JPH116500A - Centrifugal compressor swirl generator - Google Patents
Centrifugal compressor swirl generatorInfo
- Publication number
- JPH116500A JPH116500A JP9159380A JP15938097A JPH116500A JP H116500 A JPH116500 A JP H116500A JP 9159380 A JP9159380 A JP 9159380A JP 15938097 A JP15938097 A JP 15938097A JP H116500 A JPH116500 A JP H116500A
- Authority
- JP
- Japan
- Prior art keywords
- pipe
- main pipe
- sub
- impeller
- main
- 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.)
- Pending
Links
- 230000007423 decrease Effects 0.000 claims abstract description 10
- 230000001154 acute effect Effects 0.000 claims abstract description 5
- 238000011144 upstream manufacturing Methods 0.000 claims description 3
- 238000004804 winding Methods 0.000 abstract description 12
- 239000003507 refrigerant Substances 0.000 description 7
- 230000003247 decreasing effect Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
- F04D29/462—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps
- F04D29/464—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps adjusting flow cross-section, otherwise than by using adjustable stator blades
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2250/00—Geometry
- F05D2250/50—Inlet or outlet
- F05D2250/51—Inlet
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2260/00—Function
- F05D2260/14—Preswirling
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
(57)【要約】
【課題】 構造を簡単にする。気体流の合流時の損失を
低減する。
【解決手段】 入口管４から回転中の羽根車２に流入す
る気体流に羽根車２と同一方向の旋回を与える遠心圧縮
機の旋回流発生装置１１において、入口管４を主管１２
と副管１３に分岐し、主管１２を直管にして羽根車２の
入口に接続し、副管１３を主管１２に巻き付けてその巻
き付け部１４を主管１２に接続し、巻き付け部１４を流
れる気体流を主管１２の回りを旋回させつつ主管１２に
流入させ、巻き付け部１４から主管１２に流入する気体
流を、主管１２の下流側に偏向させて、主管１２の軸芯
との間の角度α1，α2が鋭角になる向きにし、主管１２
の流量を増加（または減少）させると副管１３の流量が
減少（または増加）する流量制御弁１６，１７を設け
た。
(57) [Summary] [Problem] To simplify the structure. Reduces loss when gas flows merge. SOLUTION: In a swirl flow generating device 11 of a centrifugal compressor which gives a gas flow flowing from an inlet pipe 4 to a rotating impeller 2 in the same direction as the impeller 2, the inlet pipe 4 is connected to a main pipe 12.
And the main pipe 12 is connected to the inlet of the impeller 2, the sub pipe 13 is wound around the main pipe 12, the wrapped portion 14 is connected to the main pipe 12, and the gas flowing through the wrapped section 14 The gas flows into the main pipe 12 while swirling around the main pipe 12, and the gas flow flowing into the main pipe 12 from the winding portion 14 is deflected to the downstream side of the main pipe 12, and the angle α between the main pipe 12 and the axis of the main pipe 12 is adjusted. 1 and α 2 are oriented so that they are acute angles.
The flow control valves 16 and 17 are provided so that the flow rate of the sub pipe 13 decreases (or increases) when the flow rate of the auxiliary pipe 13 increases (or decreases).
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、遠心圧縮機におい
て、気体流が回転中の羽根車に流入する際に発生する損
失を低減するため、回転中の羽根車に流入する気体流に
羽根車と同一方向の旋回を与える旋回流発生装置に関す
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a centrifugal compressor, in which a gas flow flowing into a rotating impeller is reduced in order to reduce a loss generated when the gas flow flows into the rotating impeller. The present invention relates to a swirl flow generating device that gives a swirl in the same direction as the swirl flow.
【０００２】[0002]
＜第１従来例＞ターボチャージャ用遠心圧縮機の旋回流
発生装置は、特願平８−１８０５１２号と特願平９−１
４７３５９号に開示されているように、羽根車と同芯状
の空気入口に複数枚の案内羽根を羽根車の軸芯方向から
の傾斜角度を調整可能に設けている。空気流量が少なく
なるエンジンの低速域では、案内羽根の傾斜角度を大き
くして、回転中の羽根車に流入する空気流に羽根車と同
一方向の大きな旋回を与える。空気流量が多くなるエン
ジンの高速域では、案内羽根の傾斜角度を小さくし、ま
たは、零にして、回転中の羽根車に流入する空気流に羽
根車と同一方向の小さな旋回を与え、または、旋回を与
えない。<First Conventional Example> Japanese Patent Application Nos. 8-180512 and 9-1 describe a swirling flow generator for a centrifugal compressor for a turbocharger.
