JPS587150Y2 - planetary gearbox - Google Patents
planetary gearboxInfo
- Publication number
- JPS587150Y2 JPS587150Y2 JP1979005185U JP518579U JPS587150Y2 JP S587150 Y2 JPS587150 Y2 JP S587150Y2 JP 1979005185 U JP1979005185 U JP 1979005185U JP 518579 U JP518579 U JP 518579U JP S587150 Y2 JPS587150 Y2 JP S587150Y2
- Authority
- JP
- Japan
- Prior art keywords
- gear
- internal gear
- planetary
- internal
- planetary gear
- 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.)
- Expired
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
- F16H1/2809—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels
- F16H1/2818—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels by allowing limited movement of the ring gear relative to the casing or shaft
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
Description
【考案の詳細な説明】 本考案は遊星歯車装置の改良に関する。[Detailed explanation of the idea] The present invention relates to improvements in planetary gearing.
第１図は従来の船舶用遊星歯車式減速装置の１例を示し
、同図において１は図示しないディーゼル機関の出力軸
に連結される入力軸、２は該入力軸１に固着された太陽
歯車、４ａ、４ｂはピン７及び固定金具８を介してケー
シング９に固定された１対の内歯車、１０は図示しない
プロペラ軸に連結される出力軸、６は該出力軸１０に固
着されたキャリヤ、５は該キャリヤに固着された遊星歯
車軸、３ａ、３ｂは遊星歯車軸５に軸受１２を介して軸
支され、太陽歯車２及び内歯車４ａ 、 ４ｂに噛合す
る複数対の遊星歯車であり、入力軸１を介して太陽歯車
２が回転せしめられると、遊星歯車３ ａ 、３ ｂが
太陽歯車２と内歯車４ａ 、４ｂとの間を公転しながら
自転することによりキャリヤ６及び出力軸１０が入力軸
１と同一方向に回転せしめられ、入力軸１から出力軸１
０に動力が伝達される。FIG. 1 shows an example of a conventional planetary gear reduction gear for ships, in which 1 is an input shaft connected to the output shaft of a diesel engine (not shown), and 2 is a sun gear fixed to the input shaft 1. , 4a and 4b are a pair of internal gears fixed to the casing 9 via pins 7 and fixing fittings 8, 10 is an output shaft connected to a propeller shaft (not shown), and 6 is a carrier fixed to the output shaft 10. , 5 is a planetary gear shaft fixed to the carrier, and 3a, 3b are a plurality of pairs of planetary gears that are supported by the planetary gear shaft 5 via bearings 12 and mesh with the sun gear 2 and internal gears 4a, 4b. When the sun gear 2 is rotated via the input shaft 1, the planetary gears 3a and 3b rotate while revolving between the sun gear 2 and the internal gears 4a and 4b, thereby causing the carrier 6 and the output shaft 10 to rotate. is rotated in the same direction as the input shaft 1, and the output shaft 1 is rotated from the input shaft 1 to the output shaft 1.
Power is transmitted to 0.
１０ａはスラストカラー、１１はスラスト軸受である。10a is a thrust collar, and 11 is a thrust bearing.
また軸受１２はその外周に形成された歯を太陽歯車２に
噛合せしめることにより遊星歯車軸５の廻りを回転可能
としている。Further, the bearing 12 is rotatable around the planetary gear shaft 5 by meshing teeth formed on its outer periphery with the sun gear 2.
かかる遊星歯車装置においては、太陽歯車２、遊星歯車
３ａ 、３ｂ及び内歯車４ａ、４ｂの製作誤差２組立誤
差等により、太陽歯車２と複数対の遊星歯車３ａ、３ｂ
、並びに該遊星歯車３ａ 、 ３ｂと内歯車４ａ 、４
ｂとの歯当りが不均等になり、このため入力軸１からの
動力が各遊星歯車３ａｔ３ｂに均等に配分されずに強い
歯当りを余儀なくされた歯がピッチングや曲げ疲労によ
る破壊を起すことが多々ある。In such a planetary gear device, due to manufacturing errors, assembly errors, etc. of the sun gear 2, the planet gears 3a, 3b, and the internal gears 4a, 4b, the sun gear 2 and the plurality of pairs of planet gears 3a, 3b.
, as well as the planetary gears 3a, 3b and internal gears 4a, 4
The tooth contact between the input shaft 1 and the gears 3a and 3b becomes uneven, and as a result, the power from the input shaft 1 is not evenly distributed to each planetary gear 3at3b, and the teeth forced into strong tooth contact may cause pitting or breakage due to bending fatigue. There are many.
