JPS5954844A - Multi-stage planetary gear device - Google Patents

Multi-stage planetary gear device

Info

Publication number
JPS5954844A
JPS5954844A JP57166875A JP16687582A JPS5954844A JP S5954844 A JPS5954844 A JP S5954844A JP 57166875 A JP57166875 A JP 57166875A JP 16687582 A JP16687582 A JP 16687582A JP S5954844 A JPS5954844 A JP S5954844A
Authority
JP
Japan
Prior art keywords
stage
gear
carrier
gears
planetary
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
JP57166875A
Other languages
Japanese (ja)
Other versions
JPS6250690B2 (en
Inventor
Masahiro Hasegawa
昌弘 長谷川
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Shinko Electric Co Ltd
Original Assignee
Shinko Electric Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Shinko Electric Co Ltd filed Critical Shinko Electric Co Ltd
Priority to JP57166875A priority Critical patent/JPS5954844A/en
Publication of JPS5954844A publication Critical patent/JPS5954844A/en
Publication of JPS6250690B2 publication Critical patent/JPS6250690B2/ja
Granted legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H1/00Toothed gearings for conveying rotary motion
    • F16H1/28Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/46Systems consisting of a plurality of gear trains each with orbital gears, i.e. systems having three or more central gears
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H1/00Toothed gearings for conveying rotary motion
    • F16H1/28Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/48Special means compensating for misalignment of axes, e.g. for equalising distribution of load on the face width of the teeth

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • Retarders (AREA)

Abstract

PURPOSE:To aim at equalizing load to a planetary gear device, by self-aligning sun gears with planetary gears in the planetary gear device. CONSTITUTION:A plurality of primary stage planetary gears 7a are meshed with a sun gear 6a integrally incorporated with an input shaft 5, and an internal gear 10. A carrier 8a bearing the first stage primary gears 7a is integrally incorporated with a second sun gear 6b with which second stage planetary gears 7b are meshed. Thus, a multi-stage transmission unit having an output shaft 9 is constituted by successively carrying out the above-mentioned steps. The sun gears 6a through 6d and the planetary gears 7a through 7d are floatingly supported by disposing balls 11a through 11d between adjacent sun gears 6a through 6d.

Description

【発明の詳細な説明】 この発明は多段(11)’迦星t@□車装;占に関する
DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a multi-stage (11) 'car star t@□ vehicle installation; divination.

遊星歯車装置は、太陽歯車と、これに噛合う複数の遊星
歯車と、遊星歯蓋を支持するキャリヤーから構成され、
太陽歯車、キャリヤーのセンター中□心への□支承が最
も、重要である。1−なわ□ち、第、7図に示すように
□、キャリヤー(3)中心が上ノ戸こすれる□と、遊星
歯車(1A)の内□両歯車(4)との噛合部の、遊星歯
車(1B)’ 、 (1c)の太陽歯Jlt t2]と
の噛合部1〕。
The planetary gear device consists of a sun gear, a plurality of planetary gears that mesh with the sun gear, and a carrier that supports the planetary gears.
The support of the sun gear to the center of the carrier is most important. 1 - As shown in Figure 7, the center of the carrier (3) rubs against the upper surface of the planetary gear at the meshing part with both inner gears (4) of the planetary gear (1A). (1B)', meshing part 1] with the sun tooth Jlt t2] of (1c).