As disclosed in Japanese Patent No. 47359, a plurality of guide blades are provided at an air inlet concentric with the impeller so as to adjust the inclination angle of the impeller from the axial center direction. In the low-speed range of the engine where the air flow rate decreases, the inclination angle of the guide blade is increased to give the air flow flowing into the rotating impeller a large turn in the same direction as the impeller. In the high-speed region of the engine where the air flow rate is large, the inclination angle of the guide blade is reduced or set to zero to give the air flow flowing into the rotating impeller a small turn in the same direction as the impeller, or Does not give a turn.
【０００３】＜第２従来例＞冷凍機用遠心圧縮機の旋回
流発生装置は、特開平７−１７４０９８号に開示されて
いるように、羽根車と同芯状の入口管にその周方向に沿
って流入管の先端を接続し、流入管の末端を羽根車の出
口、ディフューザの出口またはスクロールに接続してい
る。冷凍機の負荷が小さいときに、羽根車の出口、ディ
フューザの出口またはスクロール内の冷媒ガスを流入管
から入口管に流入させて、回転中の羽根車に流入する冷
媒ガス流に羽根車と同一方向の旋回を与える。<Second Conventional Example> As disclosed in Japanese Patent Application Laid-Open No. 7-174098, a swirling flow generating device for a centrifugal compressor for a refrigerator is provided with an inlet pipe concentric with an impeller in a circumferential direction thereof. The end of the inflow pipe is connected to the outlet of the impeller, the outlet of the diffuser or the scroll. When the load on the refrigerator is small, the refrigerant gas in the outlet of the impeller, the outlet of the diffuser or the scroll is caused to flow from the inlet pipe to the inlet pipe, and the refrigerant gas flowing into the rotating impeller is the same as the impeller. Give a turn in the direction.
【０００４】[0004]
【発明が解決しようとする課題】ところが、上記のよう
な第１従来例においては、複数枚の案内羽根の傾斜角度
を制御するので、案内羽根とその傾斜角度を制御する機
構が複雑になって部品点数が多くなる。However, in the first conventional example as described above, since the inclination angles of a plurality of guide blades are controlled, the guide blades and a mechanism for controlling the inclination angle become complicated. The number of parts increases.
【０００５】上記のような第２従来例においては、入口
管をその軸芯方向に流れる冷媒ガス流に、流入管から入
口管に流入する冷媒ガス流が直角に衝突するので、合流
時の損失が大きくなる。また、入口管を流れる冷媒ガス
流の制御と流入管を流れる冷媒ガス流の制御が別々にな
るので、制御機構が複雑になる。In the above-mentioned second conventional example, the refrigerant gas flow flowing from the inlet pipe to the inlet pipe collides with the refrigerant gas flow flowing in the axial direction of the inlet pipe at right angles, so that the loss at the time of merging is reduced. Becomes larger. Further, since the control of the refrigerant gas flow flowing through the inlet pipe and the control of the refrigerant gas flow flowing through the inflow pipe are separated, the control mechanism is complicated.
【０００６】[0006]
【課題を解決するための手段】本発明は、入口管から回
転中の羽根車に流入する空気流や冷媒ガス流のような気
体流に羽根車と同一方向の旋回を与える遠心圧縮機の旋
回流発生装置において、入口管を主管と副管に分岐し、
主管を直管にして羽根車の入口に同芯状に接続し、副管
を主管に巻き付けて副管の巻き付け部を主管に接続し、
副管の巻き付け部を流れる気体流を主管の回りを旋回さ
せつつ主管に流入させ、副管の巻き付け部から主管に流
入する気体流を、主管を流れる気体流の下流側に偏向さ
せて、主管の軸芯との間の角度が鋭角になる向きにし、
主管と副管の接続部上流側位置に、主管の流量を増加さ
せると副管の流量が減少し、主管の流量を減少させると
副管の流量が増加する流量制御弁を設けた。SUMMARY OF THE INVENTION The present invention relates to a centrifugal compressor for rotating a gas flow such as an air flow or a refrigerant gas flow flowing from an inlet pipe into a rotating impeller in the same direction as the impeller. In the flow generator, the inlet pipe is branched into a main pipe and a sub pipe,
The main pipe is made straight and connected concentrically to the inlet of the impeller, the sub pipe is wound around the main pipe, and the winding part of the sub pipe is connected to the main pipe,
The gas flow flowing through the wrapped portion of the sub-pipe is caused to flow into the main pipe while swirling around the main pipe, and the gas flow flowing from the wrapped portion of the sub-pipe into the main pipe is deflected to the downstream side of the gas flow flowing through the main pipe. The angle between the axis and the
A flow control valve is provided at a position upstream of the connection between the main pipe and the sub pipe, in which the flow rate of the sub pipe decreases when the flow rate of the main pipe increases, and the flow rate of the sub pipe increases when the flow rate of the main pipe decreases.
