CN205155058U - Friction power transmission device - Google Patents
Friction power transmission device Download PDFInfo
- Publication number
- CN205155058U CN205155058U CN201520784853.9U CN201520784853U CN205155058U CN 205155058 U CN205155058 U CN 205155058U CN 201520784853 U CN201520784853 U CN 201520784853U CN 205155058 U CN205155058 U CN 205155058U
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- Prior art keywords
- bearing
- planetary rollers
- shell
- inner ring
- rotation
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 57
- 230000002093 peripheral effect Effects 0.000 claims abstract description 51
- 238000009434 installation Methods 0.000 claims abstract description 12
- 239000007787 solid Substances 0.000 claims description 64
- 230000007246 mechanism Effects 0.000 claims description 54
- 238000003825 pressing Methods 0.000 claims description 30
- 230000002265 prevention Effects 0.000 claims description 6
- 230000005489 elastic deformation Effects 0.000 abstract 1
- 239000000314 lubricant Substances 0.000 description 10
- 230000008878 coupling Effects 0.000 description 9
- 238000010168 coupling process Methods 0.000 description 9
- 238000005859 coupling reaction Methods 0.000 description 9
- 239000003638 chemical reducing agent Substances 0.000 description 6
- 238000004519 manufacturing process Methods 0.000 description 3
- 230000004323 axial length Effects 0.000 description 2
- 239000011230 binding agent Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 239000012141 concentrate Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 229920001971 elastomer Polymers 0.000 description 1
- 239000000806 elastomer Substances 0.000 description 1
- NJPPVKZQTLUDBO-UHFFFAOYSA-N novaluron Chemical group C1=C(Cl)C(OC(F)(F)C(OC(F)(F)F)F)=CC=C1NC(=O)NC(=O)C1=C(F)C=CC=C1F NJPPVKZQTLUDBO-UHFFFAOYSA-N 0.000 description 1
Classifications
-
- 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
- F16H13/00—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members
- F16H13/06—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members with members having orbital motion
- F16H13/08—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members with members having orbital motion with balls or with rollers acting in a similar manner
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Friction Gearing (AREA)
Abstract
The utility model provides a friction power transmission device, its have shell, first rotator, first bearing, with second rotator, second bearing and the annular inner ring of the power transmission of realization by the friction carry out between the first rotator. First rotator has first rotatory axial region and sun roller. The second rotator has the configuration at a plurality of planet rollers of the outer peripheral face of the outer peripheral face of circumference and each and sun roller and the contact of endocyclic inner peripheral surface, with the supporting of a plurality of planet rollers for using the central axis as rotatory planet carrier portion in center and the second rotation axial region be connected with planet carrier portion. Utilize endocyclic elastic deformation, a plurality of planet rollers are pressed to sun roller, and endocyclic installation inner peripheral surface is fixed in the outer peripheral face that encircles fixing bearing for arbitrary bearing of shell first rotator of supporting or second rotator promptly.
Description
Technical field
The utility model relates to a kind of driving-force transmission mechanism.
Background technique
In the past, multiple planetary rollers is clipped the outer circumferential face that lubricant oil presses on sun roller by the driving-force transmission mechanism as speed reducer or booster engine.In driving-force transmission mechanism, compared with the gear transmission mechanism making multiple gears meshing, reduce the vibration & noise caused because of back clearance.
In planetary roller power transmitting deice disclosed in Japanese Unexamined Patent Publication 57-163044 publication, multiple planetary rollers is configured between sun roller and elastic cylinder.Planetary rollers is pressed against sun roller by elastic cylinder.Shell is fixed in one end of elastic cylinder.
But, in driving-force transmission mechanism, require higher assembly precision.If the parts particularly planetary rollers pressed to sun roller are from center axis deviation, then plus-pressure change, and become the reason that vibration and rotational speed change.In device disclosed in Japanese Unexamined Patent Publication 57-163044 publication, shell is fixed in one end of elastic cylinder.Therefore, improve elastic cylinder and the processing needing to carry out shell height when comprising the coaxality of assembly body of planetary rollers, increase the manufacture cost of parts.
Model utility content
The purpose of this utility model improves the parts that planetary rollers pressed to sun roller relative to the coaxality of the assembly body comprising planetary rollers by simple structure in driving-force transmission mechanism.
Exemplary driving-force transmission mechanism of the present utility model comprises shell, the first solid of rotation, clutch shaft bearing, the second solid of rotation, the second bearing and inner ring.Clutch shaft bearing can by the first solid of rotation supporting for can rotate relative to shell centered by central axis.Second solid of rotation carries out the transmission of power realized by rubbing between the first solid of rotation.Second solid of rotation supports as can rotate relative to shell centered by central axis by the second bearing.Inner ring in the form of a ring, and is configured in the radial outside of the second solid of rotation.First solid of rotation has: the first rotary shaft, described first rotary shaft be centrally located at central axis; And sun roller, described sun roller together rotates with the first rotary shaft in the enclosure.Second solid of rotation has multiple planetary rollers, planet carrier portion and the second rotary shaft.In the enclosure, planetary rollers is configured in the radial outside of sun roller in the circumferential.The outer circumferential face of multiple planetary rollers contacts with the outer circumferential face of sun roller and the inner peripheral surface of inner ring respectively.In the enclosure, planet carrier portion by the supporting of multiple planetary rollers for can to rotate centered by the planetocentric axis in the centrally direction of axis.Second rotary shaft be centrally located at central axis, and the second rotary part is connected with planet carrier portion.Utilize the resiliently deformable of inner ring, multiple planetary rollers is pressed by sun roller.The installation inner peripheral surface of inner ring is fixed on the outer circumferential face of ring rigid bearing.Ring rigid bearing is the arbitrary bearing relative to outer casing supporting first solid of rotation or the second solid of rotation.
Inner ring is fixed on the outer circumferential face of ring rigid bearing by press-in or shrink fit.
Inner ring comprise prevent inner ring in the circumferential relative to shell rotate rotation prevention portion.
Inner ring is at the point of contact contacted with multiple planetary rollers and install between inner peripheral surface and comprise thinner wall section.The radial thickness of thinner wall section is less than the radial thickness at point of contact place.
At each planetary rollers of multiple planetary rollers and the first make contact place of inner ring, the diameter of the inner peripheral surface of inner ring reduces gradually along with the side to axis or increases.In the axial direction, the second point of contact that first make contact and each planetary rollers contact with sun roller is positioned at different positions.
