JPS6349086B2 - - Google Patents
Info
- Publication number
- JPS6349086B2 JPS6349086B2 JP18684383A JP18684383A JPS6349086B2 JP S6349086 B2 JPS6349086 B2 JP S6349086B2 JP 18684383 A JP18684383 A JP 18684383A JP 18684383 A JP18684383 A JP 18684383A JP S6349086 B2 JPS6349086 B2 JP S6349086B2
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- ceramic
- segments
- underwater
- underwater 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
Links
- 239000000919 ceramic Substances 0.000 claims description 41
- 239000002184 metal Substances 0.000 claims description 13
- 229910052751 metal Inorganic materials 0.000 claims description 13
- 239000007788 liquid Substances 0.000 claims description 12
- UONOETXJSWQNOL-UHFFFAOYSA-N tungsten carbide Chemical compound [W+]#[C-] UONOETXJSWQNOL-UHFFFAOYSA-N 0.000 claims description 7
- HBMJWWWQQXIZIP-UHFFFAOYSA-N silicon carbide Chemical compound [Si+]#[C-] HBMJWWWQQXIZIP-UHFFFAOYSA-N 0.000 claims description 6
- 229910052581 Si3N4 Inorganic materials 0.000 claims description 5
- HQVNEWCFYHHQES-UHFFFAOYSA-N silicon nitride Chemical compound N12[Si]34N5[Si]62N3[Si]51N64 HQVNEWCFYHHQES-UHFFFAOYSA-N 0.000 claims description 5
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 19
- 239000007789 gas Substances 0.000 description 10
- 239000000463 material Substances 0.000 description 10
- 239000002002 slurry Substances 0.000 description 10
- VYPSYNLAJGMNEJ-UHFFFAOYSA-N Silicium dioxide Chemical compound O=[Si]=O VYPSYNLAJGMNEJ-UHFFFAOYSA-N 0.000 description 7
- 239000010935 stainless steel Substances 0.000 description 6
- 229910001220 stainless steel Inorganic materials 0.000 description 6
- 238000000034 method Methods 0.000 description 5
- 239000002245 particle Substances 0.000 description 5
- 239000013535 sea water Substances 0.000 description 5
- 239000000853 adhesive Substances 0.000 description 4
- 230000001070 adhesive effect Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 239000013505 freshwater Substances 0.000 description 4
- 229910010271 silicon carbide Inorganic materials 0.000 description 4
- 238000012360 testing method Methods 0.000 description 4
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 3
- PNEYBMLMFCGWSK-UHFFFAOYSA-N aluminium oxide Inorganic materials [O-2].[O-2].[O-2].[Al+3].[Al+3] PNEYBMLMFCGWSK-UHFFFAOYSA-N 0.000 description 3
- 229910052799 carbon Inorganic materials 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 3
- 239000004576 sand Substances 0.000 description 3
- 229910000906 Bronze Inorganic materials 0.000 description 2
- 229910004298 SiO 2 Inorganic materials 0.000 description 2
- 239000010974 bronze Substances 0.000 description 2
- 239000000470 constituent Substances 0.000 description 2
- KUNSUQLRTQLHQQ-UHFFFAOYSA-N copper tin Chemical compound [Cu].[Sn] KUNSUQLRTQLHQQ-UHFFFAOYSA-N 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000011156 evaluation Methods 0.000 description 2
- 230000020169 heat generation Effects 0.000 description 2
- 238000002347 injection Methods 0.000 description 2
- 239000007924 injection Substances 0.000 description 2
- 230000001050 lubricating effect Effects 0.000 description 2
- 239000000377 silicon dioxide Substances 0.000 description 2
- 229910018072 Al 2 O 3 Inorganic materials 0.000 description 1
- 229910000881 Cu alloy Inorganic materials 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 239000004809 Teflon Substances 0.000 description 1
- 229920006362 Teflon® Polymers 0.000 description 1
- 239000003570 air Substances 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 230000000052 comparative effect Effects 0.000 description 1
- 230000007797 corrosion Effects 0.000 description 1
- 238000005260 corrosion Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000005552 hardfacing Methods 0.000 description 1
