CN1873244A - Roller thrust bearing - Google Patents
Roller thrust bearing Download PDFInfo
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- CN1873244A CN1873244A CN 200610074823 CN200610074823A CN1873244A CN 1873244 A CN1873244 A CN 1873244A CN 200610074823 CN200610074823 CN 200610074823 CN 200610074823 A CN200610074823 A CN 200610074823A CN 1873244 A CN1873244 A CN 1873244A
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Abstract
There is provided a roller thrust bearing providing reduced differential slip, free of significant friction and wear, and providing increased longevity against flaking. The present invention provides a thrust bearing in the form of a roller thrust bearing including at least two radially arranged rows of rollers and a cage holding the rollers, the rollers including at least one roller crowned.
Description
The application is for dividing an application, its female case be the application number submitted on September 26th, 2002 be 02143939.7, title is the application for a patent for invention of " roller thrust bearing ".
Technical field
The present invention relates generally to roller thrust bearing, roller thrust bearing comprises needle thrust bearing, relate in particular to and be arranged on car deceleration device (manually or automatically), transport feedway or be used for the thrust-bearing of rotating part of electrical assembly of the compressor etc. of motorcar air conditioner, these bearings are applied to thrust load on these rotating parts in order to supporting.
Background technique
With reference to Fig. 6 A and 6B, roller thrust bearing 1 comprises: the roller 2 of a plurality of circumference, radially equidistant arrangement; A bearing cage 3 that forms a plurality of rollers 2 of rotatable maintenance by circular ring; And outside and inner loop 4 and 5, these rings are clipped together as a roller bearing race, and thus at a plurality of rollers 2 of their opposite side upper support.External rings and inner loop 4 and 5 all are to be made of the circle that the sheet metal with enough hardness forms.External rings 4 has an annulus surface 6, and inner loop 5 has an annulus surface.
Roller thrust bearing is a kind of bearing with multiple advantage.For example, it simple in structure and higher load performance and higher rigidity can be provided.In addition, it also can be can't help above-mentioned roller bearing race and constitutes, but only is made of a bearing cage and roller.In this case, axle, case and so on object with a rolling contact surfaces corresponding with roller can have roughness, hardness or any similar function that can compare with the bearer ring surface, and use axle, case and so on can allow bearing to omit roller bearing race, can make bearing become more compact thus as ring surface.Specifically,, use the roller thrust bearing of needle roller or the height of needle roller thrust bearing to reduce, be applicable to the Machine Design of compact type thus as can be observed from sectional view.
A main application of needle roller thrust bearing (a kind of typical roller thrust bearing) is the compressor that is used for motorcar air conditioner.It comprises all kinds.For example, Fig. 7 shows the board-like compressor of a kind of diclinic, and one of them double-side inclined plate 9 is fixed in the input rotating shaft 8, thereby allows piston 10 reciprocating.Again for example, Fig. 8 shows the board-like compressor of a kind of monocline, and wherein a skew back plate 12 is fixed in the input rotating shaft 11, thereby allows piston 14 reciprocating by bar 13.Again for example, Fig. 9 shows a kind of board-like compressor of monocline of volume-variable, is fixed on to one of them swash plate 26 variable-angleization in the input rotating shaft 15, thereby allows piston 18 reciprocating by bar 17.All these types all have a rotating part in conjunction with roller bearing.
Be pointed out that the compressor of Fig. 7-9 needn't necessarily belong to the conventional art field.They should be considered to a kind of like this device, that is, this device for example can also further be improved in the future by the further developing of roller thrust bearing by the present invention's design.In other words, the device that need be modified such as their structures, material of being a kind of its internal component.
In common bearing, as in ball bearing, differential can take place within rolling element and roller bearing race slide.The differential of this bearing the poor of circumferencial direction speed in the contact surface that depends primarily on rolling element and roller bearing race that slide.More particularly, ball bearing provides a contact, and a very little area of contact is provided thus.Like this, in contact surface, the difference of their circumferencial direction speed is very little, so their differential slides also very little.
On the contrary, in roller thrust bearing, its main structure is, the rolling element of cylindrical rollers shape is set on the roller bearing race with smooth ring surface, roller contacts mutually along a straight line with roller bearing race, and the rotating center of the center of rotation of bearing and roller is complementary.In this case, circumferencial direction speed on the rolling contact surfaces of roller is same speed, and as radially outwards viewed, along with rotation, the circumferencial direction speed of the roller bearing race that contacts with roller can increase (being directly proportional with the radius of gyration of roller bearing race) along the direction of leaving the bearing center of rotation.Therefore, the difference of roller and roller bearing race circumferencial direction speed is maximum at the opposed end place of roller.In theory, only on the pitch circle of bearing, have nonslipping rotation.From the pitch circle of roller a bit towards opposed end of roller, the difference of the circumferencial direction speed between roller and the roller bearing race increases with the length of roller with being directly proportional, thus differential slip increase.
As mentioned above, the bearing of other type of differential slip ratio of roller thrust bearing inside is big.So disadvantageously, the differential of roller and roller bearing race slides and will produce stress at the edge of the roller between roller bearing race and the roller, and these stress will make the roller edge and the operation of the roller bearing race that begins from the surface of ring is partly peeled off.
Generally, above-mentioned shortcoming can solve by the bearing that roller length reduces, and reduces the relatively slidably property of roller end surface, perhaps solves by having the roller bearing that two rows' (promptly arrange) are arranged in each bag portion of bearing cage more.In addition, harmful stress on the roller end or load for example also can solve (Japan Patent is No.9-14131 openly) by the roller that use has a camber.
Roller thrust bearing is had a requirement, that is, size need reduce, to save energy and space and to make weight reduce (frictional loss is reduced).Therefore, according to bearing capacity, the bearing in actual the use can run into a kind of especially exacting terms.As mentioned above, in roller thrust bearing, the differential slip between roller and the roller bearing surface can increase frictional loss and the loss that is caused by contact surface.In addition, the contact surface oil film is shaped can be impaired, and be easy to cause the edge stress between roller bearing race and the roller itself at the roller edge, and this will make the edge of the rolling machinery of the roller bearing race that begins from the surface peel off.Can reduce differential simply by the length that reduces roller slides.Yet this will make the area of contact of roller reduce, thereby contact pressure is increased.It is impaired in the increase of the contact pressure at contact surface place oil film to be shaped thus, and the disadvantageous situations such as come off (peeling off) that for example has at roller radially-outer surface place takes place.
