embodiment of the present invention;
fig. 7 is a schematic structural diagram of a motor according to an embodiment of the present invention;
fig. 8 is a schematic structural diagram of a rotating body according to an embodiment of the present invention.
In the figure:
1. a lateral damper with adjustable stiffness; 11. a damper; 12. a mass block; 13. a motor; 131. a rotating body; 132. a helical groove; 14. a spring;
2. mooring the tower; 3. a mooring rigid arm; 4. a vessel; 5. wave period monitoring sensor.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, 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 some, but not all, embodiments of the present invention. All other embodiments, which can be obtained by a person skilled in the art without any inventive step based on the embodiments of the present invention, are within the scope of the present invention.
Embodiments of the present invention provide a stiffness-adjustable lateral damper, a mooring apparatus, a system, and a method, which can solve the problem in the related art that a TLD cannot damp all sea conditions and cannot be applied to a bottle-shaped or other form of mooring rigid arm.
Referring to fig. 1 and 2, a stiffness-adjustable lateral damper 1 according to an embodiment of the present invention may include: a damper 11, wherein a mass block 12 is mounted on the damper 11, and the mass block 12 can move along the extending direction of the damper 11; the damper 11 may be a hydraulic damper 11 or an oil pressure damper 11, or may be other types of dampers 11, the damper 11 can provide resistance to movement, and reduce movement energy, the mass block 12 is mounted on the damper 11, and under the action of the damper 11, the frequency of movement of the mass block 12 can be gradually reduced in the movement process, and the permanent movement of the mass block 12 is slowed down; at least two motors 13, two motors 13 are mounted on the damper 11, and two motors 13 are respectively located on two opposite sides of the mass block 12, wherein after the motors 13 are mounted on the damper 11, the motors 13 are fixed relative to the damper 11, the motors 13 and the mass block 12 can be connected through springs 14, and the motors 13 can adjust the effective number of turns of the springs 14 between the motors 13 and the mass block 12, that is, each motor 13 and the mass block 12 are arranged at intervals, and a spring 14 is arranged between each motor 13 and the mass block 12, one end of each spring 14 is connected with the motor 13, the mass block 12 can move between the two motors 13, and each motor 13 can adjust the effective number of turns of the springs 14 between each motor 13 and the mass block 12 correspondingly, increasing or decreasing the effective number of turns of spring 14 located between motor 13 and mass 12; meanwhile, when the spring 14 moves to the target effective number of turns, the motor 13 can lock the spring 14 internally, so that the effective number of turns of the spring 14 between the motor 13 and the mass block 12 is fixed.
The mass block 12 may be made of metal or reinforced concrete.
In the present application, the motor 13 and the mass block 12 are mounted on the damper 11, the motor 13 is connected with the mass block 12 through the spring 14, due to the action of the damper 11, the motion of the mass block 12 itself has a "hysteresis" characteristic, that is, the motion frequency of the mass block 12 is gradually reduced, and since the motor 13 can adjust the effective number of turns of the spring 14 between the motor 13 and the mass block 12, the stiffness of the spring 14 is inversely proportional to the effective number of turns, therefore, the larger the effective number of turns of the spring 14 between the motor 13 and the mass block 12 is, the smaller the stiffness of the spring 14 between the motor 13 and the mass block 12 is, the lower the natural frequency of the adjustable stiffness transverse damper 1 is, and conversely, the smaller the effective number of turns of the spring 14 is, the larger the stiffness of the spring 14 between the motor 13 and the mass block 12 is, the higher the natural frequency of the adjustable stiffness transverse damper 1 is, therefore, the effective number of turns of the spring 14 between the motor 13 and the mass block 12 is adjusted by the motor 13, so that the stiffness of the spring 14 between the motor 13 and the mass block 12 can be adjusted, and further the natural frequency of the whole stiffness-adjustable transverse damper 1 can be adjusted, that is, the stiffness-adjustable transverse damper 1 of the present application can be adjusted at any time by the motor 13, when the stiffness-adjustable transverse damper 1 is installed on the mooring rigid arm 3, along with the difference of wave frequency, the natural frequency of the stiffness-adjustable transverse damper 1 can be adjusted at any time by the motor 13 to generate a constraint force opposite to the vibration direction of the mooring rigid arm 3, so as to achieve the effect of vibration and shake reduction, and the stiffness-adjustable transverse damper 1 can be installed outside the mooring rigid arm 3 without being limited by the structure of the mooring rigid arm 3, can be applied to any form of mooring rigid arm 3. Of course, the adjustable-stiffness transverse damper 1 of the present application can be used on any structural component that requires adjustment of the vibration frequency or use at a fixed vibration frequency to achieve a vibration damping function.
