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WO2010004843A1 - Dispositif de réduction - Google Patents

Dispositif de réduction Download PDF

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Publication number
WO2010004843A1
WO2010004843A1 PCT/JP2009/061099 JP2009061099W WO2010004843A1 WO 2010004843 A1 WO2010004843 A1 WO 2010004843A1 JP 2009061099 W JP2009061099 W JP 2009061099W WO 2010004843 A1 WO2010004843 A1 WO 2010004843A1
Authority
WO
WIPO (PCT)
Prior art keywords
cam
outer diameter
roller
pocket
input shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2009/061099
Other languages
English (en)
Japanese (ja)
Inventor
幸治 秋吉
隆英 齋藤
義主 寺田
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NTN Corp
Original Assignee
NTN Corp
NTN Toyo Bearing Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2008178207A external-priority patent/JP5179978B2/ja
Priority claimed from JP2008178259A external-priority patent/JP5189423B2/ja
Application filed by NTN Corp, NTN Toyo Bearing Co Ltd filed Critical NTN Corp
Publication of WO2010004843A1 publication Critical patent/WO2010004843A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • 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
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/04—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion
    • F16H25/06—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion with intermediate members guided along tracks on both rotary members

Definitions

  • the present invention relates to a reduction gear used for industrial robots, automobile auxiliary machines, and the like.
  • an input shaft with an eccentric disk and a plurality of rollers that are in rolling contact with the outer diameter surface of the eccentric disk are held at equal pitches in the circumferential direction.
  • the number of rollers is one less than the number of cam peaks, the output shaft rotates in the opposite direction to the input shaft, and when the input shaft makes one rotation, the rollers Revolution by one pitch provides a reduction ratio equal to the number of rollers.
  • the speed reduction device described in Patent Document 1 can obtain a medium speed reduction ratio of about 10 to 50, which is required for industrial robots and automotive auxiliary machines, and can increase rigidity. Since it is necessary to arrange
  • an object of the present invention is to provide a reduction gear device that can obtain a medium reduction ratio of about 10 to 50 with high rigidity and that can be designed to have a compact axial dimension and outer diameter.
  • the speed reducer of the present invention includes an input shaft having a cylindrical inner surface that is eccentric to the cylindrical portion, and an annular shape that includes a pocket that holds a plurality of rollers that are in rolling contact with the eccentric cylindrical inner surface.
  • An output shaft having a cage portion, and a base shaft formed by equidistantly forming a plurality of cam ridges in contact with a roller held in the pocket in the circumferential direction of the outer diameter surface, and The roller is held at a position where the number of dividing points when the cage portion is divided at equal pitches in the circumferential direction is different from the number of the cam crests by one or all of the divided points.
  • an eccentric cylindrical inner diameter surface is provided in the cylindrical portion of the input shaft, and the same coaxial is formed between the cam ridges formed at an equal pitch in the circumferential direction of the outer diameter surface of the base shaft disposed coaxially on the inner diameter side.
  • the roller held in the pocket of the holder part of the output shaft arranged on the center is brought into rolling contact, and the number of dividing points when the annular holder part is divided at equal pitches in the circumferential direction is
  • a pocket for holding the roller is provided at all or a part of the dividing points that differ from the number by one, and the shape of one pitch of the cam crest is held in the pocket when the input shaft is rotated.
  • a rotational drive source such as a motor can be arranged on the outer diameter side of the input shaft, and the axial dimension can be designed more compactly. it can.
  • the output shaft can be rotated in the same direction as the input shaft by increasing the number of dividing points of the cage part by one more than the number of cam peaks.
  • the input shaft 1 rotates clockwise, and an eccentric cylindrical inner diameter surface and cam crest 4a are formed.
  • the maximum portion A of the annular space with the outer diameter surface of the base shaft 4 is at a position of 0 ° (12 o'clock) clockwise and the minimum portion B is at a position of 180 ° (6 o'clock)
  • the input shaft 1 is rotated.
