JPS61197788A - Unlubricated screw compressor - Google Patents
Unlubricated screw compressorInfo
- Publication number
- JPS61197788A JPS61197788A JP3848985A JP3848985A JPS61197788A JP S61197788 A JPS61197788 A JP S61197788A JP 3848985 A JP3848985 A JP 3848985A JP 3848985 A JP3848985 A JP 3848985A JP S61197788 A JPS61197788 A JP S61197788A
- Authority
- JP
- Japan
- Prior art keywords
- rotor
- tooth profile
- rotors
- teeth
- coating
- 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
-
- 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
- F04C2230/00—Manufacture
- F04C2230/60—Assembly methods
- F04C2230/602—Gap; Clearance
-
- 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
- F04C2230/00—Manufacture
- F04C2230/90—Improving properties of machine parts
- F04C2230/91—Coating
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Rotary-Type Compressors (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
この発明は、実働時の熱膨脹を考慮して最適な党−夕間
ギャップをもって噛合するようにした一対のロータを備
えた無給式スクリュー圧縮機に係秒、特に一対のロータ
の一方又は両方のロータ歯形の表面にコーティングを施
こした無給式スクリュー圧縮機に関する。[Detailed Description of the Invention] [Field of Industrial Application] The present invention provides a non-feeding screw compressor equipped with a pair of rotors that are meshed with each other with an optimal rotor gap in consideration of thermal expansion during actual operation. In particular, the present invention relates to a non-feed type screw compressor in which the surface of one or both rotor teeth of a pair of rotors is coated.
〔白ｉ、朗す
一般にスクリュー圧縮機などから吐出されるガス中に油
分の混在が望ましくない場合に用いられ無給油式スクリ
ュー圧縮機においては、一対のロータ間の回転伝達は、
各ロータの作動室外の軸部忙殺けられた同期歯車を介し
て行なわれ、このときロータ同志は互いに接触すること
なく、噛合して回転する。この種のスクリュー圧縮機は
、油をロータ同志が噛合する作動室内圧噴射し、ロータ
間の潤滑、冷却およびシールを施こす油冷式スクリュー
圧縮機に比較してロータの歯形部が高温になるため、常
一時とは歯形部の形状が大幅に変形する。このため実働
時に両ロータが接触するようになり、圧縮−の運転を続
けるのが危険になる。In an oil-free screw compressor, which is generally used when it is undesirable for oil to be mixed in the gas discharged from a screw compressor, rotation transmission between a pair of rotors is
This is done through synchronous gears arranged on the shafts of each rotor outside the working chamber, and at this time the rotors rotate in mesh with each other without contacting each other. In this type of screw compressor, oil is injected under pressure in the working chamber where the rotors mesh with each other, and the tooth profile of the rotor becomes hotter than in an oil-cooled screw compressor, which provides lubrication, cooling, and sealing between the rotors. Therefore, the shape of the tooth profile is significantly deformed compared to the normal state. As a result, both rotors come into contact during actual operation, making it dangerous to continue compression operation.
このふうな問題点を解決するために、予め熱膨脹を考慮
してロータ歯形やロータ切削用ホブを設計する手段が、
文献「日立評論、Ｖｏ１６５．Ａ５（１９８３−６）Ｊ
Ｋ提案されている。In order to solve these problems, there is a way to design the rotor tooth profile and rotor cutting hob by considering thermal expansion in advance.
Literature “Hitachi Review, Vo165.A5 (1983-6) J
K has been proposed.
