JP2009275853A - Output part structure of reduction gear - Google Patents

Output part structure of reduction gear Download PDF

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Publication number
JP2009275853A
JP2009275853A JP2008128826A JP2008128826A JP2009275853A JP 2009275853 A JP2009275853 A JP 2009275853A JP 2008128826 A JP2008128826 A JP 2008128826A JP 2008128826 A JP2008128826 A JP 2008128826A JP 2009275853 A JP2009275853 A JP 2009275853A
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Prior art keywords
ring member
inner ring
outer ring
rolling
bearing
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JP5074292B2 (en
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Masayuki Ishizuka
正幸 石塚
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Sumitomo Heavy Industries Ltd
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Sumitomo Heavy Industries Ltd
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Priority to JP2008128826A priority Critical patent/JP5074292B2/en
Priority to CN2009101329072A priority patent/CN101581359B/en
Priority to TW098112497A priority patent/TWI369457B/en
Priority to DE102009019040A priority patent/DE102009019040A1/en
Priority to KR1020090041595A priority patent/KR101033810B1/en
Publication of JP2009275853A publication Critical patent/JP2009275853A/en
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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
    • 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
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/02—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type
    • 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/02—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for connecting two abutting shafts or the like
    • 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
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • 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

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • General Details Of Gearings (AREA)
  • Rolling Contact Bearings (AREA)
  • Braking Arrangements (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To reduce the number of parts, to relax the management of dimension at the time of manufacturing, and to achieve connection between the reduction gear and its partner machine at a low cost and with a precise dimensional accuracy. <P>SOLUTION: The output part structure of a reduction gear is provided with an inner ring member 54, a rolling member 56, and an outer ring member 58 which constitutes a large bearing 52. The inner ring member 54 is connected to a driven shaft of a partner machine 24 as the output member of the reduction gear 22, and the outer periphery 58B of the outer ring member 58 is engaged with part of the inner periphery 46A of the (second) main unit casing 46 of the reduction gear 22 and part of the inner periphery 50A of the connecting casing 50 of the partner machine 24 to function as pillbox sections E2, E3 which provide criteria at the time of attachment. The large bearing 52 receives axial loads in both directions of the inner ring member 54 and a driven shaft connected to the inner ring member 54 by the inner ring member 54, the rolling member 56, and the outer ring member 58. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、減速機を相手機械（被駆動機械）に連結するための、減速機の出力部構造に関する。   The present invention relates to an output part structure of a speed reducer for connecting the speed reducer to a counterpart machine (driven machine).

減速機は、モータ等の駆動源の回転を減速し、相手機械の被駆動軸に伝達する。そのため、減速機の出力側においては、減速機の本体ケーシング（固定系）を相手機械の連結ケーシングに連結する必要がある。また、減速機の出力部材（回転系）を相手機械の被駆動軸と連結する必要がある。   The speed reducer decelerates the rotation of a drive source such as a motor and transmits it to the driven shaft of the counterpart machine. Therefore, on the output side of the speed reducer, it is necessary to connect the main body casing (fixed system) of the speed reducer to the connection casing of the counterpart machine. Moreover, it is necessary to connect the output member (rotating system) of the reduction gear to the driven shaft of the counterpart machine.

図３に、特許文献１にて開示された減速機２を示す。   FIG. 3 shows the speed reducer 2 disclosed in Patent Document 1.

減速機２の本体ケーシング４の内周４Ａには一対の軸受６、８が配置され、この一対の軸受６、８を介して出力部材１０が本体ケーシング４に回転自在に支持されている。   A pair of bearings 6 and 8 are disposed on the inner periphery 4 </ b> A of the main body casing 4 of the speed reducer 2, and the output member 10 is rotatably supported by the main body casing 4 through the pair of bearings 6 and 8.

この基本構成の下で、減速機２の本体ケーシング４の外周４Ｂに形成された印籠部（いんろう部）Ｅ１を用いて該減速機２の本体ケーシング（固定系）４が相手機械１２の連結ケーシング１４に連結される。なお、この明細書において「印籠部」とは、２つの部材が当接する際に各部材の取付位置の基準を提供する嵌合部のことを意味している。即ち、減速機２の本体ケーシング４の外周４Ｂに形成した印籠部Ｅ１が相手機械１２の連結ケーシング１４の内周１４Ａと嵌合することにより、減速機２の本体ケーシング４と相手機械１２の連結ケーシング１４の軸心合わせ及び軸方向の位置合わせが行なわれるようになっている。   Under this basic configuration, the main casing (fixed system) 4 of the speed reducer 2 is connected to the mating machine 12 by using the stamping part (welding part) E1 formed on the outer periphery 4B of the main body casing 4 of the speed reducer 2. Connected to the casing 14. In this specification, “an imprinting portion” means a fitting portion that provides a reference for the mounting position of each member when the two members come into contact with each other. That is, the stamped part E1 formed on the outer periphery 4B of the body casing 4 of the speed reducer 2 is engaged with the inner periphery 14A of the connection casing 14 of the counterpart machine 12, thereby connecting the main body casing 4 of the speed reducer 2 and the counterpart machine 12. The casing 14 is axially aligned and aligned in the axial direction.

また、本体ケーシング４に軸受６、８を介して支持された出力部材（回転系）１０は、この特許文献１に係る例では中実の出力軸として構成され、図示せぬキーを介して相手機械１２の被駆動軸（図示略）と連結される。   Further, the output member (rotary system) 10 supported by the main body casing 4 via the bearings 6 and 8 is configured as a solid output shaft in the example according to Patent Document 1, and is opposed to the other party via a key (not shown). It is connected to a driven shaft (not shown) of the machine 12.

