JP4685474B2 - Oil-free screw air compressor - Google Patents

Oil-free screw air compressor Download PDF

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JP4685474B2
JP4685474B2 JP2005063551A JP2005063551A JP4685474B2 JP 4685474 B2 JP4685474 B2 JP 4685474B2 JP 2005063551 A JP2005063551 A JP 2005063551A JP 2005063551 A JP2005063551 A JP 2005063551A JP 4685474 B2 JP4685474 B2 JP 4685474B2
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compressed air
stage compressor
compressor body
heat exchanger
pressure stage
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JP2006249934A (en
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広志 太田
仁 西村
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Hitachi Industrial Equipment Systems Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Description

本発明は、無給油式スクリュー空気圧縮機に係わり、さらに詳しくは、圧縮空気を冷却する熱交換器を備えた無給油式スクリュー空気圧縮機に関する。   The present invention relates to an oil-free screw air compressor, and more particularly to an oil-free screw air compressor including a heat exchanger that cools compressed air.

単段無給油式スクリュー空気圧縮機は、非接触かつ無給油で回転可能な一対の雄ロータ及び雌ロータを有する圧縮機本体を備えており、雄ロータ及び雌ロータの回転駆動により無給油状態で空気を圧縮する。この空気圧縮に要する動力が熱に変化し、生成した圧縮空気の温度は非常に高くなり、例えば約３００〜３５０℃まで上昇する。そこで従来、圧縮機本体から吐出された圧縮空気を冷却するチューブ式熱交換器を備えた構成が開示されている（例えば、特許文献１参照）。   The single-stage oil-free screw air compressor has a compressor body having a pair of male and female rotors that can rotate in a non-contact and oil-free manner. Compress the air. The power required for this air compression changes to heat, and the temperature of the generated compressed air becomes very high, for example, rises to about 300 to 350 ° C. Therefore, conventionally, a configuration including a tube heat exchanger that cools compressed air discharged from a compressor body has been disclosed (see, for example, Patent Document 1).

また２段無給油式スクリュー圧縮機では、無給油状態で空気を圧縮する低圧段圧縮機本体と、この低圧段圧縮機本体で圧縮された空気をさらに無給油状態で圧縮する高圧段圧縮機本体とを備えており、低圧段圧縮機本体及び高圧段圧縮機本体で生成した圧縮空気の温度は、それぞれ例えば約１６０〜２５０℃まで上昇する。そこで従来、低圧段圧縮機本体から吐出された圧縮空気を冷却して高圧段圧縮機本体に流出するチューブ式熱交換器（インタークーラ）と、高圧段圧縮機本体から吐出された圧縮空気を冷却するチューブ式熱交換器（アフタークーラ）とを備えた構成が開示されている（例えば、特許文献２参照）。   In the two-stage oilless screw compressor, a low-pressure compressor main body that compresses air in an oil-free state, and a high-pressure compressor main body that further compresses air compressed in the low-pressure compressor main body in an oil-free state. The temperature of the compressed air generated by the low-pressure stage compressor main body and the high-pressure stage compressor main body rises to, for example, about 160 to 250 ° C. Therefore, conventionally, a tube-type heat exchanger (intercooler) that cools the compressed air discharged from the low-pressure stage compressor body and flows out to the high-pressure stage compressor body, and cools the compressed air discharged from the high-pressure stage compressor body. The structure provided with the tube-type heat exchanger (aftercooler) to perform is disclosed (for example, refer patent document 2).

上記チューブ式熱交換器は、例えばシェル内に複数のＵ字管を設けた構造であり、Ｕ字管内に圧縮空気を流しシェル内に冷却水（冷却液）を流し（逆に、Ｕ字管内に冷却水を流しシェル内に圧縮空気を流してもよい）、圧縮空気と冷却水が熱交換することにより圧縮空気を冷却するようになっている。また、シェル内のＵ字管は、熱による伸縮を吸収し熱応力の影響を回避するので、耐熱温度が比較的高い構造である。   The tube heat exchanger has a structure in which, for example, a plurality of U-shaped tubes are provided in a shell, and compressed air is flowed into the U-shaped tube and cooling water (coolant) is flowed into the shell (reversely, inside the U-shaped tube The compressed air may be allowed to flow in the shell and the compressed air may flow in the shell), and the compressed air is cooled by heat exchange between the compressed air and the cooling water. Further, the U-shaped tube in the shell has a structure with a relatively high heat-resistant temperature because it absorbs expansion and contraction due to heat and avoids the influence of thermal stress.

特開平３−２９００８９号公報JP-A-3-290089 特開２００１−１５３０８０号公報JP 2001-153080 A

しかしながら、上記従来技術には以下のような改善の余地があった。
すなわち、無給油式スクリュー空気圧縮機においては、上記チューブ式熱交換器の容積が大きな割合を占めており、熱交換器を小型化することで圧縮機全体の小型化を図ることが可能である。ところが、チューブ式熱交換器では、Ｕ字管の径寸法を小さくして本数を増加したり、熱伝達率のよい材質に変更したり、若しくはＵ字管の肉厚を小さくする等の方法により小型化が図れるものの、その小型化には限界があった。 However, the above prior art has room for improvement as follows.
That is, in the oil-free screw air compressor, the volume of the tube heat exchanger occupies a large proportion, and it is possible to reduce the size of the entire compressor by downsizing the heat exchanger. . However, in the tube heat exchanger, the diameter of the U-shaped tube is reduced to increase the number, the material is changed to a material having a good heat transfer coefficient, or the thickness of the U-shaped tube is decreased. Although the size can be reduced, there is a limit to the size reduction.

本発明の目的は、耐熱性を確保しつつ大幅な小型化を図ることができる無給油式スクリュー圧縮機を提供することにある。   An object of the present invention is to provide an oil-free screw compressor that can achieve a significant reduction in size while ensuring heat resistance.

（１）上記目的を達成するために、本発明は、無給油状態で空気を圧縮する低圧段圧縮機本体と、前記低圧段圧縮機本体で圧縮された空気をさらに無給油状態で圧縮する高圧段圧縮機本体と、前記低圧段圧縮機本体の圧縮空気を冷却して前記高圧段圧縮機本体へ流出する低圧側熱交換器、及び前記高圧段圧縮機本体の圧縮空気を冷却する高圧側熱交換器を一体構成したプレート式熱交換器とを備えた無給油式スクリュー空気圧縮機であって、前記プレート式熱交換器は、前記高圧段圧縮機本体の圧縮空気が下方向に流れる第１の圧縮空気流路と、前記低圧段圧縮機本体の圧縮空気が上方向に流れる第２の圧縮空気流路と、前記高圧段圧縮機本体の圧縮空気を冷却する冷却液が上方向に流れる第１の冷却流路と、前記第１の冷却流路に直列接続され、前記低圧段圧縮機本体の圧縮空気を冷却する冷却液が下方向に流れる第２の冷却流路とを備える。 ( 1 ) In order to achieve the above object, the present invention provides a low pressure stage compressor body that compresses air in an oil-free state, and a high pressure that further compresses air compressed in the low pressure stage compressor body in an oil-free state. A main stage compressor body, a low pressure side heat exchanger that cools the compressed air of the low pressure stage compressor body and flows out to the high pressure stage compressor body, and a high pressure side heat that cools the compressed air of the high pressure stage compressor body An oil-free screw air compressor including a plate-type heat exchanger integrally configured with an exchanger, wherein the plate-type heat exchanger is a first where the compressed air of the high-pressure stage compressor body flows downward. A compressed air flow path, a second compressed air flow path through which the compressed air of the low pressure stage compressor body flows upward, and a cooling liquid that cools the compressed air of the high pressure stage compressor body flows upward. 1 cooling flow path and the first cooling flow path in series Is, coolant for cooling the compressed air of the low pressure stage compressor body and a second cooling channel flowing downward.

