CN104235176A - Bearing and stepless transmission - Google Patents
Bearing and stepless transmission Download PDFInfo
- Publication number
- CN104235176A CN104235176A CN201410171293.XA CN201410171293A CN104235176A CN 104235176 A CN104235176 A CN 104235176A CN 201410171293 A CN201410171293 A CN 201410171293A CN 104235176 A CN104235176 A CN 104235176A
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- China
- Prior art keywords
- bearing
- outer ring
- ring
- retainer
- peripheral surface
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- 230000005540 biological transmission Effects 0.000 title abstract description 10
- 238000005096 rolling process Methods 0.000 claims abstract description 24
- 230000002093 peripheral effect Effects 0.000 claims description 54
- 230000007246 mechanism Effects 0.000 claims description 50
- 239000000314 lubricant Substances 0.000 abstract description 36
- ZZUFCTLCJUWOSV-UHFFFAOYSA-N furosemide Chemical compound C1=C(Cl)C(S(=O)(=O)N)=CC(C(O)=O)=C1NCC1=CC=CO1 ZZUFCTLCJUWOSV-UHFFFAOYSA-N 0.000 description 4
- 230000035515 penetration Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
- F16H29/02—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts
- F16H29/04—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts in which the transmission ratio is changed by adjustment of a crank, an eccentric, a wobble-plate, or a cam, on one of the shafts
Abstract
The invention provides a bearing and a stepless transmission. According to the bearing of the invention, through smoothly placing lubricant at a position between a holder and the inner circumferential surface of the outer ring and a position between the holder and the outer circumferential surface of an inner ring, a friction resistance and holder wearing are reduced, thereby improving durability. The bearing (16) is provided with the outer ring (161), the inner ring (162), a plurality of rolling members (164) and the holder (163). The bearing (16) is configured in a manner which is characterized in that: when the rotation axis direction of the inner ring (162) is used as the width direction, a dimension of an outer ring width (L1) between the center and one end of the outer ring (161), an inner ring width (L2) between the center and one end of the inner ring (162), and a holder width (L3) between the center and one end of the holder (163) satisfy a relationship L1>L3>L2.
Description
Technical field
The present invention relates to the stepless speed variator of bearing and this bearing of use.
Background technique
In the past, known what is called four like this saved the stepless speed variator of linkage mechanism type, and it possesses: input shaft, and it is passed the driving force from driving sources such as motors; Output shaft, it is configured to parallel with input shaft; And crankrocker mechanism, the rotation of input shaft is passed to output shaft (for example, referring to patent documentation 1) by it.
The crankrocker mechanism that this stepless speed variator possesses has turning radius controlling mechanism, connecting rod and fork.
Turning radius controlling mechanism has: the discoid cam part rotated integrally with input shaft; With the discoid rotary part that will wrap in this cam part in circular receiving orifice.Cam part is formed as the shape relative to input shaft bias, and receiving orifice is formed in the position of the center bias relative to rotary part.Further, rotary part rotates with the position of the cam part of the inside with receiving orifice (the axis of rotation position of input shaft) corresponding eccentric degree.
Distance between the center of rotary part and the rotating center axis of input shaft can be changed by adjustment driving sources such as the pinion shaft that to possess small gear (external tooth) integratedly and the motors driving this pinion shaft to rotate.Input shaft is formed as hollow, and pinion shaft runs through the concentric position of the inside being inserted in input shaft.Input shaft being formed the cut hole for making the small gear of pinion shaft expose, being formed with at the inner peripheral surface of the receiving orifice of rotary part the internal tooth that the small gear that expose with the cut hole from input shaft engages.
When making small gear rotate relative to rotary part, the position of cam part is changed relative to the receiving orifice of rotary part.Thus, the distance between the center of rotary part and the rotating center axis of the input shaft consistent with the rotating center axis of small gear is changed, and rotary part becomes the degree of eccentricity corresponding with this distance relative to its center.
The annulus formed in an end of connecting rod is rotatably installed on the periphery of rotary part through bearing.Fork is rotatably linked to another end of connecting rod.Fork is installed on output shaft through overrunning clutch, only the rotation in fork direction is passed to output shaft.
When making input shaft and pinion shaft rotate with same speed, cam part is fixed relative to the position of the receiving orifice of rotary part, and rotary part maintains the degree of eccentricity corresponding with the position of cam part around the rotating center axis of input shaft and rotates.
By the rotary motion of the bias of rotary part of giving through cam part from input shaft, connecting rod makes fork swing, and the overrunning clutch that swings by of fork is passed to output shaft, thus output shaft is rotated.
Further, if make input shaft different with the rotating speed of pinion shaft in the desired moment, then cam part moves relative to the position of rotary part and rotary part is changed relative to the degree of eccentricity of input shaft, and accompany therewith, gear ratio is changed.
In addition, between the outer periphery and the annulus of an end being formed at connecting rod of rotary part, be provided with the bearing for making both rotate swimmingly mutually.This bearing is by outer ring, inner ring, multiple rolling element and keep the retainer of rolling element to form.