【０００７】入口管の流量が多いときには、流量制御弁
で、主管の流量を増加させて副管の流量を減少させる。
すると、羽根車に流入する気体流に与えられる旋回が小
さくなる。When the flow rate of the inlet pipe is high, the flow rate of the main pipe is increased and the flow rate of the sub pipe is decreased by the flow control valve.
Then, the turning given to the gas flow flowing into the impeller becomes smaller.
【０００８】逆に、入口管の流量が少ないときには、流
量制御弁で、主管の流量を減少させて副管の流量を増加
させる。すると、羽根車に流入する気体流に与えられる
旋回が大きくなる。Conversely, when the flow rate of the inlet pipe is small, the flow rate of the main pipe is reduced and the flow rate of the sub pipe is increased by the flow control valve. Then, the turning given to the gas flow flowing into the impeller increases.
【０００９】[0009]
【発明の効果】本発明においては、主管と副管及び流量
制御弁で構成されるので、構造が簡単になる。According to the present invention, the structure is simplified since it is composed of the main pipe, the sub pipe, and the flow control valve.
【００１０】また、副管から主管に流入する気体流が、
主管を流れる気体流の下流側に偏向していて、副管の気
体流が主管の気体流に鋭角に衝突するので、合流時の損
失が大きくならない。Further, the gas flow flowing from the sub pipe to the main pipe is:
Since the gas flow flowing through the main pipe is deflected to the downstream side and the gas flow of the sub pipe collides with the gas flow of the main pipe at an acute angle, the loss at the time of merging does not increase.
【００１１】[0011]
【発明の実施の形態】ターボチャージャ用遠心圧縮機
は、図１に示すように、ケーシング１の中央部に羽根車
２を入れ、羽根車２の軸３をケーシング１の後部に軸受
し、ケーシング１の前部に空気入口管４を接続し、ケー
シング１の外周部にディフューザ５とスクロール６を内
外に同芯状に設けている。スクロール６の大径部には、
図示しないが、空気出口管を接続している。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS In a centrifugal compressor for a turbocharger, as shown in FIG. 1, an impeller 2 is placed in the center of a casing 1 and a shaft 3 of the impeller 2 is bearing at a rear portion of the casing 1. An air inlet pipe 4 is connected to a front portion of the casing 1, and a diffuser 5 and a scroll 6 are provided concentrically inside and outside the outer periphery of the casing 1. In the large diameter part of the scroll 6,
Although not shown, an air outlet tube is connected.
【００１２】羽根車２は、図１に示すように、円盤形状
の主板７の中心部に軸３を貫通して固定し、主板７の前
面に湾曲板形状の羽根８を等間隔位置にほぼ径方向に沿
って固定している。As shown in FIG. 1, the impeller 2 is fixed to the center of a disk-shaped main plate 7 by penetrating the shaft 3, and a curved plate-shaped blade 8 is provided on the front surface of the main plate 7 at substantially equal intervals. It is fixed along the radial direction.
【００１３】エンジンの吸気通路を流れる空気は、遠心
圧縮機の空気入口管４から回転中の羽根車２の前面の入
口に流入し、羽根車２の羽根８の間の湾曲通路を通っ
て、羽根車２の外周の出口からディフューザ５を経てス
クロール６に流入し、高圧になった空気がスクロール６
の空気出口管からエンジンのシリンダに流入する。エン
ジンの排気通路を流れる排気ガスは、タービンを回転
し、タービンが遠心圧縮機を回転させる。The air flowing through the intake passage of the engine flows from the air inlet pipe 4 of the centrifugal compressor into the front inlet of the rotating impeller 2, passes through the curved passage between the blades 8 of the impeller 2, The high-pressure air flows into the scroll 6 from the outlet on the outer periphery of the impeller 2 via the diffuser 5 and becomes high-pressure.
