JPH0742797A - Vibrationproof structure of planetary gear - Google Patents
Vibrationproof structure of planetary gearInfo
- Publication number
- JPH0742797A JPH0742797A JP19440293A JP19440293A JPH0742797A JP H0742797 A JPH0742797 A JP H0742797A JP 19440293 A JP19440293 A JP 19440293A JP 19440293 A JP19440293 A JP 19440293A JP H0742797 A JPH0742797 A JP H0742797A
- Authority
- JP
- Japan
- Prior art keywords
- planetary gear
- shaft
- gear mechanism
- meshing
- vibration
- 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.)
- Pending
Links
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- Retarders (AREA)
- Vibration Prevention Devices (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、遊星歯車装置の防振構
造に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vibration isolation structure for a planetary gear device.
【０００２】[0002]
【従来の技術】一般に、船舶においては、ディーゼルエ
ンジン等の駆動装置の駆動軸の回転を遊星歯車装置を介
してプロペラ軸へ伝えるようにしており、その一例とし
ては、例えば、図３に示されるようなものがあり、１は
駆動装置の駆動軸、２は駆動軸１に接続される入力軸、
３はプロペラ軸、４はプロペラ軸３に接続される出力
軸、５は入力軸２の回転を出力軸４に伝えるための遊星
歯車機構、６は遊星歯車機構５の歯車箱、７はプロペラ
軸３から出力軸４へ伝わるプロペラ推力を受けるための
スラスト軸受であり、駆動装置の駆動軸１の回転は、入
力軸２から該入力軸２と一体の太陽歯車８と、遊星歯車
９と、出力軸４と歯車継手で連結された内歯歯車１０と
を介して出力軸４へ伝えられ、該出力軸４の回転がプロ
ペラ軸３へ伝達されるようになっている。2. Description of the Related Art Generally, in a ship, the rotation of a drive shaft of a drive unit such as a diesel engine is transmitted to a propeller shaft via a planetary gear unit. One example thereof is shown in FIG. Such as, 1 is the drive shaft of the drive device, 2 is the input shaft connected to the drive shaft 1,
3 is a propeller shaft, 4 is an output shaft connected to the propeller shaft 3, 5 is a planetary gear mechanism for transmitting the rotation of the input shaft 2 to the output shaft 4, 6 is a gear box of the planetary gear mechanism 5, and 7 is a propeller shaft. 3 is a thrust bearing for receiving a propeller thrust transmitted from the drive shaft 3 to the output shaft 4, and the rotation of the drive shaft 1 of the drive device is such that the input shaft 2 rotates the sun gear 8 integral with the input shaft 2, the planetary gear 9, and the output. The rotation of the output shaft 4 is transmitted to the propeller shaft 3 by being transmitted to the output shaft 4 via the shaft 4 and an internal gear 10 connected by a gear joint.
【０００３】[0003]
【発明が解決しようとする課題】しかしながら、前述の
如き遊星歯車装置では、プロペラ推力を受けるスラスト
軸受７が遊星歯車機構５の歯車箱６内に一体に組み込ま
れており、該歯車箱６は、プロペラの大きな推力と遊星
歯車機構５の噛合反力による回転モーメントを受けるこ
ととなるため、船殻に固定の据付台１１に対し図示して
いない数多くのリーマボルト及び締付ボルトによって前
記歯車箱６を強固に固定しなければならず、この結果、
遊星歯車機構５の歯車８，９，１０の噛合部で発生する
噛合振動が歯車８，９，１０、軸受、歯車箱６、固定ボ
ルト類から船殻へ固体伝播振動として伝わり、船室等の
壁から放射され、騒音の問題を引き起こしていた。However, in the planetary gear device as described above, the thrust bearing 7 that receives the propeller thrust is integrally incorporated in the gear box 6 of the planetary gear mechanism 5, and the gear box 6 is Since a large thrust of the propeller and a rotational moment due to the meshing reaction force of the planetary gear mechanism 5 are received, the gear box 6 is fixed to the mounting base 11 fixed to the hull by a large number of reamer bolts and tightening bolts (not shown). It has to be firmly fixed, which results in
The meshing vibration generated at the meshing portion of the gears 8, 9 and 10 of the planetary gear mechanism 5 is transmitted from the gears 8, 9 and 10, the bearing, the gear box 6 and the fixing bolts to the hull as solid propagating vibration, and the wall of the cabin etc. Radiated from it, causing noise problems.