- 238000007689 inspection Methods 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 150000004767 nitrides Chemical class 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 230000001681 protective effect Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/046—Bearings
- F04D29/047—Bearings hydrostatic; hydrodynamic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/046—Bearings
- F04D29/0465—Ceramic bearing designs
-
- 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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/043—Sliding surface consisting mainly of ceramics, cermets or hard carbon, e.g. diamond like carbon [DLC]
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Ceramic Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Sliding-Contact Bearings (AREA)
Description
本発明は、液体中及び気体中で使用される水中
軸受に関し、特に、起動時及び停止時等に気体中
におかれて無潤滑条件下で運転され、定常運転時
に水中又はスラリ中で運転される立軸ポンプ又は
斜軸ポンプに使用される水中軸受に関する。
従来、立軸ポンプ及び斜軸ポンプの水中軸受に
は、ゴム軸受、鉛青銅軸受等が使用されていた。
ところが、これらのポンプを起動する場合には、
水中軸受が気体中におかれていることが多く、そ
のままの状態で起動することは困難であつた。そ
の理由は、ゴム軸受も鉛青銅等の金属製軸受も、
水中或いは水や油でも潤滑された状態で使用され
る場合は極めて安定した摺動特性を示すが、気体
中、即ち無潤滑条件下で使用するときは、摺動部
から激しく発熱し、軸受部が速やかに破損される
からである。そのため、従来の立軸ポンプや斜軸
ポンプでは、起動時の無潤滑条件下の運転から水
中軸受を保護するため、軸受摺動部への潤滑油の
供給、或いは軸受部への注水等の手段が採用され
ていた。この軸受部への注水装置を第1図及び第
2図によつて説明する。
第1図は、軸受部へ注水する装置を設けた従来
の立軸ポンプの縦断面図であつて、1は外水位で
あり、この外水位1に水没する位置に羽根車2が
くるように立軸ポンプは設置されている。駆動用
モータ3は保守、点検が容易なように地上に設け
られ、該駆動用モータ3の回転は軸継手4を介し
て軸5,5′に伝達され、軸5′の先端部に接続さ
れた羽根車2を回転する。なお、6は軸5と軸
5′とを接続する中間軸継手である。羽根車2の
回転によつて、水は吸込みベル7から吸い込まれ
吐出しボウル8、吊下げ管9,10を通つて吐出
エルボ11から吐出される。12,13は、軸
5,5′を保護すると共に上部水中軸受14及び
下部水中軸受15へ潤滑水を導くための保護管で
ある。また上部水中軸受14は水中軸受支え16
によつて支持されており、下部水中軸受15はリ
ブ17,17′によつて支持されている。
第2図は、第1図A部の上部水中軸受14の拡
大断面図であつて、軸5′には、ステンレス製の
円筒状のスリーブ18が止めネジ18aによつて
固着されて該軸5′と一体に回転するようになつ
ており、また、水中軸受支え16には、ゴム軸受
19がスリーブ18の外周面と僅かの隙間をもつ
て固定されている。なお、このゴム軸受19の水
平断面の内周形状は円形であつて、通常、潤滑水
用の縦溝が数本設けられている。上記ゴム軸受1
9は、軸5,5′の回転によつて生じる該軸5,
5′の半径方向の振れを、スリーブ18の外周面
を該ゴム軸受19の内周面に摺接させることによ
つて制限している。
そして、第1図及び第2図に示される立軸ポン
プの起動時及び定常運転時には、上部に設けられ
た注水口20から、軸5,5′と保護管12,1
3との間に注水して、上部水中軸受14と下部水
中軸受15の2個の水中軸受を水で潤滑して保護
している。ところが、立軸ポンプでは軸5,5′
の長さが数10mにも及ぶことがあり、この場合に
は多数の水中軸受が用いられ、その間の軸を保護
管で保護している。従つて、ポンプ起動時におけ
る水中軸受の保護のために、多大の設備費を強い
られる欠点があつた。なお、以上の第1図及び第
2図の説明は立軸ポンプに関するものであるが、
斜軸ポンプにおいても、全く同様の問題があつ
た。
本発明の目的は、上記した従来技術の欠点を除
去することができ、液体中と気体中とで使用され
る水中軸受において、双方の使用条件において安
定した摺動特性をもち、しかも製作が容易な水中
軸受を提供することであり、特に、立軸ポンプ及
び斜軸ポンプの水中軸受として、ポンプ起動時に
水中軸受部が気体中におかれていて無潤滑条件下
で起動することが可能であり、起動後の定常運転
時においても良好な摺動特性を示し、しかも、清
水中のみならず海水のような良電導度液体やスラ
リ液中においても、安定した摺動特性を示す水中
軸受を提供するにある。
この目的を達成するために、本発明は、固定側
部材をタングステンカーバイド(WC)を含む超
硬合金で、また回転側部材を窒化珪素(Si3N4)
又は炭化珪素{SiC)のセラミツクスでそれぞれ
構成し、該セラミツクスをセグメント状に分割し
て回転側部材の周面に環状に配列して取り付けた
ことを特徴としている。
以下、本発明を実施例によつて詳しく説明す
る。
先ず、本発明の特徴の一つとする、水中軸受の
回転側及び固定側に使用される材料について説明
すると、立軸ポンプ又は斜軸ポンプ等に使用され
る従来の水中軸受における摺動部材の組合せとし
て、例えば、「ゴム軸受―ステンレス鋼製軸スリ
ーブ」或いは「カーボン含有テフロン(商標名)
軸受―ステンレス鋼軸スリーブ」等の場合にあつ
ては、清水中の摺動特性は優れているが、無潤滑
条件下においては全く使用できず、又「カーボン
軸受又はカーボン含有銅合金軸受―ステンレス鋼
軸スリーブ」の組合せにおいては、水中軸受部が
珪砂(砂)やアルミナ粒子を含むスラリ液によつ
て浸漬されると、摺動面ば速やかに損傷され、必
ずしも満足できるものではなかつた。
そこで本発明者等は、ラジアル軸受の摺動特性
を調べる試験装置及び保護管を具えない第4図に
示すような立軸ポンプを用い、さまざまな部材に
ついて清水条件、気体条件、スラリ条件、海水条
件或いはスラリを含む海水条件等のさまざまな使
用環境における摺動特性を調べ、前記のような本
発明の水中軸受に使用される材料が最も優れてい
ることを見い出した。前記摺動試験の結果得られ
たデータを第1表に示す。
The present invention relates to submersible bearings used in liquids and gases, and in particular, submersible bearings that are operated under non-lubricated conditions in gas during startup and shutdown, and in water or slurry during steady operation. This invention relates to submersible bearings used in vertical shaft pumps or oblique shaft pumps. Conventionally, rubber bearings, lead bronze bearings, and the like have been used as submersible bearings for vertical shaft pumps and oblique shaft pumps.
