WO2017054409A1 - Rouleau élastique, réducteur cycloïdal à engrenage à broche et palier - Google Patents

Rouleau élastique, réducteur cycloïdal à engrenage à broche et palier Download PDF

Info

Publication number
WO2017054409A1
WO2017054409A1 PCT/CN2016/075141 CN2016075141W WO2017054409A1 WO 2017054409 A1 WO2017054409 A1 WO 2017054409A1 CN 2016075141 W CN2016075141 W CN 2016075141W WO 2017054409 A1 WO2017054409 A1 WO 2017054409A1
Authority
WO
WIPO (PCT)
Prior art keywords
roller
elastic
hollow
solid
gap
Prior art date
Application number
PCT/CN2016/075141
Other languages
English (en)
Chinese (zh)
Inventor
孙子健
刘毅
郑美珠
Original Assignee
昆山光腾智能机械有限公司
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 昆山光腾智能机械有限公司 filed Critical 昆山光腾智能机械有限公司
Publication of WO2017054409A1 publication Critical patent/WO2017054409A1/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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/34—Rollers; Needles
    • F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
    • 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
    • F16H53/00—Cams ; Non-rotary cams; or cam-followers, e.g. rollers for gearing mechanisms
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/34—Rollers; Needles

Definitions

  • the invention relates to the technical field of reducers, in particular to an elastic roller having both flexibility and strength, a pinion cycloid reducer and a bearing having the elastic roller.
  • the pin-tooth cycloidal speed reducer represented by the RV type reducer has the advantages of compact structure and strong transmission capability, and becomes the most important component of the robot system.
  • the RV type pin-tooth cycloidal speed reducer is mainly composed of a pin gear housing 1, a pin gear 2, a cycloid disk 3, an eccentric shaft 4, and the like.
  • the eccentric shaft 4 rotates to drive the cycloidal disc 3, so that the cycloidal disc 3 performs a cycloidal motion on the needle teeth 2 to push the cycloidal disc 3 forward.
  • FIG. 1 Three different cases in which the pin 2 is in contact with the cycloidal disk 3 are shown in FIG.
  • the deviation due to various reasons causes the pin 2 to be in contact with the cycloidal disk 3 only at B, and the cycloidal disk 3 can be pushed forward just right.
  • the distance between the two is too close.
  • the needle 2 is strongly compressed and produces a large deformation.
  • the needle 2 may still push the cycloidal disc 3 forward, if the needle 2 is subjected to too much pressure, the needle 2 may be crushed. Or it is worn out very quickly, and the same is true for the cycloidal disc 3. So this situation cannot be allowed.
  • the pin 2 is a solid cylinder, the stiffness is very large, and the deformation generated during the actual operation is very small; the contact change shown in Fig. 2 is actually very small, generally only a few micrometers, which is invisible to the naked eye. The changes reflected on the map are actually extremely exaggerated and magnified.
  • the measures taken at present are mainly to further improve the processing precision and move closer to the imported original.
  • the main measure to improve the processing accuracy is to purchase more advanced, mainly imported processing equipment.
  • simply doing so does not completely achieve the goal, and the resulting production cost is expensive, and it also makes people doubt whether it can be truly commercialized in the future, so as to achieve the ability to compete with foreign products.
  • the present invention provides an elastic roller comprising a hollow roller and a solid roller disposed inside the hollow roller, between the inner wall surface of the hollow roller and the outer wall surface of the solid roller A floating gap is provided for the elastic roller to be elastically deformed.
  • the wall thickness of the hollow roller is 0.12-0.18 times the outer diameter of the hollow roller.
  • the floating gap is uniformly formed around the solid roller, and the floating gap is hollow along the radial direction of the hollow roller. 0.002-0.007 times the outer diameter of the roller.
  • the floating gap is filled with a soft rubber.
  • an elastic member is disposed in the floating gap.
  • the elastic member is a spring sleeved on the periphery of the solid roller