Rolling element is located in the annular spaces that is formed between the inner peripheral surface of outer ring and the outer circumferential face of inner ring, and rolls and contact with the outer circumferential face of inner ring with the inner peripheral surface of outer ring freely.Retainer is formed as ring-type, is positioned at above-mentioned annular spaces and remains each rolling element.
, the bearing arranged based on the periphery at rotary part of said structure has been applied in secund centrifugal force along with the rotation of the bias of rotary part.Therefore, there is such worry in the retainer of the centrifugal force of being partial to: its part contacts with the inner peripheral surface of outer ring or the outer circumferential face of inner ring and produces surface friction drag, thus rotary part can be hindered relative to the rotation of the annulus of connecting rod, or retainer is caused to wear and tear.
On the other hand, in the stepless speed variator of said structure, lubricant oil disperses in its case of transmission.If the lubricant oil dispersed in case of transmission is attached to the surface of the rotary part of rotation, then can arrive bearing along the Radial Flow of rotary part.
Therefore, the lubricant oil also radially flowed by being attached to rotary part is taken between retainer and the inner peripheral surface of outer ring and between retainer and the outer circumferential face of inner ring, can expect the generation of reducing friction resistance and the wearing and tearing of retainer thus.
; for existing bearing, because the width of the outer ring along spin axis direction is equal with the width of inner ring, therefore; the lubricant oil arriving inner ring from rotary part seldom enters between outer ring and inner ring, thus cannot the fully generation of reducing friction resistance and the wearing and tearing of retainer.
Patent documentation 1: Japanese Unexamined Patent Publication 2013-19429 publication
Summary of the invention
Point in view of the above-mentioned problems, the object of the present invention is to provide a kind of bearing and stepless speed variator, described bearing by being taken into swimmingly between retainer and the inner peripheral surface of outer ring and between retainer and the outer circumferential face of inner ring by lubricant oil, coming the generation of reducing friction resistance and the wearing and tearing of retainer thus improves durability.
[1] in order to reach above-mentioned purpose, the 1st invention is a kind of bearing, and it possesses: outer ring, and it has inner peripheral surface, inner ring, it has from the inner side of the inner peripheral surface of this outer ring and the opposed outer circumferential face of the inner peripheral surface of this outer ring, and can freely rotate around the axis concentric with this outer ring, multiple rolling element, they be arranged on be formed at described outer ring the annular spaces between inner peripheral surface and the outer circumferential face of described inner ring in, and roll contact with the outer circumferential face of described inner ring with the inner peripheral surface of described outer ring freely, with the retainer of ring-type, it is positioned at described annular spaces, keep each rolling element, described outer ring another axis around the rotation axis parallel with this inner ring together with described inner ring rotates, the feature of described bearing is, described bearing is configured to, using the spin axis direction of described inner ring as width direction time, the size from central authorities to one end of described outer ring and outer ring width, the size from central authorities to one end of described inner ring and inner race width, and the size from central authorities to one end of described retainer and retainer width meet the relation of outer ring width G reatT.GreaT.GT retainer width G reatT.GreaT.GT inner race width.
Be arranged to outer ring other axis around the rotation axis parallel with inner ring together with inner ring due to described bearing rotate, therefore there is such situation: a part for the retainer of the centrifugal force of being partial to contacts with the outer circumferential face of the inner peripheral surface of outer ring or inner ring.
Consider this situation, bearing of the present invention is configured to the relation meeting " outer ring width G reatT.GreaT.GT retainer width G reatT.GreaT.GT inner race width ".According to such structure, an end of retainer extend out to the axially outside of one end of inner ring.Thus, when the lubricant oil radially flowed from the spin axis side of the inner ring rotated exceeds inner ring, retainer can be utilized to accept this lubricant oil at least partially, therefore, it is possible to be taken into swimmingly between retainer and the outer circumferential face of inner ring by lubricant oil.
And according to said structure, an end of outer ring extend out to the axially outside of one end of retainer.Thereby, it is possible to utilize the lubricant oil of inner peripheral surface undertaking beyond retainer of outer ring.Therefore, it is possible to lubricant oil is taken between the inner peripheral surface of outer ring and retainer swimmingly.
Like this, even if receive a part for the retainer of the centrifugal force of deflection to contact with the outer circumferential face of the inner peripheral surface of outer ring or inner ring, also lubricant oil can be taken into swimmingly between retainer and the inner peripheral surface of outer ring and between retainer and the outer circumferential face of inner ring, therefore, it is possible to the reliably generation of reducing friction resistance and the wearing and tearing of retainer, thus the bearing that durability is high can be provided.
[2] in addition, about the 2nd invention, in the bearing of above-mentioned 1st invention, the inner peripheral surface of described outer ring possesses the large-diameter portion that diameter radially expands in one end, described retainer possesses the protuberance of the ring-type protruding outside to radial direction in the position corresponding with described large-diameter portion.
Roll because rolling element contacts with inner ring with outer ring, therefore, when lubricant oil excessively invade receive rolling element between outer ring and inner ring time, rolling element is had to push lubricant oil open and is rolled, and this may hinder the rolling smoothly of rolling element on the contrary.
