CN1120131A - Composite rolling body automatic pumping oil lubricating type radial rolling bearing - Google Patents
Composite rolling body automatic pumping oil lubricating type radial rolling bearing Download PDFInfo
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- CN1120131A CN1120131A CN 93105860 CN93105860A CN1120131A CN 1120131 A CN1120131 A CN 1120131A CN 93105860 CN93105860 CN 93105860 CN 93105860 A CN93105860 A CN 93105860A CN 1120131 A CN1120131 A CN 1120131A
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Abstract
The rolling bearing features that its primary rollers are used to bear load, its secondary rollers are arranged between primary ones and serves as integral holder to ensure very small gap between primary rollers without contact, and the relative movement and special gap between parts constitute a dynamic pressure oil pump for forcing lubrication. Its advantages include high bearing power, allowable rotation speed and reliability, low noise and long service life.
Description
The invention relates to radial rolling bearing, particularly about in a bearing, having adopted the bigger rolling element of a group or more diameter as supporting roll kinetoplast (female rolling element), the less rolling element (sub-rolling element) of a group or more diameter is as separation roller, the composite rolling body automatic pumping oil lubricating type radial rolling bearing that has pump functional oil voluntarily and can carry out pressure lubrication to rolling element and raceway.
Radial rolling bearing (referring to mainly that here rolling element is various radial rolling bearings such as spherical, cylindrical, taper, sphere be cylindrical) is permitted to hold the rotating speed height owing to have, and starting and operation friction moment are little, can bear radial load and thrust load simultaneously, reliable operation, the rotation precision advantages of higher is widely used in lathe at present, motor, aviation, vehicle, boats and ships, in the engineering running mechanism system, be to use one of rolling bearing the most widely.
In existing various types of radial rolling bearings, nominal operation load and maximum functional rotating speed are arranged all.In general, it is very difficult and contradiction wanting to improve simultaneously the two.Under the prerequisite of base dimension that does not change bearing and material property, one of effective ways that improve nominal operation load are the cancellation retainers, utilize the space that increases therefrom to increase the number of rolling element.But the shortcoming of this way is: when bearing rotates, since between each rolling element without any spacer, two adjacent rollers of counterrotating just be easy to high-speed friction takes place and cause bearing temperature to rise rapidly and roller between wearing and tearing, so permitted to hold rotating speed usually well below the rolling bearing that has retainer.In addition, owing to make aspects such as assembling and the stressed back distortion of roller, must consider between each roller, to leave certain clearance (hx), shown in figure one, because the existence in this gap, along with the rotation of bearing, each roller just produces with another roller in turn and impacts, and causes noise.
On the other hand, though that influence further improves the factor of rotating speed is a lot, wherein one of the most effective means are the lubricating condition of improving bearing.Mostly method commonly used at present is to adopt a cover supplementary equipment, as the banjo lubrication oil pump, and jet lubrication device etc.These methods no doubt can be improved the lubricating condition of bearing inside greatly, improve its working speed, but correspondingly make equipment cost, installation cost and usage space all increase to some extent and bring problems such as reliability reduction.
At this present situation, purpose of the present invention aim to provide a series of have permitted to hold the rotating speed height, load rating is big, reliability is high, noise is little, the life-span is long radial rolling bearing.
The intention of invention is realized by following method: in a bearing, except that the supporting roll kinetoplast of installing some equal diameters (female rolling element), the separation roller (sub-rolling element) with supporting roll kinetoplast similar number is set simultaneously.The nominal diameter of separation roller is less than the supporting roll kinetoplast but diameter can be different, and its effect is to guarantee to have only a very little gap all the time between per two supporting roll kinetoplasts but be in contact with one another never.Supporting roll kinetoplast and separation roller are alternately settled, and between promptly per two supporting roll kinetoplasts a separation roller are arranged, and also we can say between per two separation rollers has a supporting roll kinetoplast.The actual result of Bu Zhiing is like this: separation roller comes in contact with the roller surface of Internal and external cycle (or transmission shaft) simultaneously never.Separation roller both can be placed between supporting roll kinetoplast and the inner ring (the inner ring side is arranged method) also can be placed in (the outer ring side is arranged method) between supporting roll kinetoplast and the outer ring, specifically arranges the structure that the method optical axis holds and decides.In brief, in the present invention, one group of separation roller that is scattered between the supporting roll kinetoplast has replaced traditional integrated type retainer.
