JPH0456897B2 - - Google Patents
Info
- Publication number
- JPH0456897B2 JPH0456897B2 JP57209175A JP20917582A JPH0456897B2 JP H0456897 B2 JPH0456897 B2 JP H0456897B2 JP 57209175 A JP57209175 A JP 57209175A JP 20917582 A JP20917582 A JP 20917582A JP H0456897 B2 JPH0456897 B2 JP H0456897B2
- Authority
- JP
- Japan
- Prior art keywords
- hydraulic
- pockets
- vertical shaft
- bearing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
- 230000002706 hydrostatic effect Effects 0.000 claims description 14
- 230000003068 static effect Effects 0.000 claims description 2
- 230000001105 regulatory effect Effects 0.000 description 4
- 230000007423 decrease Effects 0.000 description 2
- 230000015556 catabolic process Effects 0.000 description 1
- 238000006731 degradation reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000000284 extract Substances 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
- F16C32/064—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being supplied under pressure
- F16C32/0651—Details of the bearing area per se
- F16C32/0659—Details of the bearing area per se of pockets or grooves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0681—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load
- F16C32/0692—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load for axial load only
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
- Motor Or Generator Frames (AREA)
Description
【発明の詳細な説明】
〔発明の利用分野〕
本発明は立軸回転電機の静圧推力軸受に係り、
特に主軸端面に設置される立軸回転電機の静圧推
力軸受に関するものである。[Detailed Description of the Invention] [Field of Application of the Invention] The present invention relates to a hydrostatic thrust bearing for a vertical shaft rotating electric machine,
In particular, the present invention relates to a hydrostatic thrust bearing of a vertical shaft rotating electrical machine installed on the end face of the main shaft.
最近、大容量立軸回転電機の一つとして上部に
駆動用電動機を設け、この駆動用電動機で昇速し
て減速時の慣性によつてエネルギーを取り出すフ
ライホイール発電機が多用されるようになつた。
このような立軸発電機では上述のように発電機の
上に駆動用電動機が設けられるだけで発電機の下
側にはなにも設けられないので、発電機の主軸の
下端面を推力軸受として利用できる。
Recently, flywheel generators have come into widespread use as a type of large-capacity vertical shaft rotating electric machine, in which a drive motor is installed at the top, and the drive motor speeds up and extracts energy through inertia during deceleration. .
In such a vertical shaft generator, as mentioned above, only the drive motor is installed above the generator and nothing is installed below the generator, so the lower end of the main shaft of the generator is used as a thrust bearing. Available.
現状ではこの部分の推力軸受として周知の自己
油膜形成力を持つ軸受、すなわち動圧軸受が使用
されているが、この油膜形成のためには摺動面に
おいて大きなすべり速度が必要であり、そのため
動圧軸受は第１図および第２図に示されているよ
うに、揺動自在に支持された多数の軸受シユー１
で支持するようになる。この場合に軸受シユー１
の内径より内側では例え軸受シユー１を設けても
所要のすべり速度が得られないため、この部分に
は軸受が設けられず、主軸２の下端面中央部（回
転円板３の中央部分）は利用されない形となつて
いた。 Currently, bearings with a well-known ability to form a self-oil film, that is, hydrodynamic bearings, are used as thrust bearings in this part, but in order to form this oil film, a large sliding speed is required on the sliding surface, so the dynamic As shown in Figs. 1 and 2, pressure bearings consist of a large number of bearings 1 supported in a swingable manner.
It comes to support. In this case, bearing shoe 1
Even if a bearing shoe 1 is provided inside the inner diameter of the shaft, the required sliding speed cannot be obtained. It had become unused.