However, when starting these pumps,
Submersible bearings are often placed in gas, making it difficult to start them up as they are. The reason is that both rubber bearings and metal bearings such as lead bronze,
When used in water or when lubricated with water or oil, it exhibits extremely stable sliding characteristics, but when used in gas, that is, under unlubricated conditions, the sliding parts generate intense heat, causing damage to the bearing. This is because they are quickly damaged. Therefore, in conventional vertical shaft pumps and oblique shaft pumps, in order to protect the submersible bearings from operation under unlubricated conditions at startup, it is necessary to supply lubricating oil to the sliding parts of the bearings or inject water into the bearing parts, etc. He had been hired. This water injection device for the bearing will be explained with reference to FIGS. 1 and 2. FIG. 1 is a vertical cross-sectional view of a conventional vertical shaft pump equipped with a device for injecting water into the bearing part. 1 is the outside water level, and the vertical shaft is positioned so that the impeller 2 is submerged in the outside water level 1. Pumps are installed. The drive motor 3 is installed on the ground for easy maintenance and inspection, and the rotation of the drive motor 3 is transmitted to the shafts 5, 5' via a shaft coupling 4, and is connected to the tip of the shaft 5'. The impeller 2 rotates. Note that 6 is an intermediate shaft joint that connects the shaft 5 and the shaft 5'. As the impeller 2 rotates, water is sucked through the suction bell 7, passes through the discharge bowl 8, the hanging pipes 9 and 10, and is discharged from the discharge elbow 11. 12 and 13 are protection tubes for protecting the shafts 5 and 5' and guiding lubricating water to the upper underwater bearing 14 and the lower underwater bearing 15. In addition, the upper underwater bearing 14 is connected to the underwater bearing support 16.
The lower underwater bearing 15 is supported by ribs 17, 17'. FIG. 2 is an enlarged sectional view of the upper submersible bearing 14 in section A of FIG. A rubber bearing 19 is fixed to the underwater bearing support 16 with a slight gap between it and the outer peripheral surface of the sleeve 18. The inner periphery of the rubber bearing 19 in horizontal cross section is circular, and usually has several vertical grooves for lubricating water. Above rubber bearing 1
9 represents the rotation of the shafts 5, 5';
The radial deflection of the sleeve 18 is limited by sliding the outer circumferential surface of the sleeve 18 against the inner circumferential surface of the rubber bearing 19. When the vertical shaft pump shown in FIG. 1 and FIG.
3, and the two underwater bearings, the upper underwater bearing 14 and the lower underwater bearing 15, are lubricated and protected with water. However, in a vertical shaft pump, shafts 5 and 5'
The length of the bearing can reach several tens of meters, in which case many underwater bearings are used, and the shaft between them is protected by a protective tube. Therefore, there is a drawback that a large amount of equipment costs are required to protect the underwater bearing when the pump is started. Note that although the above explanation of FIGS. 1 and 2 relates to a vertical shaft pump,
Exactly the same problem occurred with diagonal shaft pumps. It is an object of the present invention to eliminate the drawbacks of the prior art described above, to provide a submersible bearing used in both liquid and gas, with stable sliding characteristics under both usage conditions, and to be easy to manufacture. In particular, as a submersible bearing for a vertical shaft pump and a diagonal shaft pump, the submersible bearing part is placed in gas when the pump is started, so that the submersible bearing can be started under non-lubricated conditions. To provide an underwater bearing that exhibits good sliding characteristics even during steady operation after startup, and also exhibits stable sliding characteristics not only in fresh water but also in liquids with good conductivity such as seawater and slurry liquid. It is in. In order to achieve this object, the present invention uses cemented carbide containing tungsten carbide (WC) for the stationary side member and silicon nitride (Si 3 N 4 ) for the rotating side member.
Alternatively, they are each made of silicon carbide (SiC) ceramics, and are characterized in that the ceramics are divided into segments and attached to the circumferential surface of the rotating side member in an annular arrangement. Hereinafter, the present invention will be explained in detail with reference to Examples. First, we will explain the materials used for the rotating and stationary sides of underwater bearings, which is one of the features of the present invention. , for example, "Rubber bearings - stainless steel shaft sleeves" or "Carbon-containing Teflon (trade name)"
In the case of "bearings - stainless steel shaft sleeves", the sliding properties in fresh water are excellent, but they cannot be used at all under non-lubricated conditions, and "carbon bearings or carbon-containing copper alloy bearings - stainless steel" In the combination of "steel shaft sleeve", when the underwater bearing part is immersed in a slurry liquid containing silica sand or alumina particles, the sliding surface is quickly damaged, and the result is not necessarily satisfactory. Therefore, the present inventors used a testing device to examine the sliding characteristics of radial bearings and a vertical pump as shown in Fig. 4 without a protection tube, and tested various parts under fresh water conditions, gas conditions, slurry conditions, and seawater conditions. Alternatively, we investigated the sliding characteristics in various usage environments such as seawater conditions containing slurry, and found that the material used in the underwater bearing of the present invention as described above is the most excellent. Table 1 shows the data obtained as a result of the sliding test.