【０００４】このため、歯車精度を向上させたり、歯形
修正等を施し、噛合振動の発生そのものを小さくする手
段も講じられているが、加工精度並びにコスト面等で限
界があった。For this reason, measures have been taken to improve the accuracy of the gears, modify the tooth profile, etc. to reduce the occurrence of meshing vibration itself, but there is a limit in terms of machining accuracy and cost.
【０００５】一方、図４に示される如く、スラスト軸受
内蔵のスラスト軸受ブロック１２と遊星歯車機構内蔵の
歯車箱６を独立させ、該歯車箱６を弾性部材１３によっ
て支持すると共に、歯車箱６とスラスト軸受ブロック１
２との間にミスアライメント吸収用継手１４を、又、歯
車箱６と駆動装置１５との間に高ミスアライメント吸収
形弾性継手１６を夫々介在せしめることにより、前記歯
車箱６を防振支持することも考えられるが、この場合、
スラスト軸受ブロック１２と歯車箱６とが別々に設置さ
れるため、据付スペースが大きくなり、しかも、歯車箱
６に作用する回転モーメントが大きいことも防振支持の
ために大きなスペースを必要とする要因となる。又、ア
ライメントの変化が大きいため、ミスアライメント吸収
用継手１４や高ミスアライメント吸収形弾性継手１６と
いった非常に高価な継手を必要とし、実用的とはいえな
かった。On the other hand, as shown in FIG. 4, the thrust bearing block 12 having a built-in thrust bearing and the gear box 6 having a planetary gear mechanism are independent of each other, and the gear box 6 is supported by an elastic member 13, and Thrust bearing block 1
The gearbox 6 is vibration-proofed by interposing a misalignment absorbing joint 14 between the gearbox 6 and the gearbox 6, and a high misalignment absorbing elastic joint 16 between the gearbox 6 and the drive unit 15, respectively. It is possible, but in this case,
Since the thrust bearing block 12 and the gear box 6 are separately installed, the installation space becomes large, and the large rotation moment acting on the gear box 6 also causes a large space for vibration-proof support. Becomes Further, since the change in alignment is large, a very expensive joint such as the misalignment absorption joint 14 or the high misalignment absorption type elastic joint 16 is required, which is not practical.
【０００６】本発明は、斯かる実情に鑑み、据付スペー
スを増大させることなく、且つ高価な継手等を用いるこ
となく、遊星歯車機構の歯車の噛合部で発生する噛合振
動の据付台側への伝播を防止し得、騒音の発生を抑制し
得る遊星歯車装置の防振構造を提供しようとするもので
ある。In view of the above-mentioned circumstances, the present invention provides the installation base side of the meshing vibration generated at the meshing portion of the gears of the planetary gear mechanism without increasing the installation space and without using an expensive joint or the like. It is an object of the present invention to provide a vibration isolation structure for a planetary gear device that can prevent propagation and suppress noise generation.
