JP2014214740A - Oil cooling type screw compressor - Google Patents

Oil cooling type screw compressor Download PDF

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JP2014214740A
JP2014214740A JP2013095740A JP2013095740A JP2014214740A JP 2014214740 A JP2014214740 A JP 2014214740A JP 2013095740 A JP2013095740 A JP 2013095740A JP 2013095740 A JP2013095740 A JP 2013095740A JP 2014214740 A JP2014214740 A JP 2014214740A
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oil
rotor
female rotor
cylinder
male rotor
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JP6236219B2 (en
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優 小柴
Masaru Koshiba
優 小柴
金子　克
Katsu Kaneko
克 金子
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Hokuetsu Industries Co Ltd
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Hokuetsu Industries Co Ltd
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    • 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
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

PROBLEM TO BE SOLVED: To reduce a load at the time of driving an oil cooling type screw compressor.SOLUTION: An oil cooling type screw compressor 1 includes a cylinder 31 having an 8-shaped cross section in a direction orthogonal to a shaft within a casing 30. Lubricant oil is supplied to a working space when a male rotor 10 and a female rotor 20 stored in the cylinder 31 are engaged with each other and rotated. A male rotor storing segment 31a of the cylinder 31 is arranged at a higher location side with respect to a female rotor storing part 31b, the male rotor storing segment 31a is communicated with the female rotor storing part 31b at its bottom part and the lubricant oil is supplied into the cylinder 31 through an oil supplying port 35 opened only in an inner wall surface of the female rotor storing part 31b. With this configuration, since the male rotor storing part 31a does not have any bottom part acting as an oil reservoir and the lubricant oil more than necessary is not supplied, rotational resistance of the male rotor 10 is substantially reduced.

Description

本発明は，油冷式スクリュ圧縮機に関する。   The present invention relates to an oil-cooled screw compressor.

油冷式スクリュ圧縮機１００は，図６に示すように噛み合い状態で回転するオスロータ１１０とメスロータ１２０から成る一対のスクリュロータを備えていると共に，この一対のスクリュロータを噛み合い状態で回転可能に収容するシリンダ１３１が内部に形成されたケーシング１３０を備えており，前記一対のスクリュロータがシリンダ１３１内で噛み合い回転して被圧縮気体を圧縮するときに作用空間内に潤滑油を供給することで，ロータ１１０，１２０間及びロータ１１０，１２０とシリンダ１３１内壁間の密封や冷却，潤滑を行うことができるように構成されている。   As shown in FIG. 6, the oil-cooled screw compressor 100 includes a pair of screw rotors including a male rotor 110 and a female rotor 120 that rotate in a meshed state, and accommodates the pair of screw rotors so as to be rotatable in a meshed state. A cylinder 130 is formed, and a lubricating oil is supplied into the working space when the pair of screw rotors are engaged and rotated in the cylinder 131 to compress the compressed gas. Sealing, cooling and lubrication between the rotors 110 and 120 and between the rotors 110 and 120 and the inner wall of the cylinder 131 can be performed.

作用空間内に供給された潤滑油は，被圧縮気体と共に圧縮されて気液混合流体として油冷式スクリュ圧縮機１００より吐出されると共に，これをレシーバタンク等の気液分離器（図示せず）に導入して圧縮気体と潤滑油とを分離した後，分離された潤滑油を冷却して再度，油冷式スクリュ圧縮機１００に給油して循環使用する。   Lubricating oil supplied into the working space is compressed together with the gas to be compressed and discharged from the oil-cooled screw compressor 100 as a gas-liquid mixed fluid, and this is discharged into a gas-liquid separator (not shown) such as a receiver tank. ) And the compressed gas and the lubricating oil are separated, and then the separated lubricating oil is cooled and supplied to the oil-cooled screw compressor 100 for circulation.

このように被圧縮気体を潤滑油と共に圧縮する油冷式スクリュ圧縮機１００において，前述のシリンダ１３１は，ケーシング１３０内にオスロータ１１０とメスロータ１２０を水平方向に並べた状態で噛み合い回転可能に収容することができるよう，オスロータ収容部１３１ａとなる円筒部と，メスロータ収容部１３１ｂとなる円筒部を一部分が重なり合うように平行に配置した，軸直交方向の断面が横向きの８の字状となる形状に形成されており，このシリンダ１３１のオスロータ収容部１３１ａの底部内壁と，メスロータ収容部１３１ｂの底部内壁のそれぞれに給油口１３５，１３６を開口し，この給油口１３５，１３６を介してオスロータ収容部１３１ａとメスロータ収容部１３１ｂのそれぞれに潤滑油を給油するように構成されている（特許文献１参照）。   In the oil-cooled screw compressor 100 that compresses the gas to be compressed together with the lubricating oil in this way, the above-described cylinder 131 is accommodated in the casing 130 so that the male rotor 110 and the female rotor 120 are meshed and rotated in a state of being arranged in the horizontal direction. In order to be able to do so, the cylindrical portion that becomes the male rotor accommodating portion 131a and the cylindrical portion that becomes the female rotor accommodating portion 131b are arranged in parallel so that a part of them overlaps, and the cross section in the direction perpendicular to the axis is in a shape of 8 in the horizontal direction. The oil supply ports 135 and 136 are formed in the bottom inner wall of the male rotor accommodating portion 131a of the cylinder 131 and the bottom inner wall of the female rotor accommodating portion 131b, and the male rotor accommodating portion 131a is formed through the oil supply ports 135 and 136. And the female rotor accommodating portion 131b are configured to supply lubricating oil. (See Patent Document 1).

なお，前掲の特許文献１では，前述の給油口１３５，１３６をオスロータ１１０及びメスロータ１２０それぞれの圧縮開始歯溝における先行歯先から，圧縮完了歯溝における後続歯先区間であって，長手方向中央もしくはその近傍に設けること，及び，オスロータ収容部１３１ａとメスロータ収容部１３１ｂのそれぞれに対し給油を行うことにより，潤滑油の供給による冷却効率を向上させている（特許文献１[0018]〜［0020］欄）。   In the above-mentioned Patent Document 1, the above-described oil supply ports 135 and 136 are arranged from the preceding tooth tip in the compression start tooth gap of each of the male rotor 110 and the female rotor 120 to the succeeding tooth tip section in the compression completed tooth gap, and in the longitudinal center. Alternatively, the cooling efficiency by supplying lubricating oil is improved by providing it in the vicinity thereof and supplying oil to each of the male rotor accommodating portion 131a and the female rotor accommodating portion 131b (Patent Documents 1 [0018] to [0020]. ] Column).

特開２００１−１５３０７３号公報JP 2001-153073 A

油冷式スクリュ圧縮機１００の駆動源（図示せず）としては，通常，モータやエンジンが使用されることから，油冷式スクリュ圧縮機１００の吸気量や吐出圧力を低下させることなく，油冷式スクリュ圧縮機１００の駆動時に生じる負荷を軽減することができれば，より少ない電力や燃料で効率的に圧縮気体が得られることから，このような負荷の軽減を実現するための各種の提案がなされている。   As a drive source (not shown) of the oil-cooled screw compressor 100, a motor or an engine is usually used. Therefore, the oil-cooled screw compressor 100 can be used without reducing the intake air amount and the discharge pressure. If the load generated when driving the cold screw compressor 100 can be reduced, the compressed gas can be obtained efficiently with less electric power and fuel. Therefore, various proposals for realizing such a load reduction are available. Has been made.

