CN104454980A - Novel energy-saving radial sliding bearing - Google Patents
Novel energy-saving radial sliding bearing Download PDFInfo
- Publication number
- CN104454980A CN104454980A CN201410563019.7A CN201410563019A CN104454980A CN 104454980 A CN104454980 A CN 104454980A CN 201410563019 A CN201410563019 A CN 201410563019A CN 104454980 A CN104454980 A CN 104454980A
- Authority
- CN
- China
- Prior art keywords
- bearing
- hole wall
- axle
- coating
- hole
- 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.)
- Granted
Links
- 238000000576 coating method Methods 0.000 claims abstract description 45
- 239000000463 material Substances 0.000 claims abstract description 12
- 239000011248 coating agent Substances 0.000 claims description 43
- 238000005461 lubrication Methods 0.000 claims description 38
- 239000000314 lubricant Substances 0.000 claims description 23
- 229910052799 carbon Inorganic materials 0.000 claims description 4
- 230000004323 axial length Effects 0.000 claims description 3
- 238000005516 engineering process Methods 0.000 abstract description 12
- 230000008901 benefit Effects 0.000 abstract description 8
- 239000010687 lubricating oil Substances 0.000 abstract description 8
- 239000011148 porous material Substances 0.000 abstract description 2
- 239000003921 oil Substances 0.000 description 25
- 239000012530 fluid Substances 0.000 description 23
- 230000001050 lubricating effect Effects 0.000 description 10
- 238000000034 method Methods 0.000 description 8
- 238000005253 cladding Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 230000007246 mechanism Effects 0.000 description 4
- 230000003068 static effect Effects 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 238000009826 distribution Methods 0.000 description 2
- 230000002706 hydrostatic effect Effects 0.000 description 2
- 238000010422 painting Methods 0.000 description 2
- 238000005096 rolling process Methods 0.000 description 2
- 238000010008 shearing Methods 0.000 description 2
- 238000001179 sorption measurement Methods 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 229910001018 Cast iron Inorganic materials 0.000 description 1
- 229910001208 Crucible steel Inorganic materials 0.000 description 1
- 239000005662 Paraffin oil Substances 0.000 description 1
- 239000000654 additive Substances 0.000 description 1
- 230000000996 additive effect Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000000052 comparative effect Effects 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 238000011156 evaluation Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 239000003292 glue Substances 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 239000011229 interlayer Substances 0.000 description 1
- 239000003879 lubricant additive Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Landscapes
- Sliding-Contact Bearings (AREA)
Abstract
The invention provides a novel energy-saving radial sliding bearing, which is formed by matching a shaft and a bearing sleeve hole or bearing block hole. A bearing sleeve hole wall or bearing block hole wall at an inlet region of a convergent wedge-shaped pore of the bearing is coated by a thin layer material, and the surface-treated bearing sleeve hole wall or bearing block hole wall is paired with the shaft; a gap formed between the bearing sleeve hole wall or bearing block hole wall and the shaft is filled with lubricating oil. The novel energy-saving radial sliding bearing designed by adopting an interface slip technology and adopting a surface coating method has the advantages of great carrying capacity, low coefficient of friction and excellent energy-saving performance. Compared with the traditional interface-slip-free radial sliding bearing, the bearing provided by the invention has the advantages of obviously improved carrying capacity, and obviously improved antifriction and energy-saving performances, thus having an important application value.
Description
Technical field
The present invention relates to a kind of novel energy-conserving radial plain bearing.
Background technique
Bearing is used to the important mechanical part supporting axial workpiece, point sliding bearing and two kinds, rolling bearing.Following main performance requirements is had: support accuracy, support stiffness, low coefficient of friction and wear-resistant for bearing.This just requires that bearing is a kind of very accurate mechanical part, also requires that it has enough large bearing capacity.In order to the antifriction that reached and wear-resisting property, bearing is also needed to have good greasy property.
Be developed so far, although bearing technology comparative maturity, be all based upon on traditional lubrication theory basis.At present, rolling bearing and sliding bearing are respectively applied to different occasion, respectively have its advantage.Be sliding bearing due to what the present invention relates to, existing existing sliding bearing type and technology be summarized as follows:
From lubrication mechanism, sliding bearing is divided into mixed friction sliding bearing and two kinds, fluid lubrication sliding bearing.The former relies on border adsorbed film and hydrodynamic effect to realize lubrication, for low speed, underloading and inessential occasion; The latter relies on fluid film to realize lubrication, for important events, applies more extensive.