Referring to fig. 1 and 2, in some embodiments, one end of the spring 14 is fixed to the mass 12, the other end of the spring 14 is inserted into the motor 13, that is, one end of the spring 14 is rigidly connected to the mass 12, one end of the spring 14 away from the mass 12 is a movable end, and the movable end of the spring 14 is inserted into the motor 13, and the movable end is capable of moving relative to the motor 13, a driving mechanism may be disposed in the motor 13, and the driving mechanism may push the spring 14 along an extending direction of the spring 14, so that an effective number of turns of the spring 14 between the motor 13 and the mass 12 is increased or decreased, specifically, the motor 13 has a rotating shaft, and the motor 13 may drive the driving mechanism to move by controlling the rotating shaft to rotate (where the driving mechanism may be linear motion or rotational motion), thereby causing the driving mechanism to drive the movable end of the spring 14 to move left and right along the extending direction of the spring 14 (i.e., the extending direction of the damper 11), thereby adjusting the effective number of turns of the spring 14. Of course, in other embodiments, the spring 14 may be directly driven to move by the rotating shaft of the motor 13. Referring to fig. 1, a schematic structural diagram of the embodiment is provided when the number of effective turns of the spring 14 between the motor 13 and the mass block 12 is large, and it can be seen from the diagram that the distribution of the spring 14 between the motor 13 and the mass block 12 is dense, and at this time, the stiffness between the motor 13 and the mass block 12 is small; referring to fig. 2, a schematic structural diagram of the embodiment is provided, when the number of effective turns of the spring 14 between the motor 13 and the mass block 12 is small, as can be seen from the diagram, the distribution of the spring 14 between the motor 13 and the mass block 12 is sparse, and at this time, the rigidity between the motor 13 and the mass block 12 is large.
Referring to fig. 1, 7 and 8, in some alternative embodiments, the driving mechanism may include a rotating body 131, the rotating body 131 is connected to the rotating shaft of the motor 13, such that the rotating body 131 can rotate along with the rotating shaft of the motor 13, the rotating body 131 is provided with a spiral groove 132, the spiral groove 132 extends spirally along the axial direction of the rotating body 131, and the spiral groove 132 may be provided on the outer surface of the rotating body 131, wherein the inner contour shape of the spiral groove 132 may match the outer contour shape of the spring 14; the spring 14 may be partially received in the spiral groove 132, such that the spring 14 is wound around the rotating body 131, when the rotating body 131 rotates clockwise around the axis thereof, the rotating body 131 may drive the spring 14 to move toward or away from the mass 12, and when the rotating body 131 rotates counterclockwise around the axis thereof, the rotating body 131 may drive the spring 14 to move in the opposite direction. In this embodiment, the spiral groove 132 is formed in the rotating body 131, so that the rotating body 131 can stably drive the spring 14 to move along a straight line in the moving process, and the spring 14 is prevented from being separated from the motor 13. Of course, in other embodiments, the motor 13 may be connected to the driving mechanism through another adapter mechanism, so that the adapter mechanism converts the rotational motion of the motor 13 into the linear motion of the driving mechanism, and the driving mechanism drives the movable end of the spring 14 to move along the extending direction of the spring 14, so as to adjust the effective number of turns of the spring 14 between the motor 13 and the mass 12.
