CN202417695U - Staged flow-adjustable turbine casing - Google Patents
Staged flow-adjustable turbine casing Download PDFInfo
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- CN202417695U CN202417695U CN2012200099136U CN201220009913U CN202417695U CN 202417695 U CN202417695 U CN 202417695U CN 2012200099136 U CN2012200099136 U CN 2012200099136U CN 201220009913 U CN201220009913 U CN 201220009913U CN 202417695 U CN202417695 U CN 202417695U
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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
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Abstract
The utility model discloses a staged flow-adjustable turbine casing. The staged flow-adjustable turbine casing comprises a turbine casing body; a turbine assembly and a waste gas inlet runner are installed in the turbine casing body; a gas inlet communicated with the waste gas inlet runner is arranged on the turbine casing body; an intermediate wall is arrange in the waste gas inlet runner and divides the waste gas inlet runner into an inner runner and an outer runner; a first valve device which can close the outer runner is arranged in the outer runner; and a second valve device which can lead to communication or disconnection between the inner runner and the outer runner is arranged on the intermediate wall. According to the staged flow-adjustable turbine casing, the waste gas energy is made full use of to improve the rotate speed of a turbine rotor and increase gas inflow of an engine at the low-speed working condition, so that the engine performs more work, torsion of the engine at the low speed is increased, the staged flow-adjustable turbine casing can be well matched with the low speed working condition of the engine, and the dynamic property and the transient response property of the engine at the low speed working condition are improved.
Description
Technical field
The utility model relates to a kind of turbine case, relates to a kind of stage adjustable flow turbine case that comprises stage can regulate circulation cross section specifically, can satisfy the supercharging requirement under the Under Different Work Condition of Engine effectively, belongs to the engine booster field.
Background technique
Turbocharging technology improves day by day the requirement of engine performance and discharging along with society and is more and more paid attention to.Supercharging technology is through improving the suction pressure of motor; Increase engine charge density, make motor in identical swept volume, advance more gas, so can correspondingly increase the work cycle fuel delivery; Make motor do more merit; The output power and the moment of torsion of motor increase substantially, and have strengthened engine structure relatively, make the motor of equal-wattage can adopt littler form structure.Turbocharging technology uses turbine to recycle exhaust energy, and through gas compressor engine charge is carried out supercharging basically not under the prerequisite of the effective merit of consumption of engine; And turbo machine has the effect of noise elimination and make the harmful components in the waste gas further react away.So turbosupercharger has improved power character, Economy and the feature of environmental protection of motor.Turbocharging technology has been one of effective technology of reply energy scarcity and maximum discharge laws and regulations requirement.
Traditional conventional turbocharger only has efficient preferably in the design conditions scope, and can not realize efficient coupling with motor in other most of operating modes.Conventional turbine pressurized machine deficiency mainly contains: air inlet deficiency during low speed, and cause engine torque not enough, low speed and sub load are less economical; Transient response property is slow, makes engine start, acceleration performance poor, and it is serious to smolder; Supercharging is excessive during high speed, and is all influential to engine performance, structure and material; Engine power descends serious during high height above sea level.The conventional turbine pressurized machine can not satisfy the requirement of advanced motor.So, see from motor high-performance, high feature of environmental protection angle, require to have better turbocharging technology scheme.
For the turbosupercharger of band exhaust gas by-pass valve, though overcome not enough, the not enough phenomenon of supercharging of the air inlet of low speed operating mode to a certain extent, also when high operating mode through opening the rotating speed that exhaust gas by-pass valve reduces pressurized machine; Avoid supercharging excessive; But under very most of operating mode, exhaust gas by-pass valve formula turbine case is not realized the efficient coupling with motor, especially under high operating mode; Exhaust gas by-pass valve is opened; Exhaust energy is not lost through turbine, does not make full use of the energy of waste gas, makes the power character of motor and Economy bad relatively.If its undue low speed operating mode of looking after, the waste gas that then when high operating mode, pours off from exhaust gas by-pass valve is more, and the exhaust energy utilization ratio is lower.And the high-temp waste gas of the exhaust gas by-pass valve of flowing through is owing to the exhaust piping distance that flows through has reduced; The time that causes waste gas in hot environment, to be detained has lacked; Harmful components in the waste gas that should in high-temperature pipe, react away flow to downstream or are discharged in the atmosphere; And can the flue gas leading in downstream, continue to expand from the high-temp waste gas that exhaust gas by-pass valve runs off, its a big chunk Conversion of energy is the vibrational energy of sound wave, has strengthened the displacement noise of motor.Cause the emission performance of motor also to descend to some extent like this.
In the novel turbocharger, variable-area turbocharger is a developing direction, has developed now multiple variable-area turbocharger form, mainly contains variable nozzle ring pressurized machine, variable throat pressurized machine, ligulate baffle plate pressurized machine etc.Wherein, the variable nozzle ring pressurized machine is one of maximum novel turbocharger of progress.The variable nozzle ring pressurized machine to adapt to the air inlet requirement of the different operating conditionss of motor, is realized the matched well of pressurized machine and each operating mode of motor through the variation of the aperture realization actual internal area of the nozzle blade of adjusting activity.But the variable nozzle ring of variable nozzle ring pressurized machine and transmission thereof and control mechanism are complicated, and part is more, and material and processing request are high, make cost too high, are difficult to form the powerful market competitiveness.And nozzle blade system; Comprising its driving mechanism, is under engine luggine and six, 700 degrees centigrade even higher high temperature condition, to work, and it requires nozzle blade movable; Require the sealing of nozzle blade and nozzle ring again better, formed the contradiction of attending to one thing and lose sight of another; Each parts easy deformation, the damage of under this condition, working, it is big to realize accurately regulating the nozzle blade difficulty, makes that variable nozzle ring pressurized machine reliability and sealing are difficult to guarantee that service life is also shorter.These inherent defects of variable nozzle ring pressurized machine make it not extensive so far universal.
Double flow channel turbine shell-type pressurized machine (DLP) also has very big development, and its cardinal principle is exactly that air inlet state according to turbine case is divided into two with runner, adopts single runner air inlet during the low speed operating mode, adopts the double flow channel air inlet during high-speed working condition.Double flow channel turbine case and the contrast of variable nozzle ring pressurized machine, structure is simple relatively, and component processing requires lower, more is prone to realize that operating life is longer, and is more reliable.But the double flow channel of current double flow channel formula turbine case much all is arranged in juxtaposition, and promptly the arc length of two runners equates, like patent 201010279953.8, make when waste gas flows in runner and runner wall area of contact big, flow losses are bigger.In addition, known double flow channel turbine case mode of operation mostly has only two kinds of patterns now, and promptly low speed operating mode and high-speed working condition like patent 201010279953.8 and patent 201010280157.6, make that the exhaust gas utilization rate is not ideal enough when some middling speed operating mode.At last, the now known double flow channel turbine case structure particularly casting of midfeather requires height, and existing casting technique is difficult for meeting the demands.
