JPS60201141A - Gear type reduction gear - Google Patents
Gear type reduction gearInfo
- Publication number
- JPS60201141A JPS60201141A JP60014148A JP1414885A JPS60201141A JP S60201141 A JPS60201141 A JP S60201141A JP 60014148 A JP60014148 A JP 60014148A JP 1414885 A JP1414885 A JP 1414885A JP S60201141 A JPS60201141 A JP S60201141A
- Authority
- JP
- Japan
- Prior art keywords
- gear
- planetary gear
- sleeve
- reduction
- hollow
- 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
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/46—Systems consisting of a plurality of gear trains each with orbital gears, i.e. systems having three or more central gears
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/043—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel
- B60K17/046—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel with planetary gearing having orbital motion
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2200/00—Type of vehicle
- B60Y2200/20—Off-Road Vehicles
- B60Y2200/25—Track vehicles
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】
ａ、産業上の利用分野
本発明は、中空歯車と駆動テラセンブリとの間に遊星歯
車減速機構を備えていて、該遊星歯車減速機構の一部は
動力駆動車の本体に固定されたスリーブの中に収容され
ており、２つのヘアリングを使用して中空歯車がスリー
ブの外側で支承されているとともに、スリーブの先端部
に遊星歯車キャリヤを配置するよう構成された、とくに
、チェーン式動力駆動車に使用される歯車式減速装置に
関する。Detailed Description of the Invention a. Industrial Application Field The present invention includes a planetary gear reduction mechanism between a hollow gear and a drive terra assembly, and a part of the planetary gear reduction mechanism is connected to the main body of a power drive vehicle. housed in a sleeve fixed to the sleeve, the hollow gear being supported on the outside of the sleeve using two hair rings, and configured to locate the planetary gear carrier at the tip of the sleeve; In particular, it relates to a gear type reduction gear used in a chain type power driven vehicle.
ｂ、従来の技術
２つのヘアリングを用いて動力駆動車に固定されたスリ
ーブ上に支承されていて、該スリーブの先端部に遊星歯
車機構を配置するよう構成された油圧駆動式伝動装置は
ドイツ公開特許第３０１５８１８号より公知である。遊
星歯車減速段はスリーブの外側で中空歯車の中に組み込
まれていて、遊星歯車ユニットが外側で中空歯車の内歯
と噛み合っている。b. Prior Art A hydraulically driven transmission device is supported on a sleeve fixed to a power drive vehicle using two hair rings, and is constructed in such a way that a planetary gear mechanism is disposed at the tip of the sleeve. It is known from Japanese Patent Publication No. 3015818. The planetary gear reduction stage is integrated into the hollow gear on the outside of the sleeve, and the planetary gear unit meshes with the internal teeth of the hollow gear on the outside.
Ｃ１発明が解決しようとする問題点
この従来公知の装置の場合、装置を構成している歯車減
速要素は中空歯車により保護されているだけであるので
、外部から損傷をうけるおそれがある。C1 Problems to be Solved by the Invention In the case of this conventionally known device, since the gear reduction element constituting the device is only protected by a hollow gear, there is a risk of damage from the outside.
また、従来の歯車式減速装置の別の欠点は、第１の遊星
段が駆動部と勝手反対の側に配置されていることである
。このように構成されると、駆動軸は長くなり、中空軸
は第１の段の腹板と第２の段の太陽歯車の間に延設され
ることになる。Another drawback of the conventional gear reduction gear is that the first planetary stage is located on the opposite side of the drive section. With this configuration, the drive shaft is long and the hollow shaft extends between the belly plate of the first stage and the sun gear of the second stage.
中空歯車の内歯の直径はいろいろ異なった大きさに設定
されるので、製作コストが高くつくことも従来装置の付
随する欠点として指摘されている。An associated drawback of the prior art device is that the diameter of the internal teeth of the hollow gear can be set to different sizes, resulting in high production costs.
さらに、従来の装置では動力駆動車に固定されたスリー
ブの内径が比較的小さいので、駆動モーターのごく一部
分が収納されているだけであって、他の部分は動力駆動
車のスペースから突出しているから邪魔である。Furthermore, in conventional devices, the inner diameter of the sleeve fixed to the power drive vehicle is relatively small, so that only a small part of the drive motor is accommodated, and the other part protrudes from the space of the power drive vehicle. It's a hindrance.