When bearing working, inner ring or outer ring will drive the supporting roll kinetoplast and roll to a direction, per two supporting roll kinetoplasts and inner ring are (if the outer ring side is arranged method, then be the outer ring) the friction torque and the synergy of inertial force will make separation roller in revolution, with the opposite direction rotation of supporting roll kinetoplast sense of rotation.Because it is poor that separation roller and inner ring (or outer ring) exist absolute velocity at the raceway point of contact, the oil film that the elastic dynamic lubricating effect is produced will make separation roller not contact with raceway generation solid.When especially separation roller being arranged in the inner ring side, action of centrifugal force will further help separation roller to break away from raceway and only contact with the supporting roll kinetoplast.Like this, almost only there is pure rolling between supporting roll kinetoplast and the separation roller, and it is poor between separation roller and the raceway because exist absolute linear velocity, form elasticity of fluid lubricant film easily, except that having only the rolling element both ends of the surface to produce the sliding friction with both sides thrust toroidal surface, can guarantee does not almost have direct sliding friction between each part, thereby settling the supporting roll kinetoplast promptly to improve on the basis of bearing load carrying capacity to greatest extent, that can further improve bearing again is permitted to hold rotating speed.In addition since removed easy vibration and all the time with the integrated type retainer of supporting roll kinetoplast generation sliding friction, so can further reduce bearing vibration, noise and frictional heating etc., the reliability of raising bearing.
For high-speed bearing, the diameter of separation roller can be done greatly the diameter of supporting roll kinetoplast (but still less than), adopt wear resistance is good, proportion is little material such as engineering plastics, engineering ceramic material etc. simultaneously.
In order to improve the lubricating condition of bearing effectively, overcome the bearing inside that when high speed rotating, causes because of centrifugal force particularly in raceway lose oil, the present invention has adopted following method: between the cylindrical anchor ring of the interior toroidal surface of bearing outer ring both sides and inner ring, suitable (ring) gap of one size is set, on the interior toroidal surface (the perhaps cylindrical anchor ring of inner ring) of outer ring, offers the oily skewed slot (or spiral chute) of pump that several form an angle with axis then.Produce same direction oil stream as the skewed slot that will make the bearing both sides, must design the true dip direction of pump oil groove on the toroidal surface of both sides consistent.Like this, when the cylindrical anchor ring of bearing inner race during with respect to the interior toroidal surface motion of outer ring, the pump oil groove of rolling element one side just can pump into oil the inside of bearing from the outside of bearing, the pump oil groove of opposite side tiltedly then is evacuated to the outside with the oil of bearing inside, and promptly two oil pumps as one man are sent to opposite side to fluid from a certain side of bearing vertically with direction.When sense of rotation is opposite, the also corresponding change of direction of oil stream.
Except the gap that two ring faces of above-mentioned usefulness constitute, for some high-speed bearing, the clearance plane that can above-mentionedly have an oily skewed slot of pump be designed to the garden conical surface or with the plane of axis normal.That is to say, the bus of two curved surfaces that constitutes the dynamic pressure oil pump is except can being the straight line with parallel axes, it also can be the oblique line that forms an angle with axis, or with the straight line of axis normal, and the feature of the oil of the pump between gap skewed slot is: the tangent line of oil groove any place always has a certain degree with the bus of above-mentioned curved surface.When this angle equates, mean that then the oil groove of discussing is a spiral chute everywhere.
Generally speaking, in the present invention, utilized the relative movement between the part of bearing own, by some specific curved surface (toroidal surface of relative movement part, the conical surface, plane with axis normal) gap of Gou Chenging and open tipper such as spiral chute in these gaps, form one or more clearance type dynamic pressure pump, the liquid that this delivery side of pump end promptly pumps is a desirable toroidal surface or part toroidal surface and near the raceway and the rolling element of bearing, thereby can carry out effective self-contained lubrication to the rolling element and the raceway of bearing.The dynamic pressure pump of discussing has three basic elements: first element is a fundamental surface, second element has relative movement, the curved surface of formation working clearance with fundamental surface, the 3rd element then is to be opened in the pump liquid skewed slot that a plurality of and surface bus on above-mentioned any one curved surface has certain angle, and fundamental surface can be also can moving of fixing.Obviously, this dynamic pressure pump has simple in structure, the reliability height, and the transfusion characteristic just in time meets advantages such as bearing requirement.
All invade use condition such as various oil pump and the oil motor of bubble in oil for bearing, the bearing that is proposed by the present invention will further demonstrate its superiority.
The shape of the skewed slot section in the clearance type oil pump can be different shapes such as rectangle, triangle, trapezoidal, circular arc.The number of skewed slot, width, the degree of depth, spacing, geometric parameters such as angle of inclination are then answered decisions such as rotating speed that the optical axis holds and other conditions.As for the type of skewed slot, then be best with the spiral chute.
