CN109281926A - A kind of vibration damping thrust bearing with hydrostatic thrust Self-balancing - Google Patents
A kind of vibration damping thrust bearing with hydrostatic thrust Self-balancing Download PDFInfo
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- CN109281926A CN109281926A CN201811343052.3A CN201811343052A CN109281926A CN 109281926 A CN109281926 A CN 109281926A CN 201811343052 A CN201811343052 A CN 201811343052A CN 109281926 A CN109281926 A CN 109281926A
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- thrust
- vibration damping
- cylinder
- cushion cylinder
- positive vehicle
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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
- 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
-
- 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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Support Of The Bearing (AREA)
- Vibration Prevention Devices (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
The invention discloses a kind of vibration damping thrust bearing with hydrostatic thrust Self-balancing, Bearing inner is arranged two parts parallel-connection structure and bears jointly and balance thrust；Multiple cushion cylinders are respectively arranged in positive vehicle end and reversing end, and positive vehicle end cushion cylinder is connected by fluid pressure line and the seawater pressure compensator of hull outside；The shell of positive vehicle end cushion cylinder one end is vertically disposed with lubricating oil inlet and outlet, and thrust bearing realizes that lubricating oil is output and input according to seawater pressure；The reversing intracavitary hydraulic oil of end cushion cylinder is directly communicated with the intracavitary lubricating oil of vibration damping thrust bearing, does not transmit seawater pressure.Reduce shafting longitudinal vibration intrinsic frequency, to paddle shaft system just, the vibration of the full range of speeds of reversing play the role of good vibration isolation, the present invention is especially suitable for the latent device Propulsion Systems of latent device.
Description
Technical field
The present invention relates to a kind of latent device main shaft system thrust bearing, and in particular to a kind of with hydrostatic thrust Self-balancing
Vibration damping thrust bearing.
Background technique
Thrust bearing is the important equipment of latent device propulsion system, it transmits shafting forward and backward direction torque to propeller, and
Thrust and pulling force that propeller generates are passed into hull, push latent device navigation.Since propeller rotates in uneven flow field
When, there are certain alternating component in the thrust that generates, longitudinal pumping power is formed, shaft generates certain excitation, and by pushing away
Power bearing is transmitted to hull, is caused ship hull vibration and is caused noise, and therefore, the control of paddle shaft system vibration is always latent device noise control
The emphasis of system.
Dampening apparatus is arranged in shafting longitudinal vibration control general expression in vibration transfer path, and control propeller exciting force draws
The extensional vibration of hair passes through transmitting of the shafting to Ship Structure.Vibration damping member is set between the load component inside thrust bearing
Part is one of the important measures of current shafting vibration and noise reducing.
But there is certain design drawback in shafting longitudinal vibration control design case: to guarantee paddle shaft system longitudinal damping effect, if
Damping element must have lower compression stiffness in meter, but since damping element is arranged between load component, be isolated
Huge static load power is subjected to while vibration.Big load, Low rigidity make damping element in load-carrying properties, using reliable
Property etc. brings great difficulty, but also axial movement value of the paddle shaft system under thrust load is also significantly increased, jeopardizes spiral shell
Revolve paddle, sealing device, bearing, the equipment such as shaft coupling using safe.Therefore, shafting longitudinal damping technology can only be in shallow sea at present
It is used in speed operation, significantly reduces the effective range of damping technology.
Summary of the invention
The technical problem to be solved by the present invention is to, in seawater the shafting longitudinal damping technology of paddle shaft system there are big load,
The technical characterstic of Low rigidity so that damping element load-carrying properties, in terms of bring great difficulty, but also axis
Be that shifting amount is significantly increased, jeopardize the equipment such as propeller, sealing device, bearing, shaft coupling using safe, therefore can only be limited
Thrust range limitation uses shafting longitudinal damping technology, significantly reduces effective use scope of damping technology.