Fluid lubrication sliding bearing is the main body of sliding bearing, is divided into again hydrldynamic pressure lubrication sliding bearing and two kinds, hydrostatic lubrication sliding bearing.Hydrostatic lubrication sliding bearing relies on extraneous hydraulic system fuel feeding, by oil lift load, lubricate by hydraulic oil, accuracy of manufacturing is high, structure is more complicated, cost is higher, for the important events requiring that support stiffness is large, support accuracy is high and bearing capacity is large.
Hydrldynamic pressure lubrication sliding bearing relies on hydrodynamic effect to realize lubrication, has that structure is comparatively simple, cost is lower, the advantage of better performances, is the more extensive and common sliding bearing of a kind of application.It is divided into again hydrldynamic pressure lubrication radial plain bearing and hydrldynamic pressure lubrication thrust slide bearing two kinds.The former is for supporting radial load, and the latter is for supporting thrust load.Below introduce existing main fluid hydrodynamic lubrication radial plain bearing type and feature thereof.
One, big L/D ratio radial plain bearing-long bearing
This bearing as shown in Figure 1.Due to slenderness ratio
comparatively large, this bearing can be processed into endless bearing and can ignore fluid side and let out impact on bearing load carrying capacity.At the bottom-right location of bearing, bearing hole forms the wedge gap of convergence.Due to the viscosity of fluid, fluid sticks, on axle, also sticks on bearing sleeve or bearing support.Due to the rotary motion of axle, fluid is seen in by the large end section from wedge shape hole, from the small end section belt of wedge shape hole out; Fluid thus be squeezed in wedge shape hole and form lubricating film pressure, makes lubricating film possess and bears radial load
wability.This is the working mechanism of this bearing.
Two, little slenderness ratio radial plain bearing-narrow bearing
This bearing as shown in Figure 2.Due to slenderness ratio
very little, fluid is serious along the axial leakage (namely side is let out) of bearing.Fluid is let out in side in process and is squeezed in narrow and small gap thus forms lubrication pressure, makes lubricating film possess the ability of bearing load.The wedge gap effect of the hole of this bearing is relatively little, negligible.This is the working mechanism of this bearing.
Three, Finite Width sliding bearing
This bearing as shown in Figure 3.Because slenderness ratio is moderate, bearing relies on the wedge shape hole of convergence to form lubricating film pressure, but the lateral leakage of fluid makes lubricating film pressure and bearing load carrying capacity decrease; Slenderness ratio is less, and lateral leakage is more serious, and bearing load carrying capacity reduces larger.When calculating this bearing load carrying capacity, should consider on endless bearing load carrying capacity basis that fluid side is let out impact and introduces a side relevant with slenderness ratio and let out correction factor.
In accompanying drawing 1 ~ Fig. 3, the friction factor of traditional radial plain bearing and bearing capacity calculate by conventional fluid lubrication theory.Conventional fluid lubrication theory is thought, fluid can stick to solid contact surface completely and slippage can not occur.Based on conventional fluid lubrication theory, the power-economizing method of this bearing was in the past: select proper lubrication oil, reduced lubricating oil viscosity, improved lubricating oil viscosity index i.e. sticky warm stability and use lubricant additive to improve frictional behaviour.But should be noted, this power-economizing method is based upon fluid-bearing surface interface without on the conventional fluid lubrication theory basis of slippage.When there is interface sliding in fluid lubrication, the power-economizing method of bearing and technology will change.
Summary of the invention
The object of this invention is to provide a kind of novel energy-conserving radial plain bearing using interface sliding technology.This power-economizing method advocates that use has the lubricant oil-contact surface interface of low sheraing intensity and produces interface sliding, and to realize low lubrication friction power, but bearing load carrying capacity significantly improves on the contrary.Therefore this power-economizing method does not repel use thick oil, namely glues warm stability and use additive not claim in the lubricant yet to lubricating oil viscosity index.