For the occasion that does not require too big lubricants capacity, can only offer clearance type skewed slot dynamic pressure oil pump in a side of bearing.
Because it is flow with the viscosity of fluid that the oil pump of discussing belongs to the viscosity dynamic pressure type and rotating speed is closely related and the increase that is directly proportional, the requirement institute of losing this problem of oil during just in time with solution bearing high speed between inner ring and the raceway is consistent, then has the loss of what additional torque when starting or low speed hardly.In addition, as mentioned above, because pump oil skewed slot (spiral chute) is that evenly to distribute along whole roller surface be that fluid will be with the form of a ring or part ring jet face to injections such as rolling elements, so can form very desirable lubricating system.In some occasion that requires ultra high speed running, can become two curved design in the clearance type oil pump taper or with the plane of axis normal.Like this, can guarantee that oil pump can not cavitate at the inlet port place on the one hand, can make the jet that is the garden conical surface oil be sprayed to roller surface and rolling element on the other hand with certain angle.
Compare with forming axial flow pressure reduction needed, that occur in the rolling element both sides, not much bigger by the number pressure magnitude that the elasticity dynamic pressure effect between rolling element and the raceway produces, therefore, there be the unlikely problem of bearing aspect bearing capacity that cause in the former.
Be difficult to realize that from integral arrangement the fluid major cycle adds the use occasion of cooling for some, can consider on the internal surface of the outer surface of bearing outer ring or inner ring, to offer the oil groove that is communicated with the bearing both sides, so that in the scope of the flow field, both sides of bearing, form circulating of fluid.Certainly,, also can offer oil guide slot and oilhole, form the circulation canal of fluid at the bearing middle part for the heavy bearing of many rows rolling element structure.Simultaneously, the oil extraction direction of a plurality of clearance type dynamic pressure oil pumps is designed to from the bearing both sides towards the bearing middle part or from the bearing middle part towards the bearing both sides.
When making relatively large rolling bearing, can offer circular shape oil groove or spiral chute on the separation roller surface, with the further lubricity of improving.
Should be noted that: clearance type dynamic pressure oil pump is set between the inside and outside circle of bearing also has several additional advantages in addition.First advantage is, increased the heat diffusion area of bearing owing to being provided with (it is required to offer pump oil skewed slot) two lateral retaining plates, helps running up of bearing.And in traditional bearing, be difficult to take into account simultaneously the axial perforation amount that increases lubricant medium and strengthen heat diffusion area.Second advantage is, because the setting of above-mentioned two lateral retaining plates make bearing become enclosed construction basically, and the shadoweffect of enclosed construction helps reducing the noise of bearing.
In sum, the present invention is except that increasing aspect the bearing capacity, in the sliding friction of lowering bearing inside, increases aspects such as the axial perforation amount of lubricant medium and efficiently radiates heat area, all is better than existing various radial rolling bearing greatly.
Compare with existing various radial rolling bearings, the present invention has advantages such as bearing capacity is big, the selflubricating ability is strong, permitted to hold rotating speed height, good reliability, noise is little, the life-span is long.
The present invention is used for the embodiment of various annulars bearing with rolling contact by accompanying drawing 21--and accompanying drawing eight provides.
The schematic representation why figure two can roll for the explanation separation roller.
Figure three is the working principle explanation schematic representation of clearance type skewed slot dynamic pressure oil pump.
Figure four is used for the embodiment of unilateral thrust radial ball bearing for the present invention.The supporting roll kinetoplast of this bearing is one group of ball, and separation roller is that one group of, intermediate portion identical with supporting roll kinetoplast number is saddle-shaped dolioform roller.
Figure five is for having the composite-type radial force roller bearing of clearance type dynamic pressure oil pump.(a) among figure expression is opened pump oil skewed slot between Internal and external cycle, is isolated the single supporting roll substructure example of roller for so-called " outer ring side installation method ", (b) to isolate roller be that " inner ring side installation method " and clearance type skewed slot dynamic pressure pump are with the structure example of certain angle (A) to the single pressure-bearing roller of inner ring raceway oil jet lubrication in expression, (c) then be the embodiment of two-row structure, (d) clearance plane of dynamic pressure oil pump and the topology example of axis normal have been represented, (e) among the figure is " A-A " section, represented the concrete structure of planar spiral groove pump pasta.The clearance type dynamic pressure oil pump of (f) among the figure five expression rolling element both sides simultaneously to bearing middle part pump oil or from the middle part to the multirow roller beaing of both sides pump oil.