このような動圧軸受に対し高圧油を主軸と軸受
との間に送り込み、主軸を油膜で支持する静圧軸
受では第３図および第４図に示されているよう
に、主軸の下端面が利用できる。すなわち回転円
板３と摺動する軸受シユー１の中央部に油圧ポケ
ツト４を形成し、ここに油圧源５からの高圧油を
給油管６を通して導き、油圧ポケツト４に発生す
る油圧力によつて回転円板３を浮上らせ、摺動面
７と回転円板３との間に油膜を形成させる。この
ようにすれば回転円板３の中央部分も荷重の支持
に利用されるので、軸受シユー１の外径は上述の
動圧軸受よりも小さくでき、損失の少ない軸受を
得ることができる。 For hydrodynamic bearings, high-pressure oil is sent between the main shaft and the bearing, and the main shaft is supported by an oil film. In hydrostatic bearings, the lower end surface of the main shaft is Available. That is, a hydraulic pocket 4 is formed in the center of the bearing shoe 1 that slides on the rotating disc 3, and high-pressure oil from a hydraulic source 5 is guided here through an oil supply pipe 6, whereby the hydraulic pressure generated in the hydraulic pocket 4 is used to The rotating disk 3 is floated to form an oil film between the sliding surface 7 and the rotating disk 3. In this way, since the central portion of the rotating disk 3 is also used to support the load, the outer diameter of the bearing shoe 1 can be made smaller than that of the above-mentioned hydrodynamic bearing, and a bearing with less loss can be obtained.
しかしこれでは軸受シユー１の摺動面７がリン
グ状となるため、何等かの原因で摺動面７に対す
る回転円板３の浮上りに片寄りが生ずると、油膜
が厚くなつた方向で外部へ油圧ポケツト４から高
圧油が流れ易くなるため、その反対側の油流が減
ることになり、油膜厚さが減じて所要の潤滑性能
が得られなくなつてしまう。すなわちこのように
油圧ポケツト４がただ１個の静圧軸受は、軸受が
極めて小形で軸受シユー１、回転円板３の仕上げ
精度が極めてよく、このような油流の片寄りの生
ずる原因がない場合か、または給油量に十分な余
裕があつて多少の油流の片寄りがあつても、その
反対側で所要の油流、油膜厚さが確保できる場合
でなければ使用することができない。 However, in this case, the sliding surface 7 of the bearing shoe 1 becomes ring-shaped, so if the floating of the rotating disk 3 with respect to the sliding surface 7 is uneven for some reason, the oil film will become thicker in the direction of the outside. Since the high-pressure oil easily flows from the hydraulic pocket 4 to the hydraulic pocket 4, the oil flow on the opposite side decreases, and the oil film thickness decreases, making it impossible to obtain the required lubrication performance. In other words, in this hydrostatic bearing with only one hydraulic pocket 4, the bearing is extremely small and the finishing precision of the bearing shoe 1 and rotating disk 3 is extremely high, and there is no cause for such unevenness of oil flow. Even if there is sufficient margin in the amount of oil supplied and the oil flow is slightly biased, it cannot be used unless the required oil flow and oil film thickness can be secured on the opposite side.
このためこのような油流の片寄りを防止し、全
周に均一な油量、油膜厚さを形成させるものとし
て第５図および第６図に示されているように、軸
受シユー１の摺動面７を多数の扇形状に区切り、
その各々に油圧ポケツト４ａを設け、この油圧ポ
ケツト４ａに油圧源５からリングパイプ８を経由
して流量調整弁９で等分にわけられた高圧油を給
油管６を通して供給し、ちようど多数の静圧軸受
を１ケの軸受シユーに形成させたような構造が採
用されている。 For this reason, as shown in FIGS. 5 and 6, the sliding of the bearing shoe 1 is used to prevent such unevenness of the oil flow and to form a uniform oil amount and oil film thickness around the entire circumference. Divide the moving surface 7 into many fan shapes,
A hydraulic pocket 4a is provided in each of the hydraulic pockets 4a, and high-pressure oil is supplied from the hydraulic source 5 via the ring pipe 8 to the oil supply pipe 6, which is divided into equal parts by the flow rate regulating valve 9. A structure in which several hydrostatic bearings are formed into a single bearing shoe is adopted.
