JPS6240156Y2 - - Google Patents
Info
- Publication number
- JPS6240156Y2 JPS6240156Y2 JP1980085211U JP8521180U JPS6240156Y2 JP S6240156 Y2 JPS6240156 Y2 JP S6240156Y2 JP 1980085211 U JP1980085211 U JP 1980085211U JP 8521180 U JP8521180 U JP 8521180U JP S6240156 Y2 JPS6240156 Y2 JP S6240156Y2
- Authority
- JP
- Japan
- Prior art keywords
- casing
- pressure
- conduction
- stage
- flange
- 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
- 230000013011 mating Effects 0.000 claims description 15
- 239000012530 fluid Substances 0.000 description 14
- 230000007547 defect Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 238000007789 sealing Methods 0.000 description 4
- 238000005266 casting Methods 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- 238000003754 machining Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000012856 packing Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 231100000331 toxic Toxicity 0.000 description 1
- 230000002588 toxic effect Effects 0.000 description 1
Landscapes
- Details Of Reciprocating Pumps (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Compressor (AREA)
Description
【考案の詳細な説明】
本考案は多段ポンプや多段圧縮機の分割型のケ
ーシングに関するものである。[Detailed Description of the Invention] The present invention relates to a split-type casing for a multistage pump or a multistage compressor.
有毒性あるいは引火性流体を扱う機械からの漏
れ量はきびしく制限されることが多い。ポンプや
送風機、圧縮機においても、扱う流体が高温、高
圧あるいは侵蝕性が強い等のために、信頼できる
パツキン材を選定することが困難なことも少なく
なく、このような場合には金属の直接接触による
シールが行われることが多い。 Leakage rates from machines that handle toxic or flammable fluids are often severely limited. In pumps, blowers, and compressors, it is often difficult to select reliable packing materials because the fluids handled are high temperature, high pressure, or highly corrosive. Sealing by contact is often performed.
一般に金属面の直接々触によるシールを確実に
行うためには、合わせ面フランジの剛性、合わせ
面の接触圧力、合わせ面の加工精度の３つを著る
しく高くする必要がある。従つてケーシングのフ
ランジ部は胴部に比べて著るしく厚くすることが
多い。かかる必要性は特にターボ型多段ポンプや
圧縮機の上下二つ割型のケーシングにおいて強
い。ケーシングのフランジ面を著るしく厚くする
ことは経済的にも得策ではなく、鋳造欠陥や溶接
欠陥を増加させる等の不都合も生じてくる。ま
た、扱う流体が高温または低温のときには熱変形
が大きく影響するので、ケーシング合わせ面フラ
ンジを厚くしてもその効果はその割には期待しえ
ない。 In general, in order to reliably achieve sealing by direct contact between metal surfaces, it is necessary to significantly increase the rigidity of the mating surface flange, the contact pressure of the mating surface, and the machining accuracy of the mating surface. Therefore, the flange portion of the casing is often made significantly thicker than the body portion. This necessity is particularly strong in the case of a turbo-type multistage pump or a compressor, which has a casing that is divided into upper and lower halves. It is not economically advisable to significantly thicken the flange surface of the casing, and it also causes disadvantages such as an increase in casting defects and welding defects. Further, when the fluid to be handled is at a high or low temperature, thermal deformation has a large effect, so even if the casing mating surface flange is made thicker, the effect cannot be expected.
本考案は、従来のものの上記の欠点を除き、ケ
ーシング外部への流体の洩れを防止することがで
きる多段ポンプや多段圧縮機のケーシングを提供
することを目的とするものである。 SUMMARY OF THE INVENTION An object of the present invention is to provide a casing for a multistage pump or a multistage compressor that eliminates the above-mentioned drawbacks of the conventional casing and can prevent fluid from leaking to the outside of the casing.