本発明の目的は、外部から損傷をうけないよう保護され
ているとともに、とくに好ましくない傾動作用からも十
分に保護されるよう構成された、丈夫でかつ性能にすぐ
れた減速比が大きい歯車式減速装置を提供することであ
る。The object of the invention is to provide a durable and high-performance gear reduction gear with a large reduction ratio, which is protected against external damage and is particularly well protected against undesirable tilting movements. The purpose is to provide equipment.
上記の目的を達成するため、特許請求の範囲第（１）項
の特徴項に記載されている構成を特徴とする歯車式減速
装置が本発明に従って提案されたのである。本発明の有
利な実施態様については、特許請求の範囲第（２）項よ
り第００）項までを参照されたい。In order to achieve the above-mentioned object, a gear type speed reduction device characterized by the structure described in the feature item of claim (1) was proposed according to the present invention. For advantageous embodiments of the invention, reference is made to patent claims 2 to 00).
ｄ１発明の効果
ているスリーブは駆動部と２つの遊星歯本伝動段を収容
しており、該２つの遊星歯車伝動段は歯車式減速伝動装
置の固定部の中で保護された状態に取り付けられている
。スリーブは比較的大きくて丈夫であるから、遊星伝動
機構に好ましくない変形が生じることはない。d1 The sleeve according to the invention accommodates a drive part and two planetary gear transmission stages, the two planetary gear transmission stages being mounted in a protected manner in a fixed part of the gear reduction transmission. ing. Since the sleeve is relatively large and strong, no undesired deformation of the planetary transmission occurs.
スリーブは簡単な形状を呈しているので、製作技術的に
もコスト的にも有利に加工することができる。被駆動伝
動段の遊星歯車伝動機構はスリーブの先端部にぐあいよ
く取り付けることができる。Since the sleeve has a simple shape, it can be processed advantageously in terms of manufacturing technology and cost. The planetary gear transmission of the driven transmission stage can be conveniently mounted on the tip of the sleeve.
スリーブが長くかつ径が大きいので、本発明装置の特長
の１つは中空歯車を支承するために取り付けられた円錐
ローラー・ヘアリングが広い支持へ−スを形成している
ことである。外力の作用のもとローラー軸を通って伝達
された中間力が画く線はほぼ“０”の輪郭を呈していて
、この輪郭の中はスリーブの直径に応じた大きさとなる
。このように支持ベースが広いので、動力駆動車が運転
中にしばしば生じる傾動力がヘアリング系とスリーブを
へて動力駆動車の車体に伝達されても、遊星伝達機構に
不利な作用を及ばずことはない。したがって、遊星伝動
機構が損傷することを大幅に本発明装置のいま１つの特
長は、伝動段が順々に接続されていて、駆動部から中空
歯車まで短い距離をへて力を伝達することができること
であり、しかも中空歯車から駆動部に力が逆に伝達され
ることはない。Due to the long length and large diameter of the sleeve, one of the features of the device according to the invention is that the conical roller hair ring installed to support the hollow gear forms a wide support space. The line drawn by the intermediate force transmitted through the roller shaft under the action of an external force has an approximately "0" contour, the inside of which is sized according to the diameter of the sleeve. Because the support base is wide in this way, even if the tilting force that often occurs when a power-driven vehicle is in operation is transmitted to the body of the power-driven vehicle through the hair ring system and sleeve, it will not adversely affect the planetary transmission mechanism. Never. Therefore, damage to the planetary transmission mechanism is greatly reduced.Another feature of the device of the present invention is that the transmission stages are connected one after the other and power can be transmitted over a short distance from the drive part to the hollow gear. This is possible, and in addition, no force is transmitted back from the hollow gear to the drive unit.
ｅ０問題点を解決するための手段
以下、本発明の一実施例を図解した添付図面を参照しな
がら本発明の詳細な説明する。Means for Solving the e0 Problem The present invention will now be described in detail with reference to the accompanying drawings, which illustrate one embodiment of the present invention.
第１図に示されているように、中空歯車４とスリーブ５
の間にベアリング８１と８２が取り付けられているので
、中空歯車４は動力駆動車の車体６に固定されたスリー
ブ５のまわりで回転することができる。スリーブ５の先
端部に内歯５２と外歯５３が刻設されている。As shown in FIG. 1, a hollow gear 4 and a sleeve 5
Bearings 81 and 82 are mounted between them, so that the hollow gear 4 can rotate around the sleeve 5, which is fixed to the body 6 of the power drive vehicle. Internal teeth 52 and external teeth 53 are carved at the tip of the sleeve 5.
