CN109026177B - Variable-section turbocharger with variable vane track - Google Patents
Variable-section turbocharger with variable vane track Download PDFInfo
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- CN109026177B CN109026177B CN201810972308.0A CN201810972308A CN109026177B CN 109026177 B CN109026177 B CN 109026177B CN 201810972308 A CN201810972308 A CN 201810972308A CN 109026177 B CN109026177 B CN 109026177B
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- Prior art keywords
- shifting fork
- blade
- variable
- fork disc
- circular arc
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Classifications
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- 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
- F01D9/00—Stators
- F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
- F01D9/04—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles forming ring or sector
- F01D9/041—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles forming ring or sector using blades
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- 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
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- 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
- F01D17/167—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes of vanes moving in translation
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- 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
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- 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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Supercharger (AREA)
Abstract
The utility model relates to the field of turbines, and discloses a variable-section turbocharger with a variable blade track, which comprises a turbine box, a rear cover, a shifting fork disc, blades and a blade shaft, wherein a blade seat is arranged between the rear cover and the shifting fork disc, the blades are positioned between the blade seat and the rear cover, and a plurality of radial long strip-shaped through holes are uniformly formed in the blade seat around the center; the outer edge of the first surface of the shifting fork disc is uniformly provided with a plurality of positioning pins, the positioning pins are movably provided with a rocker arm mechanism capable of rotating around the positioning pins, the rocker arm mechanism is formed by sequentially rotating and connecting a plurality of connecting rods, the inner edge of the shifting fork disc is uniformly provided with a plurality of circular arc grooves penetrating through the shifting fork disc, the central axis of each circular arc groove is intersected with the center of the shifting fork disc, the circular arc grooves are in one-to-one correspondence with the radial strip-shaped through holes, and a blade shaft sequentially penetrates through the radial strip-shaped through holes and the circular arc grooves and is fixedly connected with the other end of the rocker arm mechanism; the shifting fork plate is connected with a driving piece for driving the shifting fork plate to rotate. The long strip-shaped through holes are matched with the circular arc grooves, and the blades can rotate around the blade shafts and can also move along the radial direction of the turbocharger.
Description
Technical Field
The utility model belongs to the technical field of turbochargers, and particularly relates to a variable-section turbocharger with variable blade tracks.
Background
Turbochargers are now widely used in various types of diesel and gasoline engines as an important component of the engine. With the increasingly stricter emission regulations, the requirements of users on the economy and the dynamic performance of the engine are continuously improved, and various novel supercharging technologies are continuously applied to the engine. Among them, the variable section supercharging technology is an effective method for meeting the emission and performance requirements of engines, and is widely used in the global diesel engine market.
At present, two variable cross-section turbocharging technologies of various large companies are mainly adopted, one of the variable cross-section turbocharging technologies is a rotary vane structure, a plurality of rotary vanes are arranged between a turbine shell runner and a turbine rotor, and the vanes are controlled to rotate at a low speed of an engine, so that vane airflow channels are reduced; the vane is controlled to rotate at high speed to increase the vane airflow passage and prevent over-high pressure and overspeed. The other is a movable vane structure, the vane is not rotated around a pivot, but is fixed on a whole base body, and various mechanisms are adopted to push the vane to move axially, so that the size of an exhaust gas channel entering the turbine is controlled. Both methods can meet the requirement of increasing the boost pressure of the engine at low speed and maintaining proper rated power at high speed to a certain extent, and can well meet the requirement of recycling the exhaust gas of the engine.
However, as emissions escalation and engine performance increase, matching variable-section superchargers to engines is also increasingly difficult. The variable cross section can achieve the function of regulating pressure by regulating the angle or opening of the vanes, but the efficiency of the whole turbine can be greatly different at different openings. In general, for rotating blades, the highest turbine efficiency is in the range of 25% -75% of the overall nozzle blade opening, with both too large and too small opening efficiencies. In practical application, when the engine is at low speed, the passage of the variable-section supercharger is required to be closed very small, and when the engine is at high speed, the passage of the variable-section supercharger is required to be opened sufficiently large, and in the two stages, the efficiency of the variable-section supercharger is low, so that a series of problems such as insufficient engine power and poor fuel economy are caused.