前掲の特許文献１に記載の発明も，このような発明の１つであり，前述のようにして給油を行うことで効率的な冷却が実現可能となり，これに伴い給油量を減らすことで，ロータが潤滑油を攪拌することにより生じる油攪拌損失を減少させている。   The invention described in the above-mentioned Patent Document 1 is also one of such inventions, and by performing refueling as described above, efficient cooling can be realized, and along with this, by reducing the refueling amount, The oil stirring loss caused by the rotor stirring the lubricating oil is reduced.

確かに特許文献１に記載されている発明のように，作用空間に供給する潤滑油量を減少させることができれば，潤滑油との接触抵抗，すなわち油攪拌損失の減少が期待できる。   If the amount of lubricating oil supplied to the working space can be reduced as in the invention described in Patent Document 1, it can be expected to reduce the contact resistance with the lubricating oil, that is, the oil stirring loss.

しかし，特許文献１に記載されているようにオスロータ１１０とメスロータ１２０を水平方向に並べて配置すると共に，シリンダ１３１のオスロータ収容部１３１ａとメスロータ収容部１３１ｂのそれぞれの底部に給油口１３５，１３６を設けて給油を行う構成を採用した場合（図６参照）には，潤滑油の給油量を減少することで回転時に生じる負荷を軽減することができたとしても，シリンダ１３１の底部，特に，オスロータ収容部１３１ａの底部に油溜まりが形成されることで，この底部に溜まった潤滑油の「噛み込み」とでも言うべき現象によってロータ１１０，１２０，特に，オスロータ１１０の回転が大きな抵抗を受けることとなる。   However, as described in Patent Document 1, the male rotor 110 and the female rotor 120 are arranged side by side in the horizontal direction, and oil supply ports 135 and 136 are provided at the bottoms of the male rotor accommodating portion 131a and the female rotor accommodating portion 131b of the cylinder 131, respectively. In the case of adopting a configuration that supplies oil (see FIG. 6), even if the load generated during rotation can be reduced by reducing the amount of lubricating oil supplied, the bottom of the cylinder 131, particularly the male rotor can be accommodated. By forming an oil sump at the bottom of the portion 131a, the rotation of the rotors 110 and 120, particularly the male rotor 110, receives a great resistance due to a phenomenon that can be referred to as "engagement" of the lubricating oil accumulated at the bottom. Become.

すなわち，オスロータ１１０の歯溝１１３，メスロータ１２０の歯溝１２３，及びシリンダ１３１の内壁によって画成された作用空間（図６中の斜線部分）のうち，オスロータ１１０の前進側歯面１１２ａとシリンダ内壁面とによって画成された部分は，オスロータ１１０の歯先１１２に向かって狭くなるくさび型の空間Ｗ1となっており，オスロータ１１０の歯先１１２が底部に溜まった潤滑油中を通過する時，オスロータ１１０は前進側歯面１１２ａの持つカーブによって潤滑油を押し潰すようにして加圧しながら，くさび形の空間Ｗ1の先端部（狭まった部分）に噛み込むように回転するため，加圧された潤滑油がオスロータ１１０の回転に対して大きな抵抗を与えることとなる。   That is, of the working space (shaded portion in FIG. 6) defined by the tooth groove 113 of the male rotor 110, the tooth groove 123 of the female rotor 120, and the inner wall of the cylinder 131, the forward tooth surface 112a of the male rotor 110 and the inside of the cylinder. The portion defined by the wall surface is a wedge-shaped space W1 that narrows toward the tooth tip 112 of the male rotor 110, and when the tooth tip 112 of the male rotor 110 passes through the lubricating oil accumulated at the bottom, The male rotor 110 was pressurized because it rotated to bite into the tip (narrow part) of the wedge-shaped space W1 while pressing the lubricating oil by crushing it with the curve of the forward tooth surface 112a. The lubricating oil will give a great resistance to the rotation of the male rotor 110.

なお，図６に示す構成では，メスロータ収容部１３１ｂの底部にも同様に潤滑油は溜まっており，メスロータ１２０の歯先１２２が底部に溜まった潤滑油中を通過する際にも同様の原理によって抵抗を受けることとなる。   In the configuration shown in FIG. 6, the lubricating oil is similarly accumulated at the bottom of the female rotor accommodating portion 131b, and the same principle is applied when the tooth tip 122 of the female rotor 120 passes through the lubricating oil accumulated at the bottom. You will receive resistance.

しかしながら，図６中において拡大図で示す必要があるように，メスロータ１２０の追従側歯面１２３ｂとシリンダ１３１内壁面との間に形成されるくさび型の空間Ｗ2は，オスロータ１２０の前進側歯面１１２ａとシリンダ１３１内壁面との間に形成されるくさび型の空間Ｗ1に比較して遙かに小さく，くさびの先端部（狭まった部分）に集中しようとする潤滑油量が少ないこと，また，メスロータ１２０はオスロータ１１０よりも歯数が多いためオスロータ１１０よりも回転速度が遅いこと，通常，メスロータ１２０の外径はオスロータ１１０に比較して小さく設計されることから，メスロータ１２０の歯先１２２の周速度は，オスロータ１１０の歯先１１２の周速度に比較して遅いこと等とも相俟って，オスロータ１１０の歯先１１２が底部に溜まった潤滑油によって受ける抵抗に比較して，メスロータ１２０の歯先１２２が底部に溜まった潤滑油によって受ける抵抗は遙かに小さなものとなっている。   However, as shown in an enlarged view in FIG. 6, the wedge-shaped space W <b> 2 formed between the following tooth surface 123 b of the female rotor 120 and the inner wall surface of the cylinder 131 is the forward tooth surface of the male rotor 120. 112a and the wedge-shaped space W1 formed between the inner wall surface of the cylinder 131 and much smaller than the wedge-shaped space W1, and the amount of lubricating oil to be concentrated on the front end (narrowed portion) of the wedge is small. Since the female rotor 120 has a larger number of teeth than the male rotor 110, the rotational speed is slower than that of the male rotor 110. Normally, the outer diameter of the female rotor 120 is designed to be smaller than that of the male rotor 110. The peripheral speed is low in comparison with the peripheral speed of the tooth tip 112 of the male rotor 110. Compared to the resistance experienced by accumulated lubricant parts, resistance received by the lubricating oil addendum 122 of the female rotor 120 has accumulated in the bottom portion has a small things much.

以上の点から，上記で説明した原理によってロータ，特にオスロータの回転時に加わる抵抗を減少することができれば，オスロータが回転時に受ける抵抗を大幅に減少することができ，その結果，油冷式スクリュ圧縮機の駆動に要する消費電力や燃料消費量を低減させて効率的に圧縮気体を得られることとなる。   In view of the above, if the resistance applied during rotation of the rotor, particularly the male rotor, can be reduced according to the principle described above, the resistance experienced by the male rotor during rotation can be greatly reduced. As a result, oil-cooled screw compression The compressed gas can be obtained efficiently by reducing the power consumption and fuel consumption required for driving the machine.

そこで本発明は，ロータに対して必要な潤滑油の供給を可能としつつ，潤滑油との接触によりロータに加わる回転抵抗，特にオスロータに加わる回転抵抗を可及的に低減することのできる，油冷式スクリュ圧縮機を提供することを目的とする。   Accordingly, the present invention provides an oil that can reduce the rotational resistance applied to the rotor by contact with the lubricating oil, particularly the rotational resistance applied to the male rotor as much as possible, while enabling supply of the necessary lubricating oil to the rotor. An object is to provide a cold screw compressor.

