JP2018003720A - Compressor - Google Patents

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JP2018003720A
JP2018003720A JP2016132594A JP2016132594A JP2018003720A JP 2018003720 A JP2018003720 A JP 2018003720A JP 2016132594 A JP2016132594 A JP 2016132594A JP 2016132594 A JP2016132594 A JP 2016132594A JP 2018003720 A JP2018003720 A JP 2018003720A
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compressor
oil
lubricating oil
path
lubricating
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利明 矢部
Toshiaki Yabe
利明 矢部
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Hitachi Industrial Equipment Systems Co Ltd
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Hitachi Industrial Equipment Systems Co Ltd
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Abstract

PROBLEM TO BE SOLVED: To provide a compressor which can improve reliability by supplying lubricating oil to a bearing of a compressor body in a short time after starting a compressor.SOLUTION: A compressor includes: a compressor body 1 having a bearing for supporting a rotation portion; lubrication routes 28, 29, 30, 31, 32A, 32B, and 33 for supplying lubricating oil to bearings 11A, 11B, 12A, and 12B of the compressor body; and an oil cooler 25 connected with the lubrication route so that the lubricating oil flows therein and the cooled lubricating oil is output therefrom. An opening and closing device 39 for preventing the lubricating oil from flowing back to the oil cooler in starting of the compressor body is provided in an outlet of the oil cooler.SELECTED DRAWING: Figure 1

Description

本発明は、圧縮機に係り、特に潤滑油の供給に関する。   The present invention relates to a compressor, and more particularly to supply of lubricating oil.

一般的な圧縮機の圧縮機本体は回転部を支持する軸受を有しており、その軸受に潤滑油を供給することで円滑な動作を行っている。一方、圧縮作動室に油や水といった液体を供給せずに圧縮空気を生成する無給油式圧縮機が知られている。無給油式圧縮機の圧縮機本体は高速回転駆動であるため、起動後短時間で圧縮ロータを支持する軸受や種々のギヤ装置に潤滑油を循環させることが重要である。   A compressor main body of a general compressor has a bearing that supports a rotating portion, and performs smooth operation by supplying lubricating oil to the bearing. On the other hand, an oil-free compressor that generates compressed air without supplying a liquid such as oil or water to the compression working chamber is known. Since the compressor main body of the oil-free compressor is driven at a high speed, it is important to circulate the lubricating oil to the bearings and various gear devices that support the compression rotor in a short time after startup.

本技術分野における背景技術として、特開昭６１−６５０８８号公報（特許文献１）がある。特許文献１には、圧縮機の無負荷時に、大気に放出する圧縮空気の一部を軸封装置に供給して軸封圧力を調整することで、圧縮室に潤滑油が流入することを防止する構成が開示されている。   As background art in this technical field, there is JP-A-61-65088 (Patent Document 1). In Patent Document 1, when a compressor is not loaded, a part of the compressed air released to the atmosphere is supplied to the shaft seal device to adjust the shaft seal pressure, thereby preventing the lubricating oil from flowing into the compression chamber. The structure to perform is disclosed.

また、特開平１０−９１７６号公報（特許文献２）には、圧縮機本体の軸受等に潤滑油を供給するための給油配管経路の一部を圧縮機本体の上流側で分岐し、一方の分岐経路を油溜まりが設けられたギヤケーシングに接続してバイパス経路とし、このバイパス経路の途中に排油電磁弁を設ける構成が開示されている。このような構成において、特許文献２では、圧縮機の停止時に排油電磁弁を開とすることで給油配管経路内の潤滑油を圧縮機本体に供給することなく直接ギヤケーシング内に回収し、圧縮機本体内部に潤滑油が流入することを抑制することが開示されている。   Japanese Patent Laid-Open No. 10-9176 (Patent Document 2) branches a part of an oil supply piping path for supplying lubricating oil to a bearing or the like of a compressor body on the upstream side of the compressor body, A configuration is disclosed in which a branch path is connected to a gear casing provided with an oil reservoir to serve as a bypass path, and a drain oil solenoid valve is provided in the middle of the bypass path. In such a configuration, Patent Document 2 collects the lubricating oil in the oil supply piping path directly in the gear casing without opening the oil discharge solenoid valve when the compressor is stopped, It is disclosed that lubricating oil is prevented from flowing into the compressor body.

特開昭６１−６５０８８号公報JP-A-61-65088 特開平１０−９１７６号公報Japanese Patent Laid-Open No. 10-9176

特許文献１及び特許文献２は、何れも、圧縮機起動時の短時間での圧縮機本体の軸受部等に潤滑油を供給することについて考慮されていない。   Neither Patent Document 1 nor Patent Document 2 considers supplying lubricating oil to a bearing portion or the like of the compressor body in a short time when the compressor is started.

本発明は、圧縮機起動後、短時間で圧縮機本体の軸受部等に潤滑油を供給することができる圧縮機を提供することを目的とする。   An object of this invention is to provide the compressor which can supply lubricating oil to the bearing part etc. of a compressor main body in a short time after a compressor starting.

本発明は、上記の課題を達成するために、その一例を挙げるならば、回転部を支持する軸受を有する圧縮機本体と、圧縮機本体の軸受に潤滑油を供給する潤滑経路と、潤滑経路に接続され潤滑油を流入し冷却した潤滑油を出力するオイルクーラとを備える圧縮機であって、オイルクーラの出口部に圧縮機本体の起動時にオイルクーラに潤滑油が逆流するのを防止する開閉装置を備えた構成とする。   In order to achieve the above-described object, the present invention is, for example, a compressor body having a bearing that supports a rotating part, a lubrication path for supplying lubricating oil to the bearing of the compressor body, and a lubrication path. The compressor includes an oil cooler that is connected to the oil cooler and outputs the cooled lubricating oil, and prevents the lubricating oil from flowing back to the oil cooler when the compressor body is started at the outlet of the oil cooler. It is set as the structure provided with the switchgear.