【表】
ステンレス鋼……SuS304 ステンレス鋼
超硬合金……90%以上のWCを含有するJIS
5501 G種3号品
硬質肉盛材……35%のWCを含む
スラリー水……平均粒径80μ、最大粒径100μの
SiO2を0.3重量%含む水
スラリー−河川水……川砂0.3重量%+0.3重量
%Al2O3(max100μ av80μ)を含む水
海水+スラリー……av80μ、max100μのSiO2を
03重量%を含む海水
第1表中No.1,2が本発明の水中軸受の構成材
料であり、No.3〜9が従来の水中軸受材料の組合
せ及び比較試験のための水中軸受材料を組合せで
ある。
なお、評価の欄の記号は、それぞれ
◎……充分な耐久性がある(16000時間以上)
〇……実用上使用可能(8000時間以上)
△……条件により使用可能
×……使用不能
を意味し、摩擦係数、耐摩耗性、耐焼付性等の諸
因子を総合的に評価した結果を示すものである。
また第3図は、横軸に運転時間、縦軸に摩擦係
数をとつた軸受の摺動特性を示す線図であつて、
摺動速度2.5m/s、面圧ゴム軸受―ステンレス
鋼SUS304については6.3Kgf/cm2(×印の記号で
表わす)、窒化珪素セラミツクス軸受―超硬合金
(90%WC)については67Kgf/cm2(〇印の記号
で表わされた本発明1)、炭化珪素セラミツクス
軸受―超硬合金(90%WC)については67Kgf/
cm2(本発明2)及び42Kgf/cm2(本発明2′)をそ
れぞれとつている。
前記の第1表及び第3図から明らかなように、
本発明の水中軸受における固定側部材と回転側部
材を、それぞれ超硬合金(特にタングステンカー
バイドを含有)と窒化珪素セラミツクス又は炭化
珪素セラミツクスとした摺動面は、空気中、清水
中、或いは珪砂、アルミナ粒子を含むスラリ液中
においても極めて安定した摺動特性を示すもので
あることが分かる。
なお、本発明において回定側部材を構成する窒
化又は炭化珪素セラミツクスは、引張強度、もろ
さ、線膨脹率などの機械的性質から、できるだけ
取付け容易なしかも固定側の摺動面に用いられる
べきであり、したがつて固定側部材である軸受側
の摺動部材として用いるのが望ましく、もう一方
の超硬合金は、回転側部材である軸側の摺動部材
として用いるのが望ましい。また、第1表及び第
3図に示した試験において使用した超硬合金は、
JIS H5501G種3号に相当するものであるが、90
重量%以上のタングステンカーバイド(WC)を
含む超硬合金であれば、第1表及び第3図に示さ
れる良好で且つ安定した摺動特性を有するもので
ある。
次に、上記した軸受材料を用いた本発明の水中
軸受の実施例を、第4図ないし第6c図と共に説
明する。
第4図は、第1図に示した従来の立軸ポンプに
本発明の水中軸受を適用した場合の縦断面図であ
つて、第1図における保護管12,13、注水口
20と図示していない注水装置及び下部水中軸受
15を支えるリブ17等が不要となつたので設け
られておらず、極めて簡単な構造となつている。
しかも、上部及び下部の両水中軸受14,15
が、従来のものと比べて極めて小型になつている
ことが分かる。
上記のように、本発明を適用することによつて
水中軸受を小型にできる理由は、第3図からも明
らかなように、本発明の水中軸受材料は極めて高
い面圧荷重(従来の10倍以上)にも耐えることか
ら、摺動面積を小さくすることが可能になつたか
らである。
第5図は、第4図B部の水中軸受部の拡大断面
図であつて、軸5′には、タングステンカーバイ
ドを含んだ超硬合金製軸スリーブ21が、図示し
ない止めネジによつて固着されて一体に回転する
ようになつている。また水中軸受支え16には、
金属ケース22を介して、セグメント状に分割さ
れたセラミツクス製軸受23が取り付けられてお
り、これらセグメント状に分割された各セラミツ
クス片は、金属ケース22の内側に形成された嵌
合孔に嵌め込むようにして環状に配列され、各セ
ラミツクス片の内周面が軸スリーブ21の外周面
に線接触に近い状態になるようにして取り付けら
れている。なお、この取り付けは焼嵌め或いは接
着剤によつて行われ、各セラミツクス片は金属ケ
ース22に強固に固着される。
第6a図ないし第6c図は、第5図の―線
断面図であつて、各セグメント状が水中軸受支え
16の金属ケース22の内側に環状に配列されて
取り付けられている態様が明瞭に示されている。
すなわち、第6a図は、各セグメント片が断面
円形の棒状体23aで構成されている実施例を示
し、これらの断面円形のセグメント片23aは、
金属ケース22の内側に予め間隔を隔てて軸方向
に穿設された断面円弧状の貫通孔24a内に、軸
スリーブ21の外周面と摺動する部分を若干残し
て残部を焼嵌め或いは接着剤によつて固着されて
いる。
また第6b図は、各セグメント片が断面台形の
棒状体23bによつて構成された実施例を示し、
これらの各セグメント片23bは、金属ケース2
2の内側に間隔を隔てて軸方向に穿設された断面
台形(アリ溝形)の貫通孔24b内に焼嵌め或い
は接着剤によつて固着されている。
同様に第6c図は、各セグメント片が断面長方
形状の棒状体23cで構成された実施例を示し、
これらの各セグメント片23cは、金属ケース2
2の内側に間隔を隔てて軸方向に穿設された断面
長方形の貫通孔24c内に焼嵌め或いは接着剤に
よつて固着されており、軸スリーブ21の外周面
との摺接面は、断面円弧状に形成されている。
これらの第6a図ないし第6c図に示された各
実施例によれば、水中軸受支え16に金属ケース
22を介して取り付けられたセラミツクス製軸受
23を、セグメント状に分割して金属ケース22
の周面に環状に配列して取り付けているので、下
記のような作用、効果が奏されている。
() 各セラミツクス片と軸との接触が線接触
に近い状態にできるので、気中運転時の発熱を
低下できる。これは、接触面積が極めて小さく
そのため部分的な面圧が非常に高くなるので従
来の軸受材料では不可能であつたことであり、
本発明によつて初めて可能となつた。
() セグメント状に分割された各セラミツク
ス片間の比較的広い間隙にポンプ揚水が流れる
ため、取扱液中の異物が軸方向に流れ、摺動面
へのかみ込みが減少し、前記軸受構成材料と相
俟つて耐摩耗性が更に向上する。
() 大きな軸径用のセラミツク軸受を一体で
製作した場合、材質の不均一がおき易く、強度
的に信頼性に乏しいものになりがちであり、ま
たそのため高価なものになる。しかし本発明の
ようにセグメント状に分割することにより、セ
ラミツク単体としては小さなものですみ、大型
の軸受にも適用でき、信頼性を高めることがで
き、しかもコストを下げることができる。
なお、上記の効果の外、第6a図に示す実施例
においては、各セラミツクス片23aが断面円形
の棒状体に形成されているので、加工し易く、製
作が最も容易であり、各セラミツクス片が半径方
向内側へ向けてゆるむ恐れも全くない。同様に第
6b図に示す実施例においても、各セラミツクス
片がアリ溝形の孔に嵌合されているので、内側へ
向かつてゆるむ恐れはなく、該セラミツクス片の