Referring to fig. 3 and 4, an embodiment of the present invention further provides a soft rigid arm single-point mooring apparatus, which may include: the adjustable-stiffness transverse damper comprises a mooring tower 2 and a mooring rigid arm 3 installed on the mooring tower 2, wherein one end of the mooring rigid arm 3 is hinged to the mooring tower 2, so that the mooring rigid arm 3 can rotate freely relative to the mooring tower 2, the other end of the mooring rigid arm 3 is hinged to a ship 4, and therefore the limitation on the ship 4 is achieved, in order to avoid the situation that the swing amplitude of the mooring rigid arm 3 is too large, the strength of a steel structure is damaged, and the fatigue life of the steel structure is adversely affected, the adjustable-stiffness transverse damper 1 can be installed on the mooring rigid arm 3, when the adjustable-stiffness transverse damper 1 is installed on the mooring rigid arm 3, the adjustable-stiffness transverse damper can be fixed with the mooring rigid arm 3 through a base of a motor 13, the adjustable-stiffness transverse damper 1 can adopt the technical scheme provided in any one of the above embodiments, and is not repeated. In the embodiment, the stiffness-adjustable transverse damper 1 is arranged on the mooring rigid arm 3, the stiffness-adjustable transverse damper 1 can generate opposite swinging attached to the mooring rigid arm 3 after adjusting the stiffness, the swinging of the mass block 12 opposite to the mooring rigid arm 3 generates force for restricting the swinging of the mooring rigid arm 3, the swinging of the mooring rigid arm 3 can be reduced, and therefore the effective number of turns of the spring 14 is adjusted to generate restriction force opposite to the vibration of the mooring rigid arm 3, and a good vibration reduction effect can be achieved.
Referring to fig. 5, when the ship 4 sways to drive the mooring steel arm 3 to rotate, so that the left side of the mooring steel arm 3 is lower and the right side of the mooring steel arm 3 is raised, according to the "hysteresis" characteristic of the stiffness-adjustable lateral damper 1, the mass block 12 moves towards the raised side (i.e. the right side) of the mooring steel arm 3 under the action of the inertial force F1, so that the mass block 12 is closer to the raised side, at this time, the raised side of the mooring steel arm 3 is forced to return to the original balance state under the action of the gravity F2 of the mass block 12, the sway degree of the mooring steel arm 3 is reduced, and the sway of the ship 4 is reduced.
Referring to fig. 6, when the ship 4 sways to drive the mooring steel arm 3 to rotate, so that the right side of the mooring steel arm 3 is lower, and the left side of the mooring steel arm 3 is raised, according to the "hysteresis" characteristic of the stiffness-adjustable lateral damper 1, the mass block 12 moves towards the raised side (i.e. the left side) of the mooring steel arm 3 under the action of the inertial force F1, so that the mass block 12 is closer to the raised side, and at this time, under the action of the gravity F2 of the mass block 12, the raised side of the mooring steel arm 3 is forced to return to the original balanced state, so that the sway degree of the mooring steel arm 3 is reduced, and the sway of the ship 4 is further reduced.
Referring to fig. 3 and 4, in some embodiments, the soft rigid arm single point mooring apparatus may further include: the wave period monitoring sensor 5 is used for monitoring the external wave excitation load frequency, wherein the wave period monitoring sensor 5 can float on the sea surface, the wave period monitoring sensor 5 can monitor the wave period in real time, count the effective period and transmit data to a local computer; a calculating module, wherein the calculating module can be a computer or a computer internal calculating software, the calculating module can be connected to the wave period monitoring sensor 5 through a signal transmission cable, and the calculating module is used for calculating the effective number of turns of the spring 14 between the motor 13 and the mass block 12 according to the wave excitation load frequency, and sending the effective number of turns to the motor 13, so that the motor 13 controls the number of turns of the rotating shaft of the motor 13 according to the effective number of turns of the spring 14, for example, the effective number of turns of the spring 14 needs to be adjusted to 10 turns, and assuming that the total number of turns of the spring 14 is 20 turns, the motor 13 needs to control the rotating shaft to rotate 10 turns to ensure that the effective number of turns between the motor 13 and the mass block 12 is 10 turns. In this embodiment, by providing the wave period monitoring sensor 5 and the calculation module, the natural frequency of the adjustable stiffness transverse damper 1 can be automatically adjusted in real time according to the wave frequency.
