JPH0552356U - Turbomachine impeller mounting device - Google Patents
Turbomachine impeller mounting deviceInfo
- Publication number
- JPH0552356U JPH0552356U JP11076691U JP11076691U JPH0552356U JP H0552356 U JPH0552356 U JP H0552356U JP 11076691 U JP11076691 U JP 11076691U JP 11076691 U JP11076691 U JP 11076691U JP H0552356 U JPH0552356 U JP H0552356U
- Authority
- JP
- Japan
- Prior art keywords
- impeller
- drive shaft
- shaft
- turbomachine
- male screw
- 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
Abstract
(57)【要約】
【構成】 ホイール部１１とその一方の面に設けた複数
枚の羽根部１２とからなるインペラ１と、インペラ１を
回転駆動する駆動軸２とを備え、インペラ１の背面１４
に開口する軸方向穴１６と、インペラ１の背面に突出す
る中空円筒状のインペラ取付部１５と、駆動軸２の軸端
に開口する取付穴２５を設けて形成したインペラ取付部
１５の外周に嵌合する中空円筒状の軸端部２１と、イン
ペラ１と駆動軸２を結合する螺子とを設けて、インペラ
１の背面１４と駆動軸２の軸端面２４とを密着させるよ
うにしたものである。
【効果】 高速回転時に遠心力によってインペラのホイ
ール部と駆動軸の軸端部とに生じる径方向の変形量に差
が出ないようにして、インペラと駆動軸を常に密着した
状態に維持するので、インペラがバランスを崩すことが
なく、ターボ機械の性能を安定した状態に維持すること
ができる。
(57) [Summary] [Structure] An impeller 1 including a wheel portion 11 and a plurality of blade portions 12 provided on one surface thereof and a drive shaft 2 for rotationally driving the impeller 1 are provided. 14
On the outer periphery of the impeller mounting portion 15 formed by providing an axial hole 16 that opens at the end, a hollow cylindrical impeller mounting portion 15 that projects to the back surface of the impeller 1, and a mounting hole 25 that opens at the shaft end of the drive shaft 2. A hollow cylindrical shaft end portion 21 to be fitted and a screw for connecting the impeller 1 and the drive shaft 2 are provided so that the back surface 14 of the impeller 1 and the shaft end surface 24 of the drive shaft 2 are brought into close contact with each other. is there. [Effect] At the time of high-speed rotation, there is no difference in radial deformation between the wheel part of the impeller and the shaft end part of the drive shaft due to centrifugal force, and the impeller and the drive shaft are always kept in close contact with each other. Therefore, the impeller does not lose its balance, and the performance of the turbomachine can be maintained in a stable state.
Description
【０００１】[0001]
本考案は、高速回転するターボ機械のインペラ取付装置に関する。 The present invention relates to an impeller mounting device for a turbomachine that rotates at high speed.
【０００２】[0002]
従来、ターボ圧縮機等のターボ機械のインペラを駆動軸に固定する場合、図４ に示すように、インペラ１は、円板状のホイール部１１と、その一方の面に設け た羽根部１２とからなり、ホイール部１１の中心に貫通する取付穴１３を設けて ある。インペラ１を回転駆動する駆動軸２の軸端部２１にはテーパまたは段付の 細径部２２を突出させて設け、細径部２２をインペラ１の取付穴１３に隙間のな いように嵌合し、細径部２２の先端部に設けた雄螺子２３にナット３を螺合して ある。 このように、ホイール部１１の背面１４と駆動軸２の軸端面２４とが密着する ようにナット３により締めつけて、面接触により駆動軸２からインペラ１に動力 を伝達するようにしたものが開示されている（例えば、特開昭６１−１４９６１ ５号）。 Conventionally, when fixing an impeller of a turbo machine such as a turbo compressor to a drive shaft, as shown in FIG. 4, the impeller 1 includes a disc-shaped wheel portion 11 and a blade portion 12 provided on one surface thereof. And a mounting hole 13 penetrating the center of the wheel portion 11 is provided. The shaft end 21 of the drive shaft 2 for rotating the impeller 1 is provided with a tapered or stepped small-diameter portion 22 protruding so that the small-diameter portion 22 is fitted into the mounting hole 13 of the impeller 1 without a gap. The nut 3 is screwed to the male screw 23 provided at the tip of the small diameter portion 22. As described above, the nut 14 is tightened so that the rear surface 14 of the wheel portion 11 and the shaft end surface 24 of the drive shaft 2 are in close contact with each other, and power is transmitted from the drive shaft 2 to the impeller 1 by surface contact. (For example, JP-A-61-149615).
