JP7037448B2 - Screw compressor body - Google Patents

Screw compressor body Download PDF

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JP7037448B2
JP7037448B2 JP2018136355A JP2018136355A JP7037448B2 JP 7037448 B2 JP7037448 B2 JP 7037448B2 JP 2018136355 A JP2018136355 A JP 2018136355A JP 2018136355 A JP2018136355 A JP 2018136355A JP 7037448 B2 JP7037448 B2 JP 7037448B2
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discharge
rotor
screw rotor
main body
female screw
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JP2020012439A (en
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佑樹 谷山
紘太郎 千葉
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Hitachi Industrial Equipment Systems Co Ltd
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Hitachi Industrial Equipment Systems Co Ltd
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Description

本発明は、スクリュー圧縮機本体に係り、圧縮作動空間内に供給された液体とともに吸込み気体を圧縮し、吐き出すスクリュー圧縮機本体に関する。 The present invention relates to a screw compressor main body, and relates to a screw compressor main body that compresses a suction gas together with a liquid supplied in a compression working space and discharges the suction gas.

複数のロータ（例えば、少なくとも１つの雄雌スクリューロータ）の歯溝が噛み合い、回転することで作動気体を圧縮するスクリュー圧縮機では、潤滑や冷却を目的として、ロータを格納する空間に油や水といった液体を供給する給液式のものが知られている。供給された液体は、圧縮される作動気体とともに吐出端面まで移動し、吐出ポートから排出されるようになっている。 In a screw compressor in which the tooth grooves of a plurality of rotors (for example, at least one male and female screw rotor) mesh with each other and rotate to compress the working gas, oil or water is used in the space for storing the rotors for lubrication and cooling purposes. A liquid supply type that supplies such a liquid is known. The supplied liquid moves to the discharge end face together with the compressed working gas and is discharged from the discharge port.

圧縮工程中の２つのロータ間がつくる容積（以下、「作動空間容積」という場合がある。）と、吐出ポートとが連通する部分の面積（以下、「連通面積」という場合がある。）とは、ロータの回転に伴って時々刻々と変化し、圧縮機体及び液体を吐き出していくが、通常液体は圧縮機体よりも比重が大きいために、液体は圧縮気体よりも後に吐き出される。
したがって、作動空間が吐出ポートと連通開始直後は、吐出は、液体が圧縮気体に対して大きな割合となり、吐出完了直前では、液体が圧縮気体に対して大きな割合となる。 The volume created between the two rotors during the compression process (hereinafter, may be referred to as "working space volume") and the area of the portion where the discharge port communicates (hereinafter, may be referred to as "communication area"). Changes momentarily with the rotation of the rotor and discharges the compressor body and the liquid. However, since the liquid usually has a larger specific gravity than the compressor body, the liquid is discharged after the compressed gas.
Therefore, immediately after the working space starts communicating with the discharge port, the liquid has a large ratio with respect to the compressed gas, and immediately before the discharge is completed, the liquid has a large ratio with respect to the compressed gas.

吐出完了直前での吐出ポートの連通面積は吐出開始時のそれに比べて小さい。より小さい連通面積で液体が大きな割合で吐き出されることから、液体の粘性摩擦を伴いその空間において液体が詰まるような現象を招来し、圧力損失の原因にもなる。即ち吐出完了の直前（連通面積がゼロとなる手前の状態）には、吐き出されずに詰まった液体が雌ロータ吐出側端面に覆われ、わずかに連通する吐出ポートに対して圧縮気体の吐出しによるロータ軸方向の流れを妨げ、吐出ポートが密閉状態となり、液体の吐出しが不完全となる。不完全な液体の吐出しは、作動空間容積と吐出ポートが連通する面積をその分小さくするため、圧力損失を招来するばかりでなく、滞留部からしばらくして流出した液体が吐出ポートの先の流路で作動気体へ撹拌作用を招き損失の原因ともなる。 The communication area of the discharge port immediately before the completion of discharge is smaller than that at the start of discharge. Since the liquid is discharged at a large rate in a smaller communication area, the viscous friction of the liquid causes a phenomenon that the liquid is clogged in the space, which also causes a pressure loss. That is, immediately before the completion of discharge (the state before the communication area becomes zero), the liquid that is clogged without being discharged is covered with the end face on the discharge side of the female rotor, and the compressed gas is discharged to the discharge port that communicates slightly. The flow in the rotor axial direction is obstructed, the discharge port is closed, and the liquid is incompletely discharged. Incomplete discharge of liquid not only causes pressure loss because the area where the working space volume and the discharge port communicate with each other is reduced by that amount, but also the liquid that flows out from the stagnant part after a while is connected to the tip of the discharge port. It causes a stirring action on the working gas in the flow path and causes a loss.