特開２００６−２２６３４７号公報JP 2006-226347 A

しかしながら、このような出力部構造にあっては、例えば、減速機の本体ケーシングの外周は印籠部として機能するため、正確な加工が必要である。また、本体ケーシングの内周も、軸受の受け面を構成するため、やはり精密な加工が必要である。出力部材を支持する軸受は、汎用品を用いるにしろ、内製するにしろ、遊び（がた）の寸法管理を含め、その内輪、外輪、転動体の全てについて相応の寸法管理が必要である。更に、出力部材の外周も、当然精密な加工が必要である。   However, in such an output part structure, for example, the outer periphery of the main body casing of the speed reducer functions as a stamping part, and therefore requires accurate processing. Moreover, since the inner periphery of the main body casing also constitutes the bearing surface of the bearing, it must be precisely processed. Whether the bearing that supports the output member is a general-purpose product or manufactured in-house, it is necessary to appropriately manage the dimensions of the inner ring, outer ring, and rolling elements, including the dimension control of play. . Furthermore, the outer periphery of the output member also needs to be precisely processed.

換言するならば、減速機の本体ケーシングの外周及び内周、軸受の外輪の外周及び内周、転動体の径、軸受の内輪の外周及び内周、そして出力部材の外周の全ての半径方向の寸法が適正に管理されないと、誤差の累積により減速機の本体ケーシングの軸心と相手機械の連結ケーシングの軸心、あるいは減速機の出力部材の軸心と相手機械の被駆動軸の軸心とを正確に一致させることができなくなる。そのため、上記各部の製造時の寸法管理には厳密なものが要求され、又部品点数も多く、製造コストが高くなり易かった。   In other words, the outer circumference and inner circumference of the main casing of the speed reducer, the outer circumference and inner circumference of the outer ring of the bearing, the diameter of the rolling element, the outer circumference and inner circumference of the inner ring of the bearing, and all the radial directions of the outer circumference of the output member If the dimensions are not properly controlled, the accumulation of errors will cause the shaft center of the reducer body casing and the axis of the connecting casing of the counterpart machine, or the axis of the output member of the reducer and the axis of the driven shaft of the counterpart machine. Cannot be matched exactly. For this reason, strict management is required for the dimensional management at the time of manufacturing each of the above parts, the number of parts is large, and the manufacturing cost tends to be high.

本発明は、このような従来の問題を解消するためになされたものであって、部品点数を削減すると共に、製造時の寸法の管理を緩和し、低コストで且つ正確な寸法精度で減速機と相手機械とを連結できるようにすることをその課題としている。   The present invention has been made to solve such a conventional problem, and reduces the number of parts, eases the management of dimensions during manufacturing, and reduces the speed reducer with low cost and accurate dimensional accuracy. The problem is to be able to connect the machine and the other machine.

本発明は、減速機を被駆動機械に取り付け可能に構成した減速機の出力部構造において、軸受の内輪を構成する内輪部材と、前記軸受の転動体を構成する転動部材と、前記軸受の外輪を構成する外輪部材と、を備え、前記内輪部材が、前記減速機の出力部材として前記相手機械の被駆動軸側と連結され、前記外輪部材が、減速機の本体ケーシングの内周及び前記相手機械の連結ケーシングの内周と嵌合して取付の際の基準を提供する印籠部として機能し、前記軸受が、前記内輪部材、転動部材、及び外輪部材により、前記内輪部材及び該内輪部材と連結される前記被駆動軸の両方向のアキシャル荷重を受け持つことにより、上記課題を解決した。   The present invention relates to an output part structure of a speed reducer configured such that the speed reducer can be attached to a driven machine, an inner ring member constituting an inner ring of the bearing, a rolling member constituting a rolling element of the bearing, and the bearing An outer ring member constituting an outer ring, wherein the inner ring member is connected to a driven shaft side of the counterpart machine as an output member of the speed reducer, and the outer ring member is connected to an inner periphery of the main body casing of the speed reducer and the The inner ring member and the inner ring function as an indicia portion that fits with the inner circumference of the connection casing of the counterpart machine and provides a reference for installation, and the bearing is constituted by the inner ring member, the rolling member, and the outer ring member. The above problem has been solved by taking the axial load in both directions of the driven shaft connected to the member.

本発明によれば、出力側が全体として巨大な軸受を構成し、該軸受の内輪が出力部材として機能すると共に、外輪の外周が減速機の本体ケーシング及び相手機械の連結ケーシングの双方の印籠部として直接機能する。そのため、部品点数を低減できると共に、精密な寸法管理の要求される部位の数を低減でき、低コストで正確な寸法精度を維持することができる。   According to the present invention, the output side constitutes a huge bearing as a whole, the inner ring of the bearing functions as an output member, and the outer periphery of the outer ring serves as an imprinting part for both the main body casing of the reduction gear and the connecting casing of the counterpart machine. Works directly. Therefore, the number of parts can be reduced, the number of parts required for precise dimensional management can be reduced, and accurate dimensional accuracy can be maintained at low cost.

本発明によれば、製造時の寸法の管理及び部品の管理を緩和し、低コストで且つ正確な寸法精度で減速機と相手機械とを連結できる。   ADVANTAGE OF THE INVENTION According to this invention, management of the dimension at the time of manufacture and management of components can be eased, and a reduction gear and a counterpart machine can be connected with low cost and exact dimensional accuracy.

以下、図面を参照しながら本発明の実施形態の一例について詳細に説明する。   Hereinafter, an example of an embodiment of the present invention will be described in detail with reference to the drawings.

図１は、本発明の実施形態の一例に係る減速機の出力部構造を示す断面図である。この例では、モータ２０と一体化された減速機２２が相手機械（被駆動機械）２４に連結される様子が示されている。   FIG. 1 is a cross-sectional view showing an output part structure of a reduction gear according to an example of an embodiment of the present invention. In this example, a state in which the speed reducer 22 integrated with the motor 20 is connected to a counterpart machine (driven machine) 24 is shown.