【０００３】[0003]
ところが、上記構成では、駆動軸２は中実の丸棒で比較的外径が小さく、かつ 抗張力の高い鉄系の材料を用いているため、高速回転した時でも遠心力による変 形は小さい。 一方、ホイール部１１の材料は耐熱性高抗張力軽合金を使用することが多いが 、高抗張力合金鋼などと比較すると抗張力が低く、遠心力による変形量は駆動軸 ２に比較して大きい。 遠心力は半径の２乗に比例して大きくなるが、ホイール部１１は外径が大きく 、取付穴１３を設けてあるので、さらに、遠心力による変形量は大きくなり、高 速回転時のホイール部１１と駆動軸２の遠心力による変形量に差が出る。 このように、回転していない時に、ナット３によりホイール部１１の背面１４ と駆動軸２の軸端面２４とが密着するように締めつけていても、高速回転するこ とにより、変形量の差により接触面に滑りが生じる。次に回転が停止した時、変 形が元の状態に戻ろうとして再び逆方向の滑りが生じる。しかし、回転が停止し ても、接触面に摩擦が生じるため必ずしも元の相対位置関係に戻ることはなく、 加減速のくり返しにより駆動軸２とホイール部１１との相対位置関係はミクロに 見てランダムに変化する。このことによりインペラ１のバランスが悪くなり、振 動などを引き起こすという課題があった。 本考案は、ホイール部と駆動軸の遠心力による変形量に差が出ないようにして 安定して高速回転するターボ機械を提供することを目的とするものである。 However, in the above-mentioned configuration, the drive shaft 2 is a solid round bar having a relatively small outer diameter and using an iron-based material having high tensile strength, and therefore deformation due to centrifugal force is small even when rotating at high speed. On the other hand, as the material of the wheel portion 11, a heat resistant high tensile strength light alloy is often used, but its tensile strength is lower than that of high tensile strength alloy steel and the amount of deformation due to centrifugal force is larger than that of the drive shaft 2. Centrifugal force increases in proportion to the square of the radius, but since wheel part 11 has a large outer diameter and mounting holes 13 are provided, the amount of deformation due to centrifugal force further increases, and the wheel during high-speed rotation becomes larger. There is a difference in the amount of deformation of the portion 11 and the drive shaft 2 due to the centrifugal force. Thus, even when the nut 3 is tightened so that the rear surface 14 of the wheel portion 11 and the shaft end surface 24 of the drive shaft 2 are in close contact with each other when the nut 3 is not rotating, the difference in the amount of deformation is caused by the high speed rotation. Sliding occurs on the contact surface. Next, when the rotation stops, the deformation tries to return to the original state and slips in the opposite direction again. However, even if the rotation stops, the contact surface does not always return to the original relative positional relationship due to friction, and the relative positional relationship between the drive shaft 2 and the wheel portion 11 can be seen microscopically due to repeated acceleration and deceleration. It changes randomly. As a result, the balance of the impeller 1 becomes unbalanced, causing a problem such as vibration. An object of the present invention is to provide a turbomachine that stably rotates at high speed without causing a difference in the amount of deformation of the wheel portion and the drive shaft due to centrifugal force.