特許文献１は、液体として油を、圧縮気体として空気を適用するスクリュー圧縮機であって、「作動油を収容する油分収容部が第１ロータや第２ロータに設けられているスクリュー圧縮機で、油分収容部が圧縮室と作動室を連通しない」構成を開示する。より具体的には、雄ロータ各歯の吐出側端面に、歯先から軸心寄りに向かって凹部を備え、当該凹部に油を逃がしさ、逃がした油を吐出開始時から圧縮空気とともに吐き出すことで、油の吐出しを安定させる技術を開示する。 Patent Document 1 is a screw compressor that applies oil as a liquid and air as a compressed gas, and is a screw compressor in which an oil content accommodating portion for accommodating hydraulic oil is provided in a first rotor or a second rotor. , The oil storage unit does not communicate with the compression chamber and the working chamber. " More specifically, the discharge side end face of each male rotor tooth is provided with a recess from the tip of the tooth toward the axis, and oil is released into the recess, and the released oil is discharged together with compressed air from the start of discharge. So, we disclose the technology to stabilize the discharge of oil.

特許文献２は、液体として油を、圧縮気体として空気を適用するスクリュー圧縮機であって、「吐出ポートの上部の近傍に位置する部分と、吐出圧力以下の圧力にある作動空間とを連通する油流出経路通路を設けた」構成を開示する。より具体的には、作動油を吐出ポート上部に設けた油回収経路を経て、吐出圧力よりも低い圧力空間へ戻すことにより、吐出ポート上部の油の詰まりを軽減させ且つ吐出ポートの先の流路（吐出後半の狭小な連通面積）に油をできるだけ排出しない技術を開示する。これにより、作動空間容積と吐出ポートとの連通面積を確保し且つ吐出ポートの先の流路における撹拌損失を低減している。 Patent Document 2 is a screw compressor that applies oil as a liquid and air as a compressed gas, and "communicate between a portion located near the upper part of a discharge port and an operating space at a pressure equal to or lower than the discharge pressure. The configuration of "providing an oil outflow route passage" is disclosed. More specifically, by returning the hydraulic oil to the pressure space lower than the discharge pressure via the oil recovery path provided in the upper part of the discharge port, the clogging of the oil in the upper part of the discharge port is reduced and the flow at the tip of the discharge port is reduced. Disclose a technology that minimizes oil discharge to the road (narrow communication area in the latter half of discharge). As a result, the communication area between the working space volume and the discharge port is secured, and the stirring loss in the flow path at the end of the discharge port is reduced.

特開２０１５－８６７８２号公報Japanese Unexamined Patent Publication No. 2015-86782 特開２００８－２９７９４４号公報Japanese Unexamined Patent Publication No. 2008-297944

ここで、特許文献１に記載されているスクリュー圧縮機は圧縮空気の吐出開始直後（吐出ポート下部）の工程で油と圧縮空気とを分離する構造によって、圧力損失及び撹拌損失の低減に有効な手段であるが、吐出完了直前に油の吐出には改善の余地が残るともいえる。 Here, the screw compressor described in Patent Document 1 is effective in reducing pressure loss and stirring loss due to a structure that separates oil and compressed air in the process immediately after the start of discharge of compressed air (lower part of the discharge port). Although it is a means, it can be said that there is room for improvement in the discharge of oil immediately before the completion of discharge.

特許文献２に記載されているスクリュー圧縮機はケーシングの加工により雄雌ロータの吐出完了直前における油を吐出圧力以下の圧力部分へ排出し、圧力損失および撹拌損失の低減に有効な手段であるが、圧縮過程で高温高圧となった油を低圧側へ戻すことによる動力の増加、ケーシングへの加工工数の増加という改善の余地が残る。
圧縮空気の吐出完了直前における圧力損失、撹拌損失を低減し、エネルギー効率の向上を両立する技術が望まれる。 The screw compressor described in Patent Document 2 is an effective means for reducing pressure loss and stirring loss by discharging oil to a pressure portion below the discharge pressure immediately before the completion of discharge of the male and female rotors by processing the casing. There is still room for improvement, such as an increase in power by returning the oil that has become high temperature and high pressure in the compression process to the low pressure side, and an increase in the number of processing steps for the casing.
A technology that reduces pressure loss and stirring loss immediately before the completion of discharge of compressed air and improves energy efficiency is desired.