In the axial direction, each planetary rollers of multiple planetary rollers is positioned at different positions from the second point of contact of the first make contact of inner ring and each planetary rollers and sun roller.About each planetary rollers, in the cross section in face comprising the planetocentric axis of this planetary rollers, first make contact and the second point of contact, the first pressing force vector representation acts on the first pressing force of each planetary rollers from inner ring.Second pressing force vector representation acts on the second pressing force of each planetary rollers from sun roller.First pressing force vector is relative to connecting the straight line of first make contact and the second point of contact to lopsidedness.Second pressing force vector tilts to opposite side relative to described straight line.
Shell has first shell on the first rotation side and the second housing on the second rotation side.Second housing in the axial direction with the first housing contacts.Second bearing is ring rigid bearing.Be positioned at and be positioned at second housing with the installation inner peripheral surface of inner ring in the end of the side of axial opposed.
Planet carrier portion has the first bracket, the second bracket and joint.First bracket is positioned at the side of the axis of multiple planetary rollers.First bracket is connected with the second rotary shaft.Second bracket is positioned at the opposite side of the axis of multiple planetary rollers.Joint connects the first bracket and the second bracket in the axial direction.Planet carrier portion also has outrigger bearing.Outrigger bearing between the second bracket and shell by the second bearing bracket for can rotate centered by central axis.
Second bearing is ring rigid bearing.At the radial outside of multiple planetary rollers, inner ring is separated diametrically with shell.
Shell has first shell on the first rotation side and the second housing on the second rotation side.Second housing in the axial direction with the first housing contacts.First shell and the border between second housing are overlapping with outrigger bearing diametrically.Gap is there is between the outer circumferential face of outrigger bearing and the inner peripheral surface of second housing.
Driving-force transmission mechanism also has inside bracket bearing.Sun roller supports as relatively can rotate relative to the second bracket centered by central axis by inside bracket bearing.
At the point of contact place of multiple planetary rollers and interior loop contacts, the diameter of the inner circumferential of inner ring is larger than the diameter of the outer circumferential face of ring rigid bearing.
According to the utility model, inner ring can be improved relative to the coaxality of the second solid of rotation comprising planetary rollers by simple structure.
With reference to accompanying drawing by the following detailed description to preferred implementation, above-mentioned and other key element, feature, step, feature and advantage of the present utility model will become apparent.
Accompanying drawing explanation
Fig. 1 is the longitudinal section of the driving-force transmission mechanism involved by a mode of execution.
Fig. 2 amplifies the longitudinal section that planetary rollers and the position near it are shown.
Fig. 3 amplifies the longitudinal section near the border that the first shell and second housing are shown.
Fig. 4 is the longitudinal section of another example that planetary rollers is shown.
Fig. 5 is the longitudinal section of another installation example that inner ring is shown.
Embodiment
Fig. 1 is the longitudinal section of the structure that the exemplary driving-force transmission mechanism 1 involved by a mode of execution of the present utility model is shown.In FIG, the cross section in the face of the central axis J1 comprising driving-force transmission mechanism 1 is shown.Driving-force transmission mechanism 1 is such as used as speed reducer or booster engine in precision processing machine or 3D measuring device etc.
Driving-force transmission mechanism 1 comprises shell 2, first solid of rotation 3, second solid of rotation 4 and inner ring 5.Shell 2 is in the roughly cylindrical shape centered by central axis J1.Shell 2 comprises the first shell 21 and second housing 22.Roughly cylindric in FIG in by towards centered by the central axis J1 of above-below direction of first shell 21.Second housing 22 is in the roughly cylindrical shape centered by central axis J1.Conveniently, in the following description using first shell 21 side of centrally axis J1 as upside, second housing 22 side is described as downside, but the direction of central axis J1 is necessarily not consistent with gravitational direction.Further, in the following description, by central axis J1 towards direction and above-below direction also referred to as " axis ".
First shell 21 is configured in the upside of second housing 22.The bottom of the first shell 21 and the top of second housing 22 comprise the lip part vertically expanded relative to central axis J1.The sectional position of Fig. 1 does not represent two lip parts.In two lip parts, the first shell 21 is connected to second housing 22 by multiple bolt.Multiple bolt roughly equal angles compartment of terrain is configured in the circumference centered by central axis J1.In the following description, by the circumference centered by central axis J1 referred to as " circumference ".
First shell 21 comprises bearing cage 211, cap 212 and cylindrical part 213.Bearing cage 211 in roughly cylindric, and is given prominence to upward.Cap 212 is expanded from the bottom of bearing cage 211 to the radial outside centered by central axis J1.In the following description, by the radial direction centered by central axis J1 referred to as " radial direction ".Cylindrical part 213 extends downwards from the outer edge of cap 212.Second housing 22 comprises bearing cage 221 and cylindrical part 222.Bearing cage 221 is bottoms of second housing 22.Cylindrical part 222 extends upward from the outer edge of bearing cage 221.By the upper end of cylindrical part 213 and the lower end in contact of cylindrical part 222, form the inner space of shell 2.
First solid of rotation 3 comprises the first rotary shaft 31 and sun roller 33.First rotary part 31 and sun roller 33 are respectively in being centrally located at the roughly cylindric or roughly cylindric of central axis J1.In other words, the first rotary shaft 31 and sun roller 33 are configured in coaxially.Protruding outside from the inside of the first shell 21 upward and to shell 2 of first rotary part 31.Sun roller 33 is connected with the underpart of the first rotary shaft 31.Sun roller 33 is positioned at the inside of shell 2.In addition, sun roller 33 also can be connected with the first rotary shaft 31 by miscellaneous part indirectly.
Clutch shaft bearing 24 is provided with between the outer circumferential face and the bearing cage 211 of the first shell 21 of the first rotary shaft 31.Clutch shaft bearing 24 is positioned at radial outside relative to the first rotary shaft 31.First rotary shaft 31 is supported as rotating relative to the first shell 21 by clutch shaft bearing 24.Thus, the first solid of rotation 3 is supported as rotating centered by central axis J1 by shell 2.Clutch shaft bearing 24 is such as ball bearing.In addition, various gear mechanisms outside ball bearing also can be utilized as clutch shaft bearing 24.
Second solid of rotation 4 comprises the second rotary shaft 41, planet carrier portion 42 and multiple planetary rollers 43.The diameter of the second rotary shaft 41 is larger than the diameter of the first rotary shaft 31.Planet carrier portion 42 comprises the first bracket 421, multiple planet axis portion 422 and the second bracket 423.Second rotary shaft 41 is in being centrally located at the roughly cylindric or roughly cylindric of central axis J1.Protruding outside from the inside of second housing 22 downward to shell 2 of second rotary shaft 41.In other words, the side that the second rotary shaft 41 is contrary with the first rotary shaft 31 is in the axial direction given prominence to from shell 2.Planet carrier portion 42 is configured in shell 2.
