CN105570409A - Friction power transmission device - Google Patents
Friction power transmission device Download PDFInfo
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- CN105570409A CN105570409A CN201510701268.2A CN201510701268A CN105570409A CN 105570409 A CN105570409 A CN 105570409A CN 201510701268 A CN201510701268 A CN 201510701268A CN 105570409 A CN105570409 A CN 105570409A
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- shell
- bearing
- planetary rollers
- force transmission
- rotation
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 62
- 230000007246 mechanism Effects 0.000 claims description 62
- 239000007787 solid Substances 0.000 claims description 55
- 230000002093 peripheral effect Effects 0.000 claims description 34
- 230000008878 coupling Effects 0.000 claims description 18
- 238000010168 coupling process Methods 0.000 claims description 18
- 238000005859 coupling reaction Methods 0.000 claims description 18
- 238000009826 distribution Methods 0.000 claims description 15
- 230000003287 optical effect Effects 0.000 claims description 4
- 230000005489 elastic deformation Effects 0.000 abstract 1
- 238000003825 pressing Methods 0.000 description 18
- 239000000314 lubricant Substances 0.000 description 7
- 239000003638 chemical reducing agent Substances 0.000 description 5
- 238000013461 design Methods 0.000 description 5
- 238000009434 installation Methods 0.000 description 5
- 230000008859 change Effects 0.000 description 4
- 239000011230 binding agent Substances 0.000 description 3
- 230000002265 prevention Effects 0.000 description 3
- 238000003754 machining Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000012360 testing method Methods 0.000 description 2
- 241001515806 Stictis Species 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 230000003467 diminishing effect Effects 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
- 238000012856 packing Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000008054 signal transmission Effects 0.000 description 1
- 238000012546 transfer Methods 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
- 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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- 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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
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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
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H57/082—Planet carriers
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Friction Gearing (AREA)
- Transmission And Conversion Of Sensor Element Output (AREA)
Abstract
The invention provides a friction power transmission device, and the device comprises a housing, a first rotating body, a first bearing, and a second rotating body. The second rotating body and the first rotating body carry out power transmission through friction. The device also comprises a second bearing, an annular inner ring, and a coder. The first rotating body is provided with a first rotating shaft part and a solar roller. The second rotating body is provided with a plurality of planetary rollers, a planetary rack part, and a second rotating shaft part. The plurality of planetary rollers are pressed towards the solar roller through the elastic deformation of the inner ring. The planetary rack part is provided with a first planetary rack located at an output side, a second planetary rack located at an input side, and a connection part which connects the first and second planetary racks in an axial direction. The rotating part of the coder is provided with the second planetary rack.
Description
Technical field
The present invention relates to a kind of driving-force transmission mechanism.
Background technique
The outer circumferential face in the past had to sun roller presses multiple planetary rollers, and utilizes the friction between roller to carry out the driving-force transmission mechanism of transferring power.In driving-force transmission mechanism, compared with the gear transmission mechanism of the multiple gear of engagement, reduce the vibration & noise caused by back clearance.
In the speed reducer disclosed in Japanese Laid-Open Patent Publication 2003-301905 publication, be provided with speed detecting mechanism.Speed detecting mechanism has pulse plectane and comprises the photodetector of light projector and light receiver.Pulse plectane is fixed on the side to the planet carrier that planetary rollers supports.At planet carrier, place is fixed with output shaft.
In the speed reducer disclosed in Japanese Laid-Open Patent Publication 2002-327815 publication, the magnetic paper tinsel of speed detecting mechanism is arranged at output shaft.Magnetic paper tinsel is between the clutch shaft bearing supported output shaft and the second bearing.
But in driving-force transmission mechanism, as illustrated in Japanese Laid-Open Patent Publication 2003-301905 publication and Japanese Laid-Open Patent Publication 2002-327815 publication, in the past, encoder was configured in output shaft side.Thus, skidding even if produce when utilizing friction to carry out transmitting torque, also can obtain the rotation of output exactly, and can accurately control input side.
But, when encoder being configured in output shaft side, to power to encoder or the distribution conducted from the signal of encoder is connected with drive unit from output shaft side around to input shaft side.Consequently, not only distribution is elongated, and considers the problem that also may exist and make the setting position of driving-force transmission mechanism limited that detours of distribution.
Summary of the invention
The object of the invention is to, in driving-force transmission mechanism, make the connection between encoder and drive unit become easy by simple structure.
To deal with problems required technological scheme
Driving-force transmission mechanism involved by the illustrative mode of execution of the present invention comprises: shell; First solid of rotation; Clutch shaft bearing, the first solid of rotation supports as can rotate centered by central axis relative to shell by described clutch shaft bearing; Second solid of rotation, described second solid of rotation carries out transmission of power by friction between the first solid of rotation; Second bearing, the second solid of rotation supports as can rotate centered by central axis relative to shell by described second bearing; Inner ring, described inner ring in the form of a ring, and is configured at the radial outside of the second solid of rotation; And encoder, described encoder detects the rotation of the second solid of rotation, and has fixing part and rotary part.First solid of rotation has: the first rotary shaft, and central axis is positioned at the position at the center of described first rotary shaft, and described first rotary shaft is given prominence to from shell towards the input side of the side as axis; And sun roller, described sun roller together rotates with the first rotary shaft in the enclosure.Planetary rollers in the enclosure and circumferentially configure at the radial outside of sun roller.Second solid of rotation has: planetary rollers, and described planetary rollers is multiple, and the outer circumferential face of each planetary rollers contacts with the outer circumferential face of sun roller and the inner peripheral surface of inner ring; Planet carrier portion, described planet carrier portion in the enclosure, by the supporting of multiple planetary rollers for can to rotate centered by the planetocentric axis in the centrally direction of axis; And second rotary shaft, central axis is positioned at the position at the center of described second rotary shaft, and described second rotary shaft is connected with planet carrier portion, and gives prominence to from shell towards the outlet side of the opposite side as axis.Multiple planetary rollers utilizes the resiliently deformable of inner ring to be pressed by towards sun roller.Planet carrier portion has: the first row carrier, and described first planet chord position is in the outlet side of multiple planetary rollers; Second planet carrier, described second planet carrier is positioned at the input side of multiple planetary rollers; And joint, the first row carrier is connected with the second planet carrier by described joint in the axial direction.The rotary part of encoder is arranged at the second planet carrier.
Further, described driving-force transmission mechanism also has outer row carrier bearing, and the second planet carrier supports as can rotate centered by central axis by outer row carrier bearing between the second planet carrier and shell.
Further, described driving-force transmission mechanism also has inner row carrier bearing, and sun roller supports as relatively can rotate centered by central axis relative to the second planet carrier by inner row carrier bearing.