  • the floating gap includes a first gap disposed between the hollow roller and the spring and disposed between the spring and the solid roller The second gap.
  • the radial dimension of the first gap and the second gap is 0.003-0.007 of the outer diameter of the hollow roller. Times.
  • the elastic member is a corrugated metal tube disposed around the outer side of the solid roller, and the floating gap is hollowed out along the inner wall surface of the hollow roller or the outer wall surface of the solid roller.
  • the outer diameter of the column is 0.003-0.007 times.
  • the present invention also provides a pinion cycloidal speed reducer comprising a cycloidal disk, a pin gear housing surrounding the outer side of the cycloidal disk, and a pin gear assembly clamped between the cycloidal disk and the pin gear housing,
  • the pinion assembly includes a plurality of elastic rollers evenly distributed along the inner circumferential direction of the pin housing, the elastic rollers being disposed as previously described.
  • the present invention also provides a bearing comprising spaced outer and inner bearing rings, a plurality of rollers disposed between the outer bearing ring and the inner bearing ring, the rollers being of the aforementioned elastic roller Settings.
  • the invention has the beneficial effects that the invention is manufactured by adopting an elastic roller combination manner, that is, the hollow roller is located on the outer side, the solid roller is filled on the inner side of the hollow roller, and is in the hollow roller and the solid roller.
  • a floating gap is provided for the hollow roller to be deformed, thereby providing a certain elastic deformation space of the hollow roller through the floating gap, and then selecting When the interference fit is used, sufficient elastic compensation capability can be achieved.
  • a certain supporting force can be provided through the inner solid roller to prevent the hollow roller from being crushed and broken due to excessive load, so that the elastic roller is resistant.
  • the arrangement of the middle elastic roller can also reduce the manufacturing precision of the roller, the cycloidal disc and the pin gear shell in the prior art, and is convenient to manufacture, and the structure is simple, convenient to manufacture and low in cost.
  • FIG. 1 is a schematic cross-sectional view of a prior art needle-tooth cycloidal speed reducer
  • Figure 2 is an enlarged view of the circled portion of Figure 1;
  • Figure 3 is a cross-sectional view showing the first preferred embodiment of the needle-tooth cycloidal speed reducer of the present invention
  • Figure 4 is an enlarged view of the circled portion of Figure 3;
  • Figure 5 is a view showing the state of use of the elastic roller of Figure 4 in the hollow roller being pressed against the solid roller;
  • Figure 6 is a transverse cross-sectional view showing a second preferred embodiment of the elastic roller of the present invention.
  • Figure 7 is a longitudinal cross-sectional view of the elastic roller of Figure 6;
  • Figure 8 is a longitudinal cross-sectional view showing a third preferred embodiment of the elastic roller of the present invention.
  • Figure 9 is a schematic cross-sectional view of the bearing of the present invention.
  • the pin-tooth cycloid reducer 100 includes an input shaft (not shown) interposed therebetween to connect a servo motor (not shown), an input gear (not shown) integrally formed at an end of the input shaft, and an engagement gear set on the input gear a surrounding planetary gear (not shown), a crankshaft 1 fixed to the planetary gear 1, a cycloidal disk 2 provided in cooperation with the crankshaft 1, a bearing 3 and a needle disposed between the crankshaft 1 and the cycloidal disk 2
  • the cycloid disk 2 is provided with a through hole 21 for receiving the crankshaft 1 and the bearing 3.
  • the pin assembly 5 includes a plurality of elastic rollers 51 uniformly distributed along the inner circumferential direction of the pin housing 4.
  • the elastic roller 51 includes a hollow roller 52 and a solid roller 53 disposed inside the hollow roller 52.
  • a floating gap 54 for elastically deforming the hollow roller 52 is disposed between the inner wall surface of the hollow roller 52 and the outer wall surface of the solid roller 53.
  • Fig. 4 is an enlarged view of the circled portion of Fig. 3.