上記のような歯車荷重の不等配分を防止する手段として
従来第２図及び第３図に示すものが提供されている。As a means for preventing the above-mentioned unequal distribution of gear loads, the means shown in FIGS. 2 and 3 have been conventionally provided.
即ち、第２図に示すものは、内歯車を軸方向に２分割し
て４ａ４ｂとし、これを多数のピン７にて結合した後固
定金具８を介してケーシング９に支持し、ピン７０弾性
により２分割された内歯車４ａ、４ｂをその半径方向に
相対変位可能としている。That is, in the case shown in FIG. 2, the internal gear is divided into two in the axial direction to form 4a4b, which are joined by a large number of pins 7 and then supported on a casing 9 via a fixture 8. The two divided internal gears 4a and 4b can be relatively displaced in the radial direction.
會た、第３図に示すものは、内歯車４を薄鋼板から成る
ステイ１３を介してケーシング９に支持しステイ１３の
弾性により内歯車４をその半径方向に変位可能としてい
る。In the device shown in FIG. 3, the internal gear 4 is supported by a casing 9 via a stay 13 made of a thin steel plate, and the elasticity of the stay 13 allows the internal gear 4 to be displaced in its radial direction.
しかしながら第２図に示すものは多数のピンＩが必要で
あるためピン７を挿入するための孔の加工やピン７と内
歯車４ａ 、４ｂとの結合に多大な工数を要すると共に
固定金具８を設けるためケーシング９の外径が大きくな
り、また第３図に示すものは、薄鋼板製のステイ１３の
剛性の面から伝達動力が太きいものには適用できない。However, the one shown in FIG. 2 requires a large number of pins I, and requires a large number of man-hours to prepare holes for inserting the pins 7 and to connect the pins 7 to the internal gears 4a and 4b, and also requires a fixing metal fitting 8. Because of this provision, the outer diameter of the casing 9 becomes large, and the structure shown in FIG. 3 cannot be applied to a structure in which the transmitted power is large due to the rigidity of the stay 13 made of a thin steel plate.
等の問題点があった。本考案は上記に鑑みなされたもの
で、小型かつコンパクトな装置で以って各遊星歯車への
伝達荷重を均等化すると共に大きな伝達動力にも充分耐
え得る遊星歯車装置を提供することを目的とする。There were problems such as. The present invention was developed in view of the above, and the purpose is to provide a planetary gear device that is small and compact, equalizes the load transmitted to each planetary gear, and can sufficiently withstand large transmitted power. do.
このため本考案係る遊星歯車装置は、円環状の内歯車の
外周面に１個または複数個の受圧部材を突設すると共に
受圧部材と静止部材との間に弾性体を介装し内歯車を受
圧部材及び弾性体を介して円周方向に微動可能な状態で
静止部材に支承する一方、内歯車と静止部材との間に該
内歯車をその円周方向に移動可能にかつ鉛直方向に一定
以上の移動を規制して支承する軸受を設けたことを特徴
としている。For this reason, the planetary gear device according to the present invention has one or more pressure-receiving members protruding from the outer peripheral surface of the annular internal gear, and an elastic body is interposed between the pressure-receiving member and the stationary member. The internal gear is supported by a stationary member so as to be slightly movable in the circumferential direction via a pressure receiving member and an elastic body, while the internal gear is movable in the circumferential direction and fixed in the vertical direction between the internal gear and the stationary member. It is characterized by the provision of a bearing that restricts and supports the above movement.
以下第４図ないし第５図を参照して本考案の１実施例に
つき説明すると、２１は入力軸に連動連結された太陽歯
車、２２はキャリヤ２４に軸支された複数個（この場合
は６個）の遊星歯車でありこれらの構成は第１図に示す
従来のものと同様である。Hereinafter, one embodiment of the present invention will be described with reference to FIGS. 4 and 5. Reference numeral 21 denotes a sun gear coupled to an input shaft, 22 a plurality of gears (in this case, 6 sun gears) pivotally supported by a carrier 24. These planetary gears are similar in construction to the conventional gear shown in FIG.
２３は円環状の内歯車で、上記遊星歯車２２は該内歯車
２３と太陽歯車２１に夫々噛合されている。23 is an annular internal gear, and the planetary gear 22 is meshed with the internal gear 23 and the sun gear 21, respectively.
上記内歯車２３の外周面２３ａには複数個（この場合は
４個）の受圧部材２６が突設される。A plurality of (four in this case) pressure receiving members 26 are provided protruding from the outer peripheral surface 23a of the internal gear 23.
