JP2000120596A - Water spray for turbocompressor - Google Patents
Water spray for turbocompressorInfo
- Publication number
- JP2000120596A JP2000120596A JP10289424A JP28942498A JP2000120596A JP 2000120596 A JP2000120596 A JP 2000120596A JP 10289424 A JP10289424 A JP 10289424A JP 28942498 A JP28942498 A JP 28942498A JP 2000120596 A JP2000120596 A JP 2000120596A
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- JP
- Japan
- Prior art keywords
- water
- compressed air
- spray
- water spray
- spray nozzle
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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- Structures Of Non-Positive Displacement Pumps (AREA)
- Nozzles (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、ターボ圧縮機用の
水噴霧装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a water spray device for a turbo compressor.
【０００２】[0002]
【従来の技術】従来より、ターボ圧縮機の吸込側に水を
噴霧し、その気化熱によって断熱圧縮される空気を冷却
して等温圧縮に近付け、圧縮仕事を小さくするようにし
たターボ圧縮機用の水噴霧装置が知られている。2. Description of the Related Art Conventionally, water is sprayed on the suction side of a turbocompressor, and the air adiabatically compressed by the heat of vaporization is cooled to approach isothermal compression, thereby reducing the compression work. Is known.
【０００３】[0003]
【発明が解決しようとする課題】しかし、従来の水噴霧
装置は、水のみを噴霧していたので、噴霧の粒径を十分
小さくできず、蒸発が不十分となる傾向があった。噴霧
の蒸発（気化）が不十分であると、圧縮される空気を冷
却できないばかりでなく、その水滴がインペラに当って
抵抗になるため却って圧縮仕事が大きくなってしまう。However, since the conventional water spraying device sprays only water, the particle size of the spray cannot be made sufficiently small and the evaporation tends to be insufficient. If the evaporation (evaporation) of the spray is insufficient, not only the compressed air cannot be cooled, but also the water droplets impinge on the impeller and become more resistant to compression work.
【０００４】以上の事情を考慮して創案された本発明の
目的は、噴霧の粒径を小さくしてその蒸発の促進を図っ
たターボ圧縮機用の水噴霧装置を提供することにある。[0004] An object of the present invention, which has been made in view of the above circumstances, is to provide a water spray device for a turbo compressor in which the particle size of the spray is reduced to promote the evaporation thereof.
【０００５】[0005]
【課題を解決するための手段】上記目的を達成すべく本
発明に係るターボ圧縮機用の水噴霧装置は、ターボ圧縮
機の吸込管内に、圧気と水とを混合して微細水滴として
噴霧する水噴霧ノズルを設けたものである。In order to achieve the above object, a water spray device for a turbo compressor according to the present invention mixes compressed air and water and sprays them as fine water droplets into a suction pipe of the turbo compressor. A water spray nozzle is provided.
【０００６】本発明によれば、圧気と水とを混合して微
細水滴として噴霧するようにしたので、水のみを噴霧し
ていた従来タイプと比べると噴霧の粒径が小さくなり、
その蒸発が促進される。According to the present invention, compressed air and water are mixed and sprayed as fine water droplets, so that the particle size of the spray is smaller than that of the conventional type in which only water is sprayed.
Its evaporation is promoted.
【０００７】なお、上記水噴霧ノズルに、ターボ圧縮機
で生成された圧気の一部を導く抽気供給管を接続しても
よい。こうすれば、圧気を生成する手間の一部が省け
る。[0007] The water spray nozzle may be connected to a bleed air supply pipe that guides a part of the compressed air generated by the turbo compressor. In this way, a part of the labor for generating air pressure can be omitted.
【０００８】[0008]
【発明の実施の形態】以下、本発明の一実施形態を添付
図面に基いて説明する。図１に、本発明を工場等の圧気
供給源として用いられる遠心圧縮機に適用したものを示
す。DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to the accompanying drawings. FIG. 1 shows an embodiment in which the present invention is applied to a centrifugal compressor used as a compressed air supply source in a factory or the like.