Therefore, in bearing of the present invention, be provided with described large-diameter portion in a part for the inner peripheral surface of outer ring, and, retainer is provided with described protuberance.Thus, the lubricant oil be taken between the inner peripheral surface of outer ring and retainer arrives the position of rolling element hardly, can prevent from excessively supplying lubricant oil to rolling element.That is, can think, the lubricant oil be taken between described large-diameter portion and described protuberance overcomes the centrifugal force accompanied with the rotation of bearing hardly and flows along the direction of spin axis.
Therefore, according to bearing of the present invention, the lubricant oil be taken between described large-diameter portion and described protuberance can be utilized, give sufficient lubrication, while prevent from excessively supplying lubricant oil to rolling element between the inner peripheral surface of outer ring and retainer.
And retainer possesses described protuberance in the position corresponding with described large-diameter portion, thus, even if such as lubricant oil disperses tempestuously in the rotary course of bearing, lubricant oil intrusion towards rolling element from the outside of retainer also can be prevented.
[3] in addition, the 3rd invention is a kind of stepless speed variator, it is characterized in that, described stepless speed variator possesses the bearing of above-mentioned 1st invention or the bearing of above-mentioned 2nd invention, further, described stepless speed variator possesses: input part, and it is passed the driving force from traveling driving source, output shaft, it is configured to the rotating center axis being parallel with this input part, crankrocker mechanism, it has the fork that axle is supported on this output shaft, the rotary motion of described input part is converted to the oscillating motion of described fork, mechanism is stoped with single direction rotation, it is located between described fork and described output shaft, relative to described output shaft for relatively rotating to side time described fork is fixed on described output shaft, and make described fork dally relative to described output shaft when for relatively rotating to opposite side, described crankrocker mechanism possesses: adjustment driving source, turning radius controlling mechanism, it can utilize the driving force of this adjustment driving source freely to regulate turning radius, and connecting rod, this turning radius controlling mechanism and described fork link by it, and described turning radius controlling mechanism possesses: cam part, and it rotates integratedly with described input part under the state of the rotating center axis bias relative to described input part, and rotary part, it can rotate relatively with described cam part under the state relative to this cam part bias, described rotary part changes the eccentric degree of the rotating center axis relative to described input part by means of the driving force of described adjustment driving source, described turning radius controlling mechanism changes turning radius by the eccentric degree changing described rotary part, described connecting rod possesses the annulus being embedded in described rotary part outside described bearing, the described outer ring of described bearing is arranged at the annulus of described connecting rod, the described inner ring of described bearing is arranged at the edge, periphery of described rotary part.
In stepless speed variator of the present invention, described rotary part rotates prejudicially relative to the rotating center axis of input part, thus, gives secund centrifugal force to the bearing be located between the edge, periphery of this rotary part and the annulus of described connecting rod.
Now, bearing possesses the structure of above-mentioned 1st invention or above-mentioned 2nd invention, thus, as previously mentioned, lubricant oil can be taken between retainer and the inner peripheral surface of outer ring and between retainer and the outer circumferential face of inner ring swimmingly.Therefore, it is possible to reduce the generation of the surface friction drag between the rotary part of stepless speed variator and connecting rod and suppress the reduction of the transmission efficiency of power, and, the wearing and tearing of the retainer in bearing can be reduced to improve the durability of stepless speed variator.
Accompanying drawing explanation
Fig. 1 is the sectional view of the stepless speed variator that embodiments of the present invention are shown.
Fig. 2 is the explanatory drawing of the main portions of the stepless speed variator of present embodiment.
Fig. 3 is the illustrative sectional view of the main portions that bearing is shown.
Fig. 4 is the schematic diagram of the action that turning radius controlling mechanism is shown.
Fig. 5 is the schematic diagram of the relation that turning radius controlling mechanism and fork are shown.
Fig. 6 is the illustrative sectional view of the main portions that other bearings are shown.
Label declaration
1: stepless speed variator; 2: input shaft (input part); 3: output shaft; 4: turning radius controlling mechanism; 5: cam disk (cam part); 6: rotating disc (rotary part); 16,21: bearing; 161: inner peripheral surface (outer ring); 161a: large-diameter portion; 163a: protuberance; 162: outer circumferential face (inner ring); 164: rolling element; 163: retainer; 14: motor (adjustment driving source); 15: connecting rod; 15a: the 1 annulus (annulus); 17: overrunning clutch (single direction rotation stops mechanism); 18: fork; 20: crankrocker mechanism; L1: outer ring width; L3: retainer width; L2: inner race width.
Embodiment
Based on accompanying drawing, an embodiment of the invention are described.The stepless speed variator of present embodiment is the stepless speed variator of four joint linkage mechanism types, and is gear ratio i (rotating speed of the rotating speed/output shaft of i=input shaft) can be made to be infinitely great (∞) thus make the rotating speed of output shaft be the one of speed changer, the i.e. so-called IVT (Infinity Variable Transmission: Limitless speed variator) of " 0 ".