The present invention in view of the above technical problems, using following technical scheme:
A kind of vibration damping thrust bearing with hydrostatic thrust Self-balancing, including bear box and thrust axis, thrust axis is along shell
Body center line is worn and both ends are located at hull outside；It is born jointly simultaneously it is characterized in that two parts parallel-connection structure is arranged in Bearing inner
Balance thrust；
Thrust disc is arranged in the middle part of thrust axis, and thrust disc two sides are divided into positive vehicle end and reversing end, and positive vehicle end and reversing end are respectively arranged
Multiple cushion cylinders, positive vehicle end cushion cylinder are connected by fluid pressure line and the seawater pressure compensator of hull outside；
Cushion cylinder one end housing in positive vehicle end is vertically disposed with lubricating oil inlet and outlet, and shafting tail portion crossing cabin position seawater pressure passes through seawater
Pressure compensator passes to the positive vehicle end cushion cylinder, and the shell of positive vehicle end cushion cylinder one end is vertically disposed with lubricating oil inlet and outlet,
Thrust bearing realizes that lubricating oil is output and input according to seawater pressure；Move backward the intracavitary hydraulic oil of end cushion cylinder directly with vibration damping thrust axis
It holds intracavitary lubricating oil to communicate, does not transmit seawater pressure.
Further, cushion cylinder forms spring shock absorption piston structure by piston, spring, piston cylinder, cover board, and spring is along straight line
Compression direction is arranged between piston and pressing plate；Vibration damping the cylinder piston is arranged in an axially parallel mode with thrust axis.
Further, positive vehicle cushion cylinder inner piston structure bears the partial cross section product summation and shafting crossing cabin of seawater pressure
Position sectional area is consistent.
Further, seawater pressure compensator includes the left side cylinder body and right side cylinder body for being connected with each other and fastening, in left side cylinder
Body and right side cylinder body junction, also set up diaphragm between left side cylinder body and right side cylinder body；The piston and seawater of positive vehicle end cushion cylinder
Hydraulic oil is full of by fluid pressure line between the diaphragm of pressure compensator, is joined on the outside of diaphragm and right side cylinder body with sea water service system out of my cabin
It is logical.
Further, it in positive vehicle end and reversing end, is tied by thrust block pad, support stationary ring, support shaft shoe at damping periphery
Structure accommodates the cushion cylinder；Thrust block pad is arranged in the thrust disc two sides of thrust axis and leans against thrust disc setting, thrust
The inside of block is supported by the cushion cylinder of respective side respectively；Support stationary ring is installed in the housing and is close to inner walls setting, support
Bearing shell is mounted in support stationary ring inner hole, places thrust axis inside support bearing shell；In support stationary ring exit orifice inner wall and support bearing shell
Cushion cylinder is set in the space between outer wall.
Further, in positive vehicle end and reversing end, thrust block pad and cushion cylinder are correspondingly arranged multiple；It is multiple to subtract and at each end
Circumferential direction of the cylinder along thrust axis axial line of shaking is uniformly distributed.
Further, the thrust block pad at positive vehicle end, positive vehicle end cushion cylinder, the thrust block pad at end of moving backward, reversing cushion cylinder are by eight
Block composition.
Further, shell both ends are equipped with lateral oil seal.
A kind of vibration damping thrust bearing with hydrostatic thrust Self-balancing proposed by the present invention, is mainly installed on latent device axis
On owner's Propulsion Systems, for airscrew thrust to be transferred to hull, latent device is pushed to advance, while for reducing propeller dynamic
Transmitting of the exciting force to Ship Structure, reduces the vibration noise of Ship Structure.
The principle of the present invention are as follows: deep diving dive device shafting bear thrust be mainly made of two parts: 1 out of my cabin seawater pressure squeeze
Last item system crossing cabin section bring hydrostatic thrust, 2 propellers rotate the dynamicthrust applied to shafting.According to shafting, this stress is special
Property, setting two parts parallel-connection structure in thrust bearing inside bears thrust: 1 setting piston cylinder structure jointly, introduces external dynamic sea pressure
Power generates reversed hydrostatic thrust and offsets the static thrust that submerged condition shafting is subject to；2 setting damping elements, bear propeller rotation
The dynamicthrust of generation, and the vibration that the alternating component in dynamicthrust of decaying generates.