Further, outer row carrier bearing is overlapping diametrically with inner row carrier bearing at least partially.
Further, shell has: first shell on the first rotation side; And second rotates the second housing on side, second housing directly or indirectly contacts in the axial direction with the first shell, the end face of the input side of inner ring is positioned at second housing, first shell is overlapping diametrically with outer row carrier bearing with the border between second housing, between the outer circumferential face and the inner peripheral surface of second housing of outer row carrier bearing, have gap.
Further, the second planet carrier comprises cylindrical portion, and described cylindrical portion extends along the outer circumferential face of the first rotary shaft towards input side, and the fixing part of encoder is installed on the first shell directly or indirectly, and the rotary part of encoder is installed on the outer circumferential face of cylindrical portion.
Further, the second planet carrier also comprises the vertical surface perpendicular to central axis expansion, and the rotary part of encoder is installed on vertical surface.
Further, the end of the input side of shell comprises the assembly department for being connected with drive unit, and assembly department is overlapping diametrically with the rotary part of encoder.
Further, the distribution of encoder is drawn from the end of the input side of shell, or the terminal arrangement be connected with distribution is in the end of the input side of shell.
Further, planet carrier portion also comprises multiple planet axis portion, described planet axis portion respectively towards the direction of centrally axis, multiple planetary rollers by the supporting of multiple planet axis portions for rotating, joint be multiple planet axis portions at least partially.
Further, planet carrier portion also comprises multiple coupling shaft portion, the direction of this coupling shaft portion respectively towards centrally axis between multiple planetary rollers, joint be multiple coupling shaft portions at least partially.
Further, above-mentioned encoder is optical encoders, angle sensors.
A mode of execution according to the application, can, with simple structure, make the connection between encoder and drive unit become easy.
With reference to accompanying drawing, by the detailed description of the following preferred embodiment for the present invention, above-mentioned and other key element of the present invention, feature, step, feature and advantage more clearly can be understood.
Accompanying drawing explanation
The longitudinal sectional view of the driving-force transmission mechanism of Fig. 1 involved by a mode of execution.
Fig. 2 amplifies the longitudinal sectional view that planetary rollers and the position near it are shown.
Fig. 3 amplifies the longitudinal sectional view that the position of the vicinity of encoder is shown.
Fig. 4 amplifies the longitudinal sectional view near illustrating between the first shell and second housing border.
Fig. 5 is the longitudinal sectional view of another example that planetary rollers is shown.
Fig. 6 is the figure of another installation example of the rotary part that encoder is shown.
Fig. 7 is the figure of other installation examples another of the rotary part that encoder is shown.
Embodiment
Fig. 1 is for illustrating the longitudinal sectional view of the structure of the driving-force transmission mechanism 1 involved by the mode of execution illustrated in the present invention.In FIG, the cross section comprising the face of central axis J1 of driving-force transmission mechanism 1 is shown.Driving-force transmission mechanism 1 is such as used as speed reducer in precise machining equipment or 3D testing apparatus etc.
Driving-force transmission mechanism 1 comprises shell 2, first solid of rotation 3, second solid of rotation 4, inner ring 5 and encoder 8.Shell 2 is 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.In the following description, for simplicity, centrally axis J1, with the first shell 21 side for upside, with second housing 22 side for downside is described, but central axis J1 towards necessarily not consistent with gravitational direction.Further, in the following description, also by the direction that central axis J1 extends, namely above-below direction is called " 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 expanded perpendicular to central axis J1 separately.In addition, not shown each lip part in the sectional position of Fig. 1.Each lip part abuts each other in the axial direction.Each lip part has multiple through holes through vertically respectively.The through hole of the lip part of the bottom of the first shell 21 is connected in the axial direction with the through hole of the lip part on the top of second housing 22.Bolt passes at least one pair of consistent upper and lower through hole of circumferential position.At each lip part place, the first shell 21 is connected with second housing 22 by multiple bolt.Multiple bolt is roughly equal angles interval configuration in the circumference centered by central axis J1.In other words, each through hole is in the circumferentially configuration in equal angles interval of each lip part.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 towards 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 downward from the outer edge of cap 212.Second housing 22 comprises bearing cage 221 and cylindrical part 222.Bearing cage 221 is the bottom of second housing 22.Cylindrical part 222 extends upward from the outer edge of bearing cage 221.The inner space of shell 2 is formed by the upper end of cylindrical part 213 and the lower end in contact of cylindrical part 222.
First solid of rotation 3 comprises the first rotary shaft 31 and sun roller 33.First rotary shaft 31 and sun roller 33 are positioned at the roughly cylindric or roughly cylindric of its central position respectively in central axis J1.In other words, the first rotary shaft 31 and sun roller 33 arranged coaxial.First rotary shaft 31 is the input shaft of input queued switches power.First rotary shaft 31 extends upward from the inside of the first shell 21, and its end is protruding outside to shell 2.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 means of miscellaneous part indirectly.The external diameter of sun roller 33 is less than the external diameter of the first rotary shaft 31.In a preferred embodiment, the first rotary shaft 31 forms as one with sun roller 33.But the first rotary shaft 31 also can be formed with sun roller 33 split.
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.Also various gear mechanisms except ball bearing can be adopted 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.Thereby, it is possible to increase the second rotary shaft 41 withstand load diametrically and in the axial direction respectively.Planet carrier portion 42 comprises the first row carrier 421, multiple planet axis portion 422 and the second planet carrier 423.Second rotary shaft 41 is positioned at the roughly cylindric or roughly cylindric of its central position in central axis J1.In a preferred embodiment, the second rotary shaft 41 is in roughly cylindric.Second rotary shaft 41 extends downward from the inside of second housing 22.Protruding outside towards shell 2 of the end of the second rotary shaft 41.In other words, the second rotary shaft 41 in the axial direction, is given prominence to from shell 2 in the side contrary with the first rotary shaft 31.Second rotary shaft 41 is the output shaft of output drive strength.First rotary shaft 31 is outstanding from shell 2 towards the side of axis, namely gives prominence to towards input side.Second rotary shaft 41 is given prominence to from shell 2 towards the opposite side of axis, namely gives prominence to towards outlet side.Planet carrier portion 42 is configured in shell 2.
The first row carrier 421 is positioned at the roughly discoideus of its central position in central axis J1.The first row carrier 421 is positioned at the below of multiple planetary rollers 43, is namely positioned at outlet side.The upper end of the second rotary shaft 41 is connected with the first row carrier 421.Second planet carrier 423 is positioned at the top of multiple planetary rollers 43, is namely positioned at input side.In other words, the first row carrier 421 is positioned at the side of the axis of multiple planetary rollers 43.Second planet carrier 423 is positioned at the opposite side of the axis of multiple planetary rollers 43.Second rotary shaft 41, the first row carrier 421 and the second planet carrier 423 arranged coaxial centered by central axis J1.