First, see figures.1.and.2 and the structure of the stepless speed variator 1 of present embodiment is described.The stepless speed variator 1 of present embodiment possesses input shaft 2 (input part), output shaft 3 and multiple (being 6 in the present embodiment) turning radius controlling mechanism 4.
Input shaft 2 is formed as hollow rod-shape, is driven and rotate around rotating center axis P1 by driving sources such as not shown motor or motor.
Output shaft 3 is configured to parallel with input shaft 2, although not shown, via differential gear or transmission shaft etc., rotating power is passed to the drive portions such as the driving wheel of vehicle.
Turning radius controlling mechanism 4 and input shaft 2 are uniformly set into and rotate around rotating center axis P1, and possess cam disk 5 (cam part), rotating disc 6 (rotary part) and pinion shaft 7.
Cam disk 5 is discoid, and cam disk 5 is eccentric from rotating center axis P1, and cam disk 5 is arranged at each turning radius controlling mechanism 4 in the mode being 1 group concerning 1 turning radius controlling mechanism 42.Every 1 group of cam disk 5 is set to phase shifting 60 ° respectively, and is configured to form a circle in the circumference of input shaft 2 with 6 groups of cam disks 5.
Rotating disc 6 is formed as discoid, is being provided with receiving orifice 6a from the position of its center bias.Receiving orifice 6a will be bundled in cam disk 5 and can freely rotate.In addition, the center of receiving orifice 6a is formed as: identical to the distance Rb of the center P3 of rotating disc 6 with the center P2 from cam disk 5 to the distance Ra of the center P2 (center of receiving orifice 6a) of cam disk 5 from the rotating center axis P1 of input shaft 2.In addition, in the position between 1 group of cam disk 5 of the receiving orifice 6a of rotating disc 6, internal tooth 6b is provided with.
Pinion shaft 7 is configured to input shaft 2 concentric in the input shaft 2 of hollow, and relatively rotatable relative to input shaft 2.In addition, external tooth 7a (small gear) is provided with in the periphery of pinion shaft 7.And then, pinion shaft 7 is connected with differential attachment 8.
In addition, the position between 1 group of cam disk 5 on input shaft 2 and being on the side face in the direction contrary with the eccentric direction of cam disk 5 at the rotating center axis P1 relative to input shaft 2, is formed with the cut hole 2a that inner peripheral surface is communicated with outer circumferential face.The cut hole 2a of external tooth 7a through this input shaft 2 arranged in the periphery of pinion shaft 7 engages with the internal tooth 6b that the inner circumferential of the receiving orifice 6a at rotating disc 6 is arranged.
Differential attachment 8 is configured to planetary gears, and it has: sun gear 9; The 1st gear ring 10 linked with input shaft 2; The 2nd gear ring 11 linked with pinion shaft 7; With planet carrier 13, band ladder small gear 12 axle is supported to by it can freely rotation and revolution, and described band ladder small gear 12 is made up of the large footpath teeth portion 12a engaged with sun gear 9 and the 1st gear ring 10 and the path teeth portion 12b that engages with the 2nd gear ring 11.In addition, the sun gear 9 of differential attachment 8 is linked to the running shaft 14a of the motor 14 (adjustment driving source) that driving pinion axle 7 rotates.
Therefore, when making the rotating speed of motor 14 identical with the rotating speed of input shaft 2, sun gear 9 and the 1st gear ring 10 rotate with same speed, sun gear 9, the 1st gear ring 10, these 4 components of the 2nd gear ring 11 and planet carrier 13 become the lock state that can not relatively rotate, and the pinion shaft 7 and the input shaft 2 that link with the 2nd gear ring 11 rotate with same speed.
When the rotating speed of the rotating ratio input shaft 2 making motor 14 is slow, if set the rotating speed of sun gear 9 as Ns, if the rotating speed of the 1st gear ring 10 is NR1, if the velocity ratio of sun gear 9 and the 1st gear ring 10 (number of teeth of the number of teeth/sun gear 9 of the 1st gear ring 10) is j, then the rotating speed of planet carrier 13 is (jNR1+Ns)/(j+1).In addition, if set the velocity ratio of sun gear 9 and the 2nd gear ring 11 ((number of teeth of the number of teeth/sun gear 9 of the 2nd gear ring 11) × (being with the number of teeth of the number of teeth/path teeth portion 12b of the large footpath teeth portion 12a of ladder small gear 12)) as k, then the rotating speed of the 2nd gear ring 11 is { j (k+1) NR1+ (k-j) Ns}/{ k (j+1) }.
When existing poor between the rotating speed and the rotating speed of pinion shaft 7 of input shaft 2, rotating disc 6 rotates around the periphery of cam disk 5 centered by the center P2 of cam disk 5.
As shown in Figure 2, rotating disc 6 relative to cam disk 5 bias is: the distance Ra from P1 to P2 is equal with the distance Rb from P2 to P3.Therefore, it is possible to make the rotating center axis P1 of the center P3 of rotating disc 6 and input shaft 2 be positioned on the same line, thus distance, i.e. offset R1 between the rotating center axis P1 of the input shaft 2 and center P3 of rotating disc 6 is made to be " 0 ".