From the air outlet tube of the engine into the cylinder of the engine. The exhaust gas flowing through the exhaust passage of the engine rotates the turbine, and the turbine rotates the centrifugal compressor.
【００１４】遠心圧縮機は、図１に示すように、空気入
口管４に、回転中の羽根車２に流入する空気流に羽根車
２と同一方向の旋回を与える旋回流発生装置１１を旋回
量調整可能に設けている。As shown in FIG. 1, the centrifugal compressor swirls a swirl flow generating device 11 in the air inlet pipe 4 to give a swirl of air flowing into the rotating impeller 2 in the same direction as the impeller 2. It is provided so that the amount can be adjusted.
【００１５】旋回流発生装置１１は、図１に示すよう
に、空気入口管４の下流側部分を主管１２と副管１３に
分岐している。As shown in FIG. 1, the swirling flow generator 11 branches a downstream portion of the air inlet pipe 4 into a main pipe 12 and a sub pipe 13.
【００１６】主管１２は、円筒形状の直管にして、ケー
シング１の前部に羽根車２と同芯状に接続している。The main pipe 12 is a cylindrical straight pipe, and is connected to the front part of the casing 1 concentrically with the impeller 2.
【００１７】副管１３は、図１〜図３に示すように、そ
の下流側部分を先細形状にして主管１２の途中に巻き付
け、主管１２と直交する面内で円環形状に湾曲したその
巻き付け部１４の内周の主管１２下流側部分を主管１２
の途中の周囲に接続して連通している。As shown in FIGS. 1 to 3, the sub-tube 13 has a tapered downstream portion and is wound around the main tube 12, and is wound in an annular shape in a plane perpendicular to the main tube 12. The downstream portion of the main pipe 12 on the inner periphery of the portion 14 is
It is connected and connected around the middle of.
【００１８】副管１３の巻き付け部１４を流れる空気流
は、図２に矢印で示すように、主管１２の回りを旋回し
つつ主管１２に流入する。The air flow flowing through the winding portion 14 of the sub pipe 13 flows into the main pipe 12 while turning around the main pipe 12, as indicated by arrows in FIG.
【００１９】副管１３の巻き付け部１４を流れる空気流
は、主管１２の回りを旋回するに従って、主管１２に流
入した分ずつ流量が減少するが、先細形状の巻き付け部
１４の断面積も減少するので、巻き付け部１４の位置に
拘らず、旋回速度がほぼ一定になる。巻き付け部１４か
ら主管１２に流入する空気流も、主管１２の周方向位置
に拘らず、流入速度がほぼ一定になる。As the air flow flowing through the winding portion 14 of the sub-tube 13 turns around the main tube 12, the flow rate decreases by the amount of the air flowing into the main tube 12, but the cross-sectional area of the tapering winding portion 14 also decreases. Therefore, regardless of the position of the winding portion 14, the turning speed becomes substantially constant. The flow rate of the air flowing from the winding portion 14 into the main pipe 12 is substantially constant regardless of the circumferential position of the main pipe 12.
【００２０】副管１３の巻き付け部１４と主管１２の連
通部１５が巻き付け部１４の中心面位置から主管１２の
下流側に偏在しているので、副管１３の巻き付け部１４
から主管１２に流入する空気流は、図１に示すように、
主管１２の下流側に偏向し、主管１２の軸芯との間の角
度α1，α2が鋭角になる向きになる。副管１３の巻き付
け部１４から主管１２に流入する空気流が、主管１２を
その軸芯方向に流れる空気流に鋭角に衝突するので、合
流時の損失が小さい。Since the winding portion 14 of the auxiliary pipe 13 and the communicating portion 15 of the main pipe 12 are unevenly distributed from the center plane position of the winding portion 14 to the downstream side of the main pipe 12, the winding portion 14 of the auxiliary pipe 13
As shown in FIG.
The light is deflected to the downstream side of the main pipe 12, and the angles α 1 and α 2 between the main pipe 12 and the axis of the main pipe 12 become acute angles. The airflow flowing into the main pipe 12 from the winding portion 14 of the sub pipe 13 collides with the airflow flowing through the main pipe 12 in the axial direction at an acute angle, so that the loss at the time of merging is small.