First bracket 421 is in being centrally located at the roughly discoideus of central axis J1.First bracket 421 is positioned at the below of multiple planetary rollers 43.The upper end of the second rotary shaft 41 is connected with the first bracket 421.Second bracket 423 is positioned at the top of multiple planetary rollers 43.In other words, the first bracket 421 is positioned at the side of the axis of multiple planetary rollers 43.Second bracket 423 is positioned at the opposite side of the axis of multiple planetary rollers 43.Second rotary shaft 41, first bracket 421 and the second bracket 423 are configured in coaxially centered by central axis J1.
First bracket 421 supports multiple planet axis portion 422 from below.Second bracket 423 supports multiple planet axis portion 422 from top.Multiple planet axis portion 422 is in the radial outside equal angles compartment of terrain configuration in the circumferential of sun roller 33.In the example depicted in figure 1, three planet axis portions 422 are spaced with 120 ° in the circumferential.In FIG, a planet axis portion 422 in multiple planet axis portion 422 is only shown.Multiple planetary rollers 43 also only illustrates one.
Roughly cylindric respectively in the direction towards centrally axis J1 of multiple planet axis portion 422.In the present embodiment, planet axis portion 422 is parallel with central axis J1.Multiple planet axis portion 422 is of similar shape and identical size mutually." centrally the direction of axis J1 " be meant to central shaft to J1 towards the almost parallel direction of axis, need not strictly with parallel to an axis.That is, the central axis in each planet axis portion 422 both can be parallel with central axis J1, also only can to tilt less angle relative to central axis J1.
In driving-force transmission mechanism 1, the first bracket 421 is provided with multiple holes through along the vertical direction.Be inserted into each hole by the bottom in planet axis portion 422, multiple planet axis portion 422 is connected with the first bracket 421.Each planet axis portion 422 is fixed to and can not rotates relative to the first bracket 421.In the axial direction, each planet axis portion 422 be positioned at the position roughly the same with sun roller 33 from the position that the first bracket 421 is given prominence to upward.
Other holes multiple through are along the vertical direction provided with between planet axis portion 422 in the circumference of the first bracket 421.This some holes is fixed in coupling shaft portion 424.Coupling shaft portion 424 gives prominence to upward from the first bracket 421.In the present embodiment, the quantity in coupling shaft portion 424 is three.In the circumferential, coupling shaft portion 424 is between planetary rollers 43.Planet axis portion 422 and coupling shaft portion 424 are located at interval in circumference with 60 °.
Multiple holes of caving in upward from lower surface are provided with at the second bracket 423.Not through second bracket 423 of this some holes.The top in planet axis portion 422 and the top in coupling shaft portion 424 are inserted in this some holes.Be connected with the second bracket 423 by planet axis portion 422 and coupling shaft portion 424, first bracket 421.Planet axis portion 422 and coupling shaft portion 424 play function as the joint connecting the first bracket 421 and the second bracket 423 in the axial direction.
Multiple planetary rollers 43 is supported in shell 2 by multiple planet axis portion 422 respectively.Multiple planetary rollers 43 are configured in the radial outside of sun roller 33 in the circumferential.In the example depicted in figure 1, three planetary rollers 43 are supported by three planet axis portions 422.Each planetary rollers 43 is in surrounding roughly cylindric being positioned at planet axis portion 422.Multiple planetary rollers 43 is of similar shape and identical size mutually.Planetary bearing 45 is provided with between the inner peripheral surface and the outer circumferential face in planet axis portion 422 of planetary rollers 43.Planetary bearing 45 is such as needle bearing.In addition, various gear mechanisms outside needle bearing also can be utilized as planetary bearing 45.By planetary bearing 45, each planetary rollers 43 to be supported as can to rotate centered by the central axis in the centrally direction of axis J1 by planet axis portion 422 in planet carrier portion 42.Below, the central axis in planet axis portion 422 is called " planetocentric axis ".The central axis of planetary rollers 43 is inconsistent with the central axis in planet axis portion 422 in a strict sense, but in order to substantially consistent, by the central axis of planetary rollers 43 also referred to as " planetocentric axis ".By planetary rollers 43 and the first bracket 421 and the second bracket 423, the position in planet axis portion 422 is accurately determined.
The outer circumferential face of each planetary rollers of multiple planetary rollers 43 contacts with the outer circumferential face of sun roller 33.In detail, there is micro-gap between each planetary rollers 43 and sun roller 33.The lubricant oil be filled in shell 2 is there is at this micro-gap.The outer circumferential face of each planetary rollers 43 is contacted with the outer circumferential face of sun roller 33 indirectly by the oil film of lubricant oil.
The second bearing 25 is provided with between the outer circumferential face and the bearing cage 221 of second housing 22 of the second rotary shaft 41.Second bearing 25 is positioned at the radial outside of the second rotary shaft 41.Be supported to can rotate relative to second housing 22 by the second bearing 25, second rotary shaft 41.Thus, the second solid of rotation 4 is supported as rotating centered by central axis J1 by shell 2.Second bearing 25 is such as ball bearing.In addition, various gear mechanisms outside ball bearing also can be utilized as the second bearing 25.
Inside bracket bearing 26 is configured with between the inner peripheral surface of the second bracket 423 and the outer circumferential face of the first rotary shaft 31.Second bracket 423 is supported as rotating relative to the first solid of rotation 3 by inside bracket bearing 26.Conversely, the first solid of rotation 3 comprising sun roller 33 supports as relatively rotating relative to the second bracket 423 centered by central axis J by inside bracket bearing 26.Outrigger bearing 27 is configured with between the outer circumferential face of the second bracket 423 and the inner peripheral surface of the cylindrical part 213 of the first shell 21.Second bracket 423 is supported as rotating relative to the first shell 21 by outrigger bearing 27.Outrigger bearing 27 is inserted into the first shell 21 by Spielpassung.Thus, prevent from acting on unnecessary power to the second bracket 423.Elastomer and the O type ring 7 of ring-type is configured with between the lower surface with the first shell 21 opposed with this upper-end surface of the upper-end surface of the outer ring of outrigger bearing 27.
The rigidity of the second solid of rotation 4 relative to radial load is improved by outrigger bearing 27.By outrigger bearing 27 and inside bracket bearing 26, improve the rigidity of the first solid of rotation 3 relative to radial load.By inside bracket bearing 26, the coaxality of the first solid of rotation 3 and the second solid of rotation 4 easily can be improved.Inside bracket bearing 26 is overlapping diametrically with outrigger bearing 27.