Designing the novel turbocharger that cost is relatively low, performance good, reliability is high is the requirement of motor industry, also is the target that each pressurized machine producer is pursued.
The model utility content
The problem that the utility model will solve is in order to reach the above-mentioned defective of existing known double flow channel formula turbine case (DLP) with exhaust gas by-pass valve formula turbine case, variable-nozzle ring type turbine case; Provide a kind of and can improve the engine exhaust energy utilization ratio, the stage adjustable flow turbine case that reliability is high.
In order to address the above problem, the utility model adopts following technological scheme:
A kind of stage adjustable flow turbine case comprises turbine shroud;
Turbine assembly and waste gas air inlet runner are installed in the turbine shroud; Turbine shroud is provided with the suction port that is communicated with the waste gas air inlet runner;
In the waste gas air inlet runner, be provided with midfeather, midfeather is partitioned into inner flow passage and outer flow passage with the waste gas air inlet runner;
Be provided with first valving that can outer flow passage be closed in the said outer flow passage; Said midfeather is provided with second valving that can inner flow passage is communicated with outer flow passage or break off.
Below be the further improvement of the utility model to such scheme:
Said inner flow passage is positioned at the inboard of turbine shroud, and outer flow passage is positioned at the outside of turbine shroud, and the arc flow channel length of outer flow passage is greater than the arc flow channel length of inner flow passage, and the center line of inner flow passage and outer flow passage is all perpendicular to the turbine case axis.
Further improve: first valving comprises first valve that is installed in the outer flow passage;
First valve is connected with first valve hinges near an end of suction port, and first valve hinges is positioned on the outer flow passage outer side surface;
First valve can rotate in the outer flow passage in the airintake direction downstream, drive lower edge of valve hinges away from an end of first valve hinges, i.e. angle with midfeather formation during first valve rotation is always acute angle.
Further improve: the axis of first valve hinges is vertical with the center line of outer flow passage.
Further improve: begin from the position of laying first valve hinges on the said outer flow passage outer side surface; Be provided with a structure shape and the corresponding groove of first valve; First valve when pressing close to the outer flow passage outer side surface with placement, promptly groove is as a limit position of first valve.
Further improve: said first valve hinges is connected with first actuator controller.
Further improve: said first actuator controller comprises first final controlling element that is installed in the turbine shroud outside through actuator bracket; The outside of first final controlling element is provided with the first final controlling element push rod; Be provided with first piston in first final controlling element; The housing seal of the first piston and first final controlling element is slidingly connected, and an end of the said first final controlling element push rod is positioned at first final controlling element and is fixedly connected with first piston, and the other end is in transmission connection through first continuous motion stem and first valve hinges.
Further improve: the outside of part that the said first final controlling element push rod is positioned at the housing of first final controlling element is set with the first final controlling element spring.
Further improve: said first final controlling element is provided with first pore, is connected with for first connecting tube on said first pore, and during installation, this first connecting tube is communicated with corresponding blower outlet.
Further improve: be provided with by-pass port in position on the said midfeather near suction port; Second valving comprises second valve that is installed in the by-pass port place; Second valve can change in the outer flow passage inward turning; Second valve is connected with second valve hinges, and said second valve hinges is installed in the position of by-pass port away from a side of suction port, second valve when rotation angle with midfeather formation be always acute angle.
Further improve: the axis of said second valve hinges is vertical with the center line of outer flow passage.
Further improve: said second valve hinges is connected with second actuator controller.
Further improve: second actuator controller comprises second final controlling element that is installed in the turbine shroud outside;
The outside of second final controlling element is provided with the second final controlling element push rod; Be provided with second piston in second final controlling element; The housing seal of second piston and second final controlling element is slidingly connected; One end of the said second final controlling element push rod is positioned at second final controlling element and is fixedly connected with second piston, and the other end is in transmission connection through second continuous motion stem and second valve hinges.
Further improve: the outside of part that the said second final controlling element push rod is positioned at the housing of second final controlling element is set with the second final controlling element spring.
Further improve: said second final controlling element is provided with second pore, and second pore is communicated with the third connecting pipe, and the other end of third connecting pipe is connected with the two-bit triplet gas solenoid valve, and the working state of second final controlling element is controlled by the two-bit triplet gas solenoid valve;
Said two-bit triplet gas solenoid valve is provided with outlet pore, import pore and bleeder port, and during installation, the outlet pore is communicated with the third connecting pipe; The import pore is through second connecting tube and corresponding blower outlet channel connection; Said two-bit triplet gas solenoid valve is electrically connected with engine electric-controlled unit, and the working state of two-bit triplet gas solenoid valve is controlled by engine electric-controlled unit.
The utility model is realized flexible and changeable mode of operation through the above structure, realizes that each operating mode of corresponding pressurized machine and motor efficiently matees.The embodiment of high, medium and low fast operating mode is following:
During the low engine speed operating mode, described stage adjustable flow turbine case will reduce the runner flow area, increases the flow velocity of waste gas in the turbine shroud.
At this moment, first actuator driven, first valve is fitted the wall of itself and midfeather and outer flow passage, forms enclosed construction, has stoped engine exhaust to get into the downstream of outer flow passage.
Simultaneously, second actuator driven, second valve make itself and midfeather fit and will by-pass port close, inner flow passage and outer flow passage are separated.
Like this, the upstream and downstream of whole outer flow passage does not all have exhaust-gas flow, and engine exhaust only gets into the inner flow passage of turbine shroud from the inner flow passage waste gas inlet of inner flow passage.Because this moment, the flow area of turbine shroud was minimum, made the air inlet of small flow also can in inner flow passage, obtain higher flow velocity.And the layout of midfeather makes full week of turbine intake type right and wrong that outlet nozzle ring sectional area is little, thereby waste gas can flow into turbine with higher kinetic energy on the outlet nozzle ring of turbine shroud; More exhaust energy is passed to turbine; The exhaust energy that has made full use of improves the rotating speed of turbine rotor, improves the air inflow of low engine speed operating mode; Make motor do more merit; Increase the low engine speed moment of torsion, realize the matched well with the low engine speed operating mode, improve the power character and the transient response property of low engine speed operating mode.
