JPS5937290A - Screw compressor - Google Patents
Screw compressorInfo
- Publication number
- JPS5937290A JPS5937290A JP14762182A JP14762182A JPS5937290A JP S5937290 A JPS5937290 A JP S5937290A JP 14762182 A JP14762182 A JP 14762182A JP 14762182 A JP14762182 A JP 14762182A JP S5937290 A JPS5937290 A JP S5937290A
- Authority
- JP
- Japan
- Prior art keywords
- rotors
- rotor
- teeth
- screw compressor
- gap
- 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.)
- Pending
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
- F04C18/082—Details specially related to intermeshing engagement type pumps
- F04C18/084—Toothed wheels
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】 本発明はスクリュー圧縮機の改良に関するものである。[Detailed description of the invention] The present invention relates to improvements in screw compressors.
従来の油冷式スクリュー圧縮機は第１図に示すように、
吸込ポート１３を備えるケーシング３内にねじ状のロー
プを有する互にかみ合う一対の雄ロータ１と雌ロータ２
を収納し、その両ロータ１゜２の転がシ軸受８により回
転自在に支持すよううに構成されている。前記ケーシン
グ３の吸込側に取付けられたカバー５を雄ロータ軸ＩＡ
が貫通する部分にはオイルシール７が設けられ、ケーシ
ング３の吐出側には吐出ケーシング４およびカバー８が
取付けられている。A conventional oil-cooled screw compressor, as shown in Figure 1,
A pair of intermeshed male and female rotors 1 and 2 having threaded ropes in a casing 3 with suction ports 13
The rotor 1.degree.2 is configured to be rotatably supported by a shaft bearing 8. The cover 5 attached to the suction side of the casing 3 is connected to the male rotor shaft IA.
An oil seal 7 is provided at the portion through which the oil seal 7 passes, and a discharge casing 4 and a cover 8 are attached to the discharge side of the casing 3.
上記ロータ１，２の軸直角断面のプロフィルは第２図に
示すとおりで、９．１０はそれぞれロータ１，２の理論
プロフィルを示す。通常、雄ロ−タ１の回転によシ雌ロ
ータ２は駆動され、そのロープ溝およびケーシング内壁
により形成される空間の容積はロータ１，２の回転に伴
って減少するから、吸入ポート１３よシ流入したガス（
空気）は圧縮されて吐出される。この場合、ロータはか
棒金時に前進面側（駆動面側）で互に接触して回転する
。The profiles of the rotors 1 and 2 in cross section perpendicular to their axes are as shown in FIG. 2, and 9.10 indicates the theoretical profiles of the rotors 1 and 2, respectively. Normally, the female rotor 2 is driven by the rotation of the male rotor 1, and the volume of the space formed by the rope groove and the inner wall of the casing decreases as the rotors 1 and 2 rotate. The inflowing gas (
air) is compressed and discharged. In this case, the rotors rotate while contacting each other on the advancing surface side (driving surface side) during rolling.
前記両ロータの加工が非常に高精度である場合、雄ロー
タの歯数をＺＭとすれば、ＺＭまたは。If both rotors are machined with very high precision, and the number of teeth on the male rotor is ZM, then ZM or.
Ｚｖ−ｔ のかみ合いにおいて、常時両ロータが接触し
ていることになる。ところが、実際には、両ロータが接
触してかみ合う歯数は１とＺＭとの間で変化していると
考えられ、このかみ歯数の変化がロータの回転中におけ
る振動の原因となる恐れがある。In Zv-t meshing, both rotors are in constant contact. However, in reality, the number of teeth that both rotors contact and mesh with is thought to vary between 1 and ZM, and this change in the number of teeth may cause vibrations during rotor rotation. be.
本発明は上記にかんがみロータの振動を減少して騒音の
低減をはかることを目的とするもので、両ロータ同志が
実際にかみ合って接触動力を伝達するローブ部の長さま
たは歯数を限定し、その他のローブ部または歯数では、
両ロータのプロフィル間にギャップを形成して両ロータ
同志が接触し５ないようにしたものである。In view of the above, the present invention aims to reduce the vibration of the rotor and reduce the noise.The present invention aims to reduce the vibration of the rotor and reduce the noise. , for other lobe sections or numbers of teeth,
A gap is formed between the profiles of both rotors to prevent them from coming into contact with each other.
