JPH0560097A - Centrifugal compressor - Google Patents
Centrifugal compressorInfo
- Publication number
- JPH0560097A JPH0560097A JP24651891A JP24651891A JPH0560097A JP H0560097 A JPH0560097 A JP H0560097A JP 24651891 A JP24651891 A JP 24651891A JP 24651891 A JP24651891 A JP 24651891A JP H0560097 A JPH0560097 A JP H0560097A
- Authority
- JP
- Japan
- Prior art keywords
- impeller
- opening
- chamber
- flow rate
- air
- 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.)
- Granted
Links
Landscapes
- Supercharger (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明はエンジンへの過給圧を発
生させる過給機の給気装置や、一般製造工場の空気源設
備等として用いる遠心圧縮機に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air supply device of a supercharger for generating a supercharging pressure to an engine, a centrifugal compressor used as an air source equipment of a general manufacturing plant, and the like.
【０００２】[0002]
【従来の技術】エンジンへの過給を行う過給機は、たと
えば、翼車を有するタービンと羽根車を有する遠心圧縮
機（コンプレッサ）とを軸受車室を介して一体構造と
し、上記翼車と羽根車とを、軸受車室内に回転自在に支
持させた軸にて連結し、エンジンの排気によって翼車を
回転させ、該翼車の回転で軸を介して羽根車を回転させ
ることにより、吸気を遠心圧縮機で圧縮してエンジンに
給気するようにしてある。2. Description of the Related Art A supercharger for supercharging an engine has, for example, a turbine having an impeller and a centrifugal compressor (compressor) having an impeller, which are integrally formed through a bearing casing. And the impeller are connected by a shaft rotatably supported in the bearing casing, the impeller is rotated by the exhaust of the engine, and the impeller is rotated through the shaft by the rotation of the impeller, The intake air is compressed by a centrifugal compressor and supplied to the engine.
【０００３】上記過給機で用いる遠心圧縮機において
は、図４に一例を示す如く、空気量が減少してくると、
圧縮機特性曲線Ｉがサージ線Ｓを越えてサージング領域
Ａに入るという特性がある。したがって、上記サージ線
ＳをＳ´の位置へと低流量側へ移動させることができれ
ば、エンジンの運転範囲に対してより広い範囲に亘り適
合させることができる。In the centrifugal compressor used in the above supercharger, as shown in FIG.
There is a characteristic that the compressor characteristic curve I exceeds the surge line S and enters the surging region A. Therefore, if the surge line S can be moved to the position of S ′ toward the low flow rate side, it can be adapted to a wider range with respect to the operating range of the engine.
【０００４】そのため、従来では、図５に示す如く、羽
根車ａの外周部にデュフューザ部ｂを介してスクロール
状の圧縮流路ｃを有し且つ上記デュフューザ部ｂから羽
根車ａの前方へ突出するシュラウド壁を有するハウジン
グｄを備え、更に、上記羽根車ａを、図示しないタービ
ンの翼車に軸により連結して、翼車の回転により軸を介
して羽根車ａが回転させられるようにしてある遠心圧縮
機において、上記シュラウド壁を、前端に吸込口ｅを形
成した外壁ｆと、上記吸込口ｅの下流で前端に入口ｇを
形成した内壁ｈとの二重壁構造とすると共に、上記外壁
ｆと内壁ｈの間に環状のチャンバｉを形成し、且つ上記
内壁ｈに、チャンバｉと羽根車ａとの間を連通させるた
めのスロット（又は孔）ｊを設けるようにしたものが提
案されている（特開昭６２−１７８７９９号）。Therefore, conventionally, as shown in FIG. 5, a scroll-shaped compression flow path c is provided on the outer peripheral portion of the impeller a through a diffuser portion b, and protrudes from the diffuser portion b toward the front of the impeller a. And a housing d having a shroud wall for connecting the impeller a to an impeller of a turbine (not shown) by a shaft so that the impeller a is rotated through the shaft by the rotation of the impeller. In a certain centrifugal compressor, the shroud wall has a double wall structure including an outer wall f having a suction port e formed at the front end and an inner wall h having an inlet g formed at the front end downstream of the suction port e. It is proposed that an annular chamber i is formed between the outer wall f and the inner wall h, and that the inner wall h is provided with a slot (or hole) j for communicating between the chamber i and the impeller a. Has been (special Sho 62-178799).