本発明によれば、圧縮機の起動時に短時間で圧縮機本体内の軸受等に潤滑油を供給する圧縮機を提供することができる。   ADVANTAGE OF THE INVENTION According to this invention, the compressor which supplies lubricating oil to the bearing etc. in a compressor main body in a short time at the time of starting of a compressor can be provided.

実施例１における無給油式スクリュー圧縮機の構造と潤滑油の経路及びその流れを示す模式図である。It is a schematic diagram which shows the structure of the oil-free screw compressor in Example 1, the path | route of lubricating oil, and its flow. 実施例２における無給油式スクリュー圧縮機の構造と潤滑油の経路及びその流れを示す模式図である。It is a schematic diagram which shows the structure of the oil-free screw compressor in Example 2, the path | route of lubricating oil, and its flow. 実施例２における温調弁の詳細構成を示す断面図とその低温時の動作を示す図である。It is sectional drawing which shows the detailed structure of the temperature control valve in Example 2, and the figure which shows the operation | movement at the time of the low temperature. 実施例２における温調弁の詳細構成を示す断面図とその高温時の動作を示す図である。It is sectional drawing which shows the detailed structure of the temperature control valve in Example 2, and the figure which shows the operation | movement at the time of the high temperature. 実施例２における他の構成の温調弁の詳細構成を示す断面図とその低温時の動作を示す図である。It is sectional drawing which shows the detailed structure of the temperature control valve of the other structure in Example 2, and the figure which shows the operation | movement at the time of the low temperature. 実施例２における他の構成の温調弁の詳細構成を示す断面図とその高温時の動作を示す図である。It is sectional drawing which shows the detailed structure of the temperature control valve of the other structure in Example 2, and the figure which shows the operation | movement at the time of high temperature. 従来技術による無給油式スクリュー圧縮機の構造と潤滑油の経路及びその流れを示す模式図である。It is a schematic diagram which shows the structure of the oil-free screw compressor by a prior art, the path | route of lubricating oil, and its flow. 従来技術による無給油式スクリュー圧縮機本体の縦断面図である。It is a longitudinal cross-sectional view of the oilless type screw compressor main body by a prior art.

以下、図面を用いて本発明の実施例について説明する。   Embodiments of the present invention will be described below with reference to the drawings.

まず、圧縮機のうちの無給油式スクリュー圧縮機を例にとり、本実施例の前提構造と具体的な問題点について説明する。   First, an oil-free screw compressor of the compressor is taken as an example, and the premise structure and specific problems of this embodiment will be described.

図５は、従来技術による無給油式スクリュー圧縮機（以下、単に「圧縮機１００」という。）の構造と潤滑油の経路及びその流れを示す模式図である。図５において、圧縮機１００は、圧縮機本体１、ギヤケーシング２、駆動源としてのモータ３及びオイルクーラ２５を備える。圧縮機本体１は、ギヤケーシング２の側面上方付近にフランジ取合いで取り付けられ、圧縮機本体１の上方の面と、ギヤケーシング２の上方の面は、概略水平となる。ギヤケーシング２の側面下方に配置されたモータ３の駆動力は、出力軸に取り付けられた駆動プーリ４Ａと、ギヤケーシング２を貫通したギヤシャフト８の端部に配置された従動プーリ４Ｂとに懸架されたベルト６を介して伝達される。   FIG. 5 is a schematic diagram showing the structure of an oil-free screw compressor (hereinafter simply referred to as “compressor 100”), the route of lubricating oil, and the flow thereof according to the prior art. In FIG. 5, the compressor 100 includes a compressor body 1, a gear casing 2, a motor 3 as a drive source, and an oil cooler 25. The compressor body 1 is attached by flange engagement near the upper side of the side surface of the gear casing 2, and the upper surface of the compressor body 1 and the upper surface of the gear casing 2 are substantially horizontal. The driving force of the motor 3 arranged below the side surface of the gear casing 2 is suspended between a driving pulley 4A attached to the output shaft and a driven pulley 4B arranged at the end of the gear shaft 8 penetrating the gear casing 2. Is transmitted via the belt 6.

ギヤケーシング２は、種々の伝達ギヤを収容する。具体的には、ギヤシャフト８を中心に従動プーリ４Ｂ側から、ギヤシャフト軸受１５、増速駆動ギヤ５Ａ，ギヤシャフト軸受１６及びオイルポンプ駆動ギヤ７Ａが配置される。増速駆動ギヤ５Ａは、所定のギヤ比に設定された増速従動ギヤ５Ｂと歯合し、増速従動ギヤ５Ｂに接続されたロータシャフト４８Ａを介して圧縮機本体１の雄ロータ５０Ａに駆動力を伝達するようになっている。   The gear casing 2 accommodates various transmission gears. Specifically, a gear shaft bearing 15, a speed increasing drive gear 5A, a gear shaft bearing 16, and an oil pump drive gear 7A are arranged from the driven pulley 4B side around the gear shaft 8. The speed increasing drive gear 5A meshes with the speed increasing driven gear 5B set to a predetermined gear ratio, and is driven to the male rotor 50A of the compressor body 1 via the rotor shaft 48A connected to the speed increasing driven gear 5B. It is designed to transmit power.

