JPS5996494A - Screw hydraulic machine - Google Patents
Screw hydraulic machineInfo
- Publication number
- JPS5996494A JPS5996494A JP20546082A JP20546082A JPS5996494A JP S5996494 A JPS5996494 A JP S5996494A JP 20546082 A JP20546082 A JP 20546082A JP 20546082 A JP20546082 A JP 20546082A JP S5996494 A JPS5996494 A JP S5996494A
- Authority
- JP
- Japan
- Prior art keywords
- suction port
- suction
- rotor side
- port
- point
- 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.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary-Type Compressors (AREA)
Abstract
Description
【発明の詳細な説明】
〔発明の利用分野〕
本発明はスクリュー圧縮機、スクリュー膨張機などのス
クリュー流体機械に係シ、特に吸込口に連通するおすａ
−夕側及びめすロータ側の吸込ポートの形状に関する。[Detailed Description of the Invention] [Field of Application of the Invention] The present invention relates to a screw fluid machine such as a screw compressor or a screw expander.
- Concerning the shape of the suction port on the evening side and the female rotor side.
従来のスクリュー流体機械の一例としてスクリュー圧縮
機を例にとって第１図ないし第５図によシ説明する。８
１図及び第２図において、おすロータ１とめすロータ２
は噛合状態にてケーシングに収納されている。ケーシン
グは吸込ケーシング４、吐出ケーシング３及びエンドカ
バ５より成り、吐出ケーシング３に前記の両ロータ１．
２を収納している。また吐出ケーシング３には吸込口６
及び吐出ロアが穿設され、吸込ケーシング４の内面には
吸込口６と連通する吸込ポート８が形成されている。前
記の両ロータ１．２の吐出側軸９Ａは吐出ケーシング３
に設けたラジアル軸受１０Ａ及びスラスト軸受１１に支
承されていると共に吐出ケーシング３の軸貫通部に配置
した軸封装置１２Ａを貫通し、また吸込側軸９Ｂは吸込
ケーシング４に設けたラジアル軸受１０Ｂに支承されて
いると共に吸込ケーシング４の軸貫通部に配置した軸封
装置１２Ｂを貫通している。前記の軸封装置１２Ａ、１
２Ｂは圧縮ブスのシール及び軸受よシの排油をシールす
る。またおす、めす両ロータ１．２の吐出側軸９Ａの軸
端には一対のタイミングギヤ１３が噛合状態で装着され
、両ロータ１．２同志を非接触状態で同期回転させるよ
うになっている。またおすロータ１の吸込側軸９Ｂの軸
端にはピニオン１４が装着され、このピニオン１４は駆
動源により回転されるプルギヤ（図示省略）と噛合って
いる。そして。A screw compressor will be explained as an example of a conventional screw fluid machine with reference to FIGS. 1 to 5. 8
In Figures 1 and 2, male rotor 1 and female rotor 2
are housed in the casing in an engaged state. The casing consists of a suction casing 4, a discharge casing 3, and an end cover 5, and the discharge casing 3 has both rotors 1.
It stores 2. In addition, the discharge casing 3 has a suction port 6.
and a discharge lower, and a suction port 8 communicating with the suction port 6 is formed on the inner surface of the suction casing 4 . The discharge side shaft 9A of both rotors 1.2 is connected to the discharge casing 3.
The suction side shaft 9B is supported by a radial bearing 10A and a thrust bearing 11 provided in the radial bearing 10A and a thrust bearing 11 provided in the suction casing 4. It is supported and passes through a shaft sealing device 12B disposed in the shaft penetration portion of the suction casing 4. The shaft sealing device 12A, 1
2B seals the compression bus and the drain oil from the bearing. Furthermore, a pair of timing gears 13 are attached to the shaft ends of the discharge side shafts 9A of both the male and female rotors 1.2 in a meshing state, so that the two rotors 1.2 are rotated synchronously in a non-contact state. . A pinion 14 is attached to the shaft end of the suction side shaft 9B of the male rotor 1, and this pinion 14 meshes with a pull gear (not shown) rotated by a drive source. and.
