JP6715327B2 - air compressor - Google Patents

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JP6715327B2
JP6715327B2 JP2018522267A JP2018522267A JP6715327B2 JP 6715327 B2 JP6715327 B2 JP 6715327B2 JP 2018522267 A JP2018522267 A JP 2018522267A JP 2018522267 A JP2018522267 A JP 2018522267A JP 6715327 B2 JP6715327 B2 JP 6715327B2
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oil
temperature
air
lubricating oil
suction air
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JPWO2017212623A1 (en
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良二 河井
良二 河井
小谷　正直
正直 小谷
土屋　豪
豪 土屋
紘太郎 千葉
紘太郎 千葉
美奈子 金田
美奈子 金田
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Hitachi Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0207—Lubrication with lubrication control systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0284—Constructional details, e.g. reservoirs in the casing
    • F04B39/0292—Lubrication of pistons or cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F04B39/062—Cooling by injecting a liquid in the gas to be compressed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/16—Filtration; Moisture separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F04B49/065—Control using electricity and making use of computers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D25/0606—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump
    • F04D25/0613—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump the electric motor being of the inside-out type, i.e. the rotor is arranged radially outside a central stator
    • F04D25/0626—Details of the lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/006—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids by influencing fluid temperatures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/007—Conjoint control of two or more different functions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/06—Lubrication
    • F04D29/063—Lubrication specially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/5826—Cooling at least part of the working fluid in a heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/5846—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling by injection
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00—Pump parameters
    • F04B2201/04—Carter parameters
    • F04B2201/0402—Lubricating oil temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00—Pump parameters
    • F04B2201/08—Cylinder or housing parameters
    • F04B2201/0801—Temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2205/00—Fluid parameters
    • F04B2205/10—Inlet temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/18—Lubricating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D31/00—Pumping liquids and elastic fluids at the same time

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Computer Hardware Design (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Description

本発明は、空気圧縮機に関する。 The present invention relates to an air compressor.

油冷式空気圧縮機の従来技術には、例えば特開２０１４−８８８７６号公報（特許文献１）がある。特許文献１の要約欄には、「圧縮機要素部の圧縮室に注入弁から液体が注入される液体注入式圧縮機要素部の冷却方法であって、この圧縮機要素部の圧縮室に注入される液体の量を、他の可能な調整装置に関係なく、特定の制御パラメータに応じて制御するステップを含むことを特徴とする方法」が開示されている。 As a conventional technique of the oil-cooled air compressor, there is, for example, JP-A-2014-88876 (Patent Document 1). In the summary column of Patent Document 1, "A cooling method for a liquid injection type compressor element part in which a liquid is injected into a compression chamber of the compressor element part from an injection valve, and the liquid is injected into the compression chamber of the compressor element part The method is characterized in that it comprises the step of controlling the amount of liquid dispensed, irrespective of other possible regulating devices, according to a particular control parameter.

特開２０１４−８８８７６号公報JP, 2014-88876, A

一般に、圧縮室内の空気は、圧縮作用により圧力が上昇し、それに伴って温度が上昇するだけでなく、空気中の水分が凝縮する温度である露点温度も上昇する。このため、露点温度以下の潤滑油を圧縮室に供給すると、圧縮空気中の水分が凝縮し、潤滑油の信頼性を低下させる原因になる。 In general, the pressure of the air in the compression chamber rises due to the compression action, so that not only the temperature rises, but also the dew point temperature, which is the temperature at which water in the air condenses, rises. Therefore, when lubricating oil having a dew point temperature or lower is supplied to the compression chamber, moisture in the compressed air is condensed, which causes a decrease in reliability of the lubricating oil.

特許文献１に開示の空気圧縮機では、圧縮空気出口温度を低温に保つことはできるものの、圧縮室に供給する油温に対する配慮がなされていないために、圧縮室内における水分の凝縮に起因する錆の発生、油膜破断、潤滑油の酸化劣化等によって、例えば圧縮機の軸受の信頼性上の問題が生じることがあった。 In the air compressor disclosed in Patent Document 1, although the compressed air outlet temperature can be kept at a low temperature, no consideration is given to the temperature of the oil supplied to the compression chamber, so rust caused by condensation of water in the compression chamber Occurrence of oil, rupture of oil film, oxidative deterioration of lubricating oil, etc. may cause a problem in reliability of the bearing of the compressor, for example.

本発明は、上記課題に鑑みてなされたものであり、圧縮空気中の水分の凝縮に配慮することにより信頼性の高い空気圧縮機を提供することを目的とする。 The present invention has been made in view of the above problems, and an object of the present invention is to provide an air compressor having high reliability by considering condensation of water in compressed air.

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採用する。本願は上記課題を解決する手段を複数含んでいるが、その一例を挙げるならば、圧縮機本体と、吸込空気を圧縮する前記圧縮機本体の圧縮室と、該圧縮室に潤滑油を供給する給油口と、前記圧縮室から吐出された圧縮空気と潤滑油を分離する油分離器と、前記給油口に供給する潤滑油の温度を調節する油温度調節手段と、前記吸込空気の温度を検知する吸込空気温度検知手段と、前記吸込空気の湿度を検知する吸込空気湿度検知手段と、前記吸込空気温度検知手段と前記吸込空気湿度検知手段の検知情報に基づいて前記油温度調節手段を制御する制御手段とを備え、前記油温度調節手段は、前記圧縮機本体を含むことを特徴とする。 In order to solve the above problems, for example, the configurations described in the claims are adopted. The present application includes a plurality of means for solving the above problems. To give an example thereof, a compressor body, a compression chamber of the compressor body that compresses intake air, and a lubricating oil are supplied to the compression chamber. and oil supply port, and an oil separator for separating the compressed air and lubricating oil discharged from the compression chamber, and the oil temperature adjusting means for adjusting the temperature of the supplied lubricating oil to the fuel supply port, a temperature before Symbol suction air Suction air temperature detecting means for detecting, suction air humidity detecting means for detecting the humidity of the suction air, and controlling the oil temperature adjusting means based on the detection information of the suction air temperature detecting means and the suction air humidity detecting means And a control unit for controlling the oil temperature , the oil temperature adjusting unit including the compressor main body .

本発明によれば、吸引空気の温湿度に基づいて空気圧縮機を運転するので、圧縮空気中の水分の凝縮を抑制または低減でき、信頼性の高い空気圧縮機を提供することができる。 According to the present invention, the air compressor is operated based on the temperature and humidity of the sucked air, so that condensation of water in the compressed air can be suppressed or reduced, and a highly reliable air compressor can be provided.

本発明の実施形態に係る空気圧縮機の構成を表す図である。It is a figure showing the composition of the air compressor concerning the embodiment of the present invention. 本発明の実施形態に係る空気圧縮機の制御を表すフローチャートである。It is a flow chart showing control of an air compressor concerning an embodiment of the present invention. 本発明の実施形態に係る空気圧縮機の運転モードを表す図である。It is a figure showing the driving mode of the air compressor concerning the embodiment of the present invention. 本発明の実施形態に係る空気圧縮機の制御状態を表すタイムチャートである。It is a time chart showing the control state of the air compressor concerning the embodiment of the present invention. 圧縮空気の露点温度と圧力の関係を表す図である。It is a figure showing the relationship between the dew point temperature of compressed air and pressure. 本発明の第二の実施形態に係る空気圧縮機の構成を表す図である。It is a figure showing the structure of the air compressor which concerns on 2nd embodiment of this invention. 本発明の第二の実施形態に係る空気圧縮機の制御を表すフローチャートである。It is a flow chart showing control of an air compressor concerning a second embodiment of the present invention. 本発明の第三の実施形態に係る空気圧縮機の構成を表す図である。It is a figure showing the structure of the air compressor which concerns on 3rd embodiment of this invention. 本発明の第三の実施形態に係る空気圧縮機の制御を表すフローチャートである。It is a flow chart showing control of an air compressor concerning a third embodiment of the present invention. 本発明の第四の実施形態例に係る空気圧縮機の構成を表す図である。It is a figure showing the structure of the air compressor which concerns on the example of 4th Embodiment of this invention. 本発明の第四の実施形態例に係る空気圧縮機の潤滑油温度制御を表すフローチャートである。It is a flowchart showing the lubricating oil temperature control of the air compressor which concerns on the example of 4th Embodiment of this invention.

以下、本発明に係る実施形態例について適宜図面を参照して説明する。 Hereinafter, embodiments of the present invention will be described with reference to the drawings as appropriate.

以下、本発明に係る第一の実施形態例について図１〜図５を参照しながら説明する。
図１は本実施形態例の空気圧縮機の構成図である。図１に示す通り空気圧縮機１は、圧縮機本体１０、油分を分離する油分離器２０、吐出空気を冷却する吐出空気冷却用熱交換器２１、潤滑油を冷却する油冷却用熱交換器２２、吐出空気冷却用熱交換器２１と油冷却用熱交換器２２に通風する回転数可変の送風機２３を備えている。The first embodiment of the present invention will be described below with reference to FIGS.
FIG. 1 is a configuration diagram of an air compressor of the present embodiment. As shown in FIG. 1, an air compressor 1 includes a compressor body 10, an oil separator 20 for separating oil, a discharge air cooling heat exchanger 21 for cooling discharge air, and an oil cooling heat exchanger for cooling lubricating oil. 22, a blower 23 having a variable rotation speed, which ventilates the heat exchanger 21 for discharging air cooling and the heat exchanger 22 for oil cooling.