【０００５】上記遠心圧縮機によれば、高流量運転時に
は、羽根車ａにおける入口ｇに近い領域内の圧力がチャ
ンバｉ内より低くなるので、入口ｇから羽根車ａの方へ
流れる空気とは別に、チャンバｉからもスロットｊを通
して羽根車ａの方へ空気が流れ、これにより羽根車ａに
到達する空気の量を増大させてその最大流量容量を増大
させるようにし、一方、低流量運転時には、羽根車ａに
おける入口ｇに近い領域の圧力がチャンバｉ内より高く
なるので、羽根車ａの部分からスロットｊを通してチャ
ンバｉ側への空気流を生じさせ、その空気を吸込口ｅ側
から入口ｇを通して再循環させて流量容量を減少させ、
これにより図４に示すサージ線ＳをＳ´の位置へ移動さ
せることができるものとされている。According to the above-mentioned centrifugal compressor, the pressure in the region near the inlet g of the impeller a becomes lower than that in the chamber i during high-flow rate operation, so that the air flowing from the inlet g toward the impeller a is Separately, air also flows from the chamber i through the slot j toward the impeller a, thereby increasing the amount of air reaching the impeller a and increasing its maximum flow capacity, while at the time of low flow operation. Since the pressure in the region near the inlet g of the impeller a becomes higher than that in the chamber i, an air flow from the portion of the impeller a through the slot j to the chamber i side is generated, and the air is introduced from the suction port e side. recirculate through g to reduce the flow capacity,
As a result, the surge line S shown in FIG. 4 can be moved to the position S '.
【０００６】[0006]
【発明が解決しようとする課題】ところが、上記遠心圧
縮機の場合、内壁ｈにスロットｊを設けたことにより、
高流量運転時の最大流量容量を増大させることはできる
が、チャンバｉ内に常に吸込口ｅにおける動圧が作用す
ることから、低流量運転時では、羽根車ａ側からスロッ
トｊを通しての空気の循環流が生じにくく、その結果、
図４におけるサージ線Ｓを低流量側に移動させる能力が
小さい。However, in the case of the above centrifugal compressor, since the slot j is provided in the inner wall h,
Although the maximum flow rate capacity at the time of high flow rate operation can be increased, the dynamic pressure at the suction port e always acts in the chamber i. Therefore, at the time of low flow rate operation, the air flow from the impeller a side through the slot j is reduced. Circulating flow is less likely to occur, resulting in
The ability to move the surge line S in FIG. 4 to the low flow rate side is small.
【０００７】そこで、本発明は、機関の運転範囲に対し
て遠心圧縮機の運転範囲を適合させられるように、サー
ジ線をより低流量側へ移動させることができるようにし
ようとするものである。Therefore, the present invention seeks to make it possible to move the surge line to a lower flow rate side so that the operating range of the centrifugal compressor can be adapted to the operating range of the engine. ..
【０００８】[0008]
【課題を解決するための手段】本発明は、上記課題を解
決するために、羽根車の外周部から前方に延びて吸込口
を形成するようにしたシュラウド壁を有するハウジング
を備えた遠心圧縮機において、上記シュラウド壁の吸込
口側の部分に、上記羽根車の方向へ向けて縮径する絞り
部を設け、且つ上記シュラウド壁に、羽根車設置位置に
設けた第１開口部と、上記絞り部の終端となる最小径付
近に設けた第２開口部と、該第１開口部と第２開口部と
を連絡する流路とからなる循環流路を設け、更に、上記
第２開口部を半径方向に形成してなる構成とする。SUMMARY OF THE INVENTION In order to solve the above problems, the present invention provides a centrifugal compressor having a housing having a shroud wall which extends forward from the outer peripheral portion of an impeller to form a suction port. In the suction port side portion of the shroud wall, a throttle portion that reduces in diameter in the direction of the impeller is provided, and in the shroud wall, a first opening portion provided at an impeller installation position, and the throttle portion. A second opening provided near the minimum diameter that is the end of the section, and a circulation flow path including a flow path that connects the first opening and the second opening, and further the second opening is provided. The structure is formed in the radial direction.