モータ２０は、モータケーシング２６のフランジ部２６Ａにおいてボルト（図示略：中心線のみ図示）を介して減速機２２の第１本体ケーシング２８と連結されている。モータ２０のモータ軸３２は、摩擦締結機構３４を備えた継軸３６と連結されている。継軸３６は、玉軸受４０を介して減速機２２の第１本体ケーシング２８に支持されている。継軸３６の中空部３６Ａには、減速機２２の入力軸に相当する太陽歯車３８が圧入されている。   The motor 20 is connected to the first main body casing 28 of the speed reducer 22 via a bolt (not shown: only the center line is shown) at the flange portion 26 </ b> A of the motor casing 26. The motor shaft 32 of the motor 20 is connected to a joint shaft 36 provided with a friction fastening mechanism 34. The joint shaft 36 is supported by the first main body casing 28 of the speed reducer 22 via a ball bearing 40. A sun gear 38 corresponding to the input shaft of the speed reducer 22 is press-fitted into the hollow portion 36 </ b> A of the joint shaft 36.

減速機２２は、単純遊星歯車機構の減速部３０を備える。減速部３０は、前記太陽歯車３８と、該太陽歯車３８の周りで自転しながら公転する複数の遊星歯車４２と、該遊星歯車４２が内接噛合する内歯歯車４４を備えている。遊星歯車４２は、ニードル軸受４３を介して遊星ピン４５に支持されている。遊星ピン４５はキャリヤ４８に支持されている。このため、キャリヤ４８は、遊星歯車４２の公転と同期して自転する。この例では、キャリヤ４８はキャリヤプレート４８Ａとキャリヤピン４８Ｂとで構成され、ボルト６０を介して後述する内輪部材５４に締結・固定されている。即ち、この減速機２２では、キャリヤ４８及び内輪部材５４とで、出力部材が構成され、キャリヤ４８の回転が当該減速機２２の出力回転として内輪部材５４から取り出される。なお、内歯歯車４４は減速機２２の第２本体ケーシング４６と一体化されている。   The speed reducer 22 includes a speed reducing unit 30 of a simple planetary gear mechanism. The speed reduction unit 30 includes the sun gear 38, a plurality of planetary gears 42 that revolve while rotating around the sun gear 38, and an internal gear 44 with which the planetary gear 42 meshes internally. The planetary gear 42 is supported by the planetary pin 45 via the needle bearing 43. The planet pin 45 is supported by the carrier 48. For this reason, the carrier 48 rotates in synchronization with the revolution of the planetary gear 42. In this example, the carrier 48 includes a carrier plate 48A and a carrier pin 48B, and is fastened and fixed to an inner ring member 54 described later via a bolt 60. That is, in the speed reducer 22, the carrier 48 and the inner ring member 54 constitute an output member, and the rotation of the carrier 48 is taken out from the inner ring member 54 as the output rotation of the speed reducer 22. The internal gear 44 is integrated with the second main body casing 46 of the speed reducer 22.

減速機２２は、モータ２０を連結した状態で、第２本体ケーシング４６のボルト挿入孔４９にボルト（図示略）を挿入して相手機械２４の連結ケーシング５０に締結・固定される。   The speed reducer 22 is fastened and fixed to the connection casing 50 of the counterpart machine 24 by inserting a bolt (not shown) into the bolt insertion hole 49 of the second main body casing 46 with the motor 20 connected.

以下この減速機２２の出力部構造について詳細に説明する。   Hereinafter, the output part structure of the speed reducer 22 will be described in detail.

この出力部構造は、大軸受５２をその主要構成要素として備える。この大軸受５２は、該大軸受５２の内輪を構成する内輪部材５４と、該大軸受５２の転動体を構成する転動部材５６と、該大軸受５２の外輪を構成する外輪部材５８を備える。   This output portion structure includes a large bearing 52 as its main component. The large bearing 52 includes an inner ring member 54 constituting an inner ring of the large bearing 52, a rolling member 56 constituting a rolling element of the large bearing 52, and an outer ring member 58 constituting an outer ring of the large bearing 52. .

大軸受５２の内輪部材５４は、ほぼ円柱状のブロックで、前述したようにボルト６０を介して減速部３０の前記キャリヤ４８と連結され、該キャリヤ４８と共に減速機２２の「出力部材」として機能する。この実施形態では、ボルト６４を介して図の左側から出力軸ブロック６２が該内輪部材５４に付設され、相手機械２４の図示せぬ被駆動軸側にキー（キー溝６２Ａのみ図示）を介して連結されることにより、動力を伝達する構成とされている。なお、出力軸ブロック６２を付設した動力伝達に代え、例えばボルト６４のボルト孔６６を利用して相手機械２４の被駆動軸を直接内輪部材５４と連結するような構成としてもよい。内輪部材５４には、転動部材５６が組み込まれる開度９０度のＶ溝５４Ａが形成されており、後述する外輪部材５８にも対応する開度９０度のＶ溝５８Ａが形成されている。   The inner ring member 54 of the large bearing 52 is a substantially cylindrical block, which is connected to the carrier 48 of the speed reduction unit 30 via the bolt 60 as described above, and functions as an “output member” of the speed reducer 22 together with the carrier 48. To do. In this embodiment, an output shaft block 62 is attached to the inner ring member 54 from the left side of the figure via a bolt 64, and a key (only the key groove 62A is shown) is provided on the driven shaft side (not shown) of the counterpart machine 24. It is set as the structure which transmits motive power by being connected. Instead of the power transmission provided with the output shaft block 62, for example, the driven shaft of the counterpart machine 24 may be directly connected to the inner ring member 54 using the bolt hole 66 of the bolt 64. The inner ring member 54 is formed with a V-groove 54A having an opening of 90 degrees into which the rolling member 56 is incorporated, and a V-groove 58A having an opening of 90 degrees corresponding to an outer ring member 58 described later is also formed.