Technical solution of the present invention is:
A kind of novel energy-conserving radial plain bearing, by axle with are formed bearing bush trepanning or coordinating of bearing saddle bore; Coated with sheet material on the bearing sleeve hole wall or bearing support hole wall of the inlet region of bearing convergence wedge shape hole; The central angle that on bearing hole wall, the region of applying coating is right is
,
span be:
,
preferred value be
,
with
; Surface treated bearing sleeve hole wall or bearing support hole wall and axle match, in the gap that bearing sleeve hole wall or bearing support hole wall and axle are formed, be full of lubricant oil; Dimensionless shear strength between lubricant oil and bearing hole wall coating
satisfy the following conditional expression:
（1）
Herein,
,
,
for the angular coordinates value of maximum oil film pressure position,
,
by the central angle that the surface of applying coating on bearing hole hole wall is right;
Dimensionless shear strength between lubricant oil and bearing hole wall coating
also must meet the following conditions:
（2）
Herein,
,
,
.
Further, the coating on bearing lubrication inlet region bearing sleeve hole wall or bearing support hole wall is for hating oil coating.
Further, the preferred fluororine-carbon coating of coating on bearing lubrication inlet region bearing sleeve hole wall or bearing support hole wall.
Further, the slenderness ratio L/D of this bearing is: L/D>0.2:L is the axial length of bearing, and D is the diameter of axle.
Further, the operating conditions of bearing is
; Herein
for eccentricity,
,
e: the hole heart offset distance of axle center and bearing hole;
c: bearing play,
,
for the radius of bearing hole,
for the radius of axle.
The invention has the beneficial effects as follows: the present invention uses interface sliding technology, adopt surface coating method to design novel energy-conserving radial plain bearing.Compared to traditional radial plain bearing without interface sliding, bearing of the present invention is not only significantly improved in bearing capacity, also significantly improves in antifriction and energy-efficient performance, has significant application value.The present invention has the following advantages:
(1) compared to traditional radial plain bearing, under the same terms, the friction factor of bearing of the present invention can reduce 60%, and its bearing capacity can improve 100%.
(2) bearing of the present invention has good antifriction and energy-efficient performance, and has higher bearing capacity.
(3) bearing of the present invention only need adopt coating and interface sliding technology can realize above performance, and therefore the technology of the present invention performance realizes simple, with low cost.
(4) compared to traditional radial plain bearing, bearing of the present invention has larger technical advantage and using value.
Bearing technology Be very effective of the present invention.It has larger bearing capacity, lower friction factor and excellent energy-efficient performance.Bearing technology performance of the present invention is given prominence to, and realizes simple, with low cost, has larger use value.
Accompanying drawing explanation
Fig. 1 is big L/D ratio radial plain bearing, namely
the structural representation of long bearing.
Fig. 2 is little slenderness ratio radial plain bearing, namely
the structural representation of narrow bearing.
Fig. 3 is Finite Width radial plain bearing, namely
the structural representation of bearing.
Fig. 4 is the structural representation of embodiment of the present invention bearing.
In Fig. 1, Fig. 2, Fig. 3, Fig. 4,1, axle, 2, bearing sleeve or bearing support, 3, position, lubricating oil inlet, 4, lubricating oil outlet position, 5, bearing hole.
Fig. 5 be embodiment design bearing internal pressure distribution and distribute with the radial plain bearing internal pressure without interface sliding traditional under the same terms compare schematic diagram.
Fig. 6 is different
,
with
under, the bearing capacity of embodiment's bearing
and with traditional radial plain bearing bearing capacity under the same terms
comparison schematic diagram.
Fig. 7 is different
,
with
under, the bearing hole wall friction coefficient of embodiment's bearing
and with traditional radial plain bearing bearing hole wall friction coefficient under the same terms
comparison schematic diagram.
Fig. 8 is different
,
with
under, the friction factor on the axle of embodiment's bearing
and with friction factor on traditional radial plain bearing axle under the same terms
comparison schematic diagram.
Embodiment
The preferred embodiments of the present invention are described in detail below in conjunction with accompanying drawing.
Embodiment
Embodiment coated with sheet material, has lower adsorption strength and shear strength between lubricant oil and this cladding material interface on the bearing sleeve or bearing support 2 hole wall of the inlet region of bearing convergence wedge shape hole.Work bottom bracket is static and axle 1 rotates, and lubricant oil in this section cladding material on the surface slippage occurs, and lubricant oil all slippage does not occur on bearing sleeve or bearing support 2 hole wall remaining surface and on the whole surface of axle 1.