  • the maximum portion A and the minimum portion B move clockwise, and the right half of the annular space tends to be widened and the left half of the annular space tends to be narrowed.
  • the roller 2 existing in the right half of the annular space moves in the outer diameter direction going up the cam peak 4a, and the roller 2 existing in the left half of the annular space moves in the inner diameter direction going down the cam peak 4a.
  • the retainer portion 3 a of the output shaft 3 that holds the roller 2 rotates in the same clockwise direction as the input shaft 1.
  • the reduction ratio can be increased or decreased by rotating the base shaft. That is, when the number of dividing points of the cage portion is increased by one more than the number of cam peaks, the revolution angle for one pitch of the cam peaks of the roller is increased by rotating the base shaft in the same direction as the input shaft. As a result, the reduction ratio becomes smaller, and when the roller is rotated in the opposite direction, the revolution angle for one pitch of the cam crest of the roller becomes smaller and the reduction ratio becomes larger.
  • the reduction ratio will increase, and if it is rotated in the reverse direction, the reduction ratio will be reduced. Get smaller.
  • the outer diameter portion in which the camshaft of the base shaft is formed is divided in the axial direction, and one of the divided outer diameter portions is used as a separate cam crest member, and is elastic in the axial direction between the other divided outer diameter portion.
  • the speed reducer of the present invention includes an input shaft having a cylindrical inner surface eccentric to the cylindrical portion, an output shaft having a plurality of cam ridges formed at equal pitches on the outer diameter surface, and an eccentric cylindrical inner surface of the input shaft.
  • an intermediate shaft having an annular retainer portion provided with a pocket for holding a plurality of rollers that are in rolling contact with the outer diameter surface of the output shaft formed with a cam crest, and arranged on the same axis, the annular retainer A pocket for holding the roller at a position where the number of dividing points when the part is divided at equal pitches in the circumferential direction is different from the number of the cam crests by all or part of the dividing points.
  • the shape of one pitch of the cam crest is configured such that the roller held in the pocket circumscribes when the input shaft is rotated and the output shaft rotates by one pitch of the cam crest. The configuration was also adopted.
  • the cylindrical part of the input shaft is provided with an eccentric cylindrical inner diameter surface, and a cam crest is formed on the outer diameter surface of the output shaft arranged on the inner diameter side, which is held in the pocket of the cage part of the intermediate shaft.
  • a pocket for holding the roller is provided in the thinned position, and the shape of one pitch of the cam peak is held in the pocket when the input shaft is rotated and the output shaft rotates by one pitch of the cam peak.
  • the output shaft of the reduction gear at each stage can be rotated in the same direction as the input shaft.
  • the number of division points is one less than the number of cam crests, as shown in FIG. 12 later, the input shaft 11 rotates clockwise to form an eccentric cylindrical inner surface and cam crest 13a.
  • the rotation of the input shaft 11 Accordingly, the maximum portion A and the minimum portion B move clockwise, and the right half of the annular space tends to be widened and the left half of the annular space tends to be narrowed. For this reason, the roller 12 existing in the right half of the annular space moves relative to the outer diameter direction going up the cam peak 13a, and the roller 12 existing in the left half of the annular space moves relative to the inner diameter direction going down the cam peak 13a. As indicated by the arrow, the output shaft 13 rotates in the same clockwise direction as the input shaft 11.
  • the reduction gears are arranged in a plurality of stages in series in the axial direction, and a cylinder portion having the eccentric cylindrical inner surface is provided on the output end side of the output shaft of the adjacent front reduction gear, and the subsequent reduction gear By using this input shaft, the reduction ratio can be easily increased.
  • the output shaft of the front stage It is possible to eliminate the rotation direction of the integral input / output shaft that becomes the input shaft of the subsequent stage, and to reduce the rotation direction of the plurality of reduction gears.
