WO2018168763A1 - Engrenage de réduction différentielle - Google Patents

Engrenage de réduction différentielle Download PDF

Info

Publication number
WO2018168763A1
WO2018168763A1 PCT/JP2018/009492 JP2018009492W WO2018168763A1 WO 2018168763 A1 WO2018168763 A1 WO 2018168763A1 JP 2018009492 W JP2018009492 W JP 2018009492W WO 2018168763 A1 WO2018168763 A1 WO 2018168763A1
Authority
WO
WIPO (PCT)
Prior art keywords
input shaft
eccentric
bearing
gear
differential
Prior art date
Application number
PCT/JP2018/009492
Other languages
English (en)
Japanese (ja)
Inventor
国弘 原口
Original Assignee
株式会社ニッセイ
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
Application filed by 株式会社ニッセイ filed Critical 株式会社ニッセイ
Priority to CN201880009531.3A priority Critical patent/CN110234907B/zh
Publication of WO2018168763A1 publication Critical patent/WO2018168763A1/fr

Links

Images

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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/44—Needle bearings
    • F16C19/46—Needle bearings with one row or needles
    • 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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear

Definitions

  • the present invention relates to an internal oscillation type differential reduction gear including an internal gear and an external gear that is inscribed and meshed with the internal gear.
  • the differential reduction gear includes an internal gear and an external gear that is inscribed and meshed with the internal gear, and the external gear is eccentrically moved in the internal gear by rotational input from the input shaft. Relative rotation is generated between the gears, and rotation is output to the output shaft at a reduction ratio based on the difference in rotational speed between the eccentric motion and the relative rotation.
  • a hollow input shaft is pivotally supported on a pair of front and rear support flanges via a pair of bearings, and a pair of front and rear eccentric bodies provided on the outer periphery of the input shaft between the bearings via a roller bearing.
  • a power transmission device in which two external gears are arranged in different phases and an internal pin is installed between support flanges so that an internal pin hole provided in each external gear is loosely inserted. That is, when the input shaft rotates, the external gear is oscillated (eccentric motion) in the internal gear via the eccentric body, and the relative rotational component of the difference in the number of teeth between the internal teeth and the external teeth is extracted, thereby supporting flanges.
  • the outer diameter of the input shaft is set for each part corresponding to the bearing toward the power input side.
  • the present invention has an object to provide a differential speed reducer that can increase the strength by increasing the outer diameter of a roller even when a roller bearing is used as a shaft support of an external gear. is there.
  • an invention according to claim 1 is directed to an internal gear provided in a casing, an input shaft that passes through the internal gear coaxially, and an eccentric portion provided in the input shaft.
  • An external gear externally fitted through a bearing, inscribed in mesh with the internal gear, and an output portion having a pin for loosely inserting the external gear and interposing an input shaft bearing between the input shaft, And the reduction ratio based on the number of teeth difference between the internal gear and the external gear and the number of teeth of the external gear
  • a differential reducer that rotates the output part via a pin,
  • the eccentric portion bearing is a full roller, and the outer diameter of the eccentric portion of the input shaft is smaller than the outer diameter of the portion where the input shaft bearing is provided.
  • the axial direction of the input shaft is in contact with the side surface of the input shaft bearing on the outer periphery of the input shaft between the input shaft bearing and the eccentric portion bearing.
  • a retaining portion for restricting the movement to is provided, and the eccentric portion is formed lower than the retaining portion over the entire circumference.
  • the retaining portion has a disc shape that is coaxially formed integrally with the input shaft.
  • the eccentric portion, the eccentric portion bearing, and the external gear are provided in a plurality of sets, and the outer diameters of the eccentric portions are all equal.
  • the shapes of the external gears and the eccentric part bearings are the same.
  • the eccentric part bearing is a full roller, and the outer diameter of the eccentric part in the input shaft is made smaller than the outer diameter of the part where the input shaft bearing is provided.
  • the outer diameter of the roller can be increased, leading to increased strength.
  • the retaining portion is formed in a disk shape that is coaxially formed integrally with the input shaft. It can be processed.
  • a plurality of sets of eccentric parts, eccentric part bearings, and external gears are provided, and the outer diameters of the eccentric parts are all set. Since they are equal, the same eccentric portion bearing can be arranged in each eccentric portion, and the outer diameter of the roller of each eccentric portion bearing can be increased.
  • the fifth aspect of the invention in addition to the effect of the fourth aspect, since the shapes of the external gears and the bearings for the eccentric portions are made common, further cost reduction can be expected.