Cにおいて、バックラッシュは無く過噛□合□となり、
逆□に遊星歯車OA)の太陽歯車(2)との噛合部d、
遊星歯車(IB)、 (IC;)の内歯歯車(4)との
噛合部e、fでは□バックラッシュが□大でill、0
・が多く緩噛合であり、いずれにしても有効な動力伝達
、速IW変換作用は望むべきもない。また、第8図に示
すが、太陽□歯車(2)中心がずれる場合(こおいても
、遊1P歯jIL(]、IA’との噛合部gでバックラ
ッシュか夕〆fんどjHH(’ 、<遊星歯車(]IB
、 (]C+)との噛合部h’、  iでバツ□クラ゛
リシュが□大となり、第7図の場合と同様、効率の高い
動力伝達は期□待できない。央に、複数遊y1歯車のキ
ャリヤーへの軸支誤差が人きく、第9図に示すように、
遊星歯車(IA)’lこおいてはセンター中・し・との
ピッチ力’JL<、遊星歯車(][りは逆に短い場合、
第71図、第8図と同□様の過噛i’、’i 、1 *
  k 、“緩噛・合l,m状態を来たし、適切良好の
場合は得らi”bない。
At C, there is no backlash and there is an overbite □mating□,
On the reverse □, the meshing part d of the planetary gear OA) with the sun gear (2),
At the meshing parts e and f of the planetary gears (IB) and (IC;) with the internal gears (4), □ backlash is □ large and ill, 0
In many cases, the mesh is loose, and in any case, effective power transmission and speed IW conversion effects cannot be expected. In addition, as shown in Fig. 8, when the center of the sun □ gear (2) shifts (also in this case, backlash occurs at the meshing part g with the free 1P tooth jIL() and IA') ' , <Planetary gear (] IB
, (]C+), the crush is large at the meshing portions h' and i, and as in the case of Fig. 7, highly efficient power transmission cannot be expected. In the center, there is an error in the shaft support of the multiple idle gears y1 to the carrier, as shown in Figure 9.
In the case of a planetary gear (IA), the pitch force between center and center is JL<, and if the planetary gear (IA) is short,
Fig. 71, overbite i', 'i, 1 * similar to □ as in Fig. 8
k, "loose interlocking/mating l,m state has occurred, and if the condition is properly good, it is not possible to obtain i"b.

このように、 太陽歯車、キト→1′−・力センター中
心からのずれ、遊星歯車のキ、ヤl)I・−への軸支位
11゛9課;cなどは、この種遊星歯車装置において最
も重要な問題であり、従来より、太陽歯車、キャリヤー
の文ノlkはかなり複雑・高度Q機構を用い、、また歯
車類の加」−も非常な高精度で行われてきたが、いずれ
にしてもコスト面で不利益を招くのは致しんなかった。
In this way, the deviation of the sun gear from the center of the force center, the shaft support of the planetary gear to This is the most important problem in the field of technology, and conventionally, the construction of sun gears and carriers has been done using fairly complex and advanced Q mechanisms, and the addition of gears has also been done with very high precision. However, I could not afford to incur a disadvantage in terms of cost.

この発明は、上記従来の太陽歯列(、キャリヤーを積極
的に支承・固定する機構構成を止め、内歯14.1車、
遊1+j歯中の相月位111“関係より定まるセンター
位置に太陽歯車、キャl) +−−の回転中心を自動的
に維持させるという自動調心の考えノJを適用したもの
で、以1・図面により木シロ明を、11.外的に説明す
る。
This invention eliminates the above-mentioned conventional sun gear (, mechanism configuration for actively supporting and fixing the carrier, internal gear 14.1 wheel,
This is an application of the idea of self-alignment that automatically maintains the center of rotation of the sun gear and the center position determined by the relationship 111, which is determined by the relationship 1 + j.・11. Externally explain Kishiromei using drawings.

第1図はこの会明の一実施例で、第2図は主要・:ご・
1173′愼施□例は4段式のIfl星歯j1【減速装
置で、人力い、、、−(、こl l?初、、!大、、陽
歯車(°・)より4段目の終段キャリヤー(8d)の出
力軸(9)に刻し動力伝達を行い、出力軸□(91)駆
動トルレ鉦:増人、回転、、数を減少、さ□せる。
Figure 1 shows an example of this meeting, and Figure 2 shows the main...
1173'Construction □Example is a 4-stage Ifl star gear j1 The power is transmitted to the output shaft (9) of the final stage carrier (8d), and the output shaft □ (91) drive torle gong: increases the number of people, rotates, decreases the number, and so on.