以下本発明の実施例を図面について説明する。Embodiments of the present invention will be described below with reference to the drawings.
第３図において、１１．１２は互にかみ合う駆動側雄ロ
ータおよび被動側雌ロータで、この雄ロータ１１の外周
面にはら線状の凸歯１１Ａがｎ個（図では５個）、雌ロ
ータ１２の外周面にはら線状の門歯１２Ａが（ｎ＋１）
個（図では６個）それぞれ設けられている。また両ロー
タ１１，１２゛は長さＬのローブ部を有し、このローブ
部りのうち所定部分ｔでは、両ロータ１１，１２が第４
図の実線１３Ｂ、１４Ｂで示すようにかみ合って接触す
るが、その他のローブ部（Ｌ−１）では第４図の点線１
３Ａ、１４Ａで示すように両ロータ１１．１２の全歯の
ローブ部に逃げδが設けられている。その他の構成は第
１図に示す従来例と同一であるから図面および説明を省
略する。In FIG. 3, reference numerals 11 and 12 indicate a driving male rotor and a driven female rotor that mesh with each other, and the male rotor 11 has n (5 in the figure) spiral convex teeth 11A on its outer peripheral surface, and the female rotor 12 has a spiral incisor 12A on its outer peripheral surface (n+1).
(6 in the figure) are provided respectively. Further, both the rotors 11 and 12' have a lobe portion having a length L, and in a predetermined portion t of this lobe portion, both the rotors 11 and 12 have a fourth lobe portion.
They mesh and contact as shown by the solid lines 13B and 14B in the figure, but the other lobe parts (L-1) are shown by the dotted line 1 in Figure 4.
As shown at 3A and 14A, relief δ is provided in the lobe portions of all teeth of both rotors 11, 12. The rest of the configuration is the same as the conventional example shown in FIG. 1, so drawings and explanations will be omitted.
上記逃げδを設けることによシ、両ロータ１１゜１２の
ローブ部（Ｌ−１）間にはギャップが形成、されるが、
このギャップからの漏洩を最小限とす−ｚｌめ、逃げδ
は雄ロータ１１の外径の０．３％以下の値だけ小さいよ
うに設定されている。また第４図では逃げδを両ロータ
１１．１２の双方に設けたが、いずれの一方のロータの
みに設けても同様な効果をうろことができる。By providing the relief δ, a gap is formed between the lobe portions (L-1) of both rotors 11 and 12, but
To minimize the leakage from this gap, the escape δ
is set to be smaller than 0.3% of the outer diameter of the male rotor 11. Further, although the relief δ is provided on both rotors 11 and 12 in FIG. 4, the same effect can be achieved even if the relief δ is provided on only one of the rotors.
上述したように両ロータ１１，１２がそのロープ部全長
りのうちの所定の小部分ｔでかみ合って接触し、それ以
外の部分すなわちロープ部全長りの大部分（Ｌ−１）で
は、両ロータ１１，１２の双方またはいずれか一方に逃
げδを設け、両ロータ１１，１２がかみ台部分で接触し
ないように構成したので、ロータの回転伝達精度が同上
するため、ロータの振動は減少するから騒音の発生を低
減させることができる。As described above, both rotors 11 and 12 mesh and contact each other at a predetermined small portion t of the entire length of the rope, and in other portions, that is, the majority of the entire length of the rope (L-1), both rotors Since the relief δ is provided in both or one of the rotors 11 and 12 so that the two rotors 11 and 12 do not contact each other at the rotor table, the rotation transmission accuracy of the rotors is the same as above, and the vibration of the rotors is reduced. Noise generation can be reduced.
