JP4533658B2

JP4533658B2 - Bearing structure and multi-system turbine system

Info

Publication number: JP4533658B2
Application number: JP2004141750A
Authority: JP
Inventors: 悟史杉下; 芳弘市来
Original assignee: Mitsubishi Heavy Industries Ltd
Current assignee: Mitsubishi Heavy Industries Ltd
Priority date: 2004-05-12
Filing date: 2004-05-12
Publication date: 2010-09-01
Anticipated expiration: 2024-05-12
Also published as: JP2005325847A

Description

本発明は、軸受構造、及び、複数系統タービンシステムに関し、特に、舶用蒸気タービン系の減速機車室に構成される軸受構造、及び、複数系統タービンシステムに関する。 The present invention relates to a bearing structure and a multi-system turbine system, and more particularly, to a bearing structure and a multi-system turbine system configured in a reducer casing of a marine steam turbine system.

蒸気タービン、ガスタービンのようなタービンの出力は、トルク調整のために減速機を介して取り出される。その出力は、舶用では船尾側の回転翼（プロペラ）に伝達される。減速機は、小径歯車の動力を大径歯車に伝達することによりトルクを増大させる。歯車どうしの噛合いは高精度に調整される。その噛合いの調整が不十分であることは、動力伝達系の全体に振動を誘起する原因になる。振動は、機械系の全体の機械的劣化を招く。 The output of a turbine such as a steam turbine or a gas turbine is taken out via a speed reducer for torque adjustment. The output is transmitted to the rotor blade (propeller) on the stern side for marine use. The reduction gear increases torque by transmitting the power of the small-diameter gear to the large-diameter gear. The meshing between the gears is adjusted with high accuracy. Insufficient adjustment of the meshing causes vibrations in the entire power transmission system. The vibration causes mechanical deterioration of the entire mechanical system.

軸受構造は、半割りの２つの半環が組立てられて形成される軸受環構造とその軸受環構造を支持する支持構造とから構成されている。軸受環構造と支持構造は、組付け面で互いに接合している。大質量の軸受構造の剛性を高めるためにボルトにより軸受環構造と支持構造を結合する際に、その組付け面に歪みが生じて、結果的に歯車の噛合い精度の劣化を招く。噛合い精度の劣化を抑制するために、接合部位の材料としてホワイトメタルのような柔軟な金属が用いられ（参考：特許文献１）、又は、締付け力の局所的集中を緩和するために、接合介在体として、柔軟材料の楔形状のライナが用いられる（参考：特許文献２）。 The bearing structure is composed of a bearing ring structure formed by assembling two half halves and a support structure for supporting the bearing ring structure. The bearing ring structure and the support structure are joined to each other at the assembly surface. When the bearing ring structure and the support structure are coupled with bolts in order to increase the rigidity of the large-mass bearing structure, the assembly surface is distorted, resulting in deterioration of the gear meshing accuracy. In order to suppress the deterioration of the meshing accuracy, a flexible metal such as white metal is used as the material of the joining part (Reference: Patent Document 1), or in order to reduce local concentration of the tightening force. As the interposition, a wedge-shaped liner made of a flexible material is used (reference: Patent Document 2).

締付け後の組付けが最善であることは稀であるので、試行錯誤的な複数回の組付け作業が熟練者に強いられる。公知の技術の組付けでは、タービンの動力伝達系で軸受構造の軸心線位置を簡素に思惑通りに調整することは困難である。 Since it is rare that the assembly after tightening is the best, the skilled worker is forced to perform multiple trial and error assembly operations. In the assembly of the known technology, it is difficult to simply and arbitrarily adjust the position of the shaft center line of the bearing structure in the power transmission system of the turbine.

軸受構造の軸心線位置を思惑通りに調整する技術の確立が望まれる。特に、その軸心線位置の多次元的な調整が求められる。 Establishment of a technique for adjusting the position of the shaft center line of the bearing structure as desired is desired. In particular, multidimensional adjustment of the axial center line position is required.

特開平８−２８５８１号JP-A-8-28581 特開平８−２８５４４号JP-A-8-28544

本発明の課題は、軸受構造の軸心線位置を思惑通りに調整する軸受構造、及び、複数系統タービンシステムを提供することにある。
本発明の他の課題は、軸受構造の軸心線位置を思惑通りに調整することができ、且つ、その軸心線位置を多次元的に調整することができる軸受構造、及び、複数系統タービンシステムを提供することにある。
本発明の更に他の課題は、そのような調整作業が簡素である軸受構造、及び、複数系統タービンシステムを提供することにある。 The subject of this invention is providing the bearing structure which adjusts the axial center line position of a bearing structure as expected, and a multi-system turbine system.
Another object of the present invention is to provide a bearing structure capable of adjusting the axial center line position of the bearing structure as desired, and capable of adjusting the axial center line position in a multidimensional manner, and a multi-system turbine. To provide a system.
Still another object of the present invention is to provide a bearing structure and a multi-system turbine system in which such adjustment work is simple.

本発明による軸受構造は、本体台（１８）と、本体台（１８）に支持される軸受（２２）と、本体台（１８）と軸受（２２）との間に介設される軸心調整介在体とから構成されている。軸心調整介在体は、第１調整体（２６−Ｖ）と、第２調整体（２６−Ｈ）とから形成されている。第１調整体（２６−Ｖ）は、第１調整体（２６−Ｖ）の第１ベクトル移動により軸受（２２）を本体台（１８）に対して第１方向に移動させる第１テーパ面（２７）を有している。第１テーパ面（２７）は第１調整体（２６−Ｖ）と軸受（２２）との間の接合面である。第２調整体（２６−Ｈ）は、第２調整体（２６−Ｈ）の第２ベクトル移動により軸受（２２）を本体台（１８）に対して第２方向に移動させる第２テーパ面（２８）を有している。前記第２テーパ面は前記第２調整体（２６−Ｈ）と前記軸受との間の接合面である。ここで、軸受（２２）は、軸受全体の一部分であることが有効である。第１ベクトル移動のベクトルの方向は、第１方向、第２方向に一致する必要はない。 The bearing structure according to the present invention includes a main body base (18), a bearing (22) supported by the main body base (18), and an axis adjustment that is interposed between the main body base (18) and the bearing (22). It consists of an intervening body. The shaft center adjustment intermediate body is formed of a first adjustment body (26-V) and a second adjustment body (26-H). The first adjustment body (26-V) has a first tapered surface (moving the bearing (22) in the first direction with respect to the main body base (18) by the first vector movement of the first adjustment body (26-V)). 27). The first taper surface (27) is a joint surface between the first adjustment body (26-V) and the bearing (22). The second adjustment body (26-H) has a second tapered surface (26) that moves the bearing (22) in the second direction relative to the main body base (18) by the second vector movement of the second adjustment body (26-H). 28). The second tapered surface is a joint surface between the second adjusting body (26-H) and the bearing. Here, it is effective that the bearing (22) is a part of the entire bearing. The vector direction of the first vector movement need not coincide with the first direction and the second direction.