本考案は、多段ポンプの分割型のケーシングに
おいて、分割面のフランジの合わせ面に低圧部と
導通する導通溝を複数本多重に設け、該複数本の
導通溝は内側にあるものよりも外側にあるものの
方が順次、より低圧部に導通していることを特徴
とする多段ポンプのケーシングである。 The present invention provides a split casing for a multi-stage pump, in which a plurality of conduction grooves are provided on the mating surfaces of the flanges of the divided surfaces to communicate with the low-pressure part, and the plurality of conduction grooves are located on the outside rather than on the inside. This is a multi-stage pump casing characterized in that some parts are connected to lower pressure parts in sequence.
なお、多段ポンプには多段圧縮機も含むもので
ある。 Note that the multistage pump also includes a multistage compressor.
本考案を実施例につき、図面を用いて説明す
る。 The present invention will be described with reference to embodiments and drawings.
第１図は通常の上下分割型多段ターボ圧縮機の
水平断面図であり、本例は５段圧縮機の場合であ
る。１は主軸、２は羽根車、３はシール部、４は
軸受部、５は下ケーシングである。下ケーシング
の周辺部はフランジ１１（第４図も参照）となつ
ており、この部分が上ケーシングのフランジとの
合せ面となる。従つて、フランジ１１には上ケー
シングを固定するためのネジ６が多数設けられて
いる。７は吸込みボリユート、８は吐出しボリユ
ート、９はデイフユーザリターン部、１０は平衡
室である。 FIG. 1 is a horizontal sectional view of a normal upper and lower split type multi-stage turbo compressor, and this example shows a case of a 5-stage compressor. 1 is a main shaft, 2 is an impeller, 3 is a seal portion, 4 is a bearing portion, and 5 is a lower casing. The peripheral part of the lower casing is a flange 11 (see also FIG. 4), and this part becomes the mating surface with the flange of the upper casing. Therefore, the flange 11 is provided with a large number of screws 6 for fixing the upper casing. 7 is a suction volute, 8 is a discharge volute, 9 is a differential user return section, and 10 is an equilibrium chamber.
ケーシング内の圧力は吸込ボリユート７と平衡
室１０の圧力が最も低く、デイフユーザリターン
部の圧力は吸込ボリユート７の圧力より高く、か
つ後段のデイフユーザリターン部ほど圧力が高
い。そして、吐出しボリユート８の圧力が最も高
い。一般には、ケーシングの外は大気圧であるか
ら、吐出しボリユート８および後段側デイフユー
ザリターン部の付近ではケーシング合わせ面フラ
ンジ１１の内側と外側の圧力差が高くなり、合わ
せ面フランジ１１部のシールの困難さが増してく
る。 The pressure inside the casing is the lowest in the suction volute 7 and the equilibrium chamber 10, the pressure in the differential user return section is higher than the pressure in the suction volute 7, and the pressure is higher in the later stages of the differential user return section. The pressure of the discharge volute 8 is the highest. Generally, the outside of the casing is at atmospheric pressure, so the pressure difference between the inside and outside of the casing mating flange 11 becomes high in the vicinity of the discharge volute 8 and the downstream differential user return section. The difficulty of sealing increases.
第２図は本考案の実施例を示し、合わせ面に３
本の導通溝１２，１３，１４が設けられている。 Figure 2 shows an embodiment of the present invention, in which 3
Book conduction grooves 12, 13, and 14 are provided.
最も内側の導通溝１４は、最終段である５段目
の羽根車２のまわりから、中間段である３段目の
デイフユーザリターン部９の外側に設けてあり、
３段目デイフユーザリターン部９に導通されてい
る。中間の導通溝１３は、吸込みボリユート７と
平衡室１０との間に設けてあり、吸込みボリユー
ト７と平衡室１０との両方に導通している。最外
周の導通溝１２は、両側のシール部３のまわりを
含めてケーシングの合わせ面のフランジ１１のほ
とんど全周に設けてあり、途中少なくとも一箇所
で、第３図に示す如く溝１５，キリ穴１６，ネジ
穴１７を介してケーシングの外部と導通させ得る
ようになつている。 The innermost conduction groove 14 is provided from around the impeller 2 of the fifth stage, which is the final stage, to the outside of the differential user return part 9 of the third stage, which is the intermediate stage.
