CN108561503A - The unit of dynamic absorber containing Negative stiffness spring and thrust bearing - Google Patents
The unit of dynamic absorber containing Negative stiffness spring and thrust bearing Download PDFInfo
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- CN108561503A CN108561503A CN201810327723.0A CN201810327723A CN108561503A CN 108561503 A CN108561503 A CN 108561503A CN 201810327723 A CN201810327723 A CN 201810327723A CN 108561503 A CN108561503 A CN 108561503A
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- thrust
- disc
- negative stiffness
- spring
- wear
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Classifications
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
- F16C17/08—Sliding-contact bearings for exclusively rotary movement for axial load only for supporting the end face of a shaft or other member, e.g. footstep bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- 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
- F16F15/1435—Elastomeric springs, i.e. made of plastic or rubber
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2326/00—Articles relating to transporting
- F16C2326/30—Ships, e.g. propelling shafts and bearings therefor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
- F16F2228/06—Stiffness
- F16F2228/063—Negative stiffness
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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)
- Sliding-Contact Bearings (AREA)
- Support Of The Bearing (AREA)
Abstract
According to one kind unit of dynamic absorber containing Negative stiffness spring provided by the invention and thrust bearing.The unit of dynamic absorber containing Negative stiffness spring includes dynamic vibration absorber, and the dynamic vibration absorber includes wear-resistant material body, elastomer, mass block, Negative stiffness spring；Wear-resistant material body, elastomer, mass block, Negative stiffness spring are sequentially connected.The thrust bearing includes thrust metal, thrust block portion, thrust disc, further includes the unit of dynamic absorber containing Negative stiffness spring.The present invention has following advantageous effect：The thrust bearing has substantially no effect on the structure type of existing thrust bearing, and the disc spring due to working in negative stiffness point provides a part of inertia force in vibration, can reduce requirement of the dynamic vibration absorber to mass block quality；The damping that rubber pad provides makes dynamic vibration absorber disclosure satisfy that modal frequency has certain deviation, and two mode peaks for effectively inhibiting dynamic vibration absorber to generate.
Description
Technical field
The present invention relates to thrust bearing fields, and in particular, to one kind unit of dynamic absorber containing Negative stiffness spring and thrust
Bearing.
Background technology
Thrust bearing is the important equipment of marine propuision system, on the one hand, thrust bearing need to transmit positive and negative two to propeller
The torque in direction, while the thrust that propeller generates is passed into hull；On the other hand, thrust bearing also can be by propeller unevenness
The pulsating force generated in uniform flow field passes to hull, encourages ship hull vibration acoustic radiation.This is for occupant comfort, the ship on ship
The underwater radiation noise of oceangoing ship has important influence.
For the extensional vibration of thrust bearing is transmitted, in low-frequency range, there are two system frequency peaks outstanding
Value, is the single order longitudinal vibration frequency of the in phase vibration mode and propeller-shafting-thrust bearing-pedestal of propeller respectively.If energy
It is enough to control the two peak values, then the vibration noise problem of Ship Structure can be controlled preferably.It promotes at present
The vibration control means used in shafting have longitudinal shock absorber vibration isolation, the vibration isolation of resonance converter, power antiresonance vibration isolation, actively move
The absorbing of power bump leveller, the dynamic vibration absorber on pedestal, the dynamic vibration absorber inside hollow shafting.Wherein, although vibration isolation can drop
Vibration more than low a certain frequency is transmitted, but can be had an impact to the vibration acoustic radiation of propeller；Power antiresonance can amplify
Vibration more than a certain frequency is transmitted；For active power bump leveller as a result of active control measures, system is complex；Power
Bump leveller controls low-frequency vibration due to needing, needed for quality cost it is larger, especially for shafting the first rank longitudinal vibration mode,
Its modal mass is substantially equal with the entire quality of propeller-shafting (about 15 tons), needs 2% using traditional power bump leveller
Times modal mass, reaches 300kg, this weight magnitude cost is larger easily；In addition, thrust bearing and rotating speed have it is certain related
Property causes shafting the first rank longitudinal vibration mode to shift, dynamic absorber since the rigidity of thrust bearing is different under different rotating speeds
Device needs to all have good dynamic absorber effect in larger frequency deviation range, this is more difficult for traditional power bump leveller.