The first row carrier 421 supports multiple planet axis portion 422 from below.Second planet carrier 423 supports multiple planet axis portion 422 from top.Multiple planet axis portion 422 is in the radial outside circumferentially configuration in equal angles interval of sun roller 33.In the example depicted in figure 1, three planet axis portions 422 are circumferentially spaced with 120 °.In FIG, a planet axis portion 422 in multiple planet axis portion 422 is only shown.Planetary rollers 43 too.That is, in a preferred embodiment, three planetary rollers 43 are circumferentially with 120 ° of interval configurations.
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 each other.In addition, " centrally the direction of axis J1 " represent with central axis J1 towards the almost parallel direction of axis, need not to be proper and parallel to an axis.That is, the central axis in each planet axis portion 422 both can be parallel with central axis J1, also can relative to central axis J1 only in small angle inclination.
In driving-force transmission mechanism 1, multiple holes 425 through are along the vertical direction arranged at the first row carrier 421.By being inserted with the bottom in planet axis portion 422 in each hole, thus multiple planet axis portion 422 is connected with the first row carrier 421.Each planet axis portion 422 is fixed into and can not rotates relative to the first row carrier 421.Each planet axis portion 422 is presented axially in the position roughly the same with sun roller 33 from the position that the first row carrier 421 is given prominence to upward.
Circumferentially be provided with other holes 426 multiple at the first row carrier 421 place, other holes 426 described are through along the vertical direction between planet axis portion 422.Coupling shaft portion 424 is fixed with respectively in other holes 426 multiple.Coupling shaft portion 424 gives prominence to upward from the first row carrier 421.Each coupling shaft portion 424 is towards the direction of centrally axis J1.In the present embodiment, the number in coupling shaft portion 424 is three.Further, preferably the number in other holes 426 is also coincide with the number in coupling shaft portion 424.That is, in the present embodiment, the number in other holes 426 is three.In the circumferential, coupling shaft portion 424 is between planetary rollers 43.Each planet axis portion 422 and each coupling shaft portion 424 are located at interval in circumference across 60 °.
Multiple holes of caving in upward from lower surface are provided with at the second planet carrier 423.Not through second planet carrier 423 of this some holes.The top in planet axis portion 422 and the top in coupling shaft portion 424 is inserted with in this some holes.The first row carrier 421 is connected by planet axis portion 422 and coupling shaft portion 424 with the second planet carrier 423.Planet axis portion 422 and coupling shaft portion 424 are as being played a role by the joint that the first row carrier 421 is connected with the second planet carrier 423 in the axial direction.
Multiple planetary rollers 43 is supported by multiple planet axis portion 422 respectively in shell 2.Multiple planetary rollers 43 circumferentially configures at the radial outside of sun roller 33.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 has mutually the same shape and identical size.
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.Also various gear mechanisms except needle bearing can be adopted as planetary bearing 45.Each planetary rollers 43 along with the rotation in the planet axis portion 422 in planet carrier portion 42, to rotate centered by the central axis in the centrally direction of axis J1.When each planetary rollers 43 rotates, each planetary rollers 43 is supported as rotating by planetary bearing 45.Below, the central axis in planet axis portion 422 is called " planetocentric axis ".On stricti jurise, the central axis of planetary rollers 43 and the central axis in planet axis portion 422 inconsistent, but due to consistent in fact, also the central axis of planetary rollers 43 to be called " planetocentric axis ".The position in planet axis portion 422 is accurately located by planetary rollers 43, the first row carrier 421 and the second planet carrier 423.
The respective outer circumferential face of multiple planetary rollers 43 contacts with the outer circumferential face of sun roller 33.In detail, between each planetary rollers 43 and sun roller 33, micro-gap is had.The lubricant oil be filled in shell 2 is had in this micro-gap.The oil film of outer circumferential face across lubricant oil of each planetary rollers 43 and the outer circumferential face mediate contact of sun roller 33.
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.Second rotary shaft 41 is supported as rotating relative to second housing 22 by the second bearing 25.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.Also various gear mechanisms except ball bearing can be adopted as the second bearing 25.
Inner row carrier bearing 26 is configured with between the inner peripheral surface and the outer circumferential face of the first rotary shaft 31 of the second planet carrier 423.Second planet carrier 423 is supported as rotating relative to the first solid of rotation 3 by inner row carrier bearing 26.The first solid of rotation 3 comprising sun roller 33 supports as relatively rotating centered by central axis J1 relative to the second planet carrier 423 by inner row carrier bearing 26 conversely speaking.Outer row carrier bearing 27 is configured with between the outer circumferential face of the second planet carrier 423 and the inner peripheral surface of the cylindrical part 213 of the first shell 21.Second planet carrier 423 is supported as rotating centered by central axis J1 relative to the first shell 21 by outer row carrier bearing 27.Outer row carrier bearing 27 is inserted into the first shell 21 by Spielpassung.Thereby, it is possible to prevent unnecessary power to be applied to the second planet carrier 423.The upper-end surface of the outer ring of outer row carrier bearing 27 is opposed in the axial direction with the lower surface of the first shell 21.The elastomer of ring-type is configured with, i.e. O type circle 7 between the upper-end surface and the lower surface of the first shell 21 of the outer ring of outer row carrier bearing 27.
By outer row carrier bearing 27, improve the rigidity of the second solid of rotation 4 relative to radial load.The rigidity of the first solid of rotation 3 relative to radial load is improve by outer row carrier bearing 27 and inner row carrier bearing 26.Further, by inner row carrier bearing 26, the coaxality of the first solid of rotation 3 and the second solid of rotation 4 can easily be improved.Inner row carrier bearing 26 is overlapping diametrically with outer row carrier bearing 27.Precisely, outer row carrier bearing 27 is overlapping diametrically with inner row carrier bearing 26 at least partially.Thereby, it is possible to reduce the axial dimension of driving-force transmission mechanism 1.
Second planet carrier 423 is dual stage cylindrical shape.Second planet carrier 423 comprises main body portion 461, top protuberance 462, top plate portion 463 and cylindrical portion 464.Main body portion 461 in the ring-type centered by central axis J1, and is clamped between inner row carrier bearing 26 and outer row carrier bearing 27.Top protuberance 462 in roughly cylindric, and is given prominence to upward from the inner peripheral portion of main body portion 461.Top plate portion 463 substantially planar in the form of a ring, and expand from the upper end of top protuberance 462 towards radially inner side.Cylindrical portion 464 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 inner row carrier bearing 26.Cylindrical portion 464 extends along the outer circumferential face of the first rotary shaft 31 upward from the inner circumference edge of top plate portion 463, namely extends to input side.Cylindrical portion 464 is near the outer circumferential face of the first rotary shaft 31.The top in planet axis portion 422 has shortcoming position.Thereby, it is possible to avoid the top in planet axis portion 422 and inner row carrier bearing 26 to interfere.Shortcoming position near inner row carrier bearing 26 outer circumferential face or be in contact with it.Lubricant oil is present in inner row carrier bearing 26, outer row carrier bearing 27 and the space between the second planet carrier 423 and the second bearing 25 in shell 2.