According to the radial load direction that operating conditions middle (center) bearing bears, by installing, surface treated bearing sleeve or bearing support 2 hole wall and axle 1 being matched, in the micro-gap that bearing sleeve or bearing support 2 hole wall and axle 1 are formed, being full of lubricant oil.Like this, during work, the rotary motion of the certain orientation of axle 1 just can form lubricant film in the hole of bearing hole 5, just defines bearing of the present invention.
This bearing has larger bearing capacity than the conventional bearing without interface sliding.Because lubricating film, on bearing part surface, slippage occurs, therefore it has lower friction factor than conventional to hold without interface slip shaft.Fig. 4 provides the bearing of embodiment's design.
In angle
in the region contained and figure, applying coating on the bearing sleeve in " A " district or the hole wall of bearing support 2, makes lubricating film slippage on this coating surface.Remaining bearing hole 5 hole wall does not all cover any artificial coating, there is not slippage in lubricating film on the wall of these bearing holes 5.Any artificial coating is not covered on the whole surface of axle 1 yet, there is not slippage in lubricating film on the whole surface of axle 1.
The bearing of embodiment's design in Fig. 4.
: the rotational angular velocity of axle 1,
w: bearing load,
: the central angle that on bearing hole 5 hole wall, the surface of applying coating is right.For ease of bearing working performance evaluation, as shown in Figure 4, for embodiment's bearing defines following parameter:
Eccentricity:
,
e: the offset distance of the axle center of axle 1 and the hole heart of bearing hole 5;
c: bearing play,
,
with
be respectively the radius of bearing hole 5 radius and axle 1.
The dimensionless load that bearing bears:
,
w: the load that bearing unit width bears,
u: the peripheral velocity of axle 1,
: lubricating oil viscosity.
Lubricant film dimensionless pressure in bearing:
,
p: bearing lubrication oil film pressure.
The painting interlayer dimensionless shear strength of the wall of lubricant oil and bearing hole 5 is:
,
: the painting interlaminar shearing strength of the wall of lubricant oil and bearing hole 5.
For conventional axle 1, bearing sleeve or bearing support 2 pore wall material, the coating on bearing lubrication inlet region bearing sleeve of the present invention or bearing support 2 hole wall is preferably fluororine-carbon coating, and this coating has very strong oil repellency.
When lubricant oil is common paraffin oil, interface shear strength between lubricant oil and fluororine-carbon coating at normal temperatures and pressures
be about 0.05MPa.When
,
,
time,
.
(1) when
,
,
time, the bearing capacity on bearing unit width of the present invention is
, bearing hole 5 friction factor is
, the friction factor of axle 1 is
.Under identical working condition, the bearing capacity on the traditional bearing unit width of uncoated artificial coating is
, bearing hole 5 friction factor is
, the friction factor of axle 1 is
.
(2) when
,
,
time, the bearing capacity on bearing unit width of the present invention is
, bearing hole 5 friction factor is
, the friction factor of axle 1 is
.Under identical working condition, the bearing capacity on the traditional bearing unit width of uncoated artificial coating is
, bearing hole 5 friction factor is
, the friction factor of axle 1 is
.
(3) when
,
,
time, the bearing capacity on bearing unit width of the present invention is
, bearing hole 5 friction factor is
, the friction factor of axle 1 is
.Under identical working condition, the bearing capacity on the traditional bearing unit width of uncoated artificial coating is
, bearing hole 5 friction factor is
, the friction factor of axle 1 is
.
(4) when
,
,
time, the bearing capacity on bearing unit width of the present invention is
, bearing hole 5 friction factor is
, the friction factor of axle 1 is
.Under identical working condition, the bearing capacity on the traditional bearing unit width of uncoated artificial coating is
, bearing hole 5 friction factor is
, the friction factor of axle 1 is
.
enough low, could interface sliding be produced, need meet the following conditions:
（1）
Herein,
,
,
for the angular coordinates value of maximum oil film pressure position, as shown in Figure 4,
,
by the central angle that the surface of applying coating on bearing hole 5 hole wall is right.
also must meet the following conditions:
（2）
Herein,
,
,
.