上記課題を解決するために、例えば特許請求の範囲に記載の構成を適用する。即ち、ローブを有し少なくとも１つずつの雄スクリューロータ及び雌スクリューロータと、前記雄スクリューロータ及び前記雌スクリューロータを格納して圧縮作動空間及び吸込作動空間を構成するケーシングとを備え、圧縮作動空間に供給された液体と吸込み気体を圧縮し、前記雄スクリューロータ及び前記雌スクリューロータの吐出側端面に対向する吐出ポートから圧縮混合気体を吐き出すスクリュー圧縮機本体であって、前記雌スクリューロータが、軸方向に深さを有する凹部を前記吐出側端面に備え、前記凹部は、前記雌スクリューロータが吐出完了直後の位置のときに、前記雌スクリューロータの軸方向に対しては前記吐出ポートに連通すると共に、前記雌スクリューロータの周方向に対しては前記雌スクリューロータの回転方向の吸込作動空間には連通せずに反回転方向の圧縮作動空間にのみ連通するものであるスクリュー圧縮機本体である。 In order to solve the above problems, for example, the configuration described in the claims is applied. That is, it includes at least one male screw rotor and one female screw rotor having a lobe, and a casing for accommodating the male screw rotor and the female screw rotor to form a compression operation space and a suction operation space . A screw compressor main body that compresses the liquid and suction gas supplied to the compression working space and discharges the compressed mixed gas from the discharge port facing the discharge side end faces of the male screw rotor and the female screw rotor . The female screw rotor is provided with a recess having a depth in the axial direction on the discharge side end face, and the recess is provided with respect to the axial direction of the female screw rotor when the female screw rotor is in a position immediately after the discharge is completed. Communicates with the discharge port and does not communicate with the suction working space in the rotational direction of the female screw rotor but only with the compression working space in the counter-rotating direction with respect to the circumferential direction of the female screw rotor. A screw compressor body.

本発明によれば、雌ロータ吐出側端面に凹部を備えることで、吐出完了直前時に生じる吐出ポート上部における液体の詰まり部分へ圧縮気体を流入できるような構造を有することにより、吐出完了直前の液体の詰まりを軽減し、圧力損失の低減且つエネルギー効率を向上させることができる。
本発明の他の課題・構成・効果は、以下の記載から明らかになる。 According to the present invention, by providing a recess on the discharge side end face of the female rotor, a structure is provided so that the compressed gas can flow into the clogged portion of the liquid in the upper part of the discharge port that occurs immediately before the completion of discharge, so that the liquid immediately before the completion of discharge is provided. It is possible to reduce the clogging of the gas, reduce the pressure loss, and improve the energy efficiency.
Other problems, configurations, and effects of the present invention will be clarified from the following description.

本発明を適用した実施例１によるスクリュー圧縮機本体の縦断面、スクリューロータの吐出側端面及び吐出ポートの構成を模式的に示す図である。It is a figure which shows typically the structure of the vertical cross section of the screw compressor main body, the discharge side end face of a screw rotor, and a discharge port according to Example 1 to which this invention is applied. 実施例１による吐出ポート周辺部分を拡大した様及び雌ロータ吐出側端面に備える凹部の構成を模式的に示す図である。It is a figure which shows typically the structure of the concave part provided in the female rotor discharge side end face, and the appearance which the peripheral part of the discharge port by Example 1 was enlarged. 実施例１による吐出ポートの開口の様を模式的に示す状態遷移図である。It is a state transition diagram schematically showing the opening of the discharge port according to the first embodiment. 比較例による吐出ポート周辺部分を拡大した様を模式的に示す図である。It is a figure which shows typically the appearance that the peripheral part of the discharge port by a comparative example was enlarged. 本発明を適用した実施例２による吐出ポート周辺部分を拡大した様を模式的に示す図である。It is a figure which shows typically the appearance that the peripheral part of the discharge port by Example 2 to which this invention was applied was enlarged.

以下、図面を用いて、本発明を実施するための形態を詳細に説明する。 Hereinafter, embodiments for carrying out the present invention will be described in detail with reference to the drawings.