軸受（２２）は、第１ベクトル移動と第２ベクトル移動とにより移動自在にその位置が本体台（１８）に対して相対的に２次元面内で調整される。軸受（２２）に支持される歯車の歯当たりの調整加工をしないで、それの最適の歯当たり位置にその歯車を簡素に位置づけることができる。このような歯当たり調整加工が不要であるので、設計通りに歯切りされている歯車をそのままに用いることができる。テーパ面接合は、軸受（２２）と台本体（１８）の支持構造を強固にし、且つ、それらの相対的位置を不変に維持する物理的且つ幾何学的特性を有し、更に、軸受（２２）と台本体（１８）の微小な相対的移動を容易にしている。第１方向と第２方向は当然に平行ではない。第２方向が第１方向に直交することは、位置調整の際に要求される４方向（正負の２方向）から１方向を選択するための判断を容易にする。第１方向と第２方向は、正確に直交する必要はないが、軸受（２２）の軸心線に概ね直交していることが有効である。 The position of the bearing (22) is adjusted in a two-dimensional plane relative to the main body (18) so as to be movable by the first vector movement and the second vector movement. Without adjusting the tooth contact of the gear supported by the bearing (22), the gear can be simply positioned at the optimum tooth contact position. Since such a tooth contact adjusting process is unnecessary, a gear that has been cut as designed can be used as it is. The tapered surface joint has physical and geometric characteristics that strengthen the support structure of the bearing (22) and the base body (18) and maintain their relative positions unchanged. ) And the base body (18) are easily moved relative to each other. Naturally, the first direction and the second direction are not parallel. The fact that the second direction is orthogonal to the first direction facilitates the determination for selecting one direction from the four directions (two positive and negative directions) required for position adjustment. The first direction and the second direction do not need to be exactly orthogonal, but it is effective that the first direction and the second direction are substantially orthogonal to the axial center line of the bearing (22).

本体台（１８）は、鉛直方向部位（１８−２）と、水平方向部位（１８−３）と、鉛直方向部位（１８−２）を水平方向部位（１８−３）に結合する斜め方向部位（１８−１）とから形成されている。第１調整体（２６−Ｖ）は鉛直方向部位（１８−２）と軸受（２２）との間に介設され、且つ、第２調整体（２６−Ｈ）は水平方向部位（１８−３）と軸受（２２）との間に介設されている。このような傾斜関係の存在は、複数の軸受構造（３，６）が斜面特に４５゜斜面上に配置されることに起因している。このために、重力に逆らう歯車の据付けが困難になっている。本発明では、このような困難を容易に解消することができる。軸受（２２）がタービンの出力軸を支持している実施の形態は、本発明の顕著に好適である適用例である。 The main body (18) includes a vertical part (18-2), a horizontal part (18-3), and an oblique part that connects the vertical part (18-2) to the horizontal part (18-3). (18-1). The first adjuster (26-V) is interposed between the vertical part (18-2) and the bearing (22), and the second adjuster (26-H) is a horizontal part (18-3). ) And the bearing (22). The existence of such an inclination relationship results from the fact that a plurality of bearing structures (3, 6) are arranged on a slope, particularly a 45 ° slope. This makes it difficult to install gears against gravity. In the present invention, such difficulties can be easily solved. The embodiment in which the bearing (22) supports the output shaft of the turbine is a remarkably preferred application of the present invention.

軸受（２２）に同体に結合する第１軸心調整治具本体（４９）と、第１軸心調整治具本体（４９）に螺合する第１螺子（５３）と、第１螺子（５３）を第１軸心調整治具本体（４９）に固定する第１ロック機構（５４）との追加が好ましい。第１螺子（５３）の先頭部位は、第１調整体（２６−Ｖ又は２６−Ｈ）に回転可能に結合し、第１調整体（２６−Ｖ）の第１ベクトル移動は第１螺子（５３）の螺軸線方向移動に対応している。軸受（２２）に同体に結合する第２軸心調整治具本体（４９に等価）と、第２軸心調整治具本体に螺合する第２螺子（５３に等価）と、第２螺子を第２軸心調整治具本体に固定する第２ロック機構（５４に等価）との追加は当然に好ましい。２次元的なロック（面内固着）が可能である。第２螺子の先頭部位は、第２調整体（２６−Ｈ）に回転可能に結合し、第２調整体（２６−Ｈ）の第２ベクトル移動は第２螺子の螺軸線方向移動に対応している。 A first axis adjusting jig main body (49) coupled to the bearing (22) in the same body, a first screw (53) screwed into the first axis adjusting jig main body (49), and a first screw (53 ) Is preferably added to the first lock mechanism (54) that fixes the first axis adjusting jig body (49). The leading portion of the first screw (53) is rotatably coupled to the first adjustment body (26-V or 26-H), and the first vector movement of the first adjustment body (26-V) is the first screw ( 53) corresponding to the movement in the screw axis direction. A second axis adjusting jig main body (equivalent to 49) coupled to the bearing (22) in the same body, a second screw (equivalent to 53) screwed to the second axis adjusting jig main body, and a second screw Naturally, it is preferable to add a second lock mechanism (equivalent to 54) for fixing to the second axis adjusting jig body. Two-dimensional locking (in-plane fixation) is possible. The leading portion of the second screw is rotatably coupled to the second adjustment body (26-H), and the second vector movement of the second adjustment body (26-H) corresponds to the movement of the second screw in the screw axis direction. ing.

本発明による複合系統タービンシステムは、高圧タービン（１）と、高圧タービン（１）の高圧側出力軸に結合する高圧側小径歯車（４）と、高圧側小径歯車（４）に噛み合う高圧側大径歯車（５）と、高圧側大径歯車（５）を支持する高圧側軸受構造（６）と、低圧タービン（２）と、低圧タービン（２）の低圧側出力軸に結合する低圧側小径歯車（９）と、低圧側小径歯車（９）に噛み合う低圧側大径歯車（１１）と、低圧側大径歯車（１１）を支持する低圧側軸受構造（８）とから構成されている。このような複数系統タービンシステムに用いられる軸受構造として、本発明の既述の軸受構造が最適性に利用され得る。共通出力軸が舶用プロペラに結合することは、その複合タービンシステムの利用形態を最適性に有効化する。このような利用形態では、高圧側本体台と低圧側本体台は船体に支持されてることになる。 The combined turbine system according to the present invention includes a high pressure turbine (1), a high pressure side small diameter gear (4) coupled to a high pressure side output shaft of the high pressure turbine (1), and a high pressure side large gear meshing with the high pressure side small diameter gear (4). The low pressure side small diameter coupled to the low pressure side output shaft of the low pressure turbine (2), the high pressure side bearing structure (6) supporting the radial gear (5), the high pressure side large diameter gear (5), the low pressure turbine (2). It comprises a gear (9), a low pressure side large diameter gear (11) meshing with the low pressure side small diameter gear (9), and a low pressure side bearing structure (8) that supports the low pressure side large diameter gear (11). As the bearing structure used in such a multi-system turbine system, the above-described bearing structure of the present invention can be used for optimality. The coupling of the common output shaft to the marine propeller enables the utilization of the combined turbine system to be optimal. In such a utilization form, the high-pressure side main body stand and the low-pressure side main body stand are supported by the hull.

船体用複合タービンシステムでは、高圧側小径歯車を支持する他の高圧側軸受構造と、低圧側小径歯車を支持する他の低圧側軸受構造とが存在し、他の高圧側軸受構造は、他の高圧側本体台と、他の高圧側軸受とを形成し、他の低圧側軸受構造は、他の低圧側本体台と、他の低圧側軸受とを形成し、他の高圧側軸受の軸心線は高圧側軸受の軸心線より低位に位置し、他の低圧側軸受の軸心線は低圧側軸受の軸心線より低位に位置している。このような斜め配置による重力起因の歪みに対抗して、歯車の据え付けが適正に簡素に実行され得る。他の高圧側本体台は高圧側本体台に同体に結合し、且つ、他の低圧側本体台は低圧側本体台に同体に結合していることが機械構造的に有効である。 In a composite turbine system for a hull, there are other high-pressure side bearing structures that support high-pressure side small-diameter gears and other low-pressure side bearing structures that support low-pressure side small-diameter gears. Forms a high-pressure side main base and other high-pressure side bearings, and other low-pressure side bearing structures form other low-pressure side main bases and other low-pressure side bearings. The wire is positioned lower than the shaft center line of the high pressure side bearing, and the shaft center wires of the other low pressure side bearings are positioned lower than the shaft center line of the low pressure side bearing. The gear installation can be performed appropriately and simply against the distortion caused by gravity due to such an oblique arrangement. It is effective in terms of the mechanical structure that the other high-pressure side main body is coupled to the high-pressure side main body and the other low-pressure side main body is coupled to the low-pressure side main body.