Compared with traditional hydrldynamic pressure lubrication radial plain bearing without interface sliding, the bearing lubrication mechanism of the present invention's design has further essential improvement.It uses interface sliding technology to reduce pivot friction coefficient further, but improves bearing load carrying capacity on the contrary.When the large and interface shear strength in interface sliding region
time low, pivot friction coefficient of the present invention can be lower by 60% than traditional type pivot friction coefficient under the same conditions, and its bearing capacity can exceed 100% than traditional type bearing load carrying capacity.Therefore, the technical advantage of bearing of the present invention and using value are fairly obvious.
Form embodiment's bearing by the cooperation in the hole of axle 1 and bearing sleeve or bearing support 2, here, if indicate in Fig. 42 is bearing sleeve, then bearing sleeve 2 is fixed in bearing support, if without bearing sleeve, then indicate in Fig. 42 is bearing support.Axle 1 can be made up of various trade mark steel, but does not get rid of other material can be used to make; Bearing sleeve 2 is conventional bearings lining 2, but does not get rid of other material can be used to make; Bearing support is generally cast iron, cast steel or forged steel and makes, but does not get rid of other material can be used to make.
The technology of the present invention was both applicable to long bearing, was applicable to again Finite Width bearing.That is, the slenderness ratio L/D of bearing of the present invention is: L/D>0.2.Herein: L is the axial length of bearing, D is the diameter of axle 1.
Lubricant oil is full of between bearing hole 5 wall and axle 1.Bearing hole 5 is static, and axle 1 rotates, and sees Fig. 4.What bearing hole 5 wall applies one fixed width hates oil coating, and have lower adsorption strength and shear strength between lubricant oil and this cladding material interface, in work, lubricant oil on the surface slippage occurs at this cladding material.The central angle that on bearing hole 5 wall, the region of applying coating is right is
, as shown in Figure 4, bearing of the present invention
span be:
.The remaining surface of bearing hole 5 wall does not apply any artificial coating, the whole surface of axle 1 does not apply any artificial coating yet.There is not slippage in lubricant oil, the whole surface of axle 1 also slippage does not occur on bearing hole 5 wall of uncoated artificial coating.The rotary motion of axle 1 should make the region of applying coating on bearing hole 5 wall be in the lubricating inlet district of bearing, as shown in Figure 4.
Bearing Optimization Work condition of the present invention is
, but do not repel
operating conditions.
Principle explanation
Theoretical according to the interface sliding set up before, in the bearing of the present invention's design, due to the interface sliding (reaching this interface shear strength by this interface shearing stress to cause) between static bearing hole 5 wall coating and lubricant oil, flow of lubrication between bearing hole 5 wall coating and axle 1 increases further, if bearing internal pressure does not change, then it is greater than the flow of lubrication between the working surface of uncoated coating on bearing hole 5 wall and axle 1.Like this, the flow equilibrium condition of the fluid flowing in bearing is just broken.
This just requires that bearing internal pressure increases and makes the flow of lubrication of bearing lubrication inlet region (Ji Tu4Zhong A district) reduce (because bearing lubrication inlet region pressure gradient flow increases), the flow of lubrication of bearing lubrication outlet area (Ji Tu4Zhong B district) is increased (because bearing lubrication outlet area pressure gradient flow increases), thus make the fluid flow in bearing finally maintain balance, that is: make by the fluid flow of bearing cross section equal everywhere.
Like this, setting coating and by the interface sliding of generation be improved with regard to making the bearing capacity of this bearing.Because coating surface shear strength is low, surface friction drag is little, the coating therefore arranged and by the interface sliding of generation make the friction factor of this bearing reduce on the contrary, thus make this bearing have the advantage of antifriction, energy-conservation, high bearing capacity.The working principle of Here it is this bearing.
Under the present invention and the same terms, traditional contrast distributed without the radial plain bearing internal pressure of interface sliding is as follows:
In Fig. 5, (a) and (b) provides the bearing internal pressure distribution of embodiment's design and comparing of distributing with the radial plain bearing internal pressure without interface sliding traditional under the same terms thereof,
.In figure,
for the pressure in bearing of the present invention,
for the pressure in traditional radial plain bearing,
for taking position, lubricating oil inlet 3 as the angular coordinates of tolerance reference.As seen from the figure, the pressure of the pressure in the bearing of embodiment under being higher than the same terms in traditional radial plain bearing, and
larger and
less, the pressure in embodiment's bearing increases larger, and its bearing capacity is also larger.