During the medium engine speed operating mode, described stage adjustable flow turbine case will suitably increase the runner flow area, strengthens negotiability, guarantees the necessary flow velocity of waste gas in the turbine shroud simultaneously.
At this moment, first actuator driven, first valve makes it separate with midfeather; Simultaneously, the transmission of pressurized machine and control mechanism drive second valve, and it is separated with by-pass port on the midfeather; The rotating tip of second valve is near first valve, and promptly second valve is in another limit position.
The wall of first valve and second valve and outer flow passage forms enclosed construction to outer flow passage, has stoped engine exhaust to get into the downstream canal of outer flow passage.
Inner flow passage and outer flow passage are realized being communicated with through the by-pass port of opening.Like this; The waste gas of motor can get into turbine shroud from the inner flow passage waste gas inlet and the outer flow passage waste gas inlet of turbine shroud; But because the wall of first valve and second valve and outer flow passage forms enclosed construction to outer flow passage; Stoped the waste gas that gets into outer flow passage from the outer flow passage waste gas inlet further to the downstream flow of outer flow passage, and the opening of by-pass port on the midfeather make the waste gas that gets into the outer flow passage upper reaches to collaborate through the waste gas of by-pass port with inner flow passage; The common downstream canal that flows into inner flow passage, and the outer flow passage downstream do not have exhaust-gas flow.
That is to say; During the middling speed operating mode; Said turbine shroud is to realize the expansion of flow area through opening by-pass port on the midfeather, extra increase outer flow passage waste gas inlet air inlet on the basis of inner flow passage waste gas inlet air inlet, and the waste gas air inflow of the extra increase of turbine shroud is limited; This also meets this limited fact of medium engine speed operating mode exhausted air quantity; And this moment, turbine shroud reaches the requirement that increases the waste gas air inflow through inner flow passage waste gas inlet and the air inlet simultaneously of outer flow passage waste gas inlet, can guarantee higher flowing velocity again.
Because first valve and second valve all are always acute angle with the angle that midfeather forms respectively, this just make waste gas from the outer flow passage upper reaches flow field when by-pass port gets into the inner flow passage downstream mild relatively, thereby reduce flow losses.
The logical cross section of outlet nozzle circulation when the outlet nozzle circulation of middling speed operating mode turbine shroud leads to the cross section with the low speed operating mode is the same, and turbine also is non-full admission, but relative low speed operating mode; Middling speed operating mode air inflow is bigger; Waste gas is bigger at the flow velocity at outlet nozzle ring place, and the energy of bringing turbine into is more, and convertible merit is more; Make that the turbine rotor rotating speed is higher, strengthen the boosting capability of gas compressor.Make the pressurized machine that adopts said stage adjustable flow turbine case satisfy the air inlet requirement of medium engine speed operating mode.
During the high engine speeds operating mode; The exhausted air quantity that motor is discharged is big; Exhaust energy is sufficient, if the turbine case cross section of fluid channel is less, the flow velocity of waste gas can be very high in the runner; Can cause that easily the turbine rotor rotating speed surpasses calibration value, cause the gas compressor supercharging excessively with the component of infringement turbosupercharger.
So when the high engine speeds operating mode, the runner flow area of the said stage adjustable flow turbine case of the utility model is increased to maximum.At this moment, first actuator driven, first valve makes it near the groove on the outer flow passage outer side surface, and the upstream and downstream of outer flow passage are communicated with, so that can flow into the downstream canal of outer flow passage smoothly from the waste gas of outer flow passage waste gas inlet entering.
Simultaneously, second actuator driven, second valve make itself and midfeather fit and will by-pass port close, inner flow passage and outer flow passage are separated, make the waste gas of inner flow passage downstream flow from the inner flow passage waste gas inlet.
Like this, the upstream and downstream of whole outer flow passage all has exhaust-gas flow, and engine exhaust gets into the inner flow passage and the outer flow passage of turbine case simultaneously respectively respectively from inner flow passage waste gas inlet and outer flow passage waste gas inlet, and the waste gas that flows in inner flow passage and the outer flow passage is independent of each other.
Because this moment, the flow area of turbine shroud was maximum, make turbine shroud allow the waste gas of big flow to flow into.And; Inner flow passage and outer flow passage all have exhaust-gas flow to make that the turbine air inlet is complete all forms; Thereby there is bigger outlet to supply the waste gas of big flow to pass through at the outlet nozzle ring, can makes the waste gas flow velocity that gets into turbine can be too not high and avoid the turbine rotor hypervelocity like this.
Add the layout of midfeather; Make that the waste gas streamline was parallel with midfeather as far as possible when waste gas flowed in turbine shroud, avoid waste gas to produce bigger lateral flow; Reduce big swirling flow and the flowage friction between the different layers waste gas, so that more exhaust energy is passed to turbine.
The turbine full admission makes air inlet be evenly distributed, and has reduced the disequilibrium of pressurized machine, has improved the efficient of turbine conversion exhaust energy.The waste gas that the turbine full admission also makes all motors discharge all fully expands in turbine case; Avoid exhaust gas by-pass valve formula pressurized machine directly to slattern the shortcoming of part exhaust energy; Also created condition for the further reaction of the harmful components in the waste gas; Reduce the last harmful components of getting rid of outlet pipe, reduce displacement noise, improve the emission performance of motor.The turbine full admission, the exhaust energy of not only having avoided the turbine rotor hypervelocity but also having made full use of realizes adopting the pressurized machine and the matched well of high engine speeds operating mode of said stage adjustable flow turbine case, the power character and the emission performance of raising high engine speeds operating mode.
From above working principle, adopt the pressurized machine of the described stage adjustable flow turbine case of the utility model can satisfy the high, normal, basic air inlet requirement that waits each operating mode of motor, realize efficient coupling with each operating mode of motor.Under each operating mode, compare with known bypass valve formula turbine case, variable-nozzle ring type turbine case and known double flow channel formula turbine case (DLP), the described stage adjustable flow turbine case of the utility model has following advantage:
Relative bypass valve formula turbine case; When the low speed operating mode; Have only inner flow passage that exhaust-gas flow is arranged in the described stage adjustable flow turbine case, through the cooperation of midfeather, its flow characteristic is better than the flow characteristic of bypass valve formula turbine case runner; Because the said stage adjustable flow turbine case of the utility model if with outer flow passage close and midfeather on by-pass port when closing; The pattern that only lets inner flow passage work independently is entirely low speed operating mode design, and the flowing state of bypass valve formula turbine case runner when arranging, will consider that the high-speed working condition bypass valve is opened the time, so can not too look after the low speed operating mode.Like this; Even compare with bypass valve formula turbine case; The efficient of the described stage adjustable flow turbine case of the utility model when the low speed operating mode still takes advantage, and second final controlling element of described stage adjustable flow turbine case is the same with controlling mechanism with the transmission of bypass valve formula pressurized machine.And the described stage adjustable flow turbine case of the utility model all has the design point of penetration in high, normal, basic operating mode, and bypass valve formula turbine case is a point of penetration with the low speed operating mode only, then looks after with simple venting during high speed.Under the similar situation of complex structure degree, the described stage adjustable flow turbine case of the utility model has higher exhaust energy utilization ratio, especially under the high engine speeds working condition.