油圧駆動モーター７は短いシャフトを介して遊星歯車減
速機構１の太陽歯車１１を駆動する。遊星歯車１２は太
陽歯車１１と噛み合うとともに、内歯５２とも噛み合い
、！星歯車キャリヤ１３を駆動する。The hydraulic drive motor 7 drives the sun gear 11 of the planetary gear reduction mechanism 1 via a short shaft. The planetary gear 12 meshes with the sun gear 11 and also meshes with the internal teeth 52,! The star gear carrier 13 is driven.
該遊星歯車キャリヤ１３はシャフトを介して遊星歯車減
速機構２の太陽歯車２１と作動的に接続されている。遊
星歯車２２は太陽歯車２１と噛み合っているとともに、
内歯５２とも噛み合っていて、遊星歯車キャリヤ２３を
駆動しており、該遊星歯車キャリヤ２３はさらに遊星歯
車減速機構３の太陽歯車３１と作動的に接続されている
。The planetary gear carrier 13 is operatively connected to the sun gear 21 of the planetary gear reduction mechanism 2 via a shaft. The planetary gear 22 meshes with the sun gear 21, and
It also meshes with the internal teeth 52 and drives a planetary gear carrier 23 , which is further operatively connected to the sun gear 31 of the planetary gear reduction mechanism 3 .
遊星歯車キャリヤ２３の内歯３４はスリーブ５の外歯５
３に差し込まれたうえ、前記スリーブ５に固定されてい
る。太陽歯車３１は固定の遊星歯車キャリヤ３３に回転
可能に取り付けられている遊星歯車３２を介して中空歯
車４を駆動する。遊星歯車３２は内歯４１と噛み合って
いる。The internal teeth 34 of the planetary gear carrier 23 are the external teeth 5 of the sleeve 5.
3 and is fixed to the sleeve 5. The sun gear 31 drives the hollow gear 4 via a planet gear 32 which is rotatably mounted on a fixed planet gear carrier 33. The planetary gear 32 meshes with the internal teeth 41.
第２図は、中空歯車の先端部に作用する力Ｐとベアリン
グ８１と８２に作用する力にもとづく反力Ｒを図解した
ものである。外力の作用をうりて２つのローラー軸をへ
て伝達された中間力が駆動シャフトの中心軸を横切る２
つの交差点は互にできるだけ広く離れて位置ぎめされる
ことが好ましい。FIG. 2 illustrates the reaction force R based on the force P acting on the tip of the hollow gear and the force acting on the bearings 81 and 82. The intermediate force transmitted through the two roller axes under the action of an external force crosses the central axis of the drive shaft.
Preferably, the two intersection points are located as widely apart as possible from each other.
第１図は、本発明に係る歯車減速装置の構成を概念的に
図解した断面図。第２図は円錐ローラー・ヘアリングを
取り付けた歯車減速機構の一部分の断面図。
１．２．３・・・遊星歯車減速機構、
４・・・中空歯車、 ５・・・スリーブ、６・・・動力
駆動車の車体、 ７・・・油圧駆動モーター、１１２１
、３１・・・太陽歯車、 １２．２２・・・遊星歯車、
１３、２３．３３・・・遊星歯車キャリヤ、３４、４１
．５２・・・内歯、 ５３・・・外歯、８１．８２・・
・ベアリング。FIG. 1 is a sectional view conceptually illustrating the configuration of a gear reduction gear according to the present invention. Figure 2 is a cross-sectional view of a portion of the gear reduction mechanism equipped with a conical roller hair ring. 1.2.3... Planetary gear reduction mechanism, 4... Hollow gear, 5... Sleeve, 6... Vehicle body of power drive vehicle, 7... Hydraulic drive motor, 1121
, 31... Sun gear, 12.22... Planetary gear,
13, 23.33... Planetary gear carrier, 34, 41
．． 52...Internal teeth, 53...External teeth, 81.82...
·bearing.