第２図は、この日立評論に提案された設計手段の実施例
を示したものである。まず常温での雄ロータ、雌ロータ
のいずれか一方の歯形を基本歯形ムとし、このロータが
熱膨脹したときの歯形Ｂを求める。更に、歯形Ｂに対し
て圧縮機゛の信頼性を考慮シたロータ間ギャップをもっ
た歯形Ｃを求め、歯形ＣＫよ抄相手側の歯形りを創成□
する□。モしてホブは、歯形部と、歯形りを常温忙戻し
たときの歯形Ｅとを切削するように設計される。FIG. 2 shows an embodiment of the design means proposed in this Hitachi Review. First, the tooth profile of either the male rotor or the female rotor at room temperature is taken as the basic tooth profile B, and the tooth profile B when this rotor is thermally expanded is determined. Furthermore, a tooth profile C with a gap between the rotors considering the reliability of the compressor is determined for the tooth profile B, and a tooth profile for the other side is created from the tooth profile CK.
Do□. The hob is designed to cut the tooth profile and the tooth profile E when the tooth profile is returned to room temperature.
ところで、従来ロータにコーティングする場合には、第
２図に示すように、ロータ間に適当なギヤツブ番想定し
て決定された歯型ｄＫ、歯直角方向に略□均一な厚さで
コーティングが施こされている。By the way, when coating a rotor conventionally, as shown in Figure 2, the tooth profile dK is determined by assuming an appropriate gear number between the rotors, and the coating is applied with an approximately □ uniform thickness in the direction perpendicular to the teeth. It is strained.
しかし、上記従来のコーティングされたロータにおいて
、雄ロータと雌ロータの各ロータ歯形の頂部および底部
では、軸直角ギャップと歯直角ギャップとが等しくなる
ので、コーティング厚さを見込んで歯形Ｃを決定しても
よいが、歯形の中間部では、軸直角ギャップと歯直角ギ
ャップとは異なり゛、コーテング厚さが歯直角方向く均
一な厚さであると想定すると。However, in the above-mentioned conventional coated rotor, the axis normal gap and tooth normal gap are equal at the top and bottom of each rotor tooth profile of the male rotor and female rotor, so the tooth profile C is determined taking into account the coating thickness. However, in the middle part of the tooth profile, unlike the gap perpendicular to the axis and the gap perpendicular to the tooth, it is assumed that the coating thickness is uniform in the direction perpendicular to the tooth.
歯直角ギャップ〉軸直角ギャップ となる。Tooth normal gap>Axis normal gap becomes.
このような欠点のため、ロータ歯形の表面に、歯直角方
向に略均一なコーティングを施こし九ロータを運転した
場合、熱膨脹によってロータ歯形の頂部および底部では
接触しやすく、またロータ □歯形の中間部では
ギャップが多くなり、圧縮機の性能を低下させるという
問題があった。Because of these drawbacks, when a rotor is operated with a substantially uniform coating applied to the surface of the rotor tooth profile in the direction perpendicular to the teeth, the top and bottom of the rotor tooth profile are likely to come into contact due to thermal expansion, and the rotor □ midway between the tooth profile There was a problem that there were many gaps in the compressor section, which deteriorated the performance of the compressor.
本考案は、このような問題点を解決し、ロータ実働時に
おける歯直角ギャップを略均一にすることＫより、かり
にロータが互いに接触しても部分的でなく、ロータ歯形
の構成曲線が略均一に接触するようにした無給式スクリ
ュー圧縮機を提供することを目的とするものである。The present invention solves these problems by making the normal tooth gap approximately uniform when the rotors are in actual operation.In this way, even if the rotors touch each other, it is not partial, and the constitutive curve of the rotor tooth profile is approximately uniform. The object of the present invention is to provide a non-feed type screw compressor that is brought into contact with the compressor.
かかる目的達成のため、本発明に係る第１発明は、圧縮
空間を形成して互いに噛合するロータ歯形の表面にニー
ティングを施こしている一対の口 □−夕を備え
た無給油式スクリュー圧縮機において、前記一対のロー
タの一方又は両方のロータ歯形の表面に、歯直角方向に
略均一な厚さで施こすコーティングを想定して、そのコ
ーティング厚さを予め減じたロータ歯形が基本歯形とな
るようにした予約加工されたロータを備えたものである
。In order to achieve such an object, a first aspect of the present invention provides an oil-free screw compression system having a pair of openings in which the surfaces of rotor tooth profiles that form a compression space and mesh with each other are kneaded. In this machine, assuming that the surface of the rotor tooth profile of one or both of the pair of rotors is coated with a substantially uniform thickness in the direction perpendicular to the teeth, the rotor tooth profile with the coating thickness reduced in advance is the basic tooth profile. It is equipped with a pre-machined rotor.