Fig. 2 amplifies the sectional view that the local of driving-force transmission mechanism 1 is shown.Centered by inner ring 5, axis J1 is positioned at the roughly cylindric parts of the position at its center.Inner ring 5 is configured at 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 the bottom of inner ring 5.Assembly department 51 is in the ring-type centered by central axis J1.As shown in Figure 1, the lower surface of assembly department 51 contacts with the upper surface of the bearing cage 221 of the bottom as second housing 22.The upper surface of assembly department 51 is opposed with the first row carrier 421.As shown in Figure 2, the peripheral part of assembly department 51 upward, and extends with top outward.
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 position of the roughly radial outside of the first row carrier 421.Press part 53 extends upward from the upper end of thinner wall section 52.Press part 53 is also in the roughly cylindrical shape centered by central axis J1.The thickness of the radial direction of the Thickness Ratio press part 53 of the radial direction of thinner wall section 52 is thin.Distance between the lower surface of the first row carrier 421 and the upper end of the second bearing 25 is shorter than the distance between the inner face of thinner wall section 52 and the outer circumferential face of the first row carrier 421.Thereby, it is possible to reduce driving-force transmission mechanism 1 size in the axial direction.
As shown in Figure 1, the multiple pin-and-holes 511 caved in upward from lower surface are provided with at assembly department 51.Also the multiple pin-and-holes 223 caved in downward from upper surface are provided with at the bearing cage 221 of second housing 22.In the present embodiment, pin-and-hole 511,223 is equally spaced provided with four in the circumferential separately.Pin 224 is inserted with respectively in pin-and-hole 511,223.Thus, even if the larger power in circumference is applied to inner ring 5, also can prevent inner ring 5 from rotating relative to shell 2.In other words, pin-and-hole 223 and pin 224 become the rotation prevention portion preventing inner ring 5 from rotating relative to shell 2.In addition, the second bearing 25 is loosely embedded in the bearing cage 221 of second housing 22.
The rotation relative to shell 2 of inner ring 5 also realizes by the constituting component except pin-and-hole 223 and pin 224 etc.Such as, also recess can be set at shell 2, projection is set in inner ring 5, be contacted in the circumferential by recess and projection and prevent inner ring 5 from rotating.Otherwise, also projection can be set at shell 2, recess is set in inner ring 5.The rotation prevention portion preventing inner ring 5 from rotating in the circumferential relative to shell 2 can be arranged to various mode.Rotation prevention portion preferably by inner ring 5 rotates with shell 2 or with the location contacts being fixed on shell 2 to prevent inner ring 5 in the circumferential.
As shown in Figure 2, the inner peripheral surface of press part 53 contacts with the outer circumferential face of planetary rollers 43.Say in more detail, between each planetary rollers 43 and inner ring 5, have micro-gap.The lubricant oil be filled in shell 2 is had in this micro-gap.The outer circumferential face of each planetary rollers 43 is across the oil film of lubricant oil and press part 53 mediate contact.At the circumferential position that press part 53 contacts with planetary rollers 43, press part 53 is crooked towards radial outside a little.Thinner wall section 52 also resiliently deformable thereupon.Utilize the recuperability of thinner wall section 52 and press part 53, namely utilize the resiliently deformable of inner ring 5, multiple planetary rollers 43 presses towards 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 by inner ring 5 resiliently deformable.Gap between inner ring 5 and shell 2 is very little.Preferably the radial width in this gap is narrower than the radial width of thinner wall section 52, namely little than the thickness of the most thin section of inner ring 5.
As long as between the first make contact 61 that thinner wall section 52 contacts in inner ring 5 and planetary rollers 43 and the inner peripheral surface 512 of assembly department 51, can arrange in every way.Below, inner peripheral surface 512 is called " inner peripheral surface 512 is installed ".The radial thickness of thinner wall section 52 is thinner than the radial thickness of the press part 53 at first make contact 61 place.In addition, the outer circumferential face of inner ring 5 also can be made to form the mode of depression to arrange thinner wall section 52.Also the inner peripheral surface of inner ring 5 and outer circumferential face can be made to form the mode of depression to arrange thinner wall section 52.
Owing to being provided with thinner wall section 52, the stress being therefore applied to inner ring 5 easily focuses on thinner wall section 52.Consequently, in inner ring 5, thinner wall section 52 is resiliently deformable easily.Thereby, it is possible to suppress press part 53 to tilt relative to central axis J1.Consequently, press part 53 is easily made to be positioned at axially desired position with the first make contact 61 of planetary rollers 43.Further, due to when inner ring 5 resiliently deformable, contact position diminishes towards the movement of axis, therefore, it is possible to shorten the length of the axis 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 for the fixing ring rigid bearing of 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.Rely on these ways, under the state not adding parts, inner ring 5 can be easily fixed on the second bearing 25.Thereby, it is possible to improve the coaxality of inner ring 5 relative to the second solid of rotation 4 (comprising planetary rollers 43) with simple structure.
If inner ring 5 is installed on shell 2, and the position of the central axis of inner ring 5 and situation about deciding towards the attachment face by shell 2, then require, between the inner peripheral surface of the attachment face of shell 2 and bearing cage 221, there is higher coaxality.Consequently, the manufacture cost of shell 2 is increased.Further, the coaxality between inner ring 5 and the second solid of rotation 4 is lower, be difficult to stable speed, the second solid of rotation 4 be rotated.Be directed to this, in driving-force transmission mechanism 1, due to utilize the outer circumferential face 251 of the second bearing 25 decide the central axis of inner ring 5 position and towards, therefore, it is possible to cut down the manufacture cost of driving-force transmission mechanism 1.
As mentioned above, at first make contact 61 place, multiple planetary rollers 43 contacts with inner ring 5.The diameter at first make contact 61 place of the inner circumferential of inner ring 5 is larger than the diameter of the outer circumferential face of the second bearing 25.Thus, the external diameter of the bottom of driving-force transmission mechanism 1 is easily miniaturized.