Relative variable-nozzle ring type turbine case.When the low speed operating mode; Be designed under the identical negotiability situation, the described stage adjustable flow turbine case of the utility model has only inner flow passage that exhaust-gas flow is arranged, thereby makes waste gas when mobile; Still less produce perpendicular to horizontal cyclone that flows to and the phase mutual interference between different laminar flow; It is just littler that the waste gas that flows contacts with the border on the cross section, reduces flow losses, makes exhaust energy be passed to the turbine inlet place more; And, because of having only inner flow passage exhaust-gas flow is arranged, make waste gas flow to the reduced distances of turbine case outlet nozzle ring from the turbine case suction port, mobile waste gas significantly reduces with the area that the turbine case border contacts, and further reduces flow losses and heat transfer loss; In addition, avoided variable-nozzle ring type turbine case excessively change exhaust flow to drawback.When high-speed working condition, the double flow channel of described stage adjustable flow turbine case all has exhaust-gas flow.The existence of midfeather makes mobile being independent of each other in the inside and outside runner, reduces horizontal cyclone and flowage friction, reduces flow losses.Can set different nozzle ring types respectively at the outlet nozzle ring place of inside and outside runner, so that the waste gas in two runners all has the best angle that flows into turbine.At this moment, the turbine that is equipped with said turbine case is full admission, and is the same with variable-nozzle ring type turbine case, and turbine operates steadily, energy conversion efficiency high.Said turbine case has more reasonably exhaust-gas flow flow field when the low speed operating mode, have more high efficiency, and when high-speed working condition, also can slightly have superiority.So, relative variable nozzle ring pressurized machine, the double flow channel structure of said turbine case makes exhaust-gas flow more reasonable, and energy loss is littler in the flow process, has guaranteed that more energy gets into turbine.Structurally more simple, part number is still less, processing request is little, cost is lower, the mass production of being more convenient for, and reliability is higher, service life is longer.
Known relatively double flow channel formula turbine case (DLP); Can find out that the double flow channel formula turbine case described in the patent of being mentioned in the relative background technique of the said turbine case of the utility model has following improvement: when the low speed operating mode; Be arranged in juxtaposition the turbine case (promptly the arc length of two runners equates) of double flow channel; The said turbine case of the utility model adopts inner flow passage air inlet pattern, and waste gas distance of flow in runner is littler, and is littler with the wall area of contact; Less with the wall heat transfer, make energy loss still less.During high-speed working condition, also to be arranged in juxtaposition the turbine case of double flow channel little for waste gas and the total area of contact of runner wall in the said stage adjustable flow turbine case of the utility model.And the said stage adjustable flow turbine case of the utility model also increases middling speed operating mode pattern specially, improved the exhaust energy utilization ratio of middling speed operating mode.In addition, in being arranged in juxtaposition the turbine case of double flow channel, waste gas increases energy loss in the mutual interference of outlet nozzle meeting phase during high-speed working condition; Waste gas departs from best angle easily in the ejection angle of outlet nozzle when the low speed operating mode, makes that the exhaust energy transformation efficiency behind the entering turbine reduces.At last; The now known turbine case that is arranged in juxtaposition double flow channel requires high to casting technique; Intermediate bulkheads curve design between the double flow channel requires high, and intermediate bulkheads is difficult to reach should the little requirement of casting easily again of flow losses, and the midfeather of the said stage adjustable flow turbine case of the utility model directly and the two side walls of turbine case be connected as a single entity; Promptly make things convenient for casting, reduce technological requirement, strengthened the structural strength of turbine case again.
Below in conjunction with accompanying drawing and practical implementation the utility model is further specified.
Description of drawings
Accompanying drawing 1 is a stage adjustable flow turbine case structural representation among the utility model embodiment;
Accompanying drawing 2 is the structural representation of second final controlling element of second control valve among the utility model embodiment;
Accompanying drawing 3 is the spring stress and distortion (N-S) graph of a relation of second final controlling element among the utility model embodiment;
Accompanying drawing 4 is the structural representation of first final controlling element of first control valve among the utility model embodiment;
Accompanying drawing 5 is the spring stress and distortion (N-S) graph of a relation of first final controlling element among the utility model embodiment;
Accompanying drawing 6 is the working principle schematic representation of turbine case low speed operating mode among the utility model embodiment;
Accompanying drawing 7 is the working principle schematic representation of turbine case middling speed operating mode among the utility model embodiment;
Accompanying drawing 8 is the working principle schematic representation of turbine case high-speed working condition among the utility model embodiment.
Among the figure: the 1-turbine shroud; The 2-midfeather; The 3-inner flow passage; 4-turbine assembly; 5-outlet nozzle ring; The 6-outer flow passage; The 7-by-pass port; 8-inner flow passage waste gas inlet; 9-outer flow passage waste gas inlet; 10-first valve hinges; 11-first valve; First connecting tube of 12-; 13-first final controlling element; The 14-actuator bracket; Second connecting tube of 15-; The 16-groove; 17-two-bit triplet gas solenoid valve; The 18-bleeder port; 19-third connecting pipe; 20-second final controlling element; 21-second valve; 22-second valve hinges; The 23-second final controlling element spring; 24-second piston; 25-second pore; 26-second continuous motion stem; The 27-first final controlling element spring; 28 – first pistons; 29-first pore; 30-first continuous motion stem; The 31-second final controlling element push rod; The 32-first final controlling element push rod.
Embodiment
Embodiment, as shown in Figure 1, a kind of stage adjustable flow turbine case; Comprise turbine shroud 1; Turbine assembly 4 and waste gas air inlet runner are installed in the turbine shroud 1, in the waste gas air inlet runner, are provided with midfeather 2, midfeather 2 is partitioned into inner flow passage 3 and outer flow passage 6 with the waste gas air inlet runner; Said turbine shroud 1 is provided with the suction port that is communicated with the waste gas air inlet runner, and this suction port comprises inner flow passage waste gas inlet 8 that is communicated with inner flow passage 3 and the outer flow passage waste gas inlet 9 that is communicated with outer flow passage 6.