The inside of the bearing that compressor uses has the bearing lubricant that mixes with refrigerant.In addition, along with the contraction and the expansion of compressor, oiling agent can liquefy and vaporize repeatedly.So disadvantageously, the amount of oiling agent can reduce.Like this, formed oil film can be even worse when using conventional machinery operation oiling agent, and bearing peels off can take place than expection more Zao.
In addition, in order to solve global warming and other similar environmental problem, the compressor of air conditioner uses HCFC 134a or other similar freon (flon) substitute as refrigerant.Compare with the refrigerant that tradition is used, the greasy property of these freon substitutes itself is considered to poorer.Along with the dissolving and the consequent mixing of this freon substitute, for example, the kinetic viscosity of oiling agent can reduce, and the oil film shaping of bearing can be subjected to serious damage.Like this, the rolling element that bearing has, roller bearing race etc. can peel off, wear and tear or make the surface that similar damage is arranged, thereby cause shorten working life.
This can solve by improving oiling agent.Yet because the chemical property of oiling agent and refrigerant, oiling agent only can be selected from limited scope, therefore can not expect that the ability of the formation of oil film increases significantly.The amount that increases oiling agent in refrigerant improves the amount that greasy property can reduce refrigerant, influences the cooling capacity of compressor thus.
When needle roller thrust bearing uses in cooler compressor, needle roller thrust bearing will receive the thrust load with respect to the center of rotation biasing, and show the speed fast rotational that is not less than 8000rpm at least greatly.Such rotational velocity and load also are some more strict conditions, and it can increase such shortcoming, promptly cause to produce the bearing surface damage that differential slides.
Summary of the invention
In sum, the present invention proposes a kind of roller thrust bearing, this bearing can reduce differential and slide, do not have tangible friction and wear, and good spalling resistance energy can be provided.
The invention provides a kind of roller thrust bearing, this bearing comprises the roller of at least two row's arranged radiallys and the bearing cage of a maintenance roller, and these rollers comprise a roller that has camber at least.
Many row's rollers can reduce differential effectively and slide.In addition, the roller that has camber can make effective length reduce, and slides thereby synergy reduces differential effectively.In addition, the geometrical shape that has camber can extenuated the load that causes in edge with imitating.Similarly, the bearing moment of torsion also can reduce.
In addition, preferably, bearing cage has a bag portion, and each bag portion can keep a single roller, thereby can firmly keep roller to prevent that roller is crooked.In addition, the crooked friction torque of roller also can be reduced.
In addition, the camber that roller has among radial outside one row can specific diameter little to the interior row.Like this, the roller of radial outside can have and bigger reduces pressure of contact surface imitating length, prevents that thus the roller bearing race of the radial outside of radial outside roller and radial outside roller from peeling off.
In addition, at least one row who is in radially interior row's radial outside preferably forms by directly rolling.And the camber that the roller of radial outside has can be littler than the roller of radially inner side, as mentioned above, directly rolling of radial outside can have bigger effective length similarly, thereby reduce pressure of contact surface, prevent that thus the roller bearing race of the radial outside of radial outside roller and radial outside roller from peeling off.
In addition, at least one row who is in radially interior row's radial outside can be formed to the most inboard bigger roller by the length specific diameter, thereby reduce the slide relative of radially inner side roller, and increase the bearing capacity of radial outside roller, thereby the roller bearing race that prevents the radial outside of radial outside roller and radial outside roller peels off.
In addition, roller can have at least one ball-shaped end surface, thereby prevents the tangible phase mutual interference of roller end surface, and prevents the tangible mutual interference mutually of bag portion of roller end surface and bearing cage, thereby it is crooked to reduce roller.In addition, can also reduce the friction torque that makes roller crooked.
In addition, the roller that has of at least one row that is in radially interior row's radial outside is can specific diameter few to interior row, in order to the bearing capacity of increase radial outside roller, thereby the roller bearing race that prevents the radial outside of radial outside roller and radial outside roller peels off.
In addition, roller can be needle roller, and the bearing that has needle roller also can have effect similar to the above.
Above-mentioned roller thrust bearing can be installed in the compressor and use.In compressor, require to save the space and exist oiling agent to comprise a kind of so specific situation of refrigerant, as mentioned above, the oil film of roller thrust bearing is shaped can not be subjected to serious damage.
The invention provides another kind of roller thrust bearing, this bearing comprises the roller and a roller bearing race that contacts with roller that have camber, and the carbide that the roller bearing race roller bearing race contains is no less than 10000/mm
2, but be less than 40000/mm
2, the degree of depth that begins to record from the ring surface layer is at least 0.1mm, and the diameter of particle is not less than 0.6 μ m.
The roller that has camber can be eliminated the differential slip of edge, thereby load is reduced.In roller bearing race, carbide can be used to resistance to deformation to improve the intensity of surface layer material.In addition, have one and can produce hot surface, can prevent plastic flow if produce situation such as differential slips, poor lubrication and roller bearing race between roller and the roller bearing race.
In roller bearing race, at least at surface layer to degree of depth 0.1mm place, can the precipitation particles size be 0.6 μ m or bigger carbide, per like this 1 square millimeter of unit area can exist 10000 or more such particle, thereby makes carbide be used for resisting the plastic deformation of surface layer.In order to obtain the opposing effect of higher level, be precipitated into to be no less than 14000/mm
2Be desirable.Greater than 40000/mm
2Can reduce to peel off resistivity.Being pointed out that, is not spherical as carbide, and grain size is the average particle size about direction.
As mentioned above, the density of the carbide of the surface layer of roller bearing race for example can followingly obtain: the SCM415 material is processed.For carburization, can be arranged on 890 ℃ and continue one hour, and the interior environmental conditions that is set to have in the stove has 1.5 to 2.0% carburizing ability.For quenching, can be arranged on 840 ℃ and continue 0.5 hour, stove is set to its interior environmental conditions that has and has 1.0 to 2.0% carburizing ability.After this, material is carried out oil quench, to realize above-mentioned density.Remove after the steel for carburizing, the present invention can be applicable to other steel, as Bearing Steel, carbon steel etc.