Currently, conventional solutions are to optimize turbines, optimize nozzle structures, optimize turbine boxes, etc. by fluid software to improve overall turbine performance and to increase operating range. But is limited to variable section booster constructions, the efficiency improvement is not significant. Chinese patent document CN200720025887.5 discloses a composite nozzle of a variable-section turbocharger, which is provided with a plurality of composite nozzle blades on a nozzle support disc, wherein the nozzle blades consist of moving blades and stationary blades, a rotating shaft is arranged on the blades, and air flow adjustment is realized through the cooperation of the moving blades and the stationary blades, so that the inherent adjustment characteristic of a single pneumatic nozzle of the variable-section turbocharger is solved. The patent still adopts rotary blades, only stator blades are arranged, the blades still only rotate for one movement, and the blades only rotate around the axis, and the positions of the blades are relatively fixed.
Fig. 1 shows a rotary vane variable section supercharger, the vane outlet airflow angle of which can be expressed approximately as:
α3＝arcos(L/S)
wherein: l is the throat width of the nozzle and S is the pitch of the vanes. (see figure 1)
In addition, based on past experimental and design experience, the efficiency of a variable nozzle has a large relationship with the blade-to-turbine inlet distance Δr, which can be estimated using the following equation:
wherein: b3 is the height of the nozzle vane.
From the above, it can be seen that for high efficiency, the nozzle vanes should have a smaller Δr at small openings and a larger Δr at large openings. The current rotary nozzle vanes are opposite, with Δr being larger at small openings and smaller at large openings. This results in the existing rotary nozzle vanes having a better efficiency only at intermediate openings, and a lower efficiency at large or small openings, often only about 40%.
Disclosure of Invention
The utility model aims to overcome the defects in the prior art and provide the variable cross-section turbocharger with the variable vane track, wherein the vane not only can rotate around the vane shaft, but also can radially move around the turbocharger, and the vane can provide a more reasonable airflow angle no matter the vane is in a small opening degree or a large opening degree, so that the overall efficiency is effectively improved.
The technical scheme of the utility model is as follows: the variable-section turbocharger with the variable blade track comprises a turbine box, a rear cover, a shifting fork disc, blades and a blade shaft, wherein the rear cover and the shifting fork disc are arranged in the turbine box; the outer edge of the first surface of the shifting fork disc is uniformly provided with a plurality of locating pins, the locating pins are movably sleeved with a rocker arm mechanism capable of rotating around the locating pins, the rocker arm mechanism is formed by sequentially rotating and connecting a plurality of connecting rods, the inner edge of the shifting fork disc is uniformly provided with a plurality of circular arc grooves penetrating through the shifting fork disc, the central axes of the circular arc grooves intersect at the center of the shifting fork disc, the circular arc grooves are in one-to-one correspondence with the radial strip-shaped through holes, and the blade shafts sequentially penetrate through the radial strip-shaped through holes and the circular arc grooves and are fixedly connected with the other end of the rocker arm mechanism; the shifting fork plate is connected with a driving piece for driving the shifting fork plate to rotate.
The utility model further adopts the technical scheme that: the rocker arm mechanism is connected by two connecting rods.
The utility model further adopts the technical scheme that: the rotating connection between the connecting rods of the rocker mechanism is that cylindrical pins are arranged at the connection positions of the connecting rods.
The utility model further adopts the technical scheme that: the turbine box is provided with a step groove, and a boss matched with the step groove is arranged on the second surface of the shifting fork disc so that the shifting fork disc can conveniently rotate along the step groove.
The utility model further adopts the technical scheme that: the blade seat is provided with a unilateral right-angle groove on the upper surface of the position close to the shifting fork disc boss, and the bottom of the right-angle groove is higher than the lower surface of the shifting fork disc boss; the blade seat is provided with a distance pin penetrating through the blade seat at the right-angle groove, and the other end of the distance pin is fixed on the rear cover.
The utility model further adopts the technical scheme that: the right angle groove is internally provided with a supporting wheel.
The utility model further adopts the technical scheme that: the two ends of the strip-shaped through hole are arc structures matched with the blade shaft.
The utility model further adopts the technical scheme that: the two ends of the arc groove are arc structures matched with the blade shaft.
The utility model further adopts the technical scheme that: the blade shaft is fixedly connected with the other end of the rocker arm mechanism in a welding or riveting mode.
Compared with the prior art, the utility model has the following characteristics:
1. the blade seat is arranged, the strip-shaped through holes are formed in the blade seat, meanwhile, the arc grooves corresponding to the strip-shaped through holes are formed in the shifting fork disc in a one-to-one mode, when the shifting fork disc rotates, the blades can rotate around the blade shaft under the driving of the rocker arm mechanism (the blade shaft) and can also move radially along the turbocharger, and due to the fact that the strip-shaped through holes and the arc grooves are limited by two paths, the blades can have proper radial positions and angles when in different opening degrees, and the variable-section turbocharger has good airflow flowing angles and turbine efficiency when in different opening degrees.