Claims (1)
速機構を備えていて、該遊星歯車減速機構の一部は動力
駆動車の本体に固定されたスリーブの中に収容されてお
り、２つのヘアリングを使用して中空歯車がスリーブの
外側で支承されているとともに・スリーブの先端部に遊
星歯車キャリヤを配置するよう構成された、とくに、チ
ェーン式動カ駆動車に使用される歯車式減速装置であっ
て、少なくとも１つの遊星歯車伝動機構１がスリーブ５
内に配置されていることと、遊星歯車減速機構１を収容
している内歯５３がスリーブ５の先端領域に刻設してい
るとともに、被駆動伝動機構３の遊星歯車キャリヤ３３
の内歯３４と噛み合っている外歯がスリーブ５の先端領
域に刻設していることを特徴とする歯車式減速装置。 （２）内歯５２が遊星歯車減速機構１の遊星歯車１２と
噛（１）項に記載の歯車減速装置。 （３） 太陽歯車２１が遊星歯車２２と噛み合っていて
、該遊星歯車２２が内歯５２と噛み合っていることを特
徴とする特許請求の範囲第（１）項または第（２）項に
記載の歯車式減速装置。 （４）遊星歯車２２が遊星歯車キャリヤ２３を介して遊
星歯車減速機構３の太陽歯車と作動的に接続されている
ことを特徴とする特許請求の範囲第（１）項より第（３
）項までのいずれか１項に記載の歯車減速装置。 （５）太陽歯車３１が遊星歯車キャリヤ３３上に軸支さ
れている遊星歯車３２と噛み合っていることを特徴とす
る特許請求の範囲第（１）項より第（４）項までのいず
れか１項記載の歯車式減速装置。 （６）遊星歯車キャリヤ３２が中空歯車４の先端側に刻
設された内歯４２と噛み合っていることを特徴とする特
許請求の範囲第（１）項より第（５）項までのいずれか
１項に記載の歯車式減速装置。 （７）駆動テラセンブリ７と中空歯車４の間の変速比ｉ
が１＝２２０までの大きさに設定されていることを特徴
とする特許請求の範囲第（１）項より第（６）項までの
いずれか１項に記載の歯車式減速装置。 （８） スリーブ５の外周で該スリーブ５の脚部の近傍
５３の近傍にベアリング８２が設けられており、中空歯
車が両方のベアリング８１．８２上に支承されているこ
とを特徴とする特許請求の範囲第＋１１項に記載の歯車
式減速装置。 （９） ベアリング８Ｌ ８２が円錐ローラー・ベアリ
ングであることを特徴とする特許請求の範囲第（８）項
に記載の歯車式減速装置。 ００） 中空歯車４の外径対スリーブの外径の比が１．
５から１．８までに設定されている場合、中空歯車４の
先端部に作用する力が減速装置の中心軸を横切る作用か
らベアリング８１の円錐ローラーの軸に直角に作用する
中間力の作用点までで測った距離と前記作用点からベア
リング８２０円錐ローラーの軸に作用する中間力の作用
点まで測った距離との比が０．５０から０．５５までに
はいるよう隣接したベアリング８１．８２の円錐ローラ
ーがそれぞ並んで配置されていることを特徴とする特許
請求の範囲第（８）項または第（９）項に記載の歯車式
減速装置。[Claims] (11) A planetary gear reduction mechanism is provided between the hollow gear and the drive assembly, and a part of the planetary gear reduction mechanism is housed in a sleeve fixed to the main body of the power drive vehicle. The hollow gear is supported on the outside of the sleeve using two hair rings, and the planetary gear carrier is arranged at the tip of the sleeve. It is especially used for chain drive wheels. gear type reduction gear, in which at least one planetary gear transmission mechanism 1 is connected to a sleeve 5.
The internal toothing 53 accommodating the planetary gear reduction mechanism 1 is carved in the tip region of the sleeve 5 and the planetary gear carrier 33 of the driven transmission mechanism 3.
A gear type speed reduction device characterized in that external teeth meshing with internal teeth 34 of the sleeve 5 are carved in the distal end region of the sleeve 5. (2) The gear reduction device according to item (1), in which the internal teeth 52 mesh with the planetary gear 12 of the planetary gear reduction mechanism 1. (3) The sun gear 21 meshes with a planetary gear 22, and the planetary gear 22 meshes with the internal teeth 52, as set forth in claim (1) or (2). Gear type reduction gear. (4) The planetary gear 22 is operatively connected to the sun gear of the planetary gear reduction mechanism 3 via the planetary gear carrier 23.