Can use electron microscope to duplicate and measure this density with the observation of the observation of direct, film, a kind of extraction replica or a kind of two stages, perhaps it can polish with observation by a kind of scanning electron microscope, etched sample surface comes density measurement.
The roller that has a camber can be eliminated the differential that causes in edge and slide, and reduces load, can mainly improve the performance of plasticity_resistant deformation and have to add to the roller bearing race of the above-mentioned carbide that adds surface layer.The roller and having that will have a camber wherein has the conspire roller bearing race of surface layer of carbide of height and combines the ability of significant anti-surfacial spalling can be provided, and this ability has obviously surpassed by common needle roller thrust bearing is provided with these requirements separately and it is added the effect that can reach together.In other words, the resistivity of surfacial spalling can strengthen by the synergy of the highdensity carbide in roller that has camber and the surface layer that is distributed in roller bearing race.In addition, in roller bearing race, roller etc., can reduce wear-resisting property significantly.
Above-mentioned another kind of roller thrust bearing can comprise at least two row's rollers, and two row's rollers comprise a roller that has camber at least.
Many row's rollers slide differential and are dispersed into little numerous rows.In addition, the roller that has a camber can make the load at edge reduce.As a result, the working life of anti-surfacial spalling can significant prolongation.In addition, friction torque also can reduce, and so for example just can make the air conditioner running of automobile with less power cost.
At least be not less than per unit area 0.8% to the abundance of the carbide precipitation of 0.1mm degree of depth place roller bearing race at surface layer less than 10% scope.
This both can improve the wear-resistant ability of roller bearing race, can improve anti-working life of peeling off again.For example, carbide that can the above-mentioned area percentage of following acquisition: processing SCM415 material.For carburization, can be set to 890 ℃ and continue one hour, and the interior environmental conditions that is set to have in the stove has 1.5 to 2.0% carburizing ability.For quenching, can be arranged on 840 ℃ and continue 0.5 hour, stove is set to its interior environmental conditions that has and has 1.0 to 2.0% carburizing ability.After this, material is carried out oil quench, thereby realize above-mentioned density.Except that the steel for carburizing of SCM415, the present invention also can be applicable to other steel, as Bearing Steel, and carbon steel etc.
Preferably, above-mentioned bearing has two row's rollers at least, and wherein the camber that has of radial outside one row is less than the camber of penetralia one side radially, or do not have camber.
The less roller camber of camber can not reduce the rolling contact section branch significantly, and like this, the bearing capacity of radial outside roller can be improved, and the load contact pressure of each radial outside roller can reduce.Like this, radial outside roller and the roller bearing race that rotates and move along with the radial outside roller can be in order to avoid peel off.
Bearing can have the bearing cage of a maintenance roller, and bearing cage has a bag portion, and this bag portion is used to hold many two rollers that axial direction radially extends.
Therefore, this bearing cage is configured to and can processes at low cost, and can reduce the skewness of each roller.
In addition, bearing can have the bearing cage of a maintenance roller, and bearing cage has at least two row's bag portions, and each bag portion holds a single roller.
Can reduce the crooked of roller that the supporting owing to bearing cage produces like this.In addition, it can also reduce friction torque, and for example, if this bearing is used for the tilted-plate compressor of motorcar air conditioner, this kind bearing can make air conditioner operate with lower power cost.
In addition, bearing can abovely have at least two row's rollers, wherein radially effluxes the roller length that has and is not less than inwardly row's roller of footpath.
The roller of radially inner side can not have significant differential to slide, and compares with the radially inner side roller, the roller of radial outside can have bigger rolling contact section branch, thereby the bearing capacity that has increased is provided.
Roller can have the outwards outstanding end surface of a curve.
Above-mentioned geometrical shape can prevent the end surface phase mutual interference of roller, and roller end surface and the mutual interference mutually of bearing hood bag portion.It can also reduce the crooked and friction torque of roller.
Above-mentioned roller thrust bearing can have at least two row's rollers, and wherein, the roller quantity that radial outside one row has is no less than radially inner side one row's roller quantity.
Can increase the bearing capacity of radial outside roller like this.
The surperficial Ge Shi hardness (HRC) that roller bearing race has can be not less than 58.
Roller bearing race with above-mentioned hardness can reduce to roll and the turn round plasticity flow velocity of edge section of track makes this flow velocity less than the straight roller bearing ring, and can improve wear-resisting property.For the situation of hardness less than HRC 58, wear-resisting property can not be significantly improved, and it is big to equating with the wear-resisting property of straight roller bearing ring.
According to the present invention, a kind of swash plate compressor has one and fixes and rotate about it so that the swash plate of reciprocating motion of the pistons with main shaft, in this compressor, part place at the contact swash plate is provided with a roller thrust bearing, in order to receive the thrust load when main shaft rotates and piston reciprocally produces.Bearing comprise a roller that has a camber with one with the roller bearing race that contacts, the carbide that roller bearing race contains is not less than 10000/mm
2, but less than 40000/mm
2, it is at least 0.1mm from the degree of depth that the ring surface layer begins to record, and the diameter of particle is not less than 0.6 μ m.
In contact the roller thrust bearing that is provided with swash plate, between roller bearing race and roller, can produce differential and slide.This differential slip meeting causes the lubrication of negative effect and infringement oiling agent to the shaping of contact sea surface oil slick.In addition, for example for the roller thrust bearing of the swash plate compressor that is used for motorcar air conditioner, as mentioned above, oiling agent as have an attenuation in the use of refrigerant of air conditioner.This will further damage greasy property.Thereby rolling contact surfaces produces heat, and the surface is easy to peel off or produces similar infringement.Yet, to have the roller of camber and the rolling bearing rings of the surface layer with high density distribution carbide wherein combines, even for the refrigerant and the mix lubricant lubrication circumstances together of motorcar air conditioner, also can provide a kind of performance of very good anti-surfacial spalling.The performance of this anti-surfacial spalling can obtain obviously improved, synergistic effect, and this effect has obviously surpassed will set up separately to state and requires to be provided with the effect that effect that roller, roller bearing race etc. are produced adds together to be reached.
Above-mentioned and other purpose, feature, aspect and advantage of the present invention will be from following to obtaining the detailed description of the present invention in conjunction with the accompanying drawings apparently.