Figure six is used for the embodiment of self-centering type spherical bearing for the present invention, (a) expression supporting roll kinetoplast among the figure is that ball, separation roller are the situation that the middle part is the dolioform roller of the shape of a saddle, (b) then represented a kind of spherical roller bearing, its supporting roll kinetoplast is a spherical roller, and separation roller is that the middle part is saddle-shaped spherical roller.
Figure seven is used for the topology example of radial force needle bearing for the present invention, (a) among the figure is a kind of structure of not having inner ring, isolating needle roller is " the outer ring side is arranged method ", pump oil skewed slot is opened on the interior toroidal surface of both sides, outer ring, and (b) then expression has on the needle bearing of inside and outside circle and the interior toroidal surface that pump oil skewed slot is opened in the both sides, outer ring, isolates the situation of needle roller for " the inner ring side is arranged method ".
Figure eight expression the present invention are used for the embodiment of taper roller bearing, (a) be single-row structure, (b) be double column structure, the former two groups of pumps oil skewed slots be opened on two inner cylindrical surfaces of outer ring and pump oil direction consistent all the time, the latter has then adopted four gaps to show the dynamic pressure oil pump but pump oil direction is different in twos.Both supporting roll kinetoplasts and separation roller are conical roller.
Below, with reference to accompanying drawing two--eight, describe the structure characteristic of the composite rolling body automatic pumping oil lubricating radial rolling bearing that proposes according to the present invention and working principle etc. in detail.
Shown in figure two, the situation when being placed in the inner ring side with the isolation roller is an example, illustrates that it certainly leads to the reason of rolling.For isolating roller (3), if do not consider oil film and The Effect of Inertia Force, when bearing working, then can be at (a), (b), (c) 3 respectively with pressure-bearing roller (2-1), (2-2) and the raceway of inner ring (1) come in contact.Though the friction torque (Mc) at (c) point has the trend of isolating the rotation of roller (3) generation counterclockwise direction that makes, the friction torque (Ma) that point (a) and point (b) are located (Mb) then can make isolation roller (3) produce clockwise rotation.Because the difference of normal direction contact force, as long as the friction factor between each part is identical, then (Ma) and synergy (Mb) will overcome (Mc) and make isolation roller (3) produce clockwise rotation and clockwise revolution.Certainly, this result means: if do not have oil film between isolation roller and inner ring raceway face, just then can produce slide relative between the two.But as long as design is proper, just can make isolation roller (3) be not equal to the absolute velocity values of inner ring raceway at (c) point in the absolute velocity of (c) point, this helps making both can not produce direct friction isolating generation hydrodynamic lubrication oil film between roller and the inner ring raceway.The effect of centrifugal force (Fc) helps to alleviate the frictional force of (c) point.Furthermore, because isolate two pressure-bearing rollers (2-1) of roller (3) and both sides, (2-2) switched in opposite makes to be easy to form oil film between two pairs of rolling surfaces, so can guarantee almost there is not direct sliding friction between each part except that both ends of the surface.
The working principle of clearance type skewed slot (or spiral chute) dynamic pressure oil pump is discussed now.Shown in figure three, if it is as a whole the outer ring of the bearing among the figure four (4)＜suppose two lateral retaining plates (5) and outer ring 〉, inner ring (1) launches and is expressed as 3-D graphic along garden Zhou Fangxiang, then must be opened in several heeling pump oil grooves (Cl) of both sides, outer ring, (Cr) and the position between Internal and external cycle and rolling element relation.The figure middle and upper part is divided into the expansion plane (1A) of inner ring, and the bottom is divided into the expansion plane (4A) of outer ring.When plane, top (1A) was mobile with the opposite direction of speed " V " edge " X " axle, because the effect of viscosity, the fluid between (1A) reaches (4A) just moved with the opposite direction of different speed along " X " axle.The fluid speed that sticks on (1A) face is consistent with the movement velocity " V " of inner ring, and the fluid speed on (4A) groove bottom then is zero.Because oil groove (C1) has an angle (D) with moving direction,, realized oil from of the requirement of the three unities pump to another place so the above fluid in bottom surface just is pushed to " b--b " face from " a--a " face continuously in the groove.The geometric parameter of pump oil skewed slot such as (c) among the figure three, (t), (h), (w), (D), the skewed slot number, clearance height (hc), clearance plane radius (Rc), oil viscosity and speed of related movement " V " etc. all have certain influence to pump oil ability.