  • the outer diameter portion in which the cam peak of the output shaft is formed is divided in the axial direction, one divided outer diameter portion is used as a separate cam crest member, and the other outer diameter portion is divided in the axial direction.
  • a pocket for holding the roller of the cage part is provided at a position where a part of the dividing point is thinned out, and by making the thinning interval uniform in the circumferential direction, the rotation balance of the output shaft is kept well, The number of pockets and the number of rollers can be reduced.
  • the radial dimension can be designed compactly.
  • the outer ring By providing a means for compressing the outer ring of the rolling bearing in the axial direction, the outer ring is elastically deformed so that the inner diameter of the outer ring is reduced, and the radial direction of the rolling bearing is suppressed. Can be reduced.
  • the outer ring By forming the longitudinal section of the outer ring of the rolling bearing into a crank shape, the outer ring can be easily elastically deformed so that the inner diameter of the outer ring is reduced.
  • Two pockets adjacent to each other in the circumferential direction of the cage portion are merged, two rollers are held at both ends in the circumferential direction of the merged pocket, and the two rollers are circumferentially moved.
  • the speed reducer according to the present invention is provided with an eccentric cylindrical inner surface on the cylindrical portion of the input shaft, and a cam crest formed at an equal pitch in the circumferential direction of the outer surface of the base shaft coaxially disposed on the inner diameter side.
  • the number of division points when the roller held in the pocket of the output shaft retainer portion, which is also arranged on the same coaxial axis, is brought into rolling contact with the annular retainer portion and divided at equal pitches in the circumferential direction.
  • the pockets that hold the rollers are provided at all or part of the dividing points that differ by 1 from the number of cam ridges, and the input shaft is rotated to the shape of one pitch of the cam ridges
  • the roller held in the pocket matches the inner envelope of the locus on which the roller revolves along the eccentric cylindrical inner surface, and the revolution of the roller held in the pocket of the cage part is output as the rotation of the output shaft. Because it was so, with a large rigidity of about 10-50 Reduction ratio is obtained, it is possible to design the axial dimension compact.
  • the speed reducer of the present invention is provided with an eccentric cylindrical inner surface on the cylindrical portion of the input shaft, and a cam crest is formed on the outer diameter surface of the output shaft arranged on the inner diameter side of the intermediate shaft.
  • the number of division points when the roller held in the cage pocket rolls and the annular cage part is divided at equal pitches in the circumferential direction is different from the number of cam ridges by one.
  • FIG. 7 is a longitudinal sectional view showing a modification of FIG. Sectional view along line XX in FIG.
  • Sectional drawing which shows the modification of FIG.
  • a longitudinal sectional view showing a reduction gear device according to an eighth embodiment a and b are sectional views taken along lines XVIa-XVIa and XVIb-XVIb in FIG.
  • a longitudinal sectional view showing a reduction gear device according to a ninth embodiment Sectional drawing which expands and shows the principal part of FIG.
  • FIG. 17 is a longitudinal sectional view showing a modification of FIG.
  • the speed reducer includes an input shaft 1 having a cylindrical portion 1a having an eccentric inner surface, an output shaft 3 having an annular retainer portion 3a provided with pockets 2a for holding a plurality of rollers 2, and a plurality of cam peaks 4a.
  • an input shaft 1 having a cylindrical portion 1a having an eccentric inner surface
  • an output shaft 3 having an annular retainer portion 3a provided with pockets 2a for holding a plurality of rollers 2, and a plurality of cam peaks 4a.
  • the inner ring 5b of the needle roller bearing 5 in which the outer ring 5a is fitted on the inner diameter surface of the eccentric cylindrical portion 1a The roller 2 held in each pocket 2a is brought into rolling contact with the cam crest 4a of the inner diameter surface and the outer diameter surface of the base shaft 4, and when the cage portion 3a is divided at a constant pitch in the circumferential direction.