  • the floating roller 54 in the elastic roller 51 at the B in FIG. 4 is in a normal state, and the hollow roller 52 works normally; the hollow roller 52 at the A is elastically deformed at the floating gap 54 after being pressed.
  • the resilient roller 51 is subjected to a reasonable pressure from the pin housing 4 and the cycloidal disk 2, and the hollow roller 52 at either A or B can function normally.
  • the pressure will increase greatly.
  • the hollow roller 52 may be excessively deformed; at this time, as shown in FIG. 5, in the hollow
  • the effective support of the solid roller 53 can resist the strong overload shock, effectively preventing the hollow roller 52 from being damaged by excessive extrusion deformation. That is, when a very strong impact load is applied from the outside, as long as the solid roller 53 can be supported, the hollow roller 52 is not broken, and the entire elastic roller 51 can be safe.
  • the hollow roller 52 and the solid roller 53 are made of wear-resistant and high-strength bearing steel or high-molecular carbon fiber material, and the wall thickness of the hollow roller 52 is set to the outer diameter of the hollow roller 52. 0.12-0.18 times, preferably 0.13 to 0.16 times; that is, the hollow roller 52 having a larger outer diameter may be thicker, and the hollow roller 52 having a smaller outer diameter may be thinner.
  • the wall thickness is set such that the hollow roller 52 itself has a certain impact strength, and at the same time, when subjected to a large external force, a certain elastic deformation can be compensated for.
  • the floating gap 54 is uniformly formed around the solid roller 53 when the solid roller 53 is located at the axial center position of the hollow roller 52.
  • the elastic roller 51 is rotated, the elastic compensation force on the entire circumference is the same, and the radial gap 54 is made in the radial direction of the hollow roller 52 to be 0.002-0.007 times the outer diameter of the hollow roller 52.
  • the floating gap 54 is filled with a soft rubber 55 for the convenience of installation, that is, the hollow roller is passed through the soft rubber 55.
  • the 52 and the solid rollers 53 are fixed in advance and then attached together between the cycloidal disk 2 and the pin housing 4.
  • the bearing capacity of the soft rubber 55 is negligible in mechanical analysis.
  • the both ends of the solid roller 53 are set slightly thinner, that is, the solid roller 53 is formed into a waist drum type.
  • the length of the solid roller 53 in the axial direction is also set to be slightly smaller than the length of the hollow roller 52, so that both ends of the solid roller 53 are retracted into the hollow roller 52.
  • an elastic member 56 is further disposed in the floating gap 54.
  • the elastic member 56 is a spring that is sleeved around the solid roller 53 and is wound by a round spring wire.
  • the flat spring-shaped spring wire may be wound around the periphery of the solid roller 53; in addition, as another embodiment, the elastic member 56 may also be disposed around the solid roller 53. Wavy metal tube.
  • the wall thickness of the hollow roller 52 can be relatively thinner than that of the first and second embodiments due to the further support and elasticity of the elastic member 56. The arrangement allows the elastic roller 51 of the present invention to have greater flexibility and resistance to overloading.
  • the elastic member 56 when the elastic member 56 is a spring, the spring is not disposed to be sandwiched between the hollow roller 52 and the solid roller 53, that is, between the hollow roller 52 and the spring 56, the spring 56 and the solid roller 53
  • the floating gap 54 still exists; thus, the floating gap 54 includes a first gap 541 disposed between the hollow roller 52 and the spring 56 and a second gap 542 disposed between the spring 56 and the solid roller 53.
  • the first gap 541 and the second gap 542 are in the radial direction of 0.003-0.007 times the outer diameter of the hollow roller 52. .
  • the elastic roller 51 When the elastic roller 51 is subjected to an external force impact by such an arrangement, it can be supported by the hollow roller 52, the spring 56 and the solid roller 53 in turn, and at the same time, the elastic compensation of the hollow roller 52 at the first gap 541, The spring compensation of the spring 56 itself and the spring 56 are elastically compensated in the second gap 542, so that the load and compensation effects are better.