Figure four is used for the embodiment of unilateral thrust radial ball bearing (Angular Contact BallBerring) for the present invention.Bearing is by inner ring (1), one group of pressure-bearing ball (2), and one group of but diameter less, middle part shape become the shape of a saddle dolioform roller isolation roller (3) identical with pressure-bearing ball number, outer ring (4), two blocks of side plates (5) constitute.Two groups of pump oil skewed slots (spiral chute) are opened on the interior toroidal surface of side plate (5), with cylindrical anchor ring formation two clearance type dynamic pressure oil pumps (CHP1) of inner ring, (CHP2).When the inner ring of bearing in a clockwise direction during " Wc " rotation, fluid just produces axial flow as shown in the figure.Sense of rotation as bearing changes, then the also corresponding change of direction of oil stream.Why will isolate roller (3) and make shape shown in the figure, be to produce excellent contact in order to guarantee between itself and the pressure-bearing roller.
Embodiment when figure five expression the present invention are used for radial force roller bearing (Cylindrical Roller RadialBearing), (a) among the figure is single-row roller bearing.Bearing is by inner ring (1), one group of pressure-bearing roller (2) that diameter is bigger, but isolation roller (3) that diameter less identical with supporting roll subnumber order, outer ring (4), and two lateral retaining plates (5) constitute, and this baffle plate and outer ring are fixed together.Isolating roller is outer ring side setting type.Clearance type dynamic pressure oil pump (CHP1) reaches and (CHP2) is formed by the gap between baffle plate (5) and the inner ring, and pump oil skewed slot is opened on the interior toroidal surface of baffle plate.When bearing " Wc " when rotation in a clockwise direction, oil pump just fluid from the left pump of bearing to the right.When sense of rotation was counterclockwise direction, two oil pumps " CHP1 " reached " CHP2 " and then fluid are pressed to the left side from the right side of bearing.
Situation when (b) expression among the figure will be isolated roller work " inner ring layout method ".Two clearance type dynamic pressure oil pumps (CHP1) (CHP2) still are made of baffle plate (5) and inner ring (1), and two groups of pump oil skewed slots are opened on the interior toroidal surface of baffle plate (5).For make fluid can be effectively internally raceway and roller be lubricated, the clearance plane that constitutes the dynamic pressure oil pump is made the conical surface that certain angle (A) arranged with axis.
The topology example of a kind of biserial pressure-bearing roller of (c) expression among the figure.Bearing is by inner ring (1), and two groups of pressure-bearing rollers (2) are isolated roller (3) for two groups, and outer ring (4), two baffle plate parts such as (5) constitute.Two clearance type dynamic pressure oil pumps are made of two lateral retaining plates (5) and inner ring (1), and two groups of pump oil skewed slots are opened on the baffle plate, constitute two clearance type dynamic pressure oil pumps (CHP1) with the cylindrical anchor ring of inner ring, (CHP2).
For some occasion that needs the ultra high speed running, can adopt the structure shown in (d) among the figure five.Bearing is by inner ring (1), two lateral retaining plates (5) that are fixed together with inner ring, one group of supporting roll kinetoplast (2), one group of separation roller (3), outer ring parts such as (4) is formed, pump oil skewed slot can be opened on the plane of both sides, outer ring, constitutes two planar spiral groove clearance type dynamic pressure oil pumps (CHP1) with baffle plate and reaches (CHP2).Because the suction port of dynamic pressure oil pump will be positioned among the fluid all the time and pump oil pressure and flow all can reach high value, so both made under very high rotating speed, also can carry out effective lubricating to rolling element and raceway, (e) among the figure represented that " A-A " section is the concrete structure of planar spiral groove pump pasta.When bearing inner race when " Wc " rotates in a clockwise direction, (CHP1) on right side just fluid from the outside of bearing pump into the middle part and spray to angle " A " in raceway and rolling element, (CHP2) in left side then extracts fluid outside the bearing out.Vice versa.Because the skewed slot on the plane (spiral chute) longshore current can design very longly to length, thus bigger oil mass can under higher pressure condition, be exported, so this structure especially is adapted to the ultra high speed running.