２７は台板２９に形成された支持箱であり、該支持箱２
７と上記受圧部材２６との間には板ばね２８が介装され
る。27 is a support box formed on the base plate 29, and the support box 2
A leaf spring 28 is interposed between the pressure receiving member 7 and the pressure receiving member 26 .
即ち、第５図に示すように、支持箱２Ｔの内壁に１枚重
たは複数枚（この場合は４枚）の板ばね２８の一端をボ
ルト３０により固着し、該板ばね２８の板面を上記受圧
部材２６の内歯車２３０円周方向に対向する側面２６ａ
に当接せしめ、内歯車２３がその円周方向に変位すると
板ばね２８が撓むようにする。That is, as shown in FIG. 5, one end of one or more (four in this case) leaf springs 28 is fixed to the inner wall of the support box 2T with bolts 30, and the plate surface of the leaf spring 28 is fixed to the inner wall of the support box 2T. The side surface 26a facing the internal gear 230 of the pressure receiving member 26 in the circumferential direction
When the internal gear 23 is displaced in the circumferential direction, the leaf spring 28 is bent.
２５は内歯車２３を鉛直方向に支承するすべり軸受であ
り、該すべり軸受２５は、その軸受面と内歯車２３の外
周面２３ａとの間に形成される油膜の厚さ以上に内歯車
２３が鉛直方向に移動するのを規制する。Reference numeral 25 denotes a sliding bearing that supports the internal gear 23 in the vertical direction. Prevents movement in the vertical direction.
上記装置において、入力軸及びこれに連動連結された太
陽歯車２１が回転し、遊星歯車２２及びキャリヤ２４が
回転せしめられて入力軸の動力が出力軸に伝達される際
には、遊星歯車２２と内歯車２３との噛み合いの反力に
より内歯車２３はその円周方向に微小変位せしめられる
。In the above device, when the input shaft and the sun gear 21 interlocked therewith rotate, the planet gears 22 and the carrier 24 are rotated, and the power of the input shaft is transmitted to the output shaft. The internal gear 23 is slightly displaced in the circumferential direction by the reaction force of the engagement with the internal gear 23.
その結果受圧部材２６を介して板ばね２８が撓み、上記
反力は支持箱２７を介して合板２９に吸収されることと
なる。As a result, the leaf spring 28 is bent via the pressure receiving member 26, and the reaction force is absorbed by the plywood 29 via the support box 27.
各遊星歯車２２に均等に歯車荷重が分布している場合は
内歯車２３がその自重により該内歯車２３と遊星歯車２
２との間のバックラッシュの分だけ鉛直方向に移動しよ
うとするが、すべり軸受２５によりその移動が規制され
る。When the gear load is evenly distributed to each planetary gear 22, the internal gear 23 and the planetary gear 2 due to their own weight.
2, but the slide bearing 25 restricts the movement.
各遊星歯車２２の歯車荷重が不均等にな、す、内歯車２
３０円周方向に強い噛み合いの反力が作用する場合は、
受圧部材２６を介して板ばね２８が撓壕されることによ
り内歯車２３がその円周方向に微動して上記反力が減衰
せしめられ各遊星歯車２２の歯車荷重が均等化される。If the gear loads on each planetary gear 22 are uneven, the internal gear 2
30When a strong meshing reaction force acts in the circumferential direction,
As the leaf spring 28 is biased through the pressure receiving member 26, the internal gear 23 moves slightly in its circumferential direction, the reaction force is attenuated, and the gear loads of the planetary gears 22 are equalized.
また各遊星歯車２２の歯車荷重の不均等により内歯車２
３が鉛直方向に変位せしめられようとする場合は、内歯
車２３は、その外周面２３ａとすべり軸受２５との間に
形成される油膜の厚さ分だけ微動せしめられる結果、各
遊星歯車２２の歯車荷重が均等化される。In addition, due to the uneven gear load of each planetary gear 22, the internal gear 2
3 is about to be displaced in the vertical direction, the internal gear 23 is slightly moved by the thickness of the oil film formed between its outer peripheral surface 23a and the slide bearing 25, and as a result, each planetary gear 22 Gear loads are equalized.
上記のように、各遊星歯車２２の歯車荷重が不均等にな
った場合は板ばね２８により内歯車２３０円周方向への
微動を許容しすべり軸受２５の油膜により内歯車２３の
鉛直方向への微動を許容することにより、各遊星歯車２
２の歯車荷重を均等化せしめ得る。As mentioned above, if the gear loads on each planetary gear 22 become uneven, the leaf spring 28 allows slight movement of the internal gear 230 in the circumferential direction, and the oil film of the slide bearing 25 causes the internal gear 23 to move vertically. By allowing slight movement, each planetary gear 2
The two gear loads can be equalized.