（２）上記目的を達成するために、本発明は、無給油状態で空気を圧縮する低圧段圧縮機本体と、前記低圧段圧縮機本体で圧縮された空気をさらに無給油状態で圧縮する高圧段圧縮機本体と、前記低圧段圧縮機本体の圧縮空気を冷却して前記高圧段圧縮機本体へ流出する低圧側熱交換器、及び前記高圧段圧縮機本体の圧縮空気を冷却する高圧側熱交換器を一体構成したプレート式熱交換器とを備えた無給油式スクリュー空気圧縮機であって、前記プレート式熱交換器は、前記高圧段圧縮機本体の圧縮空気が下方向に流れる第１の圧縮空気流路と、前記低圧段圧縮機本体の圧縮空気が下方向に流れる第２の圧縮空気流路と、前記高圧段圧縮機本体の圧縮空気を冷却する冷却液が上方向に流れる第１の冷却流路と、前記第１の冷却流路に直列接続され、前記低圧段圧縮機本体の圧縮空気を冷却する冷却液が下方向に流れる第２の冷却流路とを備える。 ( 2 ) In order to achieve the above object, the present invention provides a low pressure stage compressor body that compresses air in an oilless state, and a high pressure that further compresses air compressed in the low pressure stage compressor body in an oilless state. A main stage compressor body, a low pressure side heat exchanger that cools the compressed air of the low pressure stage compressor body and flows out to the high pressure stage compressor body, and a high pressure side heat that cools the compressed air of the high pressure stage compressor body An oil-free screw air compressor including a plate-type heat exchanger integrally configured with an exchanger, wherein the plate-type heat exchanger is a first where the compressed air of the high-pressure stage compressor body flows downward. A compressed air flow path, a second compressed air flow path through which the compressed air of the low-pressure stage compressor body flows downward, and a coolant that cools the compressed air of the high-pressure stage compressor body flows upward. 1 cooling flow path and the first cooling flow path in series Is, coolant for cooling the compressed air of the low pressure stage compressor body and a second cooling channel flowing downward.

（３）上記（１）又は（２）において、好ましくは、前記低圧段圧縮機本体からの圧縮空気及び前記高圧段圧縮機本体からの圧縮空気のうちいずれか一方又は両方を一次冷却して前記プレート式熱交換器へ流出するチューブ式熱交換器を備える。
（４）上記目的を達成するために、本発明は、無給油状態で空気を圧縮する低圧段圧縮機本体と、前記低圧段圧縮機本体で圧縮された空気をさらに無給油状態で圧縮する高圧段圧縮機本体と、前記低圧段圧縮機本体の圧縮空気を冷却して前記高圧段圧縮機本体へ流出する低圧側熱交換器、及び前記高圧段圧縮機本体の圧縮空気を冷却する高圧側熱交換器を一体構成したプレート式熱交換器とを備えた無給油式スクリュー空気圧縮機であって、前記プレート式熱交換器は、前記高圧段圧縮機本体の圧縮空気が流れる第１の圧縮空気流路と、前記低圧段圧縮機本体の圧縮空気が流れる第２の圧縮空気流路と、前記高圧段圧縮機本体の圧縮空気を冷却する冷却液が流れる第１の冷却流路と、前記第１の冷却流路に直列接続され、前記低圧段圧縮機本体の圧縮空気を冷却する冷却液が流れる第２の冷却流路とを備え、前記第１の圧縮空気流路の流れ方向と前記第１の冷却流路の流れ方向とが対向流となるように、かつ前記第２の圧縮空気流路の流れ方向と前記第２の冷却流路の流れ方向とが対向流となるように構成しており、前記低圧段圧縮機本体からの圧縮空気及び前記高圧段圧縮機本体からの圧縮空気のうちいずれか一方又は両方を前記プレート式熱交換器の耐熱温度まで一次冷却して前記プレート式熱交換器へ流出するチューブ式熱交換器を備える。
（５）上記目的を達成するために、本発明は、無給油状態で空気を圧縮する低圧段圧縮機本体と、前記低圧段圧縮機本体で圧縮された空気をさらに無給油状態で圧縮する高圧段圧縮機本体と、前記低圧段圧縮機本体の圧縮空気を冷却して前記高圧段圧縮機本体へ流出する低圧側熱交換器、及び前記高圧段圧縮機本体の圧縮空気を冷却する高圧側熱交換器を一体構成したプレート式熱交換器とを備えた無給油式スクリュー空気圧縮機であって、前記プレート式熱交換器は、前記高圧段圧縮機本体の圧縮空気が流れる第１の圧縮空気流路と、前記低圧段圧縮機本体の圧縮空気が流れる第２の圧縮空気流路と、前記高圧段圧縮機本体の圧縮空気を冷却する冷却液が流れる第１の冷却流路と、前記第１の冷却流路に直列接続され、前記低圧段圧縮機本体の圧縮空気を冷却する冷却液が流れる第２の冷却流路とを備え、前記第２の圧縮空気流路の流れ方向と前記第２の冷却流路の流れ方向とが平行流となるように構成しており、前記低圧段圧縮機本体からの圧縮空気及び前記高圧段圧縮機本体からの圧縮空気のうちいずれか一方又は両方を前記プレート式熱交換器の耐熱温度まで一次冷却して前記プレート式熱交換器へ流出するチューブ式熱交換器を備える。
( 3 ) In the above (1) or (2) , preferably, one or both of the compressed air from the low-pressure stage compressor body and the compressed air from the high-pressure stage compressor body are primarily cooled to A tube heat exchanger that flows out to the plate heat exchanger is provided.
(4) In order to achieve the above object, the present invention provides a low pressure stage compressor body that compresses air in an oil-free state, and a high pressure that further compresses air compressed in the low pressure stage compressor body in an oil-free state. A main stage compressor body, a low pressure side heat exchanger that cools the compressed air of the low pressure stage compressor body and flows out to the high pressure stage compressor body, and a high pressure side heat that cools the compressed air of the high pressure stage compressor body An oil-free screw air compressor including a plate heat exchanger integrally configured with an exchanger, wherein the plate heat exchanger is a first compressed air through which the compressed air of the high-pressure stage compressor body flows. A flow path, a second compressed air flow path through which the compressed air of the low-pressure stage compressor body flows, a first cooling flow path through which a coolant that cools the compressed air of the high-pressure stage compressor body, and the first The low-pressure stage compressor A second cooling flow path through which a cooling liquid for cooling the compressed air flows, and the flow direction of the first compressed air flow path and the flow direction of the first cooling flow path are opposed to each other. And the flow direction of the second compressed air flow path and the flow direction of the second cooling flow path are opposed to each other, the compressed air from the low-pressure stage compressor body and the high pressure A tube-type heat exchanger is provided that primarily cools one or both of the compressed air from the main stage compressor body to the heat-resistant temperature of the plate-type heat exchanger and flows out to the plate-type heat exchanger.
(5) In order to achieve the above object, the present invention provides a low pressure stage compressor body that compresses air in an oil-free state, and a high pressure that further compresses air compressed in the low pressure stage compressor body in an oil-free state. A main stage compressor body, a low pressure side heat exchanger that cools the compressed air of the low pressure stage compressor body and flows out to the high pressure stage compressor body, and a high pressure side heat that cools the compressed air of the high pressure stage compressor body An oil-free screw air compressor including a plate heat exchanger integrally configured with an exchanger, wherein the plate heat exchanger is a first compressed air through which the compressed air of the high-pressure stage compressor body flows. A flow path, a second compressed air flow path through which the compressed air of the low-pressure stage compressor body flows, a first cooling flow path through which a coolant that cools the compressed air of the high-pressure stage compressor body, and the first The low-pressure stage compressor A second cooling flow path through which a cooling liquid for cooling the compressed air flows, and the flow direction of the second compressed air flow path and the flow direction of the second cooling flow path are parallel flows The plate is configured such that one or both of the compressed air from the low-pressure stage compressor body and the compressed air from the high-pressure stage compressor body are primarily cooled to the heat resistant temperature of the plate heat exchanger. A tube-type heat exchanger that flows out to the heat exchanger is provided.

本発明によれば、従来のチューブ式熱交換器のみを設ける場合に比べ、耐熱性を確保しつつ大幅な小型化を図ることができる。   According to this invention, compared with the case where only the conventional tube type heat exchanger is provided, it can attain large size reduction, ensuring heat resistance.

以下、本発明の実施形態を、図面を参照しつつ説明する。   Embodiments of the present invention will be described below with reference to the drawings.

本発明の第１の実施形態を図１〜図３により説明する。本実施形態は、プレート式熱交換器を二段無給油式スクリュー空気圧縮機に設けた実施形態である。 The first embodiment of the present invention will be described with reference to FIGS. 1 to 3. This embodiment is an embodiment in which a plate heat exchanger is provided in a two-stage oilless screw air compressor.