図１に、本発明を適用した実施例１による給油式スクリュー空気圧縮機本体１００（以下、単に「圧縮機１００」と称する場合がある。）の構成を模式的に示す。図１（ａ）は、軸方向縦断面を示し、図１（ｂ）は、吐出側断面（図１（ａ）の一点鎖線矢視Ａ）を示す。
図１（ａ）、（ｂ）おいて、圧縮機１００は、互いに噛み合う螺旋状のローブを有する雌ロータ１及び雄ロータ２と、これらを格納する円筒空間３、吸込流路９、圧縮空気と油の混合気体を吐き出す吐出ポート５及び吐出ポート５を介して吐き出された混合気体が流通する吐出流路６を備えるケーシング７とを備える。雄ロータ２は、ロータシャフトに接続された駆動源（例えば、電動機や内燃機関等）から回転動力を受け、雄ロータ２の回転に伴いローブの前進面が雌ロータ１のローブ後進面と摺動することで一対の雄雌ロータが回転するようになっている。本実施例では、雌ロータ１は吐出方向に対して時計回り（図１（ｂ）において、反時計回り。）に回転し、雄ロータ２は、吐出方向に対して反時計回り（図１（ｂ）において、時計回り。）に回転する。 FIG. 1 schematically shows the configuration of a refueling type screw air compressor main body 100 (hereinafter, may be simply referred to as “compressor 100”) according to the first embodiment to which the present invention is applied. FIG. 1 (a) shows a vertical cross section in the axial direction, and FIG. 1 (b) shows a cross section on the discharge side (one-dot chain line arrow A in FIG. 1 (a)).
In FIGS. 1A and 1B, the compressor 100 includes a female rotor 1 and a male rotor 2 having spiral lobes that mesh with each other, a cylindrical space 3 for accommodating them, a suction flow path 9, and compressed air. It includes a discharge port 5 for discharging the mixed gas of oil and a casing 7 provided with a discharge flow path 6 through which the mixed gas discharged through the discharge port 5 flows. The male rotor 2 receives rotational power from a drive source (for example, an electric motor, an internal combustion engine, etc.) connected to the rotor shaft, and the forward surface of the lobe slides with the reverse surface of the lobe of the female rotor 1 as the male rotor 2 rotates. By doing so, the pair of male and female rotors rotate. In this embodiment, the female rotor 1 rotates clockwise with respect to the discharge direction (counterclockwise in FIG. 1B), and the male rotor 2 rotates counterclockwise with respect to the discharge direction (FIG. 1 (FIG. 1). In b), it rotates clockwise.).

ケーシング７は、円筒空間３を有するケーシング本体７ａと、吐出流路６を有する吐出ケーシング７ｂとから成る。ケーシング本体７ａは、円筒空間３の一側が連通する吸込み通路９を有すると共に円筒空間３の他側が開口する側端面を有する。また、ケーシング本体７ａは、外部から供給される油が圧縮機室に流通する給油路１０を有する。給油路１０は、円筒空間３の雌ロータ１側及び雄ロータ２側にそれぞれ開口する。吸込流路９は、両ロータ１、２の中心を結ぶ線Ｂより上側（吐出ポート５とはロータ軸線に対して逆側）に配置する。 The casing 7 includes a casing main body 7a having a cylindrical space 3 and a discharge casing 7b having a discharge flow path 6. The casing body 7a has a suction passage 9 through which one side of the cylindrical space 3 communicates, and has a side end surface through which the other side of the cylindrical space 3 opens. Further, the casing main body 7a has a refueling passage 10 through which oil supplied from the outside flows to the compressor chamber. The refueling passage 10 opens on the female rotor 1 side and the male rotor 2 side of the cylindrical space 3, respectively. The suction flow path 9 is arranged above the line B connecting the centers of the rotors 1 and 2 (on the opposite side of the rotor axis from the discharge port 5).

吐出ケーシング７ｂは、ケーシング本体７ａの吐出側端面と円筒空間３の開口を覆うように接続する。図１（ｂ）に示すように、ケーシング７ｂは、吐出ポート５（点線）を有する。吐出ポート５は、両ロータ１及び２の回転に伴って部分的に開口するようになっている（図１（ｂ）の黒塗部分）。 The discharge casing 7b is connected so as to cover the discharge side end surface of the casing main body 7a and the opening of the cylindrical space 3. As shown in FIG. 1 (b), the casing 7b has a discharge port 5 (dotted line). The discharge port 5 is partially opened as the rotors 1 and 2 rotate (black-painted portion in FIG. 1 (b)).

吐出ポート５は、吐出通路６に連通する構成となる。吐出流路６は両ロータ１、２の中心を結ぶ線１８より下側（吸込流路９とロータ軸線に対して逆側。）に配置する。この吐出流路６は、ロータ軸線に対して全体が斜め下方（ロータ軸線から離れる方向）に延在する。なお、吐出流路６が斜め下方に延在する形状となるのは、軸受室８を避けるためである。 The discharge port 5 is configured to communicate with the discharge passage 6. The discharge flow path 6 is arranged below the line 18 connecting the centers of the rotors 1 and 2 (on the opposite side of the suction flow path 9 and the rotor axis). The entire discharge flow path 6 extends diagonally downward (direction away from the rotor axis) with respect to the rotor axis. The shape of the discharge flow path 6 extending diagonally downward is to avoid the bearing chamber 8.