In Fig. 6, (a) and (b) provides difference
,
with
under, the bearing capacity of embodiment's bearing
and with traditional radial plain bearing bearing capacity under the same terms
comparison.As seen from the figure, under the same terms, the bearing capacity of the bearing of embodiment is larger than traditional radial plain bearing bearing capacity, and
larger and
less, the bearing capacity increasing amount of embodiment's bearing is larger, and the technique effect of embodiment's bearing is better.
In Fig. 7, (a) and (b) provides difference
,
with
under, the bearing hole 5 wall friction coefficient of embodiment's bearing
and with traditional radial plain bearing bearing hole 5 wall friction coefficient under the same terms
comparison.As seen from the figure, under the same terms, the bearing hole 5 wall friction coefficient ratio tradition radial plain bearing bearing hole 5 wall friction coefficient of embodiment's bearing is little, and
larger and
less, the bearing hole 5 wall friction coefficient of embodiment's bearing is less.
In Fig. 8, (a) and (b) provides difference
,
with
under, the friction factor on the axle 1 of embodiment's bearing
and with friction factor on traditional radial plain bearing axle 1 under the same terms
comparison.As seen from the figure, under the same terms, on the axle 1 of embodiment's bearing, friction factor is less than friction factor on traditional radial plain bearing axle 1, and
larger and
less, on the axle 1 of embodiment's bearing, friction factor is less.
Claims (5)
1. a novel energy-conserving radial plain bearing, is characterized in that: by axle with are formed bearing bush trepanning or coordinating of bearing saddle bore; Coated with sheet material on the bearing sleeve hole wall or bearing support hole wall of the inlet region of bearing convergence wedge shape hole; The central angle that on bearing hole wall, the region of applying coating is right is
,
span be:
; Surface treated bearing sleeve hole wall or bearing support hole wall and axle match, in the gap that bearing sleeve hole wall or bearing support hole wall and axle are formed, be full of lubricant oil; Dimensionless shear strength between lubricant oil and bearing hole wall coating
satisfy the following conditional expression:
（1）
Herein,
,
,
for the angular coordinates value of maximum oil film pressure position,
,
by the central angle that the surface of applying coating on bearing hole hole wall is right;
Dimensionless shear strength between lubricant oil and bearing hole wall coating
also must meet the following conditions:
（2）
Herein,
,
,
.
2. novel energy-conserving radial plain bearing as claimed in claim 1, is characterized in that: the coating on bearing lubrication inlet region bearing sleeve hole wall or bearing support hole wall is for hating oil coating.
3. novel energy-conserving radial plain bearing as claimed in claim 2, is characterized in that: the coating on bearing lubrication inlet region bearing sleeve hole wall or bearing support hole wall is fluororine-carbon coating.
4. the novel energy-conserving radial plain bearing as described in any one of claim 1-3, is characterized in that: the slenderness ratio L/D of this bearing is: L/D>0.2, L are the axial length of bearing, and D is the diameter of axle.
5. the novel energy-conserving radial plain bearing as described in any one of claim 1-3, is characterized in that: the operating conditions of bearing is
; Herein
for eccentricity,
,
e: the hole heart offset distance of axle center and bearing hole;
c: bearing play,
,
for the radius of bearing hole,
for the radius of axle.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410563019.7A CN104454980B (en) | 2014-10-22 | 2014-10-22 | Energy-saving radial sliding bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410563019.7A CN104454980B (en) | 2014-10-22 | 2014-10-22 | Energy-saving radial sliding bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104454980A true CN104454980A (en) | 2015-03-25 |
| CN104454980B CN104454980B (en) | 2017-04-12 |
Family
ID=52901544