図１は、本実施形態による無給油スクリュー空気圧縮機の全体構造を表す模式図であり、図２は、本実施形態におけるプレート式熱交換機の概略構造を表す模式図であり、図３は、本実施形態におけるプレート式熱交換器の構造を一例として表す斜視分解図である。なお、図１及び図２において、白抜きの矢印は圧縮空気の流れ、黒塗りの矢印は潤滑油の流れ、細線の矢印は冷却水の流れ、斜線塗りの矢印は冷却風の流れを示している。 Figure 1 is a schematic view showing the overall structure of the oil-free screw air compressor according to the present embodiment, FIG. 2 is a schematic view showing the schematic structure of a plate heat exchanger according to this embodiment, FIG. 3, It is a perspective exploded view showing the structure of the plate type heat exchanger in this embodiment as an example. 1 and 2 , the white arrow indicates the flow of compressed air, the black arrow indicates the flow of lubricating oil, the thin arrow indicates the flow of cooling water, and the hatched arrow indicates the flow of cooling air. Yes.

本実施形態による無給油式スクリュー圧縮機は二段圧縮機であり、電動機（モータ）４４と、この電動機４４の回転動力がギヤ装置４５を介し伝達されて駆動する低圧段圧縮機本体４６及び高圧段圧縮機本体４７と、これら低圧段圧縮機本体４６及び高圧段圧縮機本体４７で生成した圧縮空気をそれぞれ冷却するプレート式熱交換器４８とを備えている。   The oil-free screw compressor according to the present embodiment is a two-stage compressor, and includes an electric motor (motor) 44, a low-pressure compressor main body 46 that drives the rotational power of the electric motor 44 transmitted through a gear device 45, and a high-pressure compressor. A stage compressor body 47 and plate type heat exchangers 48 for cooling the compressed air generated by the low pressure stage compressor body 46 and the high pressure stage compressor body 47 are provided.

低圧段圧縮機本体４６は、一対の雄ロータ４９及び雌ロータ５０を有し、これら雄ロータ４９及び雌ロータ５０の一方側（図３中左側）端部に設けられたタイミングギヤ５１，５２が噛合している。これにより、雄ロータ４９及び雌ロータ５０は、非接触かつ無給油で回転するようになっている。同様に、高圧段圧縮機本体４７は、一対の雄ロータ５３及び雌ロータ５４を有し、これら雄ロータ５３及び雌ロータ５４の一方側（図３中左側）端部に設けられたタイミングギヤ５５，５６が噛合している。これにより、雄ロータ５３及び雌ロータ５４は、非接触かつ無給油で回転するようになっている。   The low-pressure compressor main body 46 has a pair of male rotor 49 and female rotor 50, and timing gears 51 and 52 provided at one end (left side in FIG. 3) of the male rotor 49 and female rotor 50 are provided. Meshed. Thereby, the male rotor 49 and the female rotor 50 rotate without contact and without oiling. Similarly, the high-pressure stage compressor body 47 has a pair of male rotors 53 and female rotors 54, and a timing gear 55 provided at one end (left side in FIG. 3) of the male rotors 53 and female rotors 54. 56 are engaged. Thereby, the male rotor 53 and the female rotor 54 rotate without contact and without oiling.

ギヤ装置４５は、下部に油溜め５７を有するギヤケーシング５８と、このギヤケーシング５８に回転自在に支持されブルギヤ５９を有する伝達軸６０とを備えている。電動機４４の回転軸と伝達軸６０がカップリング６１等を介し連結され、雄ロータ５１，５３の他方側（図３中右側）端部にそれぞれ設けたピニオンギヤ６２，６３と伝達軸６０のブルギヤ５９とが噛合している。これにより、電動機４４の回転動力が伝達軸６０、ブルギヤ５９、及びピニオンギヤ６２，６３を介し雄ロータ５１，５３に伝達され、雄ロータ５１，５３が回転駆動するようになっている。なお、ピニオンギヤ６２，６３及びブルギヤ５９は、ギヤケーシング５８内に収納されている。   The gear device 45 includes a gear casing 58 having an oil sump 57 at a lower portion and a transmission shaft 60 having a bull gear 59 that is rotatably supported by the gear casing 58. The rotation shaft of the electric motor 44 and the transmission shaft 60 are connected via a coupling 61 and the like, and pinion gears 62 and 63 provided on the other end (right side in FIG. 3) of the male rotors 51 and 53 and a bull gear 59 of the transmission shaft 60, respectively. Is engaged. Thereby, the rotational power of the electric motor 44 is transmitted to the male rotors 51 and 53 through the transmission shaft 60, the bull gear 59, and the pinion gears 62 and 63, and the male rotors 51 and 53 are rotationally driven. Note that the pinion gears 62 and 63 and the bull gear 59 are housed in a gear casing 58.

また、電動機等によって駆動するオイルポンプ６４が設けられており、このオイルポンプ６４の駆動により、ギヤケーシング５８内の油溜め５７からストレーナ６５を介し吸い込まれた潤滑油は、潤滑油用熱交換器（オイルクーラ）６６及びオイルフィルタ６７等を介し、低圧段圧縮機本体４６及び高圧段圧縮機本体４７のタイミングギヤ５１，５２，５５，５６及び軸受（図示せず）等に供給され、その後ギヤケーシング５８内の油溜め５７に戻って循環するようになっている。   Further, an oil pump 64 driven by an electric motor or the like is provided, and the lubricating oil sucked from the oil reservoir 57 in the gear casing 58 through the strainer 65 by the driving of the oil pump 64 is a heat exchanger for lubricating oil. (Oil cooler) 66, oil filter 67 and the like are supplied to the timing gears 51, 52, 55, 56 and bearings (not shown) of the low pressure stage compressor body 46 and the high pressure stage compressor body 47, and then the gears. It returns to the oil sump 57 in the casing 58 and circulates.

低圧段圧縮機本体４６の吸込み側（図３中上側）には、吸気フィルタ６８と、吸込み空気量を調整する吸込み絞り弁６９とが設けられている。また、吸込み絞り弁６９に連動し、高圧段圧縮機本体４７の圧縮空気をサイレンサ７０を介し放出する放気弁７１が設けられている。そして、負荷運転時は、吸気フィルタ６８及び吸込み絞り弁６９を介し低圧段圧縮機本体４６に圧縮用空気（外気）が吸込まれて所定の圧力まで圧縮され、この圧縮空気が吐出配管７２を介しプレート式熱交換器４８の低圧側熱交換器４８ａ側に吐出され、プレート式熱交換器４８の低圧側熱交換器４８ａ側で冷却された圧縮空気が導出配管７３を介し高圧段圧縮機本体４７に導入されて圧縮され、この圧縮空気が吐出配管７４を介しプレート式熱交換器４８の高圧側熱交換器４８ｂ側に吐出され、プレート式熱交換器４８の高圧側熱交換器４８ｂで冷却された圧縮空気が供給配管７５を介し外部の機器等（図示せず）に供給されるようになっている。また無負荷運転時は、吸込み絞り弁６９を閉じ状態、放気弁７１を開き状態として、低圧段圧縮機本体４６及び高圧段圧縮機本体４７が運転するようになっている。なお、吐出配管７４には逆止弁７６が設けられており、この逆止弁７８の上流側で分岐接続された放気配管７７が放気弁７１に接続されている。また、導出配管７３及び供給配管７５の下方側にはドレン配管７８，７９がそれぞれ接続され、これらドレン配管７８，７９を介し圧縮空気の冷却の際に生じたドレンを排出するようになっている。 An intake filter 68 and a suction throttle valve 69 for adjusting the amount of intake air are provided on the suction side (upper side in FIG. 3) of the low-pressure compressor main body 46. Further, an air release valve 71 that releases the compressed air of the high-pressure compressor main body 47 through the silencer 70 is provided in conjunction with the suction throttle valve 69. During load operation, compression air (outside air) is sucked into the low-pressure compressor main body 46 through the intake filter 68 and the suction throttle valve 69 and compressed to a predetermined pressure, and this compressed air passes through the discharge pipe 72. The compressed air discharged to the low pressure side heat exchanger 48 a side of the plate heat exchanger 48 and cooled on the low pressure side heat exchanger 48 a side of the plate type heat exchanger 48 is connected to the high pressure stage compressor main body 47 via the outlet pipe 73. The compressed air is discharged to the high pressure side heat exchanger 48b side of the plate heat exchanger 48 through the discharge pipe 74 and cooled by the high pressure side heat exchanger 48b of the plate heat exchanger 48. The compressed air is supplied to an external device or the like (not shown) via the supply pipe 75. Further, during no-load operation, the low-pressure stage compressor body 46 and the high-pressure stage compressor body 47 are operated with the suction throttle valve 69 closed and the vent valve 71 open. The discharge pipe 74 is provided with a check valve 76, and an air discharge pipe 77 branched and connected upstream of the check valve 78 is connected to the air discharge valve 71. Further, drain pipes 78 and 79 are connected to the lower side of the outlet pipe 73 and the supply pipe 75, respectively, and drains generated during cooling of the compressed air are discharged through the drain pipes 78 and 79. .