In thrust bearing used by spot ship thrust transferring element include thrust axis, thrust block pad, thrust balancing mechanism,
Support ring, shell, thrust bearing pedestal etc..In order to inhibit the vibration by thrust bearing to transmit situation, invent with one
Determine the thrust bearing of vibration-damping function, mainly increases rubber damper in the suitable position of thrust transferring element.This bearing for
The vibration of high frequency has certain attenuating, but does not have effect for low frequency protrusion peak value.
Invention content
For the defects in the prior art, the object of the present invention is to provide a kind of unit of dynamic absorber containing Negative stiffness spring and
Thrust bearing.
According to a kind of unit of dynamic absorber containing Negative stiffness spring provided by the invention, including dynamic vibration absorber, wherein described
Dynamic vibration absorber includes wear-resistant material body, elastomer, mass block, Negative stiffness spring；Wear-resistant material body, mass block, is born elastomer
Rigid spring is sequentially connected.
According to a kind of thrust bearing provided by the invention, including thrust metal, thrust block portion, thrust disc, further include on
The unit of dynamic absorber containing Negative stiffness spring stated；Thrust block portion is fastenedly connected in thrust metal；The disconnected matter of Negative stiffness spring
One end of gauge block connects thrust metal；The disconnected mass block of elastomer on one side connect wear-resistant material body while；Wear-resisting material
Expect that the another side of body connects thrust disc；Thrust block portion connects thrust disc.
Preferably, the Negative stiffness spring includes disc spring；Disc spring can work in negative stiffness point；It is provided on mass block
First groove；One end of disc spring is mounted on the inside of the first groove by clearance fit；The other end of disc spring is connected to thrust axis
On the inner wall of bearing.
Preferably, elastomer includes rubber pad；Rubber pad connects wear-resistant material body by sunk screw；Elastomer and quality
Block forms one by vulcanizing.
Preferably, the second groove is provided on thrust disc；The wear-resistant material body is mounted on second by clearance fit
The inside of groove.
Preferably, thrust block portion includes thrust block part, thrust-balancing block part, cushion block；Thrust-balancing block part passes through cushion block branch
Support is in thrust block part；Thrust block part connects thrust metal；Wedge-shaped oil film is formed between thrust-balancing block part and thrust disc.
Preferably, the thrust bearing includes oil circuit device；Oil circuit device provides recycle oil；Oil circuit device is thrust disc
Oil film is provided between wear-resistant material body, between thrust disc and thrust-balancing block part.
Preferably, when thrust disc rotates in the forward direction, wear-resistant material body does not rotate.
Be preferably located at thrust disc front side, reverse side disc spring size it is the same or different；Positioned at thrust
Disk front side, reverse side disc spring quantity it is the same or different；When thrust disc reversely rotates, the thrust disc compression back of the body
The disc spring of face side, the disc spring relaxation of thrust disc front side.
Preferably, elastomer provides damping；The damping disclosure satisfy that ± 10% modal frequency offset.
Compared with prior art, the present invention has following advantageous effect：The thrust axis of Negative stiffness spring dynamic vibration absorber
The structure type for having substantially no effect on existing thrust bearing is held, and since the disc spring for being operated in negative stiffness point provides one in vibration
Part inertia force can reduce requirement of the dynamic vibration absorber to mass block quality；The damping that rubber pad provides enables dynamic vibration absorber
Enough meeting modal frequency has certain deviation, and two mode peaks for effectively inhibiting dynamic vibration absorber to generate.
Description of the drawings
Upon reading the detailed description of non-limiting embodiments with reference to the following drawings, other feature of the invention,
Objects and advantages will become more apparent upon：
Fig. 1 is the structure chart of thrust bearing；
Fig. 2 is the partial enlarged view of thrust bearing；
Fig. 3 is the schematic diagram of thrust bearing；
Fig. 4 is the schematic diagram of thrust bearing.
It is shown in figure：
Specific implementation mode
With reference to specific embodiment, the present invention is described in detail.Following embodiment will be helpful to the technology of this field
Personnel further understand the present invention, but the invention is not limited in any way.It should be pointed out that the ordinary skill of this field
For personnel, without departing from the inventive concept of the premise, various modifications and improvements can be made.These belong to the present invention
Protection domain.
In the description of the present invention, it is to be understood that, term "upper", "lower", "front", "rear", "left", "right", " perpendicular
Directly ", the orientation or positional relationship of the instructions such as "horizontal", "top", "bottom", "inner", "outside" is orientation based on ... shown in the drawings or position
Relationship is set, is merely for convenience of description of the present invention and simplification of the description, device is not indicated or implied the indicated or element is necessary
With specific orientation, with specific azimuth configuration and operation, therefore be not considered as limiting the invention.