【０００９】遠心圧縮機１は、図示しないモータによっ
て回転駆動されるインペラ２と、インペラ２を収納する
ケーシング３と、ケーシング３に被圧縮流体としての空
気を導く吸込管４と、インペラ２から排出された空気を
減速して圧力に変換するディフューザ５と、ディフュー
ザ５から排出された空気を整流して後流側に流すスクロ
ール室６とを有している。なお、ディフューザ５は、ベ
ーン付タイプでもベーンレスタイプでもよい。The centrifugal compressor 1 includes an impeller 2 that is driven to rotate by a motor (not shown), a casing 3 that houses the impeller 2, a suction pipe 4 that guides air as a fluid to be compressed to the casing 3, and a discharge from the impeller 2. A diffuser 5 for decelerating the converted air into pressure and converting the pressure into a pressure, and a scroll chamber 6 for rectifying and discharging the air discharged from the diffuser 5 to the downstream side are provided. In addition, the diffuser 5 may be a vaned type or a vaneless type.
【００１０】吸込管４内には、圧気と水とを混合して微
細水滴として噴霧する水噴霧ノズル７が配置されてい
る。水噴霧ノズル７は、吸込管４の略中心から管壁を貫
通してラジアル方向に延出された保持パイプ８の先端
に、噴霧口９を後流側に向けて取り付けられている。保
持パイプ８内には、水噴霧ノズル７に圧気を供給する圧
気供給管１０と、水噴霧ノズル７に水を供給する水供給
管１１とが収容されている。[0010] A water spray nozzle 7 for mixing compressed air and water and spraying the mixture as fine water droplets is disposed in the suction pipe 4. The water spray nozzle 7 is attached to a distal end of a holding pipe 8 extending radially from a substantially center of the suction pipe 4 through the pipe wall with the spray port 9 facing the downstream side. A compressed air supply pipe 10 for supplying compressed air to the water spray nozzle 7 and a water supply pipe 11 for supplying water to the water spray nozzle 7 are accommodated in the holding pipe 8.
【００１１】圧気供給管１０には、フィルタ１２で濾過
された空気を所定圧力 (５〜７Kg/cm 2 程度) まで圧縮
する空気ポンプ１３が設けられている。水供給管１１に
は、水タンク１４から供給された水を所定圧力 (１〜３
Kg/cm 2 程度) まで圧縮する水ポンプ１５が設けられて
いる。これら空気ポンプ１３と水ポンプ１５とは、それ
ぞれ制御部１６によって適宜運転制御される。なお、圧
気供給管１０および水供給管１１には、それぞれ流量制
御弁等（図示せず）を設けてもよい。The air supply pipe 10 is provided with an air pump 13 for compressing the air filtered by the filter 12 to a predetermined pressure (about 5 to 7 kg / cm 2 ). The water supplied from the water tank 14 is supplied to the water supply pipe 11 at a predetermined pressure (1 to 3).
A water pump 15 is provided for compressing to about Kg / cm 2 ). The operation of the air pump 13 and the water pump 15 is appropriately controlled by the control unit 16. The compressed air supply pipe 10 and the water supply pipe 11 may each be provided with a flow control valve or the like (not shown).
【００１２】水噴霧ノズル７は、図２に示すように、そ
のノズルボディー１７内に、上記水供給管１１に接続さ
れる水導入通路１８と、上記圧気供給管１０に接続され
る圧気導入通路１９とを有する。水導入通路１８および
圧気導入通路１９は、それぞれ水中間通路２０および圧
気中間通路２１を介して、混合室２２に接続されてい
る。圧気中間通路２１は、中径管２１ａと細径管２１ｂ
とが繋がってなる。As shown in FIG. 2, the water spray nozzle 7 has a water introduction passage 18 connected to the water supply pipe 11 and a compressed air introduction passage connected to the compressed air supply pipe 10 in a nozzle body 17 thereof. 19. The water introduction passage 18 and the compressed air introduction passage 19 are connected to the mixing chamber 22 via a water intermediate passage 20 and a compressed air intermediate passage 21, respectively. The compressed air intermediate passage 21 includes a medium diameter pipe 21a and a small diameter pipe 21b.
Is connected.