Second bracket 423 is in dual stage cylindrical shape.Second bracket 423 comprises main part 461, top protuberance 462, top plate portion 463 and upper end cylindrical part 464.Main part 461 is in the ring-type centered by central axis J1.Main part 461 is held between inside bracket bearing 26 and outrigger bearing 27.Top protuberance 462 in roughly cylindric, and is given prominence to upward from the inner peripheral portion of main part 461.Top plate portion 463 is roughly dull and stereotyped in the form of a ring, and expands from the upper end of top protuberance 462 to radially inner side.Top protuberance 462 in roughly cylindric, and is given prominence to upward from the inner circumference edge of top plate portion 463.
Top plate portion 463 covers the top of inside bracket bearing 26.Upper end cylindrical part 464 is near the outer circumferential face of the first rotary shaft 31.The top in planet axis portion 422 is cut.Thus, the interference with inside bracket bearing 26 can be avoided in the top in planet axis portion 422.By the position that cuts near the outer circumferential face of inside bracket bearing 26 or contact with the outer circumferential face of inside bracket bearing 26.In shell 2, lubricant oil is present in inside bracket bearing 26, outrigger bearing 27 and the space between the second bracket 423 and the second bearing 25.
Fig. 2 amplifies the sectional view that a part for driving-force transmission mechanism 1 is shown.Inner ring 5 is the roughly cylindric parts being centrally located at central axis J1.Inner ring 5 is configured in the radial outside of the second solid of rotation 4.Inner ring 5 comprises assembly department 51, thinner wall section 52 and press part 53.Assembly department 51 is bottoms of inner ring 5.Assembly department 51 is in the ring-type centered by central axis J1.As shown in Figure 1, bearing cage 221 is bottoms of second housing 22.The lower surface of assembly department 51 contacts with the upper surface of bearing cage 221.The upper surface of assembly department 51 is opposed with the first bracket 421.As shown in Figure 2, the peripheral part of assembly department 51 upward, laterally and top extend.
Thinner wall section 52 extends upward from the outer edge of assembly department 51.Thinner wall section 52 is in the roughly cylindrical shape centered by central axis J1.Thinner wall section 52 is positioned at the roughly radial outside of the first bracket 421.Press part 53 extends upward from the upper end of thinner wall section 52.Press part 53 is in the roughly cylindrical shape centered by central axis J1.The radial thickness of thinner wall section 52 is less than the radial thickness of press part 53.Distance between the lower surface of the first bracket 421 and the upper end of the second bearing 25 is less than the distance between the internal surface of thinner wall section 52 and the outer circumferential face of the first bracket 421.Thereby, it is possible to reduce the axial dimension of driving-force transmission mechanism 1.
As shown in Figure 1, the pin-and-hole 511 caved in upward from lower surface is provided with at assembly department 51.Also the pin-and-hole 223 caved in from upper surface is provided with downwards at the bearing cage 221 of second housing 22.In the present embodiment, pin-and-hole 511,223 is equally spaced respectively arranged with four in the circumferential.Pin 224 is inserted into pin-and-hole 223,511.Thus, even if masterpiece larger in circumference is used for inner ring 5, also prevent inner ring 5 from rotating relative to shell 2.In addition, the second bearing 25 is had the bearing cage 221 of second housing 22 is loosely chimeric.
Inner ring 5 also can be realized by the construction element outside pin-and-hole 223 and pin 224 etc. relative to the rotation of shell 2.Also these structures can be replaced by following structure: be such as provided with recess at shell 2, inner ring 5 is provided with projection.Now, by recess in the circumferential with protuberance contacts, prevent inner ring 5 from rotating.Otherwise, also shell 2 can be provided with projection, inner ring 5 is provided with recess.In other words, by rotation prevention portion, prevent inner ring 5 from rotating relative to shell 2 in the circumferential.Rotation prevention portion can be set by various mode.The rotation prevention portion of preferred inner ring 5 in the circumferential with shell 2 or the location contacts being fixed on shell 2.Thus, prevent inner ring 5 from rotating.
As shown in Figure 2, the inner peripheral surface of press part 53 contacts with the outer circumferential face of planetary rollers 43.In detail, between each planetary rollers 43 and inner ring 5, there is micro-gap.The lubricant oil be filled in shell 2 is there is at this micro-gap.The outer circumferential face of each planetary rollers 43 is contacted with press part 53 indirectly by the oil film of lubricant oil.At the circumferential position that press part 53 contacts with planetary rollers 43, press part 53 is out of shape a little to radial outside.With its imitation, also there is resiliently deformable in thinner wall section 52.Utilize the recuperability of thinner wall section 52 and press part 53, multiple planetary rollers 43 presses to sun roller 33 by press part 53.That is, utilize the resiliently deformable of inner ring 5, multiple planetary rollers 43 presses to sun roller 33 by press part 53.
At the radial outside of multiple planetary rollers 43, inner ring 5 is separated diametrically with shell 2.Thus, can there is resiliently deformable in inner ring 5.Gap between inner ring 5 and shell 2 is very little.Preferably the radial width in this gap is less than the radial width of thinner wall section 52.That is, the radial width in this gap is less than the thickness of the most thin section of inner ring 5.
First make contact 61 is points that inner ring 5 contacts with planetary rollers 43.As long as thinner wall section 52 is between first make contact 61 and the inner peripheral surface 512 of assembly department 51, just can be arranged by various mode.Below, inner peripheral surface 512 is called " inner peripheral surface 512 is installed ".The radial thickness of thinner wall section 52 is less than the radial thickness of the press part 53 at first make contact 61 place.In addition, also thinner wall section 52 can be set by the depression at least partially of the outer circumferential face of inner ring 5.Also thinner wall section 52 can be set by the inner peripheral surface of inner ring 5 and outer circumferential face depression.
By being provided with thinner wall section 52, the resiliently deformable of inner ring 5 can be made to concentrate on thinner wall section 52.Thus, press part 53 is suppressed to tilt relative to central axis J1.Consequently, press part 53 can be made easily to be positioned at desired position in the axial direction with the first make contact 61 of planetary rollers 43.When resiliently deformable occurs inner ring 5, contact position reduces to the mobile of axis.Therefore, it is possible to shorten the axial length of planetary rollers 43.
In driving-force transmission mechanism 1, the outer circumferential face 251 that inner peripheral surface 512 is fixed on the second bearing 25 is installed.Second bearing 25 is the ring rigid bearings being fixed with inner ring 5.Preferred assembly department 51 is fixed on the outer circumferential face of the second bearing 25 by press-in or shrink fit.By these methods, do not add other parts, just easily inner ring 5 can be fixed on the second bearing 25.Thereby, it is possible to improve inner ring 5 relative to the coaxality of the second solid of rotation 4 comprising planetary rollers 43 by simple structure.