以下に，課題を解決するための手段を，発明を実施するための形態で使用する符号と共に記載する。この符号は，特許請求の範囲の記載と発明を実施するための形態の記載との対応を明らかにするためのものであり，言うまでもなく，本願発明の技術的範囲の解釈に制限的に用いられるものではない。   Hereinafter, means for solving the problem will be described together with reference numerals used in the embodiment for carrying out the invention. This code is used to clarify the correspondence between the description of the scope of claims and the description of the mode for carrying out the invention. Needless to say, it is used in a limited manner for the interpretation of the technical scope of the present invention. It is not a thing.

上記目的を達成するために，本発明の油冷式スクリュ圧縮機１は，相互に噛み合い回転するオスロータ１０及びメスロータ２０から成る一対のスクリュロータと，前記一対のスクリュロータを噛み合い回転可能に収容するシリンダ３１が内部に形成されたケーシング３０を備え，前記シリンダ３１が，オスロータ収容部３１ａとなる円筒部とメスロータ収容部３１ｂとなる円筒部とを平行に配置すると共に，前記オスロータ収容部３１ａとメスロータ収容部３１ｂの周方向における一部分を重ねて連通し，前記シリンダの軸直交方向の断面が略８の字状に形成され，前記シリンダ３１内に潤滑油を給油して被圧縮気体を圧縮する油冷式スクリュ圧縮機１において，
前記シリンダ３１の前記オスロータ収容部３１ａを前記メスロータ収容部３１ｂに対し高所側に形成すると共に，前記オスロータ収容部３１ａの底部を前記メスロータ収容部３１ｂと連通し，
前記シリンダ３１内に潤滑油を供給する給油口３５を，前記メスロータ収容部３１ｂの内壁面にのみ開口することを特徴とする（請求項１）。 In order to achieve the above object, an oil-cooled screw compressor 1 of the present invention accommodates a pair of screw rotors comprising a male rotor 10 and a female rotor 20 that mesh and rotate with each other, and the pair of screw rotors so as to mesh and rotate. The cylinder 31 includes a casing 30 formed therein, and the cylinder 31 has a cylindrical portion serving as a male rotor accommodating portion 31a and a cylindrical portion serving as a female rotor accommodating portion 31b arranged in parallel, and the male rotor accommodating portion 31a and the female rotor Oil that compresses the compressed gas by supplying lubricating oil into the cylinder 31 so that a section in the circumferential direction of the cylinder 31 is overlapped and communicated with each other in the circumferential direction of the accommodating portion 31b. In the cold screw compressor 1,
The male rotor housing portion 31a of the cylinder 31 is formed at a higher position with respect to the female rotor housing portion 31b, and the bottom portion of the male rotor housing portion 31a is communicated with the female rotor housing portion 31b.
An oil supply port 35 for supplying lubricating oil into the cylinder 31 is opened only on the inner wall surface of the female rotor housing portion 31b (Claim 1).

上記油冷式スクリュ圧縮機１において，前記オスロータ１０の軸芯１１を通る垂線ＶＬが，前記オスロータ収容部３１ａとメスロータ収容部３１ｂとの境界に形成された２つ山形部３２，３３のうち何れか一方の山形部３２の頂点３２ａを通る位置（図４参照）から，他方の山形部３３の頂点３３ａを通る位置間にあるよう前記シリンダ３１を形成することが好ましい（請求項２）。   In the oil-cooled screw compressor 1, the perpendicular VL passing through the axis 11 of the male rotor 10 is any of the two chevron portions 32 and 33 formed at the boundary between the male rotor housing portion 31 a and the female rotor housing portion 31 b. The cylinder 31 is preferably formed so as to be between a position passing through the apex 32a of one chevron 32 (see FIG. 4) and a position passing through the apex 33a of the other chevron 33 (Claim 2).

また，前述の給油口３５は，前記メスロータ収容部３１ｂの底部Ｂを通過した後，前記オスロータと噛み合う前の前記メスロータ２０の歯溝２３の通過位置において前記メスロータ収容部３１ｂの内壁面に開口するものとしても良く（請求項３），又は，
前記メスロータ収容部３１ｂの底部Ｂにおける内壁面に開口するものとしても良い（請求項４）。 Further, the above-described oil filler port 35 opens in the inner wall surface of the female rotor housing portion 31b at the passage position of the tooth groove 23 of the female rotor 20 after meshing with the male rotor after passing through the bottom B of the female rotor housing portion 31b. (Claim 3) or
It is good also as what opens to the inner wall face in the bottom part B of the said female rotor accommodating part 31b (Claim 4).

以上で説明した本発明の構成により，本発明の油冷式スクリュ圧縮機１では，シリンダ３１のオスロータ収容部３１ａはその底部においてメスロータ収容部３１ｂと連通しているために，オスロータ収容部３１ａには潤滑油が溜まる底部が存在していない。   With the configuration of the present invention described above, in the oil-cooled screw compressor 1 of the present invention, the male rotor accommodating portion 31a of the cylinder 31 communicates with the female rotor accommodating portion 31b at the bottom thereof. There is no bottom where lubricating oil accumulates.

しかも，シリンダ３１内に対する給油を，メスロータ収容部３１ｂを介してのみ行い，オスロータ収容部３１ａに対する直接の給油を行わない構成とした結果，潤滑油がオスロータ１０に対して与える回転負荷を大幅に減少することができた。   In addition, as a result of supplying oil into the cylinder 31 only through the female rotor housing 31b and not directly supplying oil to the male rotor housing 31a, the rotational load applied to the male rotor 10 by the lubricating oil is greatly reduced. We were able to.

一方，メスロータ２０によって掻き上げられた潤滑油がオスロータ１０とメスロータ２０との噛合部やオスロータ収容部３１ａ内に対しても導入されることで，オスロータ１０に対して必要な給油を確保することができた。   On the other hand, the lubricating oil scraped up by the female rotor 20 is also introduced into the meshing part of the male rotor 10 and the female rotor 20 and the inside of the male rotor accommodating part 31a, thereby ensuring the necessary oil supply to the male rotor 10. did it.

その結果，本発明の油冷式スクリュ圧縮機１では，油冷式スクリュ圧縮機の機能を損なうことなく，駆動時の圧縮機の動力を約３％減少させることができ，油冷式スクリュ圧縮機１の駆動に必要な電力消費量，燃料消費量を低く抑えてより効率的に圧縮気体を得ることができた。   As a result, in the oil-cooled screw compressor 1 of the present invention, the power of the compressor during driving can be reduced by about 3% without impairing the function of the oil-cooled screw compressor. The compressed gas can be obtained more efficiently while keeping the power consumption and fuel consumption required for driving the machine 1 low.

特に，オスロータ１０の軸芯１１を通る垂線ＶＬが，前記オスロータ収容部３１ａとメスロータ収容部３１ｂとの境界に形成された２つ山形部３２，３３のうち何れか一方の山形部３２の頂点３２ａを通る位置（図４参照）から，他方の山形部３３の頂点３３ａを通る位置間にあるようにシリンダ３１のオスロータ収容部３１ａとメスロータ収容部３１ｂとを配置した構成では，常に何れかの山形部３２，３３の頂点３２ａ，３３ａがオスロータ収容部３１ａの最下端となるため，オスロータ収容部３１ａに油溜まりが生じることを確実に防止することができた。   In particular, a vertical line VL passing through the axis 11 of the male rotor 10 is a vertex 32a of one of the two chevron portions 32, 33 formed at the boundary between the male rotor housing portion 31a and the female rotor housing portion 31b. In the configuration in which the male rotor accommodating portion 31a and the female rotor accommodating portion 31b of the cylinder 31 are arranged so as to be between the position passing through the vertex 33a of the other chevron 33 (see FIG. 4), it is always any one of the chevron shapes Since the apexes 32a and 33a of the portions 32 and 33 are the lowermost end of the male rotor accommodating portion 31a, it was possible to reliably prevent an oil pool from occurring in the male rotor accommodating portion 31a.