固定方法(手段)に高技術、高信頼性が不要であ
り、また各セラミツクス片は底面が広くなつてい
るので、安定した支持が得られる効果がある。た
だ、溝及びセラミツクス片の加工並びにその必要
な寸法精度をだすのが形状的に難しい。第6c図
に示す実施例は、前記2例に対してセラミツクス
片が半径方向に離脱し易い形状になつているの
で、セラミツクス片の固定方法(手段)に高い信
頼性が必要であるが、接着剤にて固定する場合の
組立及び第6b図に比べて溝及びセラミツクス片
の加工が容易で、精度もだし易い。
以上は、立軸ポンプの水中軸受に本発明を適用
した例について述べたが、斜軸ポンプに適用した
場合についても同様の作用効果を奏するものであ
り、またその他の水力機械の水中軸受としても利
用できることは勿論である。
また、回転軸を固定側で支持するようにしたも
のにおける軸受装置であつて、液体中及び気体中
で使用される水中軸受に使用することも可能であ
り、この場合も、セラミツクスは、機械的性質等
の点から固定した軸側に設けられる。
なお、固定側部材を構成する超硬合金は、タン
グステンカーバイドを主成分にするものであれば
よいことは勿論である。
以上説明したように、本発明は、液体中及び気
体中で使用される水中軸受において、回転側部材
をタングステンカーバイドからなる超硬合金で、
また固定側部材を窒化珪素又は炭化珪素のセラミ
ツクスでそれぞれ構成し、該セラミツクスをセグ
メント状に分割して固定側部材の周面に環状に配
列して取り付けるようにして構成しているので、
従来の水中軸受では不可能であつた無潤滑条件下
の始動、即ち気体中において摺動する場合でも極
めて安定した摺動特性を有し、水潤滑がなされて
いる条件下では勿論のこと、珪砂やアルミナ微粒
子からなるスラリ水中で摺動する場合でも良好な
摺動特性を維持するので、無潤滑状態と潤滑状態
とが繰り返えし出現する条件下、或いは摩耗性取
扱い液中で作動させるのに好適であり、また前記
両セラミツクスは良絶縁性を有するので、良電導
度液中で作動する摺動部材として用いれば、腐食
電流を遮断して周囲におかれた金属部材を保護す
ることにもなる。更に、高い面圧荷重にも耐える
ことから、セラミツクスをセグメント状の分割し
て軸との接触を線接触に近い状態にできるので、
気中運転時の発熱を低下でき、また分割された各
セラミツクス片の間隙が取扱液中の異物の通路と
して利用できるので、それだけ摺動面が保護され
て耐摩耗性が向上するばかりでなく、セラミツク
スを分割しているので、容易に大形の軸受にも適
用でき、またセラミツクスを一体成形で製作する
必要がなくコスト的にも安価となる等の効果を有
する。[Table] Stainless steel...SuS304 Stainless steel cemented carbide...JIS containing 90% or more WC
5501 G class No. 3 hardfacing material...Slurry water containing 35% WC...average particle size 80μ, maximum particle size 100μ
Water slurry containing 0.3% by weight of SiO 2 - River water... Water containing 0.3% by weight of river sand + 0.3% by weight Al 2 O 3 (max 100μ av80μ) Seawater + slurry...SiO 2 with av80μ, max 100μ
03% by weight of seawater In Table 1, Nos. 1 and 2 are the constituent materials of the underwater bearing of the present invention, and Nos. 3 to 9 are the combinations of conventional underwater bearing materials and underwater bearing materials for comparative tests. It's a combination. The symbols in the evaluation column are as follows: ◎...Sufficient durability (16,000 hours or more) 〇...Can be used for practical purposes (8,000 hours or more) △...Can be used depending on conditions ×...Cannot be used It shows the results of a comprehensive evaluation of various factors such as friction coefficient, wear resistance, and seizure resistance. FIG. 3 is a diagram showing the sliding characteristics of the bearing, with the horizontal axis representing the operating time and the vertical axis representing the friction coefficient.
Sliding speed 2.5 m/s, surface pressure rubber bearing - 6.3 Kgf/cm 2 (represented by the symbol x) for stainless steel SUS304, 67 Kgf/cm for silicon nitride ceramic bearing - cemented carbide (90% WC) 2 (Invention 1 represented by the symbol 〇), silicon carbide ceramic bearings - 67Kgf/ for cemented carbide (90% WC)
cm 2 (invention 2) and 42Kgf/cm 2 (invention 2'), respectively. As is clear from Table 1 and Figure 3 above,