本発明による軸受構造、及び、複数系統タービンシステムは、軸受構造の軸心線位置を思惑通りに調整することができる。その軸心線位置を多次元的に調整することができる。そのような調整作業が簡素である。斜め配置の複合軸受に支持される歯車の歯切り調整が不要化され、設計通りに製作される歯車をそのままに用いることができる。 The bearing structure and multi-system turbine system according to the present invention can adjust the axial center line position of the bearing structure as desired. The axial center line position can be adjusted multidimensionally. Such adjustment work is simple. It is unnecessary to adjust the gears supported by the diagonally-arranged compound bearing, and the gears manufactured as designed can be used as they are.

本発明による軸受構造の実施の最良の形態は、図に対応して、詳細に記述される。図１は、舶用タービンの減速用動力伝達系の動力伝達系統配置を省略的に示している。タービンは、高圧タービン１と低圧タービン２との複合系として構成されている。両タービン１，２は、それぞれに、多段型動翼列を形成している。高圧タービン１の出力軸は、高圧側第１軸受３に支持されて高圧側減速用第１小径歯車（ピニオン）４に結合している。高圧側減速用第１小径歯車４は、高圧側減速用大径歯車５に噛み合っている。高圧側減速用大径歯車５の出力軸は、高圧側第２軸受６に支持されている。高圧側減速用第１小径歯車４と高圧側減速用大径歯車５は、互いに逆向きに軸心線に対して斜めに向く逆方向螺旋溝が形成されている複合歯溝７をそれぞれに有している。高圧側減速用第１小径歯車４と高圧側減速用大径歯車５の間の減速比は、適正に規定されている。 The best mode for carrying out the bearing structure according to the present invention will be described in detail with reference to the drawings. FIG. 1 omits a power transmission system arrangement of a power transmission system for deceleration of a marine turbine. The turbine is configured as a composite system of a high-pressure turbine 1 and a low-pressure turbine 2. Both turbines 1 and 2 form a multistage moving blade row. The output shaft of the high-pressure turbine 1 is supported by the high-pressure side first bearing 3 and coupled to the high-pressure side reduction first small-diameter gear (pinion) 4. The high pressure side reduction first small diameter gear 4 meshes with the high pressure side reduction large diameter gear 5. The output shaft of the high-pressure side reduction large-diameter gear 5 is supported by the high-pressure side second bearing 6. The high-pressure side reduction first small-diameter gear 4 and the high-pressure side reduction large-diameter gear 5 each have a composite tooth groove 7 in which reverse spiral grooves are formed in opposite directions and obliquely directed to the axis. is doing. The reduction ratio between the high pressure side reduction first small diameter gear 4 and the high pressure side reduction large diameter gear 5 is properly defined.

低圧タービン２の出力軸は、低圧側第１軸受８に支持されて低圧側減速用第１小径歯車９に結合している。低圧側減速用第１小径歯車（図に現れず）９は、低圧側減速用大径歯車１１に噛み合っている。低圧側減速用大径歯車１１の出力軸は、低圧側第２軸受１２に支持されている。低圧側減速用第１小径歯車９と低圧側減速用大径歯車１１は、互いに逆向きに軸心線に対して斜めに向く複合歯溝７をそれぞれに有している。高圧側減速用第１小径歯車４の回転軸心線Ｌ１は、高圧側減速用大径歯車５の回転軸心線Ｌ２より重力方向に低位に位置づけられている。低圧側減速用第１小径歯車９の回転軸心線Ｌ３は、低圧側減速用大径歯車１１の回転軸心線Ｌ４より重力方向に低位に位置づけられている。低圧側減速用第１小径歯車９と低圧側減速用大径歯車１１の間の減速比は、適正に規定されている。 The output shaft of the low-pressure turbine 2 is supported by the low-pressure side first bearing 8 and is coupled to the low-pressure side reduction first small-diameter gear 9. A low-pressure-side reduction first small-diameter gear (not shown) 9 is engaged with a low-pressure-side reduction large-diameter gear 11. The output shaft of the low-pressure side reduction large-diameter gear 11 is supported by the low-pressure side second bearing 12. The low-pressure side reduction first small-diameter gear 9 and the low-pressure side reduction large-diameter gear 11 respectively have composite tooth grooves 7 that are opposite to each other and are inclined with respect to the axis. The rotation axis L1 of the high-pressure side reduction first small-diameter gear 4 is positioned lower in the direction of gravity than the rotation axis L2 of the high-pressure side reduction large-diameter gear 5. The rotation axis L3 of the low-pressure-side reduction first small-diameter gear 9 is positioned lower in the direction of gravity than the rotation axis L4 of the low-pressure-side reduction large-diameter gear 11. The reduction ratio between the first small-diameter gear 9 for low-pressure side reduction and the large-diameter gear 11 for low-pressure side reduction is properly defined.

高圧側減速用大径歯車５の出力軸は、高圧側減速用第２小径歯車１３に結合している。低圧側減速用大径歯車１１の出力軸は、低圧側減速用第２小径歯車１４に結合している。高圧側減速用第２小径歯車１３と低圧側減速用第２小径歯車１４は、共通最終段減速用大径歯車１５に噛み合っている。高圧側減速用第２小径歯車１３と低圧側減速用第２小径歯車１４とは、互いに逆向きに軸心線に対して斜めに向く複合歯溝７をそれぞれに有している。高圧側減速用第２小径歯車１３と共通最終段減速用大径歯車１５の間の減速比は、適正に規定されている。低圧側減速用第２小径歯車１４と共通最終段減速用大径歯車１５の間の減速比は、適正に規定されている。図には、高圧側減速用大径歯車５に位置的に対応し高圧側減速用第１小径歯車４に噛み合うもう１つの高圧側減速用大径歯車と、高圧側減速用大径歯車５に結合されている高圧側減速用第２小径歯車１３と、低圧側減速用第１小径歯車９に位置的に対応し低圧側減速用大径歯車１１に噛み合うもう１つの低圧側減速用大径歯車と、低圧側減速用大径歯車１１に結合されている低圧側減速用第２小径歯車１４とが省略されている。 The output shaft of the high-pressure side reduction large-diameter gear 5 is coupled to the high-pressure side reduction second small-diameter gear 13. The output shaft of the low-pressure side reduction large-diameter gear 11 is coupled to the low-pressure side reduction second small-diameter gear 14. The high pressure side reduction second small diameter gear 13 and the low pressure side reduction second small diameter gear 14 mesh with the common final stage reduction large diameter gear 15. The high-pressure-side reduction second small-diameter gear 13 and the low-pressure-side reduction second small-diameter gear 14 respectively have composite tooth grooves 7 that are opposite to each other and are inclined obliquely with respect to the axis. The reduction ratio between the high-pressure side reduction second small-diameter gear 13 and the common final-stage reduction large-diameter gear 15 is properly defined. The reduction ratio between the low-pressure side reduction second small-diameter gear 14 and the common final-stage reduction large-diameter gear 15 is properly defined. The figure shows another high-pressure side reduction large-diameter gear that corresponds to the high-pressure-side reduction large-diameter gear 5 and meshes with the high-pressure-side reduction first small-diameter gear 4, and the high-pressure side reduction large-diameter gear 5. Another high-pressure side reduction second small-diameter gear 13 and another low-pressure-side reduction large-diameter gear that meshes with the low-pressure-side reduction large-diameter gear 11 corresponding to the low-pressure-side reduction first small-diameter gear 9. In addition, the low pressure side reduction second small diameter gear 14 coupled to the low pressure side reduction large diameter gear 11 is omitted.