シリンダ３１に対する潤滑油の供給を，メスロータ収容部３１ｂの底部Ｂを通過した後，前記オスロータと噛み合う前の前記メスロータ２０の歯溝２３の通過位置におけるメスロータ収容部３１ｂの内壁面に開口した給油口３５を介して行う構成（図２，図４参照）にあっては，給油口３５がメスロータ収容部３１ｂの底部Ｂに対し上方に形成されることにより，給油された潤滑油は直接底部Ｂに落下することができず，一旦メスロータ２０によって掻き上げられて，オスロータ収容部３１ａやメスロータ収容部３１ｂの内壁，オスロータ１０及びメスロータ２０の表面に付着すると共に，各部に付着した残りの潤滑油が重力により落下してメスロータ収容部３１ｂの底部Ｂに溜まることとなるため，メスロータ収容部３１ｂの底部Ｂに直接潤滑油を給油する場合に比較して底部Ｂに溜まる潤滑油量を減少させることができた。   Lubricating oil supplied to the cylinder 31 is passed through the bottom B of the female rotor accommodating portion 31b, and then is an oil supply port opened on the inner wall surface of the female rotor accommodating portion 31b at the passage position of the tooth groove 23 of the female rotor 20 before meshing with the male rotor. 35 (see FIG. 2 and FIG. 4), the oil supply port 35 is formed above the bottom B of the female rotor housing 31b, so that the lubricated lubricating oil is directly applied to the bottom B. It cannot be dropped, and is once scraped up by the female rotor 20 and adheres to the inner walls of the male rotor accommodating portion 31a and the female rotor accommodating portion 31b, the surfaces of the male rotor 10 and the female rotor 20, and the remaining lubricating oil adhering to each portion is gravity. Is dropped and collected at the bottom B of the female rotor housing 31b. It was able to reduce the amount of lubricating oil collected in the bottom B in comparison with the case of refueling Namerayu.

その結果，メスロータ２０が底部Ｂに溜まった潤滑油を攪拌する際に生じる回転抵抗についても減少させることができた。   As a result, the rotational resistance generated when the female rotor 20 agitates the lubricating oil accumulated in the bottom B can be reduced.

本発明のスクリュ圧縮機の正面断面図。Front sectional drawing of the screw compressor of this invention. 図１のII−II線断面図。II-II sectional view taken on the line of FIG. 図２に対する給油口位置の変更例を示す説明図。Explanatory drawing which shows the example of a change of the filler opening position with respect to FIG. 図２に対する各部の位置関係の変更例を示す説明図。Explanatory drawing which shows the example of a change of the positional relationship of each part with respect to FIG. 増速装置を備えた本発明のスクリュ圧縮機の正面断面図。Front sectional drawing of the screw compressor of this invention provided with the speed increasing apparatus. 従来のスクリュ圧縮機の説明図（軸直交断面）。Explanatory drawing (axial orthogonal cross section) of the conventional screw compressor.

以下に，添付図面を参照しながら本発明の油冷式スクリュ圧縮機について説明する。   The oil-cooled screw compressor of the present invention will be described below with reference to the accompanying drawings.

図１中の符号１は，本発明の油冷式スクリュ圧縮機であり，この油冷式スクリュ圧縮機１は，オスロータ１０及びメスロータ２０から成る一対のスクリュロータと，前記スクリュロータを収容するシリンダ３１が内部に形成されたケーシング３０を備えている。   Reference numeral 1 in FIG. 1 denotes an oil-cooled screw compressor according to the present invention. The oil-cooled screw compressor 1 includes a pair of screw rotors including a male rotor 10 and a female rotor 20, and a cylinder that houses the screw rotor. 31 includes a casing 30 formed therein.

このケーシング３０内に形成するシリンダ３１は，図２に示すように，オスロータ収容部３１ａとなる円筒部と，メスロータ収容部３１ｂとなる円筒部を周方向の一部分が重なり合うように平行に配置，組み合わせた，シリンダの軸直交方向の断面において略８の字状に形状されており，前述のオスロータ１０とメスロータ２０とを噛み合わせた状態で共にシリンダ３１内に収容することができるようになっている。   As shown in FIG. 2, the cylinder 31 formed in the casing 30 is arranged and combined in parallel so that a cylindrical portion serving as the male rotor accommodating portion 31a and a cylindrical portion serving as the female rotor accommodating portion 31b overlap each other in the circumferential direction. In addition, the cross section in the direction perpendicular to the axis of the cylinder is formed in a shape of approximately 8 so that both the male rotor 10 and the female rotor 20 can be accommodated together in the cylinder 31. .

図示の例では，メスロータ２０に対し大径に形成されたオスロータ１０を収容することができるよう，メスロータ収容部３１ｂに対し，オスロータ収容部３１ａの径を大きく形成しているが，例えばメスロータとオスロータを同径に形成し，従って,オスロータ収容部とメスロータ収容部についても同径に形成した油冷式スクリュ圧縮機に対し本発明を適用するものとしても良い。   In the illustrated example, the diameter of the male rotor accommodating portion 31a is formed larger than the female rotor accommodating portion 31b so that the male rotor 10 having a large diameter relative to the female rotor 20 can be accommodated. Therefore, the present invention may be applied to an oil-cooled screw compressor in which the male rotor accommodating portion and the female rotor accommodating portion are also formed to have the same diameter.

シリンダ３１内に収容されたオスロータ１０とメスロータ２０は，相互に噛み合った状態で逆向きに回転することができるよう，図１に示すように各ロータ１０，２０の両端に設けられたロータ軸１０ａ，１０ｂ；２０ａ，２０ｂのそれぞれをケーシング３０内に設けた軸受４１〜４４によって回転可能に軸支すると共に，オスロータ１０又はメスロータ２０の一方のロータ軸，図示の例ではオスロータ１０の吸入側のロータ軸１０ａに対し，図示せざるモータやエンジン等の駆動源からの回転駆動力を入力することができるように構成されている。   As shown in FIG. 1, the rotor shafts 10a provided at both ends of the rotors 10 and 20 so that the male rotor 10 and the female rotor 20 accommodated in the cylinder 31 can rotate in opposite directions while being engaged with each other. , 10b; 20a and 20b are rotatably supported by bearings 41 to 44 provided in the casing 30, and one rotor shaft of the male rotor 10 or the female rotor 20, in the illustrated example, the rotor on the suction side of the male rotor 10 A rotational driving force from a drive source such as a motor or an engine (not shown) can be input to the shaft 10a.