大軸受５２の転動部材５６は、直径と軸長が等しいローラ（図示略）で構成され、該ローラを交互に９０度向きを変えて前記内輪部材５４のＶ溝５４Ａと外輪部材５８のＶ溝５８Ａとの間に組み込んだ構成とされている。これにより、大軸受５２は、全体として、いわゆるクロスローラ軸受を構成している。クロスローラ軸受では、転動部材５６の軌道平面（転動部材の５６の重心を含む軸Ｏ１と直角の平面）Ｔ１が１面のみ存在し、また、構造上、ラジアル荷重と、両方向のアキシャル荷重の全てを受け持つことができる。なお、この転動部材５６は、外輪部材５８の一部に半径方向に貫通形成された組込孔７１を介して１個ずつ組込まれる。   The rolling member 56 of the large bearing 52 is composed of a roller (not shown) having the same diameter and axial length, and the rollers are alternately turned 90 degrees to change the V groove 54A of the inner ring member 54 and the V of the outer ring member 58. The structure is incorporated between the groove 58A. Thereby, the large bearing 52 comprises what is called a cross roller bearing as a whole. In the cross roller bearing, there is only one raceway plane (a plane perpendicular to the axis O1 including the center of gravity of the rolling member 56) T1 of the rolling member 56, and the radial load and the axial load in both directions are structurally provided. Can take charge of everything. In addition, this rolling member 56 is assembled one by one through a built-in hole 71 formed in a part of the outer ring member 58 in a radial direction.

大軸受５２の外輪部材５８は、減速機２２の端部ケーシングの機能を兼用している。外輪部材５８の外周５８Ｂは、段差の無い単純な円筒形状とされている。この実施形態では、この外輪部材５８の外周５８Ｂが段差のない単純な円筒形状とされていることを利用して、いわゆるセンタレス研削盤（心無し研削盤：センタレスグラインダ）によって該外輪部材５８の外周５８Ｂを研削加工するようにしている。センタレス研削盤としては、ワークレスト（図示略）でワーク（この例では外輪部材５８）を支え、砥石を２個用いて研削を行うものが良く知られており、極めて真円に近い加工が可能である。   The outer ring member 58 of the large bearing 52 also serves as the end casing of the speed reducer 22. The outer periphery 58B of the outer ring member 58 has a simple cylindrical shape with no step. In this embodiment, the outer periphery 58B of the outer ring member 58 has a simple cylindrical shape without a step, and the outer periphery of the outer ring member 58 is so-called by a so-called centerless grinder (centerless grinder: centerless grinder). 58B is ground. As a centerless grinding machine, it is well known that a work rest (not shown) supports a work (in this example, the outer ring member 58) and grinds using two grindstones, and machining close to a perfect circle is possible. It is.

外輪部材５８の外周５８Ｂは、減速機２２の第２本体ケーシング４６の内周４６Ａ（の一部）と嵌合する減速機側印籠部Ｅ２及び相手機械２４の連結ケーシング５０の内周５０Ａ（の一部）と嵌合する相手機械側印籠部Ｅ３として機能する。即ち、該減速機側印籠部Ｅ２及び相手機械側印籠部Ｅ３の機能により、第２本体ケーシング４６及び大軸受５２のそれぞれの軸心Ｏ１が一致させられる。又、相手機械２４の連結ケーシング５０の端面５０Ｃが第２本体ケーシング４６のフランジ部４６Ｂの端面４６Ｃと当接することによって、連結ケーシング５０の外輪部材５８の外周５８Ｂ上における軸方向の位置決めがなされるようになっている。なお、第２本体ケーシング４６のフランジ部４６Ｂは、該第２本体ケーシング４６の円周方向全体に形成されているのではなく、いわゆる「耳部」と称せられる態様で、円周方向の４箇所において軸方向に若干延在されると共に、半径方向に突出形成されている。   The outer periphery 58B of the outer ring member 58 is connected to the inner periphery 46A (a part of) the inner periphery 46A of the second main body casing 46 of the speed reducer 22 and the inner periphery 50A (of the connection casing 50 of the counterpart machine 24). It functions as a mating machine side stamping part E3 to be fitted with a part). That is, the axes O1 of the second main body casing 46 and the large bearing 52 are made to coincide with each other by the functions of the reduction gear side stamping part E2 and the counterpart machine side stamping part E3. Further, the end surface 50C of the connection casing 50 of the counterpart machine 24 contacts the end surface 46C of the flange portion 46B of the second main body casing 46, whereby the axial positioning on the outer periphery 58B of the outer ring member 58 of the connection casing 50 is performed. It is like that. The flange portion 46B of the second main body casing 46 is not formed in the entire circumferential direction of the second main body casing 46, but is a so-called “ear portion”. Are slightly extended in the axial direction and protruded in the radial direction.

図１から明らかなように、この実施形態では、外輪部材５８の外周５８Ｂの大半が相手機械２４の連結ケーシング５０と嵌合されている。即ち、外輪部材５８の外周５８Ｂの大半が相手機械２４の連結ケーシング５０の印籠部として機能していることになる。   As is clear from FIG. 1, in this embodiment, most of the outer periphery 58 </ b> B of the outer ring member 58 is fitted with the connection casing 50 of the counterpart machine 24. That is, most of the outer periphery 58 </ b> B of the outer ring member 58 functions as a stamping part of the connection casing 50 of the counterpart machine 24.

これを転動部材５６との関係で見るならば、外輪部材５８の外周５８Ｂにおいて、減速機側印籠部Ｅ２と相手機械側印籠部Ｅ３のうち、相手機械側印籠部Ｅ３の方が長く設定されている。また、前記転動部材５６の軌道平面Ｔ１が、該長く設定された相手機械側印籠部Ｅ３の半径方向内側に収められている、ということになる。   If this is viewed in relation to the rolling member 56, the other machine side stamping part E3 is set longer than the speed reducer side stamping part E2 and the partner machine side stamping part E3 on the outer periphery 58B of the outer ring member 58. ing. In addition, the raceway plane T1 of the rolling member 56 is housed inside in the radial direction of the mating machine side stamping part E3 set to be long.