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410563019.7A Active CN104454980B (en) | 2014-10-22 | 2014-10-22 | Energy-saving radial sliding bearing |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104454980B (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104791381A (en) * | 2015-04-27 | 2015-07-22 | 张永斌 | Concentric centripetal sliding bearing formed by using interface slippage |
| CN104948588A (en) * | 2015-05-26 | 2015-09-30 | 安徽不二越精工轴承有限公司 | Shaft sleeve capable of replacing speed reducer bearing |
| CN105465170A (en) * | 2015-12-11 | 2016-04-06 | 东方电气集团东方汽轮机有限公司 | Uniform load sliding bearing |
| CN107763065A (en) * | 2017-10-11 | 2018-03-06 | 袁虹娣 | The miniature ramp platform thrust slide bearing of small inclination |
| CN107869514A (en) * | 2017-11-21 | 2018-04-03 | 袁虹娣 | With the special-shaped fixed bush segment thrust slide bearing of physical absorption |
| CN107956791A (en) * | 2017-11-10 | 2018-04-24 | 袁虹娣 | The miniature ramp platform thrust slide bearing of uniform bearing surface small inclination |
| CN110030280A (en) * | 2019-04-03 | 2019-07-19 | 张美华 | It is a kind of to prevent the radial plain bearing that oil film slides at axis surface |
| CN110043568A (en) * | 2019-04-03 | 2019-07-23 | 张美华 | The antifriction energy-saving radial plain bearing of oil film sliding at a kind of bearing hole surface |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0246424A2 (en) * | 1986-05-21 | 1987-11-25 | Ford-Werke Aktiengesellschaft | Axial plain bearing for a radial thrust surface of a gear box shaft |
| CN87107378A (en) * | 1986-11-27 | 1988-06-15 | Bbc勃朗·勃威力有限公司 | Hydraulic radial sliding bearings feeding from pump |
| JPH06123313A (en) * | 1992-08-26 | 1994-05-06 | Mitsubishi Materials Corp | Oil-impregnated sintered bearing |
| JPH09229067A (en) * | 1993-12-28 | 1997-09-02 | Mitsubishi Materials Corp | Sintered oil impregnated bearing |
| WO2005003577A1 (en) * | 2003-07-05 | 2005-01-13 | Man B & W Diesel Aktiengesellschaft | Axial friction bearing |
| CN101684842A (en) * | 2009-05-15 | 2010-03-31 | 北京金业联和电机有限公司 | Aligning sliding bearing for efficient air valve of subway |
| CN203239761U (en) * | 2013-05-06 | 2013-10-16 | 浙江正盛轴瓦有限责任公司 | Novel seat-type sliding bearing |
| CN203627520U (en) * | 2013-12-09 | 2014-06-04 | 浙江大学 | Sliding bearing capable of generating distributed heat to achieve wedge-shaped dynamic-pressure lubrication |
-
2014
- 2014-10-22 CN CN201410563019.7A patent/CN104454980B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0246424A2 (en) * | 1986-05-21 | 1987-11-25 | Ford-Werke Aktiengesellschaft | Axial plain bearing for a radial thrust surface of a gear box shaft |
| CN87107378A (en) * | 1986-11-27 | 1988-06-15 | Bbc勃朗·勃威力有限公司 | Hydraulic radial sliding bearings feeding from pump |
| JPH06123313A (en) * | 1992-08-26 | 1994-05-06 | Mitsubishi Materials Corp | Oil-impregnated sintered bearing |
| JPH09229067A (en) * | 1993-12-28 | 1997-09-02 | Mitsubishi Materials Corp | Sintered oil impregnated bearing |
| WO2005003577A1 (en) * | 2003-07-05 | 2005-01-13 | Man B & W Diesel Aktiengesellschaft | Axial friction bearing |
| CN101684842A (en) * | 2009-05-15 | 2010-03-31 | 北京金业联和电机有限公司 | Aligning sliding bearing for efficient air valve of subway |
| CN203239761U (en) * | 2013-05-06 | 2013-10-16 | 浙江正盛轴瓦有限责任公司 | Novel seat-type sliding bearing |
| CN203627520U (en) * | 2013-12-09 | 2014-06-04 | 浙江大学 | Sliding bearing capable of generating distributed heat to achieve wedge-shaped dynamic-pressure lubrication |
Non-Patent Citations (1)
| Title |
|---|
| 谢春雨等: "TiN_TiSiN复合涂层的耐磨性能研究", 《石油矿场机械》 * |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104791381A (en) * | 2015-04-27 | 2015-07-22 | 张永斌 | Concentric centripetal sliding bearing formed by using interface slippage |
| CN104791381B (en) * | 2015-04-27 | 2017-10-31 | 张永斌 | The concentric radial plain bearing formed with interface sliding |
| CN104948588A (en) * | 2015-05-26 | 2015-09-30 | 安徽不二越精工轴承有限公司 | Shaft sleeve capable of replacing speed reducer bearing |
| CN105465170A (en) * | 2015-12-11 | 2016-04-06 | 东方电气集团东方汽轮机有限公司 | Uniform load sliding bearing |