プレート式熱交換器４８は、低圧段圧縮機本体４６からの圧縮空気を冷却して高圧段圧縮機本体４８へ流出する上記低圧側熱交換器４８ａと、高圧段圧縮機本体４７からの圧縮空気を冷却する上記高圧側熱交換器４８ｂとが一体構成されている。詳細には、例えば図５に示すように、積層された複数（図５では８枚）のチャンネルプレート８０と、低圧側熱交換器４８ａ及び高圧側熱交換器４８ｂを仕切るために配設された仕切りプレート８１と、チャンネルプレート８０の両外側に配設されたカバープレート８２Ａ，８２Ｂとを備えており、これら複数のチャンネルプレート８０、仕切りプレート８１及びカバープレート８２Ａ，８２Ｂが例えば銅等によってブレージング（ろう付け）されている。チャンネルプレート８０は、例えばステンレス製薄板でヘリンボーン（Ｖ字）形状に加工されており、積層されたチャンネルプレート８０の間には、圧縮空気が流れる圧縮空気流路８３ａ又は８３ｂと、冷却水が流れる冷却流路８４ａ又は８４ｂとが交互に形成されている。これら圧縮空気流路８３ａ，８３ｂ及び冷却流路８４ａ，８４ｂは複雑な流路形状（詳細は省略）となり、流路内は乱流となって熱交換率（冷却効率）が高められる。   The plate heat exchanger 48 cools the compressed air from the low-pressure stage compressor body 46 and flows out to the high-pressure stage compressor body 48, and the compressed air from the high-pressure stage compressor body 47. The high pressure side heat exchanger 48b for cooling the air is integrally formed. Specifically, as shown in FIG. 5, for example, the plurality of stacked (8 in FIG. 5) channel plates 80 are arranged to partition the low-pressure side heat exchanger 48a and the high-pressure side heat exchanger 48b. A partition plate 81 and cover plates 82A and 82B disposed on both outer sides of the channel plate 80 are provided. The plurality of channel plates 80, the partition plate 81, and the cover plates 82A and 82B are brazed with, for example, copper ( Brazed). The channel plate 80 is made of, for example, a stainless steel thin plate and processed into a herringbone (V shape). Between the stacked channel plates 80, a compressed air flow path 83a or 83b through which compressed air flows and cooling water flow. The cooling flow paths 84a or 84b are alternately formed. The compressed air flow paths 83a and 83b and the cooling flow paths 84a and 84b have complicated flow path shapes (details are omitted), and turbulent flow is generated in the flow paths to increase the heat exchange rate (cooling efficiency).

低圧段側熱交換器４８ａを構成するカバープレート８２Ａの隅角には、上側に圧縮空気入口ポート８５ａ、下側に圧縮空気出口ポート８５ｂ及び冷却水入口ポート８５ｃが設けられ、高圧段側熱交換器４８ｂを構成するカバープレート８２Ｂの隅角には、上側に圧縮空気出口ポート８６ａ、下側に圧縮空気入口ポート８６ｂ及び冷却水出口ポート８６ｃが設けられている。また、ポート８５ａ〜８５ｃ，８６ａ〜８６ｃに対応するように複数のチャンネルプレート８０及び仕切りプレート８１に貫通孔８７が形成され、これら貫通孔８７が圧縮空気流路８３ａ又は８３ｂ、若しくは冷却流路８４ａ又は８４ｂにそれぞれ連通するようになっている。そして、冷却水入口ポート８６ｃから流入した冷却水が高圧側熱交換器４８ｂの冷却流路８４ｂを上向きに流れ、仕切りプレート８１の貫通孔８７を経て、低圧側熱交換器４８ａの冷却流路８４ａを下向きに流れて冷却水出口ポート８５ｃから流出するようになっている（言い換えれば、高圧側熱交換器４８ｂの冷却流路８４ｂと低圧側熱交換器４８ａの冷却流路８４ａは、直列接続されている）。また低圧側熱交換器４８ａでは、圧縮空気入口ポート８５ｂから流入した圧縮空気が圧縮空気流路８３ａを上向きに流れて圧縮空気出口ポート８５ａから流出し、高圧側熱交換器４８ｂでは、圧縮空気入口ポート８６ａから流入した圧縮空気が圧縮空気流路８３ｂを下向きに流れて圧縮空気出口ポート８６ｂから流出するようになっている。これにより、低圧側熱交換器４８ａ及び高圧側熱交換器４８ｂにおいて、チャンネルプレート８０を介し圧縮空気と冷却水が熱交換して圧縮空気が冷却されるようになっている。   At the corner of the cover plate 82A constituting the low pressure stage side heat exchanger 48a, a compressed air inlet port 85a is provided on the upper side, a compressed air outlet port 85b and a cooling water inlet port 85c are provided on the lower side, and the high pressure stage side heat exchange is provided. A compressed air outlet port 86a is provided on the upper side, and a compressed air inlet port 86b and a cooling water outlet port 86c are provided on the lower side at the corners of the cover plate 82B constituting the vessel 48b. Further, through holes 87 are formed in the plurality of channel plates 80 and the partition plate 81 so as to correspond to the ports 85a to 85c and 86a to 86c, and these through holes 87 serve as the compressed air flow paths 83a or 83b or the cooling flow paths 84a. Or 84b. And the cooling water which flowed in from the cooling water inlet port 86c flows upward through the cooling flow path 84b of the high pressure side heat exchanger 48b, passes through the through hole 87 of the partition plate 81, and the cooling flow path 84a of the low pressure side heat exchanger 48a. (In other words, the cooling flow path 84b of the high-pressure side heat exchanger 48b and the cooling flow path 84a of the low-pressure side heat exchanger 48a are connected in series. ing). In the low pressure side heat exchanger 48a, the compressed air flowing in from the compressed air inlet port 85b flows upward through the compressed air passage 83a and flows out from the compressed air outlet port 85a. In the high pressure side heat exchanger 48b, the compressed air inlet The compressed air flowing in from the port 86a flows downward in the compressed air flow path 83b and flows out from the compressed air outlet port 86b. Thereby, in the low pressure side heat exchanger 48a and the high pressure side heat exchanger 48b, the compressed air and the cooling water exchange heat through the channel plate 80 to cool the compressed air.

なお、上述の内容からわかるように、低圧側熱交換器４８ａにおける圧縮空気流路８３ａと冷却流路８４ａ、高圧側熱交換器４８ｂにおける圧縮空気流路８３ｂと冷却流路８４ｂはともに対向流となっている。そのためには、圧縮空気流路８３ａ，８３ｂのいずれか一方を上向きの流れとする必要があるが、本実施形態では、圧縮空気中にドレンが比較的発生しにくい（又は無負荷運転・停止時にドレンの逆流が生じない）低圧側熱交換器４８ａの圧縮空気流路８３ａを上向きとしている。   As can be seen from the above description, the compressed air flow path 83a and the cooling flow path 84a in the low-pressure side heat exchanger 48a and the compressed air flow path 83b and the cooling flow path 84b in the high-pressure side heat exchanger 48b are both opposed flow. It has become. For this purpose, either one of the compressed air flow paths 83a and 83b needs to be an upward flow, but in this embodiment, drain is relatively difficult to generate in the compressed air (or during no-load operation / stop). The compressed air passage 83a of the low pressure side heat exchanger 48a is directed upward.