【００２１】主管１２と副管１３は、図１に示すよう
に、それぞれ、その上流側部分を先細形状にし、最大径
になる入口に流量制御弁１６，１７を設けている。As shown in FIG. 1, each of the main pipe 12 and the sub pipe 13 has a tapered upstream portion, and flow rate control valves 16 and 17 are provided at inlets where the diameters thereof become maximum.
【００２２】流量制御弁１６，１７は、空気流の速度が
低くなる主管１２，副管１３の最大断面積部分に設けて
いるので、流量制御弁１６，１７の存在による主管１
２，副管１３の圧力損失が小さい。Since the flow control valves 16 and 17 are provided at the maximum cross-sectional areas of the main pipe 12 and the sub-pipe 13 where the speed of the air flow is low, the main pipe 1 is provided by the presence of the flow control valves 16 and 17.
2. The pressure loss of the auxiliary pipe 13 is small.
【００２３】主管１２の流量制御弁１６と副管１３の流
量制御弁１７は、連動していて、一方の開度を増加（ま
たは減少）させると他方の開度が減少（または増加）す
る。The flow control valve 16 of the main pipe 12 and the flow control valve 17 of the sub pipe 13 are linked, and when one opening is increased (or decreased), the other is decreased (or increased).
【００２４】図４に示すように、空気入口管４の流量が
多いときには、主管１２の弁１６の開度を増加して、主
管１２の流量を増加させると共に、副管１３の弁１７の
開度を減少して、副管１３の流量を減少させる。する
と、回転中の羽根車２に流入する空気流に与えられる旋
回が小さくなる。As shown in FIG. 4, when the flow rate of the air inlet pipe 4 is high, the opening of the valve 16 of the main pipe 12 is increased to increase the flow rate of the main pipe 12 and to open the valve 17 of the sub pipe 13. The flow rate of the auxiliary pipe 13 is reduced by decreasing the degree. Then, the turning given to the airflow flowing into the rotating impeller 2 becomes smaller.
【００２５】逆に、空気入口管４の流量が少ないときに
は、主管１２の弁１６の開度を減少して、主管１２の流
量を減少させると共に、副管１３の弁１７の開度を増加
して、副管１３の流量を増加させる。すると、回転中の
羽根車２に流入する空気流に与えられる旋回が大きくな
る。Conversely, when the flow rate of the air inlet pipe 4 is small, the opening degree of the valve 16 of the main pipe 12 is reduced to decrease the flow rate of the main pipe 12 and increase the opening degree of the valve 17 of the sub pipe 13. Thus, the flow rate of the sub pipe 13 is increased. Then, the turning given to the airflow flowing into the rotating impeller 2 increases.
【００２６】＜変形例＞ １）上記の実施形態においては、副管１３の巻き付け部
１４は、円環形状であるが、螺旋形状にする。<Modifications> 1) In the above embodiment, the winding portion 14 of the sub-tube 13 has an annular shape, but has a spiral shape.
【００２７】２）上記の実施形態においては、主管１２
と副管１３の流量制御弁１６，１７は、２個の弁からな
るが、１個の弁にする。2) In the above embodiment, the main pipe 12
The flow control valves 16 and 17 of the sub-pipe 13 consist of two valves, but they are one valve.
【図１】本発明の実施形態の旋回流発生装置を備えたタ
ーボチャージャ用遠心圧縮機の縦断側面図。FIG. 1 is a vertical sectional side view of a centrifugal compressor for a turbocharger provided with a swirling flow generator according to an embodiment of the present invention.
【図２】図１のＡ−Ａ線断面図。FIG. 2 is a sectional view taken along line AA of FIG.
【図３】同旋回流発生装置の主管と副管の接続部分の平
面図。FIG. 3 is a plan view of a connection portion between a main pipe and a sub pipe of the swirling flow generating device.
【図４】同旋回流発生装置の主管の弁と副管の弁の開度
と空気入口管の流量の関係を示す線図。FIG. 4 is a diagram showing a relationship between the opening of a main pipe valve and a sub pipe valve of the swirling flow generating device and the flow rate of an air inlet pipe.