  • the elastic member 56 When the elastic member 56 is a wavy metal tube, the elastic member 56 may be clamped between the hollow roller 52 and the solid roller 53, or may exist between the hollow roller 52 and the solid roller 53.
  • the floating gap 54 is at a time between 0.003 and 0.007 times the outer diameter of the hollow roller 52 along the inner wall surface of the hollow roller 52 or the outer wall surface of the solid roller 53.
  • the bearing 3 between the crankshaft 1 and the cycloidal disc 2 is also a weak link.
  • the bearing 3 generally includes spaced outer bearing rings 31 and inner bearing rings 32, a plurality of rollers disposed between the outer bearing rings 31 and the inner bearing rings 32 and uniformly disposed.
  • the rollers in the bearing use solid and inelastic rollers. Due to machining errors and the like, such as the roller portion, the number of rollers that actually participate in the bearing at the same time in the prior art is relatively small, and the roller is easy. The same is true for the inner and outer bearing rings in the bearing.
  • the roller 33 of the bearing 3 is also set to be elastic with reference to various embodiments of the elastic roller 51, so that the bearing 3 can also be carried as described in the above-mentioned elastic roller 51.
  • the rate is effectively ensured, and the manufacturing precision of the bearing 3 can also be reduced.
  • the bearing 3 of the present invention is also applicable to other products (not shown) where a bearing needs to be provided.
  • the bearing 3 is provided with the outer bearing ring 31 and the inner bearing ring 32 to respectively form the outer race and the inner race of the roller 33; and the bearing 3 is applied to the needle of the present invention.
  • the outer bearing ring 31 and the inner bearing ring 32 can also be directly constituted by the cycloidal disk 2 and the crank shaft 1, that is, the inner wall of the perforation 21 on the cycloidal disk 2 is directly Formed as the outer race, the cam outer surface of the crankshaft 1 is formed as an inner race, whereby the roller 33 can be clamped between the inner wall of the bore 21 and the outer surface of the cam of the crankshaft 1, on the one hand
  • the component can be reduced, the cost can be reduced, and on the other hand, the superposition of the errors can be reduced, so that the manufacturing error between the cycloidal disk 2 and the crankshaft 1 or the roller 33 itself can be offset directly by the elastic arrangement of the roller 33, and
  • the roller 33 has a better bearing effect.
  • the diameter of the roller 33 is set to be slightly larger than the gap between the inner raceway and the outer raceway, so that in the static state, the rollers 33 are all flattened and slightly elliptical in a prestressed state, squeezed in There will be no vacancies between the inner raceway and the outer raceway, so that no individual rollers 33 will be damaged by overload, and the inner raceway and outer raceway surfaces are also effectively protected.
  • the present invention is manufactured by combining the elastic rollers 51, 33 in a hollow combination, that is, the hollow roller 52 is located on the outer side, and the solid roller 53 is filled inside the hollow roller 52, and in the hollow roller 52 and A floating gap 54 is formed between the solid rollers 53 for deforming the hollow rollers 52, thereby providing a certain elastic deformation space of the hollow rollers 52 through the floating gaps 54, thereby achieving sufficient elasticity when the interference fit is selected.
  • the compensating ability at the same time, can provide a certain supporting force through the inner solid roller 53 to prevent the hollow roller 52 from being crushed and broken due to an excessive load, so that the elastic rollers 51, 33 have a strong overload shock resistance.
  • the arrangement of the middle elastic rollers 51, 33 can also reduce the manufacturing precision of the roller, the cycloidal disc and the pin gear housing in the prior art, and is convenient to manufacture, and the structure is relatively simple. And low manufacturing cost.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • Rolls And Other Rotary Bodies (AREA)