It is electrically connected to the third stage differential user return section 9. The intermediate conduction groove 13 is provided between the suction volute 7 and the balance chamber 10 and is electrically connected to both the suction volute 7 and the balance chamber 10 . The outermost conductive groove 12 is provided around the entire circumference of the flange 11 on the mating surface of the casing, including around the seal portions 3 on both sides, and at least one place along the way is provided with a groove 15 and a cutout as shown in FIG. The casing can be electrically connected to the outside through the hole 16 and the screw hole 17.
このネジ穴１７は、例えば、この多段ターボ圧
縮機の吸込み配管の途中に前置されるブースタ送
風機の吸込口に接続される。ブースタ送風機の吸
込口の圧力は、多段ターボ圧縮機の吸込口の圧力
よりも低い。ブースタ送風機が設けられない場
合、その他本体圧縮機の吸込口より低圧の部分が
ない系においては、この最も外側の導通溝１２は
設けない。 This screw hole 17 is connected, for example, to a suction port of a booster blower placed in the middle of the suction piping of this multistage turbo compressor. The pressure at the inlet of the booster blower is lower than the pressure at the inlet of the multi-stage turbo compressor. In the case where a booster blower is not provided, or in a system where there is no other part having a lower pressure than the suction port of the main body compressor, this outermost conduction groove 12 is not provided.
第３図及び第４図に示す拡大図において、導通
溝１４，１３，１２の幅b1，b2，b3及び深さd1，
d2，d3はフランジ１１の剛性を著しく低下させな
い範囲で、導通溝１４，１３，１２に漏れ出た流
体をスムーズに低圧部に流出され得るよう設定す
る。さらに導通溝１４，１３，１２とケーシング
内面又は相互の間隔１，２，３は、それぞ
れの導通溝１４，１３，１２への漏れ量が、各溝
に沿つてスムーズに低圧部に流出させ得る範囲内
に納まるよう設定する。従つてこれらの寸法に対
する適正値は、一義的なものではなく、ケーシン
グ内の圧力分布、合わせ面のフランジ１１の厚
さ，幅，締め付け圧力、締め付けボルトのピツチ
などによつて異つてくる。ただし、ケーシングの
内周と締め付けボルトの中心線との間隔０が一
般的な寸法ｔ＋（1.0〜1.5）d0〔ここにｔは胴部
の厚さ、d0は締めつけボルトの径〕より大きくな
ると、締めつけ力がケーシングの内周部に有効に
働かないことや、フランジ１１部の重量が増大す
るなどのために効果が消失するので導通溝１２，
１３，１４は、その必要な本数をｔ＋（1.0〜
1.5）d0の範囲に設ける。なお導通溝１２，１
３，１４は、上ケーシングまたは下ケーシングの
いずれか一方に設ければよいが、各溝の断面積を
大きくするために上，下両ケーシングに設けるこ
とも可能である。 In the enlarged views shown in FIGS. 3 and 4, the widths b 1 , b 2 , b 3 and depths d 1 ,
d 2 and d 3 are set within a range that does not significantly reduce the rigidity of the flange 11 so that fluid leaking into the conduction grooves 14, 13, 12 can smoothly flow out to the low pressure section. Furthermore, the distances 1 , 2 , and 3 between the conduction grooves 14, 13, and 12 and the inner surface of the casing or each other allow the amount of leakage into each of the conduction grooves 14, 13, and 12 to smoothly flow out to the low-pressure part along each groove. Set it to stay within the range. Therefore, the appropriate values for these dimensions are not unique and vary depending on the pressure distribution within the casing, the thickness and width of the flange 11 on the mating surface, the tightening pressure, the pitch of the tightening bolts, etc. However, the distance 0 between the inner circumference of the casing and the center line of the tightening bolt is larger than the general dimension t + (1.0 to 1.5) d 0 [where t is the thickness of the body and d 0 is the diameter of the tightening bolt]. In this case, the effect is lost because the tightening force does not work effectively on the inner circumference of the casing and the weight of the flange 11 increases, so the conduction groove 12,
13 and 14, the required number is t + (1.0 ~
1.5) Set in the range of d 0 . Note that the conduction grooves 12, 1
3 and 14 may be provided on either the upper casing or the lower casing, but it is also possible to provide them on both the upper and lower casings in order to increase the cross-sectional area of each groove.