  • Pockets 2a for holding the rollers 2 are provided at all positions of the dividing points where the number N of dividing points is one more than the number of cam peaks 4a, and the shape of one pitch of the cam peaks 4a is input.
  • the locus inner diameter side envelope of which revolves along the cylindrical inner diameter surface of b is adapted to match.
  • the number of pockets 2a and rollers 2, that is, the number N of dividing points is 15, and the number of cam peaks 4a is 14.
  • the input shaft 1 and the output shaft 3 are supported on the base shaft 4 by ball bearings 6a and 6b, respectively, and a gear 7 to which rotational force is input from a driving source such as a motor is provided on the outer diameter surface of the input shaft 1. ing. Further, the base shaft 4 is rotatable in both directions, and the reduction ratio of the input shaft 1 and the output shaft 3 can be increased or decreased by rotating the base shaft 4 as will be described later.
  • the deceleration mechanism of the above-described reduction gear will be described.
  • the input shaft 1 rotates clockwise
  • the maximum portion A of the annular space between the cylindrical inner surface of the eccentric inner ring 5b and the outer surface of the base shaft 4 on which the cam ridge 4a is formed is a clock.
  • the maximum portion A and the minimum portion B move clockwise as the input shaft 1 rotates, and the right half of the annular space is wide.
  • the left half of the annular space tends to become narrower.
  • the roller 2 existing in the right half of the annular space moves in the outer diameter direction going up the cam peak 4a, and the roller 2 existing in the left half of the annular space moves in the inner diameter direction going down the cam peak 4a.
  • the retainer portion 3 a of the output shaft 3 that holds the roller 2 rotates in the same clockwise direction as the input shaft 1.
  • each roller 2 rotates clockwise by one pitch of the cam peaks 4a.
  • the speed reduction ratio between the input shaft 1 and the output shaft 3 is equal to the number N of division points.
  • FIG. 3 shows a modification of the first embodiment.
  • the number N of division points of the cage portion 3a is 15, the number of cam peaks 4a is 16, and the number N of division points is one less than the number of cam peaks 4a.
  • pockets 2a for holding the rollers 2 are provided at all dividing points.
  • the input shaft 1 rotates clockwise, and the maximum portion A of the annular space between the cylindrical inner surface of the eccentric inner ring 5b and the outer surface of the base shaft 4 on which the cam ridge 4a is formed is clockwise.
  • the roller 2 existing in the right half of the annular space moves in the outer diameter direction going up the cam peak 4a and moves in the inner diameter direction going down the cam peak 4a.
  • the roller 2 is held as shown by the arrows in the figure.
  • the retainer portion 3 a of the output shaft 3 that rotates rotates counterclockwise opposite to that of the input shaft 1.
  • FIG. 4 shows a second embodiment.
  • This speed reducer has the same basic configuration as that of the first embodiment, and is thinned out every second part of the dividing points of the cage part 3a where the number N of dividing points is 15. The difference is that pockets 2a for holding the rollers 2 are provided at five locations at equal thinning intervals in the circumferential direction. The other parts are the same, and the deceleration characteristics are the same as those in the first embodiment.
  • it can be provided at three locations by dividing by another divisor of 5.
  • the pockets 2a of the cage portion 3a are preferably provided at equal thinning intervals at the number of places divided by the divisor.
  • FIG. 5 shows a third embodiment.
  • the basic structure of this reduction gear is also the same as that of the first embodiment, and two adjacent pockets 2a of the retainer portion 3a of the output shaft 3 are combined, and this combined pocket
  • the two rollers 2 held at both ends in the circumferential direction 2a are urged away by springs 8 as elastic bodies.
  • the backlash in the circumferential direction of the roller 2 in the pocket 2a is eliminated, and the backlash in the circumferential direction of the reduction gear can be reduced. Further, the processing of the pocket 2a can be facilitated.
  • the number of pockets before merging is 14 and the number of cam peaks 4a is 13, and when the number of pockets before merging is an odd number, only one extra pocket is independently created. It may be formed.