前記ピニオン１４にプルギヤからの回転力が伝達される
と、おすロータ１とめすロータ２とは一対のタイミング
ギヤ１３によって微少間隙を保持しながら同期回転する
。これにより吸込ガスが吸込口６及び吸込ポート８を通
って両ロータ１．２の歯形にて形成された吸込空間１５
．１６に吸入され、両ロータ１，２の回転に伴ない前記
吸込空間１５．１６が順次縮小して封入ガスは圧縮され
、吐出ロアから吐出されて種々の用途に供される。When the rotational force from the pull gear is transmitted to the pinion 14, the male rotor 1 and the female rotor 2 rotate synchronously with a small gap maintained by a pair of timing gears 13. As a result, the suction gas passes through the suction port 6 and the suction port 8 into the suction space 15 formed by the teeth of both rotors 1.2.
．． As the rotors 1 and 2 rotate, the suction spaces 15 and 16 are sequentially reduced to compress the sealed gas, which is then discharged from the discharge lower and used for various purposes.
第３図表いし第５図は吸込ケーシングに形成した吸込、
ｊ？−トの形状を示したもので、この吸込ポート８にお
けるおすロータ側吸込／−）８Ａ及びＩめすロータ側吸
込ポー）８Ｂは、その面積と締め切り点から始点側への
回転角との関係を任意とした形状となっている。即ち、
おすロータ側吸込ポー）８Ａにおいては、その締め切り
点イから始点口側への回転角θにと面積との関係、めす
ロータ側吸込ポー）８Ｂにおいては、その締め切り点イ
′から始点口′側への回転角θｒと面積との関係が任意
となっている。そして、主としてロータ外周あるいは両
ロータの回転中心Ｏ１０′を中心とする円弧などでその
輪郭を定めて・・る。Figures 3 to 5 show the suction formed in the suction casing,
j? The figure shows the shape of the male rotor side suction port 8A and female rotor side suction port 8B in this suction port 8. It has an arbitrary shape. That is,
For the male rotor side suction port) 8A, the relationship between the rotation angle θ from its closing point A to the starting point port side and the area, and for the female rotor side suction port) 8B, from its closing point A' to the starting point port' side. The relationship between the rotation angle θr and the area is arbitrary. Then, its outline is mainly determined by an arc centered on the outer periphery of the rotor or the center of rotation O10' of both rotors.
尚、図中θＭＯ及びθＦＯはおすロータ側吸込ポート８
Ａ及びめすロータ側吸込ポート８Ｂの締め切り点イ、イ
′と中心ｏ、ｏ’を結ぶ半径線と中心０５０′を結ぶ中
心線とのなす角度を示す。In addition, θMO and θFO in the figure are male rotor side suction port 8.
It shows the angle formed by the radial line connecting the closing points A and A' of A and the female rotor side suction port 8B and the centers o and o' and the center line connecting the center 050'.
しかるに従来のスクリュー圧縮機においては、前記吸込
ポー）８Ａ、８Ｂは、その面積と締め切り点から始点側
への回転角との関係を任意とした形状となっていて、圧
縮機の性能との関連において形状が定められていないか
ら、吸込ポー）８Ａ、８Ｂを流れる吸込がスは加速、減
速をくり返し、大きな流動損失を伴なっていた。However, in a conventional screw compressor, the suction ports 8A and 8B have a shape that allows the relationship between the area and the rotation angle from the closing point to the starting point to be arbitrary, and the relationship with the performance of the compressor. Since the shape of the suction ports is not determined, the suction gas flowing through the suction ports 8A and 8B repeatedly accelerates and decelerates, resulting in a large flow loss.
本発明の目的は、従来技術の間趙点を解消し、吸込ポー
トにおける流動損失を最小におさえることができるスク
リュー流体機械を提供することにある。SUMMARY OF THE INVENTION An object of the present invention is to provide a screw fluid machine that can eliminate the problem of the prior art and minimize flow loss at the suction port.