空気圧縮機１は、圧縮機本体１０の圧縮室１０ａ内に大気を吸引して圧縮し、高温高圧空気（例えば、８０℃、０．８ＭＰａ程度）を生成する。圧縮機本体１０は、回転数可変のモータ１０ｂと、モータ１０ｂの動力を伝達する軸の軸受部１０ｃを備えている。軸受部１０ｃには軸受部給油口１０ｄが、圧縮室１０ａには圧縮室給油口１０ｅがそれぞれ備えられており、潤滑油が供給される。圧縮空気は潤滑油とともに吐出され、吐出流路２４（図１中に太い実線で示す流路）を介して油分離器２０に至り、空気と油に分離される。なお、空気と油は必ずしも完全に分離されている必要はなく、空気に所定値以下の油が混ざっていても良い。油分が分離された空気は、空気流路２５（図１中に細い実線で示す流路）に入り、吐出空気冷却用熱交換器２１に至る。圧縮空気は、吐出空気冷却用熱交換器２１において、送風機２３の駆動により形成される気流５０（図１中に矢印で示す気流）によって大気と熱交換して使用温度域まで冷却され、空気圧縮機１の機外へ送られる。 The air compressor 1 sucks atmospheric air into the compression chamber 10a of the compressor body 10 and compresses it to generate high-temperature high-pressure air (for example, 80° C. and 0.8 MPa). The compressor body 10 includes a motor 10b having a variable rotation speed and a shaft bearing portion 10c for transmitting the power of the motor 10b. The bearing portion 10c is provided with a bearing portion oil supply port 10d, and the compression chamber 10a is provided with a compression chamber oil supply port 10e to supply lubricating oil. The compressed air is discharged together with the lubricating oil, reaches the oil separator 20 via the discharge flow path 24 (flow path indicated by a thick solid line in FIG. 1), and is separated into air and oil. It should be noted that the air and the oil do not necessarily have to be completely separated, and the oil may have a predetermined value or less mixed with the air. The air from which the oil has been separated enters the air flow path 25 (flow path indicated by a thin solid line in FIG. 1) and reaches the discharge air cooling heat exchanger 21. In the heat exchanger 21 for cooling the discharged air, the compressed air is heat-exchanged with the atmosphere by the air flow 50 (the air flow shown by the arrow in FIG. 1) formed by the drive of the blower 23 to be cooled to the operating temperature range. It is sent to the outside of machine 1.

一方、油分離器２０で分離された潤滑油（本実施例では、一般的な圧縮機用の油を用いる）は、油流路２６（図１中に一点鎖線で示す流路）に入り、油冷却用熱交換器２２に至る。潤滑油は、油冷却用熱交換器２２において、送風機２３の駆動により形成される気流によって大気と熱交換して冷却された後に、軸受部給油口１０ｄ、圧縮室給油口１０ｅから軸受部１０ｃと圧縮室１０ａに給油される。
On the other hand, the lubricating oil separated by the oil separator 20 (in this embodiment, a general compressor oil is used) enters the oil passage 26 (the passage indicated by the alternate long and short dash line in FIG. 1), It reaches the heat exchanger 22 for oil cooling. Lubricating oil in the oil cooling heat exchanger 2 2, after being cooled by air and the heat exchanger by the air flow formed by the driving of the blower 23, the bearing portion 10c bearing part filler opening 10d, from the compression chamber oil supply port 10e And the compression chamber 10a is refueled.

本実施形態例の空気圧縮機１は、吸込空気の温度（Ｔ１）を検知する吸込空気温度センサ３１、吸込空気の湿度（Ｈ１）を検知する吸込空気湿度センサ３２を備えており、ＣＰＵ、ＲＯＭやＲＡＭ等のメモリ、インターフェース回路等を搭載した図示しない制御基板（制御手段）と接続されている。圧縮機本体１０のモータ１０ｂのＯＮ／ＯＦＦや回転速度制御、送風機２３のＯＮ／ＯＦＦや回転速度制御はＲＯＭに予め搭載されたプログラムにより制御手段から行われる。 The air compressor 1 according to the present embodiment includes a suction air temperature sensor 31 that detects the temperature (T1) of the suction air, and a suction air humidity sensor 32 that detects the humidity (H1) of the suction air. It is connected to a control board (control means) (not shown) having a memory such as a RAM or RAM, an interface circuit, and the like. ON/OFF and rotation speed control of the motor 10b of the compressor body 10 and ON/OFF and rotation speed control of the blower 23 are performed from the control means by a program loaded in the ROM in advance.

図２は本実施形態例の空気圧縮機の潤滑油温度制御を表すフローチャートである。このフローチャートは、空気圧縮機１全体の動作を制御するメインプログラム（不図示）のサブルーチンとして実行されるものである。 FIG. 2 is a flowchart showing the lubricating oil temperature control of the air compressor of this embodiment. This flowchart is executed as a subroutine of a main program (not shown) that controls the overall operation of the air compressor 1.

本実施形態例の空気圧縮機１では、図２に示す制御フローにより圧縮室給油口１０eに供給する潤滑油の温度が制御される。具体的には、まず吸込空気温度Ｔ１と、吸込空気湿度Ｈ１を検知し（ステップＳ１０１）、続いて検知した吸込空気温度Ｔ１と、吸込空気湿度Ｈ１に基づいて運転モード（後述）が選定される（ステップＳ１０２）。次に現在の運転モードと選定された運転モードが一致しているか否かが判定される（ステップＳ１０３）。運転モードが一致している場合（Ｙｅｓ）、潤滑油温度制御処理を終了しメインプログラムに戻る。一方、運転モードが一致していない場合（Ｎｏ）、ステップＳ１０２で選定された運転モードにモードが変更され、潤滑油温度制御処理を終了しメインプログラムに戻る。 In the air compressor 1 of the present embodiment example, the temperature of the lubricating oil supplied to the compression chamber oil supply port 10e is controlled by the control flow shown in FIG. Specifically, first, the intake air temperature T1 and the intake air humidity H1 are detected (step S101), and then the operation mode (described later) is selected based on the detected intake air temperature T1 and the intake air humidity H1. (Step S102). Next, it is determined whether or not the current operation mode and the selected operation mode match (step S103). When the operation modes match (Yes), the lubricating oil temperature control process is terminated and the process returns to the main program. On the other hand, when the operation modes do not match (No), the mode is changed to the operation mode selected in step S102, the lubricating oil temperature control process is terminated, and the process returns to the main program.

図３は本実施形態例の空気圧縮機の運転モードを表す図である。図３に示す通り、本実施形態例の空気圧縮機１は、吸込空気温度Ｔ１と吸込空気湿度Ｈ１に基づいて運転モードが選定される。吸込空気温度Ｔ１、吸込空気湿度Ｈ１がそれぞれ高温、高湿の場合は、圧縮機本体１０を低速、送風機２３を低速で駆動する「モード１」が選定される。吸込空気温度Ｔ１と吸込空気湿度Ｈ１がそれぞれ低温、高湿の場合は、圧縮機本体１０を高速、送風機２３を低速で駆動する「モード２」が選定される。また、吸込空気温度Ｔ１によらず吸込空気湿度Ｈ１が低湿の場合は圧縮機本体１０を高速、送風機２３を高速で駆動する「モード３」が選定される。
FIG. 3 is a diagram showing operation modes of the air compressor of the present embodiment. As shown in FIG. 3, the operation mode of the air compressor 1 of the present embodiment is selected based on the intake air temperature T1 and the intake air humidity H1. Suction air temperature T1, the suction air humidity H1 is a high temperature, respectively, in the case of high humidity, the compressor body 1 0 slow, the "mode 1" for driving the blower 23 at low speed is selected. Low suction air temperature T1 and the suction air humidity H1 is respectively in the case of high humidity, high-speed compressor body 1 0, is the "mode 2" for driving the blower 23 at low speed is selected. Also, high-speed compressor body 1 0 If the suction air humidity H1 is the humidity regardless of the suction air temperature T1, the "mode 3" to drive the blower 23 at a high speed is selected.

なお、本実施形態例の空気圧縮機１においては、吸込空気温度Ｔ１が３０℃以上を高温、３０℃未満を低温、吸込空気湿度Ｈ１が相対湿度８０％以上を高湿、相対湿度８０％未満を低湿としている。また、圧縮機本体１０（モータ１０ｂ）は高速時６０００ｍｉｎ−１、低速時４０００ｍｉｎ−１、送風機２３は高速時２０００ｍｉｎ−１、低速時１０００ｍｉｎ−１で駆動される。なお、吸込空気の温度として３０℃、湿度として８０％を基準としたのは、実使用環境を考慮して設定した一例であり、必ずしもこれに限定されるものではない。In the air compressor 1 of the present embodiment, the suction air temperature T1 is high at 30° C. or higher, low at less than 30° C., and suction air humidity H1 is high relative humidity 80% or higher, relative humidity less than 80%. Is low humidity. Further, the compressor main body 10 (the motor 10b) is fast at 6000 min -1, low speed 4000 min -1, the blower 23 is driven at a high speed during 2000 min -1, low speed 1000min -1. Note that the temperature of the intake air is set to 30° C. and the humidity is set to 80%, which is an example set in consideration of the actual use environment, and is not necessarily limited thereto.