Description of drawings
Figure 1A shows a kind of roller of the roller thrust bearing of one embodiment of the invention;
Figure 1B shows the another kind of roller of the roller thrust bearing of one embodiment of the invention;
Fig. 1 C shows roller one with the roller of Figure 1A and/or Figure 1B and coexists and use another kind of roller in the roller thrust bearing of one embodiment of the invention;
Fig. 2 A is the planimetric map of upper half part of a roller thrust bearing of one embodiment of the invention (first embodiment);
Fig. 2 B is the planimetric map of upper half part of another roller thrust bearing of one embodiment of the invention (first embodiment);
Fig. 2 C is the planimetric map of upper half part of the another roller thrust bearing of one embodiment of the invention (first embodiment);
Fig. 3 A is the planimetric map of the needle bearing of one embodiment of the invention, wherein has a resin molded bearing cage (second embodiment);
Fig. 3 B is the amplification diagrammatic sketch (second embodiment) of the part A of Fig. 3 A;
Fig. 4 A is the planimetric map of the needle roller thrust bearing of one embodiment of the invention, wherein has a bearing cage box-like, that iron plate is pressed into (second embodiment);
Fig. 4 B is the sectional view (second embodiment) along the IVB-IVB line intercepting of Fig. 4 A;
Fig. 4 C is the amplification diagrammatic sketch (second embodiment) of the groove of Fig. 4;
Fig. 5 A is the longitudinal section of the needle roller thrust bearing of third embodiment of the invention;
Fig. 5 B is the planimetric map of upper half part of roller among Fig. 5 A and bearing cage;
Fig. 6 A is the longitudinal section of common needle roller thrust bearing;
Fig. 6 B is the planimetric map of upper half part of the roller of Fig. 6 A and bearing cage;
The longitudinal section of the board-like compressor of diclinic that Fig. 7 uses for air conditioner;
The longitudinal section of the board-like compressor of monocline that Fig. 8 uses for air conditioner;
Fig. 9 is used for longitudinal section volume-variable, the board-like compressor of monocline for air conditioner.
Embodiment
Shown in Fig. 6 A-8, the present invention provides a kind of needle roller thrust bearing in one embodiment, and this bearing is used in combination in the rotating part of the regulation of the compressor of motorcar air conditioner.Specifically, for example board-like for the diclinic of Fig. 7, can use the needle bearing and the needle roller thrust bearing 20 that have bearing cage 19.Monocline for Fig. 8 is board-like, can use axle sleeve type needle bearing 21 and needle roller thrust bearing 22.For the volume-variable of Fig. 9, monocline is board-like, can use the needle bearing and the needle roller thrust bearing 24 that have bearing cage 23.Needle roller thrust bearing has highly little advantage (as seeing in the sectional view), and therefore, it is specially adapted to need to save in the compressor in space.
As mentioned above, the compressor of the motorcar air conditioner of Fig. 7-9 should be considered to can further be able to improved a kind of device from now on, for example can be improved by the further developing of roller thrust bearing of being disclosed by the present invention.In other words, their structures, material of being a kind of its internal component etc. can further improved device.
(1) geometrical shape of roller.
Figure 1A shows the roller 2a that has camber 25.The length of roller 2a is L, and the length that has an opposed end of camber is L1.The roller that has a camber can reduce the load (or reducing edge stress) on the edge, and effective length reduces the roller of (straight portion is divided into L2) and can reduce differential and slide.
Figure 1B shows the roller of the blunt circle in a kind of opposed end surface.This structure can reduce owing to contacting the edge stress that causes between the roller end face in the internal surface of the bag portion of bearing cage and the bag facial planes, prevent the end face phase mutual interference of roller, and prevent the bag portion mutual interference mutually of roller end face and bearing cage, it is crooked to reduce roller thus.In addition, also can reduce the friction torque that produces because of roller is crooked.Above-mentioned circular geometry size is generally roller diameter Da's ± and 50%.
Opposite with Figure 1A, Fig. 1 C shows a kind of roller that does not have camber, promptly a kind of straight roller.This roller that does not have camber can make straight portion branch length increase.Especially under the situation of rolling that does not have to tilt and running surface, can reduce the pressure of contact surface.Be pointed out that in the present invention, straight roller is set among at least one row of interior row's radial outside.These rollers are that the Bearing Steel of HRC 60 to 65 is made by surface hardness normally.
(2) setting of roller
Fig. 2 A is respectively half planimetric map of employed roller thrust bearing in the first embodiment of the present invention that hereinafter will describe to 2C.Fig. 2 A shows a kind of roller thrust bearing, and this bearing has a bearing cage with single bag portion, and the opposed end of each bag portion can hold and have camber, and radially line up two rows' roller 2a.As hereinafter describing, this structure is used among first and second embodiments as example sample 4 of the present invention.Fig. 2 B shows a kind of roller thrust bearing, and this bearing has a bearing cage with two row's bag portions, and each bag portion will keep a single roller that has camber.This structure is used in the second embodiment of the present invention, as example sample 5 of the present invention.Fig. 2 C shows a kind of roller thrust bearing, and the quantity of the roller of wherein at least one row's radially outer equates or be more with the quantity of inner most roller radially.Can increase the bearing capacity of radially outer roller like this, make it greater than the bearing capacity of penetralia roller radially.This structure is used among second embodiment as example sample 10 of the present invention.
(3) bearing cage
Fig. 3 A-3C and 4A-4C show the bearing cage of one embodiment of the invention.Fig. 3 A-3C shows with being a kind of form (sample 4) in the second embodiment of the present invention.It has used resin molded bearing cage and the needle roller that forms by injection moulding.In this form, the bearing 3 of injection moulding is provided with one and has the more complicated bag portion of geometrical shape.Shown in Fig. 3 B, each bag portion can keep two (or two rows) rollers, and has a protuberance in its centre, to prevent the roller skew.Shown in Fig. 3 C, this protuberance allows bearing cage 3 to keep roller 2.
Fig. 4 A-4C shows second embodiment's another kind of form, and this embodiment has used a bearing cage and a needle roller by a box-like iron plate press forming.This form is identical with the form shown in Fig. 3 A-3C, and also corresponding with sample 4.The bearing cage of this form can be shaped by the low cost compacting.Shown in Fig. 4 C, two member 3a and 3b by the iron plate press forming are clamped in two rollers 2 in the bag portion, are assembled into the form of a box thus.Be pointed out that the width of bag portion is littler than the diameter of roller 2, like this, bearing cage 3 can maintain roller 2.