Since positive 6 inner piston structure of vehicle cushion cylinder bears partial cross section product summation and the shafting crossing cabin position section of seawater pressure
Area is consistent, and seawater pressure shaft is consistent with the hydrostatic thrust that bearing applies under same water pressure condition, so that shafting is just
Self-balancing is kept under hydrostatic thrust in anti-both direction, damping element is not subjected to hydrostatic thrust effect, so that thrust bearing
Effective vibration damping range is no longer limited by latent device submerged depth.
Seawater pressure compensator internal diaphragm can directly transmit outboard while insulating sea water and hydraulic oil two media
Seawater pressure, so that positive vehicle cushion cylinder cavity pressure and shafting tail portion crossing cabin position seawater pressure are almost the same, it can be ensured that shafting
Hydrostatic thrust consistency suffered by both ends.
Again, the shock-absorbing spring being arranged in cushion cylinder, to paddle shaft system just, the vibration of the full range of speeds of reversing plays very well
Vibration isolation effect.Shock-absorbing spring applies pretightning force when installing, and rigidity is stablized within the scope of propeller dynamicthrust, high reliablity, long
Time use is not in rigidity creep.
The vibration damping thrust bearing with hydrostatic thrust Self-balancing, it is characterised in that: its cushion cylinder chamber of moving backward
Interior hydraulic oil is directly connected with the intracavitary lubricating oil of thrust bearing, does not transmit external dynamic sea pressure, the intracavitary compression bullet of cushion cylinder of moving backward
Spring directly bears shafting reversing pulling force, and shafting vibration passes through transmitting of the thrust bearing to Ship Structure under astern condition of decaying.
Compared with the existing technology, the beneficial effects of the present invention are: 1, cushion cylinder is set in thrust bearing, and introduce the side of a ship
Outer seawater pressure, so that hydrostatic pressure and shafting hydrostatic thrust self-balancing, shock-absorbing spring is not subjected to hydrostatic thrust compression, vibration damping
The effective vibration damping range of thrust bearing extends to full depth；2, selecting helical spring is damping element, in propeller dynamicthrust range
Interior rigidity is stablized, high reliablity, for a long time using being not in rigidity creep.3, ahead and astern end is respectively provided with shock-absorbing spring,
Increase propeller-excited vibration frequency and natural frequency of shafting ratio, reduce shafting longitudinal vibration intrinsic frequency, just, to paddle shaft system
Good vibration isolation is played the role of in the vibration of the full range of speeds of vehicle, and the present invention is especially suitable for the latent device Propulsion Systems of latent device.
Detailed description of the invention
Attached drawing 1 is the structural schematic diagram for the vibration damping thrust bearing that the present invention has hydrostatic thrust Self-balancing.
Attached drawing 2 is positive 6 structural schematic diagram of vehicle cushion cylinder in Fig. 1 (other side is not correspondingly, otherwise shown).
Attached drawing 3 is the seawater pressure compensator structure schematic diagram in Fig. 1.
Specific embodiment
The present invention is further illustrated with use-case is implemented with reference to the accompanying drawing.The specific embodiment of the invention patent
See 1 ~ attached drawing of attached drawing 3, the present invention will be further explained below with reference to the attached drawings.
A kind of vibration damping thrust bearing with hydrostatic thrust Self-balancing being installed on main Propulsion Systems of the invention, packet
Include thrust axis 1, shell 2, reversing cushion cylinder 3, thrust block pad 4, support stationary ring 5, positive vehicle cushion cylinder 6, support bearing shell 7, fluid pressure line
8, seawater pressure compensator 9 and lateral oil seal etc..Applied to the self-balancing in paddle shaft system operation.