また第２発明は、圧縮空間を形成して互いに噛合するロ
ータ歯形の表面にコーティングを施こしている一対のロ
ータを備えた無給油式スクリュー圧縮機において、前記
一対のロータの一方又は両方のロータ歯形の表面に、歯
直角方向に略均一な厚さでコーティングを施こしたロー
タが実働時における熱膨脹により変形したロータ歯形を
想定し、このロータ歯形が基本歯形となるように、コー
ティング前のロータ歯形が予め加工されたロータを備え
たものである。Further, a second invention provides an oil-free screw compressor comprising a pair of rotors that form a compression space and have coated surfaces of rotor teeth that mesh with each other, in which one or both rotors of the pair of rotors are coated. Assuming a rotor tooth profile whose surface is coated with a substantially uniform thickness in the direction perpendicular to the teeth, the rotor tooth profile is deformed due to thermal expansion during actual operation. It is equipped with a rotor with pre-processed tooth profiles.
さらに第３発明は、圧縮空間を形成して互いに噛合する
ロータ歯形の表面にコーティングを施こしている一対の
ロータを備えた無給油式スクリュー圧縮機において、前
記一対のロータの一方又は両方のロータ歯形の表面に、
歯直角方向に略均一な厚さでコーティングを施こしたロ
ータが実働時における熱膨脹により変形したロータ歯形
Ｋ、さらに圧縮機の信頼性を考慮して所定のロータ間ギ
ャップを加えたロータ歯形が、基本歯形となるように予
め加工されたロータを備えたものである。Furthermore, a third aspect of the present invention is an oil-free screw compressor equipped with a pair of rotors that form a compression space and are coated on the surfaces of rotor tooth profiles that mesh with each other. On the surface of the tooth shape,
The rotor tooth profile K is obtained by deforming the rotor coated with a substantially uniform thickness in the direction perpendicular to the teeth due to thermal expansion during actual operation, and the rotor tooth profile is obtained by adding a predetermined gap between the rotors in consideration of the reliability of the compressor. It is equipped with a rotor that has been pre-processed to have a basic tooth profile.
また第４発明は、圧縮空間を形成して互いに噛合するロ
ータ歯形の表面にコーティングを施こしている一対のロ
ータを備えた無給油式スクリュー圧縮機において、前記
一対のロータのうち一方のロータのコーティング前のロ
ータ歯形を基本歯形とし、この歯形の表面に歯直角方向
に略均一な厚さのコーティングを施こしたロータが実働
時における熱膨脹により変形したロータ歯形に。A fourth aspect of the present invention is an oil-free screw compressor equipped with a pair of rotors that form a compression space and have a coating applied to the surface of the rotor teeth that mesh with each other. The rotor tooth profile before coating is used as the basic tooth profile, and the rotor tooth profile is deformed due to thermal expansion during actual operation, with a coating of approximately uniform thickness applied to the surface of this tooth profile in the direction perpendicular to the teeth.
さらに圧縮機の信頼性を考慮して所定のロータ間ギャッ
プを加えたロータ歯形を想定し、このロータ歯形により
他方のロータ歯形を創成し、この他方のロータ歯形が常
温となって熱収縮したロータ歯形を想定し、さらにこの
ロータ歯形の表面に歯直角方向に略均一な厚さで施こす
コーティングを想定して、そのコーティング厚さを予め
減じたロータ歯形が他方のロータの基本歯形となるよう
に予め加工されたロータを備えたものである。Furthermore, considering the reliability of the compressor, a rotor tooth profile with a predetermined inter-rotor gap added is assumed, and this rotor tooth profile is used to create the other rotor tooth profile, and this other rotor tooth profile is heated to room temperature and heat-shrinked. Assuming a tooth profile, and assuming a coating to be applied to the surface of this rotor tooth profile with a substantially uniform thickness in the direction perpendicular to the teeth, the rotor tooth profile with the coating thickness reduced in advance becomes the basic tooth profile of the other rotor. It is equipped with a rotor that has been pre-processed.