In fig. 2, with solid circular mark, 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 are shown.In fact first make contact 61 and the second point of contact 62 have size to a certain degree.Further, in fig. 2, by arrow, the first pressing force vector V 1 and the second pressing force vector V 2 is shown.First pressing force vector V 1 illustrates and is applied to the first pressing force of each planetary rollers 43 at first make contact 61 place from inner ring 5.Second pressing force vector V 2 illustrates the second pressing force being applied to each planetary rollers 43 at the second point of contact 62 place from sun roller 33.
In each planetary rollers 43, the axial position of first make contact 61 is different from the position of the axis of the second point of contact 62.In addition, when planet axis portion 422 tilts relative to central axis J1, following about in the explanation of power, precisely, axially corresponding with the direction of the planetocentric axis J2 being parallel to planet axis portion 422.But, because the inclination in planet axis portion 422 is minimum, therefore strictly need not be distinguished these.In the example depicted in figure 1, the second point of contact 62 in the axial direction than first make contact 61 near the first row carrier 421.Second point of contact 62 is roughly consistent with the center of planetary rollers 43 in the axial direction.First make contact 61 is presented axially between the center of the axis of planetary rollers 43 and the upper end of planetary rollers 43.
At first make contact 61 and the second point of contact 62 place, the sectional shape comprising the face of central axis J1 of the outer circumferential face of each planetary rollers 43 convexly.In other words, in each planetary rollers 43, the sectional shape on the face comprising first make contact 61 and central axis J1 at first make contact 61 place of the outer circumferential face of each planetary rollers 43 is convex toward the outer side in the radial direction centered by planetocentric axis J2.Further, the sectional shape on the face comprising the second point of contact 62 and central axis J1 at the second point of contact 62 place of above-mentioned outer circumferential face is convex toward the outer side in the radial direction centered by planetocentric axis J2.In fact, because the longitudinal section of outer circumferential face is the convex of unconspicuous arc-shaped at first make contact 61 and the second point of contact 62 place, therefore convex form not shown in Figure 2.
The external diameter of planetary rollers 43 is maximum in the approximate center of the axis of planetary rollers 43.The external diameter of planetary rollers 43 is the distance between the outer circumferential face of each planetary rollers 43 in the radial direction centered by planetocentric axis J2 and planetocentric axis J2.The external diameter of planetary rollers 43 reduces gradually along with the axial approximate centre of the planet leaving planetary rollers 43.
In inner ring 5, the diameter of the inner peripheral surface of press part 53 is along with reducing upward and gradually.Because the reduction of this diameter is minimum, therefore not shown in 2.By the inner peripheral surface of press part 53 is set as plane of inclination, can easily make the position of the axis of first make contact 61 different from the position of the axis of the second point of contact 62.And, at design aspect, only by changing the tilt angle of the inner peripheral surface of press part 53, first make contact 61 and the second point of contact 62 distance in the axial direction just can be changed.Further, equally, only by changing the tilt angle of the inner peripheral surface of press part 53, can also change at first make contact 61 place from inner ring 5 be applied to the power of planetary rollers 43 towards.That is, the size of the power that planetary rollers 43 is tilted easily can be changed at design aspect.Thereby, it is possible to the balance between the torque transfer efficiency easily adjusted in driving-force transmission mechanism 1 and back clearance.
The diameter of the inner peripheral surface of press part 53 need not gradually change in the entire axial length of press part 53.And the diameter of the inner peripheral surface of press part 53 also can reduce upward gradually.In general, at first make contact 61 place, the diameter of the inner peripheral surface of inner ring 5 reduces gradually along with the side towards axis or increases gradually.In addition, also can be that inner peripheral surface in press part 53 does not tilt and under the state that inner ring 5 produces resiliently deformable, makes the design that first make contact 61 is roughly consistent with the axial position of the second point of contact 62.
As in the driving-force transmission mechanism 1 of speed reducer, sun roller 33 rotates together with the first rotary shaft 31 as input shaft centered by central axis J1.In other words, the first solid of rotation 3 rotates centered by central axis J1.Micro-gap is had between sun roller 33 and each planetary rollers 43.Produced rub (traction) with the lubricant oil be present in this micro-gap by the rotation of sun roller 33.Each planetary rollers 43 is rotated centered by planetocentric axis J2 by this friction.Micro-gap is had between each planetary rollers 43 and inner ring 5.Produced by the rotation of each planetary rollers 43 and the lubricant oil be present in this micro-gap and rub.Inner ring 5 is fixed on shell 2 indirectly.Therefore, multiple planetary rollers 43 is rotated centered by central axis J1 by this friction.
In the following description, the rotation centered by planetocentric axis J2 of each planetary rollers 43 is called " rotation ", the rotation centered by central axis J1 of multiple planetary rollers 43 is called " revolution ".As mentioned above, the first row carrier 421 and the second planet carrier 423 are connected with multiple planetary rollers 43 by multiple planet axis portion 422.The second rotary shaft 41 as lower velocity shaft is connected with the first row carrier 421.Therefore, along with the revolution of multiple planetary rollers 43, the first row carrier 421, second planet carrier 423 and the second rotary shaft 41 as output shaft also rotate centered by central axis J1.That is, the second solid of rotation 4 rotates centered by central axis J1.Like this, in driving-force transmission mechanism 1, between the first solid of rotation 3 and the second solid of rotation 4, carry out transmission of power by friction.
As shown in Figure 2, in each planetary rollers 43, the position of the axis of first make contact 61 is different from the position of the axis 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 across planetary bearing 45 by the position of the radial outside centered by central axis J1 in the outer circumferential face in planet axis portion 422.Further, the underpart of the inner peripheral surface of planetary rollers 43 is pressed across planetary bearing 45 by the position of the radially inner side centered by central axis J1 in the outer circumferential face in planet axis portion 422.
Upper and lower relation between first make contact 61 with the second point of contact 62 may also be contrary.In general, the upper end portion of the inner peripheral surface of planetary rollers 43 and a side of underpart are pressed across planetary bearing 45 by the position of the radial outside centered by central axis J1 in the outer circumferential face in planet axis portion 422.Further, the opposing party in the upper end portion of the inner peripheral surface of planetary rollers 43 and underpart is pressed across planetary bearing 45 by the position of the radially inner side centered by central axis J1 in the outer circumferential face in planet axis portion 422.Consequently, in driving-force transmission mechanism 1, planetary rollers 43 tilts relative to planet axis portion 422, thus can reduce the back clearance between the planetary rollers 43 in planet axis portion 422 and rotation.