【００１３】混合室２２は、噴霧口９と同芯的に形成さ
れた円筒部２２ａと、同様に同芯的に形成された円錐空
間部２２ｂとが、一体に繋がって構成されている。混合
室２２内には、噴霧口９と同芯的な円柱状に形成された
凸部２３が設けられている。凸部２３内には、圧気中間
通路２１の細径管２１ｂが、噴霧口９と同芯的に配置さ
れている。かかる混合室２２は、噴霧口９と同芯的な中
間通路２４を介して膨張室２５に接続されている。膨張
室２５は、先端室２６に繋がっており、先端室２６の室
壁先端には、噴霧口９が形成されている。The mixing chamber 22 is formed by integrally connecting a cylindrical portion 22a formed concentrically with the spray port 9 and a conical space portion 22b formed concentrically. In the mixing chamber 22, a projection 23 formed in a column shape concentric with the spray port 9 is provided. In the protruding portion 23, a small-diameter pipe 21b of the compressed air intermediate passage 21 is arranged concentrically with the spray port 9. The mixing chamber 22 is connected to an expansion chamber 25 via an intermediate passage 24 concentric with the spray port 9. The expansion chamber 25 is connected to the tip chamber 26, and a spray port 9 is formed at the tip of the chamber wall of the tip chamber 26.
【００１４】この構成によれば、水供給管１１から水導
入通路１８および水中間通路２０を介して混合室２２に
導かれた水 (１〜３Kg/cm 2 程度) は、圧気供給管１０
から圧気導入通路１９を介し圧気中間通路２１に導かれ
た圧気 (５〜７Kg/cm 2 程度) が凸部２３先端から高速
で噴出することにより混合室２２内にて混合され、気水
混合状態で膨張室２５内にて膨張し、微細水滴（粒径十
数μｍ程度）となって噴霧口９から噴霧されることにな
る。According to this configuration, water (about 1 to 3 kg / cm 2 ) guided from the water supply pipe 11 to the mixing chamber 22 through the water introduction passage 18 and the water intermediate passage 20 is supplied to the compressed air supply pipe 10.
The compressed air (about 5 to 7 kg / cm 2 ) introduced into the compressed air intermediate passage 21 through the compressed air introduction passage 19 is ejected at high speed from the tip of the convex portion 23, and is mixed in the mixing chamber 22, and the air-water mixed state , Expands in the expansion chamber 25 and becomes fine water droplets (particle diameter of about several tens μm) and is sprayed from the spray port 9.
【００１５】本実施形態の作用を図３を用いて説明す
る。The operation of this embodiment will be described with reference to FIG.
【００１６】水噴霧が行われない通常の遠心圧縮機のサ
イクルは、破線で示すように、吸込管４における等圧吸
入４→１と、インペラ２における断熱圧縮１→２と、ス
クロール室６における等圧吐出２→３とからなり、１→
２→３→４で囲まれた面積が圧縮仕事すなわち必要動力
となる。他方、理想的な圧縮行程は、一点鎖線で示すよ
うに、圧縮しながら冷却を行うことによって得られる等
温圧縮１→２′であり、そのときの必要動力は１→２′
→３→４で囲まれた面積であるが、現実には不可能であ
る。The cycle of a normal centrifugal compressor in which water spraying is not performed includes, as shown by broken lines, an equal pressure suction 4 → 1 in the suction pipe 4, an adiabatic compression 1 → 2 in the impeller 2, and a scroll chamber 6 in the scroll chamber 6. It consists of equal pressure discharge 2 → 3, 1 →
The area surrounded by 2 → 3 → 4 is compression work, that is, required power. On the other hand, the ideal compression stroke is isothermal compression 1 → 2 ′ obtained by performing cooling while compressing, as shown by the dashed line, and the required power at that time is 1 → 2 ′.
Although the area is surrounded by → 3 → 4, it is impossible in reality.
【００１７】本実施形態では、水噴霧ノズル７からイン
ペラ２の上流側に噴霧された微細水滴が圧縮行程中に気
化し、その気化熱によって断熱圧縮される空気が冷却さ
れるため、圧縮行程が実線で示すように断熱圧縮１→２
から等温圧縮１→２′に近付いて冷却圧縮行程１→２″
となる。よって、本実施形態に係る遠心圧縮機の必要動
力は、１→２″→３→４で囲まれた面積となり、水噴霧
が行われない通常の遠心圧縮機の必要動力１→２→３→
４で囲まれた面積よりも、明らかに小さくなる。In the present embodiment, fine water droplets sprayed from the water spray nozzle 7 to the upstream side of the impeller 2 are vaporized during the compression stroke, and the adiabatically compressed air is cooled by the heat of vaporization. Adiabatic compression 1 → 2 as shown by the solid line
Approaching isothermal compression 1 → 2 ′ and cooling compression stroke 1 → 2 ″
Becomes Therefore, the required power of the centrifugal compressor according to the present embodiment is an area surrounded by 1 → 2 ″ → 3 → 4, and the required power 1 → 2 → 3 → of the normal centrifugal compressor without water spraying.