【０００７】[0007]
【課題を解決するための手段】本発明は、駆動装置の駆
動軸に接続される入力軸と、プロペラ軸に接続される出
力軸と、前記入力軸の回転を出力軸に伝えるための遊星
歯車機構とを備えた遊星歯車装置の防振構造であって、
前記出力軸に作用するプロペラ軸からのスラスト力を受
けるためのスラスト軸受が内蔵されたスラスト軸受ブロ
ックを据付台上に固定し、前記遊星歯車機構を内蔵した
歯車箱の入力軸側に該入力軸と同心に突設されたボス部
を、据付台上に固定した支持台に、所望のばね定数を有
する支持ピースを介して回動自在に支持せしめると共
に、前記歯車箱の出力軸側に該出力軸と同心に突設され
たボス部を、前記スラスト軸受ブロックに、所望のばね
定数を有する支持ピースを介して回動自在に支持せし
め、又、前記歯車箱の軸心を中心として１８０゜位相の
ずれた位置に、据付台上に並設された油圧シリンダを接
続し、且つ該一方の油圧シリンダのロッド側室及びヘッ
ド側室と、他方の油圧シリンダのヘッド側室及びロッド
側室とを接続して、前記遊星歯車機構の噛合反力によっ
て歯車箱に作用する回転モーメントを支持するための油
圧閉回路を構成したことを特徴とするものである。According to the present invention, an input shaft connected to a drive shaft of a drive unit, an output shaft connected to a propeller shaft, and a planetary gear for transmitting the rotation of the input shaft to the output shaft. A vibration-proof structure for a planetary gear device including a mechanism,
A thrust bearing block containing a thrust bearing for receiving a thrust force from a propeller shaft acting on the output shaft is fixed on a mounting table, and the input shaft is provided on the input shaft side of a gear box containing the planetary gear mechanism. A boss portion that is concentrically provided with the boss is rotatably supported by a support base fixed on the installation base via a support piece having a desired spring constant, and the output is provided on the output shaft side of the gear box. A boss portion projecting concentrically with the shaft is rotatably supported on the thrust bearing block via a support piece having a desired spring constant, and a 180 ° phase shift about the shaft center of the gear box. The hydraulic cylinders arranged side by side on the installation base are connected to the positions displaced from each other, and the rod side chamber and the head side chamber of the one hydraulic cylinder are connected to the head side chamber and the rod side chamber of the other hydraulic cylinder, Previous It is characterized in that to constitute a closed hydraulic circuit for supporting the rotating moment acting on the gearbox by meshing reaction force of the planetary gear mechanism.
【０００８】[0008]
【作用】従って、駆動装置の駆動軸の回転は、入力軸か
ら遊星歯車機構を介して出力軸へ伝えられ、該出力軸の
回転がプロペラ軸へ伝達される。Therefore, the rotation of the drive shaft of the drive device is transmitted from the input shaft to the output shaft via the planetary gear mechanism, and the rotation of the output shaft is transmitted to the propeller shaft.
【０００９】ここで、前記歯車箱の自重は、支持ピース
を介して支持台とスラスト軸受ブロックとにより支えら
れており、支持ピースのばね定数ｋと遊星歯車機構及び
歯車箱の自重とで決まる振動系の固有値ｆ0が、遊星歯
車機構の噛合部で発生する噛合振動数ｆに対しｆ／ｆ0
＞２．５となるように、前記支持ピースのばね定数ｋを
選定しておけば、遊星歯車機構の噛合部で発生する噛合
振動は、支持ピースによって防振され、据付台へ伝わる
固体伝播振動が著しく減少し、騒音として放射されるこ
ともない。Here, the self-weight of the gear box is supported by the support base and the thrust bearing block via the support piece, and the vibration is determined by the spring constant k of the support piece and the self-weight of the planetary gear mechanism and the gear box. The eigenvalue f 0 of the system is f / f 0 with respect to the meshing frequency f generated at the meshing portion of the planetary gear mechanism.
If the spring constant k of the support piece is selected so that> 2.5, the meshing vibration generated at the meshing part of the planetary gear mechanism is isolated by the support piece and propagated to the mounting table. Is significantly reduced and is not emitted as noise.
【００１０】又、前記遊星歯車機構の噛合反力によって
歯車箱に作用する回転モーメントは、油圧閉回路を構成
する油圧シリンダにより支持されており、油圧閉回路の
ばね定数ｋcと歯車箱（場合によっては歯車箱以降の軸
及びプロペラを含めたもの）の極慣性モーメントとで決
まる捩り振動固有値Ｆ0が、前記遊星歯車機構の噛合反
力による回転モーメント中の噛合振動数ｆに対しｆ／Ｆ
0＞２．５となるように、前記油圧閉回路のばね定数ｋc
を選定し、該ばね定数ｋcに基づいて前記各油圧シリン
ダの断面積、ロッド側室とヘッド側室と油路の全体積Ｖ
を決定しておけば、遊星歯車機構の噛合反力による回転
モーメント中の噛合振動は、油圧閉回路を構成する油圧
シリンダによって防振され、据付台へ伝わる固体伝播振
動は著しく減少し、騒音として放射されることもない。Further, the rotational moment acting on the gear box by the meshing reaction force of the planetary gear mechanism is supported by a hydraulic cylinder forming a hydraulic closed circuit, and the spring constant kc of the hydraulic closed circuit and the gear box (depending on the case). Is an eigenvalue of torsional vibration F 0, which is determined by the polar moment of inertia of the shaft after the gear box and the propeller) and f / F with respect to the meshing frequency f during the rotation moment due to the meshing reaction force of the planetary gear mechanism.