ところでこのような静圧軸受では次に述べるよ
うな欠点があつた。すなわち上述の第１図および
第２図の動圧軸受と同じく回転円板３の中央部分
が利用されないこと、摺動面７に多数の溝が切ら
れるため荷重支持に有効な油圧ポケツト４ａの総
面積が上述の第３図および第４図の１個の場合よ
り減少し、支持荷重が一定ならそれだけ軸受シユ
ー１の外径が増し、軸受損失が増加することであ
る。 However, such hydrostatic bearings have the following drawbacks. In other words, like the hydrodynamic bearings shown in FIGS. 1 and 2 above, the center portion of the rotating disk 3 is not utilized, and since many grooves are cut in the sliding surface 7, the total number of hydraulic pockets 4a that are effective in supporting the load is reduced. If the area is smaller than in the single case shown in FIGS. 3 and 4, and the supporting load is constant, the outer diameter of the bearing shoe 1 will increase accordingly, and the bearing loss will increase.
本発明は以上の点に鑑みなされたものであり、
その目的とするところは、回転円板の中央部分の
利用を可能とした立軸回転電機の静圧推力軸受を
提供するにある。
The present invention has been made in view of the above points,
The purpose is to provide a hydrostatic thrust bearing for a vertical shaft rotating electrical machine that allows the use of the central portion of a rotating disk.
すなわち本発明は、油圧ポケツトを、半径方向
の寸法が周方向の寸法よりも大きくなるように形
成し、このポケツトを軸受シユーの摺動面で、か
つその中心の囲りに複数個設けると共に、ポケツ
ト外周側にはポケツト半径方向寸法より大きい平
坦面が形成されるようになし、複数個の油圧ポケ
ツトに流量調整弁により均等分配された高圧油を
供給するようにしたことを特徴とするものであ
る。
That is, in the present invention, the hydraulic pockets are formed so that the radial dimension is larger than the circumferential dimension, and a plurality of these pockets are provided on the sliding surface of the bearing shoe and around the center thereof. A flat surface larger than the radial dimension of the pocket is formed on the outer circumferential side of the pocket, and high-pressure oil is supplied to the plurality of hydraulic pockets evenly distributed by a flow rate regulating valve. be.
以下、図示した実施例に基づいて本発明を説明
する。第７図および第８図には本発明の一実施例
が示されている。なお従来と同じ部品には同じ符
号を付したので説明は省略する。本実施例では油
圧ポケツト４ｂを、軸受シユー１の摺動面７で、
かつその中心の囲りに複数個設けると共に、これ
ら複数個の油圧ポケツト４ｂに流量調整弁９によ
り均等分配された高圧油を供給するようにした。
このようにすることにより摺動面７全周に均等な
油膜厚さが得られるようになつて、回転円板３の
中央部分の利用を可能とした立軸回転電機の静圧
推力軸受を得ることができる。
The present invention will be explained below based on the illustrated embodiments. An embodiment of the present invention is shown in FIGS. 7 and 8. Note that parts that are the same as those in the conventional model are given the same reference numerals, and therefore their explanations will be omitted. In this embodiment, the hydraulic pocket 4b is located on the sliding surface 7 of the bearing shoe 1.
A plurality of hydraulic pockets 4b are provided around the center thereof, and high pressure oil is evenly distributed and supplied to the plurality of hydraulic pockets 4b by a flow rate regulating valve 9.
By doing so, it becomes possible to obtain a uniform oil film thickness over the entire circumference of the sliding surface 7, and to obtain a hydrostatic thrust bearing for a vertical shaft rotating electrical machine that makes it possible to utilize the central portion of the rotating disk 3. I can do it.