また、吐出流路６は、吐出ポート５の雌ロータ１側の上部から軸方向に向かって一部延在するポケット部１２を有する。図２（ａ）に、雌ロータ１の吐出側及び吐出流路６周辺の縦断面拡大図を示す。ポケット部１２は、吐出完了直前に吐出割合が高くなる油の油溜りとして機能する空間である。図２（ａ）では、油溜りをハッチングで模式的に示している。なお、吐出ポート５の上部は、雌ロータ１、雄ロータ２の吐出側端面が吐出ポート５に連通した後、吐出完了直前まで圧縮作動室と連通する部分である（ポケット部１２と軸方向投影面で重なる部分）。 Further, the discharge flow path 6 has a pocket portion 12 that partially extends in the axial direction from the upper portion of the discharge port 5 on the female rotor 1 side. FIG. 2A shows an enlarged vertical cross-sectional view of the female rotor 1 on the discharge side and around the discharge flow path 6. The pocket portion 12 is a space that functions as an oil reservoir in which the discharge ratio increases immediately before the completion of discharge. In FIG. 2A, the oil pool is schematically shown by hatching. The upper part of the discharge port 5 is a portion where the discharge side end faces of the female rotor 1 and the male rotor 2 communicate with the discharge port 5 and then communicate with the compression operation chamber until just before the discharge is completed (pocket portion 12 and axial projection). Overlapping parts).

ここで、吐出完了状態となった次の瞬間には、ポケット部１２が雌ロータ１の端面に覆われるため密閉状態となり、ポケット部１２に滞留した油が詰まる傾向にあり、その後も解消されにくくなる。油の詰まりにより、圧縮空気が吐出される作動空間に連通する吐出ポート５の面積が小さくなるため、圧力損失の原因となる。また、ポケット部１２に滞留した油は、その後吐出流路６に流出し、吐出流路６において作動流体に対して撹拌作用を招き、これも吐出圧損失の原因となる。 Here, at the next moment when the discharge is completed, the pocket portion 12 is covered with the end face of the female rotor 1 and thus becomes a sealed state, and the oil staying in the pocket portion 12 tends to be clogged, and it is difficult to eliminate the problem thereafter. Become. Due to the clogging of the oil, the area of the discharge port 5 communicating with the working space where the compressed air is discharged becomes small, which causes a pressure loss. Further, the oil staying in the pocket portion 12 then flows out to the discharge flow path 6 and causes a stirring action on the working fluid in the discharge flow path 6, which also causes a discharge pressure loss.

このような吐出ポート５の開口具合と、油の詰まりについて図３を用いて説明する。図３（ａ）～（ｃ）は、両ロータ１及び２の回転に伴う吐出ポート５の開口遷移を模式的に示す図である。 The degree of opening of the discharge port 5 and the clogging of oil will be described with reference to FIG. 3 (a) to 3 (c) are diagrams schematically showing the opening transition of the discharge port 5 due to the rotation of both rotors 1 and 2.

図３（ａ）は、吐出中の吐出ポート５の開口の様を示し、図３（ｂ）は、吐出完了直前の吐出ポート５の開口の様を示し、図３（ｃ）は吐出完了直後の吐出ポート５の様を示す。 FIG. 3A shows the opening of the discharge port 5 during discharge, FIG. 3B shows the opening of the discharge port 5 immediately before the completion of discharge, and FIG. 3C shows the opening of the discharge port 5 immediately after the completion of discharge. The discharge port 5 of the above is shown.

まず、図３（ａ）において、吐出中は吐出ポート５に対する開口面積９（黒塗部分）が比較的大である。この時は、より比重の低い圧縮空気が吐き出される割合が油よりも大である。
次いで、図３（ｂ）において、吐出完了直前では、吐出ポート５の開口面関は符号１１で示すような狭小な面積となる。この時は、より比重が高い油が吐き出される割合が大となる。 First, in FIG. 3A, the opening area 9 (black-painted portion) with respect to the discharge port 5 is relatively large during discharge. At this time, the rate at which compressed air having a lower specific density is discharged is larger than that of oil.
Next, in FIG. 3B, immediately before the completion of ejection, the opening surface of the ejection port 5 has a narrow area as indicated by reference numeral 11. At this time, the rate at which oil having a higher specific density is discharged becomes large.

そして、図３（ｃ）において、吐出完了直後では、雌ロータ１寄りの吐出ポート５上部が雌ロータ１のローブ端面に完全に覆われる。このとき当該吐出ポート５上部の軸方向吐出側にあるポケット部１２には油が滞留し且つこれを解消するための吐出力が略無い状態となる。 Then, in FIG. 3C, immediately after the discharge is completed, the upper portion of the discharge port 5 near the female rotor 1 is completely covered with the lobe end face of the female rotor 1. At this time, oil stays in the pocket portion 12 on the axial discharge side of the upper part of the discharge port 5, and there is almost no discharge force for eliminating the oil.