なお、この実施形態は、出力部が全体として大きな軸受を形成するように構成したものであって、内輪部材５４及び外輪部材５８は、いわゆる「軸受鋼」で形成されているわけではない。したがって、転動部材５６の転送面（内輪部材５４のＶ溝５４Ａ、外輪部材５８のＶ溝５８Ａ）は、別途の硬化処理が必要である。そのため、該Ｖ溝５４Ａ、５８Ａの付近は、素材が硬くなるため、遊星ピン４５のピン孔４７やボルト孔６６等の各孔類は、この硬くなった付近での加工を避けるべく、「貫通孔」としないように配慮し、結果として軟らかい部分に各孔類を容易に且つ高精度に形成している。形状的には、その結果として、内輪部材５４には、孔の全く形成されていない（全て中実の）軸と直角の断面Ｐ１が存在している。   In this embodiment, the output portion is configured to form a large bearing as a whole, and the inner ring member 54 and the outer ring member 58 are not formed of so-called “bearing steel”. Therefore, the transfer surface of the rolling member 56 (the V groove 54A of the inner ring member 54 and the V groove 58A of the outer ring member 58) needs to be separately cured. Therefore, since the material is hard in the vicinity of the V grooves 54A and 58A, each of the holes such as the pin hole 47 and the bolt hole 66 of the planetary pin 45 is “through-hole” in order to avoid processing in the vicinity of the hardened hole. As a result, each hole is easily and highly accurately formed in the soft part. In terms of shape, as a result, the inner ring member 54 has a cross section P1 perpendicular to the axis (all solid) in which no hole is formed.

なお、図１の符号７０は、減速機２２の内外をシールするために、内輪部材５４と外輪部材５８との間に配置されたオイルシールである。   1 is an oil seal disposed between the inner ring member 54 and the outer ring member 58 in order to seal the inside and outside of the speed reducer 22.

次に、上記出力部構造を有したギヤドモータの作用を説明する。   Next, the operation of the geared motor having the output part structure will be described.

モータ２０の出力軸３２の回転すると、継軸３６を介して減速機２２の入力軸である太陽歯車３８が回転する。この減速機２２では、減速部３０の内歯歯車４４が固定状態にあるので、遊星歯車４２の公転成分がキャリヤ４８から取り出される。キャリヤ４８は、ボルト６０を介して大軸受５２の内輪部材５４と一体化されており、内輪部材５４は、出力軸ブロック６２とボルト６４を介して連結されているため、結局、出力軸ブロック６２が回転し、図示せぬキーを介して相手機械の被駆動軸が回転する。   When the output shaft 32 of the motor 20 rotates, the sun gear 38 that is the input shaft of the speed reducer 22 rotates through the joint shaft 36. In the speed reducer 22, since the internal gear 44 of the speed reduction unit 30 is in a fixed state, the revolution component of the planetary gear 42 is taken out from the carrier 48. Since the carrier 48 is integrated with the inner ring member 54 of the large bearing 52 via the bolt 60, and the inner ring member 54 is connected to the output shaft block 62 via the bolt 64, the output shaft block 62 is eventually obtained. Rotates, and the driven shaft of the counterpart machine rotates via a key (not shown).

ここで、内輪部材５４は、クロスローラ型の転動部材５６を介して外輪部材５８に支持されているため、ラジアル荷重と、両方向のアキシャル荷重の全てを受け持つことができ、結果として、内輪部材５４の軸ぶれ（モーメント成分）に対しても、対応可能である。   Here, since the inner ring member 54 is supported by the outer ring member 58 via the cross roller type rolling member 56, it can take charge of both radial load and axial load in both directions. As a result, the inner ring member It is possible to deal with 54 shaft shakes (moment components).

また、キャリヤ４８（キャリヤプレート４８Ａ及びキャリヤピン４８）は、この安定支持された内輪部材５４と一体化されているため、キャリヤプレート４８Ａの外周の軸受を省略することもできている。   Further, since the carrier 48 (the carrier plate 48A and the carrier pin 48) is integrated with the stably supported inner ring member 54, a bearing on the outer periphery of the carrier plate 48A can be omitted.

更に、クロスローラ型の転動部材５６は、９０度互い違いに組み込まれた「ローラ」によって構成されているため、がた（内輪部材５４及び外輪部材５８との間の遊び）がほとんどなく、内輪部材５４及び外輪部材５８を高い組付け精度で組み込むことができる。また、転動部材５６の軌道平面Ｔ１が１面しかないため、必要ならば大軸受５２の軸方向厚さをより薄く設計することも可能である。   Further, since the cross roller type rolling member 56 is constituted by “rollers” that are alternately mounted 90 degrees, there is almost no play (play between the inner ring member 54 and the outer ring member 58), and the inner ring The member 54 and the outer ring member 58 can be assembled with high assembly accuracy. Further, since there is only one raceway plane T1 of the rolling member 56, the axial thickness of the large bearing 52 can be designed to be thinner if necessary.