また、上記した潤滑油用熱交換器６６、プレート式熱交換器４８、低圧段圧縮機本体４６の冷却ジャケット、及び高圧段圧縮機本体の４７の冷却ジャケットに冷却水を流通する冷却水配管８８が設けられている。この冷却水配管８８は、まず潤滑油用熱交換器６６に冷却水を流通する配管系統８８ａとプレート式熱交換器４８に冷却水を流通する配管系統８８ｂとで分岐され、その後配管系統８８ａ，８８ｂが合流してから、低圧段圧縮機本体４６の冷却ジャケットに冷却水を流通する配管系統８８ｃと高圧段圧縮機本体４７の冷却ジャケットに冷却水を流通する配管系統８８ｄとで分岐され、その後配管系統８８ｃ，８８ｄが合流するように構成されている。また、冷却風を誘起する冷却ファン８９が設けられており、この冷却ファン８９の駆動により圧縮機全体を冷却するようになっている。   Further, the above-described lubricating oil heat exchanger 66, plate heat exchanger 48, cooling jacket of the low-pressure stage compressor body 46, and cooling water pipe 88 for circulating cooling water to the 47 cooling jacket of the high-pressure stage compressor body. Is provided. The cooling water pipe 88 is first branched into a piping system 88a for circulating cooling water to the lubricating oil heat exchanger 66 and a piping system 88b for circulating cooling water to the plate heat exchanger 48, and then the piping systems 88a, 88a, After the 88b merges, it is branched by a piping system 88c that distributes cooling water to the cooling jacket of the low-pressure stage compressor body 46 and a piping system 88d that distributes cooling water to the cooling jacket of the high-pressure stage compressor body 47. The piping systems 88c and 88d are configured to merge. In addition, a cooling fan 89 for inducing cooling air is provided, and the entire compressor is cooled by driving the cooling fan 89.

次に、本実施形態の動作及び作用効果を説明する。
例えば外部の機器等に供給する圧縮空気を生成する場合、電動機４４が駆動し、電動機４４の回転力が低圧段圧縮機本体４６の雄ロータ４９に伝達されると、雄ロータ４９及び雌ロータ５０が非接触かつ無給油で回転駆動する。これと同時に、電動機４４の回転力が高圧段圧縮機本体４７の雄ロータ５３に伝達されて、雄ロータ５３及び雌ロータ５４が非接触かつ無給油で回転駆動する。これにより、負荷運転時は、吸込みフィルタ６８及び吸込み絞り弁６９を介し低圧段圧縮機本体４６に圧縮用空気を吸い込んで所定の圧力まで圧縮する。このとき、低圧段圧縮機本体４６で生成した圧縮空気の温度は例えば約１６０〜２５０℃であり、また負荷運転及び無負荷運転が繰り返されると熱による繰り返し応力が発生するものの、これら圧縮空気の温度及び熱による繰り返し応力を考慮しても、プレート式熱交換器４８の耐熱温度の許容範囲となる場合がある。このような場合に、低圧段圧縮機本体４６からの圧縮空気をプレート式熱交換器４８の低圧側熱交換器４８ａで冷却し、高圧段圧縮機本体４７でさらに圧縮する。このとき、高圧段圧縮機本体４７で生成した圧縮空気の温度も例えば約１６０〜２５０℃であり、圧縮空気の温度及び熱による繰り返し応力を考慮しても、プレート式熱交換器４８の耐熱温度の許容範囲となる場合がある。このような場合に、高圧段圧縮機本体４７からの圧縮空気をプレート式熱交換器４８の高圧側熱交換器４８ｂで冷却し、供給配管７５を介し外部の機器等に供給する。 Next, the operation and effect of this embodiment will be described.
For example, when generating compressed air to be supplied to an external device or the like, when the electric motor 44 is driven and the rotational force of the electric motor 44 is transmitted to the male rotor 49 of the low-pressure stage compressor body 46, the male rotor 49 and the female rotor 50. Rotates without contact and without lubrication. At the same time, the rotational force of the electric motor 44 is transmitted to the male rotor 53 of the high-pressure compressor main body 47, and the male rotor 53 and the female rotor 54 are rotationally driven without contact and without lubrication. Thus, during the load operation, the compression air is sucked into the low-pressure stage compressor body 46 through the suction filter 68 and the suction throttle valve 69 and compressed to a predetermined pressure. At this time, the temperature of the compressed air generated in the low-pressure stage compressor body 46 is, for example, about 160 to 250 ° C., and repeated stress due to heat is generated when the load operation and the no-load operation are repeated. Even if the repeated stress due to temperature and heat is taken into account, the allowable temperature limit of the plate heat exchanger 48 may be acceptable. In such a case, the compressed air from the low pressure stage compressor body 46 is cooled by the low pressure side heat exchanger 48 a of the plate heat exchanger 48 and further compressed by the high pressure stage compressor body 47. At this time, the temperature of the compressed air generated in the high-pressure compressor main body 47 is also about 160 to 250 ° C., for example, and the heat resistance temperature of the plate heat exchanger 48 is considered even if the temperature of the compressed air and the repeated stress due to heat are taken into consideration. May be acceptable. In such a case, the compressed air from the high-pressure stage compressor main body 47 is cooled by the high-pressure side heat exchanger 48b of the plate heat exchanger 48 and supplied to an external device or the like via the supply pipe 75.

本実施形態においては、低圧段圧縮機本体４６の圧縮空気を冷却する低圧側熱交換器４８ａ、及び高圧段圧縮機本体４７の圧縮空気を冷却する高圧側熱交換器４８ｂを一体構成したプレート式熱交換器４８を設ける。これにより、従来のようにチューブ式熱交換器を低圧側熱交換器及び高圧熱交換器としてそれぞれ設ける場合に比べ、大幅な小型化を図ることができる。   In the present embodiment, a plate type in which a low-pressure side heat exchanger 48 a that cools the compressed air of the low-pressure stage compressor body 46 and a high-pressure side heat exchanger 48 b that cools the compressed air of the high-pressure stage compressor body 47 are integrally configured. A heat exchanger 48 is provided. Thereby, compared with the case where a tube type heat exchanger is each provided as a low voltage | pressure side heat exchanger and a high voltage | pressure heat exchanger like the past, significant miniaturization can be achieved.

また、プレート式熱交換器４８は、低圧側熱交換器４８ａの冷却流路８４ａと高圧側熱交換器４８ｂの冷却流路８４ｂを直列接続する。これにより、冷却流路８４ａ，８４ｂを並列接続する場合よりも、冷却水流量を低減しかつ冷却水流速を速くし、ゴミやスケールの付着を防止できる。また、プレート式熱交換器４８は、低圧側熱交換器４８ａ及び高圧側熱交換器４８ｂを一体構成とするので、冷却流路４８ａ，４８ｂを接続する配管を削減することができる。また、低圧側熱交換器４８ａにおける圧縮空気流路８３ａと冷却流路８４ａ、高圧側熱交換器４８ｂにおける圧縮空気流路８３ｂと冷却流路８４ｂをともに対向流とするため、プレート式熱交換器４８の冷却性能が向上し小型化が図れる。   The plate heat exchanger 48 connects the cooling flow path 84a of the low-pressure side heat exchanger 48a and the cooling flow path 84b of the high-pressure side heat exchanger 48b in series. Thereby, compared with the case where the cooling flow paths 84a and 84b are connected in parallel, the flow rate of the cooling water can be reduced and the flow rate of the cooling water can be increased, thereby preventing the attachment of dust and scale. Moreover, since the plate-type heat exchanger 48 is configured integrally with the low-pressure side heat exchanger 48a and the high-pressure side heat exchanger 48b, piping connecting the cooling channels 48a and 48b can be reduced. In addition, since both the compressed air flow path 83a and the cooling flow path 84a in the low pressure side heat exchanger 48a and the compressed air flow path 83b and the cooling flow path 84b in the high pressure side heat exchanger 48b are opposed to each other, the plate heat exchanger The cooling performance of 48 can be improved and the size can be reduced.

本発明の第２の実施形態を図４により説明する。本実施形態は、二段無給油式スクリュー空気圧縮機においてチューブ式熱交換器及びプレート式熱交換器を設けた実施形態である。 The second embodiment of the present invention will be described with reference to FIG. This embodiment is an embodiment in which a tube heat exchanger and a plate heat exchanger are provided in a two-stage oilless screw air compressor.

図４は、本実施形態による無給油スクリュー空気圧縮機の全体構造を表す模式図である。この図４において、上記第１の実施形態と同等の部分には同一の符号を付し、適宜説明を省略する。 FIG. 4 is a schematic diagram showing the entire structure of the oil-free screw air compressor according to the present embodiment. In FIG. 4, the same reference numerals are assigned to the first embodiment and like parts of the explanation is suitably omitted.