上述の構成によれば、第１発明では、ロータ歯形の表面
に歯直角方向に略均一な厚さのコーティングを施こした
ロータ歯形が基本歯形となるように、コーティング前の
ロータが、コーティングの厚さだけ、ロータ歯形の歯直
角方向に均一に追い込み切削加工がなされる。According to the above structure, in the first invention, the rotor before coating is coated with the coating so that the rotor tooth profile in which the surface of the rotor tooth profile is coated with a substantially uniform thickness in the direction perpendicular to the teeth becomes the basic tooth profile. Cutting is performed uniformly in the direction perpendicular to the rotor tooth profile by the thickness.
また第２発明では、ロータ歯形の表面に歯直角方向に略
均一な厚さで施こされかつ実働時に熱膨脹によって変形
したロータ歯形が基本歯形となるように、コーティング
前のロータが、ロータ歯形の歯直角方向に均一な厚さで
施こされたコーティングの厚さと、常温に戻したときの
熱収縮量とを加えた量だけ追い込み切削加工がなされる
。また第３発明は、第２発明に加えて、コーティング前
のロータが、所定のロータ間ギャップだけ追い込み切削
加工がなされる。Further, in the second invention, the rotor before coating is coated with a substantially uniform thickness in the perpendicular direction to the surface of the rotor tooth profile and deformed by thermal expansion during actual operation, so that the rotor tooth profile becomes the basic tooth profile. The cutting process is performed by an amount equal to the sum of the thickness of the coating, which is uniformly applied in the direction perpendicular to the teeth, and the amount of heat shrinkage when returned to room temperature. Further, in a third invention, in addition to the second invention, the rotor before coating is cut by a predetermined inter-rotor gap.
また第４発明では、コーティング前のロータ歯形が一方
のロータの基本歯形となり、この基本歯形の表面に歯直
角方向に略均一な厚さで施こされたコーティング厚さと
、常勤時における熱膨脹量と、圧縮機の信頼性を考慮し
たロータ間ギャップとを加えたロータ歯形により他方の
ロータのロータ歯形が創成される。そして、この他方の
ロータが、常温に戻されたときの熱収縮量と、ロータ歯
形の歯直角方向に均一なコーティング厚さとを加えた量
だけ追い込み切削加工がなされ、これＫより他方のロー
タの常温時における基本歯形が得られる。Further, in the fourth invention, the rotor tooth profile before coating becomes the basic tooth profile of one rotor, and the coating thickness that is applied to the surface of this basic tooth profile with a substantially uniform thickness in the direction perpendicular to the tooth, and the amount of thermal expansion during full-time operation. , the rotor tooth profile of the other rotor is created by adding the rotor tooth profile with the inter-rotor gap in consideration of the reliability of the compressor. Then, this other rotor is cut by an amount equal to the amount of heat shrinkage when it is returned to room temperature and a uniform coating thickness in the normal direction of the rotor tooth profile, and from this K, the other rotor is The basic tooth profile at room temperature can be obtained.
以下、本発明を図面に示す実施例に基いて説明する。 Hereinafter, the present invention will be explained based on embodiments shown in the drawings.