２ 羽根車 ４ 空気入口管 １１ 旋回流発生装置 １２ 主管 １３ 副管 １４ 巻き付け部 １６，１７ 流量制御弁 α1，α2 巻き付け部から主管に流入する空気流と主管
の軸芯の間の角度The angle between the two impellers 4 axis of the air inlet pipe 11 swirl flow generating device 12 main 13 secondary pipe 14 wound portions 16 and 17 flow control valve alpha 1, main air flow into the main pipe from the alpha 2 wrappings
Claims (1)
体流に羽根車と同一方向の旋回を与える遠心圧縮機の旋
回流発生装置において、 入口管を主管と副管に分岐し、主管を直管にして羽根車
の入口に同芯状に接続し、副管を主管に巻き付けて副管
の巻き付け部を主管に接続し、副管の巻き付け部を流れ
る気体流を主管の回りを旋回させつつ主管に流入させ、 副管の巻き付け部から主管に流入する気体流を、主管を
流れる気体流の下流側に偏向させて、主管の軸芯との間
の角度が鋭角になる向きにし、 主管と副管の接続部上流側位置に、主管の流量を増加さ
せると副管の流量が減少し、主管の流量を減少させると
副管の流量が増加する流量制御弁を設けたことを特徴と
する遠心圧縮機の旋回流発生装置。A swirl flow generator for a centrifugal compressor for imparting a swirl in the same direction as an impeller to a gas flow flowing into a rotating impeller from an inlet pipe, wherein the inlet pipe is branched into a main pipe and a sub pipe. Into a straight pipe, concentrically connected to the inlet of the impeller, wrapping the sub-pipe around the main pipe, connecting the wrapped part of the sub-pipe to the main pipe, and turning the gas flow flowing through the wrapped part of the sub-pipe around the main pipe The gas flow flowing into the main pipe from the wrapped portion of the sub pipe is deflected to the downstream side of the gas flow flowing through the main pipe so that the angle between the main pipe and the axis becomes an acute angle, At the upstream side of the connection between the main pipe and the sub pipe, a flow control valve is provided that increases the flow rate of the main pipe, decreases the flow rate of the sub pipe, and decreases the flow rate of the main pipe, increases the flow rate of the sub pipe. Centrifugal compressor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9159380A JPH116500A (en) | 1997-06-17 | 1997-06-17 | Centrifugal compressor swirl generator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9159380A JPH116500A (en) | 1997-06-17 | 1997-06-17 | Centrifugal compressor swirl generator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH116500A true JPH116500A (en) | 1999-01-12 |
Family
ID=15692554
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP9159380A Pending JPH116500A (en) | 1997-06-17 | 1997-06-17 | Centrifugal compressor swirl generator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH116500A (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2391265A (en) * | 2002-07-13 | 2004-02-04 | Imra Europ S A Uk Res Ct | Compressor inlet with swirl vanes, inner sleeve and shut-off valve |
| WO2005100798A1 (en) * | 2004-04-13 | 2005-10-27 | Integral Powertrain Ltd | A pre-whirl generator, a compressor and a method of imparting pre-whirl to a gas flow |
| US7343742B2 (en) * | 2004-08-24 | 2008-03-18 | Bayerische Motoren Werke Aktiengesellschaft | Exhaust turbocharger |
| EP2067958A3 (en) * | 2007-12-04 | 2009-11-25 | Mann+Hummel Gmbh | Exhaust gas turbocharger for a combustion engine and device to switch an air guidance device of an exhaust gas turbocharger |
| JP2011111988A (en) * | 2009-11-27 | 2011-06-09 | Toyota Central R&D Labs Inc | Supercharging engine system |
| GB2490563A (en) * | 2011-05-03 | 2012-11-07 | Peter John Bayram | Pre-rotating or de-rotating fluid flow with a volute |
| JP2013076365A (en) * | 2011-09-30 | 2013-04-25 | Ihi Corp | Centrifugal compressor, and vehicle supercharger |
| EP2682592A3 (en) * | 2012-07-06 | 2014-07-02 | Kabushiki Kaisha Toyota Jidoshokki | Intake air supply structures of turbo superchargers |
| US20160238013A1 (en) * | 2013-10-02 | 2016-08-18 | Continental Automotive Gmbh | Compressor with Variable Compressor Inlet |
| US20170284421A1 (en) * | 2016-04-04 | 2017-10-05 | Ford Global Technologies, Llc | Active swirl device for turbocharger compressor |
-
1997
- 1997-06-17 JP JP9159380A patent/JPH116500A/en active Pending