So that 0 > 2.5, the spring constant kc of the hydraulic closed circuit
Is selected, and based on the spring constant kc, the sectional area of each hydraulic cylinder, the total volume V of the rod side chamber, the head side chamber, and the oil passage V
, The meshing vibration during the rotation moment due to the meshing reaction force of the planetary gear mechanism is isolated by the hydraulic cylinders that make up the hydraulic closed circuit, and the solid propagation vibrations transmitted to the installation base are significantly reduced, resulting in noise. It will not be emitted.
【００１１】[0011]
【実施例】以下、本発明の実施例を図面を参照しつつ説
明する。Embodiments of the present invention will be described below with reference to the drawings.
【００１２】図１及び図２は本発明の一実施例であっ
て、図中、図３と同一の符号を付した部分は同一物を表
わしており、出力軸４に作用するプロペラ軸３からのス
ラスト力を受けるためのスラスト軸受７が内蔵されたス
ラスト軸受ブロック１２を複数のボルト１７により据付
台１１上に固定し、遊星歯車機構５を内蔵した歯車箱６
の入力軸２側に該入力軸２と同心に突設されたボス部１
８を、据付台１１上に固定した支持台１９に、所望のば
ね定数ｋを有する支持ピース２０を介して回動自在に支
持せしめると共に、前記歯車箱６の出力軸４側に該出力
軸４と同心に突設されたボス部２１を、前記スラスト軸
受ブロック１２のボス部２２に、所望のばね定数ｋを有
する支持ピース２３を介して回動自在に支持せしめる。
尚、前記支持ピース２０，２３としては、例えば、ゴ
ム、合成樹脂、又は弾性係数の小さなアルミ等の金属を
用い、該支持ピース２０，２３のばね定数ｋと遊星歯車
機構５及び歯車箱６の自重とで決まる振動系の固有値ｆ
0が、遊星歯車機構５の噛合部で発生する噛合振動数ｆ
に対しｆ／ｆ0＞２．５となるように、前記支持ピース
２０，２３のばね定数ｋを選定する。1 and 2 show an embodiment of the present invention. In the drawings, the parts designated by the same reference numerals as those in FIG. 3 represent the same parts, and from the propeller shaft 3 acting on the output shaft 4. A thrust bearing block 12 having a built-in thrust bearing 7 for receiving the thrust force is fixed on a mounting base 11 by a plurality of bolts 17, and a gear box 6 having a planetary gear mechanism 5 built therein.
Of the boss 1 projecting concentrically with the input shaft 2 on the input shaft 2 side of the
8 is rotatably supported on a support base 19 fixed on a mounting base 11 via a support piece 20 having a desired spring constant k, and the output shaft 4 is provided on the output shaft 4 side of the gear box 6. A boss portion 21 that is provided concentrically with is rotatably supported by the boss portion 22 of the thrust bearing block 12 via a support piece 23 having a desired spring constant k.
As the support pieces 20 and 23, for example, a metal such as rubber, synthetic resin, or aluminum having a small elastic coefficient is used, and the spring constant k of the support pieces 20 and 23 and the planetary gear mechanism 5 and the gear box 6 are set. Eigenvalue f of the vibration system determined by its own weight
0 is the meshing frequency f generated at the meshing portion of the planetary gear mechanism 5.
On the other hand, the spring constant k of the support pieces 20 and 23 is selected so that f / f 0 > 2.5.