2. The boss is arranged on the shifting fork disk and matched with the step groove on the turbine box, so that the shifting fork disk can not deviate greatly when rotating, and can always rotate around the center.
3. A distance pin is arranged between the blade seat and the rear cover, so that the space between the blade seat and the rear cover is ensured not to prevent the blade from rotating or moving.
4. The blade seat is provided with the unilateral right-angle groove, and the supporting wheel is placed in the rectangular groove formed by the right-angle groove and the shifting fork disc boss, so that the rotation of the shifting fork disc is facilitated on one hand, and the shifting fork disc can be better supported on the other hand.
The detailed structure of the present utility model is further described below with reference to the accompanying drawings and detailed description.
Drawings
Fig. 1 is a schematic diagram of a prior art rotary variable cross-section turbocharger.
Fig. 2 is a partial cross-sectional view of a variable geometry turbocharger with variable vane trajectory as described in example 1.
Fig. 3, 4 and 5 are simulated analysis graphs of flow characteristics and efficiency characteristics of the variable cross-section turbochargers of example 1 and the prior art under conditions where the nozzles are at 25%, 50% and 75% opening, respectively.
Detailed Description
Example 1
The variable-section turbocharger with the variable blade track comprises a turbine box 1, a rear cover 2, a shifting fork disc 3, blades 4 (namely nozzle blades) and a blade shaft 5, wherein the rear cover 2 and the shifting fork disc 3 are arranged in the turbine box, a blade seat 6 is further arranged between the rear cover 2 and the shifting fork disc 3, the blades 4 are arranged between the blade seat 6 and the rear cover 2, in general, the height between the blade seat 6 and the rear cover 2 is slightly larger than the height of the blades 4, and the length of the blade shaft 5 is slightly longer than the distance from the upper surface of the shifting fork disc 3 to the lower surface of the blade seat 6.
The blade seat 6 is uniformly provided with a plurality of radial strip-shaped through holes 61 around the center; the outer edge of the first surface of the shifting fork disc 3 is uniformly fixed with a plurality of positioning pins 31, the free end of each positioning pin 31 is movably sleeved with a rocker arm mechanism capable of rotating around the positioning pin, the rocker arm mechanism is formed by hinging two connecting rods through a pin shaft 71 (the connecting rods are divided into a driving connecting rod 72 and a driven connecting rod 73, the driving connecting rod 72 is connected with the positioning pin 31, the other driven connecting rod 73 is driven by the driving connecting rod 72), and the two connecting rods can rotate around the pin shaft 71; the inner edge of the shifting fork disc 3 is uniformly provided with a plurality of circular arc grooves 32 penetrating through the shifting fork disc, the central axis of each circular arc groove can finally intersect at the center of the shifting fork disc 3, and the circular arc grooves 32 correspond to the radial strip-shaped through holes 61 vertically one by one.
One end of the vane shaft 5 is connected with the vane 4, and the other end sequentially penetrates through the radial strip-shaped through hole 61 and the circular arc groove 32 and is welded or riveted with the end part of the driven connecting rod 73 in the rocker mechanism so that the vane 4 can rotate or move under the drive of the rocker mechanism; the blade seat 6 is fixedly connected with the rear cover 2, the periphery of the shifting fork disc 3 is fixedly connected with a driving piece 7 capable of driving the shifting fork disc to rotate, the driving piece can be a rocker mechanism, only a small force is applied to drive the shifting fork disc to easily rotate around the shaft, the driving piece can also adopt various conventional arrangements in the prior art, and the specific structure of the driving piece does not belong to the utility model point of the utility model, and the description is omitted here.
For better pivoting of the fork disc 3, the turbine housing 1 may be provided with a stepped groove, and the second surface of the fork disc 3 is provided with a boss 33 cooperating with the stepped groove, so that the fork disc rotates along a path set by the stepped groove, and the fork disc does not swing at will, thereby ensuring the working reliability of the turbocharger.
The blade seat 6 is equipped with unilateral formula right angle recess 62 in the upper surface that is close to shift fork dish boss 33 department, and the tank bottom of right angle recess 62 is higher than shift fork dish boss 33 lower surface, has formed a recess that the cross section is rectangular between step groove and the right angle recess 62, and this recess can cooperate with the boss 33 of shift fork dish better, makes the rotation of shift fork dish more standard more accurate.