この目的を達成するために、本発明のスクリュー流体機
械は、おすロータ側吸込ポート及びめすロータ側吸込ポ
ートの少なくともどちらか一方の吸込ポートを、そのポ
ート深さが締め切り点から始点に向うに伴い深くなる形
状として、吸込ポートを流れる吸込ガスの流速を略一定
にするようにしたものである。In order to achieve this object, the screw fluid machine of the present invention increases the suction port depth of at least one of the male rotor side suction port and the female rotor side suction port as the port depth increases from the closing point to the starting point. The deepening shape allows the flow velocity of the suction gas flowing through the suction port to be approximately constant.
以下本発明をスクリュー圧縮機に適用した実施例を第６
図ないし第８図に従って説明する。第６図は本発明によ
るスクリュー圧縮機を第２図と同様に示した図、第７図
は第６図の展開図を示している。図において、１はおす
ロータ％ ２はめす口、−タ、３は吐出ケーシング、４
は吸込ケーシング。The following is a sixth example of applying the present invention to a screw compressor.
This will be explained according to FIGS. 8 through 8. FIG. 6 shows a screw compressor according to the present invention in the same manner as FIG. 2, and FIG. 7 shows a developed view of FIG. 6. In the figure, 1 is the male rotor, 2 is the female port, 3 is the discharge casing, and 4
is the suction casing.
９Ａはおす、めす両ロータの吐出側軸である。前記吸込
ケーシング４の内面には、吸込口６に連通するおすロー
タ側吸込ポート１８Ａ及びめすロータ側吸込ポート１８
Ｂが形成されている０おすロータ側吸込ポート１８Ａは
、そのポート深さが締め切り点イから始点口に向うに従
い深くなる形状となっている、つまシ締め切り点イから
始点口に向うに従い面積が漸増する形状となっている。9A is the discharge side shaft of both the male and female rotors. On the inner surface of the suction casing 4, there are a male rotor side suction port 18A and a female rotor side suction port 18 that communicate with the suction port 6.
The 0-male rotor side suction port 18A in which B is formed has a shape in which the port depth becomes deeper from the closing point A toward the starting point, and the area increases from the closing point A toward the starting point. It has a shape that gradually increases.
また前記めすロータ側吸込ポート１８Ｂも、そのポート
深さが締め切９点イ′から始点口′に向うに従い深くな
る形状となっていて、締め切シ点イ′から始点口′に向
うに従い面積が漸増している。Furthermore, the female rotor side suction port 18B has a shape in which the port depth becomes deeper from the closing point 9 A' toward the starting point port', and the area gradually increases from the closing point A' toward the starting point port'. are doing.
従って、本発明によるスクリュー圧縮機においては、前
記のおすロータ側吸込ポー）１８Ａ及びめすロータ側吸
込＄−ト１８Ｂに吸込まれた吸込ガスの流速が略一定と
なり、該吸込ガスの流動損失を最小におさえることがで
きる。Therefore, in the screw compressor according to the present invention, the flow velocity of the suction gas sucked into the male rotor side suction port 18A and the female rotor side suction port 18B is approximately constant, and the flow loss of the suction gas is minimized. can be suppressed.
次に本発明によるスクリュー圧縮機において、吸込ポー
ト１８Ａ、１８Ｂの吸込ガスの流速が一定となる理由を
、第６図、第７図及び第８図にもとづいて理論的に説明
する。第８図はおすロータ１の吸込空間１５（第６図参
照）が該おすロータ１の回転角θに伴なって変化する様
子を示している。この図において、最大空間容積ＶＡＯ
は、吸込空間】５の軸直角断面積をＡ、ロータ長さをＬ
とすると、ＶＡｏ＝Ｌ−Ａとなる。Next, in the screw compressor according to the present invention, the reason why the flow velocity of the suction gas in the suction ports 18A and 18B is constant will be explained theoretically based on FIGS. 6, 7, and 8. FIG. 8 shows how the suction space 15 (see FIG. 6) of the male rotor 1 changes as the rotation angle θ of the male rotor 1 changes. In this figure, the maximum spatial volume VAO
is the suction space】5's axis-perpendicular cross-sectional area is A, and the rotor length is L.