第１図において、１は雌ロータ、２は雌ロータ１と互い
に噛み合う雄ロータで、これらの両ロータ１，２は、中
心点３，４を回転中心としてケーシング（図示せず）内
で矢印方向に回転することにより圧縮機の機能を満すよ
うになっており、雌ロータ１、雄ロータ２間の回転伝達
は５両ロータ１．２の作動室の外部に設けられた同期装
置、例えば同期歯車（図示せず）を介して行なわれる。In FIG. 1, 1 is a female rotor, 2 is a male rotor that meshes with the female rotor 1, and both rotors 1 and 2 rotate in the direction of the arrow within a casing (not shown) with center points 3 and 4 as rotation centers. The rotation transmission between the female rotor 1 and the male rotor 2 is performed by a synchronizer installed outside the working chamber of the five rotors 1 and 2, such as a synchronizer. This is done via gears (not shown).
またこの実施例においては雄ロータ２を基準として説明
する。なお、５，６は両ロータ１，２のピッチ円を示す
。Further, in this embodiment, the description will be made using the male rotor 2 as a reference. Note that 5 and 6 indicate pitch circles of both rotors 1 and 2.
まず第１発明および第２発明が適用される＠１実施例を
説明する。First, an example @1 to which the first invention and the second invention are applied will be described.
雄ロータ２の常温時におけるロータ歯形を基本歯形１２
とし、この基本歯形１２がロータ１，２の実働による熱
膨脹によって変形したロータ歯形１３を求める。この変
形したロータ歯形１３は予めロータ内部の温度を測定し
て得られた温度分布を基にして有限要素法などの手法に
より計算によって求める。さらに、ロータ歯形１３に対
して圧縮機の信頼性を考慮したロータ間ギャップ、例え
ば同期歯車のパララッシュ量を加えたロータ歯形１４を
求め・、このロータ歯形１４により相手側のロータ歯形
１５を創成する。モしてホブは、基本歯形１２の歯直角
方向にコーティングの厚さだけ略均一に追い込んだロー
タ歯形１１と、ロータ歯形を常温に戻したときのロータ
歯形１６を切削するように・設計される。The rotor tooth profile of the male rotor 2 at room temperature is the basic tooth profile 12.
Then, the rotor tooth profile 13 obtained by deforming this basic tooth profile 12 due to thermal expansion due to the actual operation of the rotors 1 and 2 is determined. This deformed rotor tooth profile 13 is calculated by a method such as the finite element method based on the temperature distribution obtained by measuring the temperature inside the rotor in advance. Furthermore, a rotor tooth profile 14 is determined by adding the inter-rotor gap, for example, the paralash amount of a synchronous gear, to the rotor tooth profile 13 in consideration of the reliability of the compressor, and the other rotor tooth profile 15 is created using this rotor tooth profile 14. do. Accordingly, the hob is designed to cut the rotor tooth profile 11 which is substantially uniformly driven in the direction perpendicular to the basic tooth profile 12 by the thickness of the coating, and the rotor tooth profile 16 when the rotor tooth profile is returned to room temperature. .
つぎに第３発明が適用される第２実施例を説明する。常
温での雄ロータ２の実働時のロータ歯形を基本歯形１４
とし、この基本歯形１４が常温となって熱収縮したロー
タ歯形１３を求め、さらに同期歯車のバックラッシュ量
を差し引いてロータ歯形１２とし、このロータ歯形１２
から歯直角方向にロータ内部に向ってコーティング厚さ
だけ略均一に減肉したロータ歯形１１を求める。Next, a second embodiment to which the third invention is applied will be described. The rotor tooth profile during actual operation of the male rotor 2 at room temperature is the basic tooth profile 14.
Then, calculate the rotor tooth profile 13 in which this basic tooth profile 14 heat-shrinks when the temperature reaches room temperature, and further subtract the amount of backlash of the synchronous gear to obtain the rotor tooth profile 12.
A rotor tooth profile 11 is obtained in which the thickness is reduced substantially uniformly by the coating thickness toward the inside of the rotor in the direction perpendicular to the teeth.
つぎにｔｓ４発明が適用される第３実施例を説明する。Next, a third embodiment to which the ts4 invention is applied will be described.