図４は本実施形態例の空気圧縮機の制御状態を表すタイムチャートである。図４に示す通り、時間ｔ１以前においては、吸込空気温度Ｔ１が閾値Ｔｔｈ（本実施形態例の空気圧縮機１ではＴｔｈ＝３０℃）より高い高温の状態、吸込空気湿度Ｈ１が閾値Ｈｔｈ（本実施形態例の空気圧縮機１ではＨｔｈ＝８０％（相対湿度））より低い低湿の状態となっているので、運転は「モード３」が選定され、潤滑油温度は低い温度で保たれている。時間ｔ１において、吸込空気温度Ｔ１は高温状態で維持されているが、湿度がＨｔｈに達しているので、吸込空気温度Ｔ１が高温、吸込空気湿度Ｈ１が高湿状態における運転モード「モード２」が選定され（図２のステップＳ１０２）、「モード２」による運転に切り替わる（ステップ１０３、ステップ１０４）。「モード２」による運転に切り替わったことにより図４上段に示すように、油冷却用熱交換器２２における熱交換量が低下するので潤滑油温度が上昇する。 FIG. 4 is a time chart showing the control state of the air compressor of this embodiment. As shown in FIG. 4, before the time t1, the intake air temperature T1 is higher than the threshold value Tth (Tth=30° C. in the air compressor 1 of the embodiment), and the intake air humidity H1 is equal to the threshold value Hth (main value). Since the air compressor 1 of the example embodiment is in a low humidity state lower than Hth=80% (relative humidity), “mode 3” is selected for the operation, and the lubricating oil temperature is kept at a low temperature. .. At time t1, the suction air temperature T1 is maintained in a high temperature state, but the humidity reaches Hth, so the suction air temperature T1 is high, and the operation mode “mode 2” in the high humidity state of the suction air humidity H1 is The operation is selected (step S102 in FIG. 2), and the operation is switched to the "mode 2" (step 103, step 104). As shown in the upper part of FIG. 4, the amount of heat exchange in the oil-cooling heat exchanger 22 decreases due to the switching to the “mode 2” operation, so that the lubricating oil temperature rises.

圧縮機本体１０に給油された潤滑油は、圧縮機本体１０における圧縮機構の摩擦熱や、圧縮により温度が上昇する空気からの熱で加熱されることで、温度が上昇して吐出される。潤滑油の温度上昇の度合いは圧縮機本体１０の回転速度（回転数）に依存し、給油状態が同等であれば高速（高回転）であるほど温度上昇が大きくなる。一方、圧縮機本体１０で温度が上昇した潤滑油は、油分離器２０で分離された後に、油冷却用熱交換器２２で冷却されるが、この冷却の度合いは、送風機２３の回転速度（回転数）、換言すると送風量に依存し、高速（高回転）であるほど冷却（温度の低下）が促進される。すなわち、圧縮室１０ａから圧縮機本体１０に給油される潤滑油の温度は、圧縮機本体（第一の油温度調節手段）１０と、油冷却用熱交換器２２に送風する送風機（第二の油温度調節手段）２３により制御される。なお、送風機２３を一定速とした場合、圧縮機本体１０への導入空気量を弁等で制御することで、送風量を調整する構成であっても良い。
The lubricating oil supplied to the compressor body 10 is heated by the frictional heat of the compression mechanism in the compressor body 10 and the heat from the air whose temperature rises due to compression, so that the temperature rises and is discharged. The degree of temperature increase of the lubricating oil depends on the rotation speed (rotation speed) of the compressor body 10, and if the oil supply state is the same, the higher the speed (high rotation), the greater the temperature increase. On the other hand, the lubricating oil temperature rises by the compressor main body 1 0, after being separated in the oil separator 20, but is cooled by the oil cooling heat exchanger 22, the degree of cooling, the rotational speed of the blower 23 (Rotation speed), in other words, depending on the amount of air blown, the higher the speed (higher speed), the faster the cooling (lowering of temperature). That is, the temperature of the lubricating oil to be fed between the compressor body 1 0 from the compression chamber 10 a includes a compressor main body (the first oil temperature adjusting means) 10, a blower for blowing air to the oil cooling heat exchanger 22 (second Second oil temperature adjusting means) 23. Incidentally, when the blower 23 is constant speed, the introduction amount of air to the compressor body 1 0 by controlling a valve or the like, may be configured to adjust the air volume.

図５は、吸込空気（ここでは大気圧下で３０℃の空気）が断熱圧縮された場合の温度変化と、露点温度の変化を示す図である。図５中に破線で示すように、大気圧下（０．１ＭＰａ）で３０℃の空気を０．８ＭＰａまで断熱圧縮すると温度は約２７５℃まで上昇する。このとき、露点温度も同時に上昇する。例えば、図５中に示すように、大気圧下で３０℃、相対湿度５０％の空気は、露点温度が約１８℃から約５７℃に上昇し、３０℃、相対湿度９５％の空気は、露点温度が約２９℃から約７１℃に上昇する。このように吸込空気の温度が同じであっても湿度が高いほど圧縮過程における露点も高くなるため、圧縮室１０ａに露点温度以下の潤滑油を供給すると、圧縮空気中の水分が凝縮し、錆の発生、油膜破断、潤滑油の酸化劣化等の信頼性低下の要因になる。 FIG. 5 is a diagram showing a change in temperature and a change in dew point temperature when aspirated air (here, air at 30° C. under atmospheric pressure) is adiabatically compressed. As indicated by a broken line in FIG. 5, when air at 30° C. is adiabatically compressed to 0.8 MPa under atmospheric pressure (0.1 MPa), the temperature rises to about 275° C. At this time, the dew point temperature also rises at the same time. For example, as shown in FIG. 5, air having an atmospheric pressure of 30° C. and a relative humidity of 50% has a dew point temperature rising from about 18° C. to about 57° C. The dew point temperature rises from about 29°C to about 71°C. Thus, even if the temperature of the intake air is the same, the higher the humidity is, the higher the dew point in the compression process is. Therefore, when the lubricating oil having the dew point temperature or lower is supplied to the compression chamber 10a, the moisture in the compressed air is condensed and rust is generated. May cause deterioration of reliability such as occurrence of oil, breakage of oil film, and oxidation deterioration of lubricating oil.

したがって本実施形態例の空気圧縮機１では、吸込空気温度Ｔ１と吸込空気湿度Ｈ１を検知して、その検知情報に基づいて油温調節手段（本実施例では圧縮機本体１０の回転数と送風機２３の送風量）を制御するようにしている。これにより、圧縮空気中における水分の凝縮による信頼性低下が起こりやすい状態を見極めて、油温調節手段を制御することができるため、錆の発生、油膜破断、潤滑油の酸化劣化等が起こり難い信頼性が高い空気圧縮機を提供できる。
Thus the air compressor 1 in the present embodiment, by detecting the intake air temperature T1 and the suction air humidity H1, the rotation speed of the compressor body 1 0 in the oil temperature adjusting means (the embodiment on the basis of the detection information The amount of air blown by the blower 23) is controlled. As a result, it is possible to control the oil temperature adjusting means by observing the state where reliability is likely to decrease due to the condensation of water in the compressed air, and therefore rusting, oil film breakage, and oxidative deterioration of lubricating oil are unlikely to occur It is possible to provide a highly reliable air compressor.

本実施形態例の空気圧縮機１では、圧縮機本体（第一の油温度調節手段）１０と、油冷却用熱交換器２２に通風する送風機（第二の油温度調節手段）２３と、の二つの油温調節手段を備えている。これにより、よりきめ細かい制御が実現でき、錆の発生、油膜破断、潤滑油の酸化劣化等が起こり難い信頼性が高い空気圧縮機を提供できる。 In the air compressor 1 of the present embodiment, a compressor body (first oil temperature adjusting means) 10 and a blower (second oil temperature adjusting means) 23 that ventilates the oil cooling heat exchanger 22 are provided. It is equipped with two oil temperature control means. As a result, it is possible to provide a highly reliable air compressor in which finer control can be realized and rusting, oil film breakage, oxidative deterioration of lubricating oil, etc. are less likely to occur.

また、本実施形態例の空気圧縮機１では、吸込空気温度Ｔ１がほぼ一定の場合、吸込空気湿度Ｈ１の上昇に伴って、 潤滑油の温度が上昇するように油温調節手段（圧縮機本体１０の回転速度と送風機２３の回転速度）を制御する（モード３からモード１、または、モード３からモード２に運転モードを切り替える）。これにより、圧縮空気中における水分の凝縮に起因する錆の発生、油膜破断、潤滑油の酸化劣化等が起こり難い信頼性が高い空気圧縮機としている。
Further, in the air compressor 1 of the present embodiment example, when the suction air temperature T1 is substantially constant, the oil temperature adjusting means (compressor body) is adjusted so that the temperature of the lubricating oil rises as the suction air humidity H1 rises. controls one 0 rotational speeds of the blower 23) (mode from the mode 3 1, or switches the operation mode from the mode 3 to mode 2). As a result, the air compressor has a high reliability in which rust generation, oil film breakage, oxidative deterioration of lubricating oil, etc. are unlikely to occur due to condensation of water in compressed air.

また、本実施形態例の空気圧縮機１では、吸込空気湿度（相対湿度）Ｈ１がほぼ一定の場合、吸込空気温度Ｔ１の上昇に伴って、潤滑油の温度が上昇するように油温調節手段（圧縮機本体１０の回転速度と送風機２３の回転速度）を制御する（モード２からモード１に運転モードを切り替える）。これにより、圧縮空気中における水分の凝縮に起因する錆の発生、油膜破断、潤滑油の酸化劣化等が起こり難い信頼性が高い空気圧縮機となる。
Further, in the air compressor 1 of the present embodiment example, when the suction air humidity (relative humidity) H1 is substantially constant, the oil temperature adjusting means is arranged so that the temperature of the lubricating oil rises as the suction air temperature T1 rises. controlling the (rotational speed of the compressor body 1 0 of the rotational speed and the blower 23) (switching the operation mode to the mode 1 from the mode 2). As a result, an air compressor with high reliability in which rusting due to condensation of water in compressed air, oil film breakage, oxidative deterioration of lubricating oil, etc., is unlikely to occur.

以下、本発明に係る第二の実施形態例について図６及び図７を参照しながら説明する。第一の実施形態例と同一機能部品については、同一符号を付すことで重複説明を省略する。 Hereinafter, a second embodiment of the present invention will be described with reference to FIGS. 6 and 7. The same functional components as those of the first embodiment are designated by the same reference numerals and the duplicate description is omitted.