  • FIG. 6 shows a fourth embodiment.
  • the basic structure of this reduction gear is the same as that of the first embodiment, and the outer ring 5a of the needle roller bearing 5 fitted into the cylindrical portion 1a of the input shaft 1 is connected to the end of the cylindrical portion 1a. It differs in that it is compressed in the axial direction by a nut 9 screwed into the part, and its longitudinal cross section has a crank shape.
  • the outer ring 5a is elastically deformed so that the inner diameter thereof is reduced, the radial direction of the needle roller bearing 5 is suppressed, and the circumferential direction of the reduction gear is reduced.
  • FIG. 7 and 8 show a fifth embodiment.
  • the basic structure of this reduction gear is the same as that of the first embodiment.
  • the outer diameter portion of the base shaft 4 provided with the cam ridges 4a is divided in the axial direction, and the separated cam ridges are divided.
  • the member 10a is abutted against the other integral outer diameter portion 10b with a rubber ring 25 as an elastic member interposed in the axial direction, and the cam crest 4a of the cam crest member 10a and the cam crest 4a of the integral outer diameter portion 10b
  • the difference is that a small phase difference is provided between the two.
  • the roller 2 is sandwiched between two cam ridges 4a having a phase difference, so that the play in the circumferential direction of the reduction gear can be reduced.
  • FIG. 11 and FIG. 12 show a sixth embodiment.
  • the speed reducer includes an input shaft 11 having a cylindrical portion 11a having an eccentric inner surface, an output shaft 13 having a plurality of cam ridges 13a formed on the outer surface at an equal pitch, and a pocket 12a for holding a plurality of rollers 12.
  • the intermediate shaft 14 having the annular retainer portion 14a provided is coaxially disposed, and the cylindrical inner diameter surface of the inner ring 5b of the needle roller bearing 5 and the output shaft 13 fitted into the inner diameter surface of the eccentric cylindrical portion 11a.
  • the roller 12 held in each pocket 12a is brought into rolling contact with the cam crest 13a of the outer diameter surface, and the number N of division points when the cage portion 14a is divided at a constant pitch in the circumferential direction.
  • pockets 12a for holding the rollers 12 are provided at all positions of the dividing points that are one less than the number of cam peaks 13a, and the shape of one pitch of the cam peaks 13a causes the input shaft 11 to rotate.
  • the output shaft 13 is 1 pin of the cam crest 13a.
  • rotating switch component it has a shape roller 12 held in the pocket 12a is circumscribed.
  • the number of pockets 12a and rollers 12, that is, the number N of division points is 15, and the number of cam peaks 13a is 16.
  • the intermediate shaft 14 is fixed with a ring portion 14b projecting outward so as to be prevented from rotating.
  • the deceleration mechanism of the above-described reduction gear will be described.
  • the input shaft 11 rotates clockwise, and the maximum portion A of the annular space between the eccentric cylindrical inner diameter surface of the inner ring 5b and the outer diameter surface of the output shaft 13 formed with the cam ridge 13a is obtained.
  • the clockwise position is 0 ° and the minimum portion B is 180 °, the maximum portion A and the minimum portion B move clockwise as the input shaft 11 rotates, and the right half of the annular space is The left half of the annular space tends to become narrower.
  • the roller 12 existing in the right half of the annular space moves relative to the outer diameter direction going up the cam peak 13a
  • the roller 12 existing in the left half of the annular space moves relative to the inner diameter direction going down the cam peak 13a.
  • the output shaft 13 rotates in the same clockwise direction as the input shaft 11.
  • the number N of division points is one less than the number of cam peaks 13a
  • the output shaft 13 rotates clockwise by one pitch of the cam peaks 13a
  • the input The reduction ratio between the shaft 11 and the output shaft 13 is equal to the number of cam peaks 13a.
  • FIG. 13 shows a modification of the sixth embodiment.