また、オイルポンプ駆動ギヤ７Ａは、所定のギヤ比に設定されたオイルポンプ従動ギヤ７Ｂと歯合する。オイルポンプ従動ギヤ７Ｂは、ギヤケーシング２の外部に貫通するオイルポンプシャフト２２と接続され、オイルポンプ２４に駆動力を伝達する様になっている。
オイルポンプ２４は、圧縮機１００の各種駆動部に潤滑オイルを循環させるポンプであり、オイルポンプシャフト２２を介して伝達された駆動力により、圧縮機１００に配置された種々の潤滑油の経路に潤滑油を圧送する。なお、本実施形態では自励ポンプを適用するが、圧縮機本体１の動作に応じて駆動が制御される電動の他励ポンプであってもよい。 The oil pump drive gear 7A meshes with the oil pump driven gear 7B set to a predetermined gear ratio. The oil pump driven gear 7 </ b> B is connected to an oil pump shaft 22 that penetrates to the outside of the gear casing 2, and transmits a driving force to the oil pump 24.
The oil pump 24 is a pump that circulates lubricating oil to various driving units of the compressor 100, and is driven to various lubricating oil paths disposed in the compressor 100 by the driving force transmitted through the oil pump shaft 22. Pump the lubricant. In addition, although a self-excited pump is applied in this embodiment, an electrically driven externally-excited pump whose drive is controlled according to the operation of the compressor body 1 may be used.

オイルポンプ２４は、ギヤケーシング２の下部に設けられたオイル溜り４７から、ストレーナ４０を介して潤滑油を吸い込み、潤滑経路２９を介して、オイルクーラ２５に圧送するようになっている。オイルクーラ２５は、ファン（不図示）による空冷又は水冷式の熱交換器であり、所定の温度以下となるように潤滑油を冷却する。   The oil pump 24 sucks lubricating oil from an oil reservoir 47 provided at the lower portion of the gear casing 2 through a strainer 40 and pumps the lubricating oil to the oil cooler 25 through a lubricating path 29. The oil cooler 25 is an air-cooled or water-cooled heat exchanger using a fan (not shown), and cools the lubricating oil so as to be a predetermined temperature or lower.

温調弁２３は、潤滑油の温度が低い場合には潤滑経路３１の流量比を高くし、潤滑油の温度が高い場合には潤滑経路３０の流量比を多くすることで、オイルクーラ２５に流れる潤滑油量を調整し、潤滑油の油温を所定の温度範囲に維持する。   The temperature control valve 23 increases the flow rate ratio of the lubrication path 31 when the temperature of the lubricating oil is low, and increases the flow rate ratio of the lubrication path 30 when the temperature of the lubricating oil is high. The amount of flowing lubricating oil is adjusted, and the temperature of the lubricating oil is maintained within a predetermined temperature range.

オイルクーラ２５で冷却された潤滑油は、潤滑経路３２を通り、潤滑経路３１を流れる潤滑油と合流し、オイルフィルタ２６に圧送される。オイルフィルタ２６を通過した潤滑油は、ギヤケーシング２及び圧縮機本体１の各種ギヤや回転部を支持する軸受に供給される。   The lubricating oil cooled by the oil cooler 25 passes through the lubricating path 32, merges with the lubricating oil flowing through the lubricating path 31, and is pumped to the oil filter 26. The lubricating oil that has passed through the oil filter 26 is supplied to bearings that support the gear casing 2 and the various gears and the rotating portion of the compressor body 1.

また、潤滑油の循環油量は、潤滑経路３３に設けた圧力センサ（図示せず）により判定する。潤滑経路３３を通過する潤滑油量が多ければ圧力センサ部の圧力は高くなり、少なければ圧力センサ部の圧力は低下する。圧縮機起動時は、圧力センサ部の圧力が一定時間（例えば、２０秒）以内に基準圧力（例えば、０．１４ＭＰａ）より高くなっていなければ循環油量が少ないと判断し、焦げ付き防止のために圧縮機を停止する制御となっている。   The circulating oil amount of the lubricating oil is determined by a pressure sensor (not shown) provided in the lubricating path 33. If the amount of lubricating oil passing through the lubrication path 33 is large, the pressure of the pressure sensor unit is high, and if it is small, the pressure of the pressure sensor unit is low. When starting the compressor, if the pressure in the pressure sensor is not higher than the reference pressure (for example, 0.14 MPa) within a certain time (for example, 20 seconds), it is determined that the amount of circulating oil is small to prevent burning. It is the control that stops the compressor.

次いで、圧縮機本体１の構成及び各種潤滑経路について説明する。図６に、圧縮機本体１の側断面図を示す。圧縮機本体１は、雄ロータ５０Ａ及び雌ロータ５０Ｂからなる一対のスクリューロータ５０の歯が、所定のギヤップを保った状態で噛み合い、高速回転することで、圧縮空気を生成する容量制御型の空気圧縮機である。   Next, the configuration of the compressor body 1 and various lubrication paths will be described. In FIG. 6, the sectional side view of the compressor main body 1 is shown. The compressor main body 1 is a capacity-controlled air that generates compressed air when the teeth of a pair of screw rotors 50 including a male rotor 50A and a female rotor 50B mesh with each other while maintaining a predetermined gap and rotate at high speed. It is a compressor.

雄ロータ５０Ａは、ロータシャフト４８Ａと、雌ロータ５０Ｂはロータシャフト４０Ｂと一体又は直結構成される。   The male rotor 50A is integrally or directly connected to the rotor shaft 48A and the female rotor 50B is connected to the rotor shaft 40B.

雄ロータ５０Ａ及び雌ロータ５０Ｂの夫々のロータシャフトには、空気の吸込み側端部方向に夫々軸受１１Ａ、１１Ｂ、吐出し側端部方向に軸受１２Ａ、１２Ｂが夫々配置され、これらに回転可能に支持される。また、ロータシャフト４８Ａ、４８Ｂの夫々には、軸受１２Ａ及び１２Ｂよりも更に外端部に、タイミングギヤ９及び１０が配置され、ロータシャフト４８Ａに接続された雄ロータ５０Ａの回転に伴い、タイミングギヤ９と１０の噛み合いによって雌雄ロータが互いに回転するようになっている。雌雄ロータの回転に伴い、吸込経路４１から吸い込まれた空気が圧縮室６０で圧縮され、やがて吐出経路４２から所定の圧縮空気経路を経て、ユーザ側へと供給されるようになっている。   The rotor shafts of the male rotor 50A and the female rotor 50B are respectively provided with bearings 11A and 11B in the direction of the air suction side end, and bearings 12A and 12B in the direction of the discharge side end, respectively, so that they can rotate. Supported. In addition, timing gears 9 and 10 are arranged at outer end portions of the rotor shafts 48A and 48B at the outer ends of the bearings 12A and 12B, respectively, and the timing gears are rotated along with the rotation of the male rotor 50A connected to the rotor shaft 48A. The male and female rotors rotate with each other by meshing 9 and 10. With the rotation of the male and female rotors, the air sucked from the suction passage 41 is compressed in the compression chamber 60, and is eventually supplied from the discharge passage 42 to the user side through a predetermined compressed air passage.