【０００４】[0004]
本考案は、ホイール部とその一方の面に設けられた複数枚の羽根部とからなる インペラと、前記インペラを回転駆動する駆動軸とを備え、前記インペラの背面 と前記駆動軸の軸端面とを密着させるようにして前記インペラを前記駆動軸に固 定するターボ機械のインペラ取付装置において、前記インペラの背面に開口する 軸方向穴と、前記インペラの背面に突出する中空円筒状のインペラ取付部と、前 記駆動軸に前記インペラ取付部の外周に嵌合する中空円筒状の軸端部と、前記イ ンペラと前記駆動軸を結合する螺子とを設け、前記螺子を締めつけることにより 前記駆動軸の軸端面と前記インペラの背面を密着させるものである。 The present invention includes an impeller including a wheel portion and a plurality of blade portions provided on one surface thereof, and a drive shaft that rotationally drives the impeller, and a back surface of the impeller and an end surface of the drive shaft. In a turbomachine impeller mounting device for fixing the impeller to the drive shaft so as to be in close contact with each other, an axial hole opening on the back surface of the impeller and a hollow cylindrical impeller mounting portion projecting on the back surface of the impeller. And a hollow cylindrical shaft end portion fitted to the outer periphery of the impeller attachment portion, and a screw connecting the impeller and the drive shaft to the drive shaft, and the drive shaft is tightened by tightening the screw. The end surface of the shaft and the back surface of the impeller are brought into close contact with each other.
【０００５】[0005]
インペラを高速回転させると、ホイール部は外径が大きいために大きな遠心力 が働いて径方向にミクロに変形するが、同時に嵌合部も軸方向穴によって中空円 筒状に形成されてあるため、遠心力により径方向に変形する。しかし、駆動軸の 軸端部は嵌合部ほど遠心力によって変形しないため、嵌合部と軸端部の径方向の 変形量は同じとなるか、嵌合部が軸端部の内側から外側に押し付けて径方向の変 形量に差ができず、インペラの背面と軸端面の相対的位置関係は変化しない。 したがって、高速回転の遠心力によってインペラの背面と軸端部に径方向の変 形が生じても、互いに滑りが生じることがなく、背面と軸端面の密着状態を常に 維持することができる。 When the impeller is rotated at a high speed, the wheel part has a large outer diameter, and a large centrifugal force acts on it, causing it to deform microscopically in the radial direction.At the same time, however, the fitting part is also formed into a hollow cylindrical shape by the axial hole. , It is deformed in the radial direction by centrifugal force. However, since the shaft end of the drive shaft is not deformed by centrifugal force as much as the fitting part, the amount of deformation in the radial direction of the fitting part and the shaft end is the same, or the fitting part is from the inside to the outside of the shaft end. When pressed against, the radial deformation cannot be changed, and the relative positional relationship between the impeller back surface and the shaft end surface does not change. Therefore, even if the rear surface of the impeller and the shaft end portion are deformed in the radial direction by the centrifugal force of the high-speed rotation, they do not slip with each other, and the close contact between the back surface and the shaft end surface can always be maintained.