) The gear reduction device according to any one of the preceding items. (5) Any one of claims (1) to (4), characterized in that the sun gear 31 meshes with a planetary gear 32 that is pivotally supported on a planetary gear carrier 33. Gear type reduction device as described in . (6) Any one of claims (1) to (5), characterized in that the planetary gear carrier 32 meshes with internal teeth 42 carved on the tip side of the hollow gear 4. The gear type reduction gear according to item 1. (7) Gear ratio i between drive terra assembly 7 and hollow gear 4
The gear type speed reduction device according to any one of claims (1) to (6), characterized in that: is set to a size up to 1=220. (8) A patent claim characterized in that a bearing 82 is provided on the outer periphery of the sleeve 5 in the vicinity of the leg portion 53 of the sleeve 5, and the hollow gear is supported on both bearings 81, 82. The gear type reduction gear according to item +11 in the range. (9) The gear type speed reduction device according to claim (8), wherein the bearing 8L 82 is a conical roller bearing. 00) The ratio of the outer diameter of the hollow gear 4 to the outer diameter of the sleeve is 1.
5 to 1.8, the point of application of the intermediate force is from the force acting on the tip of the hollow gear 4 across the central axis of the reduction gear to the force acting perpendicularly to the axis of the conical roller of the bearing 81. Adjacent bearings 81, 82 such that the ratio of the distance measured up to and the distance measured from said point of application to the point of application of the intermediate force acting on the axis of the conical roller bearing 820 is between 0.50 and 0.55. The gear type speed reduction device according to claim 8 or 9, wherein the conical rollers are arranged side by side.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19843410866 DE3410866A1 (en) | 1984-03-22 | 1984-03-22 | WHEEL REDUCTION GEARBOX |
| DE3410866.1 | 1984-03-22 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60201141A true JPS60201141A (en) | 1985-10-11 |
| JPH057574B2 JPH057574B2 (en) | 1993-01-29 |
Family
ID=6231489
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60014148A Granted JPS60201141A (en) | 1984-03-22 | 1985-01-28 | Gear type reduction gear |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JPS60201141A (en) |
| DE (1) | DE3410866A1 (en) |
| FR (1) | FR2561740B1 (en) |
| GB (1) | GB2156475B (en) |
| IT (1) | IT1183225B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003507668A (en) * | 1999-08-12 | 2003-02-25 | アルファ ゲトリーベバウ ゲゼルシャフト ミット ベシュレンクテル ハフツング | Planetary gear transmission |
| JP2010506104A (en) * | 2006-09-30 | 2010-02-25 | ツェットエフ、フリードリッヒスハーフェン、アクチエンゲゼルシャフト | Multistage speed reducer |
Families Citing this family (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3641656A1 (en) * | 1986-12-05 | 1988-06-16 | Wittenstein Manfred | Driving device with an electric motor and a reduction gear mechanism |
| JP2769323B2 (en) * | 1988-06-29 | 1998-06-25 | アイシン・エィ・ダブリュ株式会社 | Motor drive device with reduction gear and electric vehicle |
| DE8810135U1 (en) * | 1988-08-09 | 1989-01-05 | Cyclo-Getriebebau Lorenz Braren Gmbh, 8062 Markt Indersdorf, De | |
| DE3925937A1 (en) * | 1989-08-03 | 1991-02-14 | Mannesmann Ag | MOTOR DRIVE WITH A MULTI-SPEED GEARBOX FOR AN OUTER SLEEVE |
| GB2244684A (en) * | 1990-06-06 | 1991-12-11 | Keith Richard Bound | Electric four wheel drive wheelchair |
| FR2757458B1 (en) * | 1996-12-23 | 1999-03-05 | Renault Vehicules Ind | DEVICE FOR DRIVING A WHEEL OF A MOTOR VEHICLE COMPRISING A PARTICULAR ARRANGEMENT OF A MOTOR AND A SPEED REDUCER |