If the diameter of the roller that the roller thrust bearing of Fig. 3 A-3C and 4A-4C uses is L as Da length, preferably can stipulate Da≤5mm and 1≤L/Da≤10.More particularly, for L/Da≤1, then roller length reduces, and effective length reduces thus.The area of contact of roller reduces, and can make pressure of contact surface increase thus.In contact surface, contact pressure increases, and it is impaired that this will cause oil film to be shaped, and disadvantageously, for example the radial outer surface at roller will have the spalling phenomenon generation.
For 10≤L/Da, roller length increases, and then therefore the slip of the differential of effective length and roller and ring surface increases.In roller edge, be easy to cause the edge stress between roller bearing race and the roller itself, so disadvantageously, the rolling of the roller bearing race that begins from the surface and the edge of machinery are peeled off.
First embodiment
Use above-mentioned roller thrust bearing to carry out a life test, to prove that roller thrust bearing of the present invention can make the differential of the end face of roller slide and reduce, make near concentrated the reducing of stress of roller end, and can reduce the frictional loss and the wearing and tearing of bearing inside, thereby the life-span of rolling and machinery anti-strip is increased.
The roller diameter that tested bearing has is 3mm, and the internal diameter of the roller bearing race that it has is 65mm and external diameter is 85mm.Test is to carry out under 60-80 ℃ temperature, and load is 1000kgf, and speed is 500rpm, and the lubricant oil that bearing is coated with is main shaft oil VG2 (oil film parameter, microlitre (1ambda): 0.101).
Table 1 shows the result of test, and it is the needle roller thrust bearing with standard roller and standard rolling bearing cover that comparative example is wherein arranged.Life-span is by 10% expression in 10 test bearing life-spans.Be pointed out that for single, the length that roller has is 7.8mm, for two rows, the length that roller has is 3.8mm, and it has camber (or decline) at 5 to 15 microns.Time when peeled off by any member of tested bearing working life is determined.
As can be seen from Table 1, if be 1 the working life that comparative example sample 1 (a kind of standard rolling bearing) has, and be 2.5 times of sample 1 working life that the sample 2 with two row's rollers has, and be 4.9 times of sample 1 working life with sample 3 of the roller (single) that has certain camber, to have working lifes of sample 4 that two rows have a roller of certain camber are 7.5 times of sample 1 and by provided by the present invention, its working life is obviously than sample 1 and 2 length, as observable from test, its roller does not peel off fully.In addition, in test, be 3.9A to the minimum current of sample 4 motor consumption, this shows, this kind bearing is low moment of torsion, is understandable that the frictional loss of bearing inside is reduced.
Obviously, have roller thrust bearing that two row or multi-row have a roller of certain camber can reduce friction effectively loss and loss, increased the working life of peeling off at that opposing begins from the surface, rolling and running orbit edge, and can prevent that the radially-outer surface of roller from peeling off.
Table 1
| Classification | Catalogue number(Cat.No.) | The roller specification | Working life test result | ||||||
| The estimation in working life | Have or not the position of peeling off or peeling off | Moment of torsion | |||||||
| Geometrical shape: have camber/straight | Row's number of | 10% working life (h) | The ratio in 10% working life | Interior roller bearing race | Roller | Motor current draw (A) | |||
| Comparative example | 1 | Straight | 1 | 11 | 1 | The edge of internal | Outer surface | 7 | |
| Comparative example | 2 | | 2 | 28 | 2.5 | Inwardly arrange adjacent part with the footpath | The footpath is the outer surface of roller outwards | 4.3 | |
| Comparative example | 3 | Have camber | 1 | 54 | 4.9 | The edge of internal surface | Do not have | 5.7 | |
| Example of the | 4 | | 2 | 83 | 7.5 | Inwardly arrange adjacent part with the footpath | Do not have | 3.9 | |
Second embodiment
In test, two rows of use have the roller effective length of camber and the geometrical shape of their ends has been done change.The result that test shown in the table 2 obtains.The bag portion arranged radially that has becomes a bearing cage (sample 5) of two row or multi-row can prevent the mutual interference of roller phase, strengthen the ability that bearing cage keeps roller, reduce the crooked of roller, make frictional loss and loss reduce, thereby increased anti-working life of peeling off, and accessible ratio is 1.5 of 10% working life.
Can it is evident that from the result of test, for the footpath inwardly row's roller have camber and radially efflux the little two row or multi-row roller (sample 6) of row's roller in the camber ratio of roller, and for radially effluxing the two row or multi-row roller (sample 7) that roller is only formed by straight roller, compare with the roller of radially inner side, the pressure of contact surface of radial outside roller reduces, can stop the radial outside of roller radially-outer surface and roller bearing race to peel off like this, thereby the life-span is prolonged.
Inwardly arrange the increase of roller length and radially efflux a kind of like this roller (sample 8 that roller length specific diameter is inwardly arranged roller length weak point for the footpath, two parallelisms with other embodiment, shorter and the outside roller of inner roller is longer), inwardly arranging roller with the footpath compares, the bearing capacity that radially effluxes roller increases, thereby the radial outside that has prevented roller radially-outer surface and roller bearing race peels off, and reduced the footpath inwardly the differential of roller slide, and significantly increase (ratio be 10% working life 1.5) working life.Test structure shows, the quantity of the roller of radial outside circumference (or bag portion) is set to equate with the quantity of the roller of radially inner side or more bearer caps of the roller that radially effluxes that also can make increase (Fig. 2 C).
In addition, the roller (sample 9 and 10) with spherical surface can prevent the bearing hood bag portion phase mutual interference of mutual interference and roller end face mutually of the end face of roller own, makes thus and significantly increases working life (ratio be 10% working life 1.3 to 1.6).Because motor institute consumed current is littler than sample 4 and 5, so they equally also are effective for the moment of torsion that reduces crooked friction of roller and bearing.In addition, in sample 4-10 of the present invention, the electric energy that motor consumed trends towards frequently little than in the example, and this shows that bearing internal friction loss is less, and the moment of torsion of bearing is reduced.