ロータシャフト４８Ａ、４８Ｂの吸込み側において、雌雄のロータ５０Ａ、５０Ｂと、軸受１１Ａ、１１Ｂとの間には、軸封部１７（１７Ａ、１７Ｂ）と、軸封部１８（１８Ａ、１８Ｂ）とが配設される。軸封部１７は、エアシールであり、圧縮室６０で圧縮された空気が、軸受１１Ａ等の側に漏れ出すのを低減するための環状の部材である。軸封部１７は、ロータシャフト４８Ａ等と非接触であり、その隙間は数十μｍ程度の微小なものである。雌雄ロータ５０Ａ、５０Ｂ夫々のロータシャフト４８に、エアシール１７Ａ（雄側）、１７Ｂ（雌側）が配置される。   On the suction side of the rotor shafts 48A and 48B, between the male and female rotors 50A and 50B and the bearings 11A and 11B, there are shaft sealing portions 17 (17A and 17B) and shaft sealing portions 18 (18A and 18B). Arranged. The shaft seal portion 17 is an air seal, and is an annular member for reducing the air compressed in the compression chamber 60 from leaking out to the bearing 11A or the like side. The shaft seal portion 17 is not in contact with the rotor shaft 48A and the like, and the gap is as small as about several tens of μm. Air seals 17A (male side) and 17B (female side) are disposed on the rotor shafts 48 of the male and female rotors 50A and 50B, respectively.

軸封部１８は、ネジシールであり、経路３４を介して軸受１１Ａ、１１Ｂに供給された潤滑油が圧縮室６０に侵入するのを防止するためのものである。ネジシール１８Ａ、１８Ｂの内面には角溝が螺旋状に施され、ロータシャフト４８Ａ等と非接触で、微小な隙間を保つように組付けられる。ネジシール１８Ａ、１８Ｂは、ロータシャフト４８Ａ等の回転により、内径部の溝部にシール圧を発生させることで、潤滑油を軸受１１Ａ、１１Ｂ側に押し戻すように作用する。   The shaft seal portion 18 is a screw seal and is for preventing the lubricating oil supplied to the bearings 11 </ b> A and 11 </ b> B through the path 34 from entering the compression chamber 60. Square grooves are spirally formed on the inner surfaces of the screw seals 18A and 18B, and are assembled so as to keep a minute gap without contacting the rotor shaft 48A or the like. The screw seals 18A and 18B act to push the lubricating oil back to the bearings 11A and 11B by generating a seal pressure in the groove portion of the inner diameter portion by the rotation of the rotor shaft 48A and the like.

また、ロータシャフト４８Ａ等は、軸封部１７と１８の間において、周方向に溝が形成されており、この溝と周方向で対向する位置に、圧縮機本体ケーシングから外気に連通する穴部４３が形成される。穴部４３は、圧縮室６０からの漏れ空気を圧縮機本体１の外部に逃がすためのガス抜き穴等として機能する。   Further, the rotor shaft 48A or the like has a groove formed in the circumferential direction between the shaft seal portions 17 and 18, and a hole portion communicating with the outside air from the compressor body casing at a position facing the groove in the circumferential direction. 43 is formed. The hole 43 functions as a vent hole for letting the air leaking from the compression chamber 60 to the outside of the compressor body 1.

また、ネジシール１８Ａ、１８Ｂと、軸受１１Ａ、１１Ｂとの間に、軸受１１Ａ、１１Ｂを潤滑した潤滑油を回収し、ギヤケーシング２のオイル溜り４７に還流させるための排油口４５が形成される。   Further, between the screw seals 18A and 18B and the bearings 11A and 11B, an oil discharge port 45 for collecting the lubricating oil that has lubricated the bearings 11A and 11B and returning it to the oil reservoir 47 of the gear casing 2 is formed. .

このようなロータシャフト４８Ａ、４８Ｂの吸込み側の構成と同様に、ロータシャフト４８Ａ、４８Ｂの吐出側も軸封部１９（エアシール）や軸封部２０（ネジシール）が配置される。雌雄ロータ５０Ａ、５０Ｂと、軸受１２Ａ、１２Ｂとの間には、軸封部１９と軸封部２０が配置される。また、圧縮機本体ケーシングの軸封部１９と２０の間には、外気と連通し、圧縮室６０から漏れ出る圧縮空気のガス抜きとして機能する穴部４４が形成される。   Similar to the configuration on the suction side of the rotor shafts 48A and 48B, the shaft sealing portion 19 (air seal) and the shaft sealing portion 20 (screw seal) are also arranged on the discharge side of the rotor shafts 48A and 48B. A shaft seal portion 19 and a shaft seal portion 20 are disposed between the male and female rotors 50A and 50B and the bearings 12A and 12B. Further, a hole 44 is formed between the shaft seal portions 19 and 20 of the compressor main body casing so as to communicate with outside air and function as a vent for compressed air leaking from the compression chamber 60.