In order to ensure the mounting stability of the blade holder 6, while ensuring that the mounting of the blade holder does not hinder the rotation or movement of the blade, the blade holder of this embodiment is provided with a distance pin 8 penetrating the blade holder at the right-angle groove 62, and the blade holder 6 is fixed to the rear cover 2 by means of the distance pin 8.
A groove with a rectangular cross section is formed between the right-angle groove 62 of the blade seat and the boss 33 of the shifting fork disc, so that the shifting fork disc is well supported for better positioning, a supporting column 9 can be arranged in the right-angle groove 62, and in order to prevent the supporting column from generating great frequent friction with the rotating shifting fork disc boss, the supporting column 9 of the embodiment adopts a supporting wheel, namely, the shifting fork disc boss can drive the supporting wheel to correspondingly rotate when rotating, so that no relative motion exists between the supporting wheel and the shifting fork disc boss, and the working stability of the shifting fork disc is ensured.
When the shifting fork disc 3 is driven to rotate by the executing piece 7, the blades 4 can move or rotate under the driving of the rocker arm mechanism (the driven connecting rod drives the blade shaft), and due to the mutual cooperation restriction of the two paths of the long strip-shaped through holes 61 and the circular arc grooves 32, the blades 4 can rotate around the blade shaft 5 and can also move radially along the turbocharger, so that the blades can have proper radial positions and angles at different openings, and the variable-section turbocharger has better airflow flowing angles and turbine efficiency at different openings.
In order to enable the blade shaft 5 to move to the extreme positions of the end parts of each structure when moving in the radial long-strip-shaped through holes 61 and the circular arc grooves 32, the two ends of the long-strip-shaped through holes 61 and the circular arc grooves 32 are preferably provided with circular arc structures matched with the blade shaft 5, and the circular arc structures can also provide a certain buffering effect for the blade shaft when moving to the extreme positions, so that the blade shaft cannot rigidly collide with the end parts.
The variable cross-section turbocharger with the variable blade track can enable the nozzle blade to be close to the turbine inlet when the opening is small under the condition that the intermediate opening position is unchanged, and delta r is reduced; and at large opening, the nozzle vanes may be moved away from the turbine inlet, increasing Δr.
As can be seen from simulation analysis of fig. 3, fig. 4, and fig. 5, the variable vane trajectory turbocharger according to the present embodiment has a characteristic of flow rate, a broken line, and a characteristic of efficiency, and a characteristic of variable trajectory and fixed rotation at a 50% opening, when the opening of the nozzle is about 25%, 50%, and 75%, respectively, compared with the characteristic of the turbocharger of the fixed rotation nozzle of the prior art; at 25% and 75% nozzle opening, the flow characteristics are basically consistent, but the turbocharger efficiency of the variable track nozzle is improved by 3-4 percentage points, and the effect is remarkable.
The present utility model is not limited to the specific structure described above, and any variable-section turbocharger having a variable vane locus with substantially the same structure or design concept as the present utility model falls within the scope of the present utility model.
Claims (5)
1. The utility model provides a variable cross-section turbocharger of blade orbit is variable, includes turbine box (1), locates back lid (2) and shift fork dish (3), blade (4) and blade axle (5) in the turbine box, characterized by: a blade seat (6) is further arranged between the rear cover (2) and the shifting fork disc (3), the blade (4) is positioned between the blade seat (6) and the rear cover (2), and a plurality of radial long strip-shaped through holes (61) are uniformly formed in the blade seat (6) around the center; a plurality of locating pins (31) are uniformly arranged on the outer edge of the first surface of the shifting fork disc (3), a rocker arm mechanism capable of rotating around the locating pins is movably sleeved on the locating pins (31), the rocker arm mechanism is formed by sequentially rotating and connecting a plurality of connecting rods, a plurality of circular arc grooves (32) penetrating through the shifting fork disc are uniformly arranged on the inner edge of the shifting fork disc (3), the central axes of the circular arc grooves (32) intersect at the center of the shifting fork disc (3), the circular arc grooves (32) are in one-to-one correspondence with radial strip-shaped through holes (61), and a blade shaft (5) sequentially penetrates through the radial strip-shaped through holes (61) and the circular arc grooves (32) and is fixedly connected with the other end of the rocker arm mechanism; a driving piece (7) for driving the shifting fork disc to rotate is connected to the shifting fork disc (3);
the rocker arm mechanism is connected by two connecting rods;
the rotating connection between the connecting rods of the rocker arm mechanism is that cylindrical pins are arranged at the connection positions of the connecting rods;
the turbine box (1) is provided with a step groove, and a boss (33) matched with the step groove is arranged on the second surface of the shifting fork disc (3) so as to facilitate the shifting fork disc to rotate along the step groove;
the upper surface of the blade seat (6) close to the shifting fork disc boss (33) is provided with a unilateral right-angle groove (62), and the groove bottom of the right-angle groove (62) is higher than the lower surface of the shifting fork disc boss (33); the blade seat is provided with a distance pin (8) penetrating through the blade seat (6) at the right-angle groove (62), and the other end of the distance pin (8) is fixed on the rear cover (2).