Suppose to be installed in shell 2 in inner ring 5, and by shell 2 attachment face determine inner ring 5 central axis position and towards time, between the attachment face and the inner peripheral surface of bearing cage 221 of shell 2, require higher coaxality.Consequently, the manufacture cost of shell 2 is increased.When the coaxality of inner ring 5 and the second solid of rotation 4 is lower, the second solid of rotation 4 is made to rotate more difficult with constant speed.On the other hand, in driving-force transmission mechanism 1, the outer circumferential face 251 of the second bearing 25 is utilized to determine position and the direction of the central axis of inner ring 5.Therefore, it is possible to reduce the manufacture cost of driving-force transmission mechanism 1.
Multiple planetary rollers 43 contacts at first make contact 61 with inner ring 5.The diameter of the inner circumferential of the inner ring 5 at first make contact 61 place is larger than the diameter of the outer circumferential face of the second bearing 25.Thus, the easy miniaturization of the external diameter of the bottom of driving-force transmission mechanism 1.
In fig. 2, the first make contact 61 of each planetary rollers 43 with inner ring 5 and the second point of contact 62 of each planetary rollers 43 and sun roller 33 is represented with solid circle signs.In fact, first make contact 61 and the second point of contact 62 have size to a certain degree.First pressing force vector V 1 represents the first pressing force acting on each planetary rollers 43 from inner ring 5 in first make contact 61.Second pressing force vector V 2 represents the second pressing force acting on each planetary rollers 43 from sun roller 33 in the second point of contact 62.The first pressing force vector V 1 and the second pressing force vector V 2 is represented with arrow.
In the axial direction, the position of the first make contact 61 of each planetary rollers 43 is different from the position of the second point of contact 62 of each planetary rollers 43.In addition, when planet axis portion 422 tilts to J1 relative to central shaft, in the explanation about power described later, strictly speaking, axially with corresponding to the direction parallel with the planetocentric axis J2 in planet axis portion 422.But planet axis portion 422 tilts a little.Therefore, these need not strictly be distinguished.In the example depicted in figure 1, in the axial direction, the second point of contact 62 than first make contact 61 near the first bracket 421.In the axial direction, the position of the second point of contact 62 and the center of planetary rollers 43 roughly consistent.In the axial direction, first make contact 61 is between the axial centre and the upper end of planetary rollers 43 of planetary rollers 43.
At first make contact 61 and the second point of contact 62 place, comprise the sectional shape of the outer circumferential face of each planetary rollers 43 in the face of central axis J1 convexly.In other words, in each planetary rollers 43, the sectional shape comprising first make contact 61 place of the outer circumferential face of each planetary rollers 43 in the face of first make contact 61 and central hub axis J in the radial direction centered by planetocentric axis J2 in the convex to radial outside.The sectional shape comprising the second point of contact 62 place of the outer circumferential face of each planetary rollers 43 in the face of the second point of contact 62 and central axis J1 in the radial direction centered by planetocentric axis J2 in the convex to radial outside.In fact, the longitudinal section of outer circumferential face is the convex of arc-shaped a little at first make contact 61 and the second point of contact 62 place.Therefore, convex form is not shown in fig. 2.
The external diameter of planetary rollers 43 is maximum in the axial approximate center of planetary rollers 43.The external diameter of planetary rollers 43 is the distance between the outer circumferential face of each planetary rollers 43 and planetocentric axis J2 in the radial direction centered by planetocentric axis J2.The external diameter of planetary rollers 43 leaves and reduces gradually along with the approximate centre of the planet axial direction from planetary rollers 43.
In inner ring 5, the diametrically top of the inner peripheral surface of press part 53 reduces gradually.Because the decrease of this diameter is less, therefore not shown in Figure 2.Inner peripheral surface due to press part 53 is plane of inclination, therefore, it is possible to easily make the axial position of first make contact 61 different from the axial position of the second point of contact 62.And, the axial distance of first make contact 61 and the second point of contact 62 only can be changed in design by the tilt angle of the inner peripheral surface changing press part 53.At first make contact 61 place, also can change from inner ring 5 act on the power of planetary rollers 43 towards.That is, the size of the power that planetary rollers 43 is tilted easily is changed in design.Thereby, it is possible to easily adjust the balance of torque transfer efficiency and back clearance.
The diameter of the inner peripheral surface of press part 53 need not be made to gradually change in the entire axial length of press part 53.The diameter of the inner peripheral surface of press part 53 also can reduce upward gradually.If usually express, then at first make contact 61 place, the diameter of the inner peripheral surface of inner ring 5 reduces gradually along with the side to axis or increases gradually.In addition, not there is plane of inclination at the inner peripheral surface of press part 53, and inner ring 5 there occurs resiliently deformable state under, also can do following design: make the axial position of first make contact 61 roughly consistent with the axial position of the second point of contact 62.
When driving-force transmission mechanism 1 is used as speed reducer, sun roller 33 and the first rotary shaft 31 together rotate centered by central axis J1.In other words, the first solid of rotation 3 rotates centered by central axis J1.Micro-gap is there is between sun roller 33 and each planetary rollers 43.Lubricant oil is had at this micro-gap.By the rotation of sun roller 33, produce friction at this lubricant oil.By this friction, each planetary rollers 43 rotates centered by planetocentric axis J2.Micro-gap is there is between each planetary rollers 43 and inner ring 5.Lubricant oil is there is at this micro-gap.By the rotation of each planetary rollers 43, produce friction at this lubricant oil.Inner ring 5 is fixed on shell 2 indirectly.Therefore, by this friction, multiple planetary rollers 43 rotates centered by central axis J1.
In the following description, the rotation centered by the planetocentric axis J2 of each planetary rollers 43 is called " rotation ".Rotation centered by the central axis J1 of multiple planetary rollers 43 is called " revolution ".As mentioned above, the first bracket 421 and the second bracket 423 are connected with multiple planetary rollers 43 by multiple planet axis portion 422.First rotary shaft 31 is the high speed shafts relative to the relative High Rotation Speed of the second rotary shaft 41.Second rotary shaft 41 is the lower velocity shafts than the first rotary shaft 31 low speed rotation.Second rotary shaft 41 is connected with the first bracket 421.Therefore, along with the revolution of multiple planetary rollers 43, the first bracket 421, second bracket 423 and the second rotary shaft 41 also rotate centered by central axis J1.That is, the second solid of rotation 4 rotates centered by central axis J1.
When driving-force transmission mechanism 1 is used as booster engine, contrary with the situation being used as speed reducer, the second rotary shaft 41, first bracket 421 of the second solid of rotation 4, multiple planetary rollers 43 and the second bracket 423 rotate centered by central axis J1.The rotation by the friction produced during revolution and between inner ring 5 of each planetary rollers 43.By the rotation of each planetary rollers 43, produce between each planetary rollers 43 and sun roller 33 and rub.By this friction, the sun roller 33 of the first solid of rotation 3 and the first rotary shaft 31 rotate centered by central axis J1.