Further, the calculation module may be further configured to determine a natural frequency of the adjustable stiffness transverse damper 1 according to the wave excitation load frequency, determine a spring stiffness according to the natural frequency, and determine an effective number of turns of the spring 14 according to the spring stiffness. The method specifically comprises the following steps: according to experiments, when the natural frequency of the damper 11 with the mass block 12 is slightly larger than the external wave excitation load frequency, the damping effect is best, after the wave excitation load frequency is measured, the natural frequency of the stiffness-adjustable transverse damper 1 can be set to be slightly larger than the wave excitation load frequency, or the natural frequency of the stiffness-adjustable transverse damper 1 is set to be equal to the wave excitation load frequency, and then the spring stiffness can be calculated according to the set natural frequency of the stiffness-adjustable transverse damper 1, wherein the spring stiffness can be calculated according to a natural frequency formula, and the natural frequency calculation formula is as follows:
in the formula, T is the inherent period of the transverse damper 1 with adjustable rigidity; ω -circular frequency; k is the spring rate; m is the mass of the mass block 12, which is usually about 5% -10% of the mass of the vibration damping structure.
After the spring stiffness is calculated according to the natural frequency formula, the effective number of turns of the spring 14 can be calculated according to the spring stiffness formula. Wherein the spring rate formula is as follows:
wherein k is the spring rate; g-shear module of spring material; d is the diameter of the spring wire; d is the diameter of the spring; n-the number of effective turns of the spring 14. In the formula, G, D and D are fixed values, the effective number of turns n of the spring 14 is adjusted through the motor 13, the spring stiffness k is controlled, and the natural period T (namely the natural frequency) of the stiffness-adjustable transverse damper 1 is further controlled.
The embodiment of the invention also provides a use method of the soft rigid arm single-point mooring device, which comprises the following steps:
step 1: according to the frequency of the external wave excitation load, the effective number of turns of the spring 14 between the motor 13 and the mass block 12 is calculated.
Step 2: the motor 13 pushes the spring 14 to move along the extending direction of the damper 11 according to the effective number of turns.
Further, in step 1, calculating the effective number of turns of the spring 14 between the motor 13 and the mass block 12 according to the external wave excitation load frequency may include: determining the natural frequency of the transverse damper 1 with adjustable rigidity according to the external wave excitation load frequency; determining a spring rate from the natural frequency; the effective number of turns of the spring 14 is determined from the spring rate. And, in determining the natural frequency of the adjustable stiffness lateral damper 1, the natural frequency of the adjustable stiffness lateral damper 1 may be slightly greater than or equal to the wave excitation load frequency.
Referring to fig. 3 and 4, an embodiment of the present invention further provides a mooring system, which may include: the mooring device comprises a ship 4, wherein the soft rigid arm single-point mooring device is arranged on one side of the ship 4, and a mooring rigid arm 3 of the soft rigid arm single-point mooring device is connected with the ship 4. The soft rigid arm single-point mooring device may adopt the technical scheme provided in any of the above embodiments, and details are not repeated herein.
The mooring rigid arm 3 on the soft rigid arm single-point mooring device can greatly swing when being subjected to the rolling and swaying of the FPSO ship 4, and the rolling and swaying of the FPSO ship 4 are mainly influenced by the wave frequency, so that the waves with a certain frequency can cause the FPSO ship 4 to generate the rolling or swaying with the same frequency, further cause the mooring rigid arm 3 to greatly swing, and even generate resonance. The technical scheme provided by the embodiment of the invention can reduce the rolling and swaying of the mooring rigid arm 3 of the soft rigid arm single-point mooring device, and has beneficial effects on reducing the stress borne by the mooring structure, prolonging the fatigue life of the mooring structure, stabilizing the motion attitude of the FPSO ship 4 and bringing about the safety of mooring equipment.
In the description of the present invention, it should be noted that the terms "upper", "lower", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, which are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed in a specific orientation, and operate, and thus, should not be construed as limiting the present invention. Unless expressly stated or limited otherwise, the terms "mounted," "connected," and "connected" are intended to be inclusive and mean, for example, that they may be fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
It is to be noted that, in the present invention, relational terms such as "first" and "second", and the like, are used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Also, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising an … …" does not exclude the presence of other identical elements in a process, method, article, or apparatus that comprises the element.