このように滞留した油が、圧力損失の原因となったり又ポケット部１２からしばらくして流出した油が吐出ポート５の先の吐出流路６で作動流体へ撹拌作用を招き損失の原因となったりする。 The oil that has accumulated in this way causes a pressure loss, and the oil that has flowed out from the pocket portion 12 after a while causes a stirring action on the working fluid in the discharge flow path 6 at the end of the discharge port 5 and causes a loss. Or something.

そこで、本実施例の雌ロータ１は、その吐出側端面の一部に、軸方向に所定の深さを持つ凹部１４を備える構成を有する点を特徴の１つとする。図２（ｂ）に、雌ロータ１の吐出し側端面を示す。凹部１４は、吐出完了直後即ち雌ロータ１の吐出側端面が吐出ポート５を通過した後もポケット部１２と連通し且つ吸気側作動室１９とは連通しない形状を有する。本実施例において、凹部１４は、雌ロータ１４のローブ付け根付近に位置し、回転方向に対しては反回転方向にのみ開口を有する溝形状を有する。 Therefore, one of the features of the female rotor 1 of the present embodiment is that the female rotor 1 of the present embodiment has a configuration in which a recess 14 having a predetermined depth in the axial direction is provided in a part of the discharge side end surface thereof. FIG. 2B shows the discharge side end surface of the female rotor 1. The recess 14 has a shape that communicates with the pocket portion 12 and does not communicate with the intake side operating chamber 19 immediately after the discharge is completed, that is, even after the discharge side end surface of the female rotor 1 passes through the discharge port 5. In this embodiment, the recess 14 is located near the lobe base of the female rotor 14 and has a groove shape having an opening only in the counter-rotation direction with respect to the rotation direction.

図２（ａ）に示すように、凹部１４は吐出ポート５と雌ロータ１の吐出側端面の間に空間１４を形成する。これにより、圧縮空気がポケット部１２に滞留する油を押し出す方向への流れ２１が生成される。 As shown in FIG. 2A, the recess 14 forms a space 14 between the discharge port 5 and the discharge side end face of the female rotor 1. This creates a flow 21 in which the compressed air pushes out the oil staying in the pocket portion 12.

比較例として、雌ロータ１に凹部１４を備えない場合について述べる。
図４に、凹部１４を備えない雌ロータ１の吐出側及び吐出流路６周辺の縦断面拡大図を示す。凹部１４を備えない場合、吐出完了直後に吐出ポート５の上部が雌ロータ１のローブ端面によって覆われるため（図３（ｃ）参照）、軸方向や吐出流路６に向かう流れ２０が支配的となり、ポケット部１２に滞留する油を押し出す方向への流れは略発生しない。よって、ポケット部１２に滞留する油が圧力損失や撹拌ロスを招来する。 As a comparative example, a case where the female rotor 1 is not provided with the recess 14 will be described.
FIG. 4 shows an enlarged vertical cross-sectional view of the discharge side of the female rotor 1 having no recess 14 and the periphery of the discharge flow path 6. When the recess 14 is not provided, the upper part of the discharge port 5 is covered with the lobe end surface of the female rotor 1 immediately after the discharge is completed (see FIG. 3C), so that the flow 20 in the axial direction or toward the discharge flow path 6 is dominant. Therefore, a flow in the direction of pushing out the oil staying in the pocket portion 12 does not occur substantially. Therefore, the oil staying in the pocket portion 12 causes pressure loss and stirring loss.

このように、本実施例では雌ロータ１に凹部１４を適用することでポケット部１２に詰まった油が圧縮空気により掻き出されることにより油の詰まりが軽減され、圧縮空気が吐き出される作動空間容積と吐出ポート５が連通する面積が縮小せず、圧力損失の軽減や吐出流路６での撹拌作用を軽減することができる。 As described above, in this embodiment, by applying the concave portion 14 to the female rotor 1, the oil clogged in the pocket portion 12 is scraped out by the compressed air, so that the clogged oil is reduced and the compressed air is discharged. The area in which the discharge port 5 communicates with the discharge port 5 is not reduced, and the pressure loss can be reduced and the stirring action in the discharge flow path 6 can be reduced.

本発明を適用した実施例２について説明する。なお、実施例１と同一要素については同一符号を使用し、詳細な説明を省略する場合がある。 Example 2 to which the present invention is applied will be described. The same reference numerals may be used for the same elements as in the first embodiment, and detailed description may be omitted.