Thus, no matter be driving-force transmission mechanism 1 be used as the situation of speed reducer or be used as the situation of booster engine, between the first solid of rotation 3 and the second solid of rotation 4, the transmission of power realized by rubbing all is carried out.
As shown in Figure 2, in each planetary rollers 43, in the axial direction, the position of first make contact 61 is different from the position of the second point of contact 62.Thus, the central axis of each planetary rollers 43 tilts a little relative to the central axis in planet axis portion 422 in a strict sense.Consequently, the upper end portion of the inner peripheral surface of planetary rollers 43 is pressed against the position of the radial outside in the outer circumferential face in planet axis portion 422 centered by central axis J1 across planetary bearing 45.The underpart of the inner peripheral surface of planetary rollers 43 is pressed against the position of the radially inner side in the outer circumferential face in planet axis portion 422 centered by central axis J1 across planetary bearing 45.
In the axial direction, the position of first make contact 61 and the position of the second point of contact 62 also can be contrary.If usually express, then the one in the upper end portion of the inner peripheral surface of planetary rollers 43 and underpart is pressed against the position of the radial outside in the outer circumferential face in planet axis portion 422 centered by central axis J1 across planetary bearing 45.Another one in the upper end portion of the inner peripheral surface of planetary rollers 43 and underpart is pressed against the position of the radially inner side in the outer circumferential face in planet axis portion 422 centered by central axis J1 across planetary bearing 45.Consequently, planetary rollers 43 tilts relative to planet axis portion 422.Therefore, in driving-force transmission mechanism 1, the back clearance between the planetary rollers 43 in planet axis portion 422 and rotation can be reduced.
As shown in Figure 2, straight line L1 is the imaginary straight line connecting first make contact 61 and the second point of contact 62.Comprise planetocentric axis J2, first make contact 61 and the second point of contact 62 face each planetary rollers 43 cross section in, the first pressing force vector V 1 relative to straight line L1 to lopsidedness.Second pressing force vector V 2 tilts to opposite side relative to straight line L1.In the example shown in Fig. 2, the first pressing force vector V 1 upwards rolls tiltedly relative to straight line L1.Second pressing force vector V 2 rolls downwards tiltedly relative to straight line L1.First pressing force vector V 1 and the second pressing force vector V 2 almost parallel.
Thus, in each planetary rollers 43, the first pressing force vector V 1 and the second pressing force vector V 2 clamp straight line L1 and mutually tilt inversely.Thereby, it is possible to make the component in the direction vertical with planetocentric axis J2 of the first pressing force vector V 1 large with point quantitative change in the direction of the vertical with planetocentric axis J2 of the second pressing force vector V 2.
As mentioned above, at first make contact 61 place of each planetary rollers 43, the sectional shape of the outer circumferential face of each planetary rollers 43 in the face of central axis J1 is comprised convexly.At first make contact 61 place, necessarily do not make the sectional shape of the outer circumferential face of planetary rollers 43 convexly.The sectional shape comprising the inner peripheral surface of the press part 53 of the inner ring 5 in the face of central axis J1 also can be convexly.In other words, at first make contact 61 place of each planetary rollers 43, in the sectional shape of the inner peripheral surface of the press part 53 in the sectional shape comprising the outer circumferential face of each planetary rollers 43 in the face of central axis J1 and the face comprising central axis J1, the sectional shape of at least one convexly.Thus, in planetary rollers 43, to planet axial direction, situation is inferior a little movably, and the position of first make contact 61 can be made successfully to change.
In driving-force transmission mechanism 1, at the second point of contact 62 place of each planetary rollers 43, comprise the sectional shape of the outer circumferential face of each planetary rollers 43 in the face of central axis J1 convexly.At the second point of contact 62 place, the sectional shape of the outer circumferential face of planetary rollers 43 is not necessarily convexly.The sectional shape comprising the outer circumferential face of the sun roller 33 in the face of central axis J1 also can be convexly.In other words, at the second point of contact 62 place of each planetary rollers 43, in the sectional shape of the outer circumferential face of the sun roller 33 in the sectional shape comprising the outer circumferential face of each planetary rollers 43 in the face of central axis J1 and the face comprising central axis J1, the sectional shape of at least one convexly.Thus, in planetary rollers 43, to planet axial direction, situation is inferior a little movably, and the position of the second point of contact 62 can be made successfully to change.
Fig. 3 amplifies the longitudinal section near the border that the first shell 21 and second housing 22 are shown.First shell 21 is positions of the first solid of rotation 3 side of shell 2.Second housing 22 is positions of the second solid of rotation 4 side of shell 2.First shell 21 contacts in the axial direction with second housing 22.The upper end of inner ring 5 is positioned at the position on the lower, upper end than second housing 22.Therefore, the upper end of inner ring 5 is positioned at second housing 22.The upper end of inner ring 5 is ends of the side contrary in the axial direction with the installation inner peripheral surface 512 (with reference to Fig. 2) of inner ring 5.
In the final operation of the assembling of driving-force transmission mechanism 1, carry out the fastening of the first shell 21 and second housing 22.The upper end of inner ring 5 is positioned at second housing 22.Therefore, reliably avoid the first shell 21 to contact with inner ring 5.At the first shell 21 with the terminal operation of second housing 22, be adjusted to consistent by the central axis of worker's the first solid of rotation 3 the most at last exactly with the central axis of the second solid of rotation 4.Now, by O type ring 7 (with reference to Fig. 1), the outer shroud of outrigger bearing 27 is pressed on the pretightening force effect of below, the radial clearance supporting the second bearing 25 of the second solid of rotation 4 diminishes.Thus, the degrees of freedom of the axle core of the second solid of rotation 4 disappears.Consequently, the central axis of the first shell 21 and the central axes of second housing 22 can be made, can easily make the central axis of the first solid of rotation 3 consistent with the central axis of the second solid of rotation 4.
In driving-force transmission mechanism 1, in order to reduce axial dimension, preferred inner ring 5 diminishes with the axial clearance of outrigger bearing 27 as far as possible.Therefore, the first shell 21 is overlapping diametrically with shell pedestal bearing 27 with the border between second housing 22.The internal diameter of the upper end of second housing 22 is slightly larger than the diameter of the outer circumferential face of outrigger bearing 27.Thereby, it is possible to form gap between the outer circumferential face and the inner peripheral surface of second housing 22 of outrigger bearing 27.That is, enough and to spare can be set between the first shell 21 and second housing 22, adjust relative position diametrically.
