JPH0214970B2 - - Google Patents
Info
- Publication number
- JPH0214970B2 JPH0214970B2 JP58232699A JP23269983A JPH0214970B2 JP H0214970 B2 JPH0214970 B2 JP H0214970B2 JP 58232699 A JP58232699 A JP 58232699A JP 23269983 A JP23269983 A JP 23269983A JP H0214970 B2 JPH0214970 B2 JP H0214970B2
- Authority
- JP
- Japan
- Prior art keywords
- nozzle
- turbine
- blades
- exhaust
- area
- 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.)
- Expired - Lifetime
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D17/00—Regulating or controlling by varying flow
- F01D17/10—Final actuators
- F01D17/12—Final actuators arranged in stator parts
- F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
- F01D17/16—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes
- F01D17/165—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes for radial flow, i.e. the vanes turning around axes which are essentially parallel to the rotor centre line
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/24—Control of the pumps by using pumps or turbines with adjustable guide vanes
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Supercharger (AREA)
- Control Of Turbines (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は内燃機関の排気タービン過給機に関す
るものである。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to an exhaust turbine supercharger for an internal combustion engine.
内燃機関の排気ガスを導入してタービン羽根を
駆動して、その排気ガスのエネルギーを有効に回
収する従来の排気タービン過給機は、そのノズル
羽根が固定式になつており、その内燃機関の高出
力時においてのみ排気ガスのエネルギーの回収が
可能であり、低出力の中低速時にはタービン効率
が低下してエネルギーの回収が充分には行なわれ
ないという問題があつた。
Conventional exhaust turbine superchargers introduce exhaust gas from an internal combustion engine to drive turbine blades and effectively recover energy from the exhaust gas. There is a problem in that exhaust gas energy can be recovered only at high outputs, and at low outputs and medium to low speeds, turbine efficiency decreases and energy recovery is not sufficient.
そこで、実開昭58−90326のごとく、機関出力
の低い時にもタービンのノズル羽根の面積を変更
することにより、排気ガスエネルギーの回収を良
好にしようとした考案がなされているが、この場
合、タービンノズル部での流速の向上、方向性の
向上等により若干の改善はなされるが、回転する
タービン羽根の羽根通路面積は排気エネルギー大
のままであるため、効率の改善が少ないという問
題がある。 Therefore, as in Utility Model Application No. 58-90326, an idea has been made to improve the recovery of exhaust gas energy by changing the area of the turbine nozzle blade even when the engine output is low, but in this case, Although some improvements can be made by increasing the flow velocity at the turbine nozzle, improving directionality, etc., the blade passage area of the rotating turbine blades remains large in exhaust energy, so there is a problem that the improvement in efficiency is small.
上記のごときノズル羽根の面積を可変とする排
気タービン過給機の従来例としては、第１図の縦
断面図に示すごとく、図示されていない内燃機関
の排気Ｅをタービン羽根２に導入するための複数
のノズル羽根１をノズル回転軸３により回動可能
に支持すると共に、第１図の−方向の側断面
図である第２図に示すごとく各ノズル回転軸３に
それぞれ固定した各ノズル回転レバー４をその外
周に設け、かつ各ノズル回転レバー４と噛合する
リングギヤ５をその内燃機関の出力に応じて外部
から回転させることにより、ノズル羽根１を回転
させてノズル面積を可変にしている。 As shown in the longitudinal cross-sectional view of FIG. 1, a conventional example of an exhaust turbine supercharger in which the area of the nozzle blade is variable as described above is designed to introduce the exhaust gas E of an internal combustion engine (not shown) into the turbine blade 2. A plurality of nozzle blades 1 are rotatably supported by a nozzle rotation shaft 3, and each nozzle rotation shaft is fixed to each nozzle rotation shaft 3 as shown in FIG. 2, which is a side sectional view in the - direction of FIG. A lever 4 is provided on the outer periphery, and a ring gear 5 meshing with each nozzle rotation lever 4 is rotated from the outside according to the output of the internal combustion engine, thereby rotating the nozzle blade 1 and making the nozzle area variable.
一方、過給装置に関する実開昭58−130028号の
考案においては、タービン羽根の通路は２分割さ
れているが、ノズル羽根の面積を可変にするよう
にはなつていない。 On the other hand, in the invention of Utility Model Application Publication No. 58-130028 regarding a supercharging device, the passage of the turbine blade is divided into two, but the area of the nozzle blade is not made variable.