Table 2
| Classification | Catalogue number(Cat.No.) | The roller specification | Row's number of the bag portion of bearing cage | The result of test in working life | ||||||||
| The radially inner side roller | The radial outside roller | The geometrical shape of end surface | Ratio in 10% life-span | Have or not the position of peeling off or peeling off | Moment of torsion | |||||||
| The length of roller (ratio) | Geometrical shape: have camber/straight | The length of roller (ratio) | Geometrical shape: have camber/straight | Radially inner side | Radial outside | The consumption of motor current (A) | ||||||
| Example of the | 4 | 1 | Have camber | 1 | Have camber | Straight | 1 | 1 | The edge of internal surface | Do not have | 3.9 | |
| Example of the | 5 | 1 | Have camber | 1 | | Straight | 2 | 1.5 | The edge of internal surface | Do not have | 3.3 | |
| Example of the present invention | 6 | 1 | Have camber | 1 | Camber is less | Straight | 1 | 1 | The edge of internal surface | Do not have | 4.1 | |
| Example of the | 7 | 1 | Have camber | 1 | Straight | Straight | 1 | 1 | The edge of internal surface | Do not have | 4.3 | |
| Example of the | 8 | 1 | Have camber | 1.2 | Have camber | Straight | 1 | 1.7 | The edge of internal surface | Do not have | 3.4 | |
| Example of the | 9 | 1 | Have camber | 1 | Have camber | Spherical | 1 | 1.3 | The edge of internal surface | Do not have | 3.5 | |
The 3rd embodiment
Shown in Fig. 5 A and Fig. 5 B, use a kind of like this needle roller thrust bearing to carry out a test, its middle (center) bearing is by roller bearing race 4 and 5, is arranged on rolling element (or roller) 2 and the maintenance between the roller bearing race and guides the bearing cage 3 of rolling element 2 to form.Rolling element wherein is the rolling element that has certain camber.Rolling contact surfaces 6 is formed between the roller 2 of roller bearing race 4,5.Needle roller thrust bearing has roller bearing race, rolling element and the bearing cage of formation as shown in table 3.
Table 3
| Catalogue number(Cat.No.) | The specification of roller bearing race | The specification of | 10% working life | Ratio in 10% working life | Peel off part | Motor current draw (A) | ||||
| Unit area (mm 2) the quantity of carbide | The carbide of unit area | The geometrical shape of roller | The quantity of roller | Roller bearing race | Roller | |||||
| 31 | 6540 | 0.5 | Straight | 1 | 11 | 1 | The edge of internal | Outer surface | 7 | |
| 32 | 6540 | 0.5 | Straight | 2 rows | 28 | 2.5 | Inwardly arrange adjacent part with the footpath | The outer surface of radial outside roller | 4.3 | |
| 33 | 6540 | 0.5 | Have camber | 1 row | 54 | 4.9 | The edge of internal surface | Do not have | 5.7 | |
| 34 | 6540 | 0.5 | Have | 2 rows | 83 | 7.5 | Inwardly arrange adjacent part with the footpath | Do not have | 3.9 | |
| 35 | 39452 | 9.64 | Have | 2 rows | 227 | 20.6 | Inwardly arrange adjacent part with the footpath | Do not have | 3.9 | |
As shown in table 3, desired condition of the present invention is, (a1) the carbide density of roller bearing race and the area percentage of carbide, (a2) single roller and arrange difference between the roller more, and (a3) geometrical shape of roller (having or do not have camber), changing a condition in these necessary conditions when testing, is how to influence anti-working life of peeling off thereby observe above-mentioned condition.More particularly, the present inventor thinks, set above-mentioned condition within the scope of the invention, the end surface that roller has can not have tangible differential to slide and significant stress is concentrated, like this, after roller rolled and moves, frictional loss and loss were reduced, and the edge of bearer ring can have long anti-working life of peeling off, and the present inventor has proved its effect.
Working life, test was to use a kind of like this bearing to carry out, and the diameter of its roller tool is that internal diameter that 3mm, bearing race have is 65mm and external diameter is 85mm.Survey is carried out under 60-80 ℃ temperature, and load is 1000kgf, and speed is 500rpm, and the lubricant oil that bearing is coated with is main shaft oil VG2 (oil film parameter (microlitre): 0.101).Table 3 has provided the result of this test, and one of them comparative example is a needle roller thrust bearing with a standard roller and a standard rolling bearing cover.
In table 3, working life is by 10% expression in the working life of 10 test bearing.Be pointed out that for single, the length that roller has is 7.8mm, for two rows, the length that roller has is 3.8mm, and the camber that it has (or decline) is at 5 to 15 microns.
As shown in table 3, if with working life of standard rolling bearing respective sample 31 be 1, are 2.5 times of sample 31 working lifes that then have the sample 32 of two row's rollers.In addition, be 4.9 times of sample 31 working life with sample 33 of the single roller that has a camber.Have working lifes of sample 34 that two rows have a roller of camber and are 7.5 times of sample 31.Sample 31-34 is comparative example, and the density or the distributed areas percentage of the carbide that their bearer ring surface comprises do not drop in the scope of the present invention.
Compare with above-mentioned comparative example, remaining on the row of two in the bearing cage has the roller of camber and contains the density of carbide and distributed areas percentage falls into roller bearing race in the scope of the invention, be working life that the sample 35 of the present invention's one example has to be 20.6 times of sample 31, obviously long than sample 32-34, the roller of this sample 35 can not peel off fully.In addition, in test, sample 35 motor have consumed minimum electric current 3.9A, and this numerical value equates with sample 34, and littler than other sample, and its expression frictional loss is very little equally.
Can find from The above results, have that two row or multi-row of the present invention remain on roller in the bearing cage and the needle roller thrust bearing of a roller bearing race can reduce frictional loss and loss effectively, thereby obviously increased working life, prevent that those edges that begin from the surface peel off after roller rotation and operation, and prevent the surfacial spalling of roller radial outside.
Roller that has camber and the roller bearing race with a surface layer are combined with the highdensity carbide that is distributed in wherein, remarkable anti-surfacial spalling ability can be provided, and this ability is considerably beyond in the common needle roller thrust bearing effect that these conditions then can reach their additions being set by independent.In other words, the ability of anti-surfacial spalling can be significantly improved by a kind of roller that has a camber and the synergy that is combined in the high density carbides in the surface layer of roller bearing race.