【００１３】又、前記歯車箱６の軸心Ｏを中心として１
８０゜位相のずれた位置に、据付台１１上に並設された
油圧シリンダ２４，２５を接続し、該一方の油圧シリン
ダ２４のロッド側室２４ａと他方の油圧シリンダ２５の
ヘッド側室２５ｂとを油路２６を介して接続すると共
に、前記一方の油圧シリンダ２４のヘッド側室２４ｂと
他方の油圧シリンダ２５のロッド側室２５ａとを油路２
７を介して接続し、遊星歯車機構５の噛合反力によって
歯車箱６に作用する回転モーメントを支持するための油
圧閉回路２８を構成する。Further, with the axis O of the gear box 6 as the center,
Hydraulic cylinders 24 and 25 arranged side by side on the installation base 11 are connected at positions shifted by 80 ° in phase, and the rod side chamber 24a of the one hydraulic cylinder 24 and the head side chamber 25b of the other hydraulic cylinder 25 are oiled. The head side chamber 24b of the one hydraulic cylinder 24 and the rod side chamber 25a of the other hydraulic cylinder 25 are connected to each other via the passage 26.
A hydraulic closed circuit 28 for supporting a rotational moment acting on the gear box 6 by the meshing reaction force of the planetary gear mechanism 5 is formed.
【００１４】前記油圧閉回路２８のばね定数ｋcは、油
の体積弾性係数をＫ、各油圧シリンダ２４，２５の断面
積をＳ、ロッド側室２４ａとヘッド側室２５ｂと油路２
６の全体積をＶとすると、The spring constant kc of the hydraulic closed circuit 28 is K, the bulk elastic coefficient of oil, S is the cross-sectional area of each hydraulic cylinder 24, 25, the rod side chamber 24a, the head side chamber 25b, and the oil passage 2.
If the total volume of 6 is V,
【数１】ｋc＝Ｋ・Ｓ2／Ｖ で与えられるため、該油圧閉回路２８のばね定数ｋcと
歯車箱６（場合によっては歯車箱６以降の軸及びプロペ
ラを含めたもの）の極慣性モーメントとで決まる捩り振
動固有値Ｆ0が、前記遊星歯車機構５の噛合反力による
回転モーメント中の噛合振動数ｆに対しｆ／Ｆ0＞２．
５となるように、前記油圧閉回路２８のばね定数ｋcを
選定し、該ばね定数ｋcに基づいて前記各油圧シリンダ
２４，２５の断面積Ｓ、ロッド側室２４ａとヘッド側室
２５ｂと油路２６の全体積Ｖを決定する。Since it is given by kc = K · S 2 / V, the spring constant kc of the hydraulic closed circuit 28 and the polar inertia of the gear box 6 (including the shaft and the propeller after the gear box 6 in some cases) The torsional vibration eigenvalue F 0 determined by the moment and the meshing frequency f in the rotation moment due to the meshing reaction force of the planetary gear mechanism 5 is f / F 0 > 2.
5, the spring constant kc of the hydraulic closed circuit 28 is selected, and based on the spring constant kc, the sectional area S of the hydraulic cylinders 24 and 25, the rod side chamber 24a, the head side chamber 25b, and the oil passage 26 are selected. Determine the total volume V.
【００１５】尚、２９は歯車箱６の回転変位を検出する
リミットスイッチ、３０，３１はリミットスイッチ２９
からの検出信号に基づいて開閉され、油圧シリンダ２
４，２５におけるリーク分の油を給排するためのバルブ
である。Incidentally, 29 is a limit switch for detecting the rotational displacement of the gear box 6, and 30 and 31 are limit switches 29.
The hydraulic cylinder 2 is opened and closed based on the detection signal from the
It is a valve for supplying / discharging the oil for the leak at 4 and 25.
【００１６】次に、上記実施例の作動を説明する。Next, the operation of the above embodiment will be described.
【００１７】駆動装置の駆動軸１の回転は、入力軸２か
ら該入力軸２と一体の太陽歯車８と、遊星歯車９と、内
歯歯車１０とを介して出力軸４へ伝えられ、該出力軸４
の回転がプロペラ軸３へ伝達される。The rotation of the drive shaft 1 of the drive device is transmitted from the input shaft 2 to the output shaft 4 via the sun gear 8 integral with the input shaft 2, the planetary gear 9, and the internal gear 10. Output shaft 4
Is transmitted to the propeller shaft 3.