図１に示す実施形態にあっては，このような駆動源からの回転駆動力の入力を可能とするために，オスロータ１０の吸入側ロータ軸１０ａの一端にギヤカップリング５０の一方の構成要素であるインナーギヤ５１を取り付けると共に，駆動源の出力軸（図示せず）に連結されたフライホイール６０に，前記ギヤカップリング５０の他方の構成要素であるアウターギヤ５２を取り付け，このアウターギヤ５２をオスロータ２０の吸入側ロータ軸１０ａに取り付けたインナーギヤ５１と噛合させることで油冷式スクリュ圧縮機１を駆動できるようにしている。   In the embodiment shown in FIG. 1, one component of the gear coupling 50 is provided at one end of the suction side rotor shaft 10 a of the male rotor 10 in order to enable the input of the rotational driving force from such a driving source. The outer gear 52 which is the other component of the gear coupling 50 is attached to the flywheel 60 connected to the output shaft (not shown) of the drive source. Is engaged with an inner gear 51 attached to the suction-side rotor shaft 10a of the male rotor 20, so that the oil-cooled screw compressor 1 can be driven.

なお，図１に示す例では，オスロータ１０の吸入側ロータ軸１０ａと図示せざる駆動源の出力軸との連結を，ギヤカップリング５０及びフライホイール６０を介して行う構成としているが，駆動源とロータ軸間の連結は，図１に示す構成に限定されず，駆動源で発生した回転駆動力を入力できるものであれば他の連結手段や動力伝達手段を介して，又は，例えば駆動源の出力軸とオスロータ１０の吸入側ロータ軸１０ａを同一部材で形成する等，このよう連結手段や動力伝達手段を介さずに直接連結する構成を採用しても良い。   In the example shown in FIG. 1, the suction side rotor shaft 10a of the male rotor 10 and the output shaft of the drive source (not shown) are connected via the gear coupling 50 and the flywheel 60. The connection between the rotor shaft and the rotor shaft is not limited to the configuration shown in FIG. 1, and any other connection means or power transmission means can be used as long as the rotational driving force generated by the drive source can be input, or, for example, the drive source The output shaft and the suction-side rotor shaft 10a of the male rotor 10 may be directly connected without using any connecting means or power transmission means, for example, by using the same member.

一例として，図５に示す実施形態では，図１を参照して説明した構成に加えて，更にケーシング３０内にギヤ室７１を形成し，このギヤ室７１内に駆動ギヤ７２と従動ギヤ７３を収容して形成された増速装置７０を設けている。   As an example, in the embodiment shown in FIG. 5, in addition to the configuration described with reference to FIG. 1, a gear chamber 71 is further formed in the casing 30, and a drive gear 72 and a driven gear 73 are provided in the gear chamber 71. A speed increasing device 70 that is housed and formed is provided.

そして，この増速装置７０の駆動ギヤ７２に設けた入力軸７４を，カップリング５０及びフライホイール６０を介して図示せざる駆動源の出力軸に連結すると共に，従動ギヤ７３をオスロータ１０の吸入側ロータ軸１０ａに取り付けて，駆動源からの回転駆動力を増速してオスロータ１０の吸入側ロータ軸１０ａに入力することができるようにしている。   The input shaft 74 provided on the drive gear 72 of the speed increasing device 70 is connected to the output shaft of a drive source (not shown) via the coupling 50 and the flywheel 60, and the driven gear 73 is sucked into the male rotor 10. It is attached to the side rotor shaft 10 a so that the rotational driving force from the drive source can be accelerated and input to the suction side rotor shaft 10 a of the male rotor 10.

このように，オスロータ１０及びメスロータ２０を噛み合い回転可能に収容したシリンダ３０の吸入側端部は吸入通路３４と連通されており，この吸入通路３４を介してシリンダ３１内に導入された被圧縮気体をロータ１０，２０の噛み合い回転によって圧縮することができるようになっており，このような油冷式スクリュ圧縮機が備える基本構造については，図６を参照して説明した従来の油冷式スクリュ圧縮機と同様である。   In this way, the suction side end of the cylinder 30 that meshes with the male rotor 10 and the female rotor 20 and is rotatably accommodated communicates with the suction passage 34, and the compressed gas introduced into the cylinder 31 through the suction passage 34. Can be compressed by meshing rotation of the rotors 10 and 20, and the basic structure of such an oil-cooled screw compressor is described with reference to the conventional oil-cooled screw described with reference to FIG. It is the same as the compressor.

図６を参照して説明した従来の油冷式スクリュ圧縮機１００にあっては，オスロータ１１０の軸芯１１１と，メスロータ１２０の軸芯１２１とが水平方向に並んだ配置となるように，シリンダ１３１のオスロータ収容部１３１ａとメスロータ収容部１３１ｂについても水平方向に並んだ，軸直交方向の断面において横向き８の字状となるように配置した構成を採用すると共に，シリンダ１３１内に対する給油を，オスロータ収容部１３１ａの底部と，メスロータ収容部１３１ｂの底部にそれぞれ設けた給油口１３５，１３６を介して行う構成となっていた。   In the conventional oil-cooled screw compressor 100 described with reference to FIG. 6, the cylinder 111 is arranged so that the shaft core 111 of the male rotor 110 and the shaft core 121 of the female rotor 120 are arranged in the horizontal direction. The male rotor accommodating portion 131a and the female rotor accommodating portion 131b of 131 are arranged in a horizontal direction and arranged in a shape of 8 in the cross-section in the direction perpendicular to the axis, and the oil supply to the cylinder 131 is supplied to the male rotor. The configuration is such that it is performed through the oil filler ports 135 and 136 provided at the bottom of the housing portion 131a and the bottom of the female rotor housing portion 131b, respectively.

これに対し，本発明の油冷式スクリュ圧縮機１にあっては，シリンダ３１のオスロータ収容部３１ａをメスロータ収容部３１ｂに対し高所側に配置して，オスロータ収容部３１ａが，その底部においてメスロータ収容部３１ｂと連通するように構成すると共に，シリンダ３１内に対する給油を，メスロータ収容部３１ｂの内壁面において開口する給油口３５を介してのみ行う構成とした。   On the other hand, in the oil-cooled screw compressor 1 of the present invention, the male rotor accommodating portion 31a of the cylinder 31 is arranged on the high side with respect to the female rotor accommodating portion 31b, and the male rotor accommodating portion 31a is located at the bottom thereof. In addition to being configured to communicate with the female rotor accommodating portion 31b, oil supply to the cylinder 31 is performed only through the oil filler opening 35 opened on the inner wall surface of the female rotor accommodating portion 31b.

前述の給油口３５は，メスロータ収容部３１ｂを介してシリンダ３１内に潤滑油を供給することができるものであればメスロータ収容部３１ｂの内壁面のいずれの位置に開口するものとしても良い。   The above-described oil supply port 35 may be opened at any position on the inner wall surface of the female rotor housing portion 31b as long as it can supply lubricating oil into the cylinder 31 via the female rotor housing portion 31b.

一例として，図２に示す例では，給油口３５をメスロータ収容部３１ｂの内壁のうち，前記メスロータ収容部３１ｂの底部Ｂを通過した後，前記オスロータ１０と噛み合う前の前記メスロータ２０の歯溝２３が通過する位置で，オスロータ１０の軸芯１１とメスロータ２０の軸芯２１を結ぶ線に対し直交方向に開口するように設けており，この位置に給油口３５を設ける場合には，メスロータ収容部３１ｂの底部Ｂに溜まる潤滑油量を減少させることが可能となり，メスロータ２０の歯先２２が底部Ｂに溜まった潤滑油を攪拌する際に受ける抵抗についても低減させることができる。   As an example, in the example shown in FIG. 2, the tooth groove 23 of the female rotor 20 before meshing with the male rotor 10 after passing through the bottom B of the female rotor housing portion 31 b through the oil filler port 35 in the inner wall of the female rotor housing portion 31 b. Is provided so as to open in a direction orthogonal to the line connecting the shaft core 11 of the male rotor 10 and the shaft core 21 of the female rotor 20, and when the oil filler port 35 is provided at this position, the female rotor housing portion It is possible to reduce the amount of lubricating oil accumulated in the bottom B of 31b, and it is also possible to reduce the resistance that the tooth tip 22 of the female rotor 20 receives when stirring the lubricating oil accumulated in the bottom B.