軸受１２Ａ、１２Ｂは、雌雄ロータシャフトの夫々に３つずつ配置される。そして、圧縮機本体ケーシングには、これら３つの軸受１２の間の何れかの位置に、上方から潤滑油を供給するための経路３５が形成される。また、圧縮機本体ケーシングには、軸受１２Ａ、１２Ｂと、ネジシール２０Ａ、２０Ｂとの間の位置から潤滑油を回収する排油口４６が形成される。経路３５から供給された潤滑油は、軸受１２Ａ、１２Ｂを潤滑した後、排油口４６から回収されるようになっている。   Three bearings 12A and 12B are arranged on each of the male and female rotor shafts. A passage 35 for supplying lubricating oil from above is formed in any position between the three bearings 12 in the compressor body casing. The compressor body casing is formed with an oil discharge port 46 for collecting the lubricating oil from a position between the bearings 12A and 12B and the screw seals 20A and 20B. The lubricating oil supplied from the passage 35 is collected from the oil discharge port 46 after lubricating the bearings 12A and 12B.

圧縮機本体ケーシングには、タイミングギヤ９、１０の上方に潤滑油を供給するための経路３４が形成され、潤滑油は、タイミングギヤ９、１０を潤滑後に、下方に形成された排油口４５からオイル溜り４７に回収されるようになっている。なお、経路３４は、圧縮機ケーシング上で経路３５から途中分岐するように形成され、排油口４６は途中から排油口４５と合流するように形成されている。   A passage 34 for supplying lubricating oil to the upper part of the timing gears 9 and 10 is formed in the compressor main body casing, and the lubricating oil lubricates the timing gears 9 and 10 and then the oil discharge port 45 formed below. To the oil sump 47. The path 34 is formed so as to branch from the path 35 halfway on the compressor casing, and the oil discharge port 46 is formed so as to merge with the oil discharge port 45 from the middle.

以上の例において、圧縮機起動時の潤滑油の温度が０℃付近の場合（低温起動）とそれ以上の場合(常温起動)における潤滑油の流れについて説明する。   In the above example, the flow of the lubricating oil when the temperature of the lubricating oil at the time of starting the compressor is around 0 ° C. (low temperature starting) and when the temperature is higher than that (normal temperature starting) will be described.

すなわち、低温起動時は、運転開始直後は潤滑油の温度が０℃付近であるため、温調弁２３により、潤滑油のほぼ全量が潤滑経路３１に流れる。潤滑経路３１はオイルクーラ２５の出口の潤滑経路３２と合流しているため、潤滑経路３１を流れる潤滑油の全量が潤滑経路３３に流れず、潤滑油の一部がオールクーラ２５に流入する。そのため、潤滑経路３３を流れる潤滑油量が一時的に減少し、ギヤケーシング２及び圧縮機本体１の各種ギヤや軸受への潤滑油の供給が遅れるという問題があった。また、低温時には潤滑油の粘度が高いため、潤滑油が循環しにくくなっている。そのため、潤滑油の供給遅れが更に助長される。これにより、圧縮機が起動できない場合もあるという問題があった。また、常温起動時には、潤滑油の一部が温調弁２３から潤滑経路３０を経由してオイルクーラ２５に流入するため、ギヤケーシング２及び圧縮機本体１の各種ギヤや軸受への潤滑油の供給が遅れるという問題があった。   That is, at the time of low temperature start-up, since the temperature of the lubricating oil is around 0 ° C. immediately after the start of operation, almost all of the lubricating oil flows through the lubricating path 31 by the temperature control valve 23. Since the lubrication path 31 merges with the lubrication path 32 at the outlet of the oil cooler 25, the entire amount of the lubricating oil flowing through the lubrication path 31 does not flow into the lubrication path 33, and a part of the lubricating oil flows into the all cooler 25. Therefore, there is a problem that the amount of lubricating oil flowing through the lubricating path 33 is temporarily reduced, and the supply of lubricating oil to the gear casing 2 and the various gears and bearings of the compressor body 1 is delayed. Also, since the viscosity of the lubricating oil is high at low temperatures, the lubricating oil is difficult to circulate. Therefore, the supply delay of the lubricating oil is further promoted. Thereby, there existed a problem that a compressor might not start. In addition, since a part of the lubricating oil flows into the oil cooler 25 from the temperature control valve 23 via the lubrication path 30 at the normal temperature start-up, the lubricating oil is applied to various gears and bearings of the gear casing 2 and the compressor body 1. There was a problem that supply was delayed.

そこで、これらの問題点を解決するための構成について、以下本実施例を説明する。具体的には、圧縮機起動直後において、ギヤケーシング２及び圧縮機本体１の各種ギヤや軸受への潤滑油の供給遅れを防止するものである。   Therefore, a configuration for solving these problems will be described below. Specifically, immediately after the compressor is started, a delay in supply of lubricating oil to the gear casing 2 and the various gears and bearings of the compressor body 1 is prevented.

図１は、本実施例における無給油式スクリュー圧縮機の構造と潤滑油の経路及びその流れを示す模式図である。図１に示すように、本実施例では、オイルクーラ２５の出口の潤滑経路３２Ａと３２Ｂとの間に逆止弁３７を配置した構成としている。これにより、低温起動時における潤滑経路３２Ｂからのオイルクーラ２５への潤滑油の流入を防止することができ、圧縮機本体１への潤滑油の供給遅れを防止することができる。また、逆止弁３７は電磁弁などの開閉装置３９に置き換えることもできる。逆止弁３７と置き換えた開閉装置３９は、起動時の一定時間（例えば、起動後５〜２０秒程度）のみ閉じ、それ以降は開くことで、逆止弁３７を設けた場合と同様の効果を得ることができる。   FIG. 1 is a schematic diagram showing the structure of an oil-free screw compressor in this embodiment, the route of lubricating oil, and the flow thereof. As shown in FIG. 1, in this embodiment, a check valve 37 is arranged between the lubrication paths 32A and 32B at the outlet of the oil cooler 25. Thereby, inflow of the lubricating oil to the oil cooler 25 from the lubricating path 32B at the time of low temperature starting can be prevented, and supply delay of the lubricating oil to the compressor main body 1 can be prevented. Further, the check valve 37 can be replaced with an opening / closing device 39 such as an electromagnetic valve. The opening / closing device 39 replaced with the check valve 37 is closed only for a certain period of time at the time of activation (for example, about 5 to 20 seconds after activation), and is opened thereafter, so that the same effect as the case where the check valve 37 is provided Can be obtained.