常温での雄ロータ２のロータ歯形を基本歯形１１とし、
この基本歯形１１の歯直角方向に略均一なコーティング
厚さを想定した歯形をロータ歯形１２とし、さらに′□
、このロータ歯形１２が熱膨脹したロータ歯形１３を求
め、このロータ歯形１３に対して、同期歯・車のバック
ラッシュ量を加えたロータ歯形１４を、□求め、このロ
ータ歯形１４により相手側のロータ歯形１５を創成する
。モしてホブは、基本歯形１１と、ロータ歯形１５を常
温に戻したときのロータ歯形１６を切削するよう・に設
計される。Let the rotor tooth profile of the male rotor 2 at room temperature be the basic tooth profile 11,
The rotor tooth profile 12 is a tooth profile that assumes a substantially uniform coating thickness in the direction perpendicular to the basic tooth profile 11, and further '□
, determine the rotor tooth profile 13 in which the rotor tooth profile 12 has thermally expanded, calculate the rotor tooth profile 14 by adding the amount of backlash of the synchronous tooth/wheel to this rotor tooth profile 13, and use this rotor tooth profile 14 to A tooth profile 15 is created. The hob is designed to cut the basic tooth profile 11 and the rotor tooth profile 16 when the rotor tooth profile 15 is returned to room temperature.
つぎに１本発明の実施例の作用を説明する。Next, the operation of one embodiment of the present invention will be explained.
コーティングの厚さだけロータ歯形゛の表面は、歯直角
方向に均一に追い込み切削加工が施こされており、−５
対のロータ間の歯直角方向のギャップが略均一になり、
またがりにロータ同志が干渉しても、コーティング層が
略均一に′摩耗するため、一対のロータ間の歯直角方向
のギャップが、ロータ゛歯形の全構成要素にわたって略
均一化され、圧縮機性能が向上する。The surface of the rotor tooth profile is cut uniformly in the perpendicular direction to the thickness of the coating, and -5
The gap between the pair of rotors in the perpendicular direction becomes almost uniform,
Even if the rotors interfere with each other, the coating layer wears out almost uniformly, so the gap in the normal direction between the pair of rotors becomes almost uniform across all components of the rotor tooth profile, improving compressor performance. do.
またロータ同志が干渉すると、コーティング層が略均一
に剥離し、ロータ地肌部分での干渉のポテンシャルが少
なくなる。Furthermore, when the rotors interfere with each other, the coating layer peels off almost uniformly, reducing the potential for interference at the rotor surface.
上述のとお秒、本発明によれば□、雌ロータと雄ロータ
の噛合する歯形全域にわたって最小のクリアラ゛ンスに
保持でき、しかも歯直角ギャップが均一な値となるので
、大幅な効率および信頼性の向上が得られる。As mentioned above, according to the present invention, the minimum clearance can be maintained over the entire meshing tooth profile of the female rotor and the male rotor, and the normal gap becomes a uniform value, resulting in significant efficiency and reliability. can be improved.
第１図は本発明に係るロータの基本歯形を説明するため
の■、第２図は従来例に係るロータの基本歯形を説明す
るた゛めの図である。
１１・・・基本歯形１２の歯直角方向□ロータ内側へコ
ーティングの厚さだけ略均一に減肉させたロータ歯形、
１２・・・基本歯形、１３・・・基本歯形１２が熱膨脹
したときのロータ歯形、１４・・・ロータ歯形１３に同
期歯車のバックラッシュ量などを付加したロータ歯形、
１５・・・ロータ歯形１４によって創 成されるロ
ータ歯形、１６・・・ロータ歯形１５を常温に戻したと
きのロータ歯形。FIG. 1 is a diagram for explaining the basic tooth profile of a rotor according to the present invention, and FIG. 2 is a diagram for explaining the basic tooth profile of a rotor according to a conventional example. 11... Basic tooth profile 12 in the tooth normal direction □ A rotor tooth profile in which the thickness of the coating is reduced almost uniformly to the inner side of the rotor,
12... Basic tooth profile, 13... Rotor tooth profile when the basic tooth profile 12 thermally expands, 14... Rotor tooth profile with backlash amount of synchronous gear added to rotor tooth profile 13, etc.