図２は、機械的共通座標系の中の高圧側第１軸受３と高圧側第２軸受６と低圧側第１軸受８と低圧側第２軸受１２の複合軸受構造の詳細を示している（図２の左右は図１の左右に対して反対である。）。その複合軸受構造は、高圧側複合軸受構造１６と低圧側複合軸受構造１７とから構成されている。高圧側複合軸受構造１６は高圧側第１軸受３と高圧側第２軸受６の複合構造を有し、低圧側複合軸受構造１７は低圧側第１軸受８と低圧側第２軸受１２の複合構造を有している。 FIG. 2 shows details of a combined bearing structure of the high-pressure side first bearing 3, the high-pressure side second bearing 6, the low-pressure side first bearing 8, and the low-pressure side second bearing 12 in the mechanical common coordinate system ( 2 is opposite to the left and right in FIG. The composite bearing structure includes a high-pressure side composite bearing structure 16 and a low-pressure side composite bearing structure 17. The high pressure side composite bearing structure 16 has a composite structure of the high pressure side first bearing 3 and the high pressure side second bearing 6, and the low pressure side composite bearing structure 17 has a composite structure of the low pressure side first bearing 8 and the low pressure side second bearing 12. have.

高圧側複合軸受構造１６と低圧側複合軸受構造１７は、船体に同定され機械的座標系が固定されている共通本体を共有している。その共通本体（船体又は船体に同体）は、大径歯車側共通軸受支持体１８と小径歯車側共通軸受支持体１９とから形成されている。大径歯車側共通軸受支持体１８と小径歯車側共通軸受支持体１９は、溶接のような結合手段により同体化されている。大径歯車側共通軸受支持体１８と小径歯車側共通軸受支持体１９を一体的に構造化する手段である溶接に代えて、大径歯車側共通軸受支持体１８と小径歯車側共通軸受支持体１９を同一金属体化することは有効である。高圧側第２軸受６は、大径歯車側共通軸受支持体１８と大径歯車側軸受２１から形成されている。大径歯車側軸受２１は、半環状の大径歯車側一方側部位２２と半環状の大径歯車側他方側部位２３とから形成されている。大径歯車側他方側部位２３は、両側でそれぞれに軸方向に並ぶ多数のボルト２４により強固に大径歯車側一方側部位２２に取付け面（接合面）２５で面接合している。 The high-pressure side composite bearing structure 16 and the low-pressure side composite bearing structure 17 share a common body that is identified in the hull and has a mechanical coordinate system fixed thereto. The common main body (the same as the hull or the hull) is formed of a large-diameter gear-side common bearing support 18 and a small-diameter gear-side common bearing support 19. The large-diameter gear side common bearing support 18 and the small-diameter gear side common bearing support 19 are integrated together by a coupling means such as welding. Instead of welding which is a means for integrally structuring the large-diameter gear side common bearing support 18 and the small-diameter gear side common bearing support 19, the large-diameter gear side common bearing support 18 and the small-diameter gear side common bearing support 18 It is effective to make 19 the same metal body. The high-pressure side second bearing 6 is formed of a large-diameter gear-side common bearing support 18 and a large-diameter gear-side bearing 21. The large-diameter gear-side bearing 21 is formed of a semi-annular large-diameter gear side one side portion 22 and a semi-annular large-diameter gear side other side portion 23. The large-diameter gear side other side part 23 is firmly joined to the large-diameter gear side one side part 22 by a mounting surface (joint surface) 25 by a large number of bolts 24 arranged in the axial direction on both sides.

大径歯車側共通軸受支持体１８は、高圧側と低圧側で共通に、４５度斜面部位１８−１と４５度斜面部位１８−１の上下側部位でそれぞれに一体に連続する鉛直面部位１８−２と水平面部位１８−３とから形成されている。鉛直面部位１８−２と大径歯車側一方側部位２２の間に形成されている隙間の一部は、高圧側鉛直向き楔プレート２６−Ｖで埋められている。高圧側鉛直向き楔プレート２６−Ｖは、鉛直面部位１８−２と大径歯車側一方側部位２２の高位部分との間に楔として介設されていて、テーパ面２７を有している。テーパ面２７は大径歯車側一方側部位２２の側に形成されているテーパ面に面接合している。水平面部位１８−３と大径歯車側一方側部位２２の間に形成されている隙間の一部は、高圧側水平向き楔プレート２６−Ｈで埋められている。高圧側水平向き楔プレート２６−Ｈは、水平面部位１８−３と大径歯車側一方側部位２２の低位部分との間に楔として介設されていて、テーパ面２８を有している。テーパ面２８は大径歯車側一方側部位２２の側に形成されているテーパ面に面接合している。 The large-diameter gear side common bearing support 18 has a vertical surface portion 18 that is integrally connected to the upper and lower sides of the 45 ° slope portion 18-1 and the 45 ° slope portion 18-1 in common on the high pressure side and the low pressure side. -2 and a horizontal surface portion 18-3. A part of the gap formed between the vertical surface portion 18-2 and the one side portion 22 on the large-diameter gear side is filled with a high-pressure-side vertical-direction wedge plate 26-V. The high-pressure side vertically oriented wedge plate 26 -V is interposed as a wedge between the vertical surface portion 18-2 and the high-order portion of the large-diameter gear side one side portion 22, and has a tapered surface 27. The taper surface 27 is surface-bonded to a taper surface formed on the large-diameter gear side one side portion 22 side. A part of the gap formed between the horizontal plane part 18-3 and the large gear side one side part 22 is filled with a high-pressure side horizontal wedge plate 26-H. The high-pressure side horizontal wedge plate 26 -H is interposed as a wedge between the horizontal surface portion 18-3 and the lower portion of the large-diameter gear side one side portion 22, and has a tapered surface 28. The taper surface 28 is surface-bonded to a taper surface formed on the large-diameter gear side one side portion 22 side.