According to a kind of unit of dynamic absorber containing Negative stiffness spring provided by the invention, including dynamic vibration absorber 1, wherein institute
It includes wear-resistant material body 6, elastomer 13, mass block 12, Negative stiffness spring 11 to state dynamic vibration absorber 1；Wear-resistant material body 6, elasticity
Body 13, mass block 12, Negative stiffness spring 11 are sequentially connected.
According to a kind of thrust bearing 908 provided by the invention, including thrust metal 2, thrust block portion 3, thrust disc 5, also
Including the unit of dynamic absorber containing Negative stiffness spring；Thrust block portion 3 is fastenedly connected in thrust metal 2；Negative stiffness spring
One end of 11 disconnected mass blocks 12 connects thrust metal 2；The wear-resisting material of connection on one side of 13 disconnected mass block 12 of elastomer
Expect one side of body 6；The another side of wear-resistant material body 6 connects thrust disc 5；Thrust block portion 3 connects thrust disc 5.
Specifically, the Negative stiffness spring 11 includes disc spring 111；Disc spring 111 can work in negative stiffness point；Mass block
The first groove 121 is provided on 12；One end of disc spring 111 is mounted on the inside of the first groove 121 by clearance fit；Disc spring
111 other end is connected on the inner wall of thrust metal 2.Herein, the thrust bearing 908 includes screw division 10；Spiral shell
Nail portion 10 includes screw element 107, sunk screw part 101；Thrust block part 31 is connected to by screw 107 on thrust metal 2.Bullet
Property body 13 include rubber pad 131；Rubber pad 131 connects wear-resistant material body 6 by sunk screw 101；Elastomer 13 and mass block
12 form one by vulcanizing.
Specifically, being provided with the second groove 51 on thrust disc 5；The wear-resistant material body 6 is mounted on by clearance fit
The inside of second groove 51.Thrust block portion 3 includes thrust block part 31, thrust-balancing block part 32, cushion block 33；Thrust-balancing block part 32
It is supported in thrust block part 31 by cushion block 33；Thrust block part 31 connects thrust metal 2；Thrust-balancing block part 32 and thrust disc
Wedge-shaped oil film is formed between 5.
Specifically, the thrust bearing 908 includes oil circuit device 9；Oil circuit device 9 provides recycle oil；Oil circuit device 9 is
Oil film is provided between thrust disc 5 and wear-resistant material body 6, between thrust disc 5 and thrust-balancing block part 32.Herein, described to push away
908 inside of power bearing is full of lubricating oil, and thrust disc 5 is fastenedly connected with thrust axis 4, and thrust block part 31 is connected by screw element 107
On thrust metal 2, thrust-balancing block part 32 is supported on thrust block part 31 by the cushion block 33 with certain adjustment capability
On, wear-resistant material body 6 is mounted on by clearance fit in the groove of thrust disc 5, and it is heavy that wear-resistant material body 6 passes through with rubber pad 131
Head screw element 101 connects, and elastomer 13 forms one with mass block 12 by vulcanizing, and one end of disc spring 111 passes through clearance fit
In the groove of mass block 12, the other end of disc spring 111 is supported on the inner wall of thrust metal 2, attached oil circuit dress
It sets 9 and provides recycle oil for the thrust bearing 908 of the unit of dynamic absorber containing Negative stiffness spring to lubricate and cool down.
Herein, when thrust axis 4 rotates under water, oil film can be formed between thrust disc 5 and thrust-balancing block part 32
Oil film rigidity is provided, oil film rigidity plays the role of supporting thrust axis 4 and balances a part of static thrust, while a part of static thrust
By compressed abrasion resistant material bodies 6, rubber pad 131 and disc spring 111 so that disc spring 111 is in negative stiffness operating point, and (negative stiffness refers to bearing
Dynamic stiffness), mass block 12 and rubber pad 131 absorb thrust axis 4 as the component part of dynamic vibration absorber 1 and vibrate, disc spring 111
Negative stiffness vibration when provide inertia force can greatly reduce dynamic vibration absorber 1 to 12 quality requirement of mass block, rubber pad 131
The damping of offer makes dynamic vibration absorber 1 disclosure satisfy that control requirement when required control modal frequency has certain deviation, and effectively
Inhibit two mode peaks generated due to dynamic absorber effect.