Then, VAo=LA.
また第６図において、おすロータ側吸込ポート１８Ａの
締め切り点イを示す角度を０ＭＯ２吸込ポート１８Ａの
締め切り点イから始点口までの角度をθＭＴ、吸込ポー
ト１８Ａの締め切シ点イから任意の断面箇所までの角度
をθｙ、その断面箇所の断面積をＳＭθとし、また第７
図においておすロータ１の回転速度をｕＭｂ吸込ボート
１８Ａにおける吸込ガスの流速をｖＭとした場合、
但し、ＮＭ： おすロータ１の回転数、ＬＭ：おすロー
タｌの歯数、９Ｍ ：おすロータ１のラップ角である。In addition, in Fig. 6, the angle indicating the closing point A of the male rotor side suction port 18A is θMT, and the angle from the closing point A of the MO2 suction port 18A to the starting point is θMT, and an arbitrary cross-sectional point from the closing point A of the suction port 18A. Let θy be the angle to
In the figure, when the rotational speed of the male rotor 1 is expressed as vM and the flow rate of the suction gas in the uMb suction boat 18A is expressed as vM, where NM: rotational speed of the male rotor 1, LM: number of teeth of the male rotor 1, 9M: number of teeth of the male rotor 1. It is the wrap angle.
従って、相対流速Ｖ Ｍ ｕ Ｍが一定となるのは、
吸込ポー）ｉ８Ａの面積が、締め切り点イからの角度θ
緘に略比例して漸増する場合である。Therefore, the relative flow velocity V M u M is constant because
The area of suction port) i8A is the angle θ from the closing point
This is a case where the number increases gradually in approximately proportion to the scarcity.
まためすロータ側吸込ポー）１８Ｂについても、めすロ
ータ２の回転速度をｕ２、吸込ポート１８Ｂにおける吸
込がスの流速をｖ２とした場合、前述と同様に、
但Ｌ、ＮＦ： めすロータ１の回転数、Ｌ？ ：めすロ
ータ１の歯数、ψ、：めすロータｌのラッグ角、Ｖ！１
０ ：めすロータ側の吸込空間１６ （第６図参照）の
最大容積、θＦ：吸込ポー）１８Ｂの締め切り点イ′か
ら任意の断面箇所までの角度、８．θ：θＦにおける吸
込ポー）１８Ｂの断面積である。Also, regarding the female rotor side suction port 18B, if the rotational speed of the female rotor 2 is u2 and the flow rate of the suction at the suction port 18B is v2, the same as above, where L, NF: rotation of the female rotor 1 Number, L? : Number of teeth of female rotor 1, ψ, : Lug angle of female rotor l, V! 1
0: Maximum volume of the suction space 16 (see Figure 6) on the female rotor side, θF: Angle from the closing point A' of the suction port 18B to an arbitrary cross-sectional location, 8. θ: Cross-sectional area of suction port 18B at θF.
従って、めすロータ側についても、相対流速Ｖ ｒ
ｕ ｒが一定となるのは、吸込Ｉ−ト１８Ｂの面積が、
締め切り点イ′からの角度θｒに略比例して漸増する場
合である。Therefore, also for the female rotor side, the relative flow velocity V r
The reason why ur is constant is that the area of the suction I-t 18B is
This is a case where the angle gradually increases approximately in proportion to the angle θr from the cut-off point A'.