Abstract

L'invention concerne un rouleau élastique, un réducteur de vitesse cycloïdal à engrenage à broche (100) comportant le rouleau élastique (51), et un palier (3). Le rouleau élastique (51) comprend un rouleau creux (52) et un rouleau plein (53) disposé sur le côté interne du rouleau creux (52). Un espace flottant permettant au cylindre creux (52) de se déformer de manière élastique est situé entre une face de paroi interne du rouleau creux (52) et une face de paroi externe du rouleau plein (53). Le rouleau élastique (51) peut constituer une certain espace de déformation élastique pour le rouleau creux (52) à l'aide de l'espace flottant de façon à être apte à produire une capacité de compensation élastique suffisante lors de l'utilisation d'une adaptation à interférence ; en même temps, une certaine force de support peut être délivrée par le rouleau plein (53) sur un côté interne, empêchant le rouleau creux (52) d'être aplati et détruit du fait d'une charge excessive, de telle sorte que le rouleau élastique (51) a une forte résistance à l'impact de surcharge, qu'il est relativement fort, et qu'il ne peut pas être détruit, de manière à réaliser le but de compensation élastique fiable et, en outre, d'accroître la durée de vie du rouleau élastique, du réducteur de vitesse cycloïdal à engrenage à broche et du palier.
PCT/CN2016/075141 2015-09-30 2016-03-01 Rouleau élastique, réducteur cycloïdal à engrenage à broche et palier WO2017054409A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201510640442.7A CN105134906B (zh) 2015-09-30 2015-09-30 弹性滚柱、针齿摆线减速器和轴承
CN201510640442.7 2015-09-30

Publications (1)

Publication Number Publication Date
WO2017054409A1 true WO2017054409A1 (fr) 2017-04-06

Family

ID=54720385

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2016/075141 WO2017054409A1 (fr) 2015-09-30 2016-03-01 Rouleau élastique, réducteur cycloïdal à engrenage à broche et palier

Country Status (3)

Country Link
CN (1) CN105134906B (fr)
TW (1) TWI608180B (fr)
WO (1) WO2017054409A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105134906B (zh) * 2015-09-30 2019-04-05 昆山光腾智能机械有限公司 弹性滚柱、针齿摆线减速器和轴承
CN108730423B (zh) * 2017-04-17 2024-08-06 昆山光腾智能机械有限公司 具有弹性补偿的针齿摆线减速器
CN108506428B (zh) * 2018-06-12 2024-08-06 昆山光腾智能机械有限公司 传动滚柱及具有其的针齿摆线减速器、轴承
WO2019237238A1 (fr) * 2018-06-12 2019-12-19 昆山光腾智能机械有限公司 Rouleau de transmission, réducteur de vitesse de broche cycloïdale pourvu de celui-ci et palier
WO2020062122A1 (fr) * 2018-09-29 2020-04-02 昆山光腾智能机械有限公司 Réducteur de vitesse cycloïdal à engrenage à broche, rouleaux de broche de transmission et palier
CN108980286A (zh) * 2018-09-29 2018-12-11 昆山光腾智能机械有限公司 针齿摆线减速器、传动滚柱和轴承

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009079997A2 (fr) * 2007-12-22 2009-07-02 Schaeffler Kg Corps de roulement comprenant un rouleau creux et un corps de surcharge
CN102678757A (zh) * 2012-05-31 2012-09-19 中国人民解放军国防科学技术大学 填充型滚子和基于填充型滚子的滚子轴承
CN204533212U (zh) * 2015-03-21 2015-08-05 安庆石化联盟铸管厂 一种填充式轴承滚子
CN204647165U (zh) * 2015-05-07 2015-09-16 昆山光腾智能机械有限公司 针齿摆线减速器
CN105134906A (zh) * 2015-09-30 2015-12-09 昆山光腾智能机械有限公司 弹性滚柱、针齿摆线减速器和轴承
CN205013636U (zh) * 2015-09-30 2016-02-03 昆山光腾智能机械有限公司 弹性滚柱、针齿摆线减速器和轴承

