CN102927137B - Disc spring type vibration attenuation thrust bearing - Google Patents
Disc spring type vibration attenuation thrust bearing Download PDFInfo
- Publication number
- CN102927137B CN102927137B CN201210437526.7A CN201210437526A CN102927137B CN 102927137 B CN102927137 B CN 102927137B CN 201210437526 A CN201210437526 A CN 201210437526A CN 102927137 B CN102927137 B CN 102927137B
- Authority
- CN
- China
- Prior art keywords
- thrust
- bearing
- ring
- thrust block
- pad
- 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.)
- Active
Links
Landscapes
- Support Of The Bearing (AREA)
- Vibration Prevention Devices (AREA)
Abstract
The invention discloses a disc spring type vibration attenuation thrust bearing which comprises a shell body and a thrust shaft, bearing bushes are arranged on both sides of the shell body, the thrust shaft is supported in the bearing bushes of the shell body, a thrust ring is arranged on the thrust shaft, thrust block groups, thrust support rings and washers are symmetrically arranged on both sides of the thrust ring. The disc spring type vibration attenuation thrust bearing is characterized in that a ring-shaped dovetail groove with an opening is arranged at one end of the thrust support rings, the thrust block groups are arranged in the ring-shaped dovetail groove in a clamping mode and distributed in a ring shape, through holes are formed in the ring-shaped dovetail groove of the thrust support rings at intervals, thrust block supports and disc spring groups are arranged in the through holes, the outer ends of the thrust block supports are tightly close to the thrust block groups, the inner ends of the thrust block supports are configured with the disc spring group and gaps are reserved between the thrust block supports and the washers, and the washers are fixedly connected with the inner end of the shell body. The vibration attenuation disc spring groups are arranged so as to reduce longitudinal rigidity of a shaft system, enable longitudinal inherent frequency of the shaft system to be reduced, stagger resonance with a propeller, and decrease transmission of longitudinal vibration of the shaft system.
Description
Technical field
The present invention relates to a kind of thrust-bearing, particularly a kind of disk spring type vibration damping thrust-bearing.
Background technique
Thrust-bearing is the visual plant of marine propuision system, and it passes to propeller cavitation by the moment of torsion of the positive and negative both direction of propulsion electric machine, and thrust and pulling force that propeller cavitation is produced pass to hull, promotes ship's navigation.Because propeller cavitation rotates in inhomogeneous flow field, there is the alternating component of certain frequency in the thrust of generation, forms extensional vibration exciting force, easily by axle be-thrust-bearing transmits to hull, causes that hull vibrates.
Domestic existing boats and ships are generally comprised of ahead thrust piece, astern thrust piece, thrust axis, thrust-balancing mechanism, block bearing, upper-lower casing and turnover oil pipe line etc. with thrust-bearing.The thrust-bearing longitudinal rigidity of this structure is higher, and making axle is that longitudinal natural frequency is higher, easily with propeller exciting force, resonates, and increases the vibration transmission to hull.
Summary of the invention
Technical problem to be solved by this invention is to provide a kind of disk spring type vibration damping thrust-bearing for above-mentioned the deficiencies in the prior art, it is longitudinal rigidity that this thrust-bearing carrys out adjusting axle by change stiffness characteristics, increase propeller excited frequency and natural frequency of shafting ratio, thereby reduce shafting longitudinal vibration to the transmission of hull.
The present invention solves the problems of the technologies described above adopted technological scheme to be: disk spring type vibration damping thrust-bearing, it comprises housing and thrust axis, in the both sides of housing, be provided with bearing shell hole, thrust axis is bearing in the bearing shell hole of housing, thrust axis is provided with Thrust ring, bilateral symmetry at Thrust ring is provided with thrust block pad group, thrust bearing ring, pad, it is characterized in that the one end at thrust bearing ring is provided with the annular dovetail slot of opening, thrust block pad group is installed in annular dovetail slot and distributes ringwise, in the annular dovetail slot of thrust bearing ring, be interval with through hole, thrust block pad supporting and dish spring group are set in each through hole, the outer end of thrust block pad supporting is near thrust block pad group, inner and the assembly of dish spring is put and and pad between leave gap, described pad is fixedly connected with housing the inner.
By technique scheme, the exterior edge face of thrust block pad supporting is higher than the groove bottom of the dovetail groove of thrust bearing ring.
By technique scheme, described dish spring group is by two involutory combining of belleville spring.
By technique scheme, described thrust block pad group is comprised of 6 or 8 thrust block pads, and described thrust block pad is fan shape, and the thrust block pad between the both sides of thrust block pad are equipped with boss, are adjacent splices by boss, forms a complete annulus.