As depicted in figs. 1 and 2, the connecting rod 15 rotatably outer periphery being embedded in rotating disc 6.Connecting rod 15 has the 1st annulus 15a (annulus) in large footpath an end, have the 2nd annulus 15b that diameter is less than the diameter of the 1st annulus 15a in another end.1st annulus 15a of connecting rod 15 is embedded in rotating disc 6 outside bearing 16.
As shown in Figures 2 and 3, the inner peripheral surface 161 that bearing 16 is formed using the Inner peripheral portions of the 1st annulus 15a at connecting rod 15 as outer ring, using the outer circumferential face 162 formed in the edge, periphery of rotating disc 6 as inner ring.Further, in the space of the ring-type between the inner peripheral surface 161 being formed at the 1st annulus 15a and the outer circumferential face 162 of rotating disc 6, the multiple rolling elements 164 remained in the retainer 163 of ring-type are accommodated with.
As shown in Figure 3, each rolling element 164 contacts with the outer circumferential face 162 of rotating disc 6 with the inner peripheral surface 161 of the 1st annulus 15a, and rolls freely under the state being held in retainer 163.
And, about bearing 16, the relation between the size from central authorities to one end of outer circumferential face 162 of the size from central authorities to one end of the inner peripheral surface 161 of the 1st annulus 15a and outer ring width L1, rotating disc 6 and the size from central authorities to one end of inner race width L2 and retainer 163 and retainer width L3 is L1 > L3 > L2.Thus, be formed as, an end of retainer 163 extend out to the radial outside of the outer circumferential face 162 of rotating disc 6, and an end of the inner peripheral surface 161 of the 1st annulus 15a extend out to the radial outside of retainer 163.
As depicted in figs. 1 and 2, fork 18 is supported on output shaft 3 through overrunning clutch 17 (single direction rotation stops mechanism) axle.Overrunning clutch 17 when centered by the rotating center axis P4 of output shaft 3 for fixing fork 18 to when a sideway swivel relative to output shaft 3, when for rotating to opposite side, relative to output shaft 3, fork 18 is dallied.
Fork 18 is provided with and swings end 18a, be provided with a pair tab 18b at swing end 18a, described a pair tab 18b is formed as being sandwiched between them by the 2nd annulus 15b in the axial direction.A pair tab 18b runs through and is provided with the penetration hole 18c corresponding with the internal diameter of the 2nd annulus 15b.By connection pin 19 being inserted penetration hole 18c and the 2nd annulus 15b, thus connecting rod 15 and fork 18 are linked up.
Next, the crankrocker mechanism of the stepless speed variator 1 of present embodiment is described.As shown in Figure 2, in the stepless speed variator 1 of present embodiment, constitute crankrocker mechanism 20 (four joint linkage mechanisms) by turning radius controlling mechanism 4, connecting rod 15, fork 18.
This crankrocker mechanism 20 is utilized the rotary motion of input shaft 2 to be converted to the oscillating motion of fork 18.As shown in Figure 1, the stepless speed variator 1 of present embodiment possesses 6 crankrocker mechanism 20 altogether.
In this crankrocker mechanism 20, if do not make input shaft 2 and pinion shaft 7 rotate with identical speed for " 0 " at the offset R1 of turning radius controlling mechanism 4, then the every 60 degree of ground of each connecting rod 15 change phase place, alternately repeatedly to press or to input shaft 2 side traction to output shaft 3 thruster between input shaft 2 and output shaft 3 simultaneously, thus fork 18 is swung.
And, owing to being provided with overrunning clutch 17 between fork 18 and output shaft 3, therefore, in a kind of situation in situation about being pushed at fork 18 and trailed situation, fork 18 is fixed and makes the power of the oscillating motion of fork 18 be passed to output shaft 3, thus output shaft 3 is rotated, in another case, fork 18 dallies, and the power of the oscillating motion of fork 18 is not passed to output shaft 3.6 turning radius controlling mechanisms 4 change phase place with being configured to every 60 degree respectively, and therefore, output shaft 3 is rotated by 6 turning radius controlling mechanisms 4 successively.
In addition, in the stepless speed variator 1 of present embodiment, as shown in Figure 4, the turning radius of turning radius controlling mechanism 4, i.e. offset R1 is made to regulate freely.
(a) of Fig. 4 shows and makes offset R1 be the state of " maximum ", and pinion shaft 7 and rotating disc 6 are positioned at the position making the rotating center axis P1 of input shaft 2, the center P2 of cam disk 5 and the center P3 of rotating disc 6 be arranged in straight line.In this case gear ratio i becomes minimum.(b) of Fig. 4 show make offset R1 be less than (a) of Fig. 4 " in " state, (c) of Fig. 4 shows and makes offset R1 be the state of " little " less than (b) of Fig. 4.In (b) of Fig. 4, gear ratio i be larger than the gear ratio i of (a) of Fig. 4 " in ", in (c) of Fig. 4, gear ratio i is " greatly " larger than the gear ratio i of (b) of Fig. 4.(d) of Fig. 4 shows and makes offset R1 be the state of " 0 ", and the rotating center axis P1 of the input shaft 2 and center P3 of rotating disc 6 is positioned at concentric position.In this case gear ratio i becomes infinity (∞).