すなわち、入力軸(5)の動力は、IB段太陽歯Jii
、 (6a、)初段M星歯車(7a)、I/J段キャリ
ヤー(8a)、2段遊星歯車(7b)、2段キャリヤー
(s b)、3段遊JiL′歯1+(7,c) >3段
、キャリヤー(8,c) 、最終段の、4段遊星歯車(
7d)へと#4次伝達され、先の終段キャリヤー(8d
)を経て出力軸(9)よりL(1(り出せる。なお、内
歯歯車(コO)は固定する。 、    ′ 二の発明は、図示するよう・(こ、各段の太陽歯114
 。
That is, the power of the input shaft (5) is the IB stage sun tooth Jii
, (6a,) 1st stage M star gear (7a), I/J stage carrier (8a), 2nd stage planetary gear (7b), 2nd stage carrier (s b), 3rd stage idle JiL' tooth 1+ (7, c) >3 stages, carrier (8, c), final stage, 4 stage planetary gear (
7d) and #4 is transmitted to the final stage carrier (8d
) from the output shaft (9). Note that the internal gear (KO) is fixed. , ' The second invention is as shown in the figure.
.

キャリヤーを支承する機構構成は何ら自せず、従つ:て
、′□m+r”?*”−L= 右のあらゆるlj向に月
しフリーの状態となり、遊星歯車、内歯歯車その他構成
部品をこより定まる安定位置に自動的に調心される。ま
た、各段のキャリヤーと太陽歯車との間には自動調・し
・構成部品としてボール(11)が挿入されるが、これ
は遊星歯車機構の各段における適止なりリアランスを維
4’5させるためで、例えば第219のボ、−ル(] 
] b)は第2段ギヤリヤー(7b)と;Tシ2段人、
両歯車。
There is no mechanism structure to support the carrier, so: '□m+r''?*''-L= It moves in all lj directions to the right and becomes free, and the planetary gears, internal gears, and other components It is automatically centered to a stable position determined by this. In addition, a ball (11) is inserted between the carrier of each stage and the sun gear as a self-adjusting component, and this ball (11) is used to maintain proper clearance in each stage of the planetary gear mechanism. For example, the 219th ball (]
] b) is the second stage gear rear (7b);
Both gears.

(8b)との間に適正なりリアランスを設け、接触等の
遊ノ【!歯車(7)との度合部にはグリースチャンバー
(」2a)を設け、また遊星歯車(7)を嵌押して後、
抜け11、め1月ピン(]4)を圧入し、遊J:入山車
(7)の1lIIIl(]2)からの離脱を防(゛。な
お、キャリト一(8)と、遊刀工歯車軸(]2)との結
合は、?[J”ビーl、などの各種溶接、焼バメ、圧入
などの方法がJ)る。なお、、第3図に斜視図を示す。
Provide an appropriate clearance between (8b) and play such as contact [! A grease chamber (2a) is provided at the interface with the gear (7), and after the planetary gear (7) is fitted and pressed,
11, press-fit the first pin (4) to prevent the floating gear (7) from coming off from the 1lIIIl (2) (2). (2) can be joined by various methods such as welding, shrink fitting, press fitting, etc.A perspective view is shown in Fig. 3.

また、各段に、おける太陽、両生、キャリヤー間あるい
は当段遊’l1(41+車と前段キャリヤー中のクリア
ランス形I戊のための各ボールは。
In addition, in each stage, each ball for the sun, amphibious, carrier between carriers or the current stage'l1 (41+ car and clearance type I in the front stage carrier).

第4図、第5図に示すように、太陽歯車側あるいはキャ
リヤー側のいずれかて支承、つるようにしてもよい。
As shown in FIGS. 4 and 5, it may be supported or suspended either on the sun gear side or on the carrier side.