  • (A) to (C) are sectional views of the differential reducers 1A to 1C, respectively, taken along line AA of FIG. It is the F section enlarged view of FIG. It is the graph which compared the efficiency in case the dislocation coefficient of the internal gear 4 differs.
  • FIG. 1 and 2 show a series S including three types of differential reduction gears 1A, 1B, and 1C.
  • FIG. 1 shows a central longitudinal sectional view of the differential reducer 1A as a representative
  • FIGS. 2 (A) to 2 (C) show the structure of FIG. Cross-sectional views of the differential reduction gears 1A to 1C along the line AA are respectively shown.
  • an alphabetic character is added as in 14A to 14C.
  • reference numeral 2 denotes a casing.
  • the casing 2 includes a cylindrical inner case 3 integrally provided with an internal gear 4 on the inner side, and one of the inner cases 3 in the axial direction. It consists of a disc-shaped case cover 5 arranged on the end face (input side, right side in FIG. 1) and a cylindrical outer case 6 arranged on the other end face (output side, left side in FIG. 1).
  • the middle case 3, the case cover 5, and the outer case 6 are integrally coupled by a plurality of bolts 7, 7,... Screwed to the outer case 6 through the middle case 3 from the case cover 5 side. .
  • a disc-shaped output shaft 9 is rotatably supported inside the outer case 6 via a cross roller bearing 8 as an outer bearing.
  • a hollow cylindrical input shaft 12 is coaxially and rotatably supported inside the casing 2 via ball bearings 10 and 11 serving as input shaft bearings.
  • the ball bearing 10 as an inner bearing on the input side
  • the axial input side half of the outer ring 10a is supported by the case cover 5, and the axial output side half of the outer ring 10a is supported by a carrier 24 described later.
  • a pair of eccentric portions 14A, 14A (14B) having outer diameters equal to each other and the maximum eccentric side being 180 degrees different from each other between the shaft support portions 13, 13 on which the ball bearings 10, 11 are disposed.
  • each eccentric part 14A, 14A (14B, 14B and 14C, 14C) are formed adjacent to each other in the axial direction.
  • a full roller comprising a plurality of needles 16, 16,.
  • the external gears 17A, 17A (17B, 17B and 17C, 17C) having the same outer shape are externally rotatably mounted via the needle bearing 15. Therefore, each needle 16 is in direct contact with the inner eccentric portions 14A to 14C and the outer external gears 17A to 17C.
  • the outer diameter D1 of the shaft support portion 13 where the ball bearings 10 and 11 are disposed and the outer diameter D2 of the eccentric portion 14A (14B, 14C) where the needle bearing 15 is provided are D1> D2. It is formed so that it may become a relation.
  • the size (outer diameter) of each needle 16 provided on the outer periphery can be increased.
  • a disc-shaped retaining portion 18 that protrudes higher to the outer peripheral side than the eccentric portion 14A (14B, 14C) over the entire circumference is provided between the shaft support portion 13 and the eccentric portion 14A (14B, 14C). Each is installed.
  • the retaining portion 18 restricts the movement of the needle 16 outward in the axial direction and the movement of the ball bearings 10 and 11 inward in the axial direction over the entire circumference. As a result, the movement of the input shaft 12 in the axial direction is also restricted.
  • the movement of the ball bearing 10 to the outside is regulated by a cover 19 that is provided on the inner peripheral edge of the case cover 5 and overlaps the outer ring 10 a from the outside, and the movement of the ball bearing 11 to the outside is provided to the output shaft 9. It is regulated by the stepped portion 20.
  • the external gears 17A to 17C have a smaller number of teeth than the internal gear 4 and are inscribed in the eccentric gear 4 at an eccentric position.
  • the internal gears 4 having the same shape with 120 teeth are used.
  • the external gear 17A has a reduction ratio of 1/19 with the number of teeth being 114 and the difference in the number of teeth from the internal gear 4 being 1/19
  • the external gear 17B is The number of teeth is 116, the number of teeth difference with the internal gear 4 is 4, the reduction ratio is 1/29, the external gear 17C is 118 and the number of teeth difference with the internal gear 4 is 2.
  • the reduction ratio is 1/59.
  • the eccentric amounts ⁇ 1, ⁇ 2, and ⁇ 3 from the center O1 (the axis of the input shaft 12) of the internal gear 4 at the respective centers O2 (centers of the eccentric portions 14A to 14C) of the external gears 17A to 17C are ⁇ 1.
  • the relationship is> ⁇ 2> ⁇ 3.
  • the internal teeth of the internal gear 4 and the external teeth of the external gear 17 are each in an involute tooth type, and the dislocation coefficient of the internal gear 4 is between 1 and 1.9. Is set.
  • each of the external gears 17A to 17C eight circular pin holes 21A to 21C are formed on the concentric circle with the center O2 as a center at equal intervals in the circumferential direction, and the pin holes 21A to 21C are formed.
  • the pin 22 is installed between the output shaft 9 and a disk-shaped carrier 24 disposed inside the case cover 5 on a concentric circle centering on the axis of the internal gear 4 and parallel to the axis.
  • a cylindrical metal 23 is integrally mounted on the loose insertion portion of the external gears 17A to 17C on the outer periphery of the pin 22.