【０００９】[0009]
【作用】圧縮圧力Ｐ（図４）の増大にともない羽根車内
の入口に近い領域の圧力も高くなり、また遠心力も働く
ため、羽根車により吸引される空気の一部が循環流路内
に廻り込む。この際、循環流路は絞り部による空気の縮
流効果により負圧が作用することから、羽根車内の入口
に近い領域の空気を循環流路内に引き込み第２開口部を
通して循環させることができる。これにより、羽根車に
おける吸引領域で発生した失速流れを循環流路内へ引き
込み、失速領域の拡大を抑えることができる。したがっ
て、サージ線を低流量側へ移動させることができるよう
になる。As the compression pressure P (FIG. 4) increases, the pressure in the area near the inlet of the impeller also increases, and centrifugal force also acts, so that part of the air sucked by the impeller circulates in the circulation flow path. To be crowded. At this time, since a negative pressure acts on the circulation flow passage due to the contraction effect of air by the throttle portion, air in a region near the inlet of the impeller can be drawn into the circulation flow passage and circulated through the second opening. .. As a result, the stall flow generated in the suction region of the impeller can be drawn into the circulation passage, and the expansion of the stall region can be suppressed. Therefore, the surge line can be moved to the low flow rate side.
【００１０】[0010]
【実施例】以下、本発明の実施例を図面を参照して説明
する。Embodiments of the present invention will be described below with reference to the drawings.
【００１１】図１は本発明の一実施例を示すもので、羽
根車１の外周部にデュフューザ部２を介してスクロール
状の圧縮流路３を有し且つ上記デュフューザ部２から前
方へ延びて吸込口４を形成するようにしたシュラウド壁
５を有するハウジング６を備え、更に、上記羽根車１を
図示しないタービンの翼車に軸を介し連結し、エンジン
の排気によってタービンの翼車が回転させられることに
より軸を介して羽根車１が回転させられ、該羽根車１の
回転により、吸気を圧縮してエンジンに給気させられる
ようにしてある遠心圧縮機において、上記シュラウド壁
５の吸込口４側の部分に、上記羽根車１の方向へ向けて
縮径する絞り部７を設け、該絞り部７によって縮流効果
の与えられた空気が羽根車１により吸引されるように
し、且つ上記シュラウド壁５中に環状のチャンバ８を設
け、更に、上記シュラウド壁５に、チャンバ８内と羽根
車１の設置位置とを連通させるためのスリット状の第１
開口部９と、チャンバ８内と上記絞り部７の終端よりも
やや下流位置とを径方向へ連通させるためのスリット状
の第２開口部１０とを、それぞれ周方向に穿設し、上記
第１開口部９、チャンバ８、第２開口部１０により、低
流量運転時に羽根車１によって吸引される空気の一部を
循環させてサージ線の流量容量を減少させるための循環
流路を構成する。FIG. 1 shows an embodiment of the present invention, in which a scroll-shaped compression flow path 3 is provided on the outer peripheral portion of an impeller 1 via a diffuser portion 2 and extends forward from the diffuser portion 2. A housing 6 having a shroud wall 5 so as to form the suction port 4 is provided, and further, the impeller 1 is connected to a turbine impeller (not shown) via a shaft so that the turbine impeller is rotated by engine exhaust. In this centrifugal compressor, the impeller 1 is rotated via the shaft so that the rotation of the impeller 1 compresses the intake air to supply the engine with the suction port of the shroud wall 5. A throttle portion 7 whose diameter is reduced in the direction of the impeller 1 is provided at the portion on the 4 side so that the air having a contraction effect by the throttle portion 7 is sucked by the impeller 1. Shura An annular chamber 8 provided in de wall 5, further in the shroud wall 5, the slit for communicating the installation position of the chamber 8 and the impeller 1 of 1
An opening 9 and a slit-shaped second opening 10 for radially communicating the inside of the chamber 8 with a position slightly downstream of the end of the throttle 7 are provided in the circumferential direction, and The first opening 9, the chamber 8 and the second opening 10 constitute a circulation flow path for circulating a part of the air sucked by the impeller 1 at the time of low flow rate operation to reduce the flow capacity of the surge line. .