By technique scheme, the thrust block pad between the opening of the dovetail groove of thrust bearing ring adjacent is spliced to form a complete annulus by block.
By technique scheme, on the face contacting with Thrust ring at thrust block pad, be covered with babbit layer.
By technique scheme, the gap between thrust block pad supporting and pad is 1mm-5mm.
The obtained beneficial effect of the present invention is: 1, vibration damping dish spring group is set in propeller thrust bang path, and reducing axle is longitudinal rigidity, and making axle is that longitudinal natural frequency reduces, and the resonance staggering with propeller cavitation, reduces the transmission of shafting longitudinal vibration.2, the gap between thrust block pad supporting and pad has formed the stroke limit of dish spring group, makes the present invention have change stiffness characteristics, and low-thrust lower thrust-bearing provides low longitudinal rigidity, and adjusting axle is longitudinal natural frequency; High thrust lower thrust-bearing provides high longitudinal rigidity, and it is the user demand of other equipment that the change stiffness characteristics of bearing has met axle; 3, many group dish spring groups are evenly set in thrust bearing ring, make its suffered internal load even, while guaranteeing end thrust, each thrust block pad is stressed evenly; 4, the present invention has increased propeller-excited vibration frequency and natural frequency of shafting ratio, has reduced shafting longitudinal vibration natural frequency, and shafting vibration is played to good vibration isolation effect, and the present invention is specially adapted to marine propulsion shafting.
Accompanying drawing explanation
Fig. 1 is structural representation of the present invention.
Fig. 2 is the plan view of ahead thrust supporting ring in Fig. 1, dish spring group, pad.
Fig. 3 is the A-A sectional view of Fig. 2.
Fig. 4 is thrust block pad structural representation.
Fig. 5 is the longitudinal section of Fig. 4.
Fig. 6 is that thrust block pad is arranged schematic diagram.
In figure: 1, thrust axis, 2, top cover, 3, block, 4, ahead thrust supporting ring, 5, upper shell, 6, pad, 7, top bearing shell, 8, oil sealing, 9, flinger ring, 10, end cap, 11, lower shell body, 12, astern thrust supporting ring, 13, astern thrust piece group, 14, ahead thrust piece group, 15, thrust block pad supporting, 16, dish spring group, 17, lower bearing.
Embodiment
Below in conjunction with accompanying drawing, patent of the present invention is described further.
As shown in Figure 1, disk spring type vibration damping thrust-bearing, it comprises upper shell 5, lower shell body 11 and thrust axis 1, upper shell 5, lower shell body 11 are casting, it is the pedestal of arranging bearing major part, the both sides of the housing of assembling at upper and lower casing are provided with bearing shell hole, thrust axis 1 is bearing in the bearing shell hole of housing, the left and right two ends of thrust axis 1 are bearing in respectively on radial support bearing shell, top bearing shell 7 and lower bearing 17 that radial support bearing shell is semi-cylindrical by internal surface form, and are fixed by screws on upper shell 5 and lower shell body 11.The two ends of housing are all connected with end cap 10 flanges, are provided with successively flinger ring 9 and oil sealing 8 between end cap 10 and radial support bearing shell.In the cavity of housing, be positioned on thrust axis 1 and be provided with Thrust ring, in the both sides of Thrust ring, be disposed with respectively ahead thrust piece group 14, ahead thrust supporting ring 4, pad 6 and astern thrust piece group 13, astern thrust supporting ring 12, pad; The component that are positioned at Thrust ring both sides in housing are symmetrical set, and described pad is fixedly connected with the inner of housing.When positive car and reversing transmission power, use respectively two faces of Thrust ring.The positive car end of take below describes the structure of enclosure interior in detail as example.
As Fig. 2, 3, 4, 5, shown in 6, in one end of ahead thrust supporting ring 4, be provided with the annular dovetail slot of opening, ahead thrust piece group 14 is comprised of 6 or 8 thrust block pads, described thrust block pad is fan shape, one end correspondence of thrust block pad is arranged to swallow-tail form, thrust block pad group is installed in annular dovetail slot and distributes ringwise, the opening radian of the annular dovetail slot of ahead thrust supporting ring 4 is slightly larger than the covering of the fan radian of thrust block pad, and this opening is positioned at the upside of ahead thrust supporting ring, both sides at thrust block pad are equipped with boss, thrust block pad between adjacent is spliced to form by boss the rotation that a complete annulus prevents thrust block pad when moving, hoop residual gap is filled up by block 3.In the annular dovetail slot of ahead thrust supporting ring 4, be interval with through hole, the quantity of through hole and the quantity of thrust block pad are one to one, thrust block pad supporting 15 and dish spring group 16 are set in each through hole, and the outer end of thrust block pad supporting 15 is the groove bottom higher than the dovetail groove of ahead thrust supporting ring 4 near thrust block pad and this end face.Between the inner end face of thrust block pad supporting 15 and pad 6, leave gap, the gap between thrust block pad supporting and pad has formed the stroke limit of dish spring group.Pad and ahead thrust supporting ring 4 are bolted and are integrated, and are arranged on housing.At thrust block pad, towards the end face of Thrust ring, be covered with Babbitt, be in operation and allow this face to have appropriate wearing and tearing.