第２図の例において、吐出しボリユート８，お
よび後段側デイフユーザリターン部等高圧部から
ケーシング合わせ面に流体が侵入した場合，流体
は最内周の導通溝１４に到達するが、導通溝１４
は中圧段（本例では３段目）のデイフユーザリタ
ーン部９に導通しているので、導通溝１４に達し
た流体は中圧段のデイフユーザリターン部９に放
出され、導通溝１４内の圧力はほぼ中圧段のデイ
フユーザリターン部９の圧力と同じになる。導通
溝１４から更にフランジ１１の外周側に侵入した
流体および中圧段のデイフユーザリターン部から
直接フランジ１１面に侵入した流体は中間の導通
溝１３に到達し、吸込みボリユート７、または平
衡室１０に導かれる。従つて、導通溝１３の圧力
はほぼ吸込圧に等しくなる。更に、導通溝１３、
または吸込ボリユート７の周辺および軸受部４の
まわりから、流体が合わせ面に侵入しても最外周
の導通溝１２を介して、より低圧部であるブース
タ送風機の吸込口に戻され、導通溝１２の圧力は
一般に、低圧のため、シーが容易である、ブース
タ送風機の吸込圧力にほぼ等しくなる。従つて、
本圧縮機のケーシング合わせ面から直接外部への
漏出は著しく少なくなるかあるいは皆無にでき
る。 In the example shown in Fig. 2, when fluid enters the casing mating surface from high pressure parts such as the discharge volute 8 and the rear differential user return part, the fluid reaches the innermost conduction groove 14, but the conduction groove 14
is electrically connected to the differential user return section 9 of the intermediate pressure stage (the third stage in this example), so the fluid that has reached the conduction groove 14 is discharged to the differential user return section 9 of the intermediate pressure stage, and the fluid that has reached the conduction groove 14 is discharged to the differential user return section 9 of the intermediate pressure stage. The pressure inside 14 becomes approximately the same as the pressure in the differential user return section 9 of the intermediate pressure stage. The fluid that has entered the outer circumferential side of the flange 11 through the conduction groove 14 and the fluid that has entered directly into the flange 11 surface from the differential user return section of the intermediate pressure stage reach the intermediate conduction groove 13 and flow into the suction volute 7 or the equilibrium chamber. Guided by 10. Therefore, the pressure in the conduction groove 13 becomes approximately equal to the suction pressure. Furthermore, the conduction groove 13,
Alternatively, even if fluid enters the mating surface from around the suction volute 7 and around the bearing part 4, it is returned to the suction port of the booster blower, which is a lower pressure part, through the outermost conduction groove 12. The pressure will generally be approximately equal to the booster blower suction pressure, which is easy to see due to its low pressure. Therefore,
Leakage directly to the outside from the casing mating surfaces of this compressor can be significantly reduced or eliminated.
本考案は、合わせ面に、外側にある導通溝を内
側にあるものよりも、順次、より低圧部に導通し
て、複数本の導通溝を設けたので、漏洩流体は順
次減圧されて密封されることとなる。従つて導通
溝１本あたりのシール差圧を小さくとることがで
き、シール性も良い状態で合わせ面からの流体の
漏出を防止し、しかもフランジの厚さを薄くし、
締付ボルトの締付力を低減せしめ、重量の軽減、
鋳造欠陥や溶接欠陥の未然の防止、熱変形の防止
などをはかることを可能とする多段ポンプや多段
圧縮機のケーシングを提供することができ、実用
上極めて大なる効果を有するものである。 In the present invention, a plurality of conduction grooves are provided on the mating surfaces by sequentially connecting the conduction grooves on the outside to lower pressure areas than the ones on the inside, so that the leakage fluid is sequentially depressurized and sealed. The Rukoto. Therefore, the seal differential pressure per conduction groove can be kept small, the sealing performance is good, and fluid leakage from the mating surfaces is prevented, and the thickness of the flange can be made thinner.