【００１２】なお、上記絞り部７の角度αは１５°〜４
０°の範囲とし、又、絞り部７の終端から第２開口部１
０までの距離ｌと吸込半径ｒs との関係は、ｌ≦ｒs の
範囲としてある。The angle α of the diaphragm 7 is 15 ° to 4 °.
Within the range of 0 °, and from the end of the diaphragm 7 to the second opening 1
The relationship between the distance l to 0 and the suction radius rs is in the range of l≤rs.
【００１３】運転を行うと、羽根車１の回転により吸込
口４から吸い込まれた空気は、羽根車１における吸引領
域に吸引され、圧縮流路３を通って目的とする場所へ給
気される。低流量運転時には、羽根車１のすべての領域
における圧力がチャンバ８内の圧力よりも高くなる。し
たがって、羽根車１の羽根部分を通過する空気の一部が
第１開口部９からチャンバ８内へ向かうような空気流が
発生する。一方、このとき、吸込口４から入ってくる空
気は、絞り部７により縮流されるので、第２開口部１０
を通過する際の速度分布はその縮流効果によって外側
（壁に近いところ）で大きく（速く）なっている。した
がって、この縮流効果を受けた空気流が第２開口部１０
を通過することで、第２開口部１０からチャンバ８内の
空気を吸引することになり、その結果、チャンバ８内の
負圧を大きくし、上記羽根車１の羽根部分を通過する空
気の一部を、第１開口部９からチャンバ８内を通して第
２開口部１０から排出し、それを再び羽根車１に向けて
流すことができ、図１の破線矢印で示す如く、静圧を利
用した循環流を発生させることができる。When the operation is performed, the air sucked from the suction port 4 by the rotation of the impeller 1 is sucked into the suction region of the impeller 1 and is supplied to the intended place through the compression flow path 3. .. During low flow rate operation, the pressure in all regions of the impeller 1 becomes higher than the pressure in the chamber 8. Therefore, an air flow is generated in which a part of the air passing through the blade portion of the impeller 1 is directed from the first opening 9 into the chamber 8. On the other hand, at this time, the air entering from the suction port 4 is contracted by the throttle unit 7, so that the second opening 10
The velocity distribution when passing through is large (faster) on the outside (near the wall) due to the contraction effect. Therefore, the airflow that has received this contraction effect is the second opening 10
The air in the chamber 8 is sucked from the second opening 10 as a result of increasing the negative pressure in the chamber 8 and one of the air passing through the blade portion of the impeller 1 is passed. The part can be discharged from the second opening 10 through the first opening 9 through the chamber 8 and flow toward the impeller 1 again, and as shown by the broken line arrow in FIG. 1, static pressure was used. A circulating flow can be generated.
【００１４】このように、チャンバ８内の負圧を大きく
することにより、第１開口部９からの吸引作用を大きく
することができるので、本来、サージング領域に入るよ
うな低流量容量の運転状況でもサージング領域に入らな
いようにすることができる。すなわち、図４に示すサー
ジ線Ｓを、低流量側のＳ´の位置へ移動させることがで
きる。As described above, since the suction action from the first opening 9 can be increased by increasing the negative pressure in the chamber 8, the operating condition of the low flow rate capacity which is originally in the surging region. But you can keep it out of the surging area. That is, the surge line S shown in FIG. 4 can be moved to the position of S ′ on the low flow rate side.
【００１５】次に、図２は本発明の他の実施例を示すも
ので、上記図１の実施例で示すものと同様な構成におい
て、シュラウド壁５の内周面の第２開口部１０よりも更
に下流位置に、絞り部７´を設けて２段絞り構造とした
ものである。Next, FIG. 2 shows another embodiment of the present invention. From the second opening 10 on the inner peripheral surface of the shroud wall 5 in the same construction as that shown in the embodiment of FIG. In addition, a throttle portion 7'is provided further downstream to form a two-stage throttle structure.