Wherein each component layout relationship is shown in attached drawing 1: thrust axis 1 is threaded through 2 center of shell, thrust axis 1 along casing centerline
Both ends are located at the outside of shell 2, and thrust disc 1.1 is arranged in the middle part of thrust axis 1, and 1.1 disk of thrust disc is mutually hung down with casing centerline
Straight setting；Inside shell 2,1.1 two sides of thrust disc are divided into positive vehicle end and reversing end, in positive vehicle end and reversing end, by thrust
Block 4, support stationary ring 5, support bearing shell 7 form shock-damping structure to accommodate cushion cylinder；Thrust block pad 4 is arranged in pushing away for thrust axis 1
1.1 two sides of power disk and lean against thrust disc 1.1 setting, the inside of thrust block pad 4 respectively by respective side cushion cylinder (reversing cushion cylinder
3 and positive vehicle cushion cylinder 6) support；Support stationary ring 5 is mounted in shell 2, is close to the setting of 2 inner wall of shell, and support bearing shell 7 is mounted on
It supports in 5 inner hole of stationary ring, supports and place thrust axis 1 inside bearing shell 7；Support 5 exit orifice inner wall of stationary ring and support 7 outer wall of bearing shell it
Between, reversing cushion cylinder 3 and positive vehicle cushion cylinder 6 are separately mounted to down, in the support stationary ring 5 at just vehicle end；The thrust block pad 4 at positive vehicle end,
Positive vehicle cushion cylinder 6, thrust block pad 4, the reversing cushion cylinder 3 at end of moving backward are formed by eight pieces, are circumferentially uniformly distributed along axial line；Shell
2 both ends are equipped with lateral oil seal, and positive vehicle cushion cylinder 6 is connect by fluid pressure line 8 with the seawater pressure compensator 9 in 2 outside of shell；
Shell 2 is vertically disposed with lubricating oil inlet and outlet, and the lubricating oil for thrust bearing is output and input.
As shown in Fig. 2, including the components such as piston 10, spring 11, piston cylinder 12, cover board 13, spring 11 in positive vehicle cushion cylinder 6
It is arranged between piston 10 and pressing plate 13.Such as Fig. 3, seawater pressure compensator 9 includes left side cylinder body 14, right side cylinder body 16, diaphragm
15 equal components, diaphragm 15 are mounted between cylinder body 14,16.
By fluid pressure line 8 full of hydraulic between the piston 10 of positive vehicle cushion cylinder 6 and the diaphragm 15 of seawater pressure compensator 9
Oil, diaphragm 15 and 16 outside of right side cylinder body and sea water service system connection out of my cabin.The connection state can guarantee the piston of positive vehicle cushion cylinder 6
10 side hydraulic fluid pressures are consistent with seawater pressure out of my cabin, and the hydrostatic thrust generated is transferred to thrust block pad 4 by piston 10, into
And shafting is transferred to by thrust axis 1, offset the hydrostatic thrust that shafting is born.That is the hydrostatic thrust value of shafting is exactly crossing cabin position
Area multiply outside seawater pressure.
Reversing cushion cylinder 3 is then directly communicated with the intracavitary lubricating oil of thrust bearing, does not transmit external dynamic sea pressure, cushion cylinder of moving backward
3 shock-absorbing spring 11 bears paddle shaft system astern thrust and its oscillating component of decaying.
The positive vehicle of dynamic propulsive force that generates in paddle shaft system operation or reversing are transferred to work by thrust axis, thrust block pad
Plug 10, then shell is transferred to by spring 11, and then be transferred to Ship Structure.Dynamic propulsive force spring 11 in transmittance process
Can decay its pulsating force, and transmitting of the paddle shaft system vibration to Ship Structure is isolated.
Claims (8)
1. a kind of vibration damping thrust bearing with hydrostatic thrust Self-balancing, including bear box and thrust axis, thrust axis edge
Casing centerline is worn and both ends are located at hull outside；It is born jointly it is characterized in that two parts parallel-connection structure is arranged in Bearing inner
And balance thrust；
Thrust disc is arranged in the middle part of thrust axis, and thrust disc two sides are divided into positive vehicle end and reversing end, and positive vehicle end and reversing end are respectively arranged
Multiple cushion cylinders, positive vehicle end cushion cylinder are connected by fluid pressure line and the seawater pressure compensator of hull outside；
Cushion cylinder one end housing in positive vehicle end is vertically disposed with lubricating oil inlet and outlet, and shafting tail portion crossing cabin position seawater pressure passes through seawater
Pressure compensator passes to the positive vehicle end cushion cylinder, and the shell of positive vehicle end cushion cylinder one end is vertically disposed with lubricating oil inlet and outlet,
Thrust bearing realizes that lubricating oil is output and input according to seawater pressure；Move backward the intracavitary hydraulic oil of end cushion cylinder directly with vibration damping thrust axis
It holds intracavitary lubricating oil to communicate, does not transmit seawater pressure.