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2391265A (en) * | 2002-07-13 | 2004-02-04 | Imra Europ S A Uk Res Ct | Compressor inlet with swirl vanes, inner sleeve and shut-off valve |
| WO2005100798A1 (en) * | 2004-04-13 | 2005-10-27 | Integral Powertrain Ltd | A pre-whirl generator, a compressor and a method of imparting pre-whirl to a gas flow |
| US7343742B2 (en) * | 2004-08-24 | 2008-03-18 | Bayerische Motoren Werke Aktiengesellschaft | Exhaust turbocharger |
| EP2067958A3 (en) * | 2007-12-04 | 2009-11-25 | Mann+Hummel Gmbh | Exhaust gas turbocharger for a combustion engine and device to switch an air guidance device of an exhaust gas turbocharger |
| US8156741B2 (en) | 2007-12-04 | 2012-04-17 | Mann + Hummel Gmbh | Exhaust gas turbocharger for an internal combustion engine and device for switching an air guiding device of an exhaust gas turbocharger |
| JP2011111988A (en) * | 2009-11-27 | 2011-06-09 | Toyota Central R&D Labs Inc | Supercharging engine system |
| GB2490563A (en) * | 2011-05-03 | 2012-11-07 | Peter John Bayram | Pre-rotating or de-rotating fluid flow with a volute |
| GB2490563B (en) * | 2011-05-03 | 2015-07-22 | Peter John Bayram | Spiral energy recovery and flow pre-rotation for turbochargers, turbo-expansion valves, turbojets and marine propellers, etc |
| JP2013076365A (en) * | 2011-09-30 | 2013-04-25 | Ihi Corp | Centrifugal compressor, and vehicle supercharger |
| EP2682592A3 (en) * | 2012-07-06 | 2014-07-02 | Kabushiki Kaisha Toyota Jidoshokki | Intake air supply structures of turbo superchargers |
| US20160238013A1 (en) * | 2013-10-02 | 2016-08-18 | Continental Automotive Gmbh | Compressor with Variable Compressor Inlet |
| US20170284421A1 (en) * | 2016-04-04 | 2017-10-05 | Ford Global Technologies, Llc | Active swirl device for turbocharger compressor |
| US9932991B2 (en) * | 2016-04-04 | 2018-04-03 | Ford Global Technologies, Llc | Active swirl device for turbocharger compressor |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US7775759B2 (en) | Centrifugal compressor with surge control, and associated method | |
| US8690522B2 (en) | Multistage compressor with improved map width performance | |
| CN105909319B (en) | Turbocharger diffuser center body | |
| JP5451247B2 (en) | Turbocharger connection for reverse rotation of passive pre-turn | |
| US4315715A (en) | Diffuser for fluid impelling device | |
| US10087824B2 (en) | Wastegate with injected flow | |
| JP2004332733A (en) | Compressor | |
| US7305827B2 (en) | Inlet duct for rearward-facing compressor wheel, and turbocharger incorporating same | |
| US20070269308A1 (en) | Engine intake air compressor having multiple inlets and method | |
| JPH09310699A (en) | Centrifugal compressor | |
| JPH0861084A (en) | Gas turbine engine and diffuser for gas turbine engine | |
| WO2018146753A1 (en) | Centrifugal compressor and turbocharger | |
| JPH116500A (en) | Centrifugal compressor swirl generator | |
| EP0635644B1 (en) | Inlet guide vane dewhistler | |
| CA3082693A1 (en) | Diffuser pipe with axially-directed exit | |
| US10823195B2 (en) | Diffuser pipe with non-axisymmetric end wall | |
| JP2021095882A (en) | Centrifugal compressor | |
| EP3789618A1 (en) | Compressor with ported shroud for flow recirculation and with noise attenuator for blade passing frequency noise attenuation, and turbocharger incorporating same | |
| JPH10339152A (en) | Centrifugal compressor for turbo charger | |
| JP2000120442A (en) | Variable displacement turbocharger | |
| JP3033902B1 (en) | Turbocharger compressor | |
| Jiang et al. | Investigation of vaned diffusers as a variable geometry device for application to turbocharger compressors | |
| JPH10141074A (en) | Variable displacement exhaust turbo supercharger | |
| JPH10331792A (en) | Structure of centrifugal compressor suction section | |
| JP2022548709A (en) | Concentric introduction of wastegate mass flow into a flow-optimized axial diffuser |