この発明は」1記のように構成される。次にその作用、
効果について、’?Jr6図、第10図に基づき説明す
る。第6図は、太陽歯車(2)と、5つの遊Jix歯車
CIA)、 (IB)、 (10)と、内歯歯車(4)
の各噛合状態が理想的の場合で、各歯11tのバックラ
ッシュは適正であり、もちろん3つの遊星歯車(] A
) 、 、(] 13) 、 (コC)は平等に荷重を
分担する。ところで、逅ノ1歯Jli装(r!tにやっ
て、上記のような完全噛合状態を?!)るのは、甚だ難
しく、先に説明したように、第6図、第7図、第8図に
例示するドラフルがしばしば発生した。しかる、、1こ
、この、発明に係る、キャリヤー、太陽歯、車の支承・
固定を行わないII !li# +1lIIl尼の考え
方は、上記トラブル等猪生の余地をな鳴した。
This invention is constructed as described in section 1. Next, its effect,
About the effect,'? This will be explained based on FIG. 6 and FIG. 10. Figure 6 shows the sun gear (2), the five idler Jix gears CIA), (IB), (10), and the internal gear (4).
In the case where each meshing state of is ideal, the backlash of each tooth 11t is appropriate, and of course the three planetary gears (] A
) , , (] 13) , (C) share the load equally. By the way, it is extremely difficult to create a completely engaged state like the one shown above by applying it to r!t, and as explained earlier, Druffles as illustrated in Figure 8 often occurred. However, the carrier, sun gear, and car support according to this invention
No fixation II! li# +1lIIlni's way of thinking leaves no room for the above-mentioned troubles.

すなわ、ち、第10.図において、破線表示の遊!it
、 (Art、車(1人)、(]]3ンは、第8図に示
す不J!−合事I(“lと同一のものであるが、この発
明、にょれば、キャリヤー中心が太陽歯車(2)のセン
ター中心αより、若干角度回動したβ点に、自動的に移
行すること、とな、る。
In other words, 10th. In the diagram, the broken line indicates play! it
, (Art, car (1 person), (]] 3) is the same as the non-J! It will automatically move to point β, which is rotated by a slight angle from the center center α of the sun gear (2).

すなわち、破線表示の遊星歯車(] A) 、 (1B
)は遊星歯車(]A)の内歯歯Iff (4)との過噛
合J、太陽歯車(2)との緩噛合e、及び遊星歯車(]
IBの同じく内爾歯車(4)との緩噛合m、太陽歯+1
[(21との過噛台k、・の改善を図る/\え、実線で
示す位置へ移行するの′□であり、これはキャリヤー中
心を−に記αよりβへ □。
That is, the planetary gears (]A), (1B
) indicates overmeshing J with the internal teeth If (4) of the planetary gear (]A), loose meshing e with the sun gear (2), and planetary gear (]
Slow mesh with internal gear (4) of IB, sun tooth +1
[(Aiming to improve the overbite k, · with 21/\E, move to the position shown by the solid line'□, which means that the center of the carrier is indicated by - and moves from α to β□.

回動することになる。言い換えれば、各遊星歯車、−。It will rotate. In other words, each planetary gear, -.

の負イ・1荷重が平衡するよう、遊星1゛+1車、を、
支承讐る。::゛キャリヤーのセンター位置、(千)る
いは各遊星歯車 □と噛合する太陽IAIJliのセン
ター位i11.1を自動修正す、。
In order to balance the negative A・1 load, the planet 1゛+1 wheel,
Support and oppose. :: Automatically correct the center position of the carrier, (1,000) or the center position i11.1 of the sun IAIJli meshing with each planetary gear □.

ることにつきるのであり、」ニ記の場合−遊星歯車:の
(l倚イ1:1中の11↓も1′(グ!1な、か−)安
シ1′の噛合仄態が図示するキャリヤー中心をβ点へ(
(・行した実線表示の位置である。
In the case of ``2'', the meshing state of the planetary gear: (11↓ in 1:1 is also 1' (gu! 1, huh)) is shown in the figure. The center of the carrier to be moved to the β point (
(・This is the position of the solid line displayed.