外輪部材５８は、その外周５８Ｂが、段差のない単純な円筒形状とされていることを活用して、センタレス研削盤で研削加工されているため、極めて真円に近い加工を行うことができている。また、外輪部材５８は、当該真円に近い外周５８Ｂにて、減速機２２の第２本体ケーシング４６のフランジ部４６Ｂ及び相手機械２４の連結ケーシング５０に嵌合している。ここで、減速機２２の第２本体ケーシング４６の嵌合される減速機側印籠部Ｅ２、及び相手機械２４の連結ケーシング５０の嵌合される相手機械側印籠部Ｅ３のうち、相手機械側印籠部Ｅ３の方がより長く（実際には、外周５８Ｂの殆ど全面に）設定されている。そのため、結局、外輪部材５８は、その真円に近い外周５８Ｂのほぼ全面に亘って嵌合支持されることになる。特に、この実施形態においては、「減速機２２」の嵌合される減速機側印籠部Ｅ２ではなく、「相手機械２４」の嵌合される相手機械側印籠部Ｅ３方を長く設定するようにしているため、相手機械という質量的に大きな部材によって嵌合支持されることになる。そのため、相手機械の連結ケーシングの剛性を支持のベースとしてそのまま利用することができ、一層高い剛性を確保できている。   The outer ring member 58 is ground by a centerless grinding machine by utilizing the fact that the outer periphery 58B has a simple cylindrical shape without a step, so that it can process extremely close to a perfect circle. Yes. Further, the outer ring member 58 is fitted to the flange portion 46B of the second main body casing 46 of the speed reducer 22 and the connection casing 50 of the counterpart machine 24 at the outer periphery 58B close to the perfect circle. Here, among the speed reducer side stamping part E2 to which the second main body casing 46 of the speed reducer 22 is fitted and the mating machine side stamping part E3 to which the connecting casing 50 of the mating machine 24 is fitted, the counter machine side stamping part. The portion E3 is set to be longer (in practice, almost the entire outer periphery 58B). Therefore, as a result, the outer ring member 58 is fitted and supported over almost the entire surface of the outer periphery 58B close to its perfect circle. In particular, in this embodiment, not the speed reducer side stamping part E2 to which the “reduction gear 22” is fitted, but the counterpart machine side stamping part E3 to which the “mating machine 24” is fitted is set longer. Therefore, it is fitted and supported by a mass member having a mass as a counterpart machine. Therefore, the rigidity of the connection casing of the counterpart machine can be used as it is as a support base, and a higher rigidity can be secured.

更に、このようにして、高い剛性で安定支持された外輪部材５８の相手機械側印籠部Ｅ３の半径方向内側に転動部材５６の転走面Ｔ１が配置されているから、（例えば印籠部の軸方向寸法が短くて該印籠部の軸方向位置から外れた位置の半径方向内側に転動部材５６の転送面がある構造に比べて）転動部材５６の側から伝達されてくるラジアル負荷やスラスト負荷、あるいはぶれ等のモーメント負荷を極めて安定して受け止めることができる。   Furthermore, since the rolling surface T1 of the rolling member 56 is arranged in the radial direction inside the mating machine side stamping part E3 of the outer ring member 58 stably supported with high rigidity in this way (for example, the stamping part A radial load transmitted from the side of the rolling member 56 (compared to a structure in which the axial dimension is short and the transfer surface of the rolling member 56 is located radially inside the position deviated from the axial position of the stamping portion) Thrust load or moment load such as shaking can be received very stably.

前述した従来例と詳細に比較するまでもなく、本実施形態では厳格な寸法管理の要求される加工面の数を最小限に抑えることができ、それだけ誤差の累積が少なく、高い寸法精度の確保された組付けが可能である。   Needless to compare in detail with the above-described conventional example, in this embodiment, the number of machining surfaces required for strict dimensional control can be minimized, the accumulation of errors is reduced, and high dimensional accuracy is ensured. Assembly is possible.

なお、上記実施形態においては、前記大軸受５２が全体として、クロスローラ軸受を構成するようにしていたが、本発明においては、必ずしも全体としてクロスローラ軸受を構成する必要はない。例えば、図２に示されるように、内輪部材１５４と外輪部材１５８との間に「転動部材」として、軸方向一方側のアキシャル荷重を受け止め可能な第１転動部材１５６Ａと、該第１転動部材１５６Ａと軸方向に離れて配置され、軸方向他方側のアキシャル荷重を受け止め可能な第２転動部材１５６Ｂとを配置して、大軸受１５２が、（第１、第２転動部材１５６Ａ、１５６Ｂの軌道平面Ｔ１０１Ａ、Ｔ１０１Ｂが２面存在する）アンギュラ軸受を構成するようにしても良い。この場合でも、大軸受１５２は、内輪部材１５４、第１、第２転動部材１５６Ａ、１５６Ｂ、及び外輪部材１５８により、全体として内輪部材１５４及び該内輪部材１５４と連結される相手機械１２４の被駆動軸（図示略）の両方向のアキシャル荷重を受け持つことができ、上記と同様の作用効果を得ることができる。   In the above embodiment, the large bearing 52 forms a cross roller bearing as a whole. However, in the present invention, it is not always necessary to form a cross roller bearing. For example, as shown in FIG. 2, a first rolling member 156A capable of receiving an axial load on one side in the axial direction as a “rolling member” between the inner ring member 154 and the outer ring member 158, and the first The large bearing 152 is arranged with (the first and second rolling members) by disposing the rolling member 156A and a second rolling member 156B that is disposed in the axial direction and can receive the axial load on the other axial side. 156A, 156B orbital planes T101A, T101B may be provided) and an angular bearing may be configured. Even in this case, the large bearing 152 is covered by the inner ring member 154, the first and second rolling members 156A, 156B, and the outer ring member 158 as a whole by the inner ring member 154 and the counterpart machine 124 connected to the inner ring member 154. Axial loads in both directions of the drive shaft (not shown) can be handled, and the same effects as described above can be obtained.

なお、このように転動部材１５６の軌道平面Ｔ１０１Ａ、Ｔ１０１Ｂを２面有するような軸受構造の場合には、当該双方の軌道平面Ｔ１０１Ａ、Ｔ１０１Ｂが、共に、長く設定された方の印籠部（この実施形態では相手部材側印籠部Ｅ１０３）の半径方向内側に存在するようにするとよい。これにより、各軌道平面Ｔ１０１Ａ、Ｔ１０１Ｂが軸方向に離れていることと相まって、特に内輪部材１５４の軸ぶれに関して良好な支持特性が得られる。   In the case of a bearing structure having two raceway planes T101A and T101B of the rolling member 156 in this way, both of the raceway planes T101A and T101B are both longer stamped parts (this In the embodiment, it is preferable to exist on the inner side in the radial direction of the mating member side stamping part E103). Thereby, coupled with the fact that the track planes T101A and T101B are separated in the axial direction, good support characteristics can be obtained particularly with respect to the axial runout of the inner ring member 154.