第５図および第６図に示す他の実施例は、雌ロータ１２
の全ローブ溝（門歯）１２Ａのうちの任意数（図では３
個）のロープ溝１２Ａｉ〜１２Ａ３に逃げδを設け、点
線１２Ｃで示すようなプロフィルに加工したものである
。この加工を同一ロープ溝１２Ａｔ〜１２Ａ３について
ローブ全長りにわたって施すことによシ、雌ロータ１２
の門歯１２Ｃが雄ロータ１１の凸歯１１Ａとかみ合い接
触する際に、内ロータ１１，１２間にギャップが形成さ
れる。Another embodiment shown in FIGS. 5 and 6 is that the female rotor 12
Any number of the total lobe grooves (incisors) 12A (3 in the figure)
Relief δ is provided in the rope grooves 12Ai to 12A3 of the rope grooves 12Ai to 12A3, and the profile is processed as shown by the dotted line 12C. By applying this processing to the same rope grooves 12At to 12A3 over the entire length of the lobe, the female rotor 12
A gap is formed between the inner rotors 11 and 12 when the incisors 12C of the inner rotors 12C mesh with and contact the convex teeth 11A of the male rotor 11.
このように構成すれば、雄ロータ１１と雌ロータ１２の
一組の歯同志が−かみ台ごとに吸込側端面で接触してか
み合い、この接触かみ合いが連続して吐出側端面へ移動
して行く。したがって、本実癩例によれば、正規のプロ
フィルのロータ同志のかみ合い歯数の半分でロータ同志
の接触すなわち５駆動を行うことができる利点がある。With this configuration, a set of teeth of the male rotor 11 and the female rotor 12 come into contact with each other on the suction side end face for each toothing table, and this contact meshing continuously moves to the discharge side end face. . Therefore, according to this example, there is an advantage that the rotors can contact each other with half the number of meshing teeth of the rotors of the regular profile, that is, five drives can be performed.
第６図に示す実施例では、雌ロータ１２の門歯１２Ａに
逃げδを設けたが、これに代シ雄ロータ１１の凸歯１１
Ａの任意数（図では４個）に逃げδを設けても同様な効
果をうることかできる。In the embodiment shown in FIG. 6, the relief δ is provided in the incisor teeth 12A of the female rotor 12, but the relief δ is provided in the incisor teeth 12A of the female rotor 12.
A similar effect can be obtained by providing an arbitrary number (four in the figure) of relief δ in A.
以７上説明したように本発明によれば、両ロータのかみ
合い接触するローブ長さまたは歯数を限定することによ
シ、ロータの回転伝達精度を向上させるので、ロータの
振動を減少させて騒音の低減をはかることができる。As explained above, according to the present invention, the rotation transmission accuracy of the rotors is improved by limiting the length of the lobes or the number of teeth that engage and contact the two rotors, thereby reducing the vibrations of the rotors. Noise can be reduced.
第１図は従来の油冷式スクリュー圧縮機の断面図、第２
図は第１図のロータの断面図、第３図は本発明に係わる
スクリュー圧縮機のロータの一実施しリを示す平面図、
第４図は第３図のＡ−Ａ、Ｂ−Ｂ線における断面図、第
５図は本発明に係わるロータの他の実施例を示す平面図
、第６図は第５図のＣ−（Ｊ！における断面図、第７図
は本発明に係わるさらに他の実施例のロータ断面図であ
る。
１１・・・雄ロータ、１２・・・雌ロータ、１１Ａ・・
・凸歯、１２Ａ・・・臼歯、１３Ｂ、１４Ｂ・・・歯の
理論プロフィル、１３Ａ、１４Ａ・・・歯のプロフィル
、Ｌ・・・ロータのロープ部長さ、ｔ・・・ギャップを
設けないロープ部長さ、Ｌ−１・・・ギャップを設ける
ロープ部長さ、ａ・・・逃げ。
第 ２ 図Figure 1 is a cross-sectional view of a conventional oil-cooled screw compressor, Figure 2
The figure is a cross-sectional view of the rotor shown in FIG. 1, and FIG. 3 is a plan view showing one embodiment of the rotor of a screw compressor according to the present invention.
FIG. 4 is a cross-sectional view taken along lines A-A and B-B in FIG. 3, FIG. 5 is a plan view showing another embodiment of the rotor according to the present invention, and FIG. J!, and FIG. 7 is a sectional view of a rotor of still another embodiment according to the present invention. 11...Male rotor, 12...Female rotor, 11A...