In fig. 2, straight line L1 is the imaginary line connecting first make contact 61 and the second point of contact 62.As shown in Figure 2, comprise in the cross section in the face of planetocentric axis J2, first make contact 61 and the second point of contact 62 in each planetary rollers 43, the first pressing force vector V 1 relative to above-mentioned straight line L1 towards lopsidedness.Second pressing force vector V 2 tilts towards opposite side relative to above-mentioned straight line L1.In the example shown in Fig. 2, the first pressing force vector V 1 tilts towards upside relative to straight line L1, and the second pressing force vector V 2 tilts towards downside relative to straight line L1, the first pressing force vector V 1 and the second pressing force vector V 2 almost parallel.
Like this, in each planetary rollers 43, the first pressing force vector V 1 and the second pressing force vector V 2 clip straight line L1 direction facing opposite to each other and tilt.Thereby, it is possible to expand the component in the direction perpendicular to planetocentric axis J2 of the first pressing force vector V 1 and the component in the direction perpendicular to 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 comprising the face of central axis J1 of the outer circumferential face of each planetary rollers 43 convexly.At first make contact 61 place, the sectional shape not being necessarily the outer circumferential face of planetary rollers 43 convexly, may also be the sectional shape comprising the face of central axis of the inner peripheral surface of the press part 53 of inner ring 5 convexly.In other words, at first make contact 61 place of each planetary rollers 43, the sectional shape comprising the face of central axis J1 of the outer circumferential face of each planetary rollers 43 and the inner peripheral surface of each press part 53 comprise the sectional shape of at least one in the sectional shape in the face of central axis J1 convexly.Thereby, it is possible to inferior along the situation of planet axle direction movement a little in planetary rollers 43, the position of first make contact 61 is changed smoothly.
Further, in driving-force transmission mechanism 1, at the second point of contact 62 place of each planetary rollers 43, the sectional shape comprising the face of central axis J1 of the outer circumferential face of each planetary rollers 43 convexly.At the second point of contact 62 place, the sectional shape not being necessarily the outer circumferential face of planetary rollers 43 convexly, may also be the sectional shape comprising the face of central axis J1 of the outer circumferential face of sun roller 33 convexly.In other words, at the second point of contact 62 place of each planetary rollers 43, the sectional shape comprising the face of central axis J1 of the outer circumferential face of each planetary rollers 43 and the outer circumferential face of sun roller 33 comprise the sectional shape of at least one in the sectional shape in the face of central axis J1 convexly.Thereby, it is possible to inferior along the situation of planet axle direction movement a little in planetary rollers 43, the position of the second point of contact 62 is changed smoothly.
Fig. 3 amplifies the figure that the vicinity of encoder 8 is shown.Encoder 8 comprises fixing part 81 and rotary part 82.Encoder 8 is preferably optical encoders, angle sensors.Thereby, it is possible to easily make driving-force transmission mechanism 1 miniaturization.Further, compared with other detection mode, can resolution be improved, thus realize accurate control.In addition, encoder 8 is not defined as optical profile type.Such as, encoder 8 may also be magnetic-type.
Fixing part 81 comprises light projector and light receiver.Rotary part 82 is for having the code-disc of multiple opening.Fixing part 81 is arranged at the first shell 21.Fixing part 81 both directly can be installed on the first shell 21, also can indirectly be installed on the first shell 21 by means of miscellaneous part.In the present embodiment, fixing part 81 is fixed on the first shell 21 in the mode of the cap 212 of through first shell 21.Rotary part 82 is arranged at the second planet carrier 423.Rotary part 82 is ring-type perpendicular to central axis J1 and centered by central axis J1 and is tabular.
The inner circumference edge of rotary part 82 contacts with the outer circumferential face 465 of the cylindrical portion 464 of the second planet carrier 423.Thereby, it is possible to easily make the Center-to-Center axis J1 of rotary part 82 consistent.The lower surface of rotary part 82 contacts with the upper surface of the top plate portion 463 of the second planet carrier 423, namely contacts with vertical surface 466.Vertical surface 466 is expanded from the outer circumferential face 465 of cylindrical portion 464 perpendicular to central axis J1.Thereby, it is possible to easily make the axial position of rotary part 82 be positioned at desired position.Rotary part 82 is such as installed on vertical surface 466 by binder or screw.
In the present embodiment, rotary part 82 is installed on the outer circumferential face 465 of cylindrical portion 464 and the vertical surface 466 of top plate portion 463.But as hereinafter described, rotary part 82 also only can be arranged on any one party in the outer circumferential face 465 of cylindrical portion 464 and the vertical surface 466 of top plate portion 463.Rotary part 82 can be fixed on the second planet carrier 423 directly or indirectly.According to the signal from encoder 8, detect at least one party in the rotational speed of the second solid of rotation 4 and rotational position.That is, encoder 8 detects the rotation of the second solid of rotation 4.
Assembly department 23 is provided with in the end of the input side of shell 2.Assembly department 23 is such as connecting the drive units such as servomotor 9 and shell 2.In the present embodiment, assembly department 23 comprises tapped hole 231.Tapped hole 231 is such as being installed on shell 2 by drive unit 9.Tapped hole 231 is configured to cave in downward from upper surface at the cap 212 of the first shell 21.The rotary part 82 of encoder 8 is positioned at the side of tapped hole 231.In other words, assembly department 23 is overlapping diametrically with rotary part 82.Thereby, it is possible to easily make driving-force transmission mechanism 1 miniaturization in the axial direction.
The part of the fixing part 81 of encoder 8 is by through for cap 212 and expose from the upper surface of the first shell 21.Fixing part 81 become terminal 812 from the position that the first shell 21 exposes.Connected by distribution 811 between the light projector of terminal 812, fixing part 81 and the light receiver of fixing part 81.When drive unit 9 is installed on assembly department 23, the distribution of the controller of drive unit 9 is connected with terminal 812.In other words, the terminal 812 of encoder 8 is configured in the end of the input side of shell 2, and the distribution being connected to encoder 8 from the control device controlled drive unit 9 is connected with terminal 812.Certainly, also can omit the terminal 812 of encoder 8, but the distribution of encoder 8 is drawn by the end of the input side from shell 2 and is connected to control device.Via the end of the input side of shell 2, power and signal transmission to encoder 8.
By the rotary part 82 of encoder 8 is arranged at the second planet carrier 423, in other words, by planet carrier portion 42 is set as cage modle, and encoder 8 is configured at this simple structure of input side, makes the connection between encoder 8 and drive unit 9 become easy.Especially, be positioned at the end of the input side of shell 2 by the terminal making the distribution of encoder 8 or be connected to distribution, and without the need to making distribution extend at the outer circumferential face of driving-force transmission mechanism 1.Consequently, the distribution of encoder 8 and drive unit 9 becomes easy process, thus improves the degrees of freedom of the setting of driving-force transmission mechanism 1 and drive unit 9.