15... Rotor tooth profile created by the rotor tooth profile 14, 16... Rotor tooth profile when the rotor tooth profile 15 is returned to room temperature.
Claims (4)
表面にコーティングを施こしている一対のロータを備え
た無給油式スクリュー圧縮機において、前記一対のロー
タの一方又は両方のロータ歯形の表面に、歯直角方向に
略均一な厚さで施こすコーティングを想定して、そのコ
ーティング厚さを予め減じたロータ歯形が基本歯形とな
るようにした予め加工されたロータを備えたことを特徴
とする無給油式スクリュー圧縮機。(1) In an oil-free screw compressor equipped with a pair of rotors whose surfaces are coated with rotor teeth that mesh with each other while forming a compression space, the surface of one or both of the rotor teeth of the pair of rotors is coated. The present invention is characterized in that it is equipped with a pre-processed rotor whose basic tooth profile is a rotor tooth profile obtained by reducing the coating thickness in advance, assuming that the coating is applied with a substantially uniform thickness in the direction perpendicular to the teeth. Oil-free screw compressor.
表面にコーティングを施こしている一対のロータを備え
た無給油式スクリュー圧縮機において、前記一対のロー
タの一方又は両方のロータ歯形の表面に、歯直角方向に
略均一な厚さでコーティングを施こしたロータが実働時
における熱膨脹により変形したロータ歯形を想定し、こ
のロータ歯形が基本歯形となるように、コーティング前
のロータ歯形が予め加工されたロータを備えたことを特
徴とする無給油式スクリュー圧縮機。(2) In an oil-free screw compressor equipped with a pair of rotors in which a coating is applied to the surfaces of the rotor teeth that mesh with each other while forming a compression space, the surface of one or both of the rotor teeth of the pair of rotors is provided. Assuming a rotor tooth profile that is deformed due to thermal expansion during actual operation of a rotor coated with a substantially uniform thickness in the direction perpendicular to the teeth, the rotor tooth profile before coating is pre-coated so that this rotor tooth profile becomes the basic tooth profile. An oil-free screw compressor featuring a machined rotor.
表面にコーティングを施こしている一対のロータを備え
た無給油式スクリュー圧縮機において、前記一対のロー
タの一方又は両方のロータ歯形の表面に、歯直角方向に
略均一な厚さでコーティングを施こしたロータが実働時
における熱膨脹により変形したロータ歯形に、さらに圧
縮機の信頼性を考慮して所定のロータ間ギャップを加え
たロータ歯形が、基本歯形となるように予め加工された
ロータを備えたことを特徴とする無給式スクリュー圧縮
機。(3) In an oil-free screw compressor equipped with a pair of rotors in which a coating is applied to the surfaces of the rotor teeth that mesh with each other while forming a compression space, the surface of the rotor teeth of one or both of the pair of rotors is provided. In addition to the rotor tooth profile deformed by thermal expansion during actual operation, the rotor is coated with a substantially uniform thickness in the direction perpendicular to the teeth, and a predetermined gap between the rotors is added in consideration of the reliability of the compressor. A non-feeding screw compressor is characterized in that it is equipped with a rotor that is pre-processed to have a basic tooth profile.