このように、入陽歯j)1、キャリヤーを自動−心する
本発明は、各遊JJZ歯車にijJ能の限り平衡な負荷
分担をf′jわせるが、このことは、イ、1;L来の不
士イリ;巨→負倚分担を行うものに比し、。。’:] 
’、z Lz 、: 4.1.14□1□1,1□。、
341.、、l■’ll:(K+ Ilt iY−の減
少、 ハ、歯車誤差が吸収でき、歯車用I 211度とか転位
Jitのfini ;C’ iこ左程の精密性を要求さ
□れkい、なとの利点な冶し、また一方太陽歯車ニキャ
リヤー1″支、丞: 、f; (、L/た0とは・摩擦
部位が減少し摩擦□損失がi減、され、装置全体の効率
向上と、装置1/l”Fl←F)Q、、の簡易化などが
挙げられる。
In this way, the present invention, which automatically centers the positive teeth j)1 and the carrier, allows each idler JJZ gear to share the load f'j as balanced as possible; L's fujiri: compared to those who take on a huge burden. . ':]
', z Lz ,: 4.1.14□1□1,1□. ,
341. ,, l■'ll: (K+ Ilt iY- decrease, C, gear error can be absorbed, gear I 211 degree or transposition Jit fini ;C' , and on the other hand, the sun gear carrier 1" support, ,f; improvement, and simplification of the device 1/l"Fl←F)Q.

’1溝’ h 、”’・:、本発明の適用分野としては
各種の増速機、1、′減′4機1t’、:、・モータと
組介せギヤートモークとして、・−各、8Ii″アク□
チ、エータなどがある。
'1 groove' h, ''・:, The field of application of the present invention is various speed increasers, 1, 'reducer' 4 machines 1t', :, ・As a gear motor combined with a motor, ・-each, 8Ii ″Aku□
There are chi, eta, etc.

【図面の簡単な説明】[Brief explanation of drawings]

第1図は実施例の断面図、第2図は主要部′断面図、第
、”、図はその斜視図、第′図、第°図は・リアランス
形成用ボールの他の挿入例を示す図、第6図は各歯車噛
合の理想的の場合を示す図、1lJ7図、第8図、笹、
、9図は従来の各歯車噛合の不具合の場合を示す図、・
第10図は本発明に係る各歯車噛合の修正状□態を赤讐
図、をそれぞれ示す。 (5)・・・・1人力軸 (6a)・・・・・初段太陽歯車 (7a)・・・・・初段遊星歯車 (−・・・・・初段キャリヤー ’(jaa)  ・・・・クリアランス形成用11段ボ
ール(6b)・・・・・次段太陽歯車 (7b)・・・・・次段遊星歯・車    。 (8b)・・・・・次設ギヤリヤー  ・・・・(] 
] b)  ・・・・クリアランス形成用次段ボール(
9)・・・・・出力軸 (]0)・・・・・内歯+’JiI 11〔’ ”  
   リ(8d)・・・・・最終段キャリ、ヤー出にi
fI人 神鋼電機株式会ン1 代理人 弁理士斎 藤 /f  リ!11□ 、 1□′□ 24 オ6図 オフ01¥] 二・シ4−
Figure 1 is a sectional view of the embodiment, Figure 2 is a sectional view of the main part, Figures 1 and 2 are perspective views, and Figures 1 and 2 show other examples of insertion of balls for rearance formation. Figure 6 is a diagram showing the ideal case of each gear mesh, Figure 1lJ7, Figure 8, Sasa,
, Figure 9 is a diagram showing the case of a conventional gear meshing problem.
FIG. 10 is a diagram showing the corrected state of each gear mesh according to the present invention. (5)...1 human power shaft (6a)...First stage sun gear (7a)...First stage planetary gear (-...First stage carrier' (jaa)...Clearance Forming 11 corrugated board (6b)...Next stage sun gear (7b)...Next stage planetary gear/wheel. (8b)...Next gear gear... (]
] b) ...Next corrugated board for clearance formation (
9)...Output shaft (]0)...Internal teeth +'JiI 11['''
Li (8d)...Final carry, i at the end
fI person Shinko Electric Co., Ltd. 1 Agent Patent attorney Fuji Sai /f Ri! 11□, 1□′□ 24 O6 figure off 01¥] 2・C4-