すなわち，メスロータ収容部２０の底部Ｂに給油口３５を設けて給油を行う場合には，給油によって底部Ｂに直接潤滑油が溜まり，この底部に溜まった潤滑油をメスロータ２０の歯先２２が掻き上げることによってシリンダ３１の内壁やオス・メスロータ１０，２０の表面に対する潤滑油の拡散が行われる。   In other words, when the oil supply port 35 is provided at the bottom B of the female rotor housing portion 20 to supply oil, the lubricating oil is directly accumulated at the bottom B by the oil supply, and the tooth tip 22 of the female rotor 20 scrapes the lubricating oil accumulated at the bottom. Raising the lubricating oil diffuses the inner wall of the cylinder 31 and the surfaces of the male and female rotors 10 and 20.

これに対し，図２に示すように底部Ｂを通過した後，オスロータ１０と噛合する前のメスロータ２０の歯溝２３の通過位置において潤滑油を供給する構成では，給油口３５は底部Ｂよりも高所に設けられることとなり，給油口３５を介して給油された潤滑油は，直接，底部Ｂに溜まることができずに，一旦，メスロータ２０の追従側歯面２３ｂによって掻き上げられ，シリンダ３１の内壁，オスロータ１０やメスロータ２０の表面に付着して油膜を形成し，このような油膜の形成に使用された後の，残余の潤滑油が重力により落下してメスロータ収容部３１ｂの底部Ｂに溜まる。   On the other hand, as shown in FIG. 2, in the configuration in which the lubricating oil is supplied at the passing position of the tooth groove 23 of the female rotor 20 after meshing with the male rotor 10 after passing through the bottom portion B, the oil supply port 35 is more than the bottom portion B. The lubricating oil supplied through the oil supply port 35 cannot be directly accumulated in the bottom B, but is temporarily scraped up by the follow-up side tooth surface 23b of the female rotor 20 and is supplied to the cylinder 31. An oil film is formed by adhering to the inner wall of the rotor and the surfaces of the male rotor 10 and the female rotor 20, and after being used for forming such an oil film, the remaining lubricating oil falls due to gravity and falls on the bottom B of the female rotor accommodating portion 31b. Accumulate.

そのため，同量の給油を行った場合であっても，メスロータ収容部３１ｂの底部Ｂに直接給油口３５を開口して給油する場合に比較して，底部Ｂに溜まる潤滑油量を少なくすることができ，その結果，メスロータ２０の歯先２２がメスロータ収容部３１ｂの底部Ｂに溜まった潤滑油中を通過する際に受ける抵抗を減らすことができ，スクリュロータの回転抵抗をより一層低減することができる。   Therefore, even when the same amount of oil is supplied, the amount of lubricating oil accumulated in the bottom B is reduced as compared with the case where the oil supply port 35 is directly opened at the bottom B of the female rotor housing 31b. As a result, the resistance received when the tooth tip 22 of the female rotor 20 passes through the lubricating oil accumulated in the bottom B of the female rotor accommodating portion 31b can be reduced, and the rotational resistance of the screw rotor can be further reduced. Can do.

もっとも，前述したようにオスロータ１０に比較して，メスロータ２０の歯先が底部Ｂに溜まった潤滑油中を通過する際に受ける抵抗は小さいことから，図３に示すように給油口３５をメスロータ収容部３１ｂの底部Ｂで開口させるものとしても良い。   However, as described above, since the resistance received when the tooth tip of the female rotor 20 passes through the lubricating oil accumulated in the bottom B is smaller than that of the male rotor 10, as shown in FIG. It is good also as what opens at the bottom part B of the accommodating part 31b.

なお，図２，３に示す例では，シリンダ３１のオスロータ収容部３１ａをメスロータ収容部３１ｂの真上に形成して，オスロータ１０の軸芯１１とメスロータ２０の軸芯２１が同一垂線ＶＬ上に配置されるようにした構成例を示したが，オスロータ収容部３１ａとメスロータ収容部３１ｂの配置は，オスロータ収容部３１ａに油溜まりとなる底部が形成されない構成であれば，図２及び図３に示した配置に限定されず，図４に示すように，オスロータ１０の軸芯１１を通る垂線ＶＬが，オスロータ収容部３１ａとメスロータ収容部３１ｂの境界部分に形成された２つの山形部３２，３３の頂点３２ａ，３３ａ間の範囲内であれば図２及び図３に示した配置に対し傾斜させた配置とすることも可能である。   2 and 3, the male rotor accommodating portion 31a of the cylinder 31 is formed immediately above the female rotor accommodating portion 31b, and the shaft core 11 of the male rotor 10 and the shaft core 21 of the female rotor 20 are on the same perpendicular line VL. Although the example of a structure made to arrange | position was shown, if arrangement | positioning of the male rotor accommodating part 31a and the female rotor accommodating part 31b is a structure by which the bottom part used as an oil sump is not formed in the male rotor accommodating part 31a, FIG.2 and FIG.3. As shown in FIG. 4, the vertical line VL passing through the axis 11 of the male rotor 10 is not limited to the arrangement shown, and the two chevron portions 32 and 33 are formed at the boundary between the male rotor accommodating portion 31a and the female rotor accommodating portion 31b. As long as it is within the range between the vertices 32a and 33a, it is possible to make the arrangement inclined with respect to the arrangement shown in FIGS.

シリンダ３１の傾きが前述した範囲内であれば，常に何れかの山形部３２，３３の頂点３２ａ，３３ａがオスロータ収容部３１ａの内壁面中，最下端にあることとなるため，オスロータ収容部３１ａの内壁を伝って落下する潤滑油は，オスロータ収容部３１ａ内に留まることができずにメスロータ収容部３１ｂに落下する。   If the inclination of the cylinder 31 is within the above-described range, the apex 32a, 33a of any one of the chevron portions 32, 33 is always at the lowermost end of the inner wall surface of the male rotor housing portion 31a. Lubricating oil falling along the inner wall of the rotor cannot stay in the male rotor housing portion 31a and falls into the female rotor housing portion 31b.

その結果，オスロータ収容部３１ａには油溜まりが形成されることがなく，オスロータ１０の歯先１２が油溜まり内を通過することも無いため，オスロータ１０が回転時に潤滑油を噛み込むことで受ける負荷を確実に低下させることができる。   As a result, no oil sump is formed in the male rotor accommodating portion 31a, and the tooth tip 12 of the male rotor 10 does not pass through the oil sump, so that the male rotor 10 receives the lubricating oil during rotation. The load can be reliably reduced.