以上のように、本実施例は、回転部を支持する軸受を有する圧縮機本体と、圧縮機本体の軸受に潤滑油を供給する潤滑経路と、潤滑経路に接続され潤滑油を流入し冷却した潤滑油を出力するオイルクーラとを備える圧縮機であって、オイルクーラの出口部に圧縮機本体の起動時にオイルクーラに潤滑油が逆流するのを防止する開閉装置を備えた構成とする。   As described above, in this embodiment, the compressor body having the bearing that supports the rotating portion, the lubrication path that supplies the lubricant to the bearing of the compressor body, and the lubrication path that is connected to the lubrication path flows in and cools. The compressor includes an oil cooler that outputs lubricating oil, and includes an opening / closing device that prevents the lubricating oil from flowing back to the oil cooler when the compressor body is started at the outlet of the oil cooler.

これにより、本実施例によれば、圧縮機の起動時に短時間で圧縮機本体内のギヤや軸受等に潤滑油を供給することができる。   Thereby, according to the present Example, lubricating oil can be supplied to the gear, the bearing, etc. in a compressor main body in a short time at the time of starting of a compressor.

図２は、本実施例における無給油式スクリュー圧縮機の構造と潤滑油の経路及びその流れを示す模式図である。本実施例では、実施例１での逆止弁３７に加え、オイルクーラ２５の入口の潤滑経路３０Ａと３０Ｂの間に電磁弁などの開閉装置３８を配置した構成としている。開閉装置３８は、起動時の一定時間（例えば、起動後５〜２０秒程度）のみ閉じ、それ以降は開くように制御する。これにより、常温起動時におけるオールクーラ２５への潤滑油の流入を防止することができ、圧縮機本体１への潤滑油の供給遅れを防止することができる。   FIG. 2 is a schematic diagram showing the structure of the oil-free screw compressor in this embodiment, the route of the lubricating oil, and the flow thereof. In the present embodiment, in addition to the check valve 37 in the first embodiment, an opening / closing device 38 such as an electromagnetic valve is disposed between the lubrication paths 30A and 30B at the inlet of the oil cooler 25. The opening / closing device 38 is controlled to be closed only for a certain period of time at the time of activation (for example, about 5 to 20 seconds after activation) and to be opened thereafter. Thereby, inflow of the lubricating oil to the all cooler 25 at the time of normal temperature starting can be prevented, and supply delay of the lubricating oil to the compressor body 1 can be prevented.

なお、図２における、温調弁２３は、前述したように、潤滑油の温度が低い場合には潤滑経路３１の流量比を高くし、潤滑油の温度が高い場合には潤滑経路３０の流量比を多くすることで、オイルクーラ２５に流れる潤滑油量を調整し、潤滑油の油温を所定の温度範囲に維持するものであるが、その詳細について説明する。   2, the temperature control valve 23 increases the flow rate ratio of the lubrication path 31 when the temperature of the lubricating oil is low, and the flow rate of the lubrication path 30 when the temperature of the lubrication oil is high, as described above. By increasing the ratio, the amount of lubricating oil flowing through the oil cooler 25 is adjusted and the oil temperature of the lubricating oil is maintained within a predetermined temperature range. Details thereof will be described.

図３Ａ、図３Ｂは、温調弁２３の詳細構成を示す断面図であり、図３Ａが低温時、図３Ｂが高温時の状態を示している。低温時は、図３Ａに示すように、温調弁２３の弁部２３ａは、潤滑経路２９と潤滑経路３１とが連通する状態の位置となっており、潤滑経路２９からの潤滑油は、潤滑経路３１へ流入すると共に、潤滑経路３０を通りオイルクーラ２５にも流入する。潤滑経路２９からの潤滑油の温度の上昇と共に、弁部２３ａは図３Ａの位置から図３Ｂの位置に移動する。潤滑経路２９からの潤滑油の温度がある温度（例えば６５℃）まで上昇すると弁部２３ａは図３Ｂの位置に移動し、潤滑経路３１が弁２３ａにより遮断され、潤滑経路２９からの潤滑油の全量が潤滑経路３０を通り、オイルクーラ２５に流入する。従って、図３Ａ、図３Ｂの温調弁２３を圧縮機１００に適用した場合、低温時でも潤滑油がオイルクーラ２５に流入するので、オイルクーラ２５の入口の潤滑経路３０に開閉装置３８を設けることで、常温起動時の潤滑油の一部のオイルクーラ２５への流入を防止することができる。また、出口部に逆止弁３７又は電磁弁３９を設けることで圧縮機の起動時にオイルクーラ２５への油の流入を防止することができる。   3A and 3B are cross-sectional views showing a detailed configuration of the temperature control valve 23, in which FIG. 3A shows a state at a low temperature and FIG. 3B shows a state at a high temperature. At a low temperature, as shown in FIG. 3A, the valve portion 23a of the temperature control valve 23 is in a position where the lubrication path 29 and the lubrication path 31 communicate with each other, and the lubricating oil from the lubrication path 29 is lubricated. It flows into the path 31 and also flows into the oil cooler 25 through the lubrication path 30. As the temperature of the lubricating oil from the lubricating path 29 rises, the valve portion 23a moves from the position shown in FIG. 3A to the position shown in FIG. 3B. When the temperature of the lubricating oil from the lubricating path 29 rises to a certain temperature (for example, 65 ° C.), the valve portion 23a moves to the position of FIG. 3B, the lubricating path 31 is blocked by the valve 23a, and the lubricating oil from the lubricating path 29 The entire amount passes through the lubrication path 30 and flows into the oil cooler 25. Therefore, when the temperature control valve 23 of FIGS. 3A and 3B is applied to the compressor 100, since the lubricating oil flows into the oil cooler 25 even at a low temperature, an opening / closing device 38 is provided in the lubricating path 30 at the inlet of the oil cooler 25. In this way, it is possible to prevent a part of the lubricating oil from flowing into the oil cooler 25 when starting at room temperature. Further, by providing the check valve 37 or the electromagnetic valve 39 at the outlet, it is possible to prevent the oil from flowing into the oil cooler 25 when the compressor is started.