The foregoing are merely exemplary embodiments of the present invention, which enable those skilled in the art to understand or practice the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the invention. Thus, the present invention is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.
Claims (10)
1. An adjustable stiffness transverse damper, comprising:
a damper (11), wherein a mass block (12) is mounted on the damper (11), and the mass block (12) can move along the extension direction of the damper (11);
at least two motors (13), two motor (13) install in damper (11), and two motor (13) are located respectively the relative both sides of quality piece (12), motor (13) with quality piece (12) are connected through spring (14), just motor (13) are adjustable spring (14) are located motor (13) with the effective number of turns between quality piece (12).
2. The adjustable stiffness lateral damper of claim 1, wherein:
one end of the spring (14) is fixed with the mass block (12), and the other end of the spring (14) penetrates through the motor (13);
a driving mechanism is arranged in the motor (13), and the driving mechanism can push the spring (14) along the extension direction of the spring (14) to increase or decrease the effective number of turns of the spring (14) between the motor (13) and the mass block (12).
3. The adjustable stiffness lateral damper of claim 2, wherein:
the driving mechanism comprises a rotating body (131), the rotating body (131) is connected with a rotating shaft of the motor (13), the rotating body (131) is provided with a spiral groove (132), and the spiral groove (132) extends spirally along the axial direction of the rotating body (131);
the spring (14) is partially housed in the spiral groove (132), and the spring (14) is wound around the rotating body (131).
4. A soft rigid arm single point mooring device, its characterized in that, it includes:
a mooring tower (2) and a mooring rigid arm (3) mounted on the mooring tower (2), wherein the mooring rigid arm (3) is provided with the adjustable stiffness lateral damper according to any one of claims 1-3.
5. The soft rigid arm single point mooring of claim 4, wherein the soft rigid arm single point mooring further comprises:
a wave period monitoring sensor (5), wherein the wave period monitoring sensor (5) is used for monitoring the external wave excitation load frequency;
the calculating module is connected with the wave period monitoring sensor (5) and used for calculating the effective number of turns of the spring (14) between the motor (13) and the mass block (12) according to the wave excitation load frequency and sending the effective number of turns to the motor (13).
6. The soft rigid arm single point mooring of claim 5, wherein:
the calculation module is also used for determining the natural frequency of the transverse damper with adjustable stiffness according to the wave excitation load frequency, determining the stiffness of the spring (14) according to the natural frequency, and determining the effective number of turns of the spring (14) according to the stiffness of the spring (14).
7. A method for using the soft rigid arm single point mooring device of claim 4, is characterized by comprising the following steps:
calculating the effective number of turns of a spring (14) between the motor (13) and the mass block (12) according to the external wave excitation load frequency;
and enabling the motor (13) to push the spring (14) to move along the extending direction of the damper (11) according to the effective number of turns.
8. Use according to claim 7, wherein said calculating the effective number of turns of the spring (14) between the motor (13) and the mass (12) as a function of the external wave excitation load frequency comprises:
determining the natural frequency of the transverse damper with adjustable rigidity according to the external wave excitation load frequency;
determining the stiffness of the spring (14) from the natural frequency;
determining the effective number of turns of the spring (14) according to the stiffness of the spring (14).
9. Use according to claim 8, characterized in that:
the natural frequency of the adjustable stiffness transverse damper is greater than or equal to the wave excitation load frequency.