また、特公昭31−4705号及び特公昭38−7653号
の発明のものは、多数のノズル羽根の面積が機関
出力に応じて可変にできるので、機関の中速域の
高出力化がはかれ、機関の中速時においては、ノ
ズル羽根面積が絞られて、流速及び方向が改善さ
れているが、それを回収するタービン羽根の通路
面積は高出力時用の拡大のままになつているの
で、高効率ではない。 In addition, in the inventions of Japanese Patent Publication No. 31-4705 and No. 38-7653, the area of a large number of nozzle blades can be varied according to the engine output, so it is possible to increase the output in the medium speed range of the engine. At medium speeds of the engine, the nozzle blade area is narrowed to improve flow velocity and direction, but the passage area of the turbine blades that collects the flow remains enlarged for high output. , not high efficiency.
更に実開昭58−114844号考案があるが、これは
タービンの外部に設けた抵抗弁である開閉弁で通
路面積を絞つているので、排気ガスの損失が大と
なり、その排気ガスは更にタービンに入ることに
なり、エネルギー損失が更に大きくなる。したが
つて、中低出力時の過給圧の向上や、広範囲な出
力に対応した高い機関効率が得られないという欠
点を有する。 Furthermore, there is a device proposed in Japanese Utility Model Application Publication No. 58-114844, but this restricts the passage area with an on-off valve, which is a resistance valve, installed outside the turbine, resulting in a large loss of exhaust gas, and the exhaust gas is further transferred to the turbine. This results in even greater energy loss. Therefore, it has the disadvantage that it is not possible to improve the supercharging pressure at medium to low outputs or to obtain high engine efficiency corresponding to a wide range of outputs.
そこで、本発明は前記従来の問題点を解消する
ためになされたものであり、機関の中低速出力時
の過給圧を向上することにより、トルク向上及び
出力向上をはかりうる広範囲の出力に対応して高
い機関効率を維持しうる排気タービン過給機を提
供することを目的としたものである。
Therefore, the present invention was made in order to solve the above-mentioned conventional problems, and by improving the supercharging pressure during engine output at medium and low speeds, it is compatible with a wide range of outputs that can improve torque and output. The purpose of this invention is to provide an exhaust turbine supercharger that can maintain high engine efficiency.
即ち、本発明の排気タービン過給機は、内燃機
関の排気ガスを導入する排気タービン過給機にお
いて、該排気タービン過給機のノズル羽根を、そ
れぞれ２分割して両者を仕切り、各ノズル面積を
可変として調節可能とすると共に、それら２分割
されたノズル羽根にそれぞれ接続するタービン羽
根もノズル羽根に対応して２分割して両者を仕切
つた内燃機関の排気タービン過給機からなる。
That is, in the exhaust turbine supercharger of the present invention, the nozzle blades of the exhaust turbine supercharger are each divided into two parts to partition the two, and the area of each nozzle is is made variable and adjustable, and the turbine blades connected to the two divided nozzle blades are also divided into two corresponding to the nozzle blades to partition the two, and the exhaust turbine supercharger is an exhaust turbine supercharger for an internal combustion engine.
以下図面を参照して本発明の実施例を説明する
が、第３図は本発明の実施例における内燃機関の
排気ターボ過給機のタービン要部縦断面図、第４
図は第３図の−方向の側断面図である。
Embodiments of the present invention will be described below with reference to the drawings. FIG.
The figure is a side sectional view in the - direction of FIG. 3.
この排気タービン過給機のタービンは、第１図
の従来例と同様に、内燃機関の排気ガスＥを導入
するノズル羽根が１Ａ，１Ｂで示すように仕切板
６で相互に仕切られ、２分割に形成されており、
これらノズル羽根１Ａ，１Ｂがそれぞれのノズル
回転軸３Ａ，３Ｂに支持されると共に、ノズル回
転軸３Ａにはノズル回転レバー４Ａが、ノズル回
転軸３Ｂにはノズルレバー４Ｂがそれぞれ固定さ
れ、更に、ノズルレバー４Ａはリングギヤ５Ａに
噛合し、そしてノズルレバー４Ｂはリングギヤ５
Ｂに噛合し、各リングギヤ５Ａ，５Ｂは内燃機関
の出力に対応してそれぞれ単独に外部から回転さ
せられるようになつている。 Similar to the conventional example shown in FIG. 1, the turbine of this exhaust turbine supercharger has nozzle blades for introducing exhaust gas E from an internal combustion engine that are separated from each other by a partition plate 6 as shown by 1A and 1B, and are divided into two parts. It is formed in
These nozzle blades 1A, 1B are supported by respective nozzle rotation shafts 3A, 3B, and a nozzle rotation lever 4A is fixed to the nozzle rotation shaft 3A, and a nozzle lever 4B is fixed to the nozzle rotation shaft 3B. Lever 4A meshes with ring gear 5A, and nozzle lever 4B meshes with ring gear 5.
B, and each ring gear 5A, 5B is adapted to be independently rotated from the outside in response to the output of the internal combustion engine.