It is clearly smaller than the area enclosed by 4.
【００１８】詳しくは、冷却圧縮行程１→２″の初期に
おいては、水噴霧ノズル７から噴霧された微細水滴が未
だ気化蒸発していないため、圧縮される空気を冷却でき
ないばかりでなく、その水滴がインペラ２に当って抵抗
となり却って圧縮仕事が大きくなってしまう。これが破
線で示す断熱圧縮行程１→２より右側に食み出た部分
（面積Ｂ）であり、ここでは圧縮仕事が増えて損をす
る。しかし、その後、冷却圧縮行程１→２″の中期以降
においては、微細水滴が気化し始めるため、その気化熱
によって断熱圧縮中の空気が冷却される。よって、圧縮
ラインが断熱圧縮１→２の左側に食い込んで等温圧縮１
→２′に近付き、その分（面積Ａ）だけ圧縮仕事が減少
して必要動力が小さくなる。More specifically, in the initial stage of the cooling / compression process 1 → 2 ″, since the fine water droplets sprayed from the water spray nozzle 7 have not yet been vaporized and evaporated, not only the compressed air cannot be cooled but also the water droplets. Is a resistance against the impeller 2, resulting in an increase in compression work.This is the portion (area B) that protrudes to the right from the adiabatic compression stroke 1 → 2 shown by the broken line, where the compression work increases and the loss increases. However, thereafter, after the middle stage of the cooling / compression process 1 → 2 ″, the fine water droplets start to vaporize, and the heat of vaporization cools the air during the adiabatic compression. Therefore, the compression line cuts into the left side of the adiabatic compression 1 → 2 and the isothermal compression 1
→ approaching 2 ', the compression work is reduced by that amount (area A), and the required power is reduced.
【００１９】ここで、トータルとしての必要動力の減少
量を考えると、圧縮仕事が減少する部分の面積Ａから圧
縮仕事が増大する部分の面積Ｂを減じた面積に相当する
仕事量が、トータルとしての必要動力の減少量となる。
よって、面積Ｂを小さくすることが望まれるわけである
が、そのためには水噴霧ノズル７から噴霧される微細水
滴の粒径をできるだけ小さくすればよい。粒径が小さけ
れば小さい程、気化蒸発しやすく、水滴がインペラに当
たることによって生じる抵抗力（圧縮仕事の増大）が小
さくなるため、面積Ｂが小さくなるからである。Considering the amount of reduction in the required power as a whole, the work amount corresponding to the area obtained by subtracting the area B of the part where the compression work increases from the area A of the part where the compression work decreases is the total work amount. Required power.
Therefore, it is desired to reduce the area B. For this purpose, the particle diameter of the fine water droplet sprayed from the water spray nozzle 7 may be reduced as much as possible. This is because the smaller the particle size is, the easier it is to vaporize and evaporate, and the smaller the area B is, the smaller the resistance force (increase in compression work) generated by the water droplet hitting the impeller becomes.
【００２０】本実施形態によれば、圧気と水とをそれぞ
れ所定圧力で混合して噴霧口９から微細水滴として噴霧
する加圧空気混合式の水噴霧ノズル７を用いているの
で、水のみを噴霧していた従来タイプと比べると噴霧の
粒径が十数μｍ程度にまで小さくなり、その気化蒸発が
促進される。よって、水滴がインペラ２に当たることに
よって生じる抵抗力（圧縮仕事の増大）が小さくなっ
て、面積Ｂが小さくなる。この結果、トータルとしての
必要動力の減少を図ることができる。According to the present embodiment, since the pressurized air mixing type water spray nozzle 7 for mixing compressed air and water at a predetermined pressure and spraying them as fine water droplets from the spray port 9 is used, only water is used. The particle size of the spray is reduced to about several tens of μm as compared with the conventional type in which the spray is performed, and the vaporization and evaporation are promoted. Therefore, the resistance (increase in compression work) generated by the water droplets hitting the impeller 2 is reduced, and the area B is reduced. As a result, the required power as a whole can be reduced.
【００２１】別の実施形態を図４に示す。Another embodiment is shown in FIG.