In addition, Fig. 5 is the schematic diagram of the relation between the change of turning radius, i.e. offset R1 of the turning radius controlling mechanism 4 that present embodiment is shown and the angle of oscillation of the oscillating motion of fork 18.
(a) of Fig. 5 shows in the situation (gear ratio i is minimum situation) that offset R1 is " maximum " of (a) of Fig. 4, the hunting range θ 2 of the fork 18 corresponding with the rotary motion of turning radius controlling mechanism 4, (b) of Fig. 5 show offset R1 be (b) of Fig. 4 " in " situation (gear ratio i be in situation) under, the hunting range θ 2 of the fork 18 corresponding with the rotary motion of turning radius controlling mechanism 4, (c) of Fig. 4 shows in the situation (gear ratio i is large situation) that offset R1 is " little " of (c) of Fig. 4, the hunting range θ 2 of the fork 18 corresponding with the rotary motion of turning radius controlling mechanism 4.At this, from the rotating center axis P4 of output shaft 3 to connecting rod 15 with the length R2 swinging the tie point of end 18a, the distance namely to the center P5 of connection pin 19 is fork 18.
Clearly known according to this Fig. 5, along with offset R1 diminishes, the hunting range θ 2 of fork 18 narrows, and when offset R1 becomes " 0 ", fork 18 does not swing.
In the crankrocker mechanism 20 of action like this, rotating disc 6 rotates with above-mentioned each offset R1 in the inner side of the 1st annulus 15a of connecting rod 15.Now, rotating disc 6 is rotated relative to the 1st annulus 15a of connecting rod 15 swimmingly by bearing 16, but accompanies with the rotation under the eccentric state of rotating disc 6, and bearing 16 also rotates with eccentric state.Namely, for bearing 16, the rotating center axis P1 (other axis) of the input shaft 2 that the inner peripheral surface 161 suitable with outer ring of the 1st annulus 15a extends abreast around the axis (spin axis of inner ring) with the center P3 by rotating disc 6 together with the outer circumferential face 162 suitable with inner ring of rotating disc 6 rotates.
Therefore, can think, the centrifugal force of being partial to a direction with offset R1 accordingly can be applied to bearing 16, retainer 163 is contacted with the inner peripheral surface 161 of the 1st annulus 15a or the outer circumferential face 162 of rotating disc 6.
Therefore, in the present embodiment, as shown in Figure 3, there is by making bearing 16 be configured to the relation of outer ring width L1 > retainer width L3 > inner race width L2, thus, as previously mentioned, an end of retainer 163 extend out to the radial outside of the outer circumferential face 162 of rotating disc 6, and an end of the inner peripheral surface 161 of the 1st annulus 15a extend out to the radial outside of retainer 163.
For the stepless speed variator 1 of present embodiment, when crankrocker mechanism 20 action, lubricant oil disperses in case of transmission.If the lubricant oil dispersed in case of transmission is attached to the surface of the rotating disc 6 of rotation, then can arrive bearing 16 along the Radial Flow of rotating disc 6.Now, the end due to retainer 163 extend out to the radial outside of the outer circumferential face 162 of rotating disc 6, and therefore, the lubricant oil exceeding the outer circumferential face 162 of rotating disc 6 is kept device 163 to be stopped and invades between the outer circumferential face 162 of retainer 163 and rotating disc 6.In addition, an end due to the inner peripheral surface 161 of the 1st annulus 15a extend out to the radial outside of retainer 163, therefore, the lubricant oil exceeding retainer 163 is stopped by the inner peripheral surface 161 of the 1st annulus 15a and invades between the inner peripheral surface 161 of retainer 163 and the 1st annulus 15a.
Like this, by between the outer circumferential face 162 that lubricant oil is taken into swimmingly retainer 163 and rotating disc 6 and between the inner peripheral surface 161 of retainer 163 and the 1st annulus 15a, thus, even if retainer 163 contacts with the inner peripheral surface 161 of the 1st annulus 15a or the outer circumferential face 162 of rotating disc 6, also can the reliably generation of reducing friction resistance and the wearing and tearing of retainer 163, the durability of bearing 16 is also improved.
Further, in the stepless speed variator 1 of present embodiment, the bearing 21 of the structure shown in Fig. 6 also can be set to replace the bearing 16 shown in Fig. 3.As shown in Figure 6, this bearing 21 not only has the relation of outer ring width L1 > retainer width L3 > inner race width L2, and, also possess the large-diameter portion 161a that diameter radially expands in an end of the inner peripheral surface 161 of the 1st annulus 15a, and possess the protuberance 163a of ring-type in an end of retainer 163.
The diameter of large-diameter portion 161a is larger than other parts (hereinafter referred to as minor diameter part 161b), therefore, is formed with the wall 161c formed due to ladder difference between large-diameter portion 161a and minor diameter part 161b.Further, the protuberance 163a of retainer 163 is formed in the position corresponding with large-diameter portion 161a.