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE507577C (de) * 1927-07-02 1930-09-22 Robert Richard Gobereau Rollkoerperlager
US3765071A (en) * 1972-09-07 1973-10-16 W Bowen Method of forming a roller bearing of superior runout characteristics
JPS52156254A (en) * 1976-06-21 1977-12-26 Suehiro Seikou Kk Multiplex bearing
JP2007285397A (ja) * 2006-04-17 2007-11-01 Press Kogyo Co Ltd ころ軸受
CN201144980Y (zh) * 2008-01-16 2008-11-05 陆维钊 滚柱超越离合器
CN103573822A (zh) * 2013-10-29 2014-02-12 河南三维重工有限公司 一种用于调心滚子轴承的滚动体
CN103939475A (zh) * 2014-01-17 2014-07-23 姜立平 高承载性复合材料滚柱

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009079997A2 (fr) * 2007-12-22 2009-07-02 Schaeffler Kg Corps de roulement comprenant un rouleau creux et un corps de surcharge
CN102678757A (zh) * 2012-05-31 2012-09-19 中国人民解放军国防科学技术大学 填充型滚子和基于填充型滚子的滚子轴承
CN204533212U (zh) * 2015-03-21 2015-08-05 安庆石化联盟铸管厂 一种填充式轴承滚子
CN204647165U (zh) * 2015-05-07 2015-09-16 昆山光腾智能机械有限公司 针齿摆线减速器
CN105134906A (zh) * 2015-09-30 2015-12-09 昆山光腾智能机械有限公司 弹性滚柱、针齿摆线减速器和轴承
CN205013636U (zh) * 2015-09-30 2016-02-03 昆山光腾智能机械有限公司 弹性滚柱、针齿摆线减速器和轴承

Also Published As

Publication number Publication date
TWI608180B (zh) 2017-12-11
TW201712244A (zh) 2017-04-01
CN105134906A (zh) 2015-12-09
CN105134906B (zh) 2019-04-05

Similar Documents

Publication Publication Date Title
WO2017054409A1 (fr) Rouleau élastique, réducteur cycloïdal à engrenage à broche et palier
US10161480B2 (en) Eccentric oscillating speed reducer
US9939017B2 (en) Ball bearing for strain wave gearing
KR101740421B1 (ko) 휨 맞물림식 기어장치
KR20180064288A (ko) 감속장치
WO2011132580A1 (fr) Dispositif de ralentissement
WO2017006442A1 (fr) Dispositif d'engrenage à mouvement ondulatoire, et générateur d'ondes
JP6432338B2 (ja) 波動減速機用の玉軸受
RU2460916C1 (ru) Планетарная передача
JP5797131B2 (ja) 遊星歯車減速機
US20190309839A1 (en) Novel assembly of a flexspline and a wave generator for a harmonic gear drive
JP6604411B2 (ja) 波動減速機用の玉軸受
JP2006214540A (ja) 摺動式等速自在継手
JP7304684B2 (ja) 締結機構、締結物品および産業機械
WO2020062122A1 (fr) Réducteur de vitesse cycloïdal à engrenage à broche, rouleaux de broche de transmission et palier
JP4554586B2 (ja) 内接噛合型遊星歯車装置
JP5445961B2 (ja) 減速装置
WO2019237238A1 (fr) Rouleau de transmission, réducteur de vitesse de broche cycloïdale pourvu de celui-ci et palier
KR102257216B1 (ko) 하모닉 감속기
WO2012086327A1 (fr) Dispositif de transmission à engrenages
JP7170455B2 (ja) 締結構造および産業機械
JP2020012474A (ja) 玉軸受の組立方法
JP2014228015A (ja) 可撓式歯車
US10578161B2 (en) Spacer for rolling bearing, notably used in a wind turbine
CN211231515U (zh) 减速机偏心传动机构

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: 16850037

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: 16850037

Country of ref document: EP

Kind code of ref document: A1

122 Ep: pct application non-entry in european phase

Ref document number: 16850037

Country of ref document: EP

Kind code of ref document: A1

32PN Ep: public notification in the ep bulletin as address of the adressee cannot be established

Free format text: NOTING OF LOSS OF RIGHTS PURSUANT TO RULE 112(1) EPC (EPO FORM 1205A DATED 28/09/2018)

122 Ep: pct application non-entry in european phase

Ref document number: 16850037

Country of ref document: EP

Kind code of ref document: A1