Wherein, dish spring group 16 is by two involutory combining of belleville spring.The thrust block pad supporting, thrust bearing ring and the gasket material that contact with dish spring are high hardness Bearing Steel, and part surface has higher fatigue strength.
Working principle of the present invention is: when positive car, thrust axis 1 is delivered to ahead thrust piece group 14 by thrust by Thrust ring, the thrust block pad of ahead thrust piece group is delivered to power in thrust block pad supporting, due to gapped between thrust block pad supporting and pad, thrust block pad supporting, by compact disc spring group, when low-thrust is in the travel range of dish spring, still leaves gap between thrust block pad supporting and pad, now, thrust-bearing has low longitudinal rigidity; When high thrust, close contact between thrust block pad supporting and pad, now, thrust-bearing has high longitudinal rigidity.
Vibration damping dish spring group is set in thrust-bearing, and having reduced axle is longitudinal rigidity, is that axle is that longitudinal natural frequency reduces, and the resonance having staggered with propeller cavitation, has reduced the transmission of shafting longitudinal vibration.
Simultaneously, because axle is after longitudinal rigidity reduces, high thrust lower shaft system can produce larger length travel, and this will affect the sealability of usability, particularly stern tube seal system that axle is miscellaneous equipment, now, the gap arranging between thrust block pad supporting and pad is 1mm-5mm, axle is tied up in the length travel of design, and guaranteed the sealability of stern tube seal system, particularly during 2mm, effect is best.
In sum, to take into account axle be that longitudinal natural frequency regulates and axle is the composite demand that other equipment length travels limit in the present invention.The present invention has increased propeller-excited vibration frequency and natural frequency of shafting ratio, has reduced shafting longitudinal vibration natural frequency, and shafting vibration is played to good vibration isolation effect, and it is the user demand of other equipment that the change stiffness characteristics of while bearing has met axle.
Claims (6)
1. disk spring type vibration damping thrust-bearing, it comprises housing and thrust axis, in the both sides of housing, be provided with bearing shell hole, thrust axis is bearing in the bearing shell hole of housing, thrust axis is provided with Thrust ring, bilateral symmetry at Thrust ring is provided with thrust block pad group, thrust bearing ring, pad, it is characterized in that the one end at thrust bearing ring is provided with the annular dovetail slot of opening, thrust block pad group is installed in annular dovetail slot and distributes ringwise, in the annular dovetail slot of thrust bearing ring, be interval with through hole, thrust block pad supporting and dish spring group are set in each through hole, the outer end of thrust block pad supporting is near thrust block pad group, inner and the assembly of dish spring is put and and pad between leave gap, described pad is fixedly connected with housing the inner.
2. disk spring type vibration damping thrust-bearing according to claim 1, is characterized in that the exterior edge face of thrust block pad supporting is higher than the groove bottom of the dovetail groove of thrust bearing ring.
3. disk spring type vibration damping thrust-bearing according to claim 1 and 2, is characterized in that described dish spring group is by two involutory combining of belleville spring.
4. disk spring type vibration damping thrust-bearing according to claim 1 and 2, it is characterized in that described thrust block pad group is comprised of 6 or 8 thrust block pads, described thrust block pad is fan shape, both sides at thrust block pad are equipped with boss, thrust block pad between adjacent splices by boss, forms a complete annulus.
5. disk spring type vibration damping thrust-bearing according to claim 1 and 2, is covered with babbit layer on the face that it is characterized in that contacting with Thrust ring at thrust block pad.