例えば上記高圧段圧縮機本体４７で生成した圧縮空気の温度が上記プレート式熱交換器４８の耐熱温度を超えるような場合（詳細には、高圧段圧縮機本体４７の圧縮率が高い場合）があるため、本実施形態では、吐出配管７４における放気配管７７の分岐部より上流側に配設されたチューブ式熱交換器９０を備えている。このチューブ式熱交換器９０で高圧段圧縮機本体４７からの圧縮空気を一次冷却し、上記プレート式熱交換器４８の高圧側熱交換器４８ａに導入されて二次冷却されるようになっている。   For example, there is a case where the temperature of the compressed air generated by the high pressure stage compressor body 47 exceeds the heat resistance temperature of the plate heat exchanger 48 (specifically, when the compression rate of the high pressure stage compressor body 47 is high). Therefore, in this embodiment, the tube-type heat exchanger 90 provided in the upstream of the branch part of the discharge pipe 74 in the discharge pipe 74 is provided. The tube-type heat exchanger 90 primarily cools the compressed air from the high-pressure stage compressor main body 47, and is introduced into the high-pressure side heat exchanger 48a of the plate-type heat exchanger 48 to be secondary-cooled. Yes.

チューブ式熱交換器９０は、シェル９１内に例えば耐熱・耐蝕性が優れた複数のステンレス製Ｕ字管９２を複数（図６では便宜上２つのみ図示）設けており、それらＵ字管９２は熱による伸縮を吸収するため耐熱温度が比較的高い構造となっている。そして、Ｕ字管９２内に高圧段圧縮機本体４７からの圧縮空気が流れシェル９１内に冷却水が流れて、圧縮空気と冷却水が熱交換することにより圧縮空気が一次冷却されるようになっている。   The tube heat exchanger 90 is provided with a plurality of stainless steel U-shaped tubes 92 (for example, only two are shown in FIG. 6 for convenience) provided in the shell 91, for example, having excellent heat resistance and corrosion resistance. In order to absorb expansion and contraction due to heat, the heat resistant temperature is relatively high. Then, the compressed air from the high-pressure stage compressor body 47 flows in the U-shaped pipe 92 and the cooling water flows in the shell 91, and the compressed air is primarily cooled by heat exchange between the compressed air and the cooling water. It has become.

また、上記潤滑油用熱交換器６６、プレート式熱交換器４８、チューブ式熱交換器９０、低圧段圧縮機本体４６の冷却ジャケット、及び高圧段圧縮機本体の４７の冷却ジャケットに冷却水を流通する冷却水配管９３が設けられている。この冷却水配管９３は、まず潤滑油用熱交換器６６に冷却水を流通する配管系統９３ａと、プレート式熱交換器４８及びチューブ式熱交換器９０の順序で冷却水を流通する配管系統９３ｂとで分岐され、低圧段圧縮機本体４６の冷却ジャケットに流通する配管系統９３ｃが前記配管系統９３ｂにおけるチューブ式熱交換器９０の下流側に分岐接続され、配管系統９３ａ，９３ｂが合流して高圧段圧縮機本体４７の冷却ジャケットに冷却水を流通する配管系統９３ｄが接続され、その後配管系統９３ｃ，９３ｄが合流するように構成されている。   Further, cooling water is supplied to the lubricating oil heat exchanger 66, the plate heat exchanger 48, the tube heat exchanger 90, the cooling jacket of the low pressure stage compressor main body 46, and the cooling jacket of the high pressure stage compressor main body 47. A circulating cooling water pipe 93 is provided. The cooling water pipe 93 includes a piping system 93a that distributes the cooling water to the lubricant heat exchanger 66, and a piping system 93b that distributes the cooling water in the order of the plate heat exchanger 48 and the tube heat exchanger 90. Are connected to the downstream side of the tube-type heat exchanger 90 in the piping system 93b, and the piping systems 93a and 93b merge to generate a high pressure. A piping system 93d for circulating cooling water is connected to the cooling jacket of the stage compressor main body 47, and then the piping systems 93c, 93d are joined.

以上のように構成された本実施形態においては、耐熱温度が比較的高いチューブ式熱交換器９０で高圧段圧縮機本体４７からの圧縮空気を一次冷却し、圧縮空気の温度をプレート式熱交換器４８の耐熱温度まで下げてから、プレート式熱交換器４８に導入し二次冷却する。このようにチューブ式熱交換器９０及びプレート式熱交換器４８を併用することにより、従来のチューブ式熱交換器のみを設ける場合に比べ、耐熱性を確保しつつ大幅な小型化を図ることができる。   In the present embodiment configured as described above, the compressed air from the high-pressure compressor main body 47 is primarily cooled by the tube heat exchanger 90 having a relatively high heat resistance temperature, and the temperature of the compressed air is changed to the plate heat exchange. The temperature is lowered to the heat resistant temperature of the vessel 48 and then introduced into the plate heat exchanger 48 for secondary cooling. In this way, by using the tube heat exchanger 90 and the plate heat exchanger 48 in combination, it is possible to significantly reduce the size while ensuring heat resistance as compared with the case where only the conventional tube heat exchanger is provided. it can.

なお、上記第２の実施形態においては、高圧段圧縮機本体４７からの圧縮空気をチューブ式熱交換器９０で一次冷却し、プレート式熱交換器４８の高圧側熱交換器４８ｂで二次冷却する構成を例にとって説明したが、これに限られず、例えば低圧段圧縮機本体４６からの圧縮空気をチューブ式熱交換器で一次冷却し、プレート式熱交換器４８の低圧側熱交換器４８ａで二次冷却する構成としてもよいし、また例えば低圧段圧縮機本体４６及び高圧段圧縮機本体４７からの圧縮空気を各チューブ式熱交換器で一次冷却し、プレート式熱交換器４８で二次冷却する構成としてもよい。これらの場合も、上記同様の効果を得ることができる。 In the second embodiment, the compressed air from the high pressure stage compressor main body 47 is primarily cooled by the tube heat exchanger 90 and is secondarily cooled by the high pressure side heat exchanger 48 b of the plate heat exchanger 48. However, the present invention is not limited to this. For example, the compressed air from the low-pressure stage compressor main body 46 is primarily cooled by a tube heat exchanger, and the plate-type heat exchanger 48 has a low-pressure side heat exchanger 48a. It is good also as a structure which carries out secondary cooling, for example, compressed air from the low pressure stage compressor main body 46 and the high pressure stage compressor main body 47 is primarily cooled by each tube type heat exchanger, and is secondary by the plate type heat exchanger 48. It is good also as a structure to cool. In these cases, the same effect as described above can be obtained.

また、上記第１及び第２の実施形態においては、プレート式熱交換器４８は、低圧側熱交換器４８ａにおける圧縮空気流路８３ａと冷却流路８４ａ、高圧側熱交換器４８ｂにおける圧縮空気流路８３ｂと冷却流路８４ｂをともに対向流とする場合を例にとって説明したが、これに限られない。すなわち、例えば低圧側熱交換器４８ａにおける圧縮空気流路８３ａと冷却流路８４ａ、高圧側熱交換器４８ｂにおける圧縮空気流路８３ｂと冷却流路８４ｂのうちいずれか一方又は両方を平行流としてもよい。このような変形例を図５により説明する。 Further, in the first and second embodiments, the plate heat exchanger 48 has the compressed air flow path 83a and the cooling flow path 84a in the low pressure side heat exchanger 48a, and the compressed air flow in the high pressure side heat exchanger 48b. Although the case where the channel 83b and the cooling channel 84b are both opposed flows has been described as an example, the present invention is not limited to this. That is, for example, one or both of the compressed air flow path 83a and the cooling flow path 84a in the low pressure side heat exchanger 48a and the compressed air flow path 83b and the cooling flow path 84b in the high pressure side heat exchanger 48b may be parallel flows. Good. Such modification will be described with reference to FIG.

図５は、本変形例によるプレート式熱交換器の概略構造を表す模式図である。この図５において、上記実施形態と同等の部分には同一の符号を付し、適宜説明を省略する。 FIG. 5 is a schematic diagram showing a schematic structure of a plate heat exchanger according to this modification. In FIG. 5 , parts that are the same as in the above embodiment are given the same reference numerals, and descriptions thereof are omitted as appropriate.