Specifically, when thrust disc 5 rotates in the forward direction, wear-resistant material body 6 does not rotate.Positioned at the positive side of thrust disc 5, the back side
The size of the disc spring 111 of side is the same or different；Positioned at the positive side of thrust disc 5, the quantity of the disc spring 111 of reverse side
It is the same or different；When thrust disc 5 reversely rotates, the disc spring 111 of 5 compression rear side of thrust disc, 5 front one of thrust disc
The disc spring 111 of side relaxes.Specifically, elastomer 13 provides damping；The damping disclosure satisfy that ± 10% modal frequency is inclined
It moves.
In preference, when thrust axis 4 rotates in the forward direction, thrust disc 5 rotates in the forward direction, and wear-resistant material body 6 does not rotate, thrust disc
Oil film is formed between 5 and wear-resistant material body 6, reduces the abrasion of thrust disc 5 and wear-resistant material body 6.Herein, rotating in the forward direction is
Refer to：It is origin with propeller 909, being directed toward ship head from ship tail is reversed forward direction, if the direction of rotation of propeller 909 and this direction phase
Together, then to rotate in the forward direction.Reverse rotation refers to：It is origin with propeller 909, being directed toward ship head from ship tail is reversed forward direction, if spiral shell
The direction of rotation of paddle 909 is revolved with this direction on the contrary, being then to reversely rotate.
As shown in Figure 3 and Figure 4, in preference, when thrust axis 4 reversely rotates, thrust disc 5 is by the disc spring of compression rear
111, positive disc spring 111 will be loosened, but pass through the positioning of the first groove 121, the second groove 51, wear-resistant material body 6 and disc spring
111 all without departing from the second groove 51 on thrust disc 5.When propeller 909 rotates in the forward direction, positive static thrust is generated, is located at
Disc spring 111 between thrust disc 5 and ship head is positive disc spring 111, the disc spring 111 between ship tail and thrust disc 5 is the back of the body
The disc spring 111 in face.
In preference, when the static thrust that thrust axis 4 is rotated in the forward direction and reversely rotated is different, front and back disc spring
111 size, number are different.The ruler of disc spring 111 need to be designed according to the quiet deformation under the range of static thrust, static push force effect
Very little, number ensures that disc spring 111 is operated in negative stiffness region, and has certain negative stiffness range.
More specific detail is carried out to the present invention below.
Compared with traditional dynamic absorber, following optimum organization may be used in the dynamic vibration absorber 1 containing Negative stiffness spring
Parameter：The quality of its mass block 12 and the ratio of the modal mass of required control modal frequency can be reduced to 3 ‰, negative stiffness and oil
Ratio between film rigidity 7%, according to the ratio between mass ratio, negative stiffness design preferably the rigidity of dynamic vibration absorber 1 with
The damping value of the ratio between oil film rigidity, rubber pad 131, under this optimum ratio, the quiet deformation of shafting and do not install bump leveller or
The quiet deformation of thrust axis 4 is suitable when installing traditional power absorbing, and the damping that rubber pad 131 provides enables dynamic vibration absorber 1 to expire
The deviation of the modal frequency of foot ± 10% or offset, and two mode peaks for effectively inhibiting dynamic vibration absorber 1 to generate, at two
Amplification ratio at mode peak is less than 3.Wherein, when thrust axis 4 rotates in the forward direction, thrust disc 5 can be driven to rotate in the forward direction, and energy
Propeller 909 is enough driven to rotate in the forward direction.When thrust axis 4 reversely rotates, thrust disc 5 can be driven to reversely rotate, and can drive
Propeller 909 is set to reversely rotate.
When thrust axis 4 rotates in the forward direction, thrust disc 5 rotates, and wear-resistant material body 6 does not rotate, thrust disc 5 and wear-resistant material body 6
Between formed oil film reduce thrust disc 5 and wear-resistant material body 6 abrasion.When thrust axis 4 reversely rotates, thrust disc 5 carries on the back compression
The disc spring 111 in face, positive disc spring 111 will be loosened, but will not be taken off by the positioning wear-resistant material body 6 and disc spring 111 of groove
From the positioning groove on thrust disc 5.When the static thrust that thrust axis 4 is rotated in the forward direction and reversely rotated is different, therefore front and the back of the body
Size, the number of face disc spring 111 are different.
Size, the number of disc spring 111 need to be designed according to the quiet deformation under the range of static thrust, static push force effect, ensured
Disc spring 111 is operated in negative stiffness region, and has certain negative stiffness range.