For the multiple row supporting roll pillar heavy bearing that some requirement runs up, the oil extraction direction that is positioned at a plurality of clearance type skewed slot dynamic pressure oil pumps of bearing roller both sides can be designed to flow to both sides from both sides towards the bearing middle part or from the bearing middle part simultaneously.Shown in (f) among the figure five, bearing is by an inner ring, and four row cylindrical pressure-bearing rollers (2), four row diameters are less than the cylindrical isolation roller (3) of pressure-bearing roller, two outer rings (4), and two blocks of side plates (5), an associative ring (6) constitutes.Isolating roller arranges for the outer ring side.Four groups of pumps oil skewed slots are opened in respectively on two blocks of side plates and the associative ring, constitute four clearance type dynamic pressure oil pumps (CHP1) with the outer surface of bearing inner race, (CHP2), and (CHP3), (CHP4).Wherein, the pump of oil pump (CHP1) and (CHP2) oil direction is consistent, and (CHP3), unanimity (CHP4) but different with the former." " during rotation, (CHP1) and (CHP2) fluid is pumped into the middle part from the left side of bearing, (CHP3) and (CHP4) side pumps into the middle part of bearing to fluid to Wc from the right side, through circular groove (C1), (C2) waits and constitutes circulation in a clockwise direction when bearing inner race.When the switched in opposite of bearing inner race, fluid just by four oil pumps from the middle part of bearing respectively pump to both sides.Obviously, the method for arranging of this a plurality of clearance type skewed slot dynamic pressure oil pumps is equally applicable to ball bearing, self-centering type spherical bearing, needle bearing and taper roller bearing.
Figure six expression the present invention are used for the embodiment of self-centering type ball and roller bearing (Self-Aligning Balland Spherical Roller Bearing).(a) expression supporting roll kinetoplast among the figure is that ball, separation roller are the situation that the middle part becomes the dolioform roller of the shape of a saddle.When adopting this kind rolling element to be to make itself and supporting roll kinetoplast to carry out excellent contact, roll around raceway reliably as the reason of separation roller.Certainly, the concrete shape of separation roller also can be other forms.Bearing is by inner ring (1), two groups of pressure-bearing balls (2), and with the same number of two groups of dolioform isolation rollers of pressure-bearing ball (3), raceway is the outer ring (4) of sphere, the both sides flexible baffle (5) that is fixed together with the outer ring constitutes.Two groups of pump oil skewed slots are opened on the interior toroidal surface of baffle plate, with cylindrical anchor ring formation two clearance type dynamic pressure oil pumps (CHP1) of inner ring, (CHP2).Be to guarantee the aligning ability of bearing, should take into full account the gap length of gap oil pump and two lateral retaining plates and have enough flexible.When bearing " Wc " when rotation in a clockwise direction, two clearance type dynamic pressure oil pumps (CHP1) and (CHP2) make fluid produce as shown in the figure circulation.
Structure example when (b) expression the present invention among the figure is used for the self-centering type spherical roller bearing.Bearing is by inner ring (1), two groups of pressure-bearing sphere shape rollers (2) that diameter is bigger, and with the pressure-bearing roller is the same number of but the sphere shape that diameter is less, the middle part is horse peace saddle type is isolated roller (3), outer ring (4), two lateral retaining plates (5) constitute.Two groups of pumps oil skewed slots (or spiral chute) are opened on the interior toroidal surface of baffle plate (5), constitute two clearance type dynamic pressure oil pumps (CHP1) and (CHP2) with the cylindrical anchor ring of inner ring.When bearing when " Wc " rotates in a clockwise direction, (CHP1) and (CHP2) make fluid produce as shown in the figure axial flow.The same with the situation of self-aligning ball bearing, the size and the flexible of two lateral retaining plates that need give one's full attention to the gap are the self-alignment ability.
Figure seven is used for the application examples of the needle bearing (Needle Roller Bearing) of several different structures for the present invention.(a) among the figure represented the needle bearing of no inner ring.The bearing of this form is used in the less occasion of radial space more, and rolling element will directly contact with the generation of axle surface and roll.Bearing is isolated roller (3) by pressure-bearing roller (2), and outer ring parts such as (4) is formed.Isolating roller is arranged between pressure-bearing needle roller and the outer ring.On two interior toroidal surfaces of both sides, outer ring, two groups of pump oil skewed slots (G1) and (G 2) have been offered.After bearing is installed between hole and the axle, two groups of pump oil skewed slots (G1), (G2) will constitute two clearance type dynamic pressure oil pumps (CHP1) with the axle surface and reach (CHP2).Corresponding to the turning to clockwise of axle " Wc ", (CHP1), (CHP2) will make fluid produce flowing as shown in the figure.When the switched in opposite of axle, the also corresponding change of the flow direction of fluid.
(b) among the figure represented to have the structure example of the needle bearing of inside and outside circle.Bearing is by inner ring (1), and pressure-bearing needle roller (2) is isolated needle roller (3), and outer ring parts such as (4) is formed.Two clearance type dynamic pressure oil pumps (CHP1) and (CHP2) being arranged between the cylindrical anchor ring of the interior toroidal surface of both sides, outer ring and inner ring.Difference corresponding to inner ring turns to, the also corresponding change of direction that fluid flows vertically.