図６は、第二の実施形態例の空気圧縮機の構成を表す図である。図６に示す通り、本実施形態例の空気圧縮機１は、油冷却用熱交換器２２から圧縮室給油口１０ｅに至る経路に油温度センサ３４を備えている。また、吐出空気冷却用熱交換器２１への通風用の回転数可変の送風機２３ａと、油冷却用熱交換器２２に通風する回転数可変の送風機２３ｂ（油温調節手段）をそれぞれ備えており、それぞれ独立に制御できるようにしている。吐出空気冷却用熱交換器２１には送風機２３ａの駆動により気流５０ａ（図６中の右から上に向かう矢印で示す気流）が形成され、油冷却用熱交換器２２には送風機２３ｂの駆動により気流５０ｂ（図６中の右から下に向かう矢印で示す気流）が形成される。 FIG. 6 is a diagram showing the configuration of the air compressor of the second embodiment. As shown in FIG. 6, the air compressor 1 of the present embodiment is equipped with an oil temperature sensor 34 in the path from the oil cooling heat exchanger 22 to the compression chamber oil supply port 10e. Further, a variable speed fan 23a for ventilation to the discharge air cooling heat exchanger 21 and a variable speed fan 23b (oil temperature adjusting means) for ventilating the oil cooling heat exchanger 22 are respectively provided. , Each of them can be controlled independently. An airflow 50a (an airflow indicated by an arrow from the right to the upper side in FIG. 6) is formed in the discharge air cooling heat exchanger 21 by driving the blower 23a, and the oil cooling heat exchanger 22 is driven by the blower 23b. An airflow 50b (airflow indicated by an arrow from the right to the bottom in FIG. 6) is formed.

図７は、第二の実施形態例の空気圧縮機の潤滑油温度制御を表すフローチャートである。このフローチャートは、空気圧縮機１全体の動作を制御するメインプログラム（不図示）のサブルーチンとして実行されるものである。 FIG. 7 is a flowchart showing the lubricating oil temperature control of the air compressor of the second embodiment. This flowchart is executed as a subroutine of a main program (not shown) that controls the overall operation of the air compressor 1.

本実施形態例の空気圧縮機１は、図７に示す制御フローにより圧縮室給油口１０ｅに供給する潤滑油の温度を制御する。図７に示す通り、本実施形態例の空気圧縮機１は、吸込空気温度Ｔ１と、吸込空気湿度Ｈ１を検知し（ステップＳ２０１）、その検知情報に基づいて、潤滑油目標温度Ｔｇｏａｌを算出する（ステップＳ２０２）。なお、本実施形態例の空気圧縮機１では、圧縮室給油口１０ｅが設置される位置の圧力における露点温度（Ｔｓａｔ）を算出（推定）して潤滑油目標温度Ｔｇｏａｌとする。例えば、Ｔｇｏａｌ＝Ｔｓａｔ＋ΔＴとして、安全定数（ΔＴ）を加えて潤滑油目標温度Ｔｇｏａｌを算出する。 The air compressor 1 of the present embodiment controls the temperature of the lubricating oil supplied to the compression chamber oil supply port 10e according to the control flow shown in FIG. As shown in FIG. 7, the air compressor 1 of the present embodiment detects the intake air temperature T1 and the intake air humidity H1 (step S201), and calculates the lubricating oil target temperature Tgoal based on the detection information. (Step S202). In the air compressor 1 of the present embodiment, the dew point temperature (Tsat) at the pressure at the position where the compression chamber oil supply port 10e is installed is calculated (estimated) to be the lubricating oil target temperature Tgoal. For example, assuming that Tgoal=Tsat+ΔT, the safety constant (ΔT) is added to calculate the lubricating oil target temperature Tgoal.

次に潤滑油温度Ｔ３と目標温度Ｔｇｏａｌの差が５℃より小さいか否かが判定される（ステップＳ２０３）。ステップＳ２０３が成立している場合（Ｙｅｓ）、続いて潤滑油温度Ｔ３と目標温度Ｔｇｏａｌの差が２℃より大きいか否かが判定される（ステップＳ２０４）。ステップＳ２０４が成立している場合（Ｙｅｓ）は潤滑油温度制御処理を終了しメインプログラムに戻る。なお、ステップＳ２０３の５℃、ステップＳ２０４の２℃の基準温度は一例であって、特にこれに限定するものではない。 Next, it is determined whether the difference between the lubricating oil temperature T3 and the target temperature Tgoal is less than 5° C. (step S203). When step S203 is established (Yes), it is subsequently determined whether the difference between the lubricating oil temperature T3 and the target temperature Tgoal is larger than 2° C. (step S204). When step S204 is established (Yes), the lubricating oil temperature control process is terminated and the process returns to the main program. Note that the reference temperatures of 5° C. in step S203 and 2° C. in step S204 are examples and are not particularly limited thereto.

ステップＳ２０３が成立していない場合（Ｎｏ）は、続いて送風機２３ｂの回転数が上限回転数に到達しているか否かが判定される（ステップＳ２５０）。ちなみに、本実施形態例の空気圧縮機１では、送風機２３ｂの上限回転数は３０００ｍｉｎ−１である。ステップＳ２５０で送風機２３ｂの回転数が上限に達していると判定された場合（Ｙｅｓ）、続いて、圧縮機本体１０（モータ１０ｂ）の回転数が下限回転数に到達しているか否かが判定される（ステップＳ２５１）。ちなみに、本実施形態例の空気圧縮機１では、圧縮機本体１０の下限回転数は２０００ｍｉｎ−１である。ステップＳ２５１で圧縮機本体１０の回転数が下限回転数に到達していると判定された場合（Ｙｅｓ）、空気圧縮機１は運転を停止（圧縮機本体１０、送風機２３ａ、２３ｂを停止）して（ステップＳ２５２）、潤滑油温度制御処理を終了しメインプログラムに戻る。この場合、外気温度が高温であること等が想定されるので、異常の報知等を行う。なお、上述の送風機２３ｂの上限回転数３０００ｍｉｎ−１、圧縮機本体１０（モータ１０ｂ）の下限回転数２０００ｍｉｎ−１は一例であって、特にこれに限定するものではない。If step S203 is not established (No), it is subsequently determined whether or not the rotation speed of the blower 23b has reached the upper limit rotation speed (step S250). Incidentally, in the air compressor 1 of the present embodiment example, the upper limit rotation speed of the blower 23b is 3000 min −1 . When it is determined in step S250 that the rotation speed of the blower 23b has reached the upper limit (Yes), it is subsequently determined whether the rotation speed of the compressor body 10 (motor 10b) has reached the lower limit rotation speed. (Step S251). By the way, in the air compressor 1 of the present embodiment, the lower limit rotation speed of the compressor body 10 is 2000 min −1 . When it is determined in step S251 that the rotation speed of the compressor body 10 has reached the lower limit rotation speed (Yes), the air compressor 1 stops the operation (stops the compressor body 10 and the blowers 23a and 23b). (Step S252), the lubricating oil temperature control process is terminated and the process returns to the main program. In this case, since it is assumed that the outside air temperature is high, etc., the abnormality is notified. Incidentally, an example lower limit rotation speed 2000 min -1 is the upper limit rotation speed 3000 min -1 blower 23b described above, the compressor main body 10 (motor 10b), not particularly limited thereto.

ステップＳ２５１で圧縮機本体１０の回転数が下限回転数に到達していないと判定された場合（Ｎｏ）、圧縮機本体１０の回転数が低減され（ステップＳ２５３）、ステップＳ２０３に戻る。ステップＳ２５０で送風機２３ｂの回転数が上限に達していないと判定された場合（Ｎｏ）、送風機２３ｂの回転数が増加され（ステップＳ２５４）、ステップＳ２０３に戻る。 When it is determined in step S251 that the rotation speed of the compressor body 10 has not reached the lower limit rotation speed (No), the rotation speed of the compressor body 10 is reduced (step S253), and the process returns to step S203. When it is determined in step S250 that the rotation speed of the blower 23b has not reached the upper limit (No), the rotation speed of the blower 23b is increased (step S254), and the process returns to step S203.

ステップＳ２０４が成立していない場合（Ｎｏ）、続いて送風機２３ｂが停止しているか否かが判定される（ステップＳ２６０）。ステップＳ２６０が成立している場合（Ｙｅｓ）、潤滑油温度制御処理を終了しメインプログラムに戻る。ステップＳ２６０が成立していない場合（Ｎｏ）、送風機２３ｂの回転数が低減され（ステップＳ２６１）、ステップＳ２０４に戻る。ちなみに、本実施形態例の空気圧縮機１では、送風機２３ｂの下限回転数は５００ｍｉｎ−１であり、ステップＳ２６０において５００ｍｉｎ−１であった場合には、ステップＳ２６１で送風機２３ｂは停止する。なお、送風機２３ｂの下限回転数５００ｍｉｎ−１は一例であり、これに限定されるものではない。When step S204 is not established (No), it is subsequently determined whether or not the blower 23b is stopped (step S260). When step S260 is established (Yes), the lubricating oil temperature control process is terminated and the process returns to the main program. When step S260 is not materialized (No), the rotation speed of the blower 23b is reduced (step S261), and it returns to step S204. Incidentally, in the air compressor 1 in the present embodiment, the lower limit rotation speed of the blower 23b is 500 min -1, in the case was 500 min -1 in step S260, the blower 23b in step S261 is stopped. The lower limit rotation speed of the blower 23b, 500 min −1, is an example, and the present invention is not limited to this.

なお、本実施形態例の空気圧縮機１ではステップＳ２５３、Ｓ２５４、Ｓ２６１における操作量は、潤滑油温度Ｔ３と目標温度Ｔｇｏａｌの偏差と、潤滑油温度Ｔ３と目標温度Ｔｇｏａｌの偏差の時間積分にあらかじめ定めた定数を乗ずることにより求める。 In the air compressor 1 of the present embodiment, the manipulated variables in steps S253, S254, and S261 are calculated in advance by the time integration of the deviation between the lubricating oil temperature T3 and the target temperature Tgoal and the deviation between the lubricating oil temperature T3 and the target temperature Tgoal. It is calculated by multiplying by a fixed constant.