  • the carrier 24 supports the inner half of the outer ring 10 a of the ball bearing 10 inside the case cover 5, and can rotate integrally with the output shaft 9 via the pin 22.
  • the output shaft 9 connected via the pin 22 and the pin 22 is an output unit.
  • Each pin 22 has the outer periphery of the metal 23 inscribed in the inner periphery of the pin holes 21A to 21C of the front and rear external gears 17A, 17A (17B, 17B and 17C, 17C) with phases different from each other by 180 degrees.
  • the hole diameters of the pin holes 21A to 21C of the external gears 17A to 17C are set for each of the differential reduction gears 1A to 1C. That is, the diameter of the pin holes 21A to 21C in the external gears 17A to 17C is a dimension obtained by adding twice the eccentric amount ⁇ 1 to ⁇ 3 of the external gears 17A to 17C to the diameter of the pin 22 including the metal 23.
  • the hole diameters of the pin holes 21A to 21C are different for the differential reduction gears 1A to 1C. However, even if the hole diameters are different, the center positions of the pin holes 21A to 21C of the external gears 17A to 17C all coincide.
  • the ball bearing 10 is fitted into the inner peripheral surface of the case cover 5 and the carrier 24 so as to be interposed between the case cover 5 and the carrier 24 supporting the outer ring 10a as shown in FIG.
  • a gap A is formed in the axial direction of the shaft 12 to communicate with the inside of the casing 2.
  • ring-shaped grease grooves 25 and 25 are respectively formed on the inner peripheral surfaces of the case cover 5 and the carrier 24 over the entire circumference.
  • an oil seal 27 as a seal member is interposed between the ring-shaped protrusion 26 protruding from the front surface of the case cover 5 and the outer peripheral surface of the input shaft 12.
  • An oil seal 28 is interposed between the outer case 6 and the output shaft 9 on the output side of the cross roller bearing 8.
  • An oil seal 29 is also interposed between the output shaft 9 and the input shaft 12 on the output side of the ball bearing 11.
  • each pin hole 21A to 21C also moves eccentrically and rotates, but each pin hole 21A to 21C is formed with a larger diameter than the pin 22 including the metal 23, so that each pin 22 has a pin hole 21A to 21C. In a state in which the pin is inscribed, it relatively moves eccentrically to absorb the eccentric component, and only the rotation component is extracted from each pin 22.
  • the output shaft 9 and the carrier 24 rotate synchronously via the pin 22 and rotate in a state where the output shaft 9 is decelerated at the reduction ratio described above.
  • the differential speed reducer 1A has a reduced speed
  • the differential speed reducer 1B has a medium speed reduction
  • the differential speed reducer 1C has a high speed reduction.
  • the grease filled in the casing 2 is supplied from the gap A between the outer ring 10a, the inner peripheral surface of the case cover 5 and the inner peripheral surface of the carrier 24 to the grease grooves 25 and 25, and lubrication is performed. It is maintained and friction is reduced. Even when grease is supplied in this way, the oil seal 27 is interposed between the case cover 5 and the input shaft 12, so that no grease leakage occurs.
  • the pin holes 21A to 21C of the external gears 17A to 17C are respectively connected to the external gears 17A to 17C according to the number of external teeth. Since the internal gear 4, the pin 22, and the metal 23 are formed in different diameters for each 17 C, the external gears 17 A to 17 C have pin holes 21 A to 21 A having a hole diameter corresponding to one reduction ratio. It is sufficient to form only 21C. Therefore, it is possible to share parts and reduce manufacturing costs without reducing the strength of the external gears 17A to 17C. In particular, since the center positions of the pin holes 21A to 21C coincide with each other between the external gears 17A to 17C, the output shaft 9 and the carrier 24 can be shared.
  • the tooth patterns of the internal gear 4 and the external gears 17A to 17C are involute teeth.
  • JGMA Joint Gear Industry Association Standard
  • JGMA 611-01 “Compliance with ISO Standard Cylindrical Gear Shifting System”
  • the gear standard of the Japan Gear Industry Association the involute internal teeth
  • the dislocation coefficient of the internal gear 4 is set between 1 and 1.9, thereby increasing the root diameter of the external gears 17A to 17C meshing therewith. Therefore, the thickness of the tooth bottoms of the external gears 17A to 17C and the pin holes 21A to 21C can be secured.
  • No. 1 represents a dislocation coefficient of 1.9 (number of teeth: 76, difference in number of teeth: 1, reduction ratio: 1/75).
  • the dotted lines 2 indicate the case where the dislocation coefficient is 0.2 (60 teeth, 1 tooth difference, 1/59 reduction ratio).
  • the maximum efficiency is about 68% at a dislocation coefficient of 1.9 and about 70% at a dislocation coefficient of 0.2, and it can be seen that even when the dislocation coefficient is 1.9, there is not much influence on the efficiency. .
  • the rigidity of the differential reduction gears 1A to 1C can be increased.
  • the number of pins 22 can be easily increased to eight or more.
  • the pins 21A to 21C corresponding to one reduction gear ratio are formed in the tooth gears 17A to 17C, the distance between the pin holes 21A to 21C can be secured. Therefore, the rigidity can be easily increased by making the pins 22 thicker.