10. A mooring system, comprising:
the single-point mooring device with the soft rigid arm is characterized in that one side of the ship (4) is provided with the single-point mooring device with the soft rigid arm according to claim 4, and the mooring rigid arm (3) of the single-point mooring device with the soft rigid arm is connected with the ship (4).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111682017.6A CN114291209A (en) | 2021-12-31 | 2021-12-31 | Adjustable-stiffness transverse damper, mooring device, system and method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111682017.6A CN114291209A (en) | 2021-12-31 | 2021-12-31 | Adjustable-stiffness transverse damper, mooring device, system and method |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN114291209A true CN114291209A (en) | 2022-04-08 |
Family
ID=80975112
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111682017.6A Pending CN114291209A (en) | 2021-12-31 | 2021-12-31 | Adjustable-stiffness transverse damper, mooring device, system and method |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN114291209A (en) |
Citations (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102995786A (en) * | 2012-12-11 | 2013-03-27 | 山东电力集团公司检修公司 | Two-way horizontal adjustable tuned mass damper |
| CN103415438A (en) * | 2011-03-11 | 2013-11-27 | 辛格尔浮筒系船公司 | Yoke damping system |
| CN203337177U (en) * | 2013-05-28 | 2013-12-11 | 中国海洋石油总公司 | On-site monitoring and forecasting system for waterborne soft-yoke mooring system in Bohai Gulf |
| CN104071304A (en) * | 2014-07-07 | 2014-10-01 | 中国核动力研究设计院 | Single-point mooring system suitable for hull type floating nuclear-powered plant |
| CN105818930A (en) * | 2016-03-11 | 2016-08-03 | 大连理工大学 | Improved damping type soft steel arm single-point mooring device |
| CN106763403A (en) * | 2017-01-12 | 2017-05-31 | 华中科技大学 | A kind of adjustable spring mechanism of rigidity |
| CN206319685U (en) * | 2016-12-20 | 2017-07-11 | 上海史狄尔建筑减震科技有限公司 | Full assembled tuned mass damper, TMD |
| CN108678895A (en) * | 2018-06-06 | 2018-10-19 | 中国海洋大学 | Dynamic adjustable rigidity vortex-induced vibration marine tidal-current energy conversion equipment and its control method |
| CN108775994A (en) * | 2018-07-03 | 2018-11-09 | 武汉理工大学 | One kind being based on magnetic rheology elastic body frequency conversion damper vibration damping experimental rig and system |
| CN109733142A (en) * | 2019-03-11 | 2019-05-10 | 汉腾汽车有限公司 | A kind of spring base of changeable spring rate |
| CN110155260A (en) * | 2019-04-24 | 2019-08-23 | 华中科技大学 | A kind of tuned mass damper platform suitable for semi-submersible type wind-driven generator |
| CN110422296A (en) * | 2019-07-02 | 2019-11-08 | 哈尔滨工程大学 | An a kind of heavy amount damper device of hull global vibration control |
| CN110422299A (en) * | 2019-07-02 | 2019-11-08 | 哈尔滨工程大学 | A kind of collision mass damper PTMD device of hull global vibration control |
| CN110435837A (en) * | 2019-07-25 | 2019-11-12 | 天津大学青岛海洋技术研究院 | A method of avoid mild steel arm and floating production storage tanker stem from colliding |
| CN110715782A (en) * | 2019-10-15 | 2020-01-21 | 河海大学 | Vortex-induced vibration suppression experimental device based on nonlinear energy trap |
| CN210793523U (en) * | 2019-10-15 | 2020-06-19 | 大连船舶重工集团有限公司 | Mooring device with low swing amplitude |
| CN112502891A (en) * | 2020-11-30 | 2021-03-16 | 中国石油大学(华东) | Vortex-induced vibration power generation device with adjustable mass and rigidity |
-
2021
- 2021-12-31 CN CN202111682017.6A patent/CN114291209A/en active Pending
Patent Citations (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103415438A (en) * | 2011-03-11 | 2013-11-27 | 辛格尔浮筒系船公司 | Yoke damping system |
| US20140014017A1 (en) * | 2011-03-11 | 2014-01-16 | Single Buoy Mooring Inc. | Yoke damping system |
| CN102995786A (en) * | 2012-12-11 | 2013-03-27 | 山东电力集团公司检修公司 | Two-way horizontal adjustable tuned mass damper |
| CN203337177U (en) * | 2013-05-28 | 2013-12-11 | 中国海洋石油总公司 | On-site monitoring and forecasting system for waterborne soft-yoke mooring system in Bohai Gulf |