実施例２は、雌スクリュー１の吐出側端部に備える凹部５０の形状が実施例１の凹部１４と異なる。実施例２の凹部５０は、ロータ軸方向の深さが、雌ロータ１の回転方向に向かって小さくなる（回転方向とは逆に向かって大きくなる）形状を有することを特徴の１つとする。 In the second embodiment, the shape of the recess 50 provided at the discharge side end of the female screw 1 is different from that of the recess 14 of the first embodiment. One of the features of the recess 50 of the second embodiment is that the depth in the rotor axial direction becomes smaller in the rotation direction of the female rotor 1 (increases in the direction opposite to the rotation direction).

実施例２の凹部５０によれば、圧縮空気が油の詰まり部分１２に滞留する油を押し出す方向への流れ２１とその流れの軸方向成分２２が作り出す角度が、実施例１と比較してより鋭角になることにより、油の詰まり部分１２へ流入する圧縮流体の流れのロータ軸方向成分２２が大きくなるため、より円滑に吐出し流路方向へ油を掻き出すことを可能とし、油詰まり時間を短縮することができ、実施例１と比較して圧力損失の低減効果が見込める。 According to the recess 50 of the second embodiment, the angle created by the flow 21 in the direction in which the compressed air pushes out the oil staying in the clogged portion 12 of the oil and the axial component 22 of the flow is higher than that of the first embodiment. By making the angle sharp, the rotor axial component 22 of the flow of the compressed fluid flowing into the oil clogged portion 12 becomes large, so that the oil can be discharged more smoothly and the oil can be scraped out in the flow path direction, and the oil clogging time can be reduced. It can be shortened, and the effect of reducing the pressure loss can be expected as compared with the first embodiment.

以上、本発明を実施するための形態について説明したが、本発明は上記種々の構成に限定されるものではなく、その趣旨を逸脱しない範囲で種々の変更が可能である。
例えば、上記例では、凹部１４や５０が雌ロータ１のローブの数と同数（６つ）備える構成としたが、少なくとも１つの凹部１４・５０を備えることでも一定の上記効果を得ることができる。また、複数の場合も１ローブ飛びで凹部１４・５０を備える構成などとしてもよい。 Although the embodiment for carrying out the present invention has been described above, the present invention is not limited to the above-mentioned various configurations, and various modifications can be made without departing from the spirit of the present invention.
For example, in the above example, the number of recesses 14 and 50 is the same as the number of lobes (six) of the female rotor 1, but a certain effect can be obtained by providing at least one recess 14 and 50. .. Further, in the case of a plurality of cases, the recesses 14 and 50 may be provided by skipping one lobe.

また、上記例では雄雌ロータが一つずつのツインスクリューを適用して説明したが、３以上のスクリューロータからなるマルチスクリューに適用することも可能である。 Further, in the above example, the male and female rotors are described by applying one twin screw, but it is also possible to apply the twin screws to a multi-screw composed of three or more screw rotors.

また、上記例では、油を作動室に供給する給油式の圧縮機本体を適用して説明したが、水等他の液体を供給する構成であってもよい。同様に、圧縮気体は空気に限定するものではなく、他の気体であってもよい。 Further, in the above example, although the refueling type compressor main body that supplies oil to the working chamber has been described, the configuration may be such that other liquids such as water are supplied. Similarly, the compressed gas is not limited to air, but may be another gas.

１…雌ロータ、２…雄ロータ、３…円筒空間、４…作動空間、５…吐出ポート、６…吐出流路、７…ケーシング、７ａ…ケーシング本体、７ｂ…吐出ケーシング、８…軸受室、９…吸込流路、１０…給油孔、１１…吐出完了直前の吐出ポートの開口、１２…ポケット部、１４…凹部、１９…吐出圧力以下の圧力にある作動空間、２０・２１…吐出方向の流れ、２２…ロータ軸方向成分 1 ... Female rotor, 2 ... Male rotor, 3 ... Cylindrical space, 4 ... Operating space, 5 ... Discharge port, 6 ... Discharge flow path, 7 ... Casing, 7a ... Casing body, 7b ... Discharge casing, 8 ... Bearing chamber, 9 ... Suction flow path, 10 ... Refueling hole, 11 ... Discharge port opening just before discharge completion, 12 ... Pocket, 14 ... Recess, 19 ... Working space at pressure below discharge pressure, 20.21 ... Discharge direction Flow, 22 ... Rotor axial component

Claims (7)