Claims (1)

【特許請求の範囲】[Claims] 1 人力軸の太陽歯:車と、この太陽歯車に噛合する複
数のi/J段遊崖歯車と、こ4tら′#□星歯車を支承
する13段ギヤリヤーと、上記太陽歯車、93段キャリ
ヤーの各センタ一部に介在のクリアランス□形成用防段
ポールと、上記初段キャリヤーに一体形成の次段太陽歯
車と、こ賜次段人陽歯it”in”噛合する複数の次段
遊ノ(1歯車と、これら次段遊星歯□車1を支7トする
次段キャリヤーと、更にり□リアランス形成用の次段ボ
ール等、多段の太陽歯車□、遊□星歯”車、キャリヤー
、クリアラン□ス形成用ボールから成り、かつ、」−記
多段の複数遊星□歯車な−・体噛□合する内fM iN
t lltと、上記キャリヤーの最終段□に形成の出力
5す11より構成したことを特徴とず:る9段遊星歯[
lt装置。
1. Sun gear of human power shaft: a wheel, a plurality of i/J-stage drift gears that mesh with this sun gear, a 13-stage gear carrier that supports the star gear, and the above-mentioned sun gear and 93-stage carrier. A barrier pole for forming a clearance □ interposed in a part of each center of the second stage, a next stage sun gear integrally formed with the first stage carrier, and a plurality of next stage play teeth ( 1 gear, the next stage carrier that supports the next stage planetary gear □ wheel 1, and further □ next stage corrugated board for rearance formation, etc., multi-stage sun gear □, planetary □ star gear □ wheel, carrier, clear run □ It consists of a ball for forming a space, and a multi-stage, planetary gear.
It is characterized by consisting of an output 5 and 11 formed at the final stage □ of the carrier: a 9-stage planetary tooth [
lt equipment.
JP57166875A 1982-09-24 1982-09-24 Multi-stage planetary gear device Granted JPS5954844A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP57166875A JPS5954844A (en) 1982-09-24 1982-09-24 Multi-stage planetary gear device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP57166875A JPS5954844A (en) 1982-09-24 1982-09-24 Multi-stage planetary gear device

Publications (2)

Publication Number Publication Date
JPS5954844A true JPS5954844A (en) 1984-03-29
JPS6250690B2 JPS6250690B2 (en) 1987-10-26

Family

ID=15839241

Family Applications (1)

Application Number Title Priority Date Filing Date
JP57166875A Granted JPS5954844A (en) 1982-09-24 1982-09-24 Multi-stage planetary gear device

Country Status (1)

Country Link
JP (1) JPS5954844A (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61209883A (en) * 1985-03-11 1986-09-18 日本電池株式会社 Reduction gear with speed change mechanism for electric rotary tool
US4777847A (en) * 1985-12-27 1988-10-18 Ferro Manufacturing Corporation Axial drive mechanism
JP2006290038A (en) * 2005-04-06 2006-10-26 Hitachi Constr Mach Co Ltd Travelling device

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0375786U (en) * 1989-11-22 1991-07-30
WO1999025992A1 (en) * 1996-05-21 1999-05-27 Harmonic Drive Systems Inc. Planetary gear device
JP2006307909A (en) * 2005-04-27 2006-11-09 Nidec-Shimpo Corp Rotary support structure of carrier in planetary gear reduction gear

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61209883A (en) * 1985-03-11 1986-09-18 日本電池株式会社 Reduction gear with speed change mechanism for electric rotary tool
JPH0456178B2 (en) * 1985-03-11 1992-09-07 Japan Storage Battery Co Ltd
US4777847A (en) * 1985-12-27 1988-10-18 Ferro Manufacturing Corporation Axial drive mechanism
JP2006290038A (en) * 2005-04-06 2006-10-26 Hitachi Constr Mach Co Ltd Travelling device
JP4610399B2 (en) * 2005-04-06 2011-01-12 日立建機株式会社 Traveling device

Also Published As

Publication number Publication date
JPS6250690B2 (en) 1987-10-26

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