The 4th embodiment
On the 4th embodiment's needle roller thrust bearing, test, the roller that has certain camber and a roller bearing race that this bearing has used two row's bearing cages to keep, wherein roller length changes, and its geometrical shape with an end surface also changes.As shown in table 4, the condition of the present invention that is detected is that (b1) whether the length of the radial outside roller of two row's rollers (b2) has camber, (b3) structure of the bag portion of bearing cage, and (b4) geometrical shape of roller end surface to the influence in anti-working life of peeling off.
Table 4
| Catalogue number(Cat.No.) | Roller bearing race | The radially inner side roller | The radial outside roller | The geometrical shape of roller end surface | The quantity of bearing hood bag portion | Ratio in 10% working life | Peel off part | Motor current draw (A) | |||
| The ratio of length | Whether there is camber | The ratio of length | Whether there is camber | Radially inner side | Radial outside | ||||||
| 35 | The roller bearing race of example of the present invention | 1 | There is standard | 1 | There is standard | Straight | 1 | 1 | The edge of internal surface | Do not have | 3.9 |
| 36 | 1 | There is standard | 1 | There is | Straight | 2 | 1.5 | The edge of internal surface | Do not have | 3.3 | |
| 37 | 1 | There is standard | 1 | Exist, less | Straight | 1 | 1 | The edge of internal surface | Do not have | 4.1 | |
| 38 | 1 | There is standard | 1 | There is standard | Straight | 1 | 1 | The edge of internal surface | Do not have | 4.3 | |
| 39 | 1 | There is standard | 1.2 | There is standard | Straight | 1 | 1.7 | The edge of internal surface | Do not have | 3.4 | |
| 40 | 1 | There is standard | 1 | There is standard | R | 1 | 1.3 | The edge of internal surface | Do not have | 3.5 | |
| 41 | 1 | There is standard | 1 | There is | R | 2 | 1.6 | The edge of internal surface | Do not have | 3.2 | |
Fig. 2 A shows the needle roller thrust bearing of sample 35.Fig. 2 A is a planimetric map of having removed the top roller bearing race, and Fig. 2 B is the sectional view of Fig. 2 C.Sample 35 is provided with one single bag of portion, and each bag portion can hold the roller of two axial direction arranged radiallys.
Fig. 2 B shows the needle roller thrust bearing of sample 36.Fig. 2 A is a planimetric map of having removed the top roller bearing race, and Fig. 2 B is the sectional view of Fig. 2 A.According to table 4, the samples 36 that have the bearing cage with two row bag portions are further kept roller by bearing cage, thereby reduce crooked, the frictional loss and the loss of roller, and therefore, be 1.5 times of sample 35 the anti-working life of peeling off that makes sample 36.
As set in the sample 37, the above roller of two rows, wherein the radially inner side roller has certain camber, and the camber ratio radially inner side roller that the roller of radial outside has is little, and the anti-working life of peeling off that it can provide is identical with the sample 35 of example of the present invention.In addition, do not have the sample 37 of the radial outside roller that has certain camber, equate with sample 35 working life that promptly has the sample 38 of straight roller.In sample 37 and 38, the increase of radial outside bearing capacity can prevent effectively that the radial outside of roller radial outside surface and roller bearing race from peeling off.
As set in sample 39, the length of radial outside roller is set to 1.2 times of radially inner side roller length, the length that makes the radially inner side roller is less and the length radial outside roller is bigger, rather than make as conventional inside and outside two row the roller equal in length, can increase the bearer cap of radial outside like this, thereby the radial outside that prevents roller radially-outer surface and roller bearing race peels off, the differential that reduces the radially inner side roller simultaneously slides, and is 1.7 times of sample 35 thereby make working life of sample 39.Specifically, the radially tool that sample 39 has sidewinders column length and reduces, and makes the differential of radially inner side roller slide less than two common row's rollers, can significantly be increased working life thus.
From what these results may be obvious that be, the roller quantity in radially effluxing (or bag portion quantity) be increased to the footpath inwardly the roller quantity among the row equate or be more, also can increase the bearing capacity of radial outside, reach similar effects thus.This structure can be that example is implemented with the needle roller thrust bearing shown in Fig. 2 C also.
In addition, as set in sample 40 and 41, the roller that end face that has protrudes arc can prevent the phase mutual interference that the roller end surface is serious, and prevents the serious mutual interference mutually of bag portion of roller end surface and bearing cage.In addition, from what table 4 also may be obvious that be, the crooked of roller can reduce, and friction torque can reduce.
The 5th embodiment
The validity of needle roller thrust bearing of the present invention can prove with respect to its abrasion resistance properties of roller bearing race.Sample 35 and 31 (standard rolling bearing) rotates one definite period (10 hours) under the condition identical with table 3 with 32 with other sample 34.Be pointed out that, sample 35 has two rows and remains on the bearing cage interior roller that has camber and a roller bearing race, roller bearing race has a surface layer (beginning to measure from its surface) that contains the 0.1mm degree of depth at least, and the size of the granularity of carbide is 0.6 μ m or bigger, for per 1 square millimeter unit area precipitation 39452 such particles are arranged like this, its area percentage is 9.64%.After rotating and moving, maximum abrasion resistance properties (degree of depth) is measured, the result is as shown in table 5.
Table five
| The sample table number | The specification of roller bearing race | The specification of roller | Maximum wear intensity (μ m) | ||
| The quantity of unit square carbide (mm) | The percentage of the carbide of unit area | The geometrical shape of roller | Row's number of roller | ||
| 31 (standard rolling bearings) | 6540 | 0.5 | Straight | 1 row | 1.5 |
| 34 (comparative examples) | 6540 | 0.5 | Have | 2 rows | 0.7 |
| 42 (comparative examples) | 39452 | 9.64 | Straight | 1 row | 0.1 |
| 35 (examples of the present invention) | 39452 | 9.64 | Have | 2 rows | 0.05 |
As measured in the end of roller bearing race after rotating operation, the wear-resisting property of sample 31,34 and 42 maximums that can reach is respectively 1.5 μ m, 0.7 μ m and 0.1 μ m, and the wear-resisting property of the maximum of the sample 35 that wear-resisting property significantly improves is 0.05 μ m.