For the bearing 21 of above structure, an end due to retainer 163 extend out to the radial outside of the outer circumferential face 162 of rotating disc 6, therefore, the lubricant oil exceeding the outer circumferential face 162 of rotating disc 6 is kept device 163 to be stopped and invades between the outer circumferential face 162 of retainer 163 and rotating disc 6.In addition, an end due to the large-diameter portion 161a of the inner peripheral surface 161 of the 1st annulus 15a extend out to the radial outside of the protuberance 163a of retainer 163, therefore, the lubricant oil having exceeded the outer side surface of the protuberance 163a of retainer 163 is stopped by the large-diameter portion 161a of the inner peripheral surface 161 of the 1st annulus 15a and invades between the large-diameter portion 161a of the protuberance 163a of retainer 163 and the inner peripheral surface 161 of the 1st annulus 15a.
Thus, even if the protuberance 163a of retainer 163 contacts with the large-diameter portion 161a of the inner peripheral surface 161 of the 1st annulus 15a or retainer 163 contacts with the outer circumferential face 162 of rotating disc 6, also can the reliably generation of reducing friction resistance and the wearing and tearing of retainer 163.
And, even if the lubricant oil invaded between the protuberance 163a of the retainer 163 and large-diameter portion 161a of the inner peripheral surface 161 of the 1st annulus 15a is attached to the wall 161c between large-diameter portion 161a and minor diameter part 161b, at least during rotating disc 6 rotates, the flowing towards the direction (overcoming the direction of centrifugal force) from large-diameter portion 161a towards minor diameter part 161b of lubricant oil can not be there is.Therefore, owing to being formed with large-diameter portion 161a at the inner peripheral surface 161 of the 1st annulus 15a, therefore, it is possible to prevent lubricant oil to the overfeeding between the minor diameter part 161b and retainer 163 of the inner peripheral surface 161 of the 1st annulus 15a.
And, owing to preventing lubricant oil to the overfeeding between the minor diameter part 161b and retainer 163 of the inner peripheral surface 161 of the 1st annulus 15a, therefore, it is possible to the lubricant oil preventing from exceeding needs is attached to rolling element 164, thus the rolling smoothly of rolling element 164 can not be hindered.
In addition, the protuberance 163a that the end side in the gap between the minor diameter part 161b of the inner peripheral surface 161 of the 1st annulus 15a and retainer 163 is kept device 163 covers, therefore, the lubricant oil dispersed around bearing 21 can not directly invade this gap, and lubricant oil also can be prevented thus to the overfeeding between the minor diameter part 161b and retainer 163 of the inner peripheral surface 161 of the 1st annulus 15a.
As mentioned above, for the stepless speed variator 1 of present embodiment, because crankrocker mechanism 20 possesses the bearing 21 shown in the bearing 16 shown in Fig. 3 or Fig. 6, the transmission of power therefore between rotating disc 6 and connecting rod 15 can be carried out swimmingly, and durability is also higher.
Further, in the stepless speed variator 1 of present embodiment, use input shaft 2 as input part, but the input part used in stepless speed variator of the present invention is not limited to such input shaft 2.Such as, also can use following such input part: penetration hole is set on cam disk 5, utilize the running shaft being configured to the driving sources such as the cam part union body that is connected with this penetration hole and motor to form this input part.
In addition, in the present embodiment, use overrunning clutch 17 to stop mechanism as single direction rotation, but the single direction rotation used in stepless speed variator of the present invention stop mechanism to be not limited to such overrunning clutch 17.Such as, also can be made up of following such twin-direction clutch (twocouese clutch): the sense of rotation relative to output shaft 3 that this twin-direction clutch is configured to make moment of torsion to be passed to the fork 18 of output shaft 3 from fork 18 switches freely.
In addition, the bearing 16,21 of present embodiment makes outer ring be integrally formed in a part for connecting rod 15, and make inner ring be integrally formed in a part for rotating disc 6, number of components can be reduced thus to alleviate the weight of stepless speed variator 1, be not limited thereto, although not shown, also bearing of the present invention can be made to be separate component, although not shown, outer ring can be embedded and be fixed on the inner side of the 1st annulus 15a of connecting rod 15, and inner ring embedded and is fixed on the outside of rotating disc 6.
In this case, below the width dimensions of the outer ring of bearing is formed as by making the width dimensions on the axial direction of the 1st annulus 15a of connecting rod 15, and make the width dimensions on the axial direction of the edge, periphery of rotating disc 6 be formed as below the width dimensions of the inner ring of bearing, can obtain thus and the bearing 16 in present embodiment, 21 identical effects.
In addition, bearing of the present invention also can adopt in the device beyond the stepless speed variator 1 of present embodiment.