  • the differential reduction gears 1A to 1C can be provided even if three reduction gear ratios are used.
  • the strength of the external gears 17A to 17C does not decrease. Therefore, three or more types of series can be configured with the internal gear 4, the pin 22, the metal 23, the output shaft 9, and the carrier 24 being shared. And the weight reduction can be achieved by making the input shaft 12 hollow. Further, the strength of the external gears 17A to 17C can be maintained even if the input shaft 12 is hollow.
  • each reduction ratio is not limited to the above-described form.
  • the number of external gears provided in each differential reduction gear can also be increased or decreased.
  • the pin is made of metal, but it may be a single pin that does not have a rolling member such as a roller, or such a separate member.
  • the eccentric portion bearing is the needle roller 15 of the full roller, and the outer diameter D2 of the eccentric portions 14A to 14C of the input shaft 12 is changed to the ball bearing.
  • the outer diameter of the needle 16 can be increased, leading to an increase in strength.
  • a retaining portion that restricts movement of the input shaft 12 in the axial direction by contacting the side surface of the ball bearing 10, 11 on the outer periphery of the input shaft 12 between the ball bearings 10, 11 and the needle bearing 15.
  • the eccentric portions 14A to 14C are formed lower than the retaining portion 18 over the entire circumference, and therefore, the entire roller has the needle 16 extending over the entire circumference of the eccentric portions 14A to 14C.
  • the movement in the axial direction can be restricted.
  • the retaining portion 18 can be shared by both the ball bearings 10 and 11 and the needle 16. Further, the retaining portion 18 also serves as a retaining mechanism for the input shaft 12 itself.
  • the retaining portion 18 has a disk shape that is coaxially formed integrally with the input shaft 12, the retaining portion 18 can be easily processed by a lathe or the like.
  • the eccentric parts 14A to 14C, the needle bearing 15 and the external gears 17A to 17C are provided in plural sets so that the outer diameters of the eccentric parts 14A to 14C are all equal, the same needle is used for each eccentric part 14A to 14C.
  • the bearing 15 can be arrange
  • the external gears 17A to 17C and the needle bearings 15 have the same shape, further cost reduction can be expected.
  • the needle 16 of the needle bearing 15 can be disposed at a position close to the center O1 of the internal gear 4 (the axis of the input shaft 12), the diameter of the pin 22 for taking out the rotational motion from the external gears 17A to 17C can be reduced. Can be bigger. Therefore, the strength of the differential reducers 1A to 1C can be increased.
  • the shape of the retaining portion is not necessarily a disc shape, and may be a gear shape in which a plurality of protrusions are formed on the outer periphery as long as the movement of the needle can be restricted, or may be separate from the input shaft. It may be a member.
  • the outer ring 10a of the ball bearing 10 is supported by the case cover 5 and the carrier 24 of the casing 2, so that the input shaft 12 and the casing 2 are separated.
  • the input shaft 12 can be assembled with high accuracy by increasing the coaxiality.
  • the outer ring 10a of the ball bearing 10 is fitted with a gap between the case cover 5 and the carrier 24, so that it can be slid on the sliding surface, and the rotational resistance is reduced.
  • the grease grooves 25 and 25 are formed on the sliding surfaces of the outer ring 10a, the case cover 5 and the carrier 24, which are fitted into the gap, the grease is held on the sliding surfaces and slid with low friction. be able to. Further, since the grease groove 25 is formed in the case cover 5 and the carrier 24, the standard ball bearing 10 can be adopted, and the cost increase can be suppressed. In addition, since the grease groove 25 is formed over the entire circumference of the sliding surface, the grease groove 25 can be easily processed by a lathe or the like.
  • the oil seal 27 which seals between the casing 2 and the input shaft 12 is arrange
  • the casing 2 and the input shaft 12 with high coaxiality are arranged. Therefore, the oil seal 27 can be brought into contact with the input shaft 12 with high accuracy, and the risk of grease leakage can be reduced.
  • the outer ring of the ball bearing is fitted with a gap between both the case cover and the carrier, but the gap may be fitted with only one of them. Therefore, the grease groove may be provided only on the sliding surface on one side where the gap is fitted. Moreover, when providing a grease groove
  • the structure of the casing is not limited to the combination of the middle case, the case cover, and the outer case as in the above form, but the number of parts can be increased or decreased, or the casing can be formed by one member. It does not matter.
  • the outer bearing is not limited to the cross roller bearing, and other bearings such as a ball bearing may be employed, and the number of bearings may be increased.
  • the structure of the input shaft and the output shaft is not limited to the above-described form, and the design can be changed as appropriate, for example, the input shaft is not hollow but solid.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