Should be noted that: compare with ball or roller bearing,, thereby in traditional needle bearing, have two problems at least because the length-to-diameter of needle roller is bigger in the needle bearing; The one, needle roller is easily with respect to journal offset, the 2nd, the bearing middle part is good the lubricating of difficult acquisition when high speed rotating, so generally speaking, the figure of merit of needle bearing " Dn " (the distribution circle diameter of rolling element and the product of rotating speed) is far smaller than rolling ball or roller bearing.The needle bearing that adopts the present invention to make then may improve " Dn " greatly and be worth and increase the service life.
Figure eight is used for the example of taper roller bearing (Taper Roller Bearing) for the present invention.(a) among the figure represented the structure example of single-row taper roller bearing.Bearing is by inner ring (1), the pressure-bearing tapper (2) that diameter is bigger, but isolation tapper (3) that diameter less identical with pressure-bearing tapper number, outer ring (4), two lateral retaining plates (5) constitute.Isolating tapper is " the inner ring side is arranged method ".Two clearance type dynamic pressure oil pumps (CHP1) (CHP2) are made of the interior toroidal surface of two lateral retaining plates (5) and the cylindrical anchor ring of inner ring.Pump oil skewed slot is opened on two lateral retaining plates (5).When bearing inner race when " Wc " rotates in a clockwise direction, two oil pumps just are sent to the right side with fluid from the left side of bearing.When the sense of rotation of axle changed, the direction of oil stream also changed thereupon.
(b) among the figure is double-row type taper roller bearing structure example.Because this bearing generally is used for the heavier occasion of work loads more, need lubricating condition preferably.For this reason, four clearance type dynamic pressure oil pumps can be designed to simultaneously from both sides mutually the middle part or simultaneously from the middle part to the structure of both sides pump oil.As shown in the figure, bearing is by integrated type inner ring (1), and two groups of pressure-bearing tappers (2) are isolated tapper (3) for two groups, two separated type outer rings (4), and two baffle plates (5), associative ring parts such as (6) constitutes, and the same inner ring of baffle plate (5) (1) is fixed together.Isolating tapper is " the inner ring side is arranged method ".The inner cylindrical surface of the external cylindrical surface of inner ring and two lateral retaining plates constitutes two clearance type dynamic pressure oil pumps (CHP1), and (CHP3), two other clearance type dynamic pressure oil pump (CHP2) (CHP4) then is made of the cylindrical anchor ring in the middle part of associative ring and the inner ring.Four groups of pump oil skewed slots (spiral chute) are opened on two lateral retaining plates and the associative ring.When the inner ring of bearing in a clockwise direction during " Wc " rotation, (CHP1) and (CHP3) just oil is sent to central part from the outside of bearing, pass through (CHP2) on the guide ring (6) then, (CHP4) and radial hole (Kj), circular trough (Hc) etc.s constitute and circulate.Sense of rotation as bearing changes, and then four clearance type dynamic pressure oil pumps will make the oil miscarriage give birth to different flow directions.
Point out in passing, utilize basic principle of the present invention, can also design radial rolling bearing such as self-alignment formula roller, needle roller and the taper roller bearing of other many different structures, multiple row formula rolling bearing, adopt the composite bearing of dissimilar rolling elements, radial force and axial force combined type rolling bearing etc.
In addition, opinion is scattered with a component and is placed the separation roller between the supporting roll kinetoplast to guarantee mutual discontiguous principle between the supporting roll kinetoplast among the present invention, is adapted to make the rolling bearing movement means of other types such as the straight reciprocating motion slide unit of ball screw, ball or roller bearing etc. equally.
At last, " composite-type rolling element principle " reaches " the automatic pumping oil lubricating principle " that the present invention proposes also can be used for making various speed change gears such as planetary transmission, cycloidal-pin wheel speed changer, three ring speed changers etc.
Claims (5)
- Composite rolling body automatic pumping oil lubricating type radial rolling bearing, the radial rolling bearing that comprises that rolling element is sphere, cylinder type, sphere is cylindrical, the garden is tapered etc., mainly by a group or more the supporting roll kinetoplast or claim female rolling element (2), equate with supporting roll kinetoplast number, a group or more separation roller or claim sub-rolling element (3) and inner ring (1), outer ring parts such as (4) is formed.Feature of the present invention is: 1, in a bearing, settled a group or more the bigger supporting roll kinetoplast of diameter, a group or more, with the same number of separation roller of supporting roll kinetoplast.
- 2, according to the described bearing of claim " 1 ", it is characterized in that: the maximum diameter of any separation roller is all less than the maximum diameter of supporting roll kinetoplast.