低圧側第２軸受１２は、大径歯車側共通軸受支持体１８と大径歯車側軸受２９から形成されている。大径歯車側軸受２９は、半環状の大径歯車側一方側部位３１と半環状の大径歯車側他方側部位３２とから形成されている。大径歯車側他方側部位３２は、両側でそれぞれに軸方向に並ぶ多数のボルト３３により強固に大径歯車側一方側部位３１に取付け面（接合面）３４で面接合している。鉛直面部位１８−２と大径歯車側一方側部位３１の間に形成されている隙間の一部は、低圧側鉛直向き楔プレート３５−Ｖで埋められている。低圧側鉛直向き楔プレート３５−Ｖは、鉛直面部位１８−２と大径歯車側一方側部位３１の高位部分との間に楔として介設されていて、テーパ面３６を有している。テーパ面３６は大径歯車側一方側部位３１の側に形成されているテーパ面に面接合している。水平面部位１８−３と大径歯車側一方側部位３１の間に形成されている隙間の一部は、低圧側水平向き楔プレート３５−Ｈで埋められている。低圧側水平向き楔プレート３５−Ｈは、水平面部位１８−３と大径歯車側一方側部位３１の低位部分との間に楔として介設されていて、テーパ面３７を有している。テーパ面３７は大径歯車側一方側部位３１の側に形成されているテーパ面に面接合している。 The low pressure side second bearing 12 is formed of a large diameter gear side common bearing support 18 and a large diameter gear side bearing 29. The large-diameter gear side bearing 29 is formed of a semi-annular large-diameter gear side one side portion 31 and a semi-annular large-diameter gear side other side portion 32. The large-diameter gear side other side portion 32 is firmly joined to the large-diameter gear side one side portion 31 by a mounting surface (joint surface) 34 by a large number of bolts 33 arranged in the axial direction on both sides. A part of the gap formed between the vertical surface part 18-2 and the one side part 31 on the large-diameter gear side is filled with the wedge plate 35-V facing the low pressure side vertically. The low-pressure-side vertically oriented wedge plate 35 -V is interposed as a wedge between the vertical surface portion 18-2 and the high-order portion of the one-side portion 31 on the large-diameter gear side, and has a tapered surface 36. The taper surface 36 is surface-bonded to a taper surface formed on the one-side portion 31 side on the large-diameter gear side. A part of a gap formed between the horizontal plane part 18-3 and the large-diameter gear side one side part 31 is filled with a low-pressure side horizontally oriented wedge plate 35-H. The low-pressure side horizontally oriented wedge plate 35 -H is interposed as a wedge between the horizontal surface portion 18-3 and the lower portion of the large-diameter gear side one side portion 31, and has a tapered surface 37. The taper surface 37 is surface-bonded to a taper surface formed on the large-diameter gear side one side portion 31 side.

高圧側第１軸受３は、小径歯車側共通軸受支持体１９と小径歯車側軸受３８とから形成されている。小径歯車側軸受３８が半環状の２体の軸受環から形成されている点は、公知構造に同じである。低圧側第１軸受８は、小径歯車側共通軸受支持体１９と小径歯車側軸受３９とから形成されている。小径歯車側軸受３９が半環状の２体の軸受環から形成されている点は、公知構造に同じである。高圧側第１軸受３に対応する歯車の質量は大きくないので、小径歯車側共通軸受支持体１９と小径歯車側軸受３８との間には既述の楔プレートのような軸心位置調整プレートは挿入されていない。低圧側第１軸受８に対応する歯車の質量は大きくないので、小径歯車側共通軸受支持体１９と小径歯車側軸受３９との間には既述の楔プレートのような軸心位置調整プレートは挿入されていない。 The high pressure side first bearing 3 is formed of a small diameter gear side common bearing support 19 and a small diameter gear side bearing 38. The small gear side bearing 38 is formed of two semi-annular bearing rings, which is the same as the known structure. The first low-pressure side bearing 8 is formed of a small-diameter gear-side common bearing support 19 and a small-diameter gear-side bearing 39. The small gear side bearing 39 is the same as the known structure in that it is formed of two semi-annular bearing rings. Since the mass of the gear corresponding to the high-pressure side first bearing 3 is not large, an axial center position adjusting plate such as a wedge plate as described above is provided between the small-diameter gear-side common bearing support 19 and the small-diameter gear-side bearing 38. Not inserted. Since the mass of the gear corresponding to the low-pressure side first bearing 8 is not large, an axial center position adjusting plate such as a wedge plate as described above is provided between the small-diameter gear-side common bearing support 19 and the small-diameter gear-side bearing 39. Not inserted.

高圧側鉛直向き楔プレート２６−Ｖを両面側から挟み込む大径歯車側共通軸受支持体１８の挟込み部位と大径歯車側一方側部位２２の挟込み部位は、複数のボルト４１で強固に締め付けられている。高圧側水平向き楔プレート２６−Ｈを両面側から挟み込む大径歯車側共通軸受支持体１８の挟込み部位と大径歯車側一方側部位２２の挟込み部位は、複数のボルト４２で強固に締め付けられている。低圧側鉛直向き楔プレート３５−Ｖを両面側から挟み込む大径歯車側共通軸受支持体１８の挟込み部位と大径歯車側一方側部位３１の挟込み部位は、複数のボルト４３で強固に締め付けられている。低圧側水平向き楔プレート３５−Ｈを両面側から挟み込む大径歯車側共通軸受支持体１８の挟込み部位と大径歯車側一方側部位３１の挟込み部位は、複数のボルト４４で強固に締め付けられている。一体的な軸受構造を有する高圧側複合軸受構造１６は、船体に等価である台４５に支持されている。一体的な軸受構造を有する低圧側複合軸受構造１７は、船体に等価である台４６に支持されている。 The pinching portion of the large-diameter gear-side common bearing support 18 and the pinching portion of the one-side portion 22 on the large-diameter gear side that sandwich the high-pressure-side vertically oriented wedge plate 26-V from both sides are firmly tightened with a plurality of bolts 41. It has been. The sandwiching portion of the large-diameter gear side common bearing support 18 that sandwiches the high-pressure side horizontally oriented wedge plate 26-H from both sides is firmly tightened with a plurality of bolts 42. It has been. The pinching portion of the large-diameter gear-side common bearing support 18 and the pinching portion of the one-side portion 31 on the large-diameter gear side that sandwich the low-pressure-side vertically oriented wedge plate 35 -V from both sides are firmly tightened with a plurality of bolts 43. It has been. The sandwiching portion of the large-diameter gear side common bearing support 18 that sandwiches the low-pressure side horizontally oriented wedge plate 35 -H from both sides and the sandwiching portion of the large-diameter gear side one side portion 31 are firmly tightened with a plurality of bolts 44. It has been. The high-pressure side composite bearing structure 16 having an integral bearing structure is supported by a base 45 equivalent to a hull. The low-pressure side composite bearing structure 17 having an integral bearing structure is supported by a base 46 equivalent to a hull.

図３は、高圧側鉛直向き楔プレート２６−Ｖと高圧側水平向き楔プレート２６−Ｈと低圧側鉛直向き楔プレート３５−Ｖと低圧側水平向き楔プレート３５−Ｈに共通する軸心線位置調整機構を示し、特に、高圧側水平向き楔プレート２６−Ｈの軸心線位置調整機構を代表的に示している。高圧側水平向き楔プレート２６−Ｈを両面側から締め付ける大径歯車側一方側部位２２の締付け部位４７と水平面部位１８−３の締付け部位４８は、既述の通り、締付けボルト４２で締め付けられている。複数の締付けボルト４２は、軸方向に長く延びている高圧側水平向き楔プレート２６−Ｈを複数箇所で貫通することが可能である。その場合には、高圧側水平向き楔プレート２６−Ｈにはボルト４２が融通的に通る長穴５０が開けられている。長穴５０の長径方向は、回転軸心線Ｌ２（図２参照）に直交している。 FIG. 3 shows the axial center line position common to the high-pressure side vertical wedge plate 26-V, the high-pressure side horizontal wedge plate 26-H, the low-pressure side vertical wedge plate 35-V, and the low-pressure side horizontal wedge plate 35-H. An adjustment mechanism is shown, and in particular, an axial center line position adjustment mechanism of the high-pressure side horizontally oriented wedge plate 26-H is representatively shown. As described above, the tightening portion 47 of the large-diameter gear side one side portion 22 and the tightening portion 48 of the horizontal surface portion 18-3 for tightening the high-pressure side horizontally oriented wedge plate 26-H from both sides are tightened by the tightening bolts 42. Yes. The plurality of tightening bolts 42 can penetrate the high-pressure side horizontally oriented wedge plate 26-H extending in the axial direction at a plurality of locations. In that case, a long hole 50 through which the bolt 42 is accommodated is formed in the high-pressure side horizontal wedge plate 26-H. The major axis direction of the long hole 50 is orthogonal to the rotation axis L2 (see FIG. 2).