  • the number N of division points of the cage portion 14a is 15, the number of cam peaks 13a is 14, and the number N of division points is one more than the number of cam peaks 13a.
  • pockets 12a for holding the rollers 12 are provided at all dividing points.
  • the input shaft 11 rotates clockwise, and the maximum portion A of the annular space between the cylindrical inner surface of the eccentric inner ring 5b and the outer surface of the output shaft 13 on which the cam ridges 13a are formed is clockwise.
  • the roller 12 present in the right half of the annular space moves relative to the outer diameter direction going up the cam crest 13a and toward the inner diameter direction going down the cam crest 13a. In this modification, as shown by the arrows in FIG. 13 rotates counterclockwise opposite to the input shaft 11.
  • FIG. 14 shows a seventh embodiment.
  • This speed reducer has the same basic configuration as that of the sixth embodiment, and is thinned out at every second part of the dividing points of the cage part 14a where the number N of the dividing points is 15. The difference is that pockets 12a for holding the rollers 12 are provided at five locations at equal thinning intervals in the circumferential direction. Other parts are the same, and the deceleration characteristic is the same as that of the sixth embodiment.
  • the reduction gear of the sixth embodiment is arranged in two stages in series in the axial direction, and a cylindrical portion 21a having an inner diameter surface eccentric to the output end side of the output shaft 13 of the first reduction gear is provided.
  • the needle roller bearing 5 is fitted on the inner diameter surface of the cylindrical portion 21a, and the cylindrical inner diameter surface of the inner ring 5b and the second stage output shaft are provided.
  • the plurality of rollers 22 held in the pocket 22a of the cage portion 24a of the intermediate shaft 24 at the second stage are in contact with the cam crest 23a of the outer diameter surface 23.
  • the cam ridges 13a, 23a and the pockets 12a, 22a of the first-stage and second-stage reduction gears have the same number, and the number of the cam ridges 13a, 23a is one more than the number of the pockets 12a, 22a. ing. Note that the number of cam ridges 13a and 23a in the first and second stages and the number of pockets 12a and 22a may be different from each other.
  • the first and second intermediate shafts 14 and 24 have a phase difference between the pockets 12a and 22a of the cage portions 14a and 24a.
  • the intermediate shaft 14 at the stage is urged by the respective annular portions 14b and 24b so as to twist in the clockwise direction and the second stage intermediate shaft 24 in the counterclockwise direction. Therefore, the rotation direction of the integral input / output shaft that becomes the second-stage input shaft 21 at the first-stage output shaft 13 is eliminated, and consequently the rotation direction of the two-stage reduction gear is reduced.
  • This reduction gear has the same basic configuration as that of the sixth embodiment, and the outer diameter portion provided with the cam crest 13a of the output shaft 13 is divided in the axial direction.
  • the crest member 10a is abutted against the other integral outer diameter portion 10b with a rubber ring 25 as an elastic member interposed therebetween in the axial direction, and the cam crest 13a of the cam crest member 10a and the cam crest 13a of the integral outer diameter portion 10b.
  • a small phase difference is provided.
  • FIG. 19 shows a modification of the ninth embodiment.
  • the opposed surfaces of the divided separate cam crest members 10a and the integrated outer diameter portion 10b as in the modified example of the fifth embodiment shown in FIG. 10, it extends in the circumferential direction.
  • Arc grooves 26 are provided, coil springs 27 are accommodated in these arc grooves 26, and a phase difference is provided between the cam crest 13a of the cam crest member 10a and the cam crest 13a of the integral outer diameter portion 10b.
  • the roller 12 is sandwiched between two cam peaks 13a having a phase difference.