以上のように、本実施形態例の空気圧縮機１は、吸込空気温度Ｔ１と吸込空気湿度Ｈ１とともに、潤滑油温度Ｔ３を検知して潤滑油の温度制御を行っている。これにより、よりきめ細かく潤滑油温度Ｔ３を制御できるようになるので、圧縮空気中における水分の凝縮に起因する錆の発生、油膜破断、潤滑油の酸化劣化等が起こり難い信頼性が高い空気圧縮機を提供することができる。 As described above, the air compressor 1 of the present embodiment controls the temperature of the lubricating oil by detecting the lubricating oil temperature T3 as well as the suction air temperature T1 and the suction air humidity H1. As a result, the lubricating oil temperature T3 can be controlled more finely, and therefore a highly reliable air compressor in which rust generation, oil film breakage, oxidative deterioration of lubricating oil, etc. due to condensation of water in compressed air are unlikely to occur. Can be provided.

本実施形態例の空気圧縮機１は、吐出空気冷却用熱交換器２１への通風用の送風機２３ａと、油冷却用熱交換器２２に通風する送風機２３ｂ（油温調節手段）をそれぞれ備えており、吐出空気冷却用熱交換器２１と油冷却用熱交換器２２への送風を独立に制御できるようにしている。これにより、吐出空気を所望の温度域に冷却するための温度制御と、潤滑油の温度制御を両立しやすくなるので、圧縮空気中における水分の凝縮に起因する錆の発生、油膜破断、潤滑油の酸化劣化等が起こり難い信頼性が高い空気圧縮機となる。 The air compressor 1 of the present embodiment includes a blower 23a for ventilation to the heat exchanger 21 for discharging air cooling, and a blower 23b (oil temperature adjusting means) for ventilation to the heat exchanger 22 for oil cooling. Therefore, the blowing air to the discharge air cooling heat exchanger 21 and the oil cooling heat exchanger 22 can be controlled independently. As a result, it becomes easy to achieve both temperature control for cooling the discharge air to a desired temperature range and temperature control of the lubricating oil, so that the occurrence of rust due to the condensation of moisture in the compressed air, the oil film breakage, and the lubricating oil. A highly reliable air compressor in which oxidative deterioration and the like hardly occur.

本実施形態例の空気圧縮機１は、吸込空気温度Ｔ１と吸込空気湿度Ｈ１に基づいて潤滑油目標温度Ｔｇｏａｌを算出するステップ（ステップＳ２０２）と、潤滑油温度Ｔ３と潤滑油目標温度Ｔｇｏａｌを比較するステップ（ステップＳ２０３、Ｓ２０４）と、潤滑油温度Ｔ３と潤滑油目標温度Ｔｇｏａｌの偏差を解消するように潤滑油温度制御手段を制御するステップ（ステップＳ２５２、Ｓ２５３、Ｓ２５４、Ｓ２６１）を備えている。これにより、吸込空気温度Ｔ１と吸込空気湿度Ｈ１が変化した場合に、よりきめ細かく潤滑油温度Ｔ３を追従させることができ、圧縮空気中における水分の凝縮に起因する錆の発生、油膜破断、潤滑油の酸化劣化等が起こり難い信頼性が高い空気圧縮機となる。 The air compressor 1 of the present embodiment compares the lubricating oil temperature T3 and the lubricating oil target temperature Tgoal with the step of calculating the lubricating oil target temperature Tgoal based on the suction air temperature T1 and the suction air humidity H1 (step S202). Steps (Steps S203, S204) and Steps (Steps S252, S253, S254, S261) for controlling the lubricating oil temperature control means so as to eliminate the deviation between the lubricating oil temperature T3 and the lubricating oil target temperature Tgoal. .. As a result, when the intake air temperature T1 and the intake air humidity H1 change, the lubricating oil temperature T3 can be made to follow more finely, and the generation of rust due to the condensation of moisture in the compressed air, the oil film breakage, and the lubricating oil. A highly reliable air compressor in which oxidative deterioration and the like hardly occur.

本実施形態例の空気圧縮機１は、潤滑油温度Ｔ３が潤滑油目標温度Ｔｇｏａｌに対して所定値以上高い場合に（ステップＳ２０３）、送風機２３ｂの回転数を上げる（ステップＳ２５４）、あるいは、圧縮機本体１０の回転数を下げる（ステップＳ２５３）ように制御する。これにより潤滑油温度を低下させることができるので、水分の凝縮を抑制または低減して信頼性を確保しつつ、圧縮過程における空気の冷却を促進でき圧縮機の効率を高めることができる。 When the lubricating oil temperature T3 is higher than the lubricating oil target temperature Tgoal by a predetermined value or more (step S203), the air compressor 1 of the present embodiment increases the rotation speed of the blower 23b (step S254) or compresses it. The rotation speed of the machine body 10 is controlled to be lowered (step S253). As a result, the temperature of the lubricating oil can be lowered, so that the cooling of air in the compression process can be promoted and the efficiency of the compressor can be improved while suppressing or reducing the condensation of water to ensure reliability.

本実施形態例の空気圧縮機１は、圧縮室給油口１０ｅが設置される位置の圧力における露点温度を潤滑油目標温度Ｔｇｏａｌとしている。図５に示す通り圧縮過程で空気の露点温度は上昇するので、圧縮室給油口が設置さられる位置の圧力によって露点温度は異なる。そこで、本実施形態例の空気圧縮機１では、圧縮室給油口１０ｅが設置される位置における露点温度を算出（推定）し、潤滑油目標温度Ｔｇｏａｌとすることで、より確実に水分の凝縮を抑制でき、錆の発生、油膜破断、潤滑油の酸化劣化等が起こり難い信頼性が高い空気圧縮機となる。 In the air compressor 1 of this embodiment, the dew point temperature at the pressure at the position where the compression chamber oil supply port 10e is installed is the lubricating oil target temperature Tgoal. As shown in FIG. 5, since the dew point temperature of air rises during the compression process, the dew point temperature varies depending on the pressure at the position where the compression chamber oil supply port is installed. Therefore, in the air compressor 1 of the present embodiment example, the dew point temperature at the position where the compression chamber oil supply port 10e is installed is calculated (estimated) and set as the lubricating oil target temperature Tgoal, so that the moisture is more reliably condensed. An air compressor that can be suppressed and has high reliability in which rusting, oil film breakage, and oxidative deterioration of lubricating oil are unlikely to occur.

以下、本発明に係る第三の実施形態例について図８及び図９を参照しながら説明する。第一及び第二の実施形態例と同一機能部品については、同一符号を付すことで重複説明を省略する。 Hereinafter, a third embodiment of the present invention will be described with reference to FIGS. 8 and 9. The same functional parts as those of the first and second embodiments are designated by the same reference numerals, and the duplicated description will be omitted.

図８は、第三の実施形態例の空気圧縮機の構成を表す図である。図８に示す通り、本実施形態例の空気圧縮機１は、油分離器２０の下流側で、油冷却用熱交換器２２に向かう流路２６ａと、油冷却用熱交換器２２を流れないバイパス流路２６ｂに分岐している。流路２６ａに入った潤滑油は、油冷却用熱交換器２２で冷却された後に、バイパス流路２６ｂを流れる油冷却用熱交換器２２で冷却されていない潤滑油と合流する。バイパス流路２６ｂには潤滑油の流量を制御する油流量制御弁５１が備えられており、油流量制御弁５１の開度によって、バイパス流路２６ｂを流れる流量と、油冷却用熱交換器２２を流れる流量の比率が制御される。なお、油冷却用熱交換器２２と、吐出空気冷却用熱交換器２１には、送風機２３の駆動によって気流が形成される。なお、油流量制御弁５１以外にも、ポンプ等で潤滑油の流量を制御する構成であっても良い。 FIG. 8: is a figure showing the structure of the air compressor of 3rd embodiment. As shown in FIG. 8, the air compressor 1 of the present embodiment does not flow on the downstream side of the oil separator 20 toward the oil cooling heat exchanger 22 and the oil cooling heat exchanger 22. It branches into the bypass flow path 26b. The lubricating oil that has entered the flow passage 26a is cooled by the oil cooling heat exchanger 22 and then merges with the lubricating oil that has not been cooled by the oil cooling heat exchanger 22 that flows through the bypass passage 26b. The bypass flow passage 26b is provided with an oil flow rate control valve 51 for controlling the flow rate of the lubricating oil. Depending on the opening degree of the oil flow rate control valve 51, the flow rate flowing through the bypass flow passage 26b and the oil cooling heat exchanger 22 The ratio of the flow rates flowing through is controlled. An air flow is formed in the oil cooling heat exchanger 22 and the discharge air cooling heat exchanger 21 by driving the blower 23. Instead of the oil flow rate control valve 51, a pump or the like may be used to control the flow rate of the lubricating oil.