表面にコーティングを施こしている一対のロータを備え
た無給油式スクリュー圧縮機において、前記一対のロー
タのうち一方のロータのコーティング前のロータ歯形を
基本歯形とし、この歯形の表面に歯直角方向に略均一な
厚さのコーティングを施こしたロータが実働時における
熱膨脹により変形したロータ歯形に、さらに圧縮機の信
頼性を考慮して所定のロータ間ギャップを加えたロータ
歯形を想定し、このロータ歯形により他方のロータ歯形
を創成し、この他方のロータ歯形が常温となつて熱収縮
したロータ歯形を想定し、さらにこのロータ歯形の表面
に歯直角方向に略均一な厚さで施こすコーティングを想
定して、そのコーティング厚さを予め減じたロータ歯形
が他方のロータの基本歯形となるように予め加工された
ロータを備えたことを特徴とする無給式スクリュー圧縮
機。(4) In an oil-free screw compressor equipped with a pair of rotors whose surfaces are coated with rotor tooth profiles that form a compression space and mesh with each other, one of the pair of rotors before being coated. The rotor tooth profile is the basic tooth profile, and the rotor tooth profile is deformed due to thermal expansion during actual operation, and the rotor tooth profile is coated with a substantially uniform thickness in the perpendicular direction to the tooth profile. Assume a rotor tooth profile with a predetermined inter-rotor gap, create the other rotor tooth profile using this rotor tooth profile, assume a rotor tooth profile that is heat-shrinked when the other rotor tooth profile reaches room temperature, and then create the rotor tooth profile of this rotor tooth profile. Assuming that the coating is applied to the surface with a substantially uniform thickness in the direction perpendicular to the teeth, the rotor is machined in advance so that the rotor tooth profile with the coating thickness reduced in advance becomes the basic tooth profile of the other rotor. A non-feeding screw compressor featuring:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3848985A JPS61197788A (en) | 1985-02-27 | 1985-02-27 | Unlubricated screw compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3848985A JPS61197788A (en) | 1985-02-27 | 1985-02-27 | Unlubricated screw compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS61197788A true JPS61197788A (en) | 1986-09-02 |
Family
ID=12526671
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3848985A Pending JPS61197788A (en) | 1985-02-27 | 1985-02-27 | Unlubricated screw compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS61197788A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4974318A (en) * | 1987-03-11 | 1990-12-04 | Leybold Aktiengesellschaft | Method of making a dual-shaft machine |
| US5060531A (en) * | 1989-01-10 | 1991-10-29 | Ishikawajima-Harima Jukogyo Kabushiki Kaisha | Screw rotor |
| US6769890B2 (en) * | 1999-06-23 | 2004-08-03 | Samputensili S.P.A. | Gas rotary screw compressor |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5146418A (en) * | 1974-10-18 | 1976-04-20 | Hitachi Ltd | SUKURYUUAT SUSHUKUKI |
| JPS5150005A (en) * | 1974-10-28 | 1976-05-01 | Inoue Japax Res | SUKURYUHONPUYOROOTANO SEIZOHOHO |
| JPS57159989A (en) * | 1981-03-27 | 1982-10-02 | Hitachi Ltd | Tooth form of screw rotor |
| JPS5937291A (en) * | 1982-08-27 | 1984-02-29 | Hitachi Ltd | Screw rotor |
-
1985
- 1985-02-27 JP JP3848985A patent/JPS61197788A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5146418A (en) * | 1974-10-18 | 1976-04-20 | Hitachi Ltd | SUKURYUUAT SUSHUKUKI |
| JPS5150005A (en) * | 1974-10-28 | 1976-05-01 | Inoue Japax Res | SUKURYUHONPUYOROOTANO SEIZOHOHO |
| JPS57159989A (en) * | 1981-03-27 | 1982-10-02 | Hitachi Ltd | Tooth form of screw rotor |
| JPS5937291A (en) * | 1982-08-27 | 1984-02-29 | Hitachi Ltd | Screw rotor |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4974318A (en) * | 1987-03-11 | 1990-12-04 | Leybold Aktiengesellschaft | Method of making a dual-shaft machine |
| US5060531A (en) * | 1989-01-10 | 1991-10-29 | Ishikawajima-Harima Jukogyo Kabushiki Kaisha | Screw rotor |
| US6769890B2 (en) * | 1999-06-23 | 2004-08-03 | Samputensili S.P.A. | Gas rotary screw compressor |
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