【００２２】図示するように、この実施形態は、前実施
形態の圧気供給管のフィルタ１２を外し、そこにターボ
圧縮機１で生成された圧気の一部を導く抽気供給管２７
を接続したものである。すなわち、圧気供給管１０とス
クロール室６とを抽気供給管２７で接続した。空気ポン
プ１３は、抽気供給管２７から得られる抽気の圧力を、
所定圧力（５〜７Kg/cm 2 程度）まで高める。水噴霧ノ
ズル７に供給される圧気が所定圧力（５〜７Kg/cm 2 程
度）以上でなければ、噴霧口９から噴霧される微細水滴
の粒径が所定径以下（粒径十数μｍ程度以下）にならな
いからである。As shown in the drawing, in this embodiment, a filter 12 of the compressed air supply pipe of the previous embodiment is removed, and a bleed supply pipe 27 for guiding a part of the compressed air generated by the turbo compressor 1 there.
Are connected. That is, the compressed air supply pipe 10 and the scroll chamber 6 were connected by the bleed supply pipe 27. The air pump 13 controls the pressure of the bleed air obtained from the bleed air supply pipe 27,
The pressure is increased to a predetermined pressure (about 5 to 7 kg / cm 2 ). If the pressure supplied to the water spray nozzle 7 is not equal to or higher than a predetermined pressure (about 5 to 7 kg / cm 2 ), the particle diameter of the fine water droplet sprayed from the spray port 9 is equal to or less than a predetermined diameter (about 10 μm or less). ).
【００２３】この実施形態によれば、水噴霧ノズル７に
供給する圧気を所定圧にまで高めるための手間の一部が
省け、空気ポンプ１３の運転コストが下がる。なお、抽
気供給管２７から得られる抽気が必要な所定圧力（５〜
７Kg/cm 2 程度）以上であるならば、空気ポンプ１３は
不要である。また、水供給管１１に電熱線等を巻き付け
たヒータ２８を設け、水噴霧ノズル７に供給する水に熱
を与えて飽和水に近付け、蒸発を促進させるようにして
もよい。According to this embodiment, a part of the work for increasing the pressure of the air supplied to the water spray nozzle 7 to the predetermined pressure is omitted, and the operating cost of the air pump 13 is reduced. A predetermined pressure (5 to 5) at which bleeding obtained from the bleeding supply pipe 27 is necessary.
If it is at least 7 kg / cm 2 ), the air pump 13 is unnecessary. Further, a heater 28 in which a heating wire or the like is wound around the water supply pipe 11 may be provided to apply heat to the water supplied to the water spray nozzle 7 so as to approach the saturated water to promote evaporation.
【００２４】また、本発明は、既述したような遠心圧縮
機１を多段に接続した多段遠心圧縮装置の各段に適宜適
用してもよく、遠心圧縮機ではなく軸流圧縮機に適用し
てもよいことは勿論である。The present invention may be applied to each stage of a multistage centrifugal compressor in which the above-described centrifugal compressor 1 is connected in multiple stages, and may be applied to an axial compressor instead of a centrifugal compressor. Of course, it may be possible.
【００２５】[0025]
【発明の効果】以上説明したように本発明に係るターボ
圧縮機用の水噴霧装置によれば、圧気と水とを混合して
微細水滴として噴霧するため、噴霧の粒径が小さくなっ
てその蒸発の促進を図ることができる。よって、圧縮仕
事すなわち必要動力を低減することができる。As described above, according to the water spraying device for a turbo compressor according to the present invention, since the compressed air and water are mixed and sprayed as fine water droplets, the particle size of the spray is reduced. Evaporation can be promoted. Therefore, compression work, that is, required power can be reduced.
【図１】本発明の一実施形態を示すターボ圧縮機用の水
噴霧装置の説明図である。FIG. 1 is a diagram illustrating a water spray device for a turbo compressor according to an embodiment of the present invention.
【図２】上記水噴霧装置の水噴霧ノズルの断面図であ
る。FIG. 2 is a sectional view of a water spray nozzle of the water spray device.
【図３】上記ターボ圧縮機にサイクル図である。FIG. 3 is a cycle diagram of the turbo compressor.
【図４】別の実施形態を示すターボ圧縮機用の水噴霧装
置の説明図である。FIG. 4 is an explanatory view of a water spray device for a turbo compressor according to another embodiment.