以上の構成とすることで、油冷却用熱交換器２２における潤滑油の冷却量は、圧縮機本体（第一の油温度制御手段）１０、送風機（第二の油温度制御手段）２３の送風量によって制御されるとともに、油流量制御弁（第三の油温度制御手段）５１の開度によっても制御可能となる。油流量制御弁５１の開度が大きいと、バイパス流路２６ｂを流れる流量が増え、相対的に油冷却用熱交換器２２を流れる流量が少なくなることで熱交換量が減少し、合流後の潤滑油温度Ｔ３（油温度センサ３４での検出値）が上昇する。なお、本実施形態例の空気圧縮機１における流量制御弁５１は、ステッピングモータにより開度を自在に調節できるバタフライ弁である。なお、これ以外にも、油流量制御弁５１はニードル式弁、電磁弁等、流量を調整可能な構成であれば、あらゆる公知の弁を採用することができる。 With the above configuration, the cooling amount of the lubricating oil in the oil cooling heat exchanger 22 is determined by the compressor main body (first oil temperature control means) 10 and the blower (second oil temperature control means) 23. In addition to being controlled by the air flow rate, it can also be controlled by the opening degree of the oil flow rate control valve (third oil temperature control means) 51. When the opening degree of the oil flow rate control valve 51 is large, the flow rate flowing through the bypass flow passage 26b is increased, and the flow rate flowing through the oil cooling heat exchanger 22 is relatively decreased, so that the heat exchange amount is reduced, and after the merging. The lubricating oil temperature T3 (value detected by the oil temperature sensor 34) rises. The flow control valve 51 in the air compressor 1 of the present embodiment is a butterfly valve whose opening can be freely adjusted by a stepping motor. Other than this, the oil flow rate control valve 51 may be any known valve such as a needle valve or a solenoid valve as long as the flow rate can be adjusted.

図９は、第三の実施形態例の空気圧縮機の潤滑油温度制御を表すフローチャートである。このフローチャートは、空気圧縮機１全体の動作を制御するメインプログラム（不図示）のサブルーチンとして実行されるものである。 FIG. 9 is a flowchart showing the lubricating oil temperature control of the air compressor of the third embodiment. This flowchart is executed as a subroutine of a main program (not shown) that controls the overall operation of the air compressor 1.

本実施形態例の空気圧縮機１は、図９に示す制御フローにより圧縮室給油口１０ｅに供給する潤滑油の温度を制御する。図９に示す通り、本実施形態例の空気圧縮機１は、吸込空気温度Ｔ１と、吸込空気湿度Ｈ１を検知し（ステップＳ３０１）、その検知情報に基づいて、潤滑油目標温度Ｔｇｏａｌを算出する（ステップＳ３０２）。本実施形態例の空気圧縮機１では断熱圧縮を仮定した場合の圧縮機本体１０の吐出圧における露点温度を算出して潤滑油目標温度Ｔｇｏａｌとする。次に潤滑油温度Ｔ３と目標温度Ｔｇｏａｌの差が５℃より小さいか否かが判定される（ステップＳ３０３）。ステップＳ３０３が成立している場合（Ｙｅｓ）は、続いて潤滑油温度Ｔ３と目標温度Ｔｇｏａｌの差が２℃より大きいか否かが判定される（ステップＳ３０４）。ステップＳ３０４が成立している場合（Ｙｅｓ）は潤滑油温度制御処理を終了しメインプログラムに戻る。 The air compressor 1 of the present embodiment controls the temperature of the lubricating oil supplied to the compression chamber oil supply port 10e according to the control flow shown in FIG. As shown in FIG. 9, the air compressor 1 of the present embodiment example detects the intake air temperature T1 and the intake air humidity H1 (step S301), and calculates the lubricating oil target temperature Tgoal based on the detection information. (Step S302). In the air compressor 1 of the present embodiment example, the dew point temperature at the discharge pressure of the compressor body 10 under the assumption of adiabatic compression is calculated as the lubricating oil target temperature Tgoal. Next, it is determined whether the difference between the lubricating oil temperature T3 and the target temperature Tgoal is less than 5° C. (step S303). If step S303 is established (Yes), it is subsequently determined whether the difference between the lubricating oil temperature T3 and the target temperature Tgoal is greater than 2° C. (step S304). When step S304 is established (Yes), the lubricating oil temperature control process is terminated and the process returns to the main program.

ステップＳ３０３が成立していない場合（Ｎｏ）は、続いて弁５１が全閉か否かが判定される（ステップＳ３５０）。ステップＳ３５０が成立している場合（Ｙｅｓ）、続いて、送風機２３の回転数が上限回転数に到達しているか否かが判定される（ステップＳ３５１）。ちなみに、本実施形態例の空気圧縮機１では、送風機２３の上限回転数は３０００ｍｉｎ−１である。ステップＳ３５１が成立している場合（Ｙｅｓ）、潤滑油温度制御処理を終了しメインプログラムに戻る。なお、送風機２３の送風量を制御すると、油冷却用熱交換器２２だけでなく吐出空気冷却用熱交換器２１の熱交換量、すなわち吐出空気温度にも影響が出ることがある。そこで、本実施例では、弁５１の開度を調整した後、送風機２３の送風量を調整している。
If step S303 is not established (No), it is subsequently determined whether or not the valve 51 is fully closed (step S350). When step S350 is established (Yes), it is subsequently determined whether or not the rotation speed of the blower 23 has reached the upper limit rotation speed (step S351). Incidentally, in the air compressor 1 of the present embodiment example, the upper limit rotation speed of the blower 23 is 3000 min −1 . When step S351 is established (Yes), the lubricating oil temperature control process is terminated and the process returns to the main program. Controlling the amount of air blown by the blower 23 may affect not only the heat exchanger 22 for cooling the oil but also the heat exchange amount of the heat exchanger 21 for discharging air, that is, the discharge air temperature. Therefore, in the present embodiment, after adjusting the opening degree of the valve 51, which adjusts the air volume of feed air blower 23.

ステップＳ３５１で送風機２３の回転数が上限回転数に到達していないと判定された場合（Ｎｏ）、送風機２３の回転数が増加され（ステップＳ３５２）、ステップＳ３０３に戻る。ステップＳ３５０で弁５１が全閉ではないと判定された場合（Ｎｏ）、弁５１の開度が縮小され（ステップＳ３５３）、ステップＳ３０３に戻る。 When it is determined in step S351 that the rotation speed of the blower 23 has not reached the upper limit rotation speed (No), the rotation speed of the blower 23 is increased (step S352), and the process returns to step S303. When it is determined in step S350 that the valve 51 is not fully closed (No), the opening degree of the valve 51 is reduced (step S353), and the process returns to step S303.

ステップＳ３０４が成立していない場合（Ｎｏ）、続いて弁５１が全開か否かが判定される（ステップＳ３６０）。ステップＳ３６０が成立している場合（Ｙｅｓ）、続いて、送風機２３の回転数が下限回転数に到達しているか否かが判定される（ステップＳ３６１）。ちなみに、本実施形態例の空気圧縮機１では、送風機２３の下限回転数は５００ｍｉｎ−１である。ステップＳ３６１が成立している場合（Ｙｅｓ）、潤滑油温度制御処理を終了しメインプログラムに戻る。If step S304 is not satisfied (No), then it is determined whether the valve 51 is fully opened (step S360). When step S360 is satisfied (Yes), it is subsequently determined whether or not the rotation speed of the blower 23 has reached the lower limit rotation speed (step S361). By the way, in the air compressor 1 of the present embodiment, the lower limit rotation speed of the blower 23 is 500 min −1 . If step S361 is satisfied (Yes), the lubricating oil temperature control process is terminated and the process returns to the main program.

ステップＳ３６１で送風機２３の回転数が下限回転数に到達していないと判定された場合（Ｎｏ）、送風機２３の回転数が低減され（ステップＳ３６２）、ステップＳ３０４に戻る。ステップＳ３６０で弁５１が全開ではないと判定された場合（Ｎｏ）、弁５１の開度が増加され（ステップＳ３６３）、ステップＳ３０４に戻る。 When it is determined in step S361 that the rotation speed of the blower 23 has not reached the lower limit rotation speed (No), the rotation speed of the blower 23 is reduced (step S362), and the process returns to step S304. When it is determined that the valve 51 is not fully opened in step S360 (No), the opening degree of the valve 51 is increased (step S363), and the process returns to step S304.

なお、本実施形態例の空気圧縮機１ではステップＳ３５２、Ｓ３５３、Ｓ３６２、Ｓ３６３における操作量は、潤滑油温度Ｔ３と目標温度Ｔｇｏａｌの偏差と、潤滑油温度Ｔ３と目標温度Ｔｇｏａｌの偏差の時間積分にあらかじめ定めた定数を乗ずることにより求める。 In the air compressor 1 of the present embodiment, the manipulated variables in steps S352, S353, S362, and S363 are the time integration of the deviation between the lubricating oil temperature T3 and the target temperature Tgoal and the deviation between the lubricating oil temperature T3 and the target temperature Tgoal. It is obtained by multiplying by a predetermined constant.

以上のように本実施形態例の空気圧縮機１では、油冷却用熱交換器２２を流れる油量を増減することで潤滑油温度Ｔ３を制御している。これにより、油冷却用熱交換器２２の熱交換能力を容易に調整でき、所望の潤滑油温度が得られやすくなるので、より確実に水分の凝縮を抑制でき、錆の発生、油膜破断、潤滑油の酸化劣化等が起こり難い信頼性が高い空気圧縮機となる。 As described above, in the air compressor 1 of the present embodiment, the lubricating oil temperature T3 is controlled by increasing or decreasing the amount of oil flowing through the oil cooling heat exchanger 22. As a result, the heat exchange capacity of the oil-cooling heat exchanger 22 can be easily adjusted, and the desired lubricating oil temperature can be easily obtained, so that the condensation of water can be suppressed more reliably, rusting, oil film breakage, and lubrication It becomes a highly reliable air compressor in which oxidative deterioration of oil does not easily occur.

以下、本発明に係る第四の実施形態例について図１０及び図１１を参照しながら説明する。第一乃至第三の実施形態例と同一機能部品については、同一符号を付すことで重複説明を省略する。 Hereinafter, a fourth exemplary embodiment according to the present invention will be described with reference to FIGS. 10 and 11. The same functional parts as those of the first to third embodiments are designated by the same reference numerals, and a duplicate description will be omitted.