・Convex tooth, 12A...molar tooth, 13B, 14B...theoretical tooth profile, 13A, 14A...tooth profile, L...rotor rope length, t...rope without gap Part length, L-1... Length of the rope part that provides the gap, a... Relief. Figure 2
Claims (1)
ージング内にかみ合い状態で収納してなるスクリュー圧
縮機において、前記両ロータ同志がかみ合い接触して動
力を伝達するロープ部の長さまたは歯数を限定し、その
他のロープ部長さまたは歯数では、両ロータのプロフィ
ル間にギャップを形成するようにしたことを特徴とする
スクリュー圧縮機。 ２ 前記ギャップを形成する部分は、少くとも一方のロ
ータの全歯のプロフィルを理論プロフィルよりも駆動側
ロータ外径の０．３％以下の値だけ小さくして両ロータ
を非接触で回転させることを特徴とする特許請求の範囲
第１項記載のスクリュー圧縮機。 ３、前記ギャップを形成する部分は、雄ロータまたは雌
ロータにおける一つの歯以上のロープについて、駆動側
ロータの歯のプロフィルをねじれに沿って全長にわたり
、理論プロフィルよυも駆動側ロータ外径の０．３％以
下の値だけ小さくせることを特徴とする特許請求の範囲
第１項記載のスクリュー圧縮機。[Scope of Claims] 1. A screw compressor in which a pair of female and male rotors each having an edge-shaped rope are housed in a casing in a meshing state, and the two rotors mesh with each other and come into contact with each other to transmit power. A screw compressor characterized in that the length or number of teeth of the rope section is limited, and a gap is formed between the profiles of both rotors for other rope section lengths or number of teeth. 2 The gap forming part is such that the profile of all teeth of at least one rotor is made smaller than the theoretical profile by a value of 0.3% or less of the outer diameter of the drive side rotor, and both rotors are rotated without contact. A screw compressor according to claim 1, characterized in that: 3. For ropes with one or more teeth in the male rotor or female rotor, the part forming the gap extends over the entire length of the tooth profile of the drive side rotor along the torsion, and the theoretical profile υ is also the outside diameter of the drive side rotor. The screw compressor according to claim 1, wherein the screw compressor is reduced by a value of 0.3% or less.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14762182A JPS5937290A (en) | 1982-08-27 | 1982-08-27 | Screw compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14762182A JPS5937290A (en) | 1982-08-27 | 1982-08-27 | Screw compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS5937290A true JPS5937290A (en) | 1984-02-29 |
Family
ID=15434460
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP14762182A Pending JPS5937290A (en) | 1982-08-27 | 1982-08-27 | Screw compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5937290A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4695233A (en) * | 1986-07-10 | 1987-09-22 | Kabushiki Kaisha Kobe Seiko Sho | Screw rotor mechanism |
| JPH02252991A (en) * | 1989-03-24 | 1990-10-11 | Kobe Steel Ltd | Screw rotor for screw type pump device |
| JPH0431686A (en) * | 1990-05-25 | 1992-02-03 | Ebara Corp | Screw rotor |
| WO1992009807A1 (en) * | 1990-11-30 | 1992-06-11 | Kabushiki Kaisha Maekawa Seisakusho | Fluid jetting type screw compressor |
-
1982
- 1982-08-27 JP JP14762182A patent/JPS5937290A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4695233A (en) * | 1986-07-10 | 1987-09-22 | Kabushiki Kaisha Kobe Seiko Sho | Screw rotor mechanism |
| JPH02252991A (en) * | 1989-03-24 | 1990-10-11 | Kobe Steel Ltd | Screw rotor for screw type pump device |
| JPH0431686A (en) * | 1990-05-25 | 1992-02-03 | Ebara Corp | Screw rotor |
| WO1992009807A1 (en) * | 1990-11-30 | 1992-06-11 | Kabushiki Kaisha Maekawa Seisakusho | Fluid jetting type screw compressor |
| US5350286A (en) * | 1990-11-30 | 1994-09-27 | Kabushiki Kaisha Naekawa Seisakusho | Liquid injection type screw compressor with lubricant relief chamber |
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