| CN105465170B (en) * | 2015-12-11 | 2018-10-16 | 东方电气集团东方汽轮机有限公司 | One kind carrying sliding bearing |
| CN107763065A (en) * | 2017-10-11 | 2018-03-06 | 袁虹娣 | The miniature ramp platform thrust slide bearing of small inclination |
| CN107956791A (en) * | 2017-11-10 | 2018-04-24 | 袁虹娣 | The miniature ramp platform thrust slide bearing of uniform bearing surface small inclination |
| CN107869514A (en) * | 2017-11-21 | 2018-04-03 | 袁虹娣 | With the special-shaped fixed bush segment thrust slide bearing of physical absorption |
| CN110030280A (en) * | 2019-04-03 | 2019-07-19 | 张美华 | It is a kind of to prevent the radial plain bearing that oil film slides at axis surface |
| CN110043568A (en) * | 2019-04-03 | 2019-07-23 | 张美华 | The antifriction energy-saving radial plain bearing of oil film sliding at a kind of bearing hole surface |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104454980B (en) | 2017-04-12 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104454980A (en) | Novel energy-saving radial sliding bearing | |
| CN104791381B (en) | The concentric radial plain bearing formed with interface sliding | |
| CN102606618B (en) | Novel energy-saving tilting-pad thrust slide bearing | |
| CN104863971B (en) | Concentric micro centering slide bearing formed by physical absorption | |
| CN107228120A (en) | New energy-conservation ramp platform thrust slide bearing | |
| CN107061501A (en) | The miniature ladder bearing of abnormity | |
| Wang et al. | On the performance of dynamically loaded journal bearings lubricated with couple stress fluids | |
| CN108194498A (en) | With the special-shaped clinoplain fixed bush segment thrust slide bearing of interface sliding | |
| CN105247229A (en) | Sliding member | |
| CN110096784A (en) | A kind of quick calculating and design method of the bush(ing) bearing with axial pressure difference | |
| CN108194499A (en) | With the special-shaped ramp platform thrust slide bearing of interface sliding | |
| CN202867395U (en) | Low-friction high-frequency sound hydraulic cylinder | |
| CN107956791B (en) | Small-inclination-angle micro inclined plane platform thrust sliding bearing with uniform bearing surface | |
| CN105952797A (en) | Static-pressure spindle | |
| CN107869514A (en) | With the special-shaped fixed bush segment thrust slide bearing of physical absorption | |
| CN108488222A (en) | All there is the special-shaped clinoplain fixed bush segment thrust slide bearing of interface sliding at entire moving surface and at inlet region static surface | |
| CN205689605U (en) | A kind of magnetic lubrication sliding bearing | |
| CN110043568B (en) | Antifriction energy-saving centripetal sliding bearing with sliding oil film on surface of bearing hole | |
| CN109139699B (en) | Special-shaped inclined plane platform thrust sliding bearing with interface slippage at whole moving surface and inlet area static surface | |
| CN108006070B (en) | Small-inclination-angle miniature fixed tile thrust sliding bearing with uniform bearing surface | |
| CN108591246B (en) | Special-shaped stepped bearing applying interface sliding | |
| CN108591247A (en) | Prevent the ladder bearing that at two surface of inlet region and oil film slides at outlet area moving surface | |
| CN206054529U (en) | A kind of mixing channel water lubricated rubber bearing peculiar to vessel | |
| CN108916213A (en) | All there is the special-shaped clinoplain fixed bush segment thrust slide bearing of interface sliding at entire static surface | |
| CN109139700A (en) | All there is the special-shaped ramp platform thrust slide bearing of interface sliding at entire static surface |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20201214 Address after: 246121 Electronic Precision Machinery Industrial Park, Huaining Industrial Park, Anqing City, Anhui Province Patentee after: HUAINING JILILAI PRECISION MECHANICAL TECHNOLOGY Co.,Ltd. Address before: No.1 Gehu Road, HUTANG Town, Wujin City, Changzhou City, Jiangsu Province Patentee before: Zhang Yongbin |
|
| TR01 | Transfer of patent right |