【００１６】図２に示す実施例の場合には、絞り部７の
角度αを大きくするなどにより縮流効果を高くした場合
に、第２開口部１０から羽根車１に至る迄に、空気の縮
流の回復が不十分な場合に生じる不都合を防止するもの
であり、絞り部７´にての縮流の回復を高める効果との
組合せにより第２開口部１０の部分での空気の縮流効果
を更に高めることができ、チャンバ８内から第２開口部
１０を通しての空気の吸引作用をより大きくすることが
できるので、図４におけるサージ線の位置をＳ´よりも
更に低流量側へ移すことが可能となる。In the case of the embodiment shown in FIG. 2, when the contraction effect is enhanced by increasing the angle α of the throttle portion 7, air is blown from the second opening 10 to the impeller 1. This is intended to prevent the inconvenience that occurs when the recovery of the contracted flow is insufficient, and in combination with the effect of enhancing the recovery of the contracted flow at the throttle portion 7 ′, the contracted flow of air at the second opening 10 portion. Since the effect can be further enhanced and the suction action of air from the chamber 8 through the second opening 10 can be further increased, the position of the surge line in FIG. 4 is moved to a lower flow rate side than S ′. It becomes possible.
【００１７】なお、上記各実施例では、第１開口部９と
チャンバ８と第２開口部１０とによって空気の循環流路
を形成するようにした場合を示したが、図３に示す如
く、上記チャンバ８に代えて、単なる通路８´を設ける
ようにしてもよいこと、第１開口部９、第２開口部１０
はスリット状に代えて孔を多数配列した形状としてもよ
いこと、その他本発明の要旨を逸脱しない範囲内におい
て種々変更を加え得ることは勿論である。In each of the above-mentioned embodiments, the case where the air circulation passage is formed by the first opening 9, the chamber 8 and the second opening 10 has been described, but as shown in FIG. Instead of the chamber 8, a simple passage 8'may be provided, and the first opening 9 and the second opening 10 may be provided.
Needless to say, the slit may have a shape in which a large number of holes are arranged instead of the slit shape, and various changes may be made without departing from the scope of the invention.
【００１８】[0018]
【発明の効果】以上述べた如く、本発明の遠心圧縮機に
よれば、羽根車の外周部から前方に延びて吸込口を形成
するようにしたシュラウド壁を有するハウジングにおけ
る上記シュラウド壁の吸込口側部分に、上記羽根車の方
向へ向けて縮径する絞り部を設け、且つ上記シュラウド
壁に、羽根車設置位置に設けた第１開口部と、シュラウ
ド壁中を通って上記絞り部の最小縮径付近に設けた第２
開口部と、両開口部を連絡する流路とからなる循環流路
を設け、第２開口部を径方向に形成した構成を有するの
で、低流量運転時に、上記絞り部による空気の縮流効果
により循環流路内に負圧を与えることができ、したがっ
て、羽根車によって吸引される空気を循環流路を通して
静圧的に循環させることができ、これにより、本来、サ
ージング領域に入るような低流量容量の運転状況下でも
サージ線を低流量側へ移すことができて機関の運転範囲
に対して広範囲に亘り適合させることができる、という
優れた効果を発揮する。As described above, according to the centrifugal compressor of the present invention, the suction port of the shroud wall in the housing having the shroud wall which extends forward from the outer peripheral portion of the impeller to form the suction port. The side portion is provided with a throttle portion whose diameter is reduced in the direction of the impeller, and the shroud wall is provided with a first opening portion provided at an impeller installation position and a minimum of the throttle portion passing through the shroud wall. The second provided near the reduced diameter
Since the circulation flow path including the opening and the flow path connecting the both openings is provided and the second opening is formed in the radial direction, the effect of reducing the air flow by the throttle portion is achieved during the low flow rate operation. Can provide a negative pressure in the circulation flow path, and therefore, the air sucked by the impeller can be circulated statically through the circulation flow path, which naturally causes a low pressure to enter the surging region. Even under the operating condition of the flow capacity, the surge line can be moved to the low flow side, and the excellent effect that it can be adapted to the operating range of the engine over a wide range is exhibited.
【図１】本発明の遠心圧縮機の一実施例を示す要部の概
略図である。FIG. 1 is a schematic view of a main part showing an embodiment of a centrifugal compressor of the present invention.
【図２】本発明の他の実施例を示す要部の概略図であ
る。FIG. 2 is a schematic view of a main part showing another embodiment of the present invention.