第６図は本考案の他の実施例を示し、この場合は支持箱
２７の内壁に１対の防振ゴム４１を固着し各防振ゴム４
１を受圧部材２６の側面２６ａに当接せしめ防振ゴム４
１により受圧部材２６を挾み付けている。FIG. 6 shows another embodiment of the present invention, in which a pair of anti-vibration rubbers 41 are fixed to the inner wall of the support box 27, and each anti-vibration rubber 4
1 is brought into contact with the side surface 26a of the pressure receiving member 26, and the vibration isolating rubber 4
1, the pressure receiving member 26 is sandwiched between them.
作用、効果は上記第１実施例の場合と同様である。The operation and effect are the same as in the first embodiment.
更に図示を省略したが、支持箱２７の内壁面と受圧部材
２６の側面２６ａとの間に粘性を有する液体を介在させ
てもよい。Furthermore, although not shown, a viscous liquid may be interposed between the inner wall surface of the support box 27 and the side surface 26a of the pressure receiving member 26.
以上のように本考案に係る遊星歯車装置は、円環状の内
壁車の外周面に突設された１個または複数個の受圧部材
と静止部材との間に弾性体を介装して内歯車を上記受圧
部材及び弾性体を介して内歯車の円周方向に微動可能な
状態で静止部材に支承する一方、内歯車と静止部材との
間に該内歯車をその円周方向に移動可能にかつ鉛直方向
に一定以上の移動を規制して支承する軸受を設けたので
、各遊星歯車と太陽歯車及び内歯車との間に噛み合いの
不均一が生じた際には内歯車がその円周方向及び鉛直方
向に微動することにより各遊星歯車の歯車荷重が均等化
され、歯面のピッチングや歯の曲げ疲労の発生が未然に
防止される。As described above, in the planetary gear device according to the present invention, an elastic body is interposed between one or more pressure receiving members protruding from the outer circumferential surface of the annular inner wall wheel and the stationary member. is supported on a stationary member so as to be able to move slightly in the circumferential direction of the internal gear via the pressure receiving member and the elastic body, while the internal gear is movable in the circumferential direction between the internal gear and the stationary member. In addition, since a bearing is provided to support the planetary gears by restricting movement beyond a certain level in the vertical direction, when uneven meshing occurs between each planetary gear and the sun gear or internal gear, the internal gear will move in the circumferential direction. The gear load of each planetary gear is equalized by slight movement in the vertical direction, and pitching of the tooth surface and tooth bending fatigue are prevented from occurring.
また従来のピンによる支持方式等に比較すると構造が小
型かつ簡単である。Furthermore, the structure is smaller and simpler than conventional pin support systems.
更に板面が略半径方向に位置された受圧部材と静止部材
との間に弾性体を介装したので、受圧部材の受圧面積が
大きくとれることにより大伝動力に充分耐えることがで
きると共に弾性体のばね定数の選定にも自由度を持たせ
得る。Furthermore, since an elastic body is interposed between the pressure-receiving member and the stationary member whose plate surfaces are located approximately in the radial direction, the pressure-receiving area of the pressure-receiving member is large, and the elastic body can sufficiently withstand large transmission forces. A degree of freedom can also be given to the selection of the spring constant.
第１図ないし第３図は従来の遊星歯車装置の１例を示し
、第１図は入力軸の軸心線に沿う断面図、第２図及び第
３図は従来の内歯車の支持方式の１例を示す断面図であ
る。
第４図及び第５図は本考案の１実施例を示し、第４図は
入力軸の軸心線に直角方向の断面図、第５図は第４図の
Ｖ部を拡大した図である。
第６図は本考案の他の実施例を示す第５図に応当する図
である。
２１・・・・・・太陽歯車、２２・・・・・・遊星歯車
、２３・・・・・・内歯車、２４・・・・・・キャリヤ
、２５・・・・・・すべり軸受、２６・・・・・・受圧
部材、２８・・・・・・板ばね、２９・・・・・・台板
、４１・・・・・・防振ゴム。Figures 1 to 3 show an example of a conventional planetary gear device. Figure 1 is a sectional view along the axis of the input shaft, and Figures 2 and 3 are of a conventional internal gear support system. It is a sectional view showing one example. 4 and 5 show one embodiment of the present invention, FIG. 4 is a sectional view taken in a direction perpendicular to the axis of the input shaft, and FIG. 5 is an enlarged view of the V section in FIG. 4. . FIG. 6 is a diagram corresponding to FIG. 5 showing another embodiment of the present invention. 21...Sun gear, 22...Planet gear, 23...Internal gear, 24...Carrier, 25...Slide bearing, 26 ...Pressure receiving member, 28 ... Leaf spring, 29 ... Base plate, 41 ... Vibration isolating rubber.