すなわち油圧ポケツト４ｂを従来のように軸受
シユー１の外周側ではなく中央側に設け、本来は
１個にすべき油圧ポケツトを多数に分割し、正常
に回転円板３が浮上つた状態では互に連結されて
１個の油圧ポケツトのように作動し、この部分で
推力荷重の大部分を支持するようにした。そして
この各油圧ポケツト４ｂには、油圧源５からリン
グパイプ８、流量調整弁９を介して均等流量にな
つた高圧油が給油管６によつて供給されるように
した。このようにすることにより軸受シユー１の
摺動面７の中央部分の各油圧ポケツト４ｂに均等
流量の高圧油が配分されるので、これら各油圧ポ
ケツト４ｂから外周側に流出する流量もほぼ均等
となつて、摺動面７に形成される油膜厚さをほぼ
均等にすることができ、大形軸受に静圧軸受を利
用しても油膜厚さの片寄りによる性能低下を防止
することができる。 In other words, the hydraulic pocket 4b is provided on the center side of the bearing shoe 1 instead of on the outer circumferential side as in the conventional case, and the hydraulic pocket, which should originally be one, is divided into many parts, so that when the rotating disk 3 is normally floated, they are mutually connected. They were connected together and operated like a single hydraulic pocket, supporting most of the thrust load. Each hydraulic pocket 4b is supplied with high-pressure oil from a hydraulic source 5 through a ring pipe 8 and a flow rate regulating valve 9 at an equal flow rate through an oil supply pipe 6. By doing this, an equal flow rate of high-pressure oil is distributed to each hydraulic pocket 4b in the central portion of the sliding surface 7 of the bearing shoe 1, so that the flow rate flowing out from each hydraulic pocket 4b to the outer circumferential side is also approximately equal. As a result, the thickness of the oil film formed on the sliding surface 7 can be made almost uniform, and even if a hydrostatic bearing is used as a large bearing, it is possible to prevent performance degradation due to uneven thickness of the oil film. .
上述のように本発明は油圧ポケツトを、半径方
向の寸法が周方向の寸法よりも大きくなるように
形成し、このポケツトを軸受シユーの摺動面で、
かつその中心の周りに複数個設けると共に、ポケ
ツト外周側にはポケツト半径方向寸法より大きい
平坦面が形成されるようになし、複数個の油圧ポ
ケツトに流量調整弁により均等分配された高圧油
を供給するようにしたので、すなわち周方向に細
かい油圧ポケツトが形成されるようにしたから外
周側に流出する流量がほぼ均等となり、かつ外周
側に広い平坦面があるので摺動面全周に均等な油
膜が得られるようになり、回転円板の中央部分の
利用を可能とした立軸回転電機の静圧推力軸受を
得ることができる。
As described above, in the present invention, the hydraulic pocket is formed so that the radial dimension is larger than the circumferential dimension, and this pocket is formed on the sliding surface of the bearing shoe.
A plurality of hydraulic pockets are provided around the center, and a flat surface larger than the radial dimension of the pocket is formed on the outer peripheral side of the pocket, and high pressure oil is supplied evenly distributed to the plurality of hydraulic pockets by a flow rate adjustment valve. In other words, since fine hydraulic pockets are formed in the circumferential direction, the flow rate flowing out to the outer circumferential side is almost uniform, and since there is a wide flat surface on the outer circumferential side, the flow rate is evenly distributed over the entire circumference of the sliding surface. An oil film can now be obtained, and a hydrostatic thrust bearing for a vertical shaft rotating electric machine can be obtained, which makes it possible to utilize the central portion of the rotating disk.
第１図は従来の立軸回転電機の動圧推力軸受の
縦断側面図、第２図は従来の立軸回転電機の動圧
推力軸受の平面図、第３図は従来の立軸回転電機
の静圧推力軸受の縦断側面図、第４図は従来の立
軸回転電機の静圧推力軸受の平面図、第５図は従
来の立軸回転電機の静圧推力軸受の他の例の縦断
側面図、第６図は同じく他の例の平面図、第７図
は本発明の立軸回転電機の静圧推力軸受の一実施
例の縦断側面図、第８図は同じく一実施例の平面
図である。
１……軸受シユー、２……主軸、３……回転円
板、４ｂ……油圧ポケツト、５……油圧源、６…
…給油管、７……摺動面、９……流量調整弁。
Figure 1 is a longitudinal cross-sectional side view of the hydrodynamic thrust bearing of a conventional vertical shaft rotating electrical machine, Figure 2 is a plan view of the dynamic pressure thrust bearing of a conventional vertical shaft rotating electrical machine, and Figure 3 is the static pressure thrust of a conventional vertical shaft rotating electrical machine. 4 is a plan view of a conventional hydrostatic thrust bearing for a vertical shaft rotating electrical machine; FIG. 5 is a vertical sectional side view of another example of a conventional hydrostatic thrust bearing for a vertical shaft rotating electrical machine; FIG. 6 is a longitudinal sectional side view of the bearing; 7 is a plan view of another example, FIG. 7 is a vertical sectional side view of an embodiment of the hydrostatic thrust bearing for a vertical shaft rotating electric machine of the present invention, and FIG. 8 is a plan view of another embodiment. DESCRIPTION OF SYMBOLS 1...Bearing shoe, 2...Main shaft, 3...Rotating disk, 4b...Hydraulic pocket, 5...Hydraulic power source, 6...