Le problème décrit par la présente invention est d'agrandir le diamètre extérieur d'un rouleau et d'augmenter la résistance même lorsqu'un roulement à rouleaux est utilisé dans le tourillonnage d'un engrenage à denture externe. À cet effet, l'invention porte sur un engrenage de réduction différentielle 1A -1C comprenant un engrenage à denture interne 4 disposé à l'intérieur d'un boîtier 2, un arbre d'entrée 12 qui passe de façon coaxiale à travers l'engrenage à denture interne 4, un engrenage à denture externe 17A -17C qui est monté à l'extérieur par l'intermédiaire d'une partie excentrique prenant appui sur une partie excentrique 14A -14C disposée sur l'arbre d'entrée 12 et qui s'engrène avec le côté interne de l'engrenage à denture interne 4, et un arbre de sortie 9 pourvu de broches 22, 22… insérées de manière lâche dans l'engrenage à denture externe 17A -17C, des roulements à billes 10, 11 étant placés entre l'arbre d'entrée 12 et l'arbre de sortie 9, et l'arbre de sortie 9 étant entraîné en rotation par l'intermédiaire de la broche 22 selon un rapport de réduction prescrit du fait de la rotation de l'arbre d'entrée 12 entraînant l'engrenage à denture externe 17A -17C à se déplacer de manière excentrique par rapport à l'engrenage à denture interne 4; le palier à partie excentrique est un roulement à aiguilles à rouleaux sans écrou 15, et le diamètre D2 de la partie excentrique 14A -14C dans l'arbre d'entrée 12 est inférieur au diamètre D1 d'une partie de tourillonnage 13 à laquelle les roulements à billes 10, 11 sont rattachés.
PCT/JP2018/009492 2017-03-15 2018-03-12 Engrenage de réduction différentielle WO2018168763A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201880009531.3A CN110234907B (zh) 2017-03-15 2018-03-12 差动减速器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017-050241 2017-03-15
JP2017050241A JP6803273B2 (ja) 2017-03-15 2017-03-15 差動減速機