尚、前記の実施例においては、おすロータ側吸込ポート
１８Ａ及びめすロータ側吸込ポー）１８Ｂと、その締め
切シ点から始点に向うに従い面積が漸増する形状となし
たが、おすロータ側吸込ポート１８Ａまたはめすロータ
側吸込ポート１８Ｂのうち、どちらか一方のみを前記の
形状とすることによっても、がスの流動損失を小さくで
きる。In the above embodiment, the male rotor side suction port 18A and the female rotor side suction port 18B have a shape in which the area gradually increases from the closing point to the starting point, but the male rotor side suction port 18A Alternatively, gas flow loss can be reduced by forming only one of the female rotor-side suction ports 18B into the above-described shape.
また、本発明は前述したスクリュー圧縮機の他、スクリ
ュー膨張機にも適用できることは勿論である。Furthermore, it goes without saying that the present invention can be applied to not only the screw compressor described above but also a screw expander.
以上説明したように、本発明のスクリュー流体機械は、
吸込ポートにおけるガスの流速を略一定にすることがで
きるので、ガスの流動損失を最小におさえることができ
る。従って、高性能なスクリュー流体機械を実現するこ
とができる。As explained above, the screw fluid machine of the present invention has
Since the gas flow rate at the suction port can be made substantially constant, gas flow loss can be minimized. Therefore, a high-performance screw fluid machine can be realized.
第１図は従来のスクリュー圧縮機の縦断面図、第２図は
第１図の■−■矢視図、第３図は同じくｌ１ｌ−Ｉｌｌ
矢視図、第４図及び第５図は第３図のＩＶ−■矢視断面
図及びｖ−■矢視断面図、第６図ないし第８図は本発明
の一実施例としてスクリュー圧縮機に適用した例を示し
、第６図は本発明によるスクリュー圧縮機を第２図と同
様に示した図、第７図は第６図の展開図、第８図はおす
ロータの吸込空間の変化する様子を示す図である。
１・・・おすロータ、２・・・めすロータ、３・・・吐
出ケーシング、４・・・吸込ケーシング、６・・・吸込
口、７・・・吐出口、ＩＯＡ、 ＩＯＢ・・・ラジアル
軸受、１１・・・スラスト軸受、１８Ａ・・・おすロー
タ側吸込ポート、１８Ｂ・・・めすロータ側吸込ポート
、イ及びイ′・・・おすロータ側吸込ポート及びめすロ
ータ側吸込ポートの締め切９点、口及び口′・・・おす
ロータ側吸込ポート及びめすロータ側吸込ポートの始点
。
代理人 弁理士 秋 本 正 実Fig. 1 is a vertical cross-sectional view of a conventional screw compressor, Fig. 2 is a view taken along the ■-■ arrow in Fig. 1, and Fig. 3 is also a l1l-Ill view.
4 and 5 are cross-sectional views taken along IV-■ arrow and V-■ arrow sectional views in FIG. Fig. 6 shows a screw compressor according to the present invention in the same way as Fig. 2, Fig. 7 is a developed view of Fig. 6, and Fig. 8 shows changes in the suction space of the male rotor. FIG. 1...Male rotor, 2...Female rotor, 3...Discharge casing, 4...Suction casing, 6...Suction port, 7...Discharge port, IOA, IOB...Radial bearing , 11...Thrust bearing, 18A...Male rotor side suction port, 18B...Female rotor side suction port, A and A'...9 closing points for male rotor side suction port and female rotor side suction port , mouth and mouth'...Starting points of the male rotor side suction port and female rotor side suction port. Agent Patent Attorney Masami Akimoto
Claims (1)
を収納するケーシングと、両ロータの軸を支承する軸受
と、前記ケーシングに穿設した吸込口及び吐出口と、ケ
ーシングの内面に形成され、前記吸込口と連通ずるおす
ロータ側及びめすロータ側の吸込ポートとを備えたスク
リュー流体機械において、前記のおすロータ側吸込ポー
ト及びめスロータ側吸込ポートの少なくともどちらか一
方の吸込ポートを、その軸方向ボート深さが締め切り点
から始点に向うに従い、深くなる形状としたことを特徴