Fig. 4 amplifies the longitudinal sectional view near illustrating between the first shell 21 and second housing 22 border.First shell 21 is the position of the first solid of rotation 3 side of shell 2.Second housing 22 is the position of the second solid of rotation 4 side of shell 2.First shell 21 contacts in the axial direction with second housing 22.First shell 21 also can not directly contact with second housing 22, but indirectly contacts with second housing 22 across miscellaneous parts such as packing rings.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 as the inner ring 5 of the end face of the input side of inner ring 5 is positioned at second housing 22.The end that the upper end of inner ring 5 is the side contrary in the axial direction with the installation inner peripheral surface 512 shown in Fig. 2 of inner ring 5.
In the finishing operation of assembling driving-force transmission mechanism 1, that implements between the first shell 21 and second housing 22 is fastening.Now, the upper end of inner ring 5 is positioned at second housing 22.Therefore, it is possible to reliably avoid the first shell 21 to contact with inner ring 5.At the first shell 21 with the tightening operation of second housing 22, be adjusted to accurate consistent by the central axis of operator's the first solid of rotation 3 the most at last with the central axis of the second solid of rotation 4.Now, the effect and diminishing of exerting pressure that the outer ring of outer row carrier bearing 27 presses downward because of the O type circle 7 shown in Fig. 1 by the radial clearance supporting the second bearing 25 of the second solid of rotation 4.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 is alignd with the central axis of second housing 22, thus 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 size, preferably reduce the axial clearance between inner ring 5 and outer row carrier bearing 27 to greatest extent.Therefore, the first shell 21 is overlapping diametrically with outer row carrier bearing 27 with the border between second housing 22.On the other hand, between the first shell 21 and second housing 22, the gap adjusting relative position is diametrically required.Therefore, in driving-force transmission mechanism 1, the internal diameter of the upper end of second housing 22 is slightly larger than the diameter of the outer circumferential face of outer row carrier bearing 27.Thereby, it is possible to form gap between the outer circumferential face and the inner peripheral surface of second housing 22 of outer row carrier bearing 27.Consequently, can adjust the first shell 21 relative to second housing 22 relative position diametrically.
Fig. 5 is the longitudinal sectional view of other examples that planetary rollers 43 is shown, and merely illustrates the part identical with the structure shown in Fig. 2.The diameter on the top of planetary rollers 43 is less than the diameter of the bottom of planetary rollers 43.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 of the diameter on top also comparable bottom is large.Further, press part 53 and sun roller 33 can design arbitrarily with the upper contact of planetary rollers 43 or with the lower contacts of planetary rollers 43.
The structure shown in other structure with Fig. 1 of the driving-force transmission mechanism 1 of Fig. 5 is identical.The diameter of the inner peripheral surface of press part 53 increases gradually along with the side towards axis or reduces gradually.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. 6 is the figure of other installation examples of the rotary part 82 that encoder 8 is shown.In the example shown in Fig. 6, between top plate portion 463 and cylindrical portion 464, be provided with rake 467.The diameter of rake 467 is along with increasing downward and gradually.The plane of inclination of rake 467 is connected with the outer circumferential face of the upper surface of top plate portion 463 and cylindrical portion 464.The lower surface of rotary part 82 is fixed on the upper surface of top plate portion 463.The position of the inner circumference edge of rotary part 82 is determined by the border between top plate portion 463 and rake 467.Like this, rotary part 82 is installed on the second planet carrier 423 with also can not utilizing the outer circumferential face of cylindrical portion 464.Also ladder difference can be set at the upper surface of top plate portion 463, and decide the position in the direction perpendicular to central axis J1 of rotary part 82 by rotary part 82 being fitted to ladder difference.
Fig. 7 is the figure of other installation examples another of the rotary part 82 that encoder 8 is shown.In the example shown in Fig. 7, rotary part 82 is separated upward from top plate portion 463.The inner circumference edge of rotary part 82 is fixed on the outer circumferential face of cylindrical portion 464.Like this, rotary part 82 also can only be fixed on cylindrical portion 464.
In above-mentioned driving-force transmission mechanism 1, various change can be carried out.
Shell 2 also can be made up of the parts of more than three.The number of clutch shaft bearing 24 and the number of the second bearing 25 also can suitably change.Also other bearings can be separately established to be used for supporting first solid of rotation 3 or the second solid of rotation 4.
The shape of inner ring 5 is ring-type, is not defined as cylindrical shape.As long as inner ring 5 natural resiliency is out of shape, then also thinner wall section 52 can not be set in inner ring 5.The assembly department 51 of inner ring 5 is without the need to being fixed on the complete cycle of the outer circumferential face of ring rigid bearing.Such as, also can arrange in the inner peripheral portion of assembly department 51 groove extended in parallel vertically, part contacts with ring rigid bearing.Fixing between inner ring 5 and ring rigid bearing also can adopt binder.Such as, inner ring 5 is fixed on ring rigid bearing by press-in and binder.
The first row carrier 421 in planet carrier portion 42 is connected with the second planet carrier 423 by joint in the axial direction.This joint also can be planet axis portion 422 or also can be coupling shaft portion 424.By planet axis portion 422 is used as joint, thus simplify the structure in planet carrier portion 42.By arranging coupling shaft portion 424, thus improve the design freedom in planet axis portion 422.The number of planetary rollers is not defined as three.
In above-mentioned driving-force transmission mechanism, the first rotary shaft 31 and the second rotary shaft 41 are also configurable in shell 2.
In the second solid of rotation 4, may also be planetary rollers 43 and be fixed on planet axis portion 422, planetary bearing 45 is arranged between planet axis portion 422 and the first row carrier 421 or between planet axis portion 422 and the second planet carrier 423.In other words, planetary rollers 43 is 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.
Also the side in outer row carrier bearing 27 and inner row carrier bearing 26 or two sides can be omitted.
Structure in above-mentioned mode of execution and each variation only otherwise conflictingly can suitably to combine.
Driving-force transmission mechanism involved in the present invention, such as, can be used as speed reducer or booster engine in the various devices such as precise machining equipment or 3D testing apparatus.Driving-force transmission mechanism involved in the present invention can also be used as other purposes.