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Abstract

L'invention porte sur un dispositif de réduction ayant une rigidité élevée, capable d'assurer un rapport de réduction intermédiaire se situant dans la plage allant de 10 à 50, et ayant une dimension axiale réduite et une dimension de diamètre externe réduite. Le dispositif de réduction a, monté de façon coaxiale sur celui-ci, un arbre d'entrée (1) ayant une surface de diamètre interne cylindrique excentrée sur une section cylindrique (1a) de celui-ci, un arbre de sortie (3) ayant une section de retenue annulaire (3a) dans laquelle des poches (2a) pour contenir des rouleaux (2), qui viennent en contact de roulement avec la surface de diamètre interne cylindrique excentrée, sont formées, et un arbre de base (4) ayant des crêtes de came (4a), avec lesquelles les rouleaux (2) viennent en contact de roulement, formées à intervalles égaux sur la surface de diamètre externe de l'arbre de base (4). Les poches (2a) sont formées dans la section de retenue (3a) aux positions de points de séparation dont le nombre est déterminé par la division circonférentielle et égale de la section de retenue et est différent de un du nombre de crêtes de came. La forme de la crête de came (4a) pour un pas est alignée avec l'enveloppe côté diamètre interne d'un trajet sur lequel les rouleaux (2) maintenus dans les poches (2a) tournent sur eux-mêmes le long de la surface de diamètre interne cylindrique d'une bague interne (5b) lorsque l'arbre d'entrée (1) est amené à tourner. La révolution des rouleaux (2) maintenus dans les poches (2a) de la section de retenue (3a) est délivrée en sortie comme rotation de l'arbre de sortie (3).
PCT/JP2009/061099 2008-07-08 2009-06-18 Dispositif de réduction Ceased WO2010004843A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2008178207A JP5179978B2 (ja) 2008-07-08 2008-07-08 減速装置
JP2008-178259 2008-07-08
JP2008178259A JP5189423B2 (ja) 2008-07-08 2008-07-08 減速装置
JP2008-178207 2008-07-08

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WO2010004843A1 true WO2010004843A1 (fr) 2010-01-14

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Cited By (6)

* Cited by examiner, † Cited by third party
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US20110268333A1 (en) * 2010-04-30 2011-11-03 Klaus Klingenbeck Imaging method for enhanced visualization of vessels in an examination region of a patient and medical system for performing the method
RU2482350C1 (ru) * 2012-02-14 2013-05-20 Марат Мухамадеевич Галеев Планетарно-цевочный редуктор
US8841278B2 (en) 2009-05-13 2014-09-23 Gilead Pharmasset Llc Antiviral compounds
CN105626817A (zh) * 2016-02-05 2016-06-01 秦皇岛博硕光电设备股份有限公司 一种太阳能电池串排版机及所用的滚柱活齿减速机
WO2019003768A1 (fr) * 2017-06-29 2019-01-03 Ntn株式会社 Réducteur de vitesse
JP2025152999A (ja) * 2024-03-29 2025-10-10 本田技研工業株式会社 内接式回転運動伝達装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5247162A (en) * 1975-10-14 1977-04-14 Nisshin Koki Kk Pulley reduction gear
JPS5495864A (en) * 1977-07-19 1979-07-28 Hatano Kougiyou Kk Inscribed planetary transmission
JPS61140653A (ja) * 1984-12-11 1986-06-27 Ntn Toyo Bearing Co Ltd トロコイド減速機
JPH0228027B2 (fr) * 1985-10-18 1990-06-21 Ntn Toyo Bearing Co Ltd

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5247162A (en) * 1975-10-14 1977-04-14 Nisshin Koki Kk Pulley reduction gear
JPS5495864A (en) * 1977-07-19 1979-07-28 Hatano Kougiyou Kk Inscribed planetary transmission
JPS61140653A (ja) * 1984-12-11 1986-06-27 Ntn Toyo Bearing Co Ltd トロコイド減速機
JPH0228027B2 (fr) * 1985-10-18 1990-06-21 Ntn Toyo Bearing Co Ltd

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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JP2025152999A (ja) * 2024-03-29 2025-10-10 本田技研工業株式会社 内接式回転運動伝達装置

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