Fig. 4 is the longitudinal section of another example that planetary rollers 43 is shown.In the diagram the part different from the structure shown in Fig. 2 is only shown.In planetary rollers 43, the diameter on top is less than the diameter of bottom.The press part 53 of inner ring 5 and the upper contact of planetary rollers 43.The lower contacts of sun roller 33 and planetary rollers 43.In planetary rollers 43, the diameter on top also can be larger than the diameter of bottom.Press part 53 and sun roller 33 can be designed to arbitrarily and the upper contact of planetary rollers 43 or and lower contacts.
The structure shown in another structure with Fig. 1 of the driving-force transmission mechanism 1 of Fig. 4 is identical.The diametrically axial side of the inner peripheral surface of press part 53 increases gradually or reduces.And, the first pressing force vector at first make contact and the second point of contact place and the relation of the second pressing force vector also identical with the relation shown in Fig. 2.
Fig. 5 is the longitudinal section of another installation example that inner ring 5 is shown.In Figure 5, inner ring 5 presses the order contrary with Fig. 1 from upper arrangement assembly department 51, thinner wall section 52 and press part 53.The installation inner peripheral surface 512 of assembly department 51 is fixed on the outer circumferential face of clutch shaft bearing 24.In the structure of Fig. 5, omit the second bracket 423, inside bracket bearing 26 and the outrigger bearing 27 shown in Fig. 1.Driving-force transmission mechanism 1 shown in other structure with Fig. 1 is identical.
In the driving-force transmission mechanism 1 shown in Fig. 5, the outer circumferential face of clutch shaft bearing 24 is utilized easily to obtain the higher coaxality of the first solid of rotation 3 and inner ring 5.By adjustment during assembling, make the central axis of the first solid of rotation 3 consistent exactly with the central axis of the second solid of rotation 4.Therefore, higher coaxality is obtained between the second solid of rotation 4 and inner ring 5 after assembling.
Ring rigid bearing comprises the outer circumferential face of the installation inner peripheral surface 512 being fixed with inner ring 5.As shown in Figure 5, ring rigid bearing also can be clutch shaft bearing 24.And the outrigger bearing 27 of Fig. 1 also can be used as ring rigid bearing.If usually express, then ring rigid bearing is the arbitrary bearing supporting the first solid of rotation 3 or the second solid of rotation 4 relative to shell 2.Be fixed on the outer circumferential face of ring rigid bearing by the installation inner peripheral surface 512 of inner ring 5, easily obtain the higher coaxality between the second solid of rotation 4 and inner ring 5.
Even if in the example as shown in fig. 5, also preferably inner ring 5 is fixed in clutch shaft bearing 24 by press-in or shrink fit.Preferred inner ring 5 is provided with rotation prevention portion between the first shell 21.The diametrically axial side of the inner peripheral surface of press part 53 increases gradually or reduces.The first pressing force vector at first make contact and the second point of contact place and the relation of the second pressing force vector also identical with the structure shown in Fig. 2.The diameter of the inner circumferential of the inner ring 5 at first make contact place is larger than the diameter of the inner peripheral surface of assembly department 51.
Various change can be carried out in above-mentioned driving-force transmission mechanism 1.
Shell 2 also can be made up of the parts of more than three.The quantity of clutch shaft bearing 24 and the quantity of the second bearing 25 also can change aptly.Other bearings supporting the first solid of rotation 3 or the second solid of rotation 4 also can be arranged at driving-force transmission mechanism 1.
Inner ring 5 in the form of a ring, is not limited to cylindrical shape.As long as elastic strain occurs inner ring 5, also thinner wall section 52 can not be set in inner ring 5.The assembly department 51 of inner ring 5 need not be fixed on the complete cycle of the outer circumferential face of ring rigid bearing.Such as, also the inner peripheral portion of assembly department 51 can be provided with the groove extended abreast vertically, and assembly department 51 partly contacts with ring rigid bearing.Inner ring 5 also can utilize binder with the fixing of ring rigid bearing.Such as, also by press-in and binder, inner ring 5 can be fixed on ring rigid bearing.
In planet carrier portion 42, joint connects the first bracket 421 and the second bracket 423 in the axial direction.Joint also can be planet axis portion 422 or be coupling shaft portion 424.The quantity of planetary rollers is not limited to three.In planet carrier portion 42, also can omit the first bracket 421 or the second bracket 423.When omission first bracket 421, such as the second rotary shaft 41 is connected with the second bracket 423.
In above-mentioned driving-force transmission mechanism, the first rotary shaft 31 and the second rotary shaft 41 also can be configured in shell 2.First rotary shaft 31 and the second rotary shaft 41 necessarily not outstanding to mutually opposite direction from shell 2.Such as, in the first rotary shaft 31 and the second rotary shaft 41, can the parts of side be also hollow, the parts of opposite side be positioned at the radially inner side of the parts of this side.
In the second solid of rotation 4, planetary rollers 43 is fixed on planet axis portion 422.Also planetary bearing 45 can be provided with between planet axis portion 422 and the first bracket 421 or between planet axis portion 422 and the second bracket 423.In other words, planetary rollers 43 can be supported as rotating by planet carrier portion 42 by planet axis portion 422 and planetary bearing 45.Planetary rollers 43 and planet axis portion 422 together rotate.
The structure of above-mentioned mode of execution and each variation can be appropriately combined in the scope not producing contradiction.
Driving-force transmission mechanism involved by the utility model can be used as speed reducer or booster engine in the various devices such as precision processing machine or 3D measuring device.Driving-force transmission mechanism involved by the utility model also can be used as other purposes.
Claims (12)
1. a driving-force transmission mechanism, described driving-force transmission mechanism comprises:
Shell;
First solid of rotation;
Clutch shaft bearing, described clutch shaft bearing can by described first solid of rotation supporting for can rotate relative to described shell centered by central axis;
Second solid of rotation, described second solid of rotation carries out the transmission of power realized by rubbing between described first solid of rotation;
Second bearing, described second solid of rotation supports as can rotate relative to described shell centered by described central axis by described second bearing; And
The inner ring of ring-type, described inner ring is configured in the radial outside of described second solid of rotation,
The feature of described driving-force transmission mechanism is,
Described first solid of rotation has:
First rotary shaft, described first rotary shaft be centrally located at described central axis; And
Sun roller, described sun roller together rotates with described first rotary shaft in described shell,
Described second solid of rotation has:
Multiple planetary rollers, in described shell, described multiple planetary rollers is configured in the radial outside of described sun roller in the circumferential, and the outer circumferential face of each planetary rollers contacts with the outer circumferential face of described sun roller and the inner peripheral surface of described inner ring;
Planet carrier portion, it is can to rotate centered by the planetocentric axis in the direction along described central axis that described multiple planetary rollers supports by described planet carrier portion in described shell; And
Second rotary shaft, described second rotary shaft be centrally located at described central axis, and to be connected with described planet carrier portion,
Utilize the resiliently deformable of described inner ring, described multiple planetary rollers is pressed by described sun roller,
The installation inner peripheral surface of described inner ring is fixed on the outer circumferential face of ring rigid bearing, and described ring rigid bearing is the arbitrary bearing relative to the first solid of rotation described in described outer casing supporting or described second solid of rotation.