【図３】本発明の更に他の実施例を示す要部の概略図で
ある。FIG. 3 is a schematic view of a main part showing still another embodiment of the present invention.
【図４】遠心圧縮機の流量と圧力との関係を示す一例図
である。FIG. 4 is an example diagram showing a relationship between a flow rate and a pressure of a centrifugal compressor.
【図５】遠心圧縮機の一例を示す概要図である。FIG. 5 is a schematic diagram showing an example of a centrifugal compressor.
１ 羽根車 ４ 吸込口 ５ シュラウド壁 ６ ハウジング ７ 絞り部 ８ チャンバ（循環流路） ９ 第１開口部（循環流路） １０ 第２開口部（循環流路） DESCRIPTION OF SYMBOLS 1 Impeller 4 Suction port 5 Shroud wall 6 Housing 7 Throttling part 8 Chamber (circulation flow path) 9 1st opening part (circulation flow path) 10 2nd opening part (circulation flow path)
───────────────────────────────────────────────────── フロントページの続き (72)発明者 山口 広 東京都江東区豊洲三丁目１番15号 石川島 播磨重工業株式会社技術研究所内 (72)発明者 崎本 建夫 東京都江東区豊洲三丁目１番15号 石川島 播磨重工業株式会社技術研究所内 (72)発明者 山口 諭 東京都江東区豊洲三丁目１番15号 石川島 播磨重工業株式会社技術研究所内 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Hiroshi Yamaguchi 3-15-15 Toyosu, Koto-ku, Tokyo Ishikawajima Harima Heavy Industries, Ltd. Technical Research Institute (72) Takeo Sakimoto 3-1-1 Toyosu, Koto-ku, Tokyo No. 15 Ishikawajima Harima Heavy Industries Co., Ltd. Technical Research Institute (72) Inventor Satoshi Yamaguchi 3-15-1 Toyosu, Koto-ku, Tokyo Ishikawajima Harima Heavy Industries Co., Ltd. Technical Research Institute
Claims (1)
を形成するようにしたシュラウド壁を有するハウジング
を備えた遠心圧縮機において、上記シュラウド壁の吸込
口側の部分に、上記羽根車の方向へ向けて縮径する絞り
部を設け、且つ上記シュラウド壁に、羽根車設置位置に
設けた第１開口部と、上記絞り部の終端となる最小径付
近に設けた第２開口部と、該第１開口部と第２開口部と
を連絡する流路とからなる循環流路を設け、更に、上記
第２開口部を半径方向に形成してなることを特徴とする
遠心圧縮機。1. A centrifugal compressor provided with a housing having a shroud wall which extends forward from an outer peripheral portion of an impeller to form a suction port, wherein the impeller is provided at a portion of the shroud wall on the suction port side. A first opening provided at the impeller installation position on the shroud wall, and a second opening provided near the minimum diameter at the end of the throttle on the shroud wall. A centrifugal compressor, characterized in that a circulation flow path comprising a flow path connecting the first opening and the second opening is provided, and further the second opening is formed in the radial direction.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3246518A JP3038398B2 (en) | 1991-09-02 | 1991-09-02 | Centrifugal compressor |
| US07/869,181 US5246335A (en) | 1991-05-01 | 1992-04-16 | Compressor casing for turbocharger and assembly thereof |
| EP92303921A EP0526965B1 (en) | 1991-05-01 | 1992-04-30 | Compressor casings for turbochargers |
| DE69216938T DE69216938T2 (en) | 1991-05-01 | 1992-04-30 | Compressor housing for turbochargers |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3246518A JP3038398B2 (en) | 1991-09-02 | 1991-09-02 | Centrifugal compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0560097A true JPH0560097A (en) | 1993-03-09 |
| JP3038398B2 JP3038398B2 (en) | 2000-05-08 |
Family
ID=17149592
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3246518A Expired - Lifetime JP3038398B2 (en) | 1991-05-01 | 1991-09-02 | Centrifugal compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3038398B2 (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH11201094A (en) * | 1998-01-19 | 1999-07-27 | Ishikawajima Harima Heavy Ind Co Ltd | Turbo-compressor |