締付け部位４７の端面に、軸心位置調整本体４９が固着している。軸心位置調整本体４９は、固着螺子５１により締付け部位４７に強固に締め付けられて固着している。軸心位置調整本体４９が締付け部位４７に対向する側で軸心位置調整本体４９に空間が開けられている。その空間に、高圧側水平向き楔プレート２６−Ｈの端部として形成されている螺子嵌合部位５２が挿入されている。軸心位置調整本体４９に軸心位置調整螺子５３が螺合している。軸心位置調整螺子５３は、回転軸心線Ｌ２に直交する進退方向に進退動することができる。軸心位置調整螺子５３の先頭部位は、円板（図示されず）として形成されている。その円板は、螺子嵌合部位５２の中に形成されている円板挿入穴（図示されず）に密着的に且つ回転摺動可能に挿入されている。軸心位置調整螺子５３は、ロックナット５４によりロックされて軸心位置調整本体４９に固着される。 An axial center adjustment main body 49 is fixed to the end face of the tightening portion 47. The shaft center position adjusting body 49 is firmly fastened and fixed to the tightening portion 47 by the fixing screw 51. A space is opened in the shaft center position adjusting body 49 on the side where the shaft center position adjusting body 49 faces the tightening portion 47. A screw fitting portion 52 formed as an end portion of the high-pressure side horizontally oriented wedge plate 26-H is inserted into the space. An axial position adjusting screw 53 is screwed into the axial position adjusting main body 49. The axial center position adjusting screw 53 can move back and forth in the forward / backward direction orthogonal to the rotational axis L2. The head part of the axial center position adjusting screw 53 is formed as a disk (not shown). The disc is inserted in a disc insertion hole (not shown) formed in the screw fitting portion 52 in a close contact and slidable manner. The shaft center position adjusting screw 53 is locked by a lock nut 54 and fixed to the shaft center position adjusting body 49.

軸心位置調整螺子５３を回転させることにより、軸心位置調整螺子５３を進退動させる。軸心位置調整螺子５３の進退動は、高圧側水平向き楔プレート２６−Ｈの進退動に位置的に１対１に対応する。高圧側鉛直向き楔プレート２６−Ｖを同様に進退動させる。高圧側鉛直向き楔プレート２６−Ｖの進退動方向は、高圧側水平向き楔プレート２６−Ｈの進退動方向に直交している。高圧側鉛直向き楔プレート２６−Ｖと高圧側水平向き楔プレート２６−Ｈの進退動は、高圧側減速用第１小径歯車４の歯溝７と高圧側減速用大径歯車５の歯溝７の噛合いに影響する。高圧側鉛直向き楔プレート２６−Ｖの前進と後退は、高圧側減速用第１小径歯車４の歯溝７と高圧側減速用大径歯車５の歯溝７の噛合いをより適正にする適正調整方向とその噛合いをより不適正にする不適正調整方向の判断に有効である。高圧側水平向き楔プレート２６−Ｈの前進と後退は、高圧側減速用第１小径歯車４の歯溝７と高圧側減速用大径歯車５の歯溝７の噛合いをより適正にする適正調整方向とその噛合いをより不適正にする不適正調整方向の判断に有効である。高圧側水平向き楔プレート２６−Ｈの前進と後退と高圧側鉛直向き楔プレート２６−Ｖの前進と後退の４通りの組合せにより、最適調整方向が容易に判断される。最適調整方向の判断により、高圧側鉛直向き楔プレート２６−Ｖと高圧側水平向き楔プレート２６−Ｈの進退動位置が確定され、その確定位置の軸心位置調整螺子５３はロックナット５４によりロックされる。 By rotating the shaft center position adjusting screw 53, the shaft center position adjusting screw 53 is moved forward and backward. The forward / backward movement of the axial center position adjusting screw 53 corresponds to the forward / backward movement of the high-pressure side horizontally oriented wedge plate 26-H in a one-to-one correspondence. The high-pressure side vertically oriented wedge plate 26-V is similarly moved forward and backward. The advancing / retreating direction of the high-pressure side vertically oriented wedge plate 26-V is orthogonal to the advancing / retreating direction of the high-pressure side horizontally oriented wedge plate 26-H. The forward and backward movement of the high-pressure side vertical wedge plate 26-V and the high-pressure side horizontal wedge plate 26-H is caused by the tooth groove 7 of the high-pressure side reduction first small-diameter gear 4 and the tooth groove 7 of the high-pressure side reduction large-diameter gear 5. Affects the meshing. The forward and backward movement of the high-pressure-side vertical wedge plate 26-V is appropriate to make the meshing of the tooth groove 7 of the high-pressure side reduction first small gear 4 and the tooth groove 7 of the high-pressure side reduction large-diameter gear 5 more appropriate. This is effective for determining an inappropriate adjustment direction that makes the adjustment direction and its engagement more inappropriate. The forward and backward movement of the high-pressure side horizontally oriented wedge plate 26-H is appropriate to make the meshing of the tooth groove 7 of the high-pressure side reduction first small-diameter gear 4 and the tooth groove 7 of the high-pressure side reduction large-diameter gear 5 more appropriate. This is effective for determining an inappropriate adjustment direction that makes the adjustment direction and its engagement more inappropriate. The optimum adjustment direction is easily determined by four combinations of advancement and retraction of the high-pressure side horizontal wedge plate 26-H and advancement and retraction of the high-pressure side vertical wedge plate 26-V. By determining the optimum adjustment direction, the advancing / retreating positions of the high-pressure side vertical wedge plate 26-V and the high-pressure side horizontal wedge plate 26-H are determined, and the axial position adjusting screw 53 at the determined position is locked by a lock nut 54. Is done.

図４は、２次元ＸＹ平面上で大径歯車側軸受２１を２次元的に移動させることにより回転軸心線Ｌ２の２次元位置を調整する軸心線位置調整方法を示している。大径歯車側軸受２１の位置は、高圧側鉛直向き楔プレート２６−ＶのＸ方向位置と高圧側水平向き楔プレート２６−ＨのＹ方向位置とにより決定される。大径歯車側軸受２１の２次元位置は、高圧側鉛直向き楔プレート２６−Ｖの正負Ｘ方向移動量と高圧側水平向き楔プレート２６−Ｈの正負Ｙ方向移動量の４通りの組合せにより決定される。Ｘ方向とＹ方向は平行ではない。Ｘ方向とＹ方向が直交する場合に、調整作業はより容易であり、より高い精度の位置調整が可能である。高圧側減速用第１小径歯車４の回転軸心線Ｌ１に対して高圧側減速用大径歯車５の回転軸心線Ｌ２を相対的に移動させることにより、高圧側減速用大径歯車５の軸方向前後の螺旋歯溝７を高圧側減速用第１小径歯車４の軸方向前後の螺旋歯溝７に対する噛合いを容易に調整することができる。 FIG. 4 shows an axial center position adjusting method for adjusting the two-dimensional position of the rotational axis L2 by moving the large-diameter gear side bearing 21 two-dimensionally on the two-dimensional XY plane. The position of the large-diameter gear side bearing 21 is determined by the X-direction position of the high-pressure side vertical wedge plate 26-V and the Y-direction position of the high-pressure side horizontal wedge plate 26-H. The two-dimensional position of the large gear side bearing 21 is determined by four combinations of the positive / negative X direction movement amount of the high pressure side vertical wedge plate 26-V and the positive / negative Y direction movement amount of the high pressure side horizontal wedge plate 26-H. Is done. The X direction and the Y direction are not parallel. When the X direction and the Y direction are orthogonal to each other, the adjustment work is easier and position adjustment with higher accuracy is possible. By moving the rotation axis L2 of the high pressure side reduction large diameter gear 5 relative to the rotation axis L1 of the high pressure side reduction first small diameter gear 4, the high pressure side reduction large diameter gear 5 It is possible to easily adjust the meshing of the spiral tooth grooves 7 in the axial direction with respect to the spiral tooth grooves 7 in the longitudinal direction of the first small-diameter gear 4 for high-pressure side reduction.