Claims (1)
形成された申歯車の内周との間に第２の回転軸に連動連
結されるキャリヤに軸支された複数個の遊星歯車を配設
してこれを上記太陽歯車及び内歯車に噛合せしめ、太陽
歯車の回転を遊星歯車を介してキャリヤに伝達すること
により上記第１および第２の回転軸間に動力を伝達する
遊星歯車装置において、上記内歯車の外周面に１個會た
は複数個の受圧部材をその板面が該内歯車の略半径方向
になるように突設し、上記受圧部材の上記内歯車の円周
方向に対向する両側面と合板等の静止部材との間には、
上記内歯車をその円周方向に微動可能に上記静止部材に
支承せしめるための弾性体を介装し、上記内歯車をその
円周方向に移動可能にかつ鉛直方向には一定以上の移動
を規制せしめる軸受にて内歯車の外周を支承したことを
特徴とする遊星歯車装置。A plurality of planetary gears are pivotally supported on a carrier that is interlockingly connected to a second rotating shaft between the outer circumference of the sun gear that is interlockingly connected to the first rotating shaft and the inner circumference of the annularly formed monkey gear. a planetary gear that is arranged to mesh with the sun gear and the internal gear, and transmits the rotation of the sun gear to the carrier via the planetary gear, thereby transmitting power between the first and second rotating shafts. In the device, one or more pressure-receiving members are provided on the outer peripheral surface of the internal gear so that the plate surfaces of the pressure-receiving members extend substantially in the radial direction of the internal gear; Between both sides facing each other in the direction and a stationary member such as plywood,
An elastic body is interposed to support the stationary member so that the internal gear can be moved slightly in the circumferential direction, and the internal gear is movable in the circumferential direction and restricted from moving beyond a certain level in the vertical direction. A planetary gear device characterized in that the outer periphery of an internal gear is supported by a bearing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1979005185U JPS587150Y2 (en) | 1979-01-19 | 1979-01-19 | planetary gearbox |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1979005185U JPS587150Y2 (en) | 1979-01-19 | 1979-01-19 | planetary gearbox |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS55105653U JPS55105653U (en) | 1980-07-23 |
| JPS587150Y2 true JPS587150Y2 (en) | 1983-02-08 |
Family
ID=28810813
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1979005185U Expired JPS587150Y2 (en) | 1979-01-19 | 1979-01-19 | planetary gearbox |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS587150Y2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2019039599A1 (en) * | 2017-08-25 | 2019-02-28 | アイシン・エィ・ダブリュ株式会社 | Vehicle drive device |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5139112Y2 (en) * | 1972-03-09 | 1976-09-24 |
-
1979
- 1979-01-19 JP JP1979005185U patent/JPS587150Y2/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS55105653U (en) | 1980-07-23 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4090416A (en) | Gear boxes | |
| US4898065A (en) | Planetary reduction gear | |
| US3839922A (en) | Transmission gear | |
| US4610182A (en) | Planetary gear arranged in a gear housing between a jet engine and an electrical engine | |
| US5368529A (en) | Toroidal type continuously variable transmission | |
| US4289045A (en) | Housings of gearboxes for power units | |
| US3218889A (en) | Transmi s s ion | |
| US5025671A (en) | High ratio planetary type traction roller transmission | |
| US5472387A (en) | Self aligning planetary gear transmissions | |
| US5498215A (en) | Reduction gear assembly | |
| JPS587150Y2 (en) | planetary gearbox | |
| US4653346A (en) | Transmission for use in motor vehicle | |
| US3481222A (en) | Planetary gear reducer | |
| US3511114A (en) | Toroue wrench | |
| US6929578B1 (en) | Planetary gear carrier assembly | |
| US11913538B2 (en) | Integrated design of a sun shaft | |
| JP2896080B2 (en) | Transmissions used in geared motor series | |
| US3641842A (en) | Roller traction drive | |
| JPS608559A (en) | Friction speed changer | |
| US5255895A (en) | Gear transmission in a lifting machinery | |
| CN112728011A (en) | Gear transmission structure for testing transmission performance of alignment bevel gear | |
| JP2002061727A (en) | Differential frictoin roller reduction gear | |
| US2255717A (en) | Flexible connection | |
| CN212455436U (en) | Planetary transmission gear box and sun gear flexible supporting structure | |
| JPS639802Y2 (en) |