本変形例によるプレート式熱交換器４８’では、上記実施形態同様、冷却水入口ポートから流入した冷却水が高圧側熱交換器４８ｂの冷却流路８４ｂを上向きに流れ、その後、低圧側熱交換器４８ａの冷却流路８４ａを下向きに流れて冷却水出口ポートから流出するようになっている（言い換えれば、高圧側熱交換器４８ｂの冷却流路８４ｂと低圧側熱交換器４８ａの冷却流路８４ａは、直列接続されている）。また低圧側熱交換器４８ａ’では、圧縮空気入口ポートから流入した圧縮空気が圧縮空気流路８３ａ’を下向きに流れて圧縮空気出口ポートから流出し、高圧側熱交換器４８ｂでは、圧縮空気入口ポートから流入した圧縮空気が圧縮空気流路８３ｂを下向きに流れて圧縮空気出口ポートから流出するようになっている。すなわち、圧縮空気流路８３ａ’，８３ｂの圧縮空気の流れをともに下向きとするため、低圧側熱交換器４８ａ’における圧縮空気流路８３ａと冷却流路８４ａは平行流となり、高圧側熱交換器４８ｂにおける圧縮空気流路８３ｂと冷却流路８４ｂは対向流となっている。   In the plate heat exchanger 48 ′ according to the present modification, the cooling water flowing in from the cooling water inlet port flows upward through the cooling flow path 84b of the high-pressure side heat exchanger 48b, and then the low-pressure side heat exchange, as in the above embodiment. The cooling flow path 84a of the cooler 48a flows downward and flows out of the cooling water outlet port (in other words, the cooling flow path 84b of the high pressure side heat exchanger 48b and the cooling flow path of the low pressure side heat exchanger 48a). 84a is connected in series). In the low pressure side heat exchanger 48a ′, the compressed air flowing in from the compressed air inlet port flows downward in the compressed air flow path 83a ′ and flows out from the compressed air outlet port. In the high pressure side heat exchanger 48b, the compressed air inlet port The compressed air flowing in from the port flows downward in the compressed air flow path 83b and flows out from the compressed air outlet port. That is, since the compressed air flows in the compressed air flow paths 83a ′ and 83b are both directed downward, the compressed air flow path 83a and the cooling flow path 84a in the low pressure side heat exchanger 48a ′ become parallel flows, and the high pressure side heat exchanger The compressed air flow path 83b and the cooling flow path 84b in 48b are counterflows.

このような変形例においては、圧縮空気流路８３ａ’，８３ｂの圧縮空気がともに下方向に流れるため、圧縮空気中に発生したドレンが滞留するのを防止することができる。また、低圧側熱交換器４８ａ’における圧縮空気流路８３ａと冷却流路８４ａを平行流とすることにより、冷却能力は低下するものの、ドレンの発生を抑えて高圧段圧縮機本体４７に発錆が生じるのを防止することができる。また、低圧側熱交換器４８’が若干大きく（言い換えれば、低圧側熱交換器４８ａを構成するチャンネルプレート８０が若干多く）なったとしても、低圧側の圧縮空気のほうがその体積が大きく、圧力損失の影響を低減できるので好ましい。   In such a modification, since the compressed air in the compressed air flow paths 83a 'and 83b flows downward, it is possible to prevent the drain generated in the compressed air from staying. Further, by making the compressed air flow path 83a and the cooling flow path 84a in the low-pressure side heat exchanger 48a 'parallel flow, the cooling capacity is reduced, but the generation of drain is suppressed, and the high pressure stage compressor main body 47 is rusted. Can be prevented from occurring. Even if the low-pressure side heat exchanger 48 'is slightly larger (in other words, the channel plate 80 constituting the low-pressure side heat exchanger 48a is slightly larger), the compressed air on the low-pressure side has a larger volume, This is preferable because the influence of loss can be reduced.

本発明の無給油式スクリュー空気圧縮機の第１の実施形態の全体構造を表す模式図である。It is a mimetic diagram showing the whole structure of a 1st embodiment of an oil-free screw air compressor of the present invention. 本発明の無給油式スクリュー空気圧縮機の第１の実施形態を構成するプレート式熱交換器の概略構造を表す模式図である。It is a schematic diagram showing the schematic structure of the plate type heat exchanger which comprises 1st Embodiment of the oil-free screw air compressor of this invention. 本発明の無給油式スクリュー空気圧縮機の第１の実施形態を構成するプレート式熱交換器の構造を一例として表す斜視分解図である。It is a perspective exploded view showing the structure of the plate type heat exchanger which constitutes the 1st embodiment of the oil-free screw air compressor of the present invention as an example. 本発明の無給油式スクリュー空気圧縮機の第２の実施形態の全体構造を表す模式図である。It is a schematic diagram showing the whole structure of 2nd Embodiment of the oil-free screw air compressor of this invention. 本発明の無給油式スクリュー空気圧縮機の一変形例を構成するプレート式熱交換器の概略構造を表す模式図である。It is a schematic diagram showing the schematic structure of the plate-type heat exchanger which comprises the modification of the oilless type screw air compressor of this invention.

符号の説明Explanation of symbols

４６ 低圧段圧縮機本体
４７ 高圧段圧縮機本体
４８ プレート式熱交換器
４８ａ 低圧側熱交換器
４８ｂ 高圧側熱交換器
８３ａ 圧縮空気流路（第１の圧縮空気流路）
８３ｂ 圧縮空気流路（第２の圧縮空気流路）
８４ａ 第１の冷却流路（第１の冷却流路）
８４ｂ 第２の冷却流路（第２の冷却流路）
９０ チューブ式熱交換器 4 6 Low pressure stage compressor body 47 High pressure stage compressor body 48 Plate type heat exchanger 48a Low pressure side heat exchanger 48b High pressure side heat exchanger 83a Compressed air flow path (first compressed air flow path)
83b Compressed air flow path (second compressed air flow path)
84a First cooling flow path (first cooling flow path)
84b Second cooling flow path (second cooling flow path)
90 Tube heat exchanger

Claims (5)