... Oil supply pipe, 7 ... Sliding surface, 9 ... Flow rate adjustment valve.
Claims (1)
シユーと、この軸受シユーに設けられた油圧ポケ
ツトとを備え、この油圧ポケツトには高圧油が供
給される立軸回転電機の静圧推力軸受において、
前記油圧ポケツトを、半径方向の寸法が周方向の
寸法よりも大きくなるように形成し、このポケツ
トを前記軸受シユーの摺動面で、かつその中心の
囲りに複数個設けると共に、ポケツト外周側には
前記ポケツト半径方向寸法より大きい平坦面が形
成されるようになし、前記複数個の油圧ポケツト
に流量調整弁により均等分配された前記高圧油を
供給するようにしたことを特徴とする立軸回転電
機の静圧推力軸受。1. Static pressure thrust of a vertical shaft rotating electrical machine that is equipped with a circular bearing shoe sliding on a rotating disc of a vertical shaft and a hydraulic pocket provided in this bearing shoe, and this hydraulic pocket is supplied with high pressure oil. In bearings,
The hydraulic pockets are formed so that the radial dimension is larger than the circumferential dimension, and a plurality of these pockets are provided on the sliding surface of the bearing shoe and around the center thereof, and a plurality of pockets are provided on the sliding surface of the bearing shoe, and a plurality of pockets are provided on the outer circumferential side of the pocket. The vertical shaft rotation is characterized in that a flat surface larger than the radial dimension of the pocket is formed, and the high-pressure oil is evenly distributed to the plurality of hydraulic pockets by a flow control valve. Hydrostatic thrust bearings for electrical machinery.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP20917582A JPS5999119A (en) | 1982-11-29 | 1982-11-29 | Static pressure thrust bearing of vertical shaft rotary electric machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP20917582A JPS5999119A (en) | 1982-11-29 | 1982-11-29 | Static pressure thrust bearing of vertical shaft rotary electric machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5999119A JPS5999119A (en) | 1984-06-07 |
| JPH0456897B2 true JPH0456897B2 (en) | 1992-09-09 |
Family
ID=16568569
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP20917582A Granted JPS5999119A (en) | 1982-11-29 | 1982-11-29 | Static pressure thrust bearing of vertical shaft rotary electric machine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5999119A (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101907133B (en) * | 2010-08-16 | 2011-11-02 | 重庆齿轮箱有限责任公司 | Adaptive variable working condition cylindrical spherical pressure bearing system |
| CN102494112B (en) * | 2011-11-30 | 2014-01-08 | 重庆齿轮箱有限责任公司 | Built-in high-pressure combination bearing oil feed pipeline structure of large vertical speed reducer |
| US11355996B2 (en) * | 2019-11-06 | 2022-06-07 | Neapco Intellectual Property Holdings, Llc | Lubricant supported electric motor with controlled and balanced lubricant flow |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5268648A (en) * | 1975-12-02 | 1977-06-07 | Escher Wyss Ag | Hydroulic support device |
| JPS5421503A (en) * | 1977-07-19 | 1979-02-17 | Matsushita Electric Works Ltd | Coil frame for planar multi-pole synchronous motor |
-
1982
- 1982-11-29 JP JP20917582A patent/JPS5999119A/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5268648A (en) * | 1975-12-02 | 1977-06-07 | Escher Wyss Ag | Hydroulic support device |
| JPS5421503A (en) * | 1977-07-19 | 1979-02-17 | Matsushita Electric Works Ltd | Coil frame for planar multi-pole synchronous motor |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5999119A (en) | 1984-06-07 |
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