図４Ａ、図４Ｂは、他の構成の温調弁２３の詳細構成を示す断面図であり、同様に、図４Ａが低温時、図４Ｂが高温時の状態を示している。低温時は、図４Ａに示すように、温調弁２３の弁部２３ａは、潤滑経路２９とオイルクーラ２５への経路３０とが２３ｂ部と２３ｃ部で遮断される状態の位置にあり、潤滑経路２９からの潤滑油の全量がバイパス経路３１に流れ、オイルクーラ２５への経路３０には潤滑油が流れない。潤滑経路２９からの潤滑油の温度がある温度（例えば、５０℃）まで上昇すると弁部２３ａが移動を開始し、温度上昇と共に図４Ｂの位置に移動する。潤滑油の温度がある温度（例えば６５℃）まで上昇すると潤滑経路２９と潤滑経路３１が２３ｃ部と２３ｄ部で遮断され、潤滑経路２９からの潤滑油の全量が経路３０を通り、オイルクーラ２５に流入する。従って、図４Ａ、図４Ｂの温調弁２３を圧縮機１００に適用した場合、低温起動時は潤滑経路２９とオイルクーラ２５への潤滑経路３０は遮断されているため、オイルクーラ２５の入口の潤滑経路３０に開閉装置３８を設けても設けなくてもどちらでも構わない。出口部には逆止弁３７又は電磁弁３９を設けることで圧縮機の起動時にオイルクーラ２５への潤滑油の流入を防止することができる。   4A and 4B are cross-sectional views showing a detailed configuration of the temperature control valve 23 having another configuration. Similarly, FIG. 4A shows a state at a low temperature and FIG. 4B shows a state at a high temperature. When the temperature is low, as shown in FIG. 4A, the valve portion 23a of the temperature control valve 23 is in a position where the lubrication path 29 and the path 30 to the oil cooler 25 are blocked by the 23b section and the 23c section. The entire amount of lubricating oil from the path 29 flows to the bypass path 31, and no lubricating oil flows to the path 30 to the oil cooler 25. When the temperature of the lubricating oil from the lubricating path 29 rises to a certain temperature (for example, 50 ° C.), the valve portion 23a starts to move, and moves to the position of FIG. 4B as the temperature rises. When the temperature of the lubricating oil rises to a certain temperature (for example, 65 ° C.), the lubrication path 29 and the lubrication path 31 are cut off at the 23c portion and the 23d portion, and the entire amount of the lubricating oil from the lubrication path 29 passes through the path 30 and the oil cooler 25 Flow into. Therefore, when the temperature control valve 23 shown in FIGS. 4A and 4B is applied to the compressor 100, the lubrication path 29 and the lubrication path 30 to the oil cooler 25 are cut off at the time of low temperature start-up. It does not matter whether the lubrication path 30 is provided with the opening / closing device 38 or not. By providing the check valve 37 or the electromagnetic valve 39 at the outlet, it is possible to prevent the lubricating oil from flowing into the oil cooler 25 when the compressor is started.

以上のように、本実施例は、回転部を支持する軸受を有する圧縮機本体と、圧縮機本体の軸受に潤滑油を供給する潤滑経路と、潤滑経路に接続され潤滑油を流入し冷却した潤滑油を出力するオイルクーラとを備える圧縮機であって、オイルクーラの出口部に圧縮機本体の起動時にオイルクーラに潤滑油が逆流するのを防止する開閉装置を備え、さらに、潤滑経路から潤滑油の一部又は全量をオイルクーラの入口にバイパスさせ、オイルクーラに流入する潤滑油量を調整し、潤滑油を所定の温度に調節する機能を有する温調弁を備え、オイルクーラの入口部に圧縮機本体の起動時にオイルクーラに潤滑油が流入するのを防止する第２の開閉装置を備えた構成とする。   As described above, in this embodiment, the compressor body having the bearing that supports the rotating portion, the lubrication path that supplies the lubricant to the bearing of the compressor body, and the lubrication path that is connected to the lubrication path flows in and cools. A compressor having an oil cooler that outputs lubricating oil, and having an opening / closing device that prevents the lubricating oil from flowing back to the oil cooler at the outlet of the compressor body at the outlet of the oil cooler; A part of or the entire amount of the lubricating oil is bypassed to the inlet of the oil cooler, the amount of lubricating oil flowing into the oil cooler is adjusted, and a temperature control valve having a function of adjusting the lubricating oil to a predetermined temperature is provided. And a second opening / closing device for preventing the lubricating oil from flowing into the oil cooler when the compressor body is started.

これにより、本実施例によれば、圧縮機起動後、短時間でギヤケーシング及び圧縮機本体の各種ギヤや軸受への潤滑油を供給することができ、軸受やギヤの信頼性を向上することができる。   Thereby, according to the present embodiment, it is possible to supply lubricating oil to various gears and bearings of the gear casing and the compressor body in a short time after the compressor is started, and to improve the reliability of the bearings and gears. Can do.