Claims (12)
1. a driving-force transmission mechanism, it comprises:
Shell;
First solid of rotation;
Clutch shaft bearing, described first solid of rotation supports as can rotate centered by central axis relative to described shell by described clutch shaft bearing;
Second solid of rotation, described second solid of rotation carries out transmission of power by friction between described first solid of rotation;
Second bearing, described second solid of rotation supports as can rotate centered by described central axis relative to described shell by described second bearing;
Inner ring, described inner ring in the form of a ring, and is configured in the radial outside of described second solid of rotation; And
Encoder, described encoder detects the rotation of described second solid of rotation and has fixing part and rotary part,
Described first solid of rotation has:
First rotary shaft, described central axis is positioned at the position at the center of described first rotary shaft, and described first rotary shaft is given prominence to from described shell towards the input side of the side as axis; And
Sun roller, described sun roller together rotates with described first rotary shaft in described shell,
Described second solid of rotation has:
Planetary rollers, described planetary rollers is multiple, and circumferentially configure at the radial outside of described sun roller in described shell, the outer circumferential face of each planetary rollers is with the outer circumferential face of described sun roller and contact with the inner peripheral surface of described inner ring;
Planet carrier portion, described multiple planetary rollers supporting, in described shell, is can to rotate centered by the planetocentric axis in the direction along described central axis by described planet carrier portion; And
Second rotary shaft; Described central axis is positioned at the position at the center of described second rotary shaft, and described second rotary shaft is connected with described planet carrier portion, and gives prominence to from described shell towards the outlet side of the opposite side as axis,
The feature of described driving-force transmission mechanism is,
Described multiple planetary rollers utilizes the resiliently deformable of described inner ring to be pressed by towards described sun roller,
Described planet carrier portion has:
The first row carrier, described first planet chord position is in the described outlet side of multiple described planetary rollers;
Second planet carrier, described second planet carrier is positioned at the described input side of multiple described planetary rollers; And
Joint, described the first row carrier is connected with described second planet carrier by described joint in the axial direction,
The described rotary part of described encoder is arranged at described second planet carrier.
2. driving-force transmission mechanism according to claim 1, is characterized in that,
Described driving-force transmission mechanism also has outer row carrier bearing, and described second planet carrier supports as can rotate centered by described central axis by described outer row carrier bearing between described second planet carrier and described shell.
3. driving-force transmission mechanism according to claim 2, is characterized in that,
Described driving-force transmission mechanism also has inner row carrier bearing, and described sun roller supports as relatively can rotate centered by described central axis relative to described second planet carrier by described inner row carrier bearing.
4. driving-force transmission mechanism according to claim 3, is characterized in that,
Described outer row carrier bearing overlapping diametrically with described inner row carrier bearing at least partially.
5. the driving-force transmission mechanism according to any one in claim 2 to 4, is characterized in that,
Described shell has:
First shell on described first rotation side; And
The second housing of described second solid of rotation, described second housing directly or indirectly contacts in the axial direction with described first shell,
The end face of the described input side of described inner ring is positioned at described second housing,
Described first shell is overlapping diametrically with described outer row carrier bearing with the border between described second housing,
Gap is had between the outer circumferential face and the inner peripheral surface of described second housing of described outer row carrier bearing.
6. driving-force transmission mechanism according to claim 1, is characterized in that,
Described second planet carrier comprises cylindrical portion, and described cylindrical portion extends along the outer circumferential face of described first rotary shaft towards described input side,
The described fixing part of described encoder is installed on described first shell directly or indirectly,
The described rotary part of described encoder is installed on the outer circumferential face of described cylindrical portion.
7. driving-force transmission mechanism according to claim 1, is characterized in that,
Described second planet carrier also comprises vertical surface, and described vertical surface is expanded perpendicular to described central axis,
The described rotary part of described encoder is installed on described vertical surface.
8. driving-force transmission mechanism according to claim 1, is characterized in that,
The end of the described input side of described shell comprises the assembly department for being connected with drive unit,
Described assembly department is overlapping diametrically with the described rotary part of described encoder.
9. driving-force transmission mechanism according to claim 1, is characterized in that,
The distribution of described encoder is drawn by the end of the described input side from described shell, or the terminal arrangement be connected with described distribution is in the end of the described input side of described shell.
10. driving-force transmission mechanism according to claim 1, is characterized in that,
Described planet carrier portion also comprises multiple planet axis portion, described planet axis portion respectively towards the direction along described central axis,
Multiple described planetary rollers is supported as rotating by multiple described planet axis portion,
Described joint be multiple described planet axis portions at least partially.
11. driving-force transmission mechanisms according to claim 1, is characterized in that,
Described planet carrier portion also comprises multiple coupling shaft portion, described coupling shaft portion between multiple described planetary rollers respectively towards the direction along described central axis,
Described joint be multiple described coupling shaft portions at least partially.
12. driving-force transmission mechanisms according to claim 1, is characterized in that,
Described encoder is optical encoders, angle sensors.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014-219932 | 2014-10-29 | ||
| JP2014219932A JP6491456B2 (en) | 2014-10-29 | 2014-10-29 | Traction power transmission device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105570409A true CN105570409A (en) | 2016-05-11 |
| CN105570409B CN105570409B (en) | 2018-06-26 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520832309.7U Expired - Fee Related CN205479196U (en) | 2014-10-29 | 2015-10-26 | Friction power transmission device |
| CN201510701268.2A Active CN105570409B (en) | 2014-10-29 | 2015-10-26 | Driving-force transmission mechanism |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520832309.7U Expired - Fee Related CN205479196U (en) | 2014-10-29 | 2015-10-26 | Friction power transmission device |
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| Country | Link |
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| JP (1) | JP6491456B2 (en) |
| CN (2) | CN205479196U (en) |
Cited By (3)
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| CN107664185A (en) * | 2016-07-29 | 2018-02-06 | 日本电产新宝株式会社 | Speed changer and driver element |
| CN110475988A (en) * | 2017-03-31 | 2019-11-19 | Im系统控股有限公司 | Compound planetary friction drive device |
| CN110553017A (en) * | 2018-05-31 | 2019-12-10 | 日本电产新宝株式会社 | transmission with motor and trolley drive unit |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JP6491456B2 (en) * | 2014-10-29 | 2019-03-27 | 日本電産シンポ株式会社 | Traction power transmission device |
| JP7299565B2 (en) * | 2017-07-14 | 2023-06-28 | 株式会社ニコン | Encoder and drive |
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| CN110475988A (en) * | 2017-03-31 | 2019-11-19 | Im系统控股有限公司 | Compound planetary friction drive device |
| CN110475988B (en) * | 2017-03-31 | 2022-09-27 | Im系统控股有限公司 | Compound planetary friction driving device |
| CN110553017A (en) * | 2018-05-31 | 2019-12-10 | 日本电产新宝株式会社 | transmission with motor and trolley drive unit |
| CN110553017B (en) * | 2018-05-31 | 2023-04-07 | 日本电产新宝株式会社 | Transmission with motor and trolley drive unit |
Also Published As
| Publication number | Publication date |
|---|---|
| CN205479196U (en) | 2016-08-17 |
| JP2016084918A (en) | 2016-05-19 |
| JP6491456B2 (en) | 2019-03-27 |
| CN105570409B (en) | 2018-06-26 |
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