When the rotating speed of thrust axis 4 is when 60rpm~240rpm changes, the rigidity of thrust bearing 908 can occur
10% variation, the mode of shafting the first rank longitudinal vibration at this time can occur5% offset, 131 institute of rubber pad of the thrust bearing 908
Including damping can meetThe deviation of 10% modal frequency, therefore thrust axis 4 can be met in the entire range of speeds
Absorbing is transmitted in vibration.
The mode of realization is not only limited to the structure type of the disc spring 111 described as shown in Figure 1, Figure 2, but disc spring 111 has
Negative stiffness range is wide, negative stiffness ability is strong, to transverse direction and vertical vibration without strong excellent of interference, oil resistant and high temperature resistant, designability
Point, it is preferential to use.
The basic principle figure of the thrust bearing 908 is as shown in Figure 3, Figure 4.Between thrust disc 5 and thrust-balancing block part 32
Oil film rigidity is equivalent to spring ks, the elastomer 13 of dynamic vibration absorber 1 is equivalent to spring keWith damping c, mass block 12 is equivalent to matter
M is measured, negative stiffness component disc spring 111 is equivalent to negative stiffness kn(kn<0).Assuming that the degree of freedom of mass block 12 is x, work as dynamic absorber
The mass block 12 of device 1, when being vibrated with frequencies omega under the excitation of equipment, the inertia force that mass block 12 provides is-m ω2x<0, formula
In, m indicates the equivalent mass of mass block 12；The power that negative stiffness element provides is knx<0, thus the inertia force of mass block 12 with it is negative
The power jack per line that stiffness elements provide, therefore negative stiffness element is equivalent to and provides a part of inertia force, if you need to meet same suction
Vibration frequency, the quality requirement to mass block 12 can be reduced by increasing negative stiffness element.
When being designed to dynamic vibration absorber 1, if controlled for 909 in phase vibration mode of propeller,
The vibration at 909 in phase vibration mode of propeller can be effectively inhibited to transmit.
Fig. 4 is used propeller-shafting equivalent mould when carrying out principle analysis and design to the thrust bearing 908
Type.Propeller 909 is equivalent to the spring mass oscillator for simulating its in phase vibration mode, the blade mould for simulating its antiresonance peak
Quasi- 904 part of beam 905 and propeller hub, cardan shaft 903 are equivalent to bar and beam model, and bearing 906, intermediate bearing 907 are equivalent to after stern
Rigidity；Thrust bearing 908 is equivalent to rigidity.Assuming that propeller-shafting model is acted on by static thrust and pulsating force.
F0Indicate the static thrust in 909 paddle disk of propeller；
F indicates the pulsating force in 909 paddle disk of propeller；
k2Indicate the modal stiffness of 909 in phase vibration mode of propeller；
m2Indicate the modal mass of 909 in phase vibration mode of propeller；
m1Indicate the quality at the propeller hub 904 of propeller 909；
ρbIt is expressed as the density for 905 model of blade simulating beam that 909 antiresonance peak of simulation propeller obtains；
EbIt is expressed as the elasticity modulus for 905 model of blade simulating beam that 909 antiresonance peak of simulation propeller obtains；
IbIt is expressed as the inertia for 905 model of blade simulating beam that 909 antiresonance peak of simulation propeller obtains；
AbIt is expressed as the area of section for 905 model of blade simulating beam that 909 antiresonance peak of simulation propeller obtains；
LbIt is expressed as the length for 905 model of blade simulating beam that 909 antiresonance peak of simulation propeller obtains；
ρ indicates the density of cardan shaft 903；
E indicates the elasticity modulus of cardan shaft 903；
I indicates the inertia of cardan shaft 903；
A indicates the area of section of cardan shaft 903；
L indicates the length of cardan shaft 903；
C indicates the damping ratio that rubber pad 131 generates in dynamic vibration absorber 1.
Specific embodiments of the present invention are described above.It is to be appreciated that the invention is not limited in above-mentioned
Particular implementation, those skilled in the art can make various deformations or amendments within the scope of the claims, this not shadow
Ring the substantive content of the present invention.In the absence of conflict, the feature in embodiments herein and embodiment can arbitrary phase
Mutually combination.
Claims (10)
1. a kind of unit of dynamic absorber containing Negative stiffness spring, which is characterized in that including dynamic vibration absorber (1), wherein the power
Bump leveller (1) includes wear-resistant material body (6), elastomer (13), mass block (12), Negative stiffness spring (11)；
Wear-resistant material body (6), elastomer (13), mass block (12), Negative stiffness spring (11) are sequentially connected.