また、これらノズル羽根１Ａ，１Ｂに接続する
タービン羽根も、２Ａ，２Ｂで示すように仕切板
７で相互に仕切られ、２分割に形成されている。 Further, the turbine blades connected to these nozzle blades 1A and 1B are also partitioned from each other by a partition plate 7, as shown by 2A and 2B, and are formed into two parts.
上記の構成からなる本発明の排気タービン過給
機では、２分割されたノズル羽根１Ａ，１Ｂはそ
れぞれのノズル面積を可変にしており、リングギ
ヤ５Ａ，５Ｂを同一に回転させると第１図の従来
例の可変ノズル面積のものと同様に、第５図のノ
ズル羽根通路面積とリングギヤ回転角との関係の
Ｘで示すような面積変化となる。
In the exhaust turbine supercharger of the present invention having the above configuration, the two divided nozzle blades 1A and 1B have variable nozzle areas, and when the ring gears 5A and 5B are rotated at the same time, the conventional exhaust turbine supercharger shown in FIG. Similar to the variable nozzle area example, the area changes as shown by X in the relationship between the nozzle blade passage area and the ring gear rotation angle in FIG.
次に、ノズル羽根１Ａまたは１Ｂのいずれか一
方を閉じ、他方を回転制御すると、タービン羽根
２Ａまたは２Ｂのいずれか一方の通路に対しノズ
ル羽根面積を変更したことになり、第１図の従来
例のタービン羽根２の通路の半減した通路に排気
ガスＥを導入したことになる。 Next, when either one of the nozzle blades 1A or 1B is closed and the other is controlled to rotate, the nozzle blade area is changed for the passage of either the turbine blade 2A or 2B, and the conventional example shown in FIG. This means that the exhaust gas E is introduced into the passage of the turbine blade 2, which is reduced in size by half.
そこで、第５図の線図において、ノズル羽根１
Ａの回転による面積を斜線Ａで示しており、ノズ
ル羽根１Ｂの回転による面積を斜線Ｂで示してい
る。 Therefore, in the diagram of Fig. 5, nozzle blade 1
The area due to the rotation of A is shown by a diagonal line A, and the area due to the rotation of the nozzle blade 1B is shown by a diagonal line B.
更に、第６図で示すタービン効率と、リングギ
ヤ回転角との関係線図において、第１図の従来例
の場合とＸの線図に対して、本発明を適用した実
施例においては、ノズル羽根１Ａ及び１Ｂを別々
に制御することにより、線図Ｙで示すごとく排気
ガス量が小さい時にタービン効率が斜線Ｚの部分
だけ向上する。 Furthermore, in the relationship diagram between turbine efficiency and ring gear rotation angle shown in FIG. 6, in contrast to the conventional example in FIG. 1 and the X diagram, in the embodiment to which the present invention is applied, By controlling 1A and 1B separately, when the amount of exhaust gas is small, as shown in the diagram Y, the turbine efficiency is improved by the area indicated by the diagonal line Z.
従つて、本発明の排気タービン過給機を有する
内燃機関では、特に排気ガス量が小さい中低出力
時には、例えば排気タービンの一方のノズル羽根
を大幅に回転させて、その通路を閉じながら、他
方のノズル羽根通路面積を可変とすることによ
り、従来のものに比べてタービン効率が非常に向
上する。
Therefore, in an internal combustion engine having an exhaust turbine supercharger according to the present invention, especially at medium to low power with a small amount of exhaust gas, for example, one nozzle blade of the exhaust turbine is rotated significantly to close the passage while the other nozzle blade is rotated. By making the nozzle blade passage area variable, the turbine efficiency is greatly improved compared to conventional ones.
その結果、機関の中低出力時の過給圧が向上
し、トルク及び出力の向上がはかれ、広範囲な出
力に対応して高い機関効率が得られるという利点
がある。 As a result, the supercharging pressure at medium and low outputs of the engine is improved, torque and output are improved, and there are advantages in that high engine efficiency can be obtained over a wide range of outputs.
以上のように、本発明は排気タービン過給機の
ノズル羽根をそれぞれ２分割して、その間に仕切
りを設け、更にそれらの２分割したノズル羽根の
それぞれを別々に各ノズル面積を可変するように
調節可能としたために、各ノズル面積の変化を微
調節でき、タービン効率を大いに向上させること
ができるだけでなく、前記ノズル羽根に続くター
ビン羽根にもノズル羽根の仕切りに対応した仕切
りを設けたため、一層のタービン効率の向上が可
能となるのである。 As described above, the present invention divides the nozzle blades of the exhaust turbine supercharger into two parts, provides a partition between them, and further changes the nozzle area of each of the two divided nozzle blades separately. Because it is adjustable, it is possible to fine-tune changes in the area of each nozzle, which not only greatly improves turbine efficiency, but also because the turbine blades following the nozzle blades are provided with partitions that correspond to the partitions of the nozzle blades, making it even more efficient. This makes it possible to improve turbine efficiency.