2. the vibration damping thrust bearing according to claim 1 with hydrostatic thrust Self-balancing, it is characterised in that: vibration damping
Cylinder forms spring shock absorption piston structure by piston, spring, piston cylinder, cover board, spring along straight line compression direction be arranged in piston with
Between pressing plate；Vibration damping the cylinder piston is arranged in an axially parallel mode with thrust axis.
3. the vibration damping thrust bearing according to claim 1 with hydrostatic thrust Self-balancing, it is characterised in that: positive vehicle
The partial cross section product summation that cushion cylinder inner piston structure bears seawater pressure is consistent with shafting crossing cabin position sectional area.
4. the vibration damping thrust bearing according to claim 1 with hydrostatic thrust Self-balancing, it is characterised in that: seawater
Pressure compensator includes the left side cylinder body and right side cylinder body for being connected with each other and fastening, and cylinder body and right side cylinder body junction in left side are left
Diaphragm is also set up between side cylinder body and right side cylinder body；Lead between the piston of positive vehicle end cushion cylinder and the diaphragm of seawater pressure compensator
Fluid pressure line is crossed full of hydraulic oil, diaphragm and right side cylinder body outside and sea water service system connection out of my cabin.
5. the vibration damping thrust bearing according to claim 1 with hydrostatic thrust Self-balancing, it is characterised in that: just
In vehicle end and reversing end, the cushion cylinder is accommodated at damping peripheral structure by thrust block pad, support stationary ring, support shaft shoe；It pushes away
Power block is arranged in the thrust disc two sides of thrust axis and leans against thrust disc setting, and the inside of thrust block pad is respectively by respective side
Cushion cylinder support；Inner walls setting is installed in the housing and be close to support stationary ring, and support bearing shell is mounted on support stationary ring inner hole
In, thrust axis is placed inside support bearing shell；It is arranged in space between support stationary ring exit orifice inner wall and support bearing shell outer wall and subtracts
Shake cylinder.
6. the vibration damping thrust bearing according to claim 1 with hydrostatic thrust Self-balancing, it is characterised in that: positive vehicle
In end and reversing end, thrust block pad and cushion cylinder are correspondingly arranged multiple；And at each end, multiple cushion cylinders are along thrust axis axial line
Circumferentially it is uniformly distributed.
7. the vibration damping thrust bearing according to claim 1 with hydrostatic thrust Self-balancing, it is characterised in that: positive vehicle
The thrust block pad at end, positive vehicle end cushion cylinder, the thrust block pad at end of moving backward, reversing cushion cylinder are formed by eight pieces.