とするスクリュー流体機械。A male rotor and a female rotor that mesh with each other, a casing that accommodates both rotors, a bearing that supports the shafts of both rotors, an inlet and an outlet that are bored in the casing, and formed on the inner surface of the casing, In a screw fluid machine having a suction port on a sliding rotor side and a suction port on a female rotor side communicating with the suction port, at least one of the suction port on the male rotor side and the suction port on the female rotor side is connected to the shaft of the screw fluid machine. A screw fluid machine characterized in that the directional boat depth becomes deeper from the closing point to the starting point.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP20546082A JPS5996494A (en) | 1982-11-25 | 1982-11-25 | Screw hydraulic machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP20546082A JPS5996494A (en) | 1982-11-25 | 1982-11-25 | Screw hydraulic machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5996494A true JPS5996494A (en) | 1984-06-02 |
| JPS6340280B2 JPS6340280B2 (en) | 1988-08-10 |
Family
ID=16507239
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP20546082A Granted JPS5996494A (en) | 1982-11-25 | 1982-11-25 | Screw hydraulic machine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5996494A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60219486A (en) * | 1984-03-28 | 1985-11-02 | ソシエテ・アノニム・デー・ベー・アー | Screw compressor |
| JP2009085378A (en) * | 2007-10-01 | 2009-04-23 | Nippon Petroleum Refining Co Ltd | Pipe arrangement repairing implement |
| JP2010275995A (en) * | 2009-06-01 | 2010-12-09 | Hitachi Plant Technologies Ltd | Screw compressor |
| WO2023176517A1 (en) * | 2022-03-15 | 2023-09-21 | 株式会社日立産機システム | Screw compressor |
-
1982
- 1982-11-25 JP JP20546082A patent/JPS5996494A/en active Granted
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60219486A (en) * | 1984-03-28 | 1985-11-02 | ソシエテ・アノニム・デー・ベー・アー | Screw compressor |
| JP2009085378A (en) * | 2007-10-01 | 2009-04-23 | Nippon Petroleum Refining Co Ltd | Pipe arrangement repairing implement |
| JP2010275995A (en) * | 2009-06-01 | 2010-12-09 | Hitachi Plant Technologies Ltd | Screw compressor |
| WO2023176517A1 (en) * | 2022-03-15 | 2023-09-21 | 株式会社日立産機システム | Screw compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6340280B2 (en) | 1988-08-10 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US11506056B2 (en) | Rotary machine | |
| US5755196A (en) | Rotary positive displacement engine | |
| JPS63277880A (en) | Floating shaft type gear pump and motor | |
| JPS5996494A (en) | Screw hydraulic machine | |
| US6200116B1 (en) | Vacuum pumps | |
| JPS61138893A (en) | Trochoidal oil pump | |
| JP2006283664A (en) | Roots pump | |
| JPH02252991A (en) | Screw rotor for screw type pump device | |
| JP2002364570A (en) | Roots type fluid machine | |
| JPH042798B2 (en) | ||
| JPH0718416B2 (en) | Rotor for rotary pump | |
| JPH0658041B2 (en) | Thrust force balancing method for screw type rotary machine | |
| US3311291A (en) | Helical screw compressors | |
| JPS6143288A (en) | Internal gear pump | |
| JPH0442543Y2 (en) | ||
| JPS5990788A (en) | Rotary pump | |
| JPH041353Y2 (en) | ||
| JPS59196985A (en) | Oil pump | |
| JP3751673B2 (en) | Hollow rotor for screw type fluid machinery | |
| KR970000498B1 (en) | Rotary compressor | |
| JP2002130163A (en) | Fluid machine | |
| JPS6153482A (en) | Trochoidal pump for engine lubricatioin | |
| JPS641511Y2 (en) | ||
| JPH0431686A (en) | Screw rotor | |
| JPS6390690A (en) | Mechanical supercharger of engine |