【００１８】ここで、前記歯車箱６の自重は、支持ピー
ス２０，２３を介して支持台１９とスラスト軸受ブロッ
ク１２とにより支えられており、支持ピース２０，２３
のばね定数ｋと遊星歯車機構５及び歯車箱６の自重とで
決まる振動系の固有値ｆ0が、遊星歯車機構５の噛合部
で発生する噛合振動数ｆに対しｆ／ｆ0＞２．５となる
ように、前記支持ピース２０，２３のばね定数ｋを選定
しておけば、遊星歯車機構５の噛合部で発生する噛合振
動は、支持ピース２０，２３によって防振され、据付台
１１から船殻へ伝わる固体伝播振動は著しく減少し、船
室等の壁から騒音として放射されることもない。Here, the weight of the gear box 6 is supported by the support base 19 and the thrust bearing block 12 via the support pieces 20, 23, and the support pieces 20, 23 are supported.
The eigenvalue f 0 of the vibration system, which is determined by the spring constant k and the weight of the planetary gear mechanism 5 and the gear box 6, is f / f 0 > 2.5 with respect to the meshing frequency f generated at the meshing portion of the planetary gear mechanism 5. If the spring constant k of the supporting pieces 20 and 23 is selected so that, the meshing vibration generated at the meshing portion of the planetary gear mechanism 5 is isolated by the supporting pieces 20 and 23, and the mounting base 11 Solid-borne vibration transmitted to the hull is significantly reduced, and it is not radiated as noise from walls such as the cabin.
【００１９】又、前記遊星歯車機構５の噛合反力によっ
て歯車箱６に作用する回転モーメントは、油圧閉回路２
８を構成する油圧シリンダ２４，２５により支持されて
おり、油圧閉回路２８のばね定数ｋcと歯車箱６の極慣
性モーメントとで決まる捩り振動固有値Ｆ0が、前記遊
星歯車機構５の噛合反力による回転モーメント中の噛合
振動数ｆに対しｆ／Ｆ0＞２．５となるように、前記油
圧閉回路２８のばね定数ｋcを選定し、該ばね定数ｋcに
基づいて前記各油圧シリンダ２４，２５の断面積Ｓ、ロ
ッド側室２４ａとヘッド側室２５ｂと油路２６の全体積
Ｖを決定しておけば、遊星歯車機構５の噛合反力による
回転モーメント中の噛合振動は、油圧閉回路２８を構成
する油圧シリンダ２４，２５によって防振され、据付台
１１から船殻へ伝わる固体伝播振動は著しく減少し、船
室等の壁から騒音として放射されることもない。The rotational moment acting on the gear box 6 by the meshing reaction force of the planetary gear mechanism 5 is the hydraulic closed circuit 2.
8 is supported by the hydraulic cylinders 24 and 25, and the torsional vibration characteristic value F 0 determined by the spring constant kc of the hydraulic closed circuit 28 and the polar moment of inertia of the gear box 6 is the meshing reaction force of the planetary gear mechanism 5. The spring constant kc of the hydraulic closed circuit 28 is selected so that f / F 0 > 2.5 with respect to the meshing frequency f in the rotation moment due to the hydraulic cylinders 24, If the cross-sectional area S of 25 and the total volume V of the rod-side chamber 24a, the head-side chamber 25b, and the oil passage 26 are determined, the meshing vibration during the rotation moment due to the meshing reaction force of the planetary gear mechanism 5 causes the hydraulic closed circuit 28 to move. The solid-state propagating vibration transmitted from the installation base 11 to the hull is significantly reduced by the constituent hydraulic cylinders 24 and 25, and is not radiated as noise from the wall of the cabin or the like.
【００２０】一方、油圧シリンダ２４のロッド側室２４
ａからヘッド側室２４ｂへの油のリーク、並びに油圧シ
リンダ２５のヘッド側室２５ｂからロッド側室２５ａへ
の油のリークによって歯車箱６が回転変位したような場
合、該歯車箱６の回転変位はリミットスイッチ２９によ
って検出され、該リミットスイッチ２９からの検出信号
に基づき、バルブ３０が開かれてＢポートからリーク分
の油が注入されると共に、バルブ３１が開かれてＡポー
トからリーク分の油が抜かれることにより、前記歯車箱
６が水平に保持される。On the other hand, the rod side chamber 24 of the hydraulic cylinder 24
When the gear box 6 is rotationally displaced due to an oil leak from a to the head side chamber 24b and an oil leak from the head side chamber 25b of the hydraulic cylinder 25 to the rod side chamber 25a, the rotational displacement of the gear box 6 is limited by a limit switch. 29, and based on the detection signal from the limit switch 29, the valve 30 is opened to inject the leak oil from the B port, and the valve 31 is opened to remove the leak oil from the A port. As a result, the gear box 6 is held horizontally.