以上のように構成された本発明の油冷式スクリュ圧縮機１において，運転時にはメスロータ収容部３１ｂの内壁面に開口した給油口３５を介して，メスロータ２０の歯溝２３とメスロータ収容部内壁で区画された，図２，３中に斜線で示した作用空間内に潤滑油が給油される。この潤滑油は，メスロータ２０の回転によって上方へ掻き上げられて飛沫となり，オスロータ１０とメスロータ２０の噛み合い部へ給油されると共に，オスロータ１０の歯溝１３とオスロータ収容部３１ａの内壁とによって区画された作用空間に対しても給油される。   In the oil-cooled screw compressor 1 of the present invention configured as described above, during operation, the tooth groove 23 of the female rotor 20 and the inner wall of the female rotor housing portion are provided via the oil supply port 35 opened in the inner wall surface of the female rotor housing portion 31b. Lubricating oil is supplied into the partitioned working space indicated by hatching in FIGS. This lubricating oil is scraped upward by the rotation of the female rotor 20 and becomes splashed, and is supplied to the meshing portion of the male rotor 10 and the female rotor 20, and is partitioned by the tooth groove 13 of the male rotor 10 and the inner wall of the male rotor accommodating portion 31a. Even the working space is refueled.

この給油により，オス・メス両ロータ１０，２０間の潤滑や密封，ロータ１０，２０とシリンダ３１内壁間の密封，ロータ１０，２０や圧縮空気の冷却が行われる。   This lubrication provides lubrication and sealing between the male and female rotors 10 and 20, sealing between the rotors 10 and 20 and the inner wall of the cylinder 31, and cooling of the rotors 10 and 20 and compressed air.

給油された潤滑油のうち重力により落下したものはメスロータ収容部３１ｂの底部Ｂに溜まり，メスロータ２０の追従側歯面２３ｂによって吐出側へ搬送され，圧縮気体と共に図示せざる吐出口を介してシリンダ３１外へ吐出される。   Of the lubricated oil, the oil that has fallen due to gravity is collected at the bottom B of the female rotor accommodating portion 31b, conveyed to the discharge side by the follow-side tooth surface 23b of the female rotor 20, and cylinders via the discharge port (not shown) together with the compressed gas. 31 is discharged to the outside.

オスロータ収容部３１ａは，その底部においてメスロータ収容部３１ｂと連通しているため，オスロータ収容部３１ａには油溜まりとなる底部が存在しておらず，しかも，オスロータ収容部３１ａに対する給油は前述したようにメスロータ収容部３１ｂを介して間接的に行われ，オスロータ収容部３１ａに対する直接の給油は行われていないことから，オスロータ１０の前進側歯面１２ａとシリンダ３１の内壁面とによって画成された比較的大きなくさび形の空間Ｗ1内には比較的少量の潤滑油しか存在せず，潤滑油の噛み込みによってオスロータ１０が受ける回転抵抗は僅かである。   Since the male rotor accommodating portion 31a communicates with the female rotor accommodating portion 31b at the bottom thereof, the male rotor accommodating portion 31a does not have a bottom portion serving as an oil reservoir, and oil supply to the male rotor accommodating portion 31a is as described above. This is indirectly performed through the female rotor accommodating portion 31b and is not directly lubricated with respect to the male rotor accommodating portion 31a, and thus is defined by the advancing side tooth surface 12a of the male rotor 10 and the inner wall surface of the cylinder 31. There is only a relatively small amount of lubricating oil in the relatively large wedge-shaped space W1, and the rotational resistance received by the male rotor 10 due to the engagement of the lubricating oil is small.

なお，オスロータ１０とメスロータ２０の噛み合い部分は，ロータの軸線方向に連なるシール線を形成し，このシール線は圧縮過程にある作用空間と吸い込み過程にある作用空間の仕切り線となっている。   Note that the meshing portion of the male rotor 10 and the female rotor 20 forms a seal line continuous in the axial direction of the rotor, and this seal line is a partition line between the working space in the compression process and the working space in the suction process.

そのため，シール線を挟んで隣接する作用空間同士には圧力差が生じており，噛み合い部に導入された潤滑油は，圧縮過程にある作用空間のシール線近傍に集まりつつ，圧縮過程にある作用空間から吸い込み過程にある作用空間へと圧縮気体と潤滑油が激しく流れ込もうとしている。   For this reason, there is a pressure difference between the adjacent working spaces across the seal line, and the lubricant introduced into the meshing part gathers near the seal line in the working space in the compression process and acts in the compression process. Compressed gas and lubricating oil are violently flowing from the space into the working space in the suction process.

圧縮過程にある作用空間のシール線近傍では，オスロータの歯面とメスロータの歯面によりくさび状の空間が形成されており，このくさび状の空間内にある潤滑油は，オスロータ１０の歯面によって噛み込まれ，押しつぶされるように回転方向へ移動することから，オス，メス両ロータ１０，２０の噛み合い部に形成されたこのくさび状空間部に集まる潤滑油の量が多い場合にも，潤滑油がオス及びメスロータ１０，２０の回転に対し大きな抵抗を与えることとなるために消費動力の増大をもたらす。   In the vicinity of the seal line of the working space in the compression process, a wedge-shaped space is formed by the tooth surface of the male rotor and the tooth surface of the female rotor. The lubricating oil in this wedge-shaped space is absorbed by the tooth surface of the male rotor 10. Even if there is a large amount of lubricating oil gathered in the wedge-shaped space formed in the meshing portions of both the male and female rotors 10 and 20 because they move in the rotational direction so as to be bitten and crushed, Provides a large resistance to the rotation of the male and female rotors 10 and 20, resulting in an increase in power consumption.

しかし，本発明の油冷式スクリュ圧縮機１の構成では，オスロータ１０に対し直接の給油を行っておらず，オスロータ１０に対する給油量自体が少ないこと，オスロータ収容部３１ａに導入された潤滑油は重力によりメスロータ収容部へ流下するため，オスロータ収容部３１ａ内には必要以上の潤滑油が存在できないこと，油溜まりとなっているメスロータ収容部３１ｂの底部Ｂに対し，噛み合い部が十分に高い位置にあること等から，図６を参照して説明した従来の油冷式スクリュ圧縮機１００の構造を採用する場合に比較して，噛み合い部に対して供給される潤滑油量についても減少させることができるものとなっており，この点においても本発明の油冷式スクリュ圧縮機１ではオス・メスロータ１０，２０の回転抵抗を小さくすることが可能で，より一層の消費動力の低減が実現できるものとなっている。   However, in the configuration of the oil-cooled screw compressor 1 of the present invention, the oil supply to the male rotor 10 is not performed directly, the amount of oil supply to the male rotor 10 is small, and the lubricating oil introduced into the male rotor housing portion 31a is Since gravity flows down to the female rotor housing portion, there is no more lubricating oil than necessary in the male rotor housing portion 31a, and the position where the meshing portion is sufficiently high with respect to the bottom B of the female rotor housing portion 31b that is an oil reservoir Therefore, the amount of lubricating oil supplied to the meshing portion can be reduced as compared with the case where the structure of the conventional oil-cooled screw compressor 100 described with reference to FIG. 6 is adopted. Also in this respect, the oil-cooled screw compressor 1 of the present invention reduces the rotational resistance of the male and female rotors 10 and 20. Possible, which is assumed to further reduce the consumption power can be realized.