Claims (3)
1. a bearing, it possesses:
Outer ring, it has inner peripheral surface;
Inner ring, it has from the inner side of the inner peripheral surface of this outer ring and the opposed outer circumferential face of the inner peripheral surface of this outer ring, and can freely rotate around the axis concentric with this outer ring;
Multiple rolling element, they be arranged on be formed at described outer ring the annular spaces between inner peripheral surface and the outer circumferential face of described inner ring in, and roll contact with the outer circumferential face of described inner ring with the inner peripheral surface of described outer ring freely; With
The retainer of ring-type, it is positioned at described annular spaces, keeps each rolling element,
Described outer ring another axis around the rotation axis parallel with this inner ring together with described inner ring rotates,
The feature of described bearing is,
Described bearing is configured to, using the spin axis direction of described inner ring as width direction time, the size from central authorities to one end of described outer ring and outer ring width, the size from central authorities to one end of described inner ring and the size from central authorities to one end of inner race width and described retainer and retainer width meet the relation of outer ring width G reatT.GreaT.GT retainer width G reatT.GreaT.GT inner race width.
2. bearing according to claim 1, is characterized in that,
The inner peripheral surface of described outer ring possesses the large-diameter portion that diameter radially expands in one end,
Described retainer possesses the protuberance of the ring-type protruding outside to radial direction in the position corresponding with described large-diameter portion.
3. a stepless speed variator, is characterized in that,
Described stepless speed variator possesses the bearing described in claim 1 or 2, and,
Described stepless speed variator possesses: input part, and it is passed the driving force from traveling driving source; Output shaft, it is configured to the rotating center axis being parallel with this input part; Crankrocker mechanism, it has the fork that axle is supported on this output shaft, the rotary motion of described input part is converted to the oscillating motion of described fork; Mechanism is stoped with single direction rotation, it is located between described fork and described output shaft, relative to described output shaft for relatively rotating to side time described fork is fixed on described output shaft, and when for relatively rotating to opposite side, make described fork dally relative to described output shaft
Described crankrocker mechanism possesses: adjustment driving source; Turning radius controlling mechanism, it can utilize the driving force of this adjustment driving source freely to regulate turning radius; And connecting rod, it links this turning radius controlling mechanism and described fork,
Described turning radius controlling mechanism possesses: cam part, and it rotates integratedly with described input part under the state of the rotating center axis bias relative to described input part; And rotary part, it can rotate relatively with described cam part under the state relative to this cam part bias,
Described rotary part changes the eccentric degree of the rotating center axis relative to described input part by means of the driving force of described adjustment driving source,
Described turning radius controlling mechanism changes turning radius by the eccentric degree changing described rotary part,
Described connecting rod possesses the annulus being embedded in described rotary part outside described bearing,
The described outer ring of described bearing is arranged at the annulus of described connecting rod,
The described inner ring of described bearing is arranged at the edge, periphery of described rotary part.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013123967A JP6144121B2 (en) | 2013-06-12 | 2013-06-12 | Bearing and continuously variable transmission |
| JP2013-123967 | 2013-06-12 | ||
| JPJP2013-123967 | 2013-06-12 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104235176A true CN104235176A (en) | 2014-12-24 |
| CN104235176B CN104235176B (en) | 2016-11-30 |
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ID=
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB300024A (en) * | 1927-11-24 | 1928-11-08 | Gen Electric Co Ltd | Improvements in or relating to the lubrication of bearings |
| FR2308013A1 (en) * | 1975-04-18 | 1976-11-12 | Ina Roulements Sa | Ball race bearings with snap fit (polyamide) cages - so the cages inhibit axial track displacement |
| JP2005502543A (en) * | 2001-09-26 | 2005-01-27 | ルーク ラメレン ウント クツプルングスバウ ベタイリグングス コマンディートゲゼルシャフト | Drive device |
| CN202531634U (en) * | 2012-04-19 | 2012-11-14 | 无锡诚石轴承有限公司 | Spinning wheel bearing |
| WO2013001859A1 (en) * | 2011-06-30 | 2013-01-03 | 本田技研工業株式会社 | Four-joint link type continuously variable transmission |
| JP2013019429A (en) * | 2011-07-07 | 2013-01-31 | Honda Motor Co Ltd | Four-bar linkage type continuous variable transmission |
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB300024A (en) * | 1927-11-24 | 1928-11-08 | Gen Electric Co Ltd | Improvements in or relating to the lubrication of bearings |
| FR2308013A1 (en) * | 1975-04-18 | 1976-11-12 | Ina Roulements Sa | Ball race bearings with snap fit (polyamide) cages - so the cages inhibit axial track displacement |
| JP2005502543A (en) * | 2001-09-26 | 2005-01-27 | ルーク ラメレン ウント クツプルングスバウ ベタイリグングス コマンディートゲゼルシャフト | Drive device |
| WO2013001859A1 (en) * | 2011-06-30 | 2013-01-03 | 本田技研工業株式会社 | Four-joint link type continuously variable transmission |
| JP2013019429A (en) * | 2011-07-07 | 2013-01-31 | Honda Motor Co Ltd | Four-bar linkage type continuous variable transmission |
| CN202531634U (en) * | 2012-04-19 | 2012-11-14 | 无锡诚石轴承有限公司 | Spinning wheel bearing |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6144121B2 (en) | 2017-06-07 |
| JP2014240696A (en) | 2014-12-25 |
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