During installation, said inner flow passage waste gas inlet 8 is connected with engine exhaust pipe respectively with outer flow passage waste gas inlet 9, and turbine assembly 4 the other ends pass intermediate, connects gas compressor.
Position near turbine assembly 4 in the turbine shroud 1 is provided with outlet nozzle ring 5, and turbine shroud 1 outer wall construction can be used as the installation matrix of the related pneumatic type of the utility model or electric-controlled type transmission and control mechanism.
The plane at the center line place of the median surface of said midfeather 2 and said inner flow passage 3 and outer flow passage 6 is vertical, promptly with the parallel axes of said turbine case.Midfeather 2 curved structures, its radian can be adjusted, and the arc tail end of midfeather 2 is connected and affects the air inlet angle of waste gas entering turbine with outlet nozzle ring 5.
Said inner flow passage 3 is positioned at the inboard of turbine shroud 1; Outer flow passage 6 is positioned at the outside of turbine shroud 1; The arc flow channel length of outer flow passage 6 makes the low speed operating mode promptly have only the distance of exhaust-gas flow when in the inner flow passage 3 exhaust-gas flow being arranged little greater than the arc flow channel length of inner flow passage 3 like this.The center line of inner flow passage 3 and outer flow passage 6 is all perpendicular to the turbine case axis.
Be provided with by-pass port 7 in position on the said midfeather 2 near suction port; By-pass port 7 places are equipped with second valve 21 that can in outer flow passage 6, rotate; Second valve 21 is connected with second valve hinges 22; Said second valve hinges 22 is positioned near the side of by-pass port 7 away from suction port; The angle that forms with midfeather 2 during the rotation of second valve 21 is always acute angle, and off-gas flows can be more swimmingly from outer flow passage 6 upstream canals inflow inner flow passage 3 downstream, minimizing flow resistance when making second valve 21 open like this outer flow passage 6 upstream canals are communicated with inner flow passage 3.The axis of said second valve hinges 22 is vertical with the center line of outer flow passage 6.
Said second valve hinges 22 is connected with second actuator controller.
Second actuator controller comprises second final controlling element 20 that is installed in turbine shroud 1 outside through actuator bracket 14;
As shown in Figure 2; The outside of second final controlling element 20 is provided with the second final controlling element push rod 31; Be provided with second piston 24 in second final controlling element 20; The housing seal of second piston 24 and second final controlling element 20 is slidingly connected, and an end of the said second final controlling element push rod 31 is positioned at second final controlling element 20 and is fixedly connected with second piston 24, and the other end is in transmission connection through second continuous motion stem 26 and second valve hinges 22.
The outside of part that the said second final controlling element push rod 31 is positioned at the housing of second final controlling element 20 is set with the second final controlling element spring 23.
Said second final controlling element 20 is provided with second pore 25; Second pore 25 is communicated with third connecting pipe 19; The other end of third connecting pipe 19 is connected with the working state of two-bit triplet gas solenoid valve 17, the second final controlling element 20 and is controlled by two-bit triplet gas solenoid valve 17;
Said two-bit triplet gas solenoid valve 17 is provided with outlet pore, import pore and bleeder port 18, and during installation, the outlet pore is communicated with third connecting pipe 19; The import pore is through second connecting tube 15 and corresponding blower outlet channel connection; Said two-bit triplet gas solenoid valve 17 is electrically connected with engine electric-controlled unit ECU, and the working state of two-bit triplet gas solenoid valve 17 is controlled by engine electric-controlled unit ECU.
As shown in Figure 1; The outer side surface of said outer flow passage 6 is provided with first valve 11 that can in outer flow passage 6, rotate; When the rotating tip of first valve 11 contacted with midfeather 2, midfeather 2 formed sealing configuration with the wall and first valve 11 of outer flow passage 6, stops the downstream air inlet of said outer flow passage 6.
Said first valve 11 is connected with first valve hinges 10 near an end of suction port; First valve hinges 10 is positioned on outer flow passage 6 outer side surfaces; First valve 11 away from first valve hinges 10 an end valve hinges 10 along in the outer flow passage 6 in airintake direction downstream the rotation; The angle that forms with midfeather 2 during i.e. first valve 11 rotation is always acute angle, feasible like this second valve 21 limit position when leaving midfeather 2 that when first valve 11 contacts with midfeather 2, can be used as.
The axis of first valve hinges 10 is vertical with the center line of outer flow passage.
Begin from the position of laying first valve hinges 10 on the said outer flow passage 6; Be provided with a structure shape and first valve, 11 corresponding grooves 16; Said first valve 11 when pressing close to outer flow passage 6 outer side surfaces with placement, promptly groove 16 is as a limit position of first valve 11.
Said first valve hinges 10 is connected with first actuator controller.
As shown in Figure 4; Said first actuator controller comprises first final controlling element 13 that is installed on the actuator bracket 14; The outside of first final controlling element 13 is provided with in the first final controlling element push rod, 32, the first final controlling element 20 and is provided with first piston 28, and the housing seal of the first piston 28 and first final controlling element 13 is slidingly connected; One end of the said first final controlling element push rod 32 is positioned at first final controlling element 13 and is fixedly connected with first piston 28, and the other end is in transmission connection through first continuous motion stem 30 and first valve hinges 10.
The outside of part that the said first final controlling element push rod 32 is positioned at the housing of first final controlling element 13 is set with the first final controlling element spring 27.
Said first final controlling element 13 is provided with first pore 29, is connected with for first connecting tube 12 on said first pore 29, and during installation, this first connecting tube 12 is communicated with corresponding blower outlet.
The rotating range non-overlapping copies of first valve 11 and second valve 21, mutual noninterference.
Said first valve 11 can be with between two limit positions arbitrarily angled as the working position, the working position of said second valve 21 can only be on two limit positions, promptly said second valve 21 does not have the working position between two limit positions.
Accompanying drawing 5 is the spring stress and distortion (N-S) graph of a relation of first final controlling element, and wherein N is stressed size, and S is the distortion size.
Stressed and the linear or linear approximate relationship of distortion of the first final controlling element spring 27 of said first final controlling element 13, field of load is wider, so that said first valve 11 can be parked on a certain position between the limit position.
Accompanying drawing 3 is the spring stress and distortion (N-S) graph of a relation of second final controlling element, and wherein N is stressed size, and S is the distortion size;
Stressed and the distortion of the second final controlling element spring 23 of second final controlling element 20 is non-linear relation; Field of load is less; When the second final controlling element spring 23 received less power, the second final controlling element push rod 31 and 26 transmissions of second continuous motion stem of warp second final controlling element 20 just can make said second valve 20 conversion between limit position fast.