【０００６】[0006]
本考案を図に示す実施例について説明する。 図１は本考案の実施例を示す側断面図で、インペラ１は高抗張力軽合金からな り、ほぼ円板状のホイール部１１と、その一方の面に設けられた複数枚の羽根部 １２からなり、羽根部１２が設けられた面と反対の背面１４にはホイール部１１ と同心に突出する円柱状の嵌合部１５Ａを有するインペラ取付部１５を設けてあ る。インペラ取付部１５の中心には背面１４に開口する軸方向穴１６を設けて嵌 合部１５Ａを中空円筒状に形成してあり、先端付近を細くして雄螺子１７を設け てある。ホイール部１１の羽根部１２を設けた面の中央にはナット部１８を設け てある。 駆動軸２は高抗張力合金鋼からなり、軸端部２１には駆動軸２の外周と同心に インペラ取付部１５の嵌合部１５Ａと隙間なく嵌合する取付穴２５を設け、取付 穴２５の奥を細くしてインペラ１の雄螺子１７と螺合する雌螺子２６を設けてあ る。 インペラ１を駆動軸２に固定する場合は、インペラ取付部１５を駆動軸２の取 付穴２５に挿入して嵌合部１５Ａを取付穴２５に嵌合し、雄螺子１７を雌螺子２ ６に螺合させて、ナット部１８によって締めつけ、背面１４と軸端部２１の軸端 面２４とを密着させる。 以上の方法で駆動軸２に固定したインペラ１を高速回転させると、ホイール部 １１は外径が大きいために大きな遠心力が働いて径方向にミクロに変形するが、 同時に嵌合部１５Ａも軸方向穴１６によって中空円筒状に形成されてあるため、 遠心力により径方向に変形する。しかし、駆動軸２の軸端部２１は嵌合部１５Ａ ほど遠心力によって変形しないため、嵌合部１５Ａと軸端部２１の径方向の変形 量は同じとなるか、嵌合部１５Ａが軸端部２１の内側から外側に押し付けるよう になるので径方向の変形量に差ができず、インペラ１の背面１４と軸端面２４の 相対的位置関係は変化しない。 したがって、高速回転の遠心力によってインペラ１の背面１４と軸端部２１に 径方向の変形が生じても、互いに滑りが生じることがなく、背面１４と軸端面２ ４の密着状態を常に維持することができる。 The present invention will be described with reference to the embodiments shown in the drawings. FIG. 1 is a side sectional view showing an embodiment of the present invention, in which an impeller 1 is made of a high tensile strength light alloy and has a substantially disk-shaped wheel portion 11 and a plurality of blade portions 12 provided on one surface thereof. An impeller mounting portion 15 having a cylindrical fitting portion 15A projecting concentrically with the wheel portion 11 is provided on the rear surface 14 opposite to the surface on which the blade portion 12 is provided. At the center of the impeller attachment portion 15, an axial hole 16 that opens to the back surface 14 is provided to form a fitting portion 15A in the shape of a hollow cylinder, and a male screw 17 is provided with a thinned portion near the tip. A nut portion 18 is provided at the center of the surface of the wheel portion 11 on which the blade portion 12 is provided. The drive shaft 2 is made of high tensile strength alloy steel, and the shaft end portion 21 is provided with a mounting hole 25 which is concentric with the outer periphery of the drive shaft 2 and fits with the fitting portion 15A of the impeller mounting portion 15 without a gap. A female screw 26 is provided which has a narrowed inner portion and is screwed with the male screw 17 of the impeller 1. When fixing the impeller 1 to the drive shaft 2, the impeller mounting portion 15 is inserted into the mounting hole 25 of the drive shaft 2, the fitting portion 15A is fitted into the mounting hole 25, and the male screw 17 is inserted into the female screw 26. And then tighten the nut portion 18 to bring the back surface 14 and the shaft end surface 24 of the shaft end portion 21 into close contact with each other. When the impeller 1 fixed to the drive shaft 2 is rotated at a high speed by the above method, a large centrifugal force acts on the wheel portion 11 due to its large outer diameter, so that the fitting portion 15A is also axially deformed. Since it is formed in a hollow cylindrical shape by the direction hole 16, it is deformed in the radial direction by centrifugal force. However, since the shaft end portion 21 of the drive shaft 2 is not deformed by the centrifugal force as much as the fitting portion 15A, the fitting portion 15A and the shaft end portion 21 have the same radial deformation amount, or the fitting portion 15A has the same axial shape. Since the pressing force is applied from the inner side to the outer side of the end portion 21, there is no difference in the amount of radial deformation, and the relative positional relationship between the back surface 14 of the impeller 1 and the shaft end surface 24 does not change. Therefore, even if the back surface 14 and the shaft end portion 21 of the impeller 1 are deformed in the radial direction by the centrifugal force of the high speed rotation, the back surface 14 and the shaft end surface 24 are always kept in close contact with each other without slippage. be able to.