１ ターボ圧縮機としての遠心圧縮機 ４ 吸込管 ７ 水噴霧ノズル ２７ 抽気供給管 DESCRIPTION OF SYMBOLS 1 Centrifugal compressor as a turbo compressor 4 Suction pipe 7 Water spray nozzle 27 Bleed supply pipe
Claims (2)
を混合して微細水滴として噴霧する水噴霧ノズルを設け
たことを特徴とするターボ圧縮機用の水噴霧装置。1. A water spray device for a turbo compressor, wherein a water spray nozzle for mixing compressed air and water and spraying the same as fine water droplets is provided in a suction pipe of the turbo compressor.
成された圧気の一部を導く抽気供給管を接続した請求項
１記載のターボ圧縮機用の水噴霧装置。2. The water spray device for a turbo compressor according to claim 1, wherein a bleed air supply pipe for guiding a part of the compressed air generated by the turbo compressor is connected to the water spray nozzle.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10289424A JP2000120596A (en) | 1998-10-12 | 1998-10-12 | Water spray for turbocompressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10289424A JP2000120596A (en) | 1998-10-12 | 1998-10-12 | Water spray for turbocompressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2000120596A true JP2000120596A (en) | 2000-04-25 |
Family
ID=17743074
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10289424A Pending JP2000120596A (en) | 1998-10-12 | 1998-10-12 | Water spray for turbocompressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2000120596A (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009121318A (en) * | 2007-11-14 | 2009-06-04 | Univ Nagoya | Compressor |
| JP2010279898A (en) * | 2009-06-04 | 2010-12-16 | Ihi Corp | Droplet generator of compressor |
| US20140159257A1 (en) * | 2012-12-12 | 2014-06-12 | Minuteman International, Inc. | Wet dust suppression floor cleaning system |
| JP2016211519A (en) * | 2015-05-13 | 2016-12-15 | 隆逸 小林 | Manufacturing method and use method of high-density air |
| CN107559239A (en) * | 2017-09-20 | 2018-01-09 | 北京航空航天大学 | A kind of centrifugal gas compressor attemperator of center nozzle structure |
| CN111749932A (en) * | 2020-07-07 | 2020-10-09 | 中国空气动力研究与发展中心超高速空气动力研究所 | Centrifugal vacuum pump with water spray cooling device |
| EP4170186A1 (en) * | 2021-10-21 | 2023-04-26 | Siemens Energy Global GmbH & Co. KG | Compressor, in particular radial compressor |
-
1998
- 1998-10-12 JP JP10289424A patent/JP2000120596A/en active Pending
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009121318A (en) * | 2007-11-14 | 2009-06-04 | Univ Nagoya | Compressor |
| JP2010279898A (en) * | 2009-06-04 | 2010-12-16 | Ihi Corp | Droplet generator of compressor |
| US20140159257A1 (en) * | 2012-12-12 | 2014-06-12 | Minuteman International, Inc. | Wet dust suppression floor cleaning system |
| US8960648B2 (en) * | 2012-12-12 | 2015-02-24 | Minuteman International, Inc. | Wet dust suppression floor cleaning system |
| JP2016211519A (en) * | 2015-05-13 | 2016-12-15 | 隆逸 小林 | Manufacturing method and use method of high-density air |
| EP3296569A4 (en) * | 2015-05-13 | 2018-11-21 | Takaitsu Kobayashi | Method for producing high-density air and method for using same |
| AU2016261407B2 (en) * | 2015-05-13 | 2020-12-03 | Takaitsu Kobayashi | Method for producing high-density air and method for using same |
| CN107559239A (en) * | 2017-09-20 | 2018-01-09 | 北京航空航天大学 | A kind of centrifugal gas compressor attemperator of center nozzle structure |
| CN107559239B (en) * | 2017-09-20 | 2019-03-26 | 北京航空航天大学 | A kind of centrifugal gas compressor attemperator with center nozzle structure |
| CN111749932A (en) * | 2020-07-07 | 2020-10-09 | 中国空气动力研究与发展中心超高速空气动力研究所 | Centrifugal vacuum pump with water spray cooling device |
| EP4170186A1 (en) * | 2021-10-21 | 2023-04-26 | Siemens Energy Global GmbH & Co. KG | Compressor, in particular radial compressor |
| WO2023066585A1 (en) * | 2021-10-21 | 2023-04-27 | Siemens Energy Global GmbH & Co. KG | Compressor, in particular radial compressor |
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