2. driving-force transmission mechanism according to claim 1, is characterized in that,
Described inner ring is fixed on the described outer circumferential face of described ring rigid bearing by press-in or shrink fit.
3. driving-force transmission mechanism according to claim 1 and 2, is characterized in that,
Described inner ring comprises the rotation prevention portion of the rotation of the circumference preventing described inner ring relative to described shell.
4. driving-force transmission mechanism according to claim 1 and 2, is characterized in that,
Described inner ring comprises thinner wall section, and between the point of contact that described thinner wall section contacts with described multiple planetary rollers in described inner ring and described installation inner peripheral surface, the radial thickness of described thinner wall section is less than the radial thickness at point of contact place.
5. driving-force transmission mechanism according to claim 1 and 2, is characterized in that,
At each planetary rollers of described multiple planetary rollers and the first make contact place of described inner ring, the diameter of the inner peripheral surface of described inner ring reduces gradually along with the side to axis or increases,
In the axial direction, described first make contact and described each planetary rollers are positioned at different positions from the second point of contact of described sun roller.
6. driving-force transmission mechanism according to claim 1 and 2, is characterized in that,
In the axial direction, each planetary rollers of described multiple planetary rollers is positioned at different positions from the second point of contact of the first make contact of described inner ring and described each planetary rollers and described sun roller,
About each planetary rollers, in the cross section in face comprising the planetocentric axis of described planetary rollers, described first make contact and described second point of contact, represent act on the first pressing force of described each planetary rollers from described inner ring the first pressing force vector relative to the straight line making described first make contact be connected with described second point of contact to lopsidedness, represent that the second pressing force vector acting on the second pressing force of described each planetary rollers from described sun roller tilts to opposite side relative to described straight line.
7. driving-force transmission mechanism according to claim 1 and 2, is characterized in that,
Described shell has:
First shell, described first shell is positioned at described first and rotates side; And
Second housing, described second housing is located at and axially rotates side with described second of described first housing contacts,
Described second bearing is described ring rigid bearing,
Described inner ring be positioned at described second housing with described installation inner peripheral surface in the end of the side of axial opposed.
8. driving-force transmission mechanism according to claim 1 and 2, is characterized in that,
Described planet carrier portion has:
First bracket, described first bracket is positioned at the side of the axis of described multiple planetary rollers, and is connected with described second rotary shaft;
Second bracket, described second bracket is positioned at the opposite side of the axis of described multiple planetary rollers; And
Joint, described joint connects described first bracket and described second bracket in the axial direction,
Described planet carrier portion also has outrigger bearing, described outrigger bearing between described second bracket and described shell by described second bearing bracket for can rotate centered by described central axis.
9. driving-force transmission mechanism according to claim 8, is characterized in that,
Described second bearing is described ring rigid bearing,
At the radial outside of described multiple planetary rollers, described inner ring is separated diametrically with described shell.
10. driving-force transmission mechanism according to claim 9, is characterized in that,
Described shell has:
First shell, described first shell is positioned at described first and rotates side; And
Second housing, described second housing is located at and axially rotates side with second of described first housing contacts,
Described first shell and the border between described second housing are overlapping with described outrigger bearing diametrically,
Gap is there is between the outer circumferential face of described outrigger bearing and the inner peripheral surface of described second housing.
11. driving-force transmission mechanisms according to claim 8, is characterized in that,
Described driving-force transmission mechanism also has inside bracket bearing, and described sun roller supports as relatively can rotate relative to described second bracket centered by described central axis by described inside bracket bearing.
12. driving-force transmission mechanisms according to claim 1 and 2, is characterized in that,
Described multiple planetary rollers is larger than the diameter of the described outer circumferential face of described ring rigid bearing with the diameter of the inner circumferential of the described inner ring at the point of contact place of described interior loop contacts.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014211751A JP6372752B2 (en) | 2014-10-16 | 2014-10-16 | Traction power transmission device |
| JP2014-211751 | 2014-10-16 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN205155058U true CN205155058U (en) | 2016-04-13 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520784853.9U Expired - Fee Related CN205155058U (en) | 2014-10-16 | 2015-10-12 | Friction power transmission device |
| CN201510655147.9A Active CN105526322B (en) | 2014-10-16 | 2015-10-12 | Driving-force transmission mechanism |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510655147.9A Active CN105526322B (en) | 2014-10-16 | 2015-10-12 | Driving-force transmission mechanism |
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| Country | Link |
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| JP (1) | JP6372752B2 (en) |
| CN (2) | CN205155058U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105526322A (en) * | 2014-10-16 | 2016-04-27 | 日本电产新宝株式会社 | Frictional power transmission device |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP7380979B2 (en) * | 2018-05-31 | 2023-11-15 | ニデックドライブテクノロジー株式会社 | Motorized transmission and trolley drive unit |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57163044U (en) * | 1981-04-08 | 1982-10-14 | ||
| JPH06341501A (en) * | 1993-06-03 | 1994-12-13 | Mitsubishi Heavy Ind Ltd | Planetary roller reduction gear |
| EP2187096B1 (en) * | 2008-11-14 | 2012-09-12 | Sankyo Seisakusho Co. | Planetary rolling rotation transmission device |
| JP5508197B2 (en) * | 2010-08-30 | 2014-05-28 | 日本電産シンポ株式会社 | transmission |
| JP6372752B2 (en) * | 2014-10-16 | 2018-08-15 | 日本電産シンポ株式会社 | Traction power transmission device |
-
2014
- 2014-10-16 JP JP2014211751A patent/JP6372752B2/en active Active
-
2015
- 2015-10-12 CN CN201520784853.9U patent/CN205155058U/en not_active Expired - Fee Related
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105526322A (en) * | 2014-10-16 | 2016-04-27 | 日本电产新宝株式会社 | Frictional power transmission device |
| CN105526322B (en) * | 2014-10-16 | 2018-06-26 | 日本电产新宝株式会社 | Driving-force transmission mechanism |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6372752B2 (en) | 2018-08-15 |
| CN105526322B (en) | 2018-06-26 |
| CN105526322A (en) | 2016-04-27 |
| JP2016080064A (en) | 2016-05-16 |
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