図５は、噛合いの適正と不適正を判別する慣用方法を示している。複合歯溝７に色付き油又はセラミック蒸着層が塗られ又は形成された高圧側減速用第１小径歯車４を複数回に回転させ、高圧側減速用大径歯車５を１回転させることにより、高圧側減速用第１小径歯車４の複合歯溝７に付着している色付き油が高圧側減速用大径歯車５の複合歯溝７に転写される。不適正調整のときの転写の模様は、（ａ），（ｂ）に示されるように、螺旋方向に短く、且つ、先鋭に途切れる。適正調整のときの転写の模様は、（ｃ），（ｄ）に示されるように、螺旋方向に長く、且つ、途切れない。このような転写模様を長くする方向に高圧側鉛直向き楔プレート２６−Ｖと高圧側水平向き楔プレート２６−Ｈを移動させることにより、試行錯誤的繰り返し調整作業をしないで、確実に適正調整方向を見出すことができる。このような調整方法は、マイクロメータのオーダの微調整を可能にしている。 FIG. 5 shows a conventional method for discriminating whether or not meshing is appropriate. By rotating the high pressure side reduction first small-diameter gear 4 in which colored oil or a ceramic vapor-deposited layer is coated or formed on the composite tooth groove 7 a plurality of times and rotating the high pressure side reduction large-diameter gear 5 once, a high pressure is achieved. The colored oil adhering to the composite tooth groove 7 of the first reduction-use side small gear 4 is transferred to the composite tooth groove 7 of the high-pressure side reduction large-diameter gear 5. The imprint adjustment pattern is short in the spiral direction and sharply interrupted, as shown in FIGS. The transfer pattern at the time of proper adjustment is long in the spiral direction and uninterrupted as shown in (c) and (d). By moving the high-voltage-side vertical wedge plate 26-V and the high-voltage-side horizontal wedge plate 26-H in the direction in which such a transfer pattern is lengthened, the proper adjustment direction is ensured without repeated trial and error adjustment work. Can be found. Such an adjustment method enables fine adjustment of the order of the micrometer.

楔プレートの位置調整による歯当たり調整の後の既述のロックナットによる相対位置固定に代えられるテーパピン固着は有効である。テーパピン固着は、固着力が強力であり位置保持が確実であることの他に、再度の調整が要求される場合に、その固着の解消を容易にすることができる。歯車の据付け精度は車室の加工精度に依存する。加工されている車室に合わせて歯車の歯切り加工が行われる。１つの車室に対応してその車室に据え付けられる歯車の加工が行われる。このため、公知技術では歯車の統一的加工が行われていないが、本発明の調整技術では、任意の車室に据え付けられる歯車は、その据え付け位置を簡素に調整することができるので、統一的に生産される多数の歯車のうちから任意に選択することができる。大径歯車側一方側部位２２と大径歯車側一方側部位３１とはともに、船体に等価である車室に対して構造的に独立しているので、歯当たりを調整することにより、歯車を最適の位置と角度位置に据え付けることができ、歯車を設計通りに製作することができ、調整加工により歯車を最良の加工状態を悪化させないで、歯車を設計通りの最良の状態で用いることができる。このような調整が可能であるので、車室と小径歯車側共通軸受支持体１９を一体化することが有効である。 It is effective to fix the taper pin instead of fixing the relative position by the lock nut described above after the tooth contact adjustment by adjusting the position of the wedge plate. The taper pin fixing not only has a strong fixing force and reliable position holding, but also makes it easy to eliminate the fixing when re-adjustment is required. The gear installation accuracy depends on the processing accuracy of the passenger compartment. Gear cutting is performed in accordance with the vehicle compartment being processed. Gears installed in the vehicle compartment are processed corresponding to one vehicle compartment. For this reason, in the known technology, the gears are not uniformly processed. However, in the adjustment technology of the present invention, the gears installed in an arbitrary passenger compartment can be simply adjusted, so that the installation position can be adjusted uniformly. It is possible to arbitrarily select from among a large number of gears to be produced. Since the large-diameter gear side one side portion 22 and the large-diameter gear side one side portion 31 are both structurally independent from the cabin equivalent to the hull, the gears can be adjusted by adjusting the tooth contact. It can be installed at the optimum position and angular position, the gear can be manufactured as designed, and the gear can be used in the best condition as designed without deteriorating the best machining state by adjustment process . Since such adjustment is possible, it is effective to integrate the casing and the small-diameter gear side common bearing support 19.

図１は、本発明による複合系統タービンシステムの実施の好ましい形態を示す斜軸投影図である。FIG. 1 is an oblique projection showing a preferred embodiment of a composite turbine system according to the present invention. 図２は、図１の斜軸方向視の背面断面図である。FIG. 2 is a rear sectional view of the oblique axis view of FIG. 図３は、図２の一部の正面断面図である。3 is a front sectional view of a part of FIG. 図４は、図２の他の一部の正面断面図である。4 is a front sectional view of another part of FIG. 図５（ａ），（ｂ），（ｃ），（ｄ）は、歯切り調整方法を示す写真である。FIGS. 5A, 5B, 5C and 5D are photographs showing a gear trimming adjustment method.

Explanation of symbols

１…高圧タービン
３…軸受構造
４…高圧側小径歯車
５…高圧側大径歯車
６…軸受構造（高圧側軸受構造）
８…低圧側軸受構造
９…低圧側小径歯車
１１…低圧側大径歯車
１８…本体台
１８−１…斜め方向部位
１８−２…鉛直方向部位
１８−３…水平方向部位
２２…軸受
２６−Ｖ…第１調整体
２６−Ｈ…第２調整体
２７…第１テーパ面
２８…第２テーパ面
４９…第１軸心調整治具本体（第２軸心調整治具本体）
５３…第１螺子（第２螺子）
５４…第１ロック機構 DESCRIPTION OF SYMBOLS 1 ... High pressure turbine 3 ... Bearing structure 4 ... High pressure side small diameter gear 5 ... High pressure side large diameter gear 6 ... Bearing structure (high pressure side bearing structure)
8 ... Low pressure side bearing structure 9 ... Low pressure side small diameter gear 11 ... Low pressure side large diameter gear 18 ... Main body base 18-1 ... Slanted direction portion 18-2 ... Vertical direction portion 18-3 ... Horizontal direction portion 22 ... Bearing 26-V ... 1st adjustment body 26-H ... 2nd adjustment body 27 ... 1st taper surface 28 ... 2nd taper surface 49 ... 1st axis adjustment jig main body (2nd axis adjustment jig main body)
53 ... 1st screw (2nd screw)
54. First locking mechanism

Claims

A main body stand,
A bearing supported by the main body base;
Comprising an axis adjustment interposition body interposed between the main body base and the bearing,
The shaft center adjustment intermediate is
A first adjustment body;
A second adjustment body,
The first adjustment body has a first taper surface that moves the bearing in a first direction relative to the main body base by movement of the first adjustment body in a first movement direction, and the first taper surface is A joint surface between the first adjusting body and the bearing;
The second adjustment body has a second taper surface that moves the bearing in a second direction relative to the main body base by movement of the second adjustment body in a second movement direction, and the second taper surface is A joint surface between the second adjustment body and the bearing;
The first direction and the second direction are not parallel,
The first movement direction and the second movement direction are both orthogonal to the axial center line of the bearing,
The main body base is
And lead facing site was stretched in the vertical direction,
Water plane portion stretched in the horizontal direction,
The vertical plane portion position and the water plane portion, and a diagonal direction site for binding together respectively the upper portion and the lower portion,
The bearing,
Comprising a clamping portion position provided on both ends that put in the direction perpendicular to the previous SL axial line,
The first adjustment is interposed between the tightening portion of the vertical plane portion and one, and the second adjusting member is interposed between the tightening portion of the water plane portion and the other The bearing structure.