Publications (1)

Publication Number Publication Date
WO2018168763A1 true WO2018168763A1 (fr) 2018-09-20

Family

ID=63523637

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2018/009492 WO2018168763A1 (fr) 2017-03-15 2018-03-12 Engrenage de réduction différentielle

Country Status (3)

Country Link
JP (1) JP6803273B2 (fr)
CN (1) CN110234907B (fr)
WO (1) WO2018168763A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110748611A (zh) * 2019-10-25 2020-02-04 青岛郑洋机器人有限公司 一种大中空结构偏心输入轴刚性齿轮传动的减速器
JP2023015745A (ja) 2021-07-20 2023-02-01 住友重機械工業株式会社 偏心揺動型歯車装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006085536A1 (fr) * 2005-02-09 2006-08-17 Sumitomo Heavy Industries, Ltd. Dispositif de transmission de puissance
JP2007285396A (ja) * 2006-04-17 2007-11-01 Sumitomo Heavy Ind Ltd 揺動内接噛合遊星歯車装置
JP2011047457A (ja) * 2009-08-26 2011-03-10 Sumitomo Heavy Ind Ltd 軸受構造及び軸受
JP2017214947A (ja) * 2016-05-30 2017-12-07 日本電産シンポ株式会社 歯車減速機

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0627532B2 (ja) * 1987-04-13 1994-04-13 住友重機械工業株式会社 遊星歯車増減速機
CN2591333Y (zh) * 2002-11-29 2003-12-10 夏正权 摆线针轮减速器
JP4265748B2 (ja) * 2003-03-31 2009-05-20 ナブテスコ株式会社 針状ころ軸受を用いた減速機
JP5654798B2 (ja) * 2010-07-30 2015-01-14 住友重機械工業株式会社 ローラのリテーナ及び揺動内接噛合型の歯車装置
JP2014122681A (ja) * 2012-12-21 2014-07-03 Jtekt Corp 風力発電装置の減速機、および風力発電装置の減速機の製造方法
JP2015175512A (ja) * 2014-03-18 2015-10-05 Ntn株式会社 インホイールモータ駆動装置
CN104565261A (zh) * 2014-12-26 2015-04-29 浙江恒丰泰减速机制造有限公司 精密回转传动机构

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006085536A1 (fr) * 2005-02-09 2006-08-17 Sumitomo Heavy Industries, Ltd. Dispositif de transmission de puissance
JP2007285396A (ja) * 2006-04-17 2007-11-01 Sumitomo Heavy Ind Ltd 揺動内接噛合遊星歯車装置
JP2011047457A (ja) * 2009-08-26 2011-03-10 Sumitomo Heavy Ind Ltd 軸受構造及び軸受
JP2017214947A (ja) * 2016-05-30 2017-12-07 日本電産シンポ株式会社 歯車減速機

Also Published As

Publication number Publication date
CN110234907A (zh) 2019-09-13
JP6803273B2 (ja) 2020-12-23
CN110234907B (zh) 2023-03-10
JP2018155264A (ja) 2018-10-04

Similar Documents

Publication Publication Date Title
JP5822392B2 (ja) 偏心揺動型減速機
JP4590299B2 (ja) 遊星歯車減速機におけるキャリアの回動支持構造
US11078991B2 (en) Planetary gear device
US20130102433A1 (en) Gear transmission
WO2019090900A1 (fr) Réducteur de vitesse cycloïdal précis pour articulation rotative
TW201109549A (en) Simple planetary gear speed reducer series
WO2018168763A1 (fr) Engrenage de réduction différentielle
US8545358B2 (en) Gear transmission
WO2018168762A1 (fr) Série pour engrenage réducteur différentiel et procédé de fabrication d'une série pour engrenage réducteur différentiel
WO2018168764A1 (fr) Engrenage réducteur différentiel
US8460148B2 (en) Gear set for differential
JP2017201194A (ja) 減速装置
JP7129308B2 (ja) 偏心揺動型減速装置
JP6284368B2 (ja) 歯車伝動装置
JP5606587B2 (ja) 歯車装置
CN211501500U (zh) 差动摆线针轮变速装置
JP7442364B2 (ja) 潤滑性能を向上させた差動減速機
CN219221168U (zh) 一种改进的滚柱减速器
JP2021001648A (ja) 多段遊星ローラ式動力伝達装置
JP5339743B2 (ja) 歯車装置
JP2020020409A (ja) 差動減速機
JP6570837B2 (ja) 減速機
JP6354971B2 (ja) 遊星ローラ式摩擦伝動装置
JP5635341B2 (ja) ローラ式減速装置
KR20170070986A (ko) 기어치를 구비하는 베어링 및 이를 이용한 감속기

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 18767942

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 18767942

Country of ref document: EP

Kind code of ref document: A1