【０００７】 図２は第２の実施例を示す側断面図で、図１に示したインペラ取付部１５の先 端に雄螺子を設ける代わりに、軸方向穴１６がホイール１１を貫通するようにし 、両端に雄螺子４１、４２を有するボルト４を軸方向穴１６に挿入して雄螺子４ １を雌螺子２６に螺合させ、ホイール部１１から突出する雄螺子４２にナット３ を螺合して締めつけ、背面１４と軸端面２４とを密着させるものである。 この構造により、嵌合部１５Ａを取付穴２５に嵌合する際に、雄螺子４１が取 付穴２５の内面とすれ合って傷をつけることがなくなる。 図３は第３の実施例を示す側断面図で、ホイール部１１の背面１４に軸方向穴 １６と同心円状のリング溝１９を設けて、軸方向穴１６とリング溝１９との間に 嵌合部１５Ａを有するインペラ取付部１５を形成してある。駆動軸２の軸端部２ １には細径部２２を設けて軸方向穴１６に嵌合させるとともに、リング溝１９に 挿入し、嵌合部１５Ａに嵌合するリング状の突起部２７を設けてある。また、細 径部２２の先端部に雄螺子２３を設けてナット３を螺合し、リング溝１９に突起 部２７を嵌合させた状態で、駆動軸２の軸端面２４とインペラ１の背面１４を密 着するようにしてある。 従って、インペラ１が高速回転して、ホイール部１１と軸端部２１に遠心力が 作用しても、嵌合部１５Ａと突起部２７とが嵌合しているため、軸端部２１とイ ンペラ１との径方向の変形量の差は発生しない。 なお、本考案はターボ圧縮機のインペラの取付装置に限るものでは無く、高速 ガスタービンなど、高速回転するターボ機械全般に適用できる。FIG. 2 is a side sectional view showing a second embodiment. Instead of providing a male screw at the front end of the impeller mounting portion 15 shown in FIG. 1, an axial hole 16 is made to penetrate the wheel 11. , The bolt 4 having male screws 41, 42 at both ends is inserted into the axial hole 16 so that the male screw 41 is screwed into the female screw 26, and the nut 3 is screwed into the male screw 42 protruding from the wheel portion 11. The rear surface 14 and the shaft end surface 24 are brought into close contact with each other. With this structure, when the fitting portion 15A is fitted into the mounting hole 25, the male screw 41 does not come into contact with the inner surface of the mounting hole 25 to cause damage. FIG. 3 is a side sectional view showing a third embodiment, in which a rear surface 14 of the wheel portion 11 is provided with a ring groove 19 which is concentric with the axial hole 16 and is fitted between the axial hole 16 and the ring groove 19. An impeller attachment portion 15 having a joint portion 15A is formed. A small diameter portion 22 is provided on the shaft end portion 21 of the drive shaft 2 so as to be fitted into the axial hole 16 and is also inserted into the ring groove 19 to form a ring-shaped projection portion 27 which is fitted to the fitting portion 15A. It is provided. In addition, the male screw 23 is provided at the tip of the small diameter portion 22, the nut 3 is screwed, and the protrusion 27 is fitted in the ring groove 19, and the shaft end surface 24 of the drive shaft 2 and the back surface of the impeller 1 are attached. 14 are closely attached. Therefore, even if the impeller 1 rotates at a high speed and centrifugal force acts on the wheel portion 11 and the shaft end portion 21, the fitting portion 15A and the protrusion 27 are fitted to each other, so that the shaft end portion 21 and the shaft end portion 21 are fitted together. There is no difference in the amount of radial deformation from the impeller 1. It should be noted that the present invention is not limited to the installation device for the impeller of the turbo compressor, but can be applied to all turbo machines that rotate at high speed, such as a high-speed gas turbine.