無給油状態で空気を圧縮する低圧段圧縮機本体と、
前記低圧段圧縮機本体で圧縮された空気をさらに無給油状態で圧縮する高圧段圧縮機本体と、
前記低圧段圧縮機本体の圧縮空気を冷却して前記高圧段圧縮機本体へ流出する低圧側熱交換器、及び前記高圧段圧縮機本体の圧縮空気を冷却する高圧側熱交換器を一体構成したプレート式熱交換器とを備えた無給油式スクリュー空気圧縮機であって、
前記プレート式熱交換器は、
前記高圧段圧縮機本体の圧縮空気が下方向に流れる第１の圧縮空気流路と、
前記低圧段圧縮機本体の圧縮空気が上方向に流れる第２の圧縮空気流路と、
前記高圧段圧縮機本体の圧縮空気を冷却する冷却液が上方向に流れる第１の冷却流路と、
前記第１の冷却流路に直列接続され、前記低圧段圧縮機本体の圧縮空気を冷却する冷却液が下方向に流れる第２の冷却流路とを備えたことを特徴とする無給油式スクリュー空気圧縮機。 A low-pressure compressor body that compresses air in an oil-free state;
A high-pressure stage compressor body that further compresses the air compressed by the low-pressure stage compressor body in an oil-free state;
A low pressure side heat exchanger that cools the compressed air of the low pressure stage compressor body and flows out to the high pressure stage compressor body, and a high pressure side heat exchanger that cools the compressed air of the high pressure stage compressor body are integrally configured. An oil-free screw air compressor equipped with a plate heat exchanger,
The plate heat exchanger is
A first compressed air flow path through which the compressed air of the high-pressure stage compressor body flows downward;
A second compressed air flow path through which the compressed air of the low-pressure stage compressor body flows upward;
A first cooling flow path in which a coolant for cooling the compressed air of the high-pressure stage compressor body flows upward;
An oil-free screw comprising: a second cooling flow path that is connected in series to the first cooling flow path and in which a cooling liquid that cools the compressed air of the low-pressure stage compressor body flows downward. air compressor. 無給油状態で空気を圧縮する低圧段圧縮機本体と、
前記低圧段圧縮機本体で圧縮された空気をさらに無給油状態で圧縮する高圧段圧縮機本体と、
前記低圧段圧縮機本体の圧縮空気を冷却して前記高圧段圧縮機本体へ流出する低圧側熱交換器、及び前記高圧段圧縮機本体の圧縮空気を冷却する高圧側熱交換器を一体構成したプレート式熱交換器とを備えた無給油式スクリュー空気圧縮機であって、
前記プレート式熱交換器は、
前記高圧段圧縮機本体の圧縮空気が下方向に流れる第１の圧縮空気流路と、
前記低圧段圧縮機本体の圧縮空気が下方向に流れる第２の圧縮空気流路と、
前記高圧段圧縮機本体の圧縮空気を冷却する冷却液が上方向に流れる第１の冷却流路と、
前記第１の冷却流路に直列接続され、前記低圧段圧縮機本体の圧縮空気を冷却する冷却液が下方向に流れる第２の冷却流路とを備えたことを特徴とする無給油式スクリュー空気圧縮機。 A low-pressure compressor body that compresses air in an oil-free state;
A high-pressure stage compressor body that further compresses the air compressed by the low-pressure stage compressor body in an oil-free state;
A low pressure side heat exchanger that cools the compressed air of the low pressure stage compressor body and flows out to the high pressure stage compressor body, and a high pressure side heat exchanger that cools the compressed air of the high pressure stage compressor body are integrally configured. An oil-free screw air compressor equipped with a plate heat exchanger,
The plate heat exchanger is
A first compressed air flow path through which the compressed air of the high-pressure stage compressor body flows downward;
A second compressed air passage through which the compressed air of the low-pressure stage compressor body flows downward;
A first cooling flow path in which a coolant for cooling the compressed air of the high-pressure stage compressor body flows upward;
An oil-free screw comprising: a second cooling flow path that is connected in series to the first cooling flow path and in which a cooling liquid that cools the compressed air of the low-pressure stage compressor body flows downward. air compressor. 請求項１又は２記載の無給油式スクリュー空気圧縮機において、前記低圧段圧縮機本体からの圧縮空気及び前記高圧段圧縮機本体からの圧縮空気のうちいずれか一方又は両方を一次冷却して前記プレート式熱交換器へ流出するチューブ式熱交換器を備えたことを特徴とする無給油式スクリュー空気圧縮機。 The oilless screw air compressor according to claim 1 or 2 , wherein either one or both of compressed air from the low-pressure stage compressor body and compressed air from the high-pressure stage compressor body is primarily cooled, and An oil-free screw air compressor comprising a tube heat exchanger that flows out to a plate heat exchanger. 無給油状態で空気を圧縮する低圧段圧縮機本体と、A low-pressure compressor body that compresses air in an oil-free state;
前記低圧段圧縮機本体で圧縮された空気をさらに無給油状態で圧縮する高圧段圧縮機本体と、A high-pressure stage compressor body that further compresses the air compressed by the low-pressure stage compressor body in an oil-free state;
前記低圧段圧縮機本体の圧縮空気を冷却して前記高圧段圧縮機本体へ流出する低圧側熱交換器、及び前記高圧段圧縮機本体の圧縮空気を冷却する高圧側熱交換器を一体構成したプレート式熱交換器とを備えた無給油式スクリュー空気圧縮機であって、  A low pressure side heat exchanger that cools the compressed air of the low pressure stage compressor body and flows out to the high pressure stage compressor body, and a high pressure side heat exchanger that cools the compressed air of the high pressure stage compressor body are integrally configured. An oil-free screw air compressor equipped with a plate heat exchanger,
前記プレート式熱交換器は、The plate heat exchanger is
前記高圧段圧縮機本体の圧縮空気が流れる第１の圧縮空気流路と、A first compressed air passage through which the compressed air of the high-pressure stage compressor body flows;
前記低圧段圧縮機本体の圧縮空気が流れる第２の圧縮空気流路と、A second compressed air flow path through which the compressed air of the low-pressure stage compressor body flows;
前記高圧段圧縮機本体の圧縮空気を冷却する冷却液が流れる第１の冷却流路と、A first cooling flow path through which a cooling liquid for cooling the compressed air of the high-pressure stage compressor body flows;
前記第１の冷却流路に直列接続され、前記低圧段圧縮機本体の圧縮空気を冷却する冷却液が流れる第２の冷却流路とを備え、A second cooling channel that is connected in series to the first cooling channel and through which a coolant that cools the compressed air of the low-pressure stage compressor body flows,
前記第１の圧縮空気流路の流れ方向と前記第１の冷却流路の流れ方向とが対向流となるように、かつ前記第２の圧縮空気流路の流れ方向と前記第２の冷却流路の流れ方向とが対向流となるように構成しており、The flow direction of the first compressed air flow path and the flow direction of the first cooling flow path are opposite to each other, and the flow direction of the second compressed air flow path and the second cooling flow are It is configured so that the flow direction of the road is counterflow,
前記低圧段圧縮機本体からの圧縮空気及び前記高圧段圧縮機本体からの圧縮空気のうちいずれか一方又は両方を前記プレート式熱交換器の耐熱温度まで一次冷却して前記プレート式熱交換器へ流出するチューブ式熱交換器を備えたことを特徴とする無給油式スクリュー空気圧縮機。Either or both of the compressed air from the low-pressure stage compressor body and the compressed air from the high-pressure stage compressor body are primarily cooled to the heat resistant temperature of the plate heat exchanger to the plate heat exchanger. An oil-free screw air compressor comprising a tube-type heat exchanger that flows out. 無給油状態で空気を圧縮する低圧段圧縮機本体と、A low-pressure compressor body that compresses air in an oil-free state;
前記低圧段圧縮機本体で圧縮された空気をさらに無給油状態で圧縮する高圧段圧縮機本体と、A high-pressure stage compressor body that further compresses the air compressed by the low-pressure stage compressor body in an oil-free state;
前記低圧段圧縮機本体の圧縮空気を冷却して前記高圧段圧縮機本体へ流出する低圧側熱交換器、及び前記高圧段圧縮機本体の圧縮空気を冷却する高圧側熱交換器を一体構成したプレート式熱交換器とを備えた無給油式スクリュー空気圧縮機であって、A low pressure side heat exchanger that cools the compressed air of the low pressure stage compressor body and flows out to the high pressure stage compressor body, and a high pressure side heat exchanger that cools the compressed air of the high pressure stage compressor body are integrally configured. An oil-free screw air compressor equipped with a plate heat exchanger,
前記プレート式熱交換器は、The plate heat exchanger is
前記高圧段圧縮機本体の圧縮空気が流れる第１の圧縮空気流路と、A first compressed air passage through which the compressed air of the high-pressure stage compressor body flows;
前記低圧段圧縮機本体の圧縮空気が流れる第２の圧縮空気流路と、A second compressed air flow path through which the compressed air of the low-pressure stage compressor body flows;
前記高圧段圧縮機本体の圧縮空気を冷却する冷却液が流れる第１の冷却流路と、A first cooling flow path through which a cooling liquid for cooling the compressed air of the high-pressure stage compressor body flows;
前記第１の冷却流路に直列接続され、前記低圧段圧縮機本体の圧縮空気を冷却する冷却液が流れる第２の冷却流路とを備え、A second cooling channel that is connected in series to the first cooling channel and through which a coolant that cools the compressed air of the low-pressure stage compressor body flows,
前記第２の圧縮空気流路の流れ方向と前記第２の冷却流路の流れ方向とが平行流となるように構成しており、The flow direction of the second compressed air flow path and the flow direction of the second cooling flow path are configured to be parallel flows,
前記低圧段圧縮機本体からの圧縮空気及び前記高圧段圧縮機本体からの圧縮空気のうちいずれか一方又は両方を前記プレート式熱交換器の耐熱温度まで一次冷却して前記プレート式熱交換器へ流出するチューブ式熱交換器を備えたことを特徴とする無給油式スクリュー空気圧縮機。Either or both of the compressed air from the low-pressure stage compressor body and the compressed air from the high-pressure stage compressor body are primarily cooled to the heat resistant temperature of the plate heat exchanger to the plate heat exchanger. An oil-free screw air compressor comprising a tube-type heat exchanger that flows out.
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JP4991408B2 (en) 2007-06-19 2012-08-01 株式会社日立産機システム Water-cooled air compressor
JP4885077B2 (en) 2007-07-03 2012-02-29 株式会社日立産機システム Oil-free screw compressor
JP4717048B2 (en) * 2007-10-26 2011-07-06 株式会社神戸製鋼所 Screw compressor
JP5706681B2 (en) * 2010-12-24 2015-04-22 株式会社日立産機システム Multistage compressor
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