なお、本発明はターボコンパウンド機関の排気
エネルギー回収タービンに対しても有効に適用す
ることができる。 Note that the present invention can also be effectively applied to an exhaust energy recovery turbine of a turbo compound engine.
第１図は従来の内燃機関の排気ターボ過給機の
タービン要部縦断面図、第２図は第１図の−
方向の側断面図、第３図は本発明の実施例におけ
る内燃機関の排気ターボ過給機のタービン要部縦
断面図、第４図は第３図の−方向の側断面
図、第５図はノズル羽根通路面積とリングギヤ回
転角との関係線図、第６図はタービン効率とリン
グギヤ回転角との関係線図である。
１，１Ａ，１Ｂ……ノズル羽根、２，２Ａ，２
Ｂ……タービン羽根、４，４Ａ，４Ｂ……ノズル
回転レバー、５，５Ａ，５Ｂ……リングギヤ、
６，７……仕切板、Ｅ……排気ガス。
Figure 1 is a vertical cross-sectional view of the main part of the turbine of an exhaust turbocharger for a conventional internal combustion engine, and Figure 2 is a -
3 is a longitudinal sectional view of a main part of a turbine of an exhaust turbocharger for an internal combustion engine according to an embodiment of the present invention; FIG. 4 is a side sectional view in the − direction of FIG. 3; FIG. 6 is a diagram showing the relationship between the nozzle blade passage area and the rotation angle of the ring gear, and FIG. 6 is a diagram showing the relationship between the turbine efficiency and the rotation angle of the ring gear. 1, 1A, 1B... Nozzle blade, 2, 2A, 2
B... Turbine blade, 4, 4A, 4B... Nozzle rotation lever, 5, 5A, 5B... Ring gear,
6, 7... Partition plate, E... Exhaust gas.
Claims (1)
過給機において、該排気タービン過給機のノズル
羽根を、それぞれ２分割して両者を仕切り、各ノ
ズル面積を可変として調節可能とすると共に、そ
れら２分割されたノズル羽根にそれぞれ接続する
タービン羽根もノズル羽根に対応して２分割して
両者を仕切つたことを特徴とする内燃機関の排気
タービン過給機。1. In an exhaust turbine supercharger that introduces exhaust gas from an internal combustion engine, the nozzle blades of the exhaust turbine supercharger are each divided into two parts to partition the two, and the area of each nozzle is variable and adjustable. An exhaust turbine supercharger for an internal combustion engine, characterized in that turbine blades connected to the divided nozzle blades are also divided into two corresponding to the nozzle blades to partition the two.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP58232699A JPS60125727A (en) | 1983-12-12 | 1983-12-12 | Exhaust turbocharger for use in internal-combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP58232699A JPS60125727A (en) | 1983-12-12 | 1983-12-12 | Exhaust turbocharger for use in internal-combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60125727A JPS60125727A (en) | 1985-07-05 |
| JPH0214970B2 true JPH0214970B2 (en) | 1990-04-10 |
Family
ID=16943383
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP58232699A Granted JPS60125727A (en) | 1983-12-12 | 1983-12-12 | Exhaust turbocharger for use in internal-combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60125727A (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH01227803A (en) * | 1988-03-08 | 1989-09-12 | Honda Motor Co Ltd | Variable capacity turbine |
| EP1710415A1 (en) * | 2005-04-04 | 2006-10-11 | ABB Turbo Systems AG | Multiple step turbocharging |
| JP2013104335A (en) * | 2011-11-11 | 2013-05-30 | Mitsubishi Heavy Ind Ltd | Radial turbine wheel |
| KR101915092B1 (en) * | 2012-04-27 | 2018-11-06 | 보르그워너 인코퍼레이티드 | Exhaust-gas turbocharger |
| GB2514789B (en) * | 2013-06-04 | 2017-03-29 | Jaguar Land Rover Ltd | Exhaust turbocharger having different turbine geometries for separate exhaust streams |
| WO2015048238A1 (en) * | 2013-09-30 | 2015-04-02 | Borgwarner Inc. | Actuating mechanism and gear driven adjustment ring for a variable geometry turbocharger |
| DE102014215885B3 (en) * | 2014-08-11 | 2015-12-31 | Ford Global Technologies, Llc | Supercharged internal combustion engine with mixed-flow turbine |
| KR102567540B1 (en) * | 2016-05-03 | 2023-08-16 | 한화파워시스템 주식회사 | Turbine |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58114844U (en) * | 1982-01-30 | 1983-08-05 | いすゞ自動車株式会社 | supercharging device |
-
1983
- 1983-12-12 JP JP58232699A patent/JPS60125727A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS60125727A (en) | 1985-07-05 |
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