| CN104071304A (en) * | 2014-07-07 | 2014-10-01 | 中国核动力研究设计院 | Single-point mooring system suitable for hull type floating nuclear-powered plant |
| CN105818930A (en) * | 2016-03-11 | 2016-08-03 | 大连理工大学 | Improved damping type soft steel arm single-point mooring device |
| CN206319685U (en) * | 2016-12-20 | 2017-07-11 | 上海史狄尔建筑减震科技有限公司 | Full assembled tuned mass damper, TMD |
| CN106763403A (en) * | 2017-01-12 | 2017-05-31 | 华中科技大学 | A kind of adjustable spring mechanism of rigidity |
| CN108678895A (en) * | 2018-06-06 | 2018-10-19 | 中国海洋大学 | Dynamic adjustable rigidity vortex-induced vibration marine tidal-current energy conversion equipment and its control method |
| CN108775994A (en) * | 2018-07-03 | 2018-11-09 | 武汉理工大学 | One kind being based on magnetic rheology elastic body frequency conversion damper vibration damping experimental rig and system |
| CN109733142A (en) * | 2019-03-11 | 2019-05-10 | 汉腾汽车有限公司 | A kind of spring base of changeable spring rate |
| CN110155260A (en) * | 2019-04-24 | 2019-08-23 | 华中科技大学 | A kind of tuned mass damper platform suitable for semi-submersible type wind-driven generator |
| CN110422296A (en) * | 2019-07-02 | 2019-11-08 | 哈尔滨工程大学 | An a kind of heavy amount damper device of hull global vibration control |
| CN110422299A (en) * | 2019-07-02 | 2019-11-08 | 哈尔滨工程大学 | A kind of collision mass damper PTMD device of hull global vibration control |
| CN110435837A (en) * | 2019-07-25 | 2019-11-12 | 天津大学青岛海洋技术研究院 | A method of avoid mild steel arm and floating production storage tanker stem from colliding |
| CN110715782A (en) * | 2019-10-15 | 2020-01-21 | 河海大学 | Vortex-induced vibration suppression experimental device based on nonlinear energy trap |
| CN210793523U (en) * | 2019-10-15 | 2020-06-19 | 大连船舶重工集团有限公司 | Mooring device with low swing amplitude |
| CN112502891A (en) * | 2020-11-30 | 2021-03-16 | 中国石油大学(华东) | Vortex-induced vibration power generation device with adjustable mass and rigidity |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US20170037832A1 (en) | Wind Turbine with Floating Foundation and Position Regulating Control System and Method Thereof | |
| KR101109810B1 (en) | A wind turbine for use offshore | |
| KR20190088998A (en) | Control System for Floating Wind Turbine Structures | |
| CA1087035A (en) | Riser and yoke mooring system | |
| EP3874161B1 (en) | Tuned mass damper for floating structures | |
| CN101384474B (en) | Mooring system for a floating structure | |
| CN103402865B (en) | A kind of method of ring float and elimination buoyancy aid heave movement | |
| JP2003520725A (en) | Mooring system with active reaction system and passive damping | |
| US6705440B2 (en) | Cable stay damper band and method of use for reduction of fluid induced cable vibrations | |
| JP2009535560A (en) | Wave energy converter | |
| CN103708004A (en) | Stabilizing device, floating foundation and offshore wind power generator | |
| CN203652079U (en) | Stabilizer, floating foundation and offshore wind turbine | |
| JP4766844B2 (en) | Wind turbine generator | |
| KR20100113202A (en) | Apparatus for reducing rolling motion for ships | |
| US4010704A (en) | Buoyant sphere | |
| CN114291209A (en) | Adjustable-stiffness transverse damper, mooring device, system and method | |
| AU2004324515B2 (en) | Oscillation suppression and control system for a floating platform | |
| KR20190017276A (en) | Movement reducing apparatus of floating offshore structure | |
| US6910438B2 (en) | Oscillation suppression and control system for a floating platform | |
| CN106170624B (en) | Wave energy converter | |
| JP2013160109A (en) | Windmill device with vibration absorbing mechanism | |
| KR100545914B1 (en) | Mass mobile transverse shaking damping device with automatic damping force | |
| JP2013525670A (en) | A system for generating energy from ocean waves | |
| JP2024500479A (en) | Floating wind turbine control below rated wind speed | |
| US5098226A (en) | Apparatus and method for damping low frequency perturbations of marine structures |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20220408 |