| EP1143149A2 (en) * | 2000-04-07 | 2001-10-10 | Ishikawajima-Harima Jukogyo Kabushiki Kaisha | Method and apparatus for expanding operating range of centrifugal compressor |
| JP2003314496A (en) * | 2002-04-18 | 2003-11-06 | Ishikawajima Harima Heavy Ind Co Ltd | Centrifugal compressor |
| JP2004144029A (en) * | 2002-10-25 | 2004-05-20 | Toyota Central Res & Dev Lab Inc | Centrifugal compressor for turbocharger |
| JP2004332734A (en) * | 2003-04-30 | 2004-11-25 | Holset Eng Co Ltd | Compressor |
| JP2012509428A (en) * | 2008-11-18 | 2012-04-19 | ボーグワーナー インコーポレーテッド | Exhaust gas turbocharger compressor |
| JP2013527382A (en) * | 2010-06-04 | 2013-06-27 | ボーグワーナー インコーポレーテッド | Exhaust gas turbocharger compressor |
| WO2018208874A1 (en) * | 2017-05-12 | 2018-11-15 | Borgwarner Inc. | Turbocharger having improved ported shroud compressor housing |
| WO2018208873A1 (en) * | 2017-05-12 | 2018-11-15 | Borgwarner Inc. | Turbocharger having improved ported shroud compressor housing |
| JP2019011688A (en) * | 2017-06-29 | 2019-01-24 | 株式会社日立製作所 | Fluid machine |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104847703A (en) * | 2015-05-29 | 2015-08-19 | 无锡科博增压器有限公司 | Flow regulation mechanism surge proof and blocking proof for gas compressor |
-
1991
- 1991-09-02 JP JP3246518A patent/JP3038398B2/en not_active Expired - Lifetime
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH11201094A (en) * | 1998-01-19 | 1999-07-27 | Ishikawajima Harima Heavy Ind Co Ltd | Turbo-compressor |
| EP1143149A2 (en) * | 2000-04-07 | 2001-10-10 | Ishikawajima-Harima Jukogyo Kabushiki Kaisha | Method and apparatus for expanding operating range of centrifugal compressor |
| JP2001289197A (en) * | 2000-04-07 | 2001-10-19 | Ishikawajima Harima Heavy Ind Co Ltd | Method and device for increasing operating area of centrifugal compressor |
| US6447241B2 (en) | 2000-04-07 | 2002-09-10 | Ishikawajima-Harima Jukogyo Kabushiki Kaisha | Method and apparatus for expanding operating range of centrifugal compressor |
| EP1143149A3 (en) * | 2000-04-07 | 2003-01-15 | Ishikawajima-Harima Jukogyo Kabushiki Kaisha | Method and apparatus for expanding operating range of centrifugal compressor |
| JP2003314496A (en) * | 2002-04-18 | 2003-11-06 | Ishikawajima Harima Heavy Ind Co Ltd | Centrifugal compressor |
| JP2004144029A (en) * | 2002-10-25 | 2004-05-20 | Toyota Central Res & Dev Lab Inc | Centrifugal compressor for turbocharger |
| JP2004332734A (en) * | 2003-04-30 | 2004-11-25 | Holset Eng Co Ltd | Compressor |
| JP2012509428A (en) * | 2008-11-18 | 2012-04-19 | ボーグワーナー インコーポレーテッド | Exhaust gas turbocharger compressor |
| JP2013527382A (en) * | 2010-06-04 | 2013-06-27 | ボーグワーナー インコーポレーテッド | Exhaust gas turbocharger compressor |
| WO2018208874A1 (en) * | 2017-05-12 | 2018-11-15 | Borgwarner Inc. | Turbocharger having improved ported shroud compressor housing |
| WO2018208873A1 (en) * | 2017-05-12 | 2018-11-15 | Borgwarner Inc. | Turbocharger having improved ported shroud compressor housing |
| US10309417B2 (en) | 2017-05-12 | 2019-06-04 | Borgwarner Inc. | Turbocharger having improved ported shroud compressor housing |
| US10316859B2 (en) | 2017-05-12 | 2019-06-11 | Borgwarner Inc. | Turbocharger having improved ported shroud compressor housing |
| JP2019011688A (en) * | 2017-06-29 | 2019-01-24 | 株式会社日立製作所 | Fluid machine |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3038398B2 (en) | 2000-05-08 |
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