2. The variable-section turbocharger with variable vane trajectories according to claim 1, characterized in that: the right angle groove (62) is internally provided with a supporting wheel (9).
3. The variable-section turbocharger with variable vane trajectories according to claim 1, characterized in that: both ends of the strip-shaped through hole (61) are arc structures matched with the blade shaft (5).
4. The variable-section turbocharger with variable vane trajectories according to claim 1, characterized in that: both ends of the arc groove (32) are arc structures matched with the blade shaft (5).
5. The variable-section turbocharger with variable vane trajectories according to claim 1, characterized in that: the blade shaft (5) is fixedly connected with the other end of the rocker arm mechanism in a welding or riveting mode.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810972308.0A CN109026177B (en) | 2018-08-24 | 2018-08-24 | Variable-section turbocharger with variable vane track |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810972308.0A CN109026177B (en) | 2018-08-24 | 2018-08-24 | Variable-section turbocharger with variable vane track |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109026177A CN109026177A (en) | 2018-12-18 |
| CN109026177B true CN109026177B (en) | 2023-09-22 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810972308.0A Active CN109026177B (en) | 2018-08-24 | 2018-08-24 | Variable-section turbocharger with variable vane track |
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Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111456843B (en) * | 2020-04-27 | 2024-06-14 | 湖南天雁机械有限责任公司 | Variable cross-section turbocharger |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004084545A (en) * | 2002-08-27 | 2004-03-18 | Komatsu Ltd | Variable turbo supercharger |
| JP2007056791A (en) * | 2005-08-25 | 2007-03-08 | Mitsubishi Heavy Ind Ltd | Variable displacement exhaust turbosupercharger and manufacturing method for variable nozzle mechanism constituent member |
| CN2916154Y (en) * | 2006-05-23 | 2007-06-27 | 湖南天雁机械有限责任公司 | Rotary-vane type variable-cross-section turbocharger |
| CN202810965U (en) * | 2012-09-20 | 2013-03-20 | 江西省萍乡市三善机电有限公司 | Sundries prevention and jamming-prevention nozzle ring with variable section |
| CN204511532U (en) * | 2015-01-27 | 2015-07-29 | 长城汽车股份有限公司 | Nozzle ring capable of changing cross sections, turbosupercharger and motor |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2009102546A1 (en) * | 2008-02-12 | 2009-08-20 | Honeywell International Inc. | Process for calibrating a variable-nozzle assembly of a turbochanger and a variable-nozzle assembly facilitating such process |
| CN102297016B (en) * | 2011-08-15 | 2012-12-12 | 无锡凯迪增压器配件有限公司 | Turbocharger for double-vane nozzle systems |
-
2018
- 2018-08-24 CN CN201810972308.0A patent/CN109026177B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004084545A (en) * | 2002-08-27 | 2004-03-18 | Komatsu Ltd | Variable turbo supercharger |
| JP2007056791A (en) * | 2005-08-25 | 2007-03-08 | Mitsubishi Heavy Ind Ltd | Variable displacement exhaust turbosupercharger and manufacturing method for variable nozzle mechanism constituent member |
| CN2916154Y (en) * | 2006-05-23 | 2007-06-27 | 湖南天雁机械有限责任公司 | Rotary-vane type variable-cross-section turbocharger |
| CN202810965U (en) * | 2012-09-20 | 2013-03-20 | 江西省萍乡市三善机电有限公司 | Sundries prevention and jamming-prevention nozzle ring with variable section |
| CN204511532U (en) * | 2015-01-27 | 2015-07-29 | 长城汽车股份有限公司 | Nozzle ring capable of changing cross sections, turbosupercharger and motor |
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| CN109026177A (en) | 2018-12-18 |
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