- 3, according to the described bearing of claim " 1 ", it is characterized in that: supporting roll kinetoplast and separation roller are alternately placed.Separation roller will be never simultaneously with inner ring on raceway (or axle surface) and the raceway on the outer ring come in contact.
- 4, be provided with a clearance type skewed slot or spiral chute dynamic pressure oil pump at least in the both sides of bearing roller.
- 5, according to the described bearing of claim " 3 ", its oil pump is characterised in that: the formation element of oil pump is the particular geometric gap between the relative movement part of bearing, and being opened in several pumps oil skewed slot or spiral chutes that constitute on the curved surface of above-mentioned gap, every skewed slot or spiral fluted center line all have an angle with respect to the bus of discussing curved surface.The function of this oil pump is that lubricant medium is delivered to opposite side from a side pressure of rolling element, and rolling element and raceway are carried out pressure lubrication.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 93105860 CN1120131A (en) | 1993-05-28 | 1993-05-28 | Composite rolling body automatic pumping oil lubricating type radial rolling bearing |
| PCT/GB1994/000820 WO1994024446A1 (en) | 1993-04-19 | 1994-04-19 | Self-pumping roller bearings |
| JP52292394A JP2002515105A (en) | 1993-04-19 | 1994-04-19 | Self pump operated roller bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 93105860 CN1120131A (en) | 1993-05-28 | 1993-05-28 | Composite rolling body automatic pumping oil lubricating type radial rolling bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1120131A true CN1120131A (en) | 1996-04-10 |
Family
ID=4985943
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 93105860 Pending CN1120131A (en) | 1993-04-19 | 1993-05-28 | Composite rolling body automatic pumping oil lubricating type radial rolling bearing |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1120131A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1717463A2 (en) * | 2005-04-28 | 2006-11-02 | JTEKT Corporation | Liquid-lubricated tapered roller bearing and bearing arrangement of a vehicle pinion shaft |
| CN109713843A (en) * | 2018-12-25 | 2019-05-03 | 南京航空航天大学 | A kind of bearing arrangement cold for external rotor permanent magnet synchronous machine oil |
| CN111664191A (en) * | 2019-11-08 | 2020-09-15 | 摩登汽车有限公司 | Fixed constant velocity joint |
| CN113847337A (en) * | 2021-08-16 | 2021-12-28 | 人本股份有限公司 | Ball bearing with big and small ball structure |
| CN114412736A (en) * | 2022-01-27 | 2022-04-29 | 北京三力新能科技有限公司 | Bearing lubricating grease feeding device and wind generating set |
| CN114934954A (en) * | 2022-05-11 | 2022-08-23 | 西安电子科技大学 | Totally-enclosed medium self-circulation lubrication high-speed rolling bearing |
-
1993
- 1993-05-28 CN CN 93105860 patent/CN1120131A/en active Pending
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1717463A2 (en) * | 2005-04-28 | 2006-11-02 | JTEKT Corporation | Liquid-lubricated tapered roller bearing and bearing arrangement of a vehicle pinion shaft |
| EP1717463A3 (en) * | 2005-04-28 | 2010-03-24 | JTEKT Corporation | Liquid-lubricated tapered roller bearing and bearing arrangement of a vehicle pinion shaft |
| CN109713843A (en) * | 2018-12-25 | 2019-05-03 | 南京航空航天大学 | A kind of bearing arrangement cold for external rotor permanent magnet synchronous machine oil |
| CN109713843B (en) * | 2018-12-25 | 2022-06-28 | 南京航空航天大学 | Bearing structure for oil cooling of outer rotor permanent magnet synchronous motor |
| CN111664191A (en) * | 2019-11-08 | 2020-09-15 | 摩登汽车有限公司 | Fixed constant velocity joint |
| CN111664191B (en) * | 2019-11-08 | 2021-10-08 | 摩登汽车有限公司 | Fixed constant velocity joint |
| CN113847337A (en) * | 2021-08-16 | 2021-12-28 | 人本股份有限公司 | Ball bearing with big and small ball structure |
| CN114412736A (en) * | 2022-01-27 | 2022-04-29 | 北京三力新能科技有限公司 | Bearing lubricating grease feeding device and wind generating set |
| CN114934954A (en) * | 2022-05-11 | 2022-08-23 | 西安电子科技大学 | Totally-enclosed medium self-circulation lubrication high-speed rolling bearing |
| CN114934954B (en) * | 2022-05-11 | 2023-02-07 | 西安电子科技大学 | Full-closed medium self-circulation lubrication high-speed rolling bearing |
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