In the underwater bearing of the present invention, the stationary side member and the rotating side member are respectively made of cemented carbide (containing tungsten carbide) and silicon nitride ceramics or silicon carbide ceramics, and the sliding surfaces can be in air, fresh water, silica sand, It can be seen that it exhibits extremely stable sliding characteristics even in slurry liquid containing alumina particles. In addition, in the present invention, the nitride or silicon carbide ceramics constituting the rotation side member should be as easy to install as possible and should be used for the fixed side sliding surface due to its mechanical properties such as tensile strength, fragility, and coefficient of linear expansion. Therefore, it is desirable to use it as a sliding member on the bearing side, which is a fixed side member, and it is desirable to use the other cemented carbide as a sliding member on the shaft side, which is a rotating side member. In addition, the cemented carbide used in the tests shown in Table 1 and Figure 3 was
It is equivalent to JIS H5501G type No. 3, but 90
A cemented carbide containing tungsten carbide (WC) in a weight percent or more has good and stable sliding properties as shown in Table 1 and FIG. 3. Next, an embodiment of the underwater bearing of the present invention using the above-mentioned bearing material will be described with reference to FIGS. 4 to 6c. FIG. 4 is a longitudinal cross-sectional view of the conventional vertical shaft pump shown in FIG. 1 to which the submersible bearing of the present invention is applied. Since the water injection device and the rib 17 supporting the lower underwater bearing 15 are no longer necessary, they are not provided, resulting in an extremely simple structure.
Moreover, both the upper and lower underwater bearings 14, 15
However, it can be seen that it is much smaller than the conventional one. As mentioned above, the reason why underwater bearings can be made smaller by applying the present invention is that, as is clear from FIG. This is because it can withstand the above), making it possible to reduce the sliding area. FIG. 5 is an enlarged cross-sectional view of the underwater bearing part in part B of FIG. It is designed to rotate as a unit. In addition, the underwater bearing support 16 includes
A ceramic bearing 23 divided into segments is attached through the metal case 22, and each of the ceramic pieces divided into segments is fitted into a fitting hole formed inside the metal case 22. The ceramic pieces are arranged in an annular shape so that the inner circumferential surface of each ceramic piece is in close to line contact with the outer circumferential surface of the shaft sleeve 21. Note that this attachment is performed by shrink fitting or adhesive, and each ceramic piece is firmly fixed to the metal case 22. 6a to 6c are cross-sectional views taken along the line -- in FIG. 5, and clearly show how the segments are arranged and attached to the inside of the metal case 22 of the underwater bearing support 16 in an annular manner. has been done. That is, FIG. 6a shows an embodiment in which each segment piece is constituted by a rod-shaped body 23a having a circular cross section, and these segment pieces 23a having a circular cross section are as follows.