The bearing structure according to claim 1, wherein the second direction is orthogonal to the first direction.

The bearing structure according to claim 1, wherein the first direction and the second direction are both orthogonal to the axial center line of the bearing.

The bearing structure according to claim 1, wherein the bearing supports an output shaft of a turbine.

A first axis adjusting jig main body coupled to the bearing in the same body;
A first screw threadably engaged with the first axis adjustment jig body;
A first lock mechanism for fixing the first screw to the first axis adjustment jig body;
A head portion of the first screw is rotatably coupled to the first adjustment body, and the first movement direction of the first adjustment body corresponds to a movement of the first screw in a screw axis direction;
A second axis adjusting jig main body coupled to the bearing in the same body;
A second screw threadably engaged with the second axis adjustment jig body;
A second lock mechanism for fixing the second screw to the second axis adjusting jig body;
The head portion of the second screw is rotatably coupled to the second adjustment body, and the second movement direction of the second adjustment body corresponds to the movement of the second screw in the screw axis direction. Bearing structure.

A high-pressure turbine,
A high pressure side small diameter gear coupled to a high pressure side output shaft of the high pressure turbine;
A high pressure side large diameter gear meshing with the high pressure side small diameter gear;
A high pressure side bearing structure for supporting the high pressure side large diameter gear;
A low pressure turbine;
A low pressure side small diameter gear coupled to a low pressure side output shaft of the low pressure turbine;
A low pressure side large diameter gear meshing with the low pressure side small diameter gear;
Comprising a low pressure side bearing structure for supporting the low pressure side large diameter gear;
The high-pressure side bearing structure is
A main body on the high pressure side,
A high-pressure side bearing supported by the high-pressure side body base;
A high-pressure side axis adjustment intervening body interposed between the high-pressure side main body base and the high-pressure side bearing,
The high-pressure side axis adjustment interposition is
A first high-pressure side adjustment body;
A second high-pressure side adjustment body,
The first high-pressure side adjusting body moves the high-pressure side bearing in the high-pressure side first direction with respect to the high-pressure side main body by moving the first high-pressure side adjusting body in the high-pressure side first moving direction. A high-pressure side taper surface, the first high-pressure side taper surface is a joint surface between the first high-pressure side adjustment body and the high-pressure side bearing;
The second high-pressure side adjusting body moves the high-pressure side bearing in the high-pressure side second direction with respect to the high-pressure side main body by moving the second high-pressure side adjusting body in the high-pressure side second moving direction. A high-pressure side taper surface, the second high-pressure side taper surface is a joint surface between the second high-pressure side adjustment body and the high-pressure side bearing;
The high pressure side first direction and the high pressure side second direction are not parallel,
Both the high-pressure side first movement direction and the high-pressure side second movement direction are perpendicular to the high-pressure side axis of the high-pressure side bearing,
The high-pressure body stand is
A high pressure side vertical plane portion stretched in the vertical direction,
A high-pressure-side water plane portion stretched in the horizontal direction,
The high-pressure side vertical plane portion position and the high-pressure-side water plane portion, and a high-pressure side oblique direction site that binds together respectively the upper portion and the lower portion,
The high-pressure side bearing,
Comprising a high-pressure-side fastening portion position provided on both ends that put in the direction perpendicular to the front Symbol pressure side axial line,
The high-pressure side first adjustment is provided between the portion clamping the high pressure side of the high-pressure side vertical plane site and one, and the second adjusting member is the high pressure side of the high-pressure-side water plane portion and the other Interposed between the tightening parts,
The low-pressure side bearing structure is
A low-pressure body stand,
A low-pressure side bearing supported by the low-pressure side body base;
A low-pressure side axis adjustment intervening body interposed between the low-pressure side body base and the low-pressure side bearing,
The low-pressure side axis adjustment intermediate is
A first low pressure side regulator;
A second low-pressure side adjustment body,
The first low-pressure side adjusting body moves the low-pressure side bearing in the low-pressure side first direction with respect to the low-pressure side main body by moving the first low-pressure side adjusting body in the low-pressure side first moving direction. A low-pressure side taper surface, the first low-pressure side taper surface is a joint surface between the first low-pressure side adjustment body and the low-pressure side bearing;
The second low-pressure side adjusting body moves the low-pressure side bearing in the low-pressure side second direction with respect to the low-pressure side main body by moving the second low-pressure side adjusting body in the low-pressure side second moving direction. A low pressure side taper surface, the second low pressure side taper surface is a joint surface between the second low pressure side adjuster and the low pressure side bearing;
The low-pressure side first direction and the low-pressure side second direction are not parallel,
Both the low-pressure side first moving direction and the low-pressure side second moving direction are perpendicular to the low-pressure side axis of the low-pressure side bearing,
The low-pressure body stand is
And the low-voltage side vertical plane portion stretched in the vertical direction,
And the low-pressure-side water plane portion stretched in the horizontal direction,
The low-pressure side vertical plane portion position and the low-pressure-side water plane portion, and a low pressure side oblique direction site that binds together respectively the upper portion and the lower portion,
The low pressure side bearing,
Comprising a low-pressure-side fastening portion position provided on both ends that put in the direction perpendicular to the front Symbol low voltage side axial line,
The low-pressure side first adjustment is provided between the portion clamping the low pressure side of the low-pressure side vertical plane site and one, and the second adjusting member is the low pressure side of the low-pressure-side water plane portion and the other Interposed between the tightening parts,
The high-pressure-side large-diameter gear and the low-pressure-side large-diameter gear are coupled to a common output shaft through a speed reduction mechanism.

The multi-system turbine system according to claim 6, wherein the common output shaft is coupled to a marine propeller.

The multi-system turbine system according to claim 7, wherein the high-pressure side main body stand and the low-pressure side main body stand are supported by a hull.

Other high-pressure side bearing structure that supports the high-pressure side small-diameter gear;
Another low pressure side bearing structure for supporting the low pressure side small diameter gear,
The other high-pressure side bearing structure is:
With other high-pressure side body stand,
With other high-pressure side bearings,
The other low-pressure side bearing structure is:
With other low-pressure side body stand,
With other low-pressure side bearings,
The shaft center line of the other high-pressure side bearing is located lower than the shaft center line of the high-pressure side bearing,
The multi-system turbine system according to claim 6, wherein a shaft center line of the other low-pressure side bearing is positioned lower than a shaft center line of the low-pressure side bearing.

The multi-system turbine system according to claim 9, wherein the other high-pressure side main body base is coupled to the high-pressure side main body base in a body, and the other low-pressure side main body base is coupled to the low-pressure side body base.