Make when surpassing certain pressure; The second final controlling element spring 23 rotates rapidly through the second final controlling element push rod 31 and second continuous motion stem 26 drivings, second valve 21 with regard to rapid distortion, has guaranteed that the working position of second valve 21 can only be on the limit position and do not rest on certain position between two limit positions.
When motor is in the low speed operating mode; ECU sends signal makes two-bit triplet gas solenoid valve 17 cut off being connected of import pore and import pore; And import pore and bleeder port 18 are communicated with; The second final controlling element push rod 31 and second continuous motion stem 26 drive second valve 21 by-pass port 7 are closed, and isolate inside and outside runner; Simultaneously, first final controlling element 13 drives first continuous motion stem, 30 first final controlling element push rods 32, drives first valve 11 and fits with midfeather 2.
When motor is in the middling speed operating mode; ECU sends signal and makes the import pore of two-bit triplet gas solenoid valve 17 and being connected of import pore; And import pore and bleeder port 18 are broken off, second continuous motion stem 26 drives second valve 21 and leaves by-pass port 7, is communicated with inside and outside runner; Simultaneously, first final controlling element 13 drives second continuous motion stem 30, drives that first valve 11 separates with midfeather 2 and a certain position between limit position.
When motor is in high-speed working condition; ECU sends signal makes two-bit triplet gas solenoid valve 17 cut off being connected of import pore and import pore; And import pore and bleeder port 18 are communicated with, second continuous motion stem 26 drives second valve 21 by-pass port 7 is closed, and isolates inside and outside runner; Simultaneously, first final controlling element 13 drives first continuous motion stem 30, drives first valve 11 near the groove on the outer flow passage 6 16.
The embodiment of each operating mode of the utility model is following:
Shown in accompanying drawing 6, during the low engine speed operating mode, described stage adjustable flow turbine case will reduce the runner flow area, increases the flow velocity of waste gas in the turbine shroud 1.
At this moment, first final controlling element 13 drives first valve 11, and its wall with midfeather 2 and outer flow passage 6 is fitted, and forms enclosed construction, has stoped the downstream of engine exhaust entering outer flow passage 6.
Simultaneously, second final controlling element 20 drive second valve 21 make itself and midfeather 2 fit and will by-pass port 7 close, inner flow passage 3 and outer flow passage 6 are separated.
Like this, the upstream and downstream of whole outer flow passage 6 does not all have exhaust-gas flow, and engine exhaust only gets into the inner flow passage 3 of turbine shroud 1 from the inner flow passage waste gas inlet 8 of inner flow passage 3.Because this moment, the flow area of turbine shroud 1 was minimum, made the air inlet of small flow also can in inner flow passage 3, obtain higher flow velocity.And the layout of midfeather 2 makes full week of turbine intake type right and wrong that outlet nozzle ring 5 sectional areas are little, thereby waste gas can flow into turbine with higher kinetic energy on the outlet nozzle ring 5 of turbine shroud 1; More exhaust energy is passed to turbine; The exhaust energy that has made full use of improves the rotating speed of turbine rotor, improves the air inflow of low engine speed operating mode; Make motor do more merit; Increase the low engine speed moment of torsion, realize the matched well with the low engine speed operating mode, improve the power character and the transient response property of low engine speed operating mode.
Shown in the accompanying drawing 7, during the medium engine speed operating mode, described stage adjustable flow turbine case will suitably increase the runner flow area, strengthens negotiability, guarantees the necessary flow velocity of waste gas in the turbine shroud 1 simultaneously.
At this moment; First final controlling element 13 drives first valve 11, it is separated, simultaneously with midfeather 2; The transmission of pressurized machine and control mechanism drive second valve 21; It is separated with by-pass port 7 on the midfeather 2, and the rotating tip 13 of second valve 21 is near first valve 11, and promptly second valve 21 is in another limit position.
The wall of first valve 11 and second valve 21 and outer flow passage 6 forms enclosed construction to outer flow passage 6, has stoped engine exhaust to get into the downstream canal of outer flow passage 6.
Inner flow passage 3 is realized being communicated with through the by-pass port of opening 7 with outer flow passage 6.Like this; The waste gas of motor can get into turbine shroud 1 with outer flow passage waste gas inlet 9 from the inner flow passage waste gas inlet 8 of turbine shroud 1; But because the wall of first valve 11 and second valve 21 and outer flow passage 6 forms enclosed construction to outer flow passage 6; Stoped the waste gas that gets into outer flow passages 6 from outer flow passage waste gas inlet 9 further to the downstream flow of outer flow passage 6, and the opening of by-pass port 7 on the midfeather 2 make that the waste gas that gets into outer flow passage 6 upper reaches can be through the waste gas interflow of by-pass port 7 with inner flow passage 3; The common downstream canal that flows into inner flow passage 3, and outer flow passage 6 downstream do not have exhaust-gas flow.
That is to say; During the middling speed operating mode; Said turbine shroud 1 is to realize the expansion of flow areas through opening by-pass port 7 on the midfeather 2, extra increase outer flow passage waste gas inlet 9 air inlets on the basis of inner flow passage waste gas inlet 8 air inlets, and the waste gas air inflow of turbine shroud 1 extra increase is limited; This also meets this limited fact of medium engine speed operating mode exhausted air quantity; And this moment, 9 air inlets simultaneously reach the requirement that increases the waste gas air inflow to turbine shroud 1 with the outer flow passage waste gas inlet through inner flow passage waste gas inlet 8, can guarantee higher flowing velocity again.
Because first valve 11 and second valve 21 all are always acute angle with the angle that midfeather 2 forms respectively, this just make waste gas from outer flow passage 6 upper reaches flow field when by-pass port 7 gets into the inner flow passage downstream mild relatively, thereby the minimizing flow losses.
The logical cross section of the outlet nozzle circulation of outlet nozzle ring 5 flow areas of middling speed operating mode turbine shroud 1 during with the low speed operating mode is the same, and turbine also is non-full admission, but relative low speed operating mode; Middling speed operating mode air inflow is bigger; Waste gas is bigger at the flow velocity at outlet nozzle ring 5 places, and the energy of bringing turbine into is more, and convertible merit is more; Make that the turbine rotor rotating speed is higher, strengthen the boosting capability of gas compressor.Make the pressurized machine that adopts said stage adjustable flow turbine case satisfy the air inlet requirement of medium engine speed operating mode.