A through hole 24a having an arc-shaped cross section is drilled in the axial direction at predetermined intervals inside the metal case 22, and a portion that slides on the outer peripheral surface of the shaft sleeve 21 is left slightly, and the remaining portion is shrink-fitted or glued. It is fixed by. Further, FIG. 6b shows an embodiment in which each segment piece is constituted by a rod-shaped body 23b having a trapezoidal cross section,
Each of these segment pieces 23b is attached to the metal case 2.
It is fixed by shrink-fitting or adhesive into a through-hole 24b having a trapezoidal cross section (dovetail groove shape) which is bored in the axial direction at intervals inside the holder 2. Similarly, FIG. 6c shows an embodiment in which each segment piece is composed of a rod-shaped body 23c having a rectangular cross section,
Each of these segment pieces 23c is attached to the metal case 2.
It is fixed by shrink-fitting or adhesive into through-holes 24c having a rectangular cross section that are bored in the axial direction at intervals inside the shaft sleeve 21, and the sliding surface with the outer peripheral surface of the shaft sleeve 21 has a rectangular cross section. It is formed in an arc shape. According to each of the embodiments shown in FIGS. 6a to 6c, the ceramic bearing 23 attached to the underwater bearing support 16 via the metal case 22 is divided into segments and the metal case 22 is divided into segments.
Since they are arranged and attached in an annular manner around the circumferential surface, the following functions and effects are achieved. () Since the contact between each ceramic piece and the shaft can be made to be close to line contact, heat generation during air operation can be reduced. This was not possible with conventional bearing materials because the contact area was extremely small and the local surface pressure was extremely high.
This was made possible for the first time by the present invention. () Since the pumped water flows through the relatively wide gaps between the ceramic pieces divided into segments, foreign matter in the handled liquid flows in the axial direction, reducing the amount of foreign matter caught in the sliding surface, and reducing the amount of the bearing constituent material. Combined with this, wear resistance is further improved. () When ceramic bearings for large shaft diameters are manufactured in one piece, the material tends to be non-uniform, resulting in poor strength and reliability, and as a result, it becomes expensive. However, by dividing the ceramic into segments as in the present invention, the ceramic itself can be small and can be applied to large bearings, improving reliability and reducing costs. In addition to the above effects, in the embodiment shown in FIG. 6a, since each ceramic piece 23a is formed into a rod-shaped body with a circular cross section, it is easy to process and manufacture. There is no fear of it loosening inward in the radial direction. Similarly, in the embodiment shown in FIG. 6b, each ceramic piece is fitted into a dovetail hole, so there is no risk of it loosening inwardly, and the method (means) for fixing the ceramic piece is made using a high technology. , high reliability is not required, and since each ceramic piece has a wide bottom surface, it has the effect of providing stable support. However, it is difficult to process the grooves and ceramic pieces and achieve the required dimensional accuracy due to their shape. The embodiment shown in FIG. 6c has a shape in which the ceramic pieces are easily separated in the radial direction compared to the above two examples, so the method (means) for fixing the ceramic pieces needs to be highly reliable. It is easier to assemble and process the grooves and ceramic pieces than in FIG. 6b when fixing with adhesive, and it is also easier to achieve accuracy. The above describes an example in which the present invention is applied to a submersible bearing of a vertical shaft pump, but the same effect can be achieved when applied to a diagonal shaft pump, and the invention can also be used as a submersible bearing of other hydraulic machines. Of course it can be done. In addition, it is a bearing device in which the rotating shaft is supported on the fixed side, and it can also be used as an underwater bearing used in liquid or gas. It is installed on the fixed shaft side due to its properties. It goes without saying that the cemented carbide constituting the stationary side member may be one containing tungsten carbide as a main component. As explained above, the present invention provides an underwater bearing used in liquid and gas, in which the rotating side member is made of a cemented carbide made of tungsten carbide.
Furthermore, the fixed side member is made of ceramics such as silicon nitride or silicon carbide, and the ceramics are divided into segments and arranged and attached in an annular manner on the circumferential surface of the fixed side member.
It has extremely stable sliding characteristics even when starting under non-lubricated conditions, that is, sliding in gas, which was impossible with conventional underwater bearings, and it has extremely stable sliding characteristics even under water-lubricated conditions. It maintains good sliding characteristics even when sliding in slurry water made of aluminum and fine alumina particles, so it can be operated under conditions where unlubricated and lubricated conditions repeatedly occur or in abrasive handling fluids. Furthermore, since both ceramics have good insulating properties, if used as a sliding member that operates in a liquid with good conductivity, they can cut off corrosion current and protect surrounding metal members. It will also happen. Furthermore, since it can withstand high surface pressure loads, it is possible to divide the ceramic into segments and make the contact with the shaft close to a line contact.
Heat generation during air operation can be reduced, and the gaps between the divided ceramic pieces can be used as passages for foreign matter in the liquid being handled, which not only protects the sliding surfaces and improves wear resistance, but also Since the ceramic is divided, it can be easily applied to large-sized bearings, and there is no need to manufacture the ceramic by integral molding, resulting in lower costs.