ローブを有し少なくとも１つずつの雄スクリューロータ及び雌スクリューロータと、前記雄スクリューロータ及び前記雌スクリューロータを格納して圧縮作動空間及び吸込作動空間を構成するケーシングとを備え、圧縮作動空間に供給された液体と吸込み気体を圧縮し、前記雄スクリューロータ及び前記雌スクリューロータの吐出側端面に対向する吐出ポートから圧縮混合気体を吐き出すスクリュー圧縮機本体であって、
前記雌スクリューロータが、
軸方向に深さを有する凹部を前記吐出側端面に備え、
前記凹部は、
前記雌スクリューロータが吐出完了直後の位置のときに、前記雌スクリューロータの軸方向に対しては前記吐出ポートに連通すると共に、前記雌スクリューロータの周方向に対しては前記雌スクリューロータの回転方向の吸込作動空間には連通せずに反回転方向の圧縮作動空間にのみ連通するものであるスクリュー圧縮機本体。 It is provided with at least one male screw rotor and female screw rotor having a lobe, and a casing for accommodating the male screw rotor and the female screw rotor to form a compression operation space and a suction operation space , and compressing. A screw compressor main body that compresses the liquid and suction gas supplied to the working space and discharges the compressed mixed gas from the discharge port facing the discharge side end faces of the male screw rotor and the female screw rotor .
The female screw rotor
The discharge side end face is provided with a recess having a depth in the axial direction.
The recess is
When the female screw rotor is in the position immediately after the completion of discharge, the female screw rotor communicates with the discharge port in the axial direction of the female screw rotor, and the female screw rotor communicates with the circumferential direction of the female screw rotor. The screw compressor body that does not communicate with the suction operating space in the rotational direction, but communicates only with the compression operating space in the anti-rotation direction. 請求項１に記載のスクリュー圧縮機本体であって、
前記凹部の軸方向深さが、同一深さであるスクリュー圧縮機本体。 The screw compressor main body according to claim 1.
A screw compressor body having the same depth in the axial direction of the recess. 請求項１に記載のスクリュー圧縮機本体であって、
前記凹部の軸方向深さが、前記雌スクリューロータの反回転方向に向かって深くなるものであるスクリュー圧縮機本体。 The screw compressor main body according to claim 1.
A screw compressor main body in which the axial depth of the recess becomes deeper in the counter-rotation direction of the female screw rotor . 請求項１～３のいずれか一項に記載のスクリュー圧縮機本体であって、
前記吐出ポートに連通し、前記圧縮混合気体の吐出方向に延在する吐出流路を備え、
前記吐出流路が、
前記雄スクリューロータ及び前記雌スクリューロータの軸線から徐々に離間する方向に延在するものであり、
前記吐出ポートにおける前記雌スクリューロータ寄り且つ前記吸込作動空間寄りの部分から前記雌スクリューロータの軸方向に平行に延在するポケット部を有するものであるスクリュー圧縮機本体。 The screw compressor main body according to any one of claims 1 to 3.
A discharge flow path that communicates with the discharge port and extends in the discharge direction of the compressed mixed gas is provided.
The discharge flow path
It extends in a direction gradually separated from the axes of the male screw rotor and the female screw rotor .
A screw compressor main body having a pocket portion extending in parallel with the axial direction of the female screw rotor from a portion of the discharge port closer to the female screw rotor and closer to the suction operating space. 請求項１～４のいずれか一項に記載のスクリュー圧縮機本体であって、
前記凹部を、複数備えるものであるスクリュー圧縮機本体。 The screw compressor main body according to any one of claims 1 to 4.
A screw compressor main body having a plurality of the recesses. 請求項１～４のいずれか一項に記載のスクリュー圧縮機本体であって、
前記凹部の数が、前記雌スクリューロータの前記ローブの数と同数であるスクリュー圧縮機本体。 The screw compressor main body according to any one of claims 1 to 4 .
A screw compressor body in which the number of recesses is the same as the number of lobes of the female screw rotor. 請求項１～６のいずれか一項に記載のスクリュー圧縮機本体であって、
前記液体が油又は水のいずれかであり、
前記吸込み気体が空気であるスクリュー圧縮機本体。 The screw compressor main body according to any one of claims 1 to 6.
The liquid is either oil or water
The screw compressor body in which the suction gas is air.
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JP3081590B2 (en) 1998-10-23 2000-08-28 福蔵 佐藤 Floor cleaning method
JP2001519503A (en) 1997-10-08 2001-10-23 カーテー クリステン テクノロジー−エントヴィックラング ゲーエムベーハー Screw compressor

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US5002472A (en) 1987-01-06 1991-03-26 Societe Anonyme: Baudot-Hardoll S.A. Profiles of screw-type rotors for rotary machines conveying a gaseous fluid
WO1992009807A1 (en) 1990-11-30 1992-06-11 Kabushiki Kaisha Maekawa Seisakusho Fluid jetting type screw compressor
JP2001519503A (en) 1997-10-08 2001-10-23 カーテー クリステン テクノロジー−エントヴィックラング ゲーエムベーハー Screw compressor
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