2. a kind of thrust bearing (908), which is characterized in that including thrust metal (2), thrust block portion (3), thrust disc (5), also
Including the unit of dynamic absorber containing Negative stiffness spring described in claim 1；
Thrust block portion (3) is fastenedly connected in thrust metal (2)；
One end connection thrust metal (2) of Negative stiffness spring (11) disconnected mass block (12)；
Elastomer (13) disconnected mass block (12) on one side connection wear-resistant material body (6) while；
The another side connection thrust disc (5) of wear-resistant material body (6)；
Thrust block portion (3) connects thrust disc (5).
3. thrust bearing (908) according to claim 2, which is characterized in that the Negative stiffness spring (11) includes dish
Spring (111)；
Disc spring (111) can work in negative stiffness point；
The first groove (121) is provided on mass block (12)；
One end of disc spring (111) is mounted on the inside of the first groove (121) by clearance fit；
The other end of disc spring (111) is connected on the inner wall of thrust metal (2).
4. thrust bearing (908) according to claim 2, which is characterized in that elastomer (13) includes rubber pad (131)；
Rubber pad (131) connects wear-resistant material body (6) by sunk screw (101)；
Elastomer (13) forms one with mass block (12) by vulcanizing.
5. thrust bearing (908) according to claim 2, which is characterized in that thrust disc is provided with the second groove on (5)
(51)；
The wear-resistant material body (6) is mounted on the inside of the second groove (51) by clearance fit.
6. thrust bearing (908) according to claim 2, which is characterized in that thrust block portion (3) includes thrust block part
(31), thrust-balancing block part (32), cushion block (33)；
Thrust-balancing block part (32) is supported on by cushion block (33) in thrust block part (31)；
Thrust block part (31) connects thrust metal (2)；
Wedge-shaped oil film is formed between thrust-balancing block part (32) and thrust disc (5).
7. thrust bearing (908) according to claim 2, which is characterized in that including oil circuit device (9)；
Oil circuit device (9) provides recycle oil；
Oil circuit device (9) is between thrust disc (5) and wear-resistant material body (6), between thrust disc (5) and thrust-balancing block part (32)
Oil film is provided.
8. thrust bearing (908) according to claim 3, which is characterized in that wear-resisting when thrust disc (5) rotates in the forward direction
Material bodies (6) do not rotate.
9. thrust bearing (908) according to claim 2, which is characterized in that be located at the positive side of thrust disc (5), the back side
The size of the disc spring (111) of side is the same or different；
Quantity positioned at the positive side of thrust disc (5), the disc spring (111) of reverse side is the same or different；
When thrust disc (5) reversely rotate, the disc spring (111) of thrust disc (5) compression rear side, thrust disc (5) front side
Disc spring (111) relaxation.
10. thrust bearing (908) according to claim 1, which is characterized in that elastomer (13) provides damping；
The damping disclosure satisfy that ± 10% modal frequency offset.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810327723.0A CN108561503A (en) | 2018-04-12 | 2018-04-12 | The unit of dynamic absorber containing Negative stiffness spring and thrust bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810327723.0A CN108561503A (en) | 2018-04-12 | 2018-04-12 | The unit of dynamic absorber containing Negative stiffness spring and thrust bearing |
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| CN108561503A true CN108561503A (en) | 2018-09-21 |
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| CN201810327723.0A Pending CN108561503A (en) | 2018-04-12 | 2018-04-12 | The unit of dynamic absorber containing Negative stiffness spring and thrust bearing |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110107632A (en) * | 2019-06-03 | 2019-08-09 | 江南大学 | A kind of positive and negative Stiffness low frequency vibration isolation device coupling dynamic vibration absorber |
| CN110888464A (en) * | 2019-11-12 | 2020-03-17 | 上海交通大学 | Longitudinal and transverse multi-mode vibration control device and method for variable-speed propeller shaft system |
| CN114802686A (en) * | 2022-04-28 | 2022-07-29 | 中国舰船研究设计中心 | Disc spring type integrated vibration damping thrust bearing |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110107632A (en) * | 2019-06-03 | 2019-08-09 | 江南大学 | A kind of positive and negative Stiffness low frequency vibration isolation device coupling dynamic vibration absorber |
| CN110888464A (en) * | 2019-11-12 | 2020-03-17 | 上海交通大学 | Longitudinal and transverse multi-mode vibration control device and method for variable-speed propeller shaft system |
| CN114802686A (en) * | 2022-04-28 | 2022-07-29 | 中国舰船研究设计中心 | Disc spring type integrated vibration damping thrust bearing |
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Application publication date: 20180921 |