【０００８】[0008]
以上述べたように、本考案によれば、高速回転時に遠心力によってインペラの ホイール部と駆動軸の軸端部とに生じる径方向の変形量に差が出ないようにして 、インペラと駆動軸を常に密着した状態に維持するので、インペラがバランスを 崩すことがなく、ターボ機械の性能を安定した状態に維持することができる効果 がある。 As described above, according to the present invention, there is no difference in radial deformation between the wheel portion of the impeller and the shaft end portion of the drive shaft due to centrifugal force during high-speed rotation, so that the impeller and the drive shaft do not differ. Since the engine is always in close contact, the impeller does not lose its balance and the turbomachine performance can be maintained in a stable state.
【図１】本考案の実施例を示す側断面図である。FIG. 1 is a side sectional view showing an embodiment of the present invention.
【図２】本考案の第２の実施例を示す側断面図である。FIG. 2 is a side sectional view showing a second embodiment of the present invention.
【図３】本考案の第３の実施例を示す側断面図である。FIG. 3 is a side sectional view showing a third embodiment of the present invention.
【図４】従来例を示す側断面図である。FIG. 4 is a side sectional view showing a conventional example.
１ インペラ １１ ホイール 部 １２ 羽根部 １４ 背面 １５ インペラ取付部 １５Ａ 嵌合部 １６ 軸方向穴 １７、２３、４ １、４２ 雄螺子 １８ ナット部 １９ リング溝 ２ 駆動軸 ２１ 軸端部 ２２ 細径部 ２４ 軸端面 ２５ 取付穴 ２６ 雌螺子 ２７ 突起部 ３ ナット ４ ボルト DESCRIPTION OF SYMBOLS 1 Impeller 11 Wheel part 12 Blade part 14 Back surface 15 Impeller mounting part 15A Fitting part 16 Axial hole 17,23,41,42 Male screw 18 Nut part 19 Ring groove 2 Drive shaft 21 Shaft end part 22 Small diameter part 24 Shaft end face 25 Mounting hole 26 Female screw 27 Projection part 3 Nut 4 Bolt
フロントページの続き (72)考案者 久米 常生 福岡県北九州市八幡西区黒崎城石２番１号 株式会社安川電機内Continuation of the front page (72) Creator Tsuneo Kume No. 2 Kurosaki Shiroishi, Hachimannishi-ku, Kitakyushu, Fukuoka Prefecture Yasukawa Electric Co., Ltd.
Claims (5)
枚の羽根部とからなるインペラと、前記インペラを回転
駆動する駆動軸とを備え、前記インペラの背面と前記駆
動軸の軸端面とを密着させるようにして前記インペラを
前記駆動軸に固定するターボ機械のインペラ取付装置に
おいて、前記インペラの背面に開口する軸方向穴と、前
記インペラの背面に突出する中空円筒状のインペラ取付
部と、前記駆動軸の軸端に開口する取付穴を設けて形成
した前記インペラ取付部の外周に嵌合する中空円筒状の
軸端部と、前記インペラと前記駆動軸を結合する螺子と
を設けたことを特徴とするターボ機械のインペラ取付装
置。1. An impeller comprising a wheel portion and a plurality of blade portions provided on one surface thereof, a drive shaft for rotationally driving the impeller, and a back surface of the impeller and a shaft end surface of the drive shaft. In an impeller mounting device of a turbomachine for fixing the impeller to the drive shaft so as to be in close contact with each other, an axial hole opening on the back surface of the impeller, and a hollow cylindrical impeller mounting portion projecting on the back surface of the impeller. A hollow cylindrical shaft end portion fitted to the outer periphery of the impeller mounting portion formed by providing a mounting hole opened at the shaft end of the drive shaft, and a screw connecting the impeller and the drive shaft are provided. An impeller mounting device for turbomachines, characterized in that
ペラ取付部の先端に設けた雄螺子と、前記駆動軸の前記
取付穴の奥に設けた雌螺子とで結合するようにした請求
項１記載のターボ機械のインペラ取付装置。2. A screw for connecting the drive shaft is connected by a male screw provided at the tip of the impeller attachment portion and a female screw provided at the back of the attachment hole of the drive shaft. The turbomachine impeller attachment device according to 1.