図１０は、第四の実施形態例の空気圧縮機の構成を表す図である。図１０に示す通り、本実施形態例の空気圧縮機１は、油分離器２０の下流側に油流量制御弁５１を備えている。油流量制御弁５１は、入口５１ａと出口５１ｂと５１ｃを備えた三方弁であり、出口５１ｂと出口５１ｃをともに開放状態（状態Ａ）、出口５１ｂを開放状態として、出口５１ｃを閉鎖状態（状態Ｂ）、出口５１ｂを閉鎖状態として、出口５１ｃを開放状態（状態Ｃ）、に制御可能な弁である。油流量制御弁５１の出口５１ｂと５１ｃは、それぞれ流路２６ａと流路２６ｂに接続され、流路２６ａと流路２６ｂは、油冷却用熱交換器２２の一部２２ａを流れる流路と残りの部分２２ｂを流れる流路にそれぞれ接続される。油冷却用熱交換器２２の一部２２ａの空気側の伝熱面積は油冷却用熱交換器２２の残りの部分２２ｂより大きくしてある。また、油冷却用熱交換器２２の一部２２ａと残りの部分２２ｂの出口は、それぞれ流路２６ｃと流路２６ｄに接続され、接続部２６ｅで合流する。
FIG. 10 is a diagram showing the configuration of the air compressor of the fourth embodiment. As shown in FIG. 10, the air compressor 1 of the present embodiment example includes an oil flow rate control valve 51 on the downstream side of the oil separator 20. The oil flow control valve 51 is a three-way valve having an inlet 51a, outlets 51b and 51c, both the outlet 51b and the outlet 51c in an open state (state A), the outlet 51b in an open state, and the outlet 51c in a closed state (state). B) is a valve that can be controlled so that the outlet 51b is closed and the outlet 51c is opened (state C). The outlets 51 b and 51 c of the oil flow rate control valve 51 are connected to the flow paths 26a and 26b, respectively, and the flow paths 26a and 26b flow through the part 22a of the oil cooling heat exchanger 22. And the remaining portions 22b are respectively connected to the flow paths. The air-side heat transfer area of a part 22a of the oil cooling heat exchanger 22 is larger than that of the remaining part 22b of the oil cooling heat exchanger 22. Further, the outlets of the part 22a and the remaining part 22b of the oil cooling heat exchanger 22 are connected to the flow passage 26c and the flow passage 26d, respectively, and join at the connecting portion 26e.

油流量制御弁５１が状態Ａに制御される場合、潤滑油は油冷却用熱交換器２２の一部２２ａと残りの部分２２ｂの両方を流れるので、油冷却用熱交換器２２の全体で空気と熱交換して温度が低下する。また、油流量制御弁５１が状態Ｂに制御される場合、潤滑油は油冷却用熱交換器２２の一部２２ａのみに流れる。さらに、油流量制御弁５１が状態Ｃに制御される場合、潤滑油は油冷却用熱交換器２２の残りの部分２２ｂのみに流れる。状態Ｂ及び状態Ｃでは、油冷却用熱交換器２２の全体で空気と熱交換する状態Ａより熱交換量が小さくなるため、潤滑油の温度低下は小さくなる。また、油冷却用熱交換器２２の一部２２ａの空気側の伝熱面積は、油冷却用熱交換器２２の残りの部分２２ｂより大きいので、状態Ｂの方が、状態Ｃより熱交換量が大きくなる（温度低下が大きくなる）。 When the oil flow control valve 51 is controlled to the state A, the lubricating oil flows through both the part 22a and the remaining part 22b of the oil cooling heat exchanger 22, so that the entire oil cooling heat exchanger 22 is air-cooled. Exchanges heat with the temperature drop. When the oil flow rate control valve 51 is controlled to the state B, the lubricating oil flows only in the part 22a of the oil cooling heat exchanger 22. Further, when the oil flow control valve 51 is controlled to the state C, the lubricating oil flows only to the remaining portion 22b of the oil cooling heat exchanger 22. In states B and C, the amount of heat exchange is smaller than in state A in which the heat exchanger 22 for oil cooling as a whole exchanges heat with air, so the temperature drop of the lubricating oil is small. Further, since the air-side heat transfer area of the part 22a of the oil cooling heat exchanger 22 is larger than the remaining part 22b of the oil cooling heat exchanger 22, the heat exchange amount in the state B is larger than that in the state C. Becomes larger (the temperature drop becomes larger).

以上から、油流量制御弁５１の制御状態と熱交換量の大小関係は、状態Ａ＞状態Ｂ＞状態Ｃとなり、同等の送風条件下では、潤滑油温度Ｔ３は状態Ａが最も低く、状態Ｃが最も高くなる。 From the above, the magnitude relationship between the control state of the oil flow rate control valve 51 and the heat exchange amount is State A>State B>State C, and under the same blowing condition, the lubricating oil temperature T3 is the lowest in the state A and the state C. Is the highest.

図１１は、第四の実施形態例の空気圧縮機の潤滑油温度制御を表すフローチャートである。このフローチャートは、空気圧縮機１全体の動作を制御するメインプログラム（不図示）のサブルーチンとして実行されるものである。 FIG. 11 is a flowchart showing the lubricating oil temperature control of the air compressor of the fourth embodiment. This flowchart is executed as a subroutine of a main program (not shown) that controls the overall operation of the air compressor 1.

本実施形態例の空気圧縮機１は、図１１に示す制御フローにより、圧縮室給油口１０ｅに供給する潤滑油の温度を制御する。図１１に示す通り、本実施形態例の空気圧縮機１は、吸込空気温度Ｔ１と、吸込空気湿度Ｈ１を検知し（ステップＳ４０１）、その検知情報に基づいて、潤滑油目標温度Ｔｇｏａｌを算出する（ステップＳ４０２）。本実施形態例の空気圧縮機１では、断熱圧縮を仮定した場合の圧縮機本体１０の吐出圧における露点温度を算出して潤滑油目標温度Ｔｇｏａｌとする。次に、潤滑油温度Ｔ３と目標温度Ｔｇｏａｌの差が５℃より小さいか否かが判定される（ステップＳ４０３）。ステップＳ４０３が成立している場合（Ｙｅｓ）は、続いて潤滑油温度Ｔ３と目標温度Ｔｇｏａｌの差が２℃より大きいか否かが判定される（ステップＳ４０４）。ステップＳ４０４が成立している場合（Ｙｅｓ）は潤滑油温度制御処理を終了しメインプログラムに戻る。 The air compressor 1 of the present embodiment controls the temperature of the lubricating oil supplied to the compression chamber oil supply port 10e according to the control flow shown in FIG. As shown in FIG. 11, the air compressor 1 of the present embodiment example detects the intake air temperature T1 and the intake air humidity H1 (step S401), and calculates the lubricating oil target temperature Tgoal based on the detection information. (Step S402). In the air compressor 1 of the present embodiment example, the dew point temperature at the discharge pressure of the compressor body 10 under the assumption of adiabatic compression is calculated as the lubricating oil target temperature Tgoal. Next, it is determined whether the difference between the lubricating oil temperature T3 and the target temperature Tgoal is smaller than 5° C. (step S403). If step S403 is established (Yes), then it is determined whether the difference between the lubricating oil temperature T3 and the target temperature Tgoal is greater than 2° C. (step S404). When step S404 is established (Yes), the lubricating oil temperature control process is terminated and the process returns to the main program.

ステップＳ４０３が成立していない場合（Ｎｏ）は、続いて弁５１が状態Ａ（出口５１ｂ開放状態、出口５１ｃ開放状態）か否かが判定される（ステップＳ４５０）。ステップＳ４５０が成立している場合（Ｙｅｓ）、続いて、送風機２３の回転数が上限回転数に到達しているか否かが判定される（ステップＳ４５１）。ステップＳ４５１が成立している場合（Ｙｅｓ）、潤滑油温度制御処理を終了しメインプログラムに戻る。 When step S403 is not established (No), it is subsequently determined whether or not the valve 51 is in the state A (outlet 51b open state, outlet 51c open state) (step S450). When step S450 is established (Yes), it is subsequently determined whether or not the rotation speed of the blower 23 has reached the upper limit rotation speed (step S451). When step S451 is established (Yes), the lubricating oil temperature control process is terminated and the process returns to the main program.

ステップＳ４５１で送風機２３の回転数が上限回転数に到達していないと判定された場合（Ｎｏ）、送風機２３の回転数が増加され（ステップＳ４５２）、ステップＳ４０３に戻る。ステップＳ４５０で弁５１が状態Ａではないと判定された場合（Ｎｏ）、続いて弁５１が状態Ｂ（出口５１ｂ開放状態、出口５１ｃ閉鎖状態）か否かが判定され（ステップＳ４５３）、ステップＳ４５３が成立している場合（Ｙｅｓ）、弁５１は状態Ａに制御され（ステップＳ４５４）、ステップＳ４０３に戻る。ステップＳ４５３が成立していない場合（Ｎｏ）、弁５１は状態Ｂに制御され（ステップＳ４５５）、ステップＳ４０３に戻る。 When it is determined in step S451 that the rotation speed of the blower 23 has not reached the upper limit rotation speed (No), the rotation speed of the blower 23 is increased (step S452), and the process returns to step S403. When it is determined in step S450 that the valve 51 is not in the state A (No), it is subsequently determined whether or not the valve 51 is in the state B (the outlet 51b open state, the outlet 51c closed state) (step S453), and step S453. When is satisfied (Yes), the valve 51 is controlled to the state A (step S454), and the process returns to step S403. When step S453 is not satisfied (No), the valve 51 is controlled to the state B (step S455), and the process returns to step S403.