【００２１】こうして、据付スペースを増大させること
なく、且つ高価な継手等を用いることなく、遊星歯車機
構５の噛合部で発生する噛合振動の据付台１１側への伝
播を防止し得、騒音の発生を抑制し得る。In this way, it is possible to prevent the meshing vibration generated at the meshing portion of the planetary gear mechanism 5 from propagating to the mounting base 11 side without increasing the installation space and without using an expensive joint or the like, and to reduce noise. Occurrence can be suppressed.
【００２２】尚、本発明の遊星歯車装置の防振構造は、
上述の実施例にのみ限定されるものではなく、図１に示
すように遊星歯車９が太陽歯車８の周りを公転しない、
いわゆるスター形遊星歯車装置の代りに、遊星歯車９が
太陽歯車８の周りを公転する、いわゆるプラネタリー形
遊星歯車装置に適用してもよいこと等、その他、本発明
の要旨を逸脱しない範囲内において種々変更を加え得る
ことは勿論である。The anti-vibration structure of the planetary gear device of the present invention is as follows.
The present invention is not limited to the above embodiment, and the planet gear 9 does not revolve around the sun gear 8 as shown in FIG.
Instead of the so-called star type planetary gear device, the planetary gear 9 revolves around the sun gear 8, may be applied to a so-called planetary type planetary gear device, and the like, within the scope of the present invention. It goes without saying that various changes can be made in.
【００２３】[0023]
【発明の効果】以上、説明したように本発明の遊星歯車
装置の防振構造によれば、据付スペースを増大させるこ
となく、且つ高価な継手等を用いることなく、遊星歯車
機構の歯車の噛合部で発生する噛合振動の据付台側への
伝播を防止し得、騒音の発生を抑制し得るという優れた
効果を奏し得る。As described above, according to the vibration isolating structure of the planetary gear device of the present invention, the meshing of the gears of the planetary gear mechanism is achieved without increasing the installation space and without using an expensive joint or the like. It is possible to prevent the transmission of the meshing vibration generated in the section to the side of the mounting base and to suppress the generation of noise, which is an excellent effect.
【図１】本発明の一実施例の平断面図である。FIG. 1 is a plan sectional view of an embodiment of the present invention.
【図２】本発明の一実施例における歯車箱の回転モーメ
ントに対する支持の仕方を模式的に表わす概要正面図で
ある。FIG. 2 is a schematic front view schematically showing how to support a gear box with respect to a rotation moment in an embodiment of the present invention.
【図３】従来におけるスラスト軸受ブロックを一体とし
た遊星歯車装置の防振構造の一例を表わす概要側断面図
である。FIG. 3 is a schematic side cross-sectional view showing an example of a conventional vibration damping structure for a planetary gear device in which a thrust bearing block is integrated.
【図４】従来におけるスラスト軸受ブロックを別体とし
た遊星歯車装置の防振構造の一例を表わす概要側面図で
ある。FIG. 4 is a schematic side view showing an example of a conventional vibration damping structure for a planetary gear device in which a thrust bearing block is provided separately.