と、前記駆動軸の軸端面に突出して前記軸方向穴に挿入
された先端が前記インペラから突出し、その先端に雄螺
子を有する細径部と、前記雄螺子に螺合するナットとを
設けた請求項１記載のターボ機械のインペラ取付装置。3. A small diameter having an axial hole penetrating through the center of the impeller and a tip protruding into the axial end surface of the drive shaft and inserted into the axial hole protruding from the impeller, and having a male screw at the tip. The turbomachine impeller attachment device according to claim 1, further comprising a portion and a nut screwed with the male screw.
に挿入したボルトの一方端の雄螺子と前記駆動軸の前記
取付穴の奥に設けた雌螺子とを螺合し、前記ボルトの他
方端に設けた雄螺子を前記インペラから突出させてナッ
トを螺合するようにした請求項１記載のターボ機械のイ
ンペラ取付装置。4. A male screw at one end of a bolt inserted into an axial hole passing through the center of the impeller and a female screw provided at the back of the mounting hole of the drive shaft are screwed together, and the other of the bolts is screwed. The impeller mounting device for a turbomachine according to claim 1, wherein a male screw provided at an end is projected from the impeller and a nut is screwed into the male screw.
前記インペラ取付部を形成し、前記駆動軸の軸端部に前
記リング溝に挿入し前記インペラ取付部の外周に嵌合す
る突起部を形成した請求項１から４までのいずれか１項
に記載のターボ機械のインペラ取付装置。5. A ring groove is provided on the back surface of the impeller to form the impeller mounting portion, and a projection portion which is inserted into the ring groove at the shaft end portion of the drive shaft and fits on the outer periphery of the impeller mounting portion. The turbomachine impeller attachment device according to any one of claims 1 to 4, which is formed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11076691U JPH0552356U (en) | 1991-12-17 | 1991-12-17 | Turbomachine impeller mounting device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11076691U JPH0552356U (en) | 1991-12-17 | 1991-12-17 | Turbomachine impeller mounting device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0552356U true JPH0552356U (en) | 1993-07-13 |
Family
ID=14544040
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP11076691U Pending JPH0552356U (en) | 1991-12-17 | 1991-12-17 | Turbomachine impeller mounting device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0552356U (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006214341A (en) * | 2005-02-03 | 2006-08-17 | Shimadzu Corp | Turbo rotating equipment |
| JP2010096113A (en) * | 2008-10-17 | 2010-04-30 | Ihi Corp | Impeller fastening structure |
| JP2011122539A (en) * | 2009-12-11 | 2011-06-23 | Ihi Corp | Supercharger |
| WO2012115086A1 (en) | 2011-02-21 | 2012-08-30 | 株式会社Ihi | Turbo device |
| JP2015166604A (en) * | 2014-03-03 | 2015-09-24 | 山洋電気株式会社 | Joint structure for shaft |
| WO2017203917A1 (en) * | 2016-05-25 | 2017-11-30 | 株式会社Ihi | Rotating body and supercharger |
-
1991
- 1991-12-17 JP JP11076691U patent/JPH0552356U/en active Pending
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006214341A (en) * | 2005-02-03 | 2006-08-17 | Shimadzu Corp | Turbo rotating equipment |
| JP2010096113A (en) * | 2008-10-17 | 2010-04-30 | Ihi Corp | Impeller fastening structure |
| JP2011122539A (en) * | 2009-12-11 | 2011-06-23 | Ihi Corp | Supercharger |
| WO2012115086A1 (en) | 2011-02-21 | 2012-08-30 | 株式会社Ihi | Turbo device |
| JP2015166604A (en) * | 2014-03-03 | 2015-09-24 | 山洋電気株式会社 | Joint structure for shaft |
| WO2017203917A1 (en) * | 2016-05-25 | 2017-11-30 | 株式会社Ihi | Rotating body and supercharger |
| CN109072776A (en) * | 2016-05-25 | 2018-12-21 | 株式会社Ihi | Rotary body and booster |
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