8. the vibration damping thrust bearing according to claim 1 with hydrostatic thrust Self-balancing, it is characterised in that: shell
Both ends are equipped with lateral oil seal.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811343052.3A CN109281926B (en) | 2018-11-13 | 2018-11-13 | Vibration reduction thrust bearing with hydrostatic thrust self-balancing function |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811343052.3A CN109281926B (en) | 2018-11-13 | 2018-11-13 | Vibration reduction thrust bearing with hydrostatic thrust self-balancing function |
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| Publication Number | Publication Date |
|---|---|
| CN109281926A true CN109281926A (en) | 2019-01-29 |
| CN109281926B CN109281926B (en) | 2020-01-14 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201811343052.3A Active CN109281926B (en) | 2018-11-13 | 2018-11-13 | Vibration reduction thrust bearing with hydrostatic thrust self-balancing function |
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Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110588942A (en) * | 2019-07-19 | 2019-12-20 | 中国船舶重工集团公司第七一九研究所 | Ship shafting thrust transmission device |
| CN111442051A (en) * | 2020-04-24 | 2020-07-24 | 中国舰船研究设计中心 | Active thrust balance type shafting longitudinal vibration damper |
| CN112503091A (en) * | 2020-12-16 | 2021-03-16 | 华中科技大学 | Hydraulic supporting structure of ship sliding thrust bearing |
| CN113107971A (en) * | 2021-05-06 | 2021-07-13 | 东台市远洋船舶配件有限公司 | Thrust bearing with vibration-damping piston |
| CN113386939A (en) * | 2021-06-24 | 2021-09-14 | 中国舰船研究设计中心 | Thrust bearing device with compact structure |
| CN113494525A (en) * | 2021-07-22 | 2021-10-12 | 中国船舶重工集团公司第七一一研究所 | Thrust bearing |
| CN113653764A (en) * | 2021-07-27 | 2021-11-16 | 中国舰船研究设计中心 | Damping thrust bearing based on hydraulic servo control |
| CN114087280A (en) * | 2021-12-23 | 2022-02-25 | 中车株洲电机有限公司 | Thrust air bearing assembly |
| CN114112395A (en) * | 2021-12-21 | 2022-03-01 | 上海交通大学 | Multi-condition vibration-damping loading thrust sliding bearing test bench |
| CN114810883A (en) * | 2022-04-28 | 2022-07-29 | 中国舰船研究设计中心 | Thrust bearing vibration damping structure with double springs supported in parallel on two sides |
| CN115076222A (en) * | 2022-06-29 | 2022-09-20 | 中国舰船研究设计中心 | Thrust and support function decoupling thrust bearing longitudinal vibration damper |
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Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110588942A (en) * | 2019-07-19 | 2019-12-20 | 中国船舶重工集团公司第七一九研究所 | Ship shafting thrust transmission device |
| CN111442051A (en) * | 2020-04-24 | 2020-07-24 | 中国舰船研究设计中心 | Active thrust balance type shafting longitudinal vibration damper |
| CN112503091A (en) * | 2020-12-16 | 2021-03-16 | 华中科技大学 | Hydraulic supporting structure of ship sliding thrust bearing |
| CN113107971A (en) * | 2021-05-06 | 2021-07-13 | 东台市远洋船舶配件有限公司 | Thrust bearing with vibration-damping piston |
| CN113386939B (en) * | 2021-06-24 | 2022-06-28 | 中国舰船研究设计中心 | Thrust bearing device with compact structure |
| CN113386939A (en) * | 2021-06-24 | 2021-09-14 | 中国舰船研究设计中心 | Thrust bearing device with compact structure |
| CN113494525A (en) * | 2021-07-22 | 2021-10-12 | 中国船舶重工集团公司第七一一研究所 | Thrust bearing |
| CN113494525B (en) * | 2021-07-22 | 2023-02-03 | 中国船舶集团有限公司第七一一研究所 | Thrust bearing |
| CN113653764A (en) * | 2021-07-27 | 2021-11-16 | 中国舰船研究设计中心 | Damping thrust bearing based on hydraulic servo control |
| CN114112395A (en) * | 2021-12-21 | 2022-03-01 | 上海交通大学 | Multi-condition vibration-damping loading thrust sliding bearing test bench |
| CN114087280A (en) * | 2021-12-23 | 2022-02-25 | 中车株洲电机有限公司 | Thrust air bearing assembly |
| CN114810883A (en) * | 2022-04-28 | 2022-07-29 | 中国舰船研究设计中心 | Thrust bearing vibration damping structure with double springs supported in parallel on two sides |
| CN114810883B (en) * | 2022-04-28 | 2024-04-26 | 中国舰船研究设计中心 | Thrust bearing vibration reduction structure with double springs and double-side parallel support |
| CN115076222A (en) * | 2022-06-29 | 2022-09-20 | 中国舰船研究设计中心 | Thrust and support function decoupling thrust bearing longitudinal vibration damper |
| CN115076222B (en) * | 2022-06-29 | 2024-04-12 | 中国舰船研究设计中心 | Thrust bearing longitudinal vibration damper with decoupling thrust and supporting function |
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