第1図は従来の立軸ポンプの縦断面図、第2図
は第1図A部の拡大断面図、第3図は軸受の摺動
特性を示す線図、第4図は本発明の一実施例の水
中軸受を適用した立軸ポンプの縦断面図、第5図
は第4図B部の拡大断面図、第6a図ないし第6
c図は第5図の―線断面図で異なる実施例を
示す。
5′…回転軸、16…軸受支え、21…軸スリ
ーブ、23…セラミツクス、23a,23b,2
3c…セラミツクス片。
Fig. 1 is a longitudinal sectional view of a conventional vertical shaft pump, Fig. 2 is an enlarged sectional view of section A in Fig. 1, Fig. 3 is a diagram showing the sliding characteristics of a bearing, and Fig. 4 is an embodiment of the present invention. A vertical cross-sectional view of a vertical shaft pump to which the submersible bearing of the example is applied, FIG. 5 is an enlarged cross-sectional view of part B in FIG.
Figure c is a sectional view taken along the line -- in Figure 5 and shows a different embodiment. 5'...Rotating shaft, 16...Bearing support, 21...Shaft sleeve, 23...Ceramics, 23a, 23b, 2
3c...Ceramics piece.
Claims (1)
いて、回転側部材をタングステンカーバイド
(WC)を含む超硬合金で、また固定側部材を窒
化珪素(Si3N4)又は炭化珪素(SiC)のセラミ
ツクスでそれぞれ構成し、該セラミツクスをセグ
メント状に分割して固定側部材の周面に環状に配
列して取り付けたことを特徴とする水中軸受。 2 セグメント状に分割された各セラミツクス片
は、金属ケースに設けた嵌合孔に固定され、該金
属ケースの外周部は軸受支えで支持されている特
許請求の範囲第1項記載の水中軸受。 3 セグメント状に分割された各セラミツクス片
が、断面円形に形成されている特許請求の範囲第
1項記載の水中軸受。 4 セグメント状に分割された各セラミツクス片
が、断面台形に形成されている特許請求の範囲第
1項記載の水中軸受。 5 セグメント状に分割された各セラミツクス片
が、断面長方形状に形成されている特許請求の範
囲第1項記載の水中軸受。[Claims] 1. In an underwater bearing used in liquid and gas, the rotating side member is made of cemented carbide containing tungsten carbide (WC), and the stationary side member is made of silicon nitride (Si 3 N 4 ) or What is claimed is: 1. An underwater bearing comprising a silicon carbide (SiC) ceramic, the ceramic being divided into segments and arranged in an annular manner on the circumferential surface of a stationary member. 2. The underwater bearing according to claim 1, wherein each ceramic piece divided into segments is fixed to a fitting hole provided in a metal case, and the outer circumference of the metal case is supported by a bearing support. 3. The underwater bearing according to claim 1, wherein each ceramic piece divided into segments has a circular cross section. 4. The underwater bearing according to claim 1, wherein each of the ceramic pieces divided into segments has a trapezoidal cross section. 5. The underwater bearing according to claim 1, wherein each ceramic piece divided into segments has a rectangular cross section.
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP18684383A JPS6081517A (en) | 1983-10-07 | 1983-10-07 | Submersible bearing |
AU32968/84A AU579834B2 (en) | 1983-09-30 | 1984-09-12 | Combination of slide members |
US06/651,039 US4664595A (en) | 1983-09-30 | 1984-09-14 | Combination of slide members |
DE3435821A DE3435821C2 (en) | 1983-09-30 | 1984-09-28 | Bearing for a pump |
KR1019840006058A KR930002055B1 (en) | 1983-09-30 | 1984-09-29 | Active part combined structure of bearing |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP18684383A JPS6081517A (en) | 1983-10-07 | 1983-10-07 | Submersible bearing |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS6081517A JPS6081517A (en) | 1985-05-09 |
JPS6349086B2 true JPS6349086B2 (en) | 1988-10-03 |
Family
ID=16195602
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP18684383A Granted JPS6081517A (en) | 1983-09-30 | 1983-10-07 | Submersible bearing |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS6081517A (en) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6084423A (en) * | 1983-10-17 | 1985-05-13 | Ebara Corp | Sliding bearing |
JPH028100Y2 (en) * | 1985-06-24 | 1990-02-27 | ||
JPH028099Y2 (en) * | 1985-06-24 | 1990-02-27 | ||
JPH0211609Y2 (en) * | 1985-06-24 | 1990-03-27 | ||
JPS62107294A (en) * | 1985-11-05 | 1987-05-18 | Ebara Corp | Single suction type multi-stage volute pump |
JPH048797U (en) * | 1990-05-11 | 1992-01-27 | ||
JP3627614B2 (en) * | 1992-03-18 | 2005-03-09 | 株式会社日立製作所 | Drainage pump |
EP0561391B1 (en) * | 1992-03-18 | 1998-06-24 | Hitachi, Ltd. | Bearing unit, drainage pump and hydraulic turbine each incorporating the bearing unit, and method of manufacturing the bearing unit |
JP6472735B2 (en) * | 2015-09-25 | 2019-02-20 | 株式会社荏原製作所 | Slide bearing device |
-
1983
- 1983-10-07 JP JP18684383A patent/JPS6081517A/en active Granted
Also Published As
Publication number | Publication date |
---|---|
JPS6081517A (en) | 1985-05-09 |
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