１ 駆動軸 ２ 入力軸 ３ プロペラ軸 ４ 出力軸 ５ 遊星歯車機構 ６ 歯車箱 ７ スラスト軸受 １１ 据付台 １２ スラスト軸受ブロック １９ 支持台 ２０ 支持ピース ２１ ボス部 ２２ ボス部 ２３ 支持ピース ２４ 油圧シリンダ ２４ａ ロッド側室 ２４ｂ ヘッド側室 ２５ 油圧シリンダ ２５ａ ロッド側室 ２５ｂ ヘッド側室 ２８ 油圧閉回路 1 Drive shaft 2 Input shaft 3 Propeller shaft 4 Output shaft 5 Planetary gear mechanism 6 Gear box 7 Thrust bearing 11 Installation base 12 Thrust bearing block 19 Support base 20 Support piece 21 Boss section 22 Boss section 23 Support piece 24 Hydraulic cylinder 24a Rod side chamber 24b Head side chamber 25 Hydraulic cylinder 25a Rod side chamber 25b Head side chamber 28 Hydraulic closed circuit
Claims (1)
と、プロペラ軸に接続される出力軸と、前記入力軸の回
転を出力軸に伝えるための遊星歯車機構とを備えた遊星
歯車装置の防振構造であって、前記出力軸に作用するプ
ロペラ軸からのスラスト力を受けるためのスラスト軸受
が内蔵されたスラスト軸受ブロックを据付台上に固定
し、前記遊星歯車機構を内蔵した歯車箱の入力軸側に該
入力軸と同心に突設されたボス部を、据付台上に固定し
た支持台に、所望のばね定数を有する支持ピースを介し
て回動自在に支持せしめると共に、前記歯車箱の出力軸
側に該出力軸と同心に突設されたボス部を、前記スラス
ト軸受ブロックに、所望のばね定数を有する支持ピース
を介して回動自在に支持せしめ、又、前記歯車箱の軸心
を中心として１８０゜位相のずれた位置に、据付台上に
並設された油圧シリンダを接続し、且つ該一方の油圧シ
リンダのロッド側室及びヘッド側室と、他方の油圧シリ
ンダのヘッド側室及びロッド側室とを接続して、前記遊
星歯車機構の噛合反力によって歯車箱に作用する回転モ
ーメントを支持するための油圧閉回路を構成したことを
特徴とする遊星歯車装置の防振構造。1. A planetary gear device including an input shaft connected to a drive shaft of a drive device, an output shaft connected to a propeller shaft, and a planetary gear mechanism for transmitting the rotation of the input shaft to the output shaft. A vibration-proof structure, wherein a thrust bearing block having a built-in thrust bearing for receiving a thrust force from a propeller shaft acting on the output shaft is fixed on a mounting table, and a gear box having the planetary gear mechanism built-in A boss portion projecting concentrically with the input shaft on the side of the input shaft is rotatably supported by a support base fixed on a mounting base via a support piece having a desired spring constant, and the gear A boss portion, which is provided concentrically with the output shaft on the output shaft side of the box, is rotatably supported by the thrust bearing block via a support piece having a desired spring constant. 180 ° around the axis Connect the hydraulic cylinders arranged side by side on the installation base at the positions out of phase, and connect the rod side chamber and the head side chamber of the one hydraulic cylinder to the head side chamber and the rod side chamber of the other hydraulic cylinder. A vibration isolation structure for a planetary gear device, comprising a hydraulic closed circuit for supporting a rotational moment acting on a gear box by a meshing reaction force of the planetary gear mechanism.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19440293A JPH0742797A (en) | 1993-08-05 | 1993-08-05 | Vibrationproof structure of planetary gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19440293A JPH0742797A (en) | 1993-08-05 | 1993-08-05 | Vibrationproof structure of planetary gear |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0742797A true JPH0742797A (en) | 1995-02-10 |
Family
ID=16324010
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP19440293A Pending JPH0742797A (en) | 1993-08-05 | 1993-08-05 | Vibrationproof structure of planetary gear |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0742797A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1997030300A1 (en) * | 1996-02-12 | 1997-08-21 | Zf Friedrichshafen Ag | PlANETARY GEARBOX WITH HELICAL TEETH |
| JP2010540870A (en) * | 2007-10-01 | 2010-12-24 | オルビタル２ リミテッド | Transmission system for power generation |
| CN112865415A (en) * | 2021-01-12 | 2021-05-28 | 苏州川力塑业有限公司 | Control driving method adopting servo motor and three-stage gearbox |
-
1993
- 1993-08-05 JP JP19440293A patent/JPH0742797A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1997030300A1 (en) * | 1996-02-12 | 1997-08-21 | Zf Friedrichshafen Ag | PlANETARY GEARBOX WITH HELICAL TEETH |
| JP2010540870A (en) * | 2007-10-01 | 2010-12-24 | オルビタル２ リミテッド | Transmission system for power generation |
| CN112865415A (en) * | 2021-01-12 | 2021-05-28 | 苏州川力塑业有限公司 | Control driving method adopting servo motor and three-stage gearbox |
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