Shown in accompanying drawing 8; During the high engine speeds operating mode, the exhausted air quantity that motor is discharged is big, and exhaust energy is sufficient; If the less words of turbine case cross section of fluid channel; The flow velocity of waste gas can be very high in the runner, can cause that easily the turbine rotor rotating speed surpasses calibration value, cause the gas compressor supercharging excessively with the component of infringement turbosupercharger.
So when the high engine speeds operating mode, the stage adjustable flow turbine case of the utility model is increased to maximum with the runner flow area.At this moment, first final controlling element 13 drives first valve 11, makes it near the groove 16 on outer flow passage 6 outer side surfaces, and the upstream and downstream of outer flow passage 6 are communicated with, so that can flow into the downstream canal of outer flow passage 6 smoothly from the waste gas of outer flow passage waste gas inlet 9 entering.
Simultaneously, second final controlling element 20 drive second valve 21 make itself and midfeather 2 fit and will by-pass port 7 close, inner flow passage 3 and outer flow passage 6 are separated, make the waste gas of inner flow passage 3 downstream flow from inner flow passage waste gas inlet 8.
Like this; The upstream and downstream of whole outer flow passage 6 all has exhaust-gas flow; Engine exhaust gets into the inner flow passage 3 and outer flow passage 6 of turbine case simultaneously respectively respectively from inner flow passage waste gas inlet 8 and outer flow passage waste gas inlet 9, inner flow passage 3 is independent of each other with the outer flow passage 6 interior waste gas that flow.
Because this moment, the flow area of turbine shroud 1 was maximum, make turbine shroud 1 allow the waste gas of big flow to flow into.And; Inner flow passage 3 all has exhaust-gas flow to make that the turbine air inlet is complete all forms with outer flow passage 6; Thereby there is bigger outlet to supply the waste gas of big flow to pass through at outlet nozzle ring 5, can makes the waste gas flow velocity that gets into turbine can be too not high and avoid the turbine rotor hypervelocity like this.
Add the layout of midfeather 2; Make that the waste gas streamline was parallel with midfeather 2 as far as possible when waste gas flowed in turbine shroud 1, avoid waste gas to produce bigger lateral flow; Reduce big swirling flow and the flowage friction between the different layers waste gas, so that more exhaust energy is passed to turbine.
The turbine full admission makes air inlet be evenly distributed, and has reduced the disequilibrium of pressurized machine, has improved the efficient of turbine conversion exhaust energy.The waste gas that the turbine full admission also makes all motors discharge all fully expands in turbine case; Avoid exhaust gas by-pass valve formula pressurized machine directly to slattern the shortcoming of part exhaust energy; Also created condition for the further reaction of the harmful components in the waste gas; Reduce the last harmful components of getting rid of outlet pipe, reduce displacement noise, improve the emission performance of motor.The turbine full admission, the exhaust energy of not only having avoided the turbine rotor hypervelocity but also having made full use of realizes adopting the pressurized machine and the matched well of high engine speeds operating mode of said stage adjustable flow turbine case, the power character and the emission performance of raising high engine speeds operating mode.
From above embodiment to each operating mode of motor, said stage adjustable flow turbine case is simple in structure, and control flexibly, and is reliable.Satisfy the high, normal, basic air inlet requirement that waits each operating mode of motor, realize efficient coupling with each operating mode of motor.Adopt the efficient of the pressurized machine of said stage adjustable flow turbine case to compare with the variable nozzle ring pressurized machine and have superiority, and exhaust-gas flow is more reasonable, structure is simpler, part number still less, reliability is higher.Compare with bypass valve formula pressurized machine, the exhaust energy utilization ratio is then higher.
More than be the explanation that we carry out model utility according to the national patent method, the concrete realization of the utility model is not limited to above-mentioned explanation, can discern the improvement or the replacement of specific embodiment disclosed herein for those skilled in the art.These modifications are in spirit of the utility model and scope.
Claims (17)
1. a stage adjustable flow turbine case comprises turbine shroud (1);
Turbine assembly (4) and waste gas air inlet runner are installed in the turbine shroud (1); Turbine shroud (1) is provided with the suction port that is communicated with the waste gas air inlet runner;
In the waste gas air inlet runner, be provided with midfeather (2), midfeather (2) is partitioned into inner flow passage (3) and outer flow passage (6) with the waste gas air inlet runner;
It is characterized in that:
Be provided with first valving that can outer flow passage (6) be closed in the said outer flow passage (6); Said midfeather (2) is provided with second valving that can inner flow passage (3) and outer flow passage (6) are communicated with or break off.
2. a kind of stage adjustable flow turbine case according to claim 1; It is characterized in that: said inner flow passage (3) is positioned at the inboard of turbine shroud (1); Outer flow passage (6) is positioned at the outside of turbine shroud (1); The arc flow channel length of outer flow passage (6) is greater than the arc flow channel length of inner flow passage (3), and the center line of inner flow passage (3) and outer flow passage (6) is all perpendicular to the turbine case axis.
3. a kind of stage adjustable flow turbine case according to claim 1 and 2 is characterized in that: first valving comprises first valve (11) that is installed in the outer flow passage (6);
First valve (11) is connected with first valve hinges (10) near an end of suction port, and first valve hinges (10) is positioned on outer flow passage (6) outer side surface;
First valve (11) can rotation in the outer flow passage (6) in the airintake direction downstream, drive lower edge of valve hinges (10) away from an end of first valve hinges (10).
4. a kind of stage adjustable flow turbine case according to claim 3 is characterized in that: first valve (11) when rotation the angle with midfeather (2) formation be always acute angle.
5. a kind of stage adjustable flow turbine case according to claim 4, it is characterized in that: the axis of first valve hinges (10) is vertical with the center line of outer flow passage.
6. a kind of stage adjustable flow turbine case according to claim 5; It is characterized in that: begin from the position of laying first valve hinges (10) on said outer flow passage (6) outer side surface; Be provided with a structure shape and the corresponding groove of first valve (11) (16); First valve (11) when pressing close to outer flow passage (6) outer side surface with placement, promptly groove (16) is as a limit position of first valve (11).
7. a kind of stage adjustable flow turbine case according to claim 6, it is characterized in that: said first valve hinges (10) is connected with first actuator controller.
8. a kind of stage adjustable flow turbine case according to claim 7; It is characterized in that: said first actuator controller comprises first final controlling element (13) that is installed in turbine shroud (1) outside through actuator bracket (14); The outside of first final controlling element (13) is provided with the first final controlling element push rod (32); Be provided with first piston (28) in first final controlling element (20); First piston (28) is slidingly connected with the housing seal of first final controlling element (13); One end of the said first final controlling element push rod (32) is positioned at first final controlling element (13) and is fixedly connected with first piston (28), and the other end is in transmission connection through first continuous motion stem (30) and first valve hinges (10).