その他の構成については、先の実施形態とほぼ同様であるため、図中で図１に示した構成と同一または機能的に同一の部分に、図２中で下２桁が同一の符号を付すにとどめ、重複説明を省略する。   The other configurations are almost the same as those of the previous embodiment, and therefore, the same reference numerals in FIG. 2 denote the same or functionally the same parts as those shown in FIG. Only redundant explanations are omitted.

なお、上記実施形態においては、外輪部材の外周を段差のない単純な円筒形状とし、（この単純な形状を活用して）センタレス研削盤によって研削加工することにより、印籠部を構成する外輪部材の外周を高精度に加工するようにしていた。しかし、本発明においては、必ずしも外輪部材の外周の形状を段差のない単純な円筒形状とする必要はなく、例えば、相手機械の連結ケーシングの嵌合を外輪部材の軸方向の途中で中止させるような場合には、段差を形成するようにしてもよい。すなわち、本発明においては、外輪部材の外周に対して相手機械の連結ケーシングや減速機の本体ケーシングをどの程度嵌合させるかについては、特に限定されない。段差のない円筒形状の場合であっても、必ずしも外周全部を印籠部にしなくても良い。   In the above embodiment, the outer ring member has a simple cylindrical shape with no step and is ground by a centerless grinder (utilizing this simple shape), thereby forming the outer ring member constituting the stamping part. The outer periphery was processed with high accuracy. However, in the present invention, the outer ring member does not necessarily have a simple cylindrical shape with no step, and for example, the connection casing of the counterpart machine is stopped in the middle of the outer ring member in the axial direction. In such a case, a step may be formed. That is, in the present invention, there is no particular limitation as to how much the connection casing of the counterpart machine and the main body casing of the speed reducer are fitted to the outer periphery of the outer ring member. Even in the case of a cylindrical shape without a step, the entire outer periphery does not necessarily have to be a stamped part.

内輪部材の形状も上記形状に限定されるものではなく、各孔の形成も（例えば半径方向に余裕があるときなどでは）貫通孔とするようにしても良い。この場合は、内輪部材の軸方向長をより短縮することができる。   The shape of the inner ring member is not limited to the above shape, and each hole may be formed as a through hole (for example, when there is a margin in the radial direction). In this case, the axial length of the inner ring member can be further shortened.

また、減速機の具体的な減速部の構造も、上記構成に限定されない。   Moreover, the structure of the specific deceleration part of a reduction gear is not limited to the said structure.

本発明は、さまざまな減速機の出力部の構造として広く利用できる。   The present invention can be widely used as the structure of the output part of various reduction gears.

本発明の実施形態の一例を示す減速機の断面図Sectional drawing of the reduction gear which shows an example of embodiment of this invention 本発明の他の実施形態の一例を示す減速機の断面図Sectional drawing of the reduction gear which shows an example of other embodiment of this invention 従来の減速機の出力部構造の一例を示す減速機の断面図Sectional drawing of the reduction gear which shows an example of the output part structure of the conventional reduction gear

符号の説明Explanation of symbols

２０…モータ
２２…減速機
２４…相手機械
２６…モータケーシング
２８…第１本体ケーシング
３０…減速部
３２…モータ軸
３６…継軸
３８…太陽歯車
４２…遊星歯車
４４…内歯歯車
４６…第２本体ケーシング
４８…キャリヤ
５０…連結ケーシング
５２…大軸受
５４…内輪部材
５４Ａ…Ｖ溝
５６…転動部材
５８…外輪部材
５８Ａ…Ｖ溝
６０、６４…ボルト
６２…出力軸ブロック
Ｔ１…軌道平面
Ｅ２…減速機側印籠部
Ｅ３…相手機械側印籠部 DESCRIPTION OF SYMBOLS 20 ... Motor 22 ... Reducer 24 ... Counter machine 26 ... Motor casing 28 ... 1st main body casing 30 ... Reduction part 32 ... Motor shaft 36 ... Joint shaft 38 ... Sun gear 42 ... Planetary gear 44 ... Internal gear 46 ... 2nd Main body casing 48 ... Carrier 50 ... Connection casing 52 ... Large bearing 54 ... Inner ring member 54A ... V groove 56 ... Rolling member 58 ... Outer ring member 58A ... V groove 60, 64 ... Bolt 62 ... Output shaft block T1 ... Track plane E2 ... Reducer side stamped part E3 ... Counterpart machine side stamped part

Claims (5)