Reduces the tightening force of tightening bolts, reduces weight,
It is possible to provide a casing for a multistage pump or a multistage compressor that can prevent casting defects, welding defects, thermal deformation, etc., and has extremely large practical effects.
第１図は上下分割型多段ターボ圧縮機の水平断
面の平面図、第２図は本考案の実施例の平面図、
第３図は第２図のＡ部詳細図、第４図はその−
線断面図である。
１……主軸、２……羽根車、３……シール部、
４……軸受部、５……下ケーシング部、６……ネ
ジ、７……吸込みボリユート、８……吐出しボリ
ユート、９……デイフユーザリターン部、１０…
…平衡室、１１……フランジ、１２，１３，１４
……導通溝、１５……溝、１６……キリ穴、１７
……ネジ穴。
Fig. 1 is a horizontal cross-sectional plan view of an upper and lower split type multi-stage turbo compressor, Fig. 2 is a plan view of an embodiment of the present invention,
Figure 3 is a detailed view of part A in Figure 2, and Figure 4 is its -
FIG. 1... Main shaft, 2... Impeller, 3... Seal part,
4... Bearing part, 5... Lower casing part, 6... Screw, 7... Suction volute, 8... Discharge volute, 9... Differential user return part, 10...
...Equilibrium chamber, 11...Flange, 12, 13, 14
...Conduction groove, 15...Groove, 16...Drill hole, 17
...screw hole.
Claims (1)
割面のフランジの合わせ面に低圧部と導通する導
通溝を複数本多重に設け、該複数本の導通溝は内
側にあるものよりも外側にあるものの方が順次、
より低圧部に導通していることを特徴とする多段
ポンプのケーシング。 In a split-type casing of a multi-stage pump, a plurality of conduction grooves are provided on the mating surfaces of the flanges of the divided surfaces to communicate with the low-pressure part, and the conduction grooves on the outside are larger than those on the inside. Sequentially,
A multi-stage pump casing characterized by electrical conduction to a lower pressure section.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1980085211U JPS6240156Y2 (en) | 1980-06-18 | 1980-06-18 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1980085211U JPS6240156Y2 (en) | 1980-06-18 | 1980-06-18 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS578989U JPS578989U (en) | 1982-01-18 |
| JPS6240156Y2 true JPS6240156Y2 (en) | 1987-10-14 |
Family
ID=29447479
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1980085211U Expired JPS6240156Y2 (en) | 1980-06-18 | 1980-06-18 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6240156Y2 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60121030A (en) * | 1983-12-05 | 1985-06-28 | Toraji Mochizuki | Method of forming end of metallic tube to u-shaped articulated body |
| JPS6098782U (en) * | 1983-12-12 | 1985-07-05 | 株式会社ボッシュオートモーティブ システム | vane compressor |
| JP5618558B2 (en) * | 2009-02-18 | 2014-11-05 | 株式会社クボタ | How to use a double suction centrifugal pump and a double suction centrifugal pump |
| KR101315358B1 (en) * | 2011-11-23 | 2013-10-08 | 윤용길 | Pump with multiple stage of impeller |
| JP5988290B2 (en) * | 2012-05-31 | 2016-09-07 | 株式会社日立製作所 | Casing and turbomachine and compressor provided with casing |
-
1980
- 1980-06-18 JP JP1980085211U patent/JPS6240156Y2/ja not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS578989U (en) | 1982-01-18 |
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