9. a kind of stage adjustable flow turbine case according to claim 8 is characterized in that: the outside of part that the said first final controlling element push rod (32) is positioned at the housing of first final controlling element (13) is set with the first final controlling element spring (27).
10. a kind of stage adjustable flow turbine case according to claim 9; It is characterized in that: said first final controlling element (13) is provided with first pore (29); Be connected with first connecting tube (12) on said first pore (29); During installation, this first connecting tube (12) is communicated with corresponding blower outlet.
11. a kind of stage adjustable flow turbine case according to claim 3 is characterized in that:
Said midfeather (2) upward is provided with by-pass port (7) in the position near suction port; Second valving comprises and is installed in second valve (21) that by-pass port (7) is located; Second valve (21) can rotate in outer flow passage (6); Second valve (21) is connected with second valve hinges (22), and said second valve hinges (22) is installed in the position of by-pass port (7) away from a side of suction port.
12. a kind of stage adjustable flow turbine case according to claim 11 is characterized in that: second valve (21) when rotation the angle with midfeather (2) formation be always acute angle.
13. a kind of stage adjustable flow turbine case according to claim 12, it is characterized in that: the axis of said second valve hinges (22) is vertical with the center line of outer flow passage (6).
14. a kind of stage adjustable flow turbine case according to claim 13, it is characterized in that: said second valve hinges (22) is connected with second actuator controller.
15. a kind of stage adjustable flow turbine case according to claim 14 is characterized in that:
Second actuator controller comprises second final controlling element (20) that is installed in turbine shroud (1) outside;
The outside of second final controlling element (20) is provided with the second final controlling element push rod (31); Be provided with second piston (24) in second final controlling element (20); Second piston (24) is slidingly connected with the housing seal of second final controlling element (20); One end of the said second final controlling element push rod (31) is positioned at second final controlling element (20) and is fixedly connected with second piston (24), and the other end is in transmission connection through second continuous motion stem (26) and second valve hinges (22).
16. a kind of stage adjustable flow turbine case according to claim 15 is characterized in that:
The outside of part that the said second final controlling element push rod (31) is positioned at the housing of second final controlling element (20) is set with the second final controlling element spring (23).
17. a kind of stage adjustable flow turbine case according to claim 16 is characterized in that:
Said second final controlling element (20) is provided with second pore (25); Second pore (25) is communicated with third connecting pipe (19); The other end of third connecting pipe (19) is connected with two-bit triplet gas solenoid valve (17), and the working state of second final controlling element (20) is controlled by two-bit triplet gas solenoid valve (17);
Said two-bit triplet gas solenoid valve (17) is provided with outlet pore, import pore and bleeder port (18), and during installation, the outlet pore is communicated with third connecting pipe (19); The import pore is through second connecting tube (15) and corresponding blower outlet channel connection; Said two-bit triplet gas solenoid valve (17) is electrically connected with engine electric-controlled unit (ECU), and the working state of two-bit triplet gas solenoid valve (17) is controlled by engine electric-controlled unit (ECU).
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| CN2012200099136U CN202417695U (en) | 2012-01-11 | 2012-01-11 | Staged flow-adjustable turbine casing |
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| Application Number | Priority Date | Filing Date | Title |
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| CN2012200099136U CN202417695U (en) | 2012-01-11 | 2012-01-11 | Staged flow-adjustable turbine casing |
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| CN202417695U true CN202417695U (en) | 2012-09-05 |
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN102536433A (en) * | 2012-01-11 | 2012-07-04 | 康跃科技股份有限公司 | Staged flow-adjustable turbine shell |
| CN103161567A (en) * | 2013-02-16 | 2013-06-19 | 李光顺 | Comb-shaped tongue piece shunting variable cross-section turbine pressurizer |
| WO2016134584A1 (en) * | 2015-02-25 | 2016-09-01 | 康跃科技股份有限公司 | Variable geometry wastegate turbine meeting the requirements of egr circulation |
| CN108167066A (en) * | 2017-01-06 | 2018-06-15 | 苏州意驱动汽车科技有限公司 | A kind of turbocharging control method and control system and engine |
| CN108167068A (en) * | 2017-01-06 | 2018-06-15 | 苏州意驱动汽车科技有限公司 | A kind of turbocharger electronic actuators scaling method and system |
| CN110541754A (en) * | 2019-09-24 | 2019-12-06 | 车行天下网络科技股份有限公司 | Variable flow exhaust gas turbocharger |
| CN111608791A (en) * | 2020-04-23 | 2020-09-01 | 无锡凝众科技有限公司 | Three-scroll adjustable turbocharger |
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- 2012-01-11 CN CN2012200099136U patent/CN202417695U/en not_active Expired - Fee Related
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102536433A (en) * | 2012-01-11 | 2012-07-04 | 康跃科技股份有限公司 | Staged flow-adjustable turbine shell |
| WO2013104090A1 (en) * | 2012-01-11 | 2013-07-18 | Wang Hang | Staged variable flow turbine housing |
| CN102536433B (en) * | 2012-01-11 | 2014-05-07 | 康跃科技股份有限公司 | Staged flow-adjustable turbine shell |
| CN103161567A (en) * | 2013-02-16 | 2013-06-19 | 李光顺 | Comb-shaped tongue piece shunting variable cross-section turbine pressurizer |
| CN103161567B (en) * | 2013-02-16 | 2016-05-25 | 李光顺 | Comb shape tongue piece shunting variable section turbocharger |
| WO2016134584A1 (en) * | 2015-02-25 | 2016-09-01 | 康跃科技股份有限公司 | Variable geometry wastegate turbine meeting the requirements of egr circulation |
| US10662870B2 (en) | 2015-02-25 | 2020-05-26 | Kangyue Technology Co., Ltd. | Variable geometry wastegate turbine |
| CN108167066A (en) * | 2017-01-06 | 2018-06-15 | 苏州意驱动汽车科技有限公司 | A kind of turbocharging control method and control system and engine |
| CN108167068A (en) * | 2017-01-06 | 2018-06-15 | 苏州意驱动汽车科技有限公司 | A kind of turbocharger electronic actuators scaling method and system |
| CN110541754A (en) * | 2019-09-24 | 2019-12-06 | 车行天下网络科技股份有限公司 | Variable flow exhaust gas turbocharger |
| CN111608791A (en) * | 2020-04-23 | 2020-09-01 | 无锡凝众科技有限公司 | Three-scroll adjustable turbocharger |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20120905 Termination date: 20160111 |