ステップＳ４０４が成立していない場合（Ｎｏ）、続いて弁５１が状態Ｃ（出口５１ｂ閉鎖状態、出口５１ｃ開放状態）か否かが判定される（ステップＳ４６０）。ステップＳ４６０が成立している場合（Ｙｅｓ）、続いて、送風機２３の回転数が下限回転数に到達しているか否かが判定される（ステップＳ４６１）。ステップＳ４６１が成立している場合（Ｙｅｓ）、潤滑油温度制御処理を終了しメインプログラムに戻る。
If step S 4 04 is not satisfied (No), then the valve 51 the state C (outlet 51b closed, the outlet 51c open) it is determined whether or not the (step S460). When step S460 is established (Yes), it is subsequently determined whether or not the rotation speed of the blower 23 has reached the lower limit rotation speed (step S461). If step S461 is satisfied (Yes), the lubricating oil temperature control process is terminated and the process returns to the main program.

ステップＳ４６１で送風機２３の回転数が下限回転数に到達していないと判定された場合（Ｎｏ）、送風機２３の回転数が低減され（ステップＳ４６２）、ステップＳ４０４に戻る。ステップＳ４６０で弁５１が状態Ｃではないと判定された場合（Ｎｏ）、続いて弁５１が状態Ｂか否かが判定され（ステップＳ４６３）、ステップＳ４６３が成立している場合（Ｙｅｓ）、弁５１は状態Ｃに制御され（ステップＳ４６４）、ステップＳ４０４に戻る。ステップＳ４６３が成立していない場合（Ｎｏ）、弁５１は状態Ｂに制御され（ステップＳ４６５）、ステップＳ４０４に戻る。
If the rotational speed of the blower 23 is determined not to have reached the lower limit rotation speed in Step S 46 1 (No), the rotational speed of the blower 23 is reduced (step S462), the flow returns to step S404. If it is determined in step S460 that the valve 51 is not in the state C (No), then it is determined whether the valve 51 is in the state B (step S463). If step S463 is established (Yes), the valve is 51 is controlled to the state C (step S464), the flow returns to step S40 4. If step S463 is not satisfied (No), the valve 51 is controlled to the state B (step S465), the flow returns to step S40 4.

以上のように本実施形態例の空気圧縮機１では、油冷却用熱交換器２２内を流れる潤滑油の状態を制御することで潤滑油温度Ｔ３を制御している。これにより、油冷却用熱交換器２２の熱交換能力を容易に調整でき、所望の潤滑油温度が得られやすくなるので、より確実に水分の凝縮を抑制でき、錆の発生、油膜破断、潤滑油の酸化劣化等が起こり難い信頼性が高い空気圧縮機となる。 As described above, in the air compressor 1 of the present embodiment, the lubricating oil temperature T3 is controlled by controlling the state of the lubricating oil flowing in the oil cooling heat exchanger 22. As a result, the heat exchange capacity of the oil-cooling heat exchanger 22 can be easily adjusted, and the desired lubricating oil temperature can be easily obtained, so that the condensation of water can be suppressed more reliably, rusting, oil film breakage, and lubrication It becomes a highly reliable air compressor in which oxidative deterioration of oil does not easily occur.

なお、本実施形態例では油流量制御弁５１として２つの出口を開閉可能な三方弁を用いているが、複数の開閉弁を組み合わせて流量制御弁５１を構成したり、開度を多段階で切り替え可能な弁を用いてよりきめ細かく制御したりしても良い。 Although the three-way valve capable of opening and closing the two outlets is used as the oil flow rate control valve 51 in the present embodiment, the flow rate control valve 51 is configured by combining a plurality of on-off valves, and the opening degree is set in multiple stages. Finer control may be performed using a switchable valve.

以上で本発明の実施形態例を説明したが、本発明は上記した各実施形態例に限定されるものではなく、様々な変形例が含まれる。例えば、第一の実施形態例の空気圧縮機では、３つの運転モードを切り替えるように制御するが、複数の運転モード（少なくとも２つの運転モード）を吸込空気温度Ｔ１と吸込空気湿度Ｈ１に基づいて切り替える他の実施形態としてもよい。また、各実施形態例の温度センサや湿度センサは、その目的を満たすことができれば設置位置は変えてもよい。すなわち、上記した実施例は本発明を分かりやすく説明したものであり、必ずしも説明した構成を備えるものに限定されるものではない。 Although the exemplary embodiments of the present invention have been described above, the present invention is not limited to the above-described exemplary embodiments and includes various modifications. For example, in the air compressor of the first embodiment, control is performed so as to switch between three operation modes, but a plurality of operation modes (at least two operation modes) are performed based on the intake air temperature T1 and the intake air humidity H1. Other embodiments may be used for switching. Further, the temperature sensor and the humidity sensor of each embodiment may be installed at different positions as long as the purpose can be satisfied. That is, the above-described embodiments are provided to explain the present invention in an easy-to-understand manner, and are not necessarily limited to those having the described configuration.

１ 空気圧縮機
１０ 圧縮機本体（第一の油温度調節手段）
１０ａ 圧縮室
１０ｂ モータ
１０ｃ 軸受部
１０ｄ 軸受部給油口
１０ｅ、１０ｆ 圧縮室給油口
２０ 油分離器
２１ 吐出空気冷却用熱交換器
２２ 油冷却用熱交換器
２３ 送風機（第二の油温度調節手段）
３１ 吸込空気温度センサ（吸込空気温度検知手段）
３２ 吸込空気湿度センサ（吸込空気湿度検知手段）
３４ 油温度センサ
５０ 気流
５１ 油流量制御弁（第三の油温度調節手段）1 Air compressor 10 Compressor body (first oil temperature adjusting means)
10a compression chamber 10b motor 10c bearing part 10d bearing part oil supply port 10e, 10f compression chamber oil supply port 20 oil separator 21 discharge air cooling heat exchanger 22 oil cooling heat exchanger 23 blower (second oil temperature adjusting means)
31 Suction air temperature sensor (suction air temperature detection means)
32 Suction air humidity sensor (suction air humidity detection means)
34 oil temperature sensor 50 air flow 51 oil flow control valve (third oil temperature adjusting means)

Claims (5)

圧縮機本体と、吸込空気を圧縮する前記圧縮機本体の圧縮室と、該圧縮室に潤滑油を供給する給油口と、前記圧縮室から吐出された圧縮空気と潤滑油を分離する油分離器と、前記給油口に供給する潤滑油の温度を調節する油温度調節手段と、前記吸込空気の温度を検知する吸込空気温度検知手段と、前記吸込空気の湿度を検知する吸込空気湿度検知手段と、前記吸込空気温度検知手段と前記吸込空気湿度検知手段の検知情報に基づいて前記油温度調節手段を制御する制御手段とを備え、前記油温度調節手段は、前記圧縮機本体を含むことを特徴とする空気圧縮機。 Compressor main body, compression chamber of the compressor main body for compressing intake air, oil supply port for supplying lubricating oil to the compression chamber, oil separator for separating compressed air discharged from the compression chamber and lubricating oil When an oil temperature adjusting means for adjusting the temperature of the supplied lubricating oil to the fuel supply port, a suction air temperature detecting means for detecting the temperature of the pre-Symbol suction air, the suction air humidity detector that detects humidity of the suction air And a control means for controlling the oil temperature adjusting means based on the detection information of the suction air temperature detecting means and the suction air humidity detecting means , wherein the oil temperature adjusting means includes the compressor body. Characteristic air compressor. 前記吸込空気温度検知手段により検知される吸込空気の温度が略一定で、前記吸込空気湿度検知手段により検知される吸込空気の湿度が上昇した場合に、前記給油口に供給する潤滑油の温度が上昇するように前記油温度調節手段を制御することを特徴とする、請求項１に記載の空気圧縮機。 When the temperature of the suction air detected by the suction air temperature detection means is substantially constant and the humidity of the suction air detected by the suction air humidity detection means rises, the temperature of the lubricating oil supplied to the oil supply port is The air compressor according to claim 1, wherein the oil temperature adjusting means is controlled so as to rise. 潤滑油を冷却する油冷却用熱交換器と、該油冷却用熱交換器に通風する送風機と、を備え、
前記油温度調節手段は、前記送風機を含むことを特徴とする、請求項１または２に記載の空気圧縮機。 An oil cooling heat exchanger for cooling the lubricating oil; and a blower for ventilating the oil cooling heat exchanger,
The oil temperature adjustment means, characterized in that it comprises a pre-Symbol blower, an air compressor according to claim 1 or 2. 前記油分離器の下流側で、前記油冷却用熱交換器に向かう流路と、前記油冷却用熱交換器をバイパスした後に前記流路と合流するバイパス流路と、を備え、
該バイパス流路に潤滑油の流量を制御する油流量制御弁を備えたことを特徴とする、請求項１乃至３の何れかに記載の空気圧縮機。 On the downstream side of the oil separator, a flow path toward the oil cooling heat exchanger, and a bypass flow path that merges with the flow path after bypassing the oil cooling heat exchanger,
The air compressor according to any one of claims 1 to 3 , wherein an oil flow rate control valve for controlling a flow rate of the lubricating oil is provided in the bypass passage. 前記給油口に供給する潤滑油の温度を検知する油温度検知手段を備え、該油温度検知手段により検知される潤滑油温度と、前記吸込空気温度検知手段により検知される吸込空気温度と前記吸込空気湿度検知手段により検知される吸込空気湿度とから目標温度を算出し、前記潤滑油温度と前記目標温度との差異を縮小するように、前記油温度調節手段を制御することを特徴とする、請求項１乃至３の何れかに記載の空気圧縮機。 An oil temperature detection means for detecting the temperature of the lubricating oil supplied to the oil supply port is provided, and the lubricating oil temperature detected by the oil temperature detection means, the suction air temperature detected by the suction air temperature detection means, and the suction A target temperature is calculated from the intake air humidity detected by the air humidity detecting means, and the oil temperature adjusting means is controlled so as to reduce the difference between the lubricating oil temperature and the target temperature. The air compressor according to any one of claims 1 to 3.
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