| JP2002507170A (en) | 1997-07-02 | 2002-03-05 | ボリンジア インドゥストリー アクチェンゲゼルシャフト | Drive wheel |
| US6907951B2 (en) | 2000-03-07 | 2005-06-21 | Arctic Cat, Inc. | Snowmobile planetary drive system |
| US6742618B2 (en) | 2000-03-07 | 2004-06-01 | Arctic Cat, Inc. | Snowmobile planetary drive system |
| US7182708B2 (en) * | 2002-12-20 | 2007-02-27 | Caterpillar Inc | Final drive for electric motor to wheel |
| DE102013225693B4 (en) * | 2013-09-12 | 2022-02-24 | Robert Bosch Gmbh | Drive unit with drive motor and planetary gear |
| NL2014781B1 (en) * | 2015-05-08 | 2017-01-26 | Zuidberg Techniek Holding B V | Combination of a drive wheel and a gearbox for a continuous track system. |
| US10093177B2 (en) * | 2017-03-06 | 2018-10-09 | Fairfield Manufacturing Company, Inc. | Compact planetary wheel drive |
| CN112638686B (en) * | 2018-09-11 | 2023-11-21 | 沃尔沃建筑设备公司 | hub drive system |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2529330A (en) * | 1948-02-20 | 1950-11-07 | Euclid Road Machinery Co | Double planetary drive axle |
| FR1131004A (en) * | 1955-09-16 | 1957-02-14 | Konstruktions Und Montagebetr | Epicyclic gear shift mechanism for cable drums |
| FR1249299A (en) * | 1959-11-09 | 1960-12-30 | Engrenages Et Machines Maag Sa | Mechanism usable as a high ratio reduction gear or multiplier |
| DE1130237B (en) * | 1960-10-10 | 1962-05-24 | Heinrich Desch G M B H | Epicyclic gears with several sets of epicyclic gears arranged one behind the other |
| US3459070A (en) * | 1967-07-03 | 1969-08-05 | Borg Warner | Wheel drive mechanism |
| US4092878A (en) * | 1976-11-19 | 1978-06-06 | Caterpillar Tractor Co. | Floating carrier retention for a planetary gearset |
| GB1568658A (en) * | 1977-07-28 | 1980-06-04 | Caterpillar Tractor Co | Bearing retainer assembly |
| FR2411295A1 (en) * | 1978-11-10 | 1979-07-06 | Haza Jean | Transmission for electric motor driven roller blind - has epicyclic gear train whose planet wheels mesh with helicoidal wheel engaging endless screw coupled to manual input |
| DE2943944C2 (en) * | 1979-10-31 | 1983-04-28 | Carl Hurth Maschinen- und Zahnradfabrik GmbH & Co, 8000 München | Drive device for rotating a solar collector independently around two mutually perpendicular axes |
| DE3015818C2 (en) * | 1980-04-22 | 1982-08-19 | Mannesmann AG, 4000 Düsseldorf | Non-rotatable connection of an axially movable planet carrier with a pin, in particular the support pin of a hydrostatic travel gear |
| DE3029578C2 (en) * | 1980-08-05 | 1982-05-27 | A. Friedr. Flender Gmbh & Co Kg, 4290 Bocholt | Planetary coupling gear |
-
1984
- 1984-03-22 DE DE19843410866 patent/DE3410866A1/en active Granted
-
1985
- 1985-01-28 JP JP60014148A patent/JPS60201141A/en active Granted
- 1985-02-08 IT IT19439/85A patent/IT1183225B/en active
- 1985-03-08 FR FR8503443A patent/FR2561740B1/en not_active Expired
- 1985-03-21 GB GB08507375A patent/GB2156475B/en not_active Expired
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003507668A (en) * | 1999-08-12 | 2003-02-25 | アルファ ゲトリーベバウ ゲゼルシャフト ミット ベシュレンクテル ハフツング | Planetary gear transmission |
| JP2010506104A (en) * | 2006-09-30 | 2010-02-25 | ツェットエフ、フリードリッヒスハーフェン、アクチエンゲゼルシャフト | Multistage speed reducer |
Also Published As
| Publication number | Publication date |
|---|---|
| GB2156475A (en) | 1985-10-09 |
| GB8507375D0 (en) | 1985-05-01 |
| GB2156475B (en) | 1987-07-29 |
| DE3410866A1 (en) | 1985-10-03 |
| JPH057574B2 (en) | 1993-01-29 |
| IT8519439A0 (en) | 1985-02-08 |
| FR2561740B1 (en) | 1988-12-16 |
| IT1183225B (en) | 1987-10-15 |
| FR2561740A1 (en) | 1985-09-27 |
| DE3410866C2 (en) | 1988-04-21 |
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