以上、実施例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適宜変更や置換が可能であることは言うまでもない。例えば、本実施例では雌雄一対のスクリュー型圧縮機を例としたが、本発明はこれに限定するものではなく、シングル或いはトリプルロータ型のスクリュー圧縮機でもよいし、シングル又はダブルスクロール型でもよいし、レシプロ型でもよいし、多段圧縮機構成であってもよく、圧縮機本体に潤滑油供給による潤滑対象を含む圧縮機形式であればよい。また、ある実施例の構成の一部を他の実施例の構成に置き換えることが可能であり、また、ある実施例の構成に他の実施例の構成を加えることも可能である。また、各実施例の構成の一部について、他の構成の追加、削除、置換をすることが可能である。   Although the embodiments have been described above, the present invention is not limited to the various configurations described above, and it is needless to say that changes and substitutions can be made as appropriate without departing from the spirit of the present invention. For example, in this embodiment, a pair of male and female screw compressors is taken as an example, but the present invention is not limited to this, and a single or triple rotor type screw compressor may be used, or a single or double scroll type may be used. In addition, a reciprocating type or a multi-stage compressor configuration may be used as long as it is a compressor type that includes an object to be lubricated by supplying lubricating oil in the compressor body. Further, a part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment. Further, it is possible to add, delete, and replace other configurations for a part of the configuration of each embodiment.

１：圧縮機本体、２：ギヤケーシング、３：モータ、４Ａ：駆動プーリ、４Ｂ：従動プーリ、５Ａ：増速駆動ギヤ、５Ｂ：増速従動ギヤ、６：ベルト、７Ａ：オイルポンプ駆動ギヤ、７Ｂ：オイルポンプ従動ギヤ、８：ギヤシャフト、９、１０：タイミングギヤ、１１Ａ、１１Ｂ、１２Ａ、１２Ｂ：軸受、１５、１６：ギヤシャフト軸受、１７、１８、１９、２０：軸封部、２１：バイパス配管、２２：オイルポンプシャフト、２３：温調弁、２４：オイルポンプ、２５：オイルクーラ、２６：オイルフィルタ、２８、２９、３０、３１、３２、３３：潤滑経路、３７：逆止弁、３８、３９：開閉装置、４０：ストレーナ、４１：吸込経路、４２：吐出経路、４３、４４：穴部、４５、４６：排油口、４７：オイル溜り、４８Ａ、４８Ｂ：ロータシャフト、５１：吐出配管、６０：圧縮室、１００：圧縮機 1: compressor body, 2: gear casing, 3: motor, 4A: drive pulley, 4B: driven pulley, 5A: speed increasing drive gear, 5B: speed increasing driven gear, 6: belt, 7A: oil pump driving gear, 7B: Oil pump driven gear, 8: Gear shaft, 9, 10: Timing gear, 11A, 11B, 12A, 12B: Bearing, 15, 16: Gear shaft bearing, 17, 18, 19, 20: Shaft seal, 21 : Bypass piping, 22: Oil pump shaft, 23: Temperature control valve, 24: Oil pump, 25: Oil cooler, 26: Oil filter, 28, 29, 30, 31, 32, 33: Lubrication path, 37: Check Valves, 38, 39: Opening and closing device, 40: Strainer, 41: Suction path, 42: Discharge path, 43, 44: Hole, 45, 46: Oil outlet, 47: Oil reservoir, 48A, 48B: B Tashafuto, 51: discharge pipe, 60: compression chamber, 100: compressor

Claims (4)

回転部を支持する軸受を有する圧縮機本体と、前記圧縮機本体の軸受に潤滑油を供給する潤滑経路と、前記潤滑経路に接続され前記潤滑油を流入し冷却した潤滑油を出力するオイルクーラとを備える圧縮機であって、
前記オイルクーラの出口部に前記圧縮機本体の起動時に前記オイルクーラに前記潤滑油が逆流するのを防止する開閉装置を備えたことを特徴とする圧縮機。 A compressor body having a bearing for supporting the rotating portion; a lubrication path for supplying lubricant to the bearing of the compressor body; and an oil cooler connected to the lubrication path for outputting the cooled and lubricated oil A compressor comprising:
A compressor characterized in that an opening / closing device is provided at an outlet of the oil cooler to prevent the lubricating oil from flowing back to the oil cooler when the compressor body is started. 請求項１に記載の圧縮機であって、
前記開閉装置は逆止弁であることを特徴とする圧縮機。 The compressor according to claim 1,
The compressor characterized in that the opening / closing device is a check valve. 請求項１に記載の圧縮機であって、
前記潤滑経路から前記潤滑油の一部又は全量を前記オイルクーラの入口にバイパスさせ、前記オイルクーラに流入する潤滑油量を調整し、前記潤滑油を所定の温度に調節する機能を有する温調弁を備え、
前記オイルクーラの入口部に前記圧縮機本体の起動時に前記オイルクーラに前記潤滑油が流入するのを防止する第２の開閉装置を備えたことを特徴とする圧縮機。 The compressor according to claim 1,
Temperature control having a function of bypassing part or all of the lubricating oil from the lubricating path to the inlet of the oil cooler, adjusting the amount of lubricating oil flowing into the oil cooler, and adjusting the lubricating oil to a predetermined temperature With a valve,
A compressor comprising a second opening / closing device for preventing the lubricating oil from flowing into the oil cooler when the compressor main body is started up at an inlet of the oil cooler. 請求項１から３の何れか1項に記載の圧縮機であって、
前記圧縮機本体は、気体を圧縮するロータ、ロータシャフト及びロータシャフトを回転可能に支持する軸受を有する無給油式圧縮機本体であり、
前記圧縮機本体を駆動するための駆動力を生成する駆動源と、前記駆動力を前記圧縮機本体に伝達するギヤを収容するギヤケーシングを有し、
前記潤滑経路は前記軸受及びギヤに前記潤滑油を供給する経路であることを特徴とする圧縮機。 The compressor according to any one of claims 1 to 3,
The compressor body is an oil-free compressor body having a rotor that compresses gas, a rotor shaft, and a bearing that rotatably supports the rotor shaft,
A drive source that generates a driving force for driving the compressor body; and a gear casing that houses a gear that transmits the driving force to the compressor body;
The compressor characterized in that the lubricating path is a path for supplying the lubricating oil to the bearings and gears.
JP2016132594A 2016-07-04 2016-07-04 Compressor Pending JP2018003720A (en)

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