１ 油冷式スクリュ圧縮機
１０ オスロータ
１０ａ 吸入側ロータ軸
１０ｂ 吐出側ロータ軸
１１ 軸芯（オスロータの）
１２ 歯先
１２ａ 前進側歯面
１２ｂ 追従側歯面
１３ 歯溝
２０ メスロータ
２１ 軸芯（メスロータの）
２２ 歯先
２３ 歯溝
２３ａ 前進側歯面
２３ｂ 追従側歯面
３０ ケーシング
３１ シリンダ
３１ａ オスロータ収容部
３１ｂ メスロータ収容部
３２，３３ 山形部
３２ａ，３３ａ 頂点（山形部３２，３３の）
３４ 吸入通路
３５ 給油口
４１〜４４ 軸受
５０ カップリング（ギヤカップリング）
５１ インナーギヤ
５２ アウターギヤ
６０ フライホイール
７０ 増速装置
７１ ギヤ室
７２ 駆動ギヤ
７３ 従動ギヤ
７４ 入力軸
ＶＬ 垂線
Ｂ 底部（メスロータ収容部の）
Ｗ1，Ｗ2 くさび型の空間
１００ 油冷式スクリュ圧縮機
１１０ オスロータ
１１１ 軸芯（オスロータの）
１１２ 歯先
１１２ａ 前進側歯面
１１３ 歯溝
１２０ メスロータ
１２１ 軸芯（メスロータの）
１２２ 歯先
１２３ 歯溝
１２３ｂ 追従側歯面
１３０ ケーシング
１３１ シリンダ
１３１ａ オスロータ収容部
１３１ｂ メスロータ収容部
１３４ 吸入通路
１３５，１３６ 給油口 DESCRIPTION OF SYMBOLS 1 Oil-cooled screw compressor 10 Male rotor 10a Suction side rotor shaft 10b Discharge side rotor shaft 11 Shaft core (male rotor)
12 tooth tip 12a advance side tooth surface 12b follow side tooth surface 13 tooth groove 20 female rotor 21 shaft core (of female rotor)
22 tooth tip 23 tooth gap 23a advance side tooth surface 23b follow side tooth surface 30 casing 31 cylinder 31a male rotor accommodating portion 31b female rotor accommodating portion 32, 33 chevron portion 32a, 33a apex (of chevron portion 32, 33)
34 Suction passage 35 Refueling port 41 to 44 Bearing 50 Coupling (gear coupling)
51 inner gear 52 outer gear 60 flywheel 70 speed increasing device 71 gear chamber 72 drive gear 73 driven gear 74 input shaft VL perpendicular B bottom (of the female rotor housing)
W1, W2 wedge-shaped space 100 Oil-cooled screw compressor 110 Male rotor 111 Shaft core (male rotor)
112 tooth tip 112a advance side tooth surface 113 tooth gap 120 female rotor 121 shaft core (of female rotor)
122 tooth tip 123 tooth gap 123b following side tooth surface 130 casing 131 cylinder 131a male rotor accommodating portion 131b female rotor accommodating portion 134 suction passage 135,136 oil supply port

Claims (4)

相互に噛み合い回転するオスロータ及びメスロータから成る一対のスクリュロータと，前記一対のスクリュロータを噛み合い回転可能に収容するシリンダが内部に形成されたケーシングを備え，前記シリンダが，オスロータ収容部となる円筒部とメスロータ収容部となる円筒部とを平行に配置すると共に，前記オスロータ収容部とメスロータ収容部の周方向における一部分を重ねて連通し，前記シリンダの軸直交方向の断面が略８の字状に形成され，前記シリンダ内に潤滑油を供給して被圧縮気体を圧縮する油冷式スクリュ圧縮機において，
前記シリンダの前記オスロータ収容部を前記メスロータ収容部に対し高所側に形成すると共に，前記オスロータ収容部の底部を前記メスロータ収容部と連通し，
前記シリンダ内に潤滑油を供給する給油口を，前記メスロータ収容部の内壁面にのみ開口することを特徴とする油冷式スクリュ圧縮機。 A cylindrical portion that includes a pair of screw rotors that are meshed and rotated with each other, and a casing in which a cylinder that meshes with and rotates and accommodates the pair of screw rotors is formed. And a cylindrical portion serving as a female rotor accommodating portion are arranged in parallel, and a part of the male rotor accommodating portion and a female rotor accommodating portion in the circumferential direction are overlapped and communicated with each other, so that a cross section in the axis-perpendicular direction of the cylinder is approximately 8 characters. In the oil-cooled screw compressor formed and supplied with lubricating oil into the cylinder to compress the compressed gas,
The male rotor housing portion of the cylinder is formed on the high side with respect to the female rotor housing portion, and the bottom of the male rotor housing portion is communicated with the female rotor housing portion,
An oil-cooled screw compressor, wherein an oil supply port for supplying lubricating oil into the cylinder is opened only on an inner wall surface of the female rotor housing portion. 前記オスロータの軸芯を通る垂線が，前記オスロータ収容部とメスロータ収容部との境界に形成された２つ山形部のうち何れか一方の山形部の頂点を通る位置から，他方の山形部の頂点を通る位置間にあるよう前記シリンダを形成したことを特徴とする請求項１記載の油冷式スクリュ圧縮機。   From the position where the perpendicular passing through the axis of the male rotor passes through the apex of one of the two chevron parts formed at the boundary between the male rotor accommodating part and the female rotor accommodating part, the apex of the other chevron part 2. The oil-cooled screw compressor according to claim 1, wherein the cylinder is formed so as to be between positions passing through the cylinder. 前記給油口を，前記メスロータ収容部の底部を通過した後，前記オスロータと噛み合う前の前記メスロータの歯溝の通過位置において前記メスロータ収容部の内壁面に開口したことを特徴とする請求項１又は２記載の油冷式スクリュ圧縮機。   The said oil filler opening was opened in the inner wall surface of the said female rotor accommodating part in the passage position of the tooth gap of the said female rotor after meshing with the said male rotor after passing the bottom part of the said female rotor accommodating part. 2. The oil-cooled screw compressor according to 2. 前記給油口を，前記メスロータ収容部の底部の内壁面に開口したことを特徴とする請求項１又は２記載の油冷式スクリュ圧縮機。   The oil-cooled screw compressor according to claim 1 or 2, wherein the oil supply port is opened in an inner wall surface of a bottom portion of the female rotor housing portion.
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CN108443144A (en) * 2018-04-02 2018-08-24 宁波英德菲尔机械科技有限公司 A kind of novel oil-free helical-lobe compressor
JPWO2019207945A1 (en) * 2018-04-26 2021-03-11 株式会社日立産機システム Liquid supply type screw compressor
CN111936745A (en) * 2018-04-26 2020-11-13 株式会社日立产机*** Liquid supply type screw compressor
WO2019207945A1 (en) * 2018-04-26 2019-10-31 株式会社日立産機システム Liquid supply type screw compressor
KR20210029261A (en) 2018-08-27 2021-03-15 가부시키가이샤 고베 세이코쇼 Liquid-cooled screw compressor
CN109058103A (en) * 2018-09-25 2018-12-21 宁波鲍斯能源装备股份有限公司 Water jet helical-lobe compressor
WO2020084916A1 (en) * 2018-10-26 2020-04-30 株式会社日立産機システム Screw compressor
CN113167278A (en) * 2018-10-26 2021-07-23 株式会社日立产机*** Screw compressor
JP2020067064A (en) * 2018-10-26 2020-04-30 株式会社日立産機システム Screw compressor
JP7229720B2 (en) 2018-10-26 2023-02-28 株式会社日立産機システム screw compressor
US11719241B2 (en) 2018-10-26 2023-08-08 Hitachi Industrial Equipment Systems Co., Ltd. Screw compressor having a lubrication path for a plurality of suction side bearings

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