Although above detailed description has also illustrated the present invention, be understandable that these only are explanation and example, and the present invention are not played any restriction.For example, the most broadly, the present invention can be applicable to any needle roller thrust bearing, and this bearing comprises single roller and roller bearing race with surface layer of the carbide that above-specified high density wherein is housed that has certain camber.The spirit and scope of the present invention are only determined by appended claims.
Claims (2)
1. a method of making roller thrust bearing is pressed from both sides between interior ring and outer shroud and is established the rollers that remain in the bearing cage of arranging more, to accept to be applied to the thrust load between the described inside and outside ring, said method comprising the steps of:
Described bearing cage forms has a bag portion that holds described many row's rollers;
Make all described many row's rollers have camber, and described roller is arranged in the described bag portion, providing the differential that reduces to slide, but the pressure of contact surface that is applied to the described thrust load generation on described many row's rollers by ring and outer shroud in described is arranged on contact pressure in bag portion, when all having a plurality of roller of through ship exterior feature greater than having when described bag portion.
2. the method for claim 1 is characterized in that, described many rows are two rows, and described bag portion has two rollers that have camber that are arranged on wherein.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001292742A JP3871537B2 (en) | 2001-09-26 | 2001-09-26 | Thrust roller bearing |
| JP2001292742 | 2001-09-26 | ||
| JP2001357710 | 2001-11-22 |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB021439397A Division CN1258044C (en) | 2001-09-26 | 2002-09-26 | Roller thrust bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1873244A true CN1873244A (en) | 2006-12-06 |
| CN100472079C CN100472079C (en) | 2009-03-25 |
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Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200610074824 Pending CN1873225A (en) | 2001-09-26 | 2002-09-26 | Roller thrust bearing |
| CNB2006100748234A Expired - Fee Related CN100472079C (en) | 2001-09-26 | 2002-09-26 | Roller thrust bearing |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200610074824 Pending CN1873225A (en) | 2001-09-26 | 2002-09-26 | Roller thrust bearing |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP3871537B2 (en) |
| CN (2) | CN1873225A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101622464B (en) * | 2007-02-28 | 2012-02-01 | 谢夫勒两合公司 | Multi-part axial cage for a large-diameter roller bearing |
| CN103133525A (en) * | 2011-11-25 | 2013-06-05 | 徐工集团工程机械股份有限公司 | Bearing and bearing lifting hook structure with the bearing |
| CN106246718A (en) * | 2016-08-12 | 2016-12-21 | 安徽江淮汽车股份有限公司 | A kind of needle roller lining and auxiliary assembling structure thereof |
| CN107429736A (en) * | 2015-04-20 | 2017-12-01 | 舍弗勒技术股份两合公司 | Method for manufacturing the rolling element for rolling bearing |
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| JP2006009913A (en) * | 2004-06-24 | 2006-01-12 | Ntn Corp | Bearing structure for electric brake, and double-row thrust needle rolling bearing for electric brake |
| JP2006112380A (en) * | 2004-10-18 | 2006-04-27 | Jtekt Corp | Bearing device for swash plate type compressor |
| JP2008020020A (en) * | 2006-07-14 | 2008-01-31 | Ntn Corp | Tapered roller bearing, and structure for supporting shaft at pilot portion |
| JP5173213B2 (en) * | 2007-02-28 | 2013-04-03 | 本田技研工業株式会社 | Tripod type constant velocity joint |
| JP2008312436A (en) | 2007-05-15 | 2008-12-25 | Ntn Corp | Electric direct acting actuator and electric braking device |
| WO2008140097A1 (en) * | 2007-05-15 | 2008-11-20 | Ntn Corporation | Electric linear actuator and electric brake device |
| CN101947735B (en) * | 2010-09-10 | 2012-07-25 | 康凤明 | Super-short cylinder rolling rotary table |
| CN107013612B (en) * | 2017-03-30 | 2019-02-15 | 庆安集团有限公司 | A kind of self-tightening type machine automatization brake gear |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR567239A (en) * | 1923-06-08 | 1924-02-27 | Cie Applic Mecaniques | Elastic helical roller thrust bearing |
| US2959458A (en) * | 1959-02-02 | 1960-11-08 | Rollway Bearing Company Inc | Thrust bearing |
| JPH0375312U (en) * | 1989-11-27 | 1991-07-29 | ||
| JP3661133B2 (en) * | 1994-08-19 | 2005-06-15 | 日本精工株式会社 | Rolling bearing for compressor |
| JP3604458B2 (en) * | 1995-07-03 | 2004-12-22 | 光洋精工株式会社 | Thrust roller bearing for swash plate compressor |
| JPH09236119A (en) * | 1995-12-27 | 1997-09-09 | Ntn Corp | Thrust cylinder roller bearing |
| JP2000240645A (en) * | 1999-02-22 | 2000-09-05 | Nkk Corp | Thrust bearing |
-
2001
- 2001-09-26 JP JP2001292742A patent/JP3871537B2/en not_active Expired - Fee Related
-
2002
- 2002-09-26 CN CN 200610074824 patent/CN1873225A/en active Pending
- 2002-09-26 CN CNB2006100748234A patent/CN100472079C/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101622464B (en) * | 2007-02-28 | 2012-02-01 | 谢夫勒两合公司 | Multi-part axial cage for a large-diameter roller bearing |
| CN103133525A (en) * | 2011-11-25 | 2013-06-05 | 徐工集团工程机械股份有限公司 | Bearing and bearing lifting hook structure with the bearing |
| CN103133525B (en) * | 2011-11-25 | 2016-03-23 | 徐工集团工程机械股份有限公司 | Bearing and be provided with the Suspension hook structure of this bearing |
| CN107429736A (en) * | 2015-04-20 | 2017-12-01 | 舍弗勒技术股份两合公司 | Method for manufacturing the rolling element for rolling bearing |
| CN106246718A (en) * | 2016-08-12 | 2016-12-21 | 安徽江淮汽车股份有限公司 | A kind of needle roller lining and auxiliary assembling structure thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3871537B2 (en) | 2007-01-24 |
| CN1873225A (en) | 2006-12-06 |
| JP2003097562A (en) | 2003-04-03 |
| CN100472079C (en) | 2009-03-25 |
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