減速機を被駆動機械に取り付け可能に構成した減速機の出力部構造において、
軸受の内輪を構成する内輪部材と、
前記軸受の転動体を構成する転動部材と、
前記軸受の外輪を構成する外輪部材と、を備え、
前記内輪部材が、前記減速機の出力部材として前記相手機械の被駆動軸側と連結され、
前記外輪部材が、減速機の本体ケーシングの内周及び前記相手機械の連結ケーシングの内周と嵌合して取付の際の基準を提供する印籠部として機能し、
前記軸受が、前記内輪部材、転動部材、及び外輪部材により、前記内輪部材及び該内輪部材と連結される前記被駆動軸の両方向のアキシャル荷重を受け持つ
ことを特徴とする減速機の出力部構造。 In the structure of the output part of the reducer configured so that the reducer can be attached to the driven machine,
An inner ring member constituting an inner ring of the bearing;
A rolling member constituting a rolling element of the bearing;
An outer ring member constituting an outer ring of the bearing,
The inner ring member is connected to the driven shaft side of the counterpart machine as an output member of the speed reducer;
The outer ring member functions as a stamping part that fits with the inner periphery of the main body casing of the speed reducer and the inner periphery of the connection casing of the counterpart machine to provide a reference for installation,
The output part structure of a reduction gear, wherein the bearing bears an axial load in both directions of the inner ring member and the driven shaft connected to the inner ring member by the inner ring member, the rolling member, and the outer ring member . 請求項１において、
前記外輪部材の外周が、段差のない単純な円筒形状とされた
ことを特徴とする減速機の出力部構造。 In claim 1,
The outer periphery of the outer ring member has a simple cylindrical shape having no step. 請求項１または２において、
前記外輪部材の外周における前記減速機の本体ケーシングが嵌合する減速機側印籠部、及び前記外輪部材の外周における相手機械の連結ケーシングが嵌合する相手機械側印籠部のうち、いずれか一方が、他方より長く設定され、且つ、前記転動部材の重心を含む前記出力部材の軸と直角の平面が、該長く設定された方の印籠部の半径方向内側に存在する
ことを特徴とする減速機の出力部構造。 In claim 1 or 2,
Any one of a reduction gear side stamping part in which the main body casing of the reduction gear on the outer periphery of the outer ring member fits and a counterpart machine side stamping part in which the connection casing of the counterpart machine on the outer periphery of the outer ring member fits. And a plane that is set longer than the other and that is perpendicular to the axis of the output member including the center of gravity of the rolling member is present radially inward of the longer stamping portion. Output unit structure of the machine. 請求項１〜３のいずれかにおいて、
前記大軸受が、前記転動部材の重心を含む前記出力部材の軸と直角の平面が、１面のみ存在するクロスローラ軸受とされている
ことを特徴とする減速機の出力部構造。 In any one of Claims 1-3,
The output part structure of a speed reducer, wherein the large bearing is a cross roller bearing in which a plane perpendicular to the axis of the output member including the center of gravity of the rolling member is present. 請求項１〜３のいずれかにおいて、
前記大軸受が、前記転動部材として、軸方向一方側のアキシャル荷重を受け止め可能な第１の転動部材と、該第１の転動部材と軸方向に離れて配置され、軸方向他方側のアキシャル荷重を受け止め可能な第２の転動部材と、を備え、前記第１、第２転動部材の重心を含む前記出力部材の軸と直角の平面が２面存在する軸受とされている
ことを特徴とする減速機の出力部構造。 In any one of Claims 1-3,
The large bearing is disposed as the rolling member, the first rolling member capable of receiving an axial load on one axial side, the axially separated from the first rolling member, and the other axial side A second rolling member capable of receiving the axial load of the first and second rolling members, and a bearing having two planes perpendicular to the axis of the output member including the center of gravity of the first and second rolling members. The output part structure of the reduction gear characterized by this.
JP2008128826A 2008-05-15 2008-05-15 Reducer output section structure Expired - Fee Related JP5074292B2 (en)

Priority Applications (5)

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JP2008128826A JP5074292B2 (en) 2008-05-15 2008-05-15 Reducer output section structure
CN2009101329072A CN101581359B (en) 2008-05-15 2009-03-31 Output part structure of speed reducer
TW098112497A TWI369457B (en) 2008-05-15 2009-04-15 Output structure for a reduction gearbox
DE102009019040A DE102009019040A1 (en) 2008-05-15 2009-04-27 Output part structure for reduction gear includes large bearing in inner ring to hold the bidirectional axial load of driven shaft connected with inner ring, rolling member and outer ring
KR1020090041595A KR101033810B1 (en) 2008-05-15 2009-05-13 Output structure of reducer

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113996380A (en) * 2022-01-04 2022-02-01 山西天地煤机装备有限公司 Built-in speed reduction crusher

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6255267B2 (en) 2014-02-06 2017-12-27 株式会社日立国際電気 Substrate processing apparatus, heating apparatus, ceiling insulator, and semiconductor device manufacturing method
JP7122883B2 (en) * 2018-06-18 2022-08-22 住友重機械工業株式会社 robot

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06307505A (en) * 1993-04-19 1994-11-01 Mitsubishi Heavy Ind Ltd Differential plant gear transmission
JP2000179629A (en) * 1998-12-21 2000-06-27 Harmonic Drive Syst Ind Co Ltd Small backlash planetary gear device
JP2002031150A (en) * 2000-07-13 2002-01-31 Harmonic Drive Syst Ind Co Ltd Gear device unit
JP2005312223A (en) * 2004-04-23 2005-11-04 Harmonic Drive Syst Ind Co Ltd Actuator with wave reduction gear

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6129648A (en) * 1997-11-19 2000-10-10 Harmonic Drive Systems, Inc. Planetary gear device
TW463892U (en) * 2001-04-10 2001-11-11 Apex Dynamics Inc Planet type gear reducer
JP4297443B2 (en) * 2005-02-16 2009-07-15 住友重機械工業株式会社 Power transmission device
JP4877782B2 (en) 2006-11-21 2012-02-15 株式会社 資生堂 Skin barrier function restoring agent evaluation method and evaluation kit

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06307505A (en) * 1993-04-19 1994-11-01 Mitsubishi Heavy Ind Ltd Differential plant gear transmission
JP2000179629A (en) * 1998-12-21 2000-06-27 Harmonic Drive Syst Ind Co Ltd Small backlash planetary gear device
JP2002031150A (en) * 2000-07-13 2002-01-31 Harmonic Drive Syst Ind Co Ltd Gear device unit
JP2005312223A (en) * 2004-04-23 2005-11-04 Harmonic Drive Syst Ind Co Ltd Actuator with wave reduction gear

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113996380A (en) * 2022-01-04 2022-02-01 山西天地煤机装备有限公司 Built-in speed reduction crusher
CN113996380B (en) * 2022-01-04 2022-03-22 山西天地煤机装备有限公司 Built-in speed reduction crusher

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KR101033810B1 (en) 2011-05-13
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CN101581359B (en) 2012-04-18
JP5074292B2 (en) 2012-11-14

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