6. disk spring type vibration damping thrust-bearing according to claim 1 and 2, is characterized in that the gap between thrust block pad supporting and pad is 1mm-5mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210437526.7A CN102927137B (en) | 2012-11-06 | 2012-11-06 | Disc spring type vibration attenuation thrust bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210437526.7A CN102927137B (en) | 2012-11-06 | 2012-11-06 | Disc spring type vibration attenuation thrust bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102927137A CN102927137A (en) | 2013-02-13 |
| CN102927137B true CN102927137B (en) | 2014-10-29 |
Family
ID=47642027
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210437526.7A Active CN102927137B (en) | 2012-11-06 | 2012-11-06 | Disc spring type vibration attenuation thrust bearing |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN102927137B (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103499582B (en) * | 2013-09-27 | 2015-11-25 | 首钢京唐钢铁联合有限责任公司 | Thrust pad inspection method for damping thrust bearing |
| CN105114608A (en) * | 2015-09-30 | 2015-12-02 | 哈尔滨广瀚动力传动有限公司 | Vibration reduction supporting device used for sliding bearing |
| CN107368662A (en) * | 2017-07-29 | 2017-11-21 | 哈尔滨理工大学 | A kind of equal loading capability computational methods of variation rigidity point support tilting thrust bearing |
| CN108561503A (en) * | 2018-04-12 | 2018-09-21 | 上海交通大学 | The unit of dynamic absorber containing Negative stiffness spring and thrust bearing |
| CN113386939B (en) * | 2021-06-24 | 2022-06-28 | 中国舰船研究设计中心 | Thrust bearing device with compact structure |
| 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 |
| CN114104244B (en) * | 2021-12-06 | 2023-06-23 | 上海涟屹轴承科技有限公司 | Thrust bearing structure for ship |
| 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 |
| 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 |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4856914A (en) * | 1987-01-26 | 1989-08-15 | Maag Gear-Wheel & Machine Company Limited | Thrust bearing arrangement |
| CN1247282A (en) * | 1998-09-04 | 2000-03-15 | 哈尔滨市大通动力设备开发有限公司 | Multi-support elastic metal-plastic thrust bearing |
| CN2473377Y (en) * | 2001-04-27 | 2002-01-23 | 许国林 | Rigid support thrust slide bearing |
-
2012
- 2012-11-06 CN CN201210437526.7A patent/CN102927137B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4856914A (en) * | 1987-01-26 | 1989-08-15 | Maag Gear-Wheel & Machine Company Limited | Thrust bearing arrangement |
| CN1247282A (en) * | 1998-09-04 | 2000-03-15 | 哈尔滨市大通动力设备开发有限公司 | Multi-support elastic metal-plastic thrust bearing |
| CN2473377Y (en) * | 2001-04-27 | 2002-01-23 | 许国林 | Rigid support thrust slide bearing |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102927137A (en) | 2013-02-13 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102927137B (en) | Disc spring type vibration attenuation thrust bearing | |
| CN102322476B (en) | Tilting-pad water-lubricated rubber alloy bearing | |
| CN204985330U (en) | Mechanical type damping thrust bearing | |
| CN105840729A (en) | Shafting bearing vibration-reducing base for ship bulkhead | |
| CN102937146A (en) | Hydraulic integrated vibration reduction and absorption thrust bearing | |
| CN109707736A (en) | A kind of compound titling-pad journal bearing of magnetic liquid based on Halbach array | |
| CN112228449B (en) | Variable-rigidity intelligent water-lubricated bearing and power transmission system thereof | |
| CN201351688Y (en) | High-elasticity spring pin shaft coupler | |
| CN113335488B (en) | Two-stage longitudinal vibration isolation shafting | |
| CN106428493B (en) | A kind of propeller for vessels pendulum rotation flexible parallel connection driving device | |
| US9221530B2 (en) | Ship propulsion system and ship equipped therewith | |
| CN103717930A (en) | Rotary joint for underwater operation and system equipped therewith for generating energy from waterpower | |
| CN113048150B (en) | Magnetic gradient and array arrangement large-bearing magnetic liquid double-floating radial bearing | |
| CN104670463A (en) | Electric steering mechanism | |
| CN203627641U (en) | Semi-active hydraulic vibration-absorption thrust bearing | |
| CN103299066A (en) | Bearing assembly for a marine turbine shaft, and marine turbine including such a bearing assembly | |
| CN108730349A (en) | A kind of integrated form oil-lubricated bearing having hub wheel edge propeller for deep-sea | |
| CN110159664A (en) | A kind of shafting thrust-compensating device | |
| CN109050861B (en) | Marine damping propeller shaft | |
| CN108374864B (en) | Liquid pulsation attenuation device and method for thrust bearing | |
| KR20080069552A (en) | Vessel with electric motor | |
| CN103527521B (en) | water jet propulsion pump | |
| CN106114797A (en) | A kind of full-rotating rudder paddle double-layer vibration damping device and method for designing thereof | |
| CN201176260Y (en) | Shock resistance axial seal device for screw shaft of ship shock resistance type axial seal device for stern shaft of shipping | |
| JP6435132B2 (en) | Superconducting rotating machine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |