CN104895667B - A kind of variable cross section exhaust gas bypass turbine for meeting EGR circulation needs - Google Patents

Abstract

The present invention discloses a kind of variable cross section exhaust gas bypass turbine for meeting EGR circulation needs, including turbine case and power turbine, turbine case is provided with the air inlet inner flow passage and air inlet outer flow passage that water conservancy diversion engine exhaust to power turbine sentences the rotation of driving power turbine, turbine case is additionally provided with without power turbine and discharges the exhaust gas bypass pipeline of waste gas, and the exhaust gas bypass valve of control exhaust gas bypass pipeline break-make；When the air inflow that waste gas enters turbine exceedes predetermined value, exhaust gas bypass valve is opened so that portion can be discharged by exhaust gas bypass pipeline.When engine is in high-speed working condition, exhaust gas bypass valve can be opened, so that portion can discharge through exhaust gas bypass pipeline, avoids booster from exceeding the speed limit.Then air inlet outer flow passage in order to avoid booster hypervelocity during high speed without being arranged to large area, and when going to middling speed operating mode by low speed, running on the lower load and opening control valve, the relatively small area official post of inside and outside runner obtains expansion-loss and is reduced.

Description

A kind of variable cross section exhaust gas bypass turbine for meeting EGR circulation needs

Technical field

The present invention relates to technical field of engines, by more particularly to a kind of variable cross section waste gas for meeting EGR circulation needs Logical turbine.

Background technology

Increasingly strict with Abgasgesetz, more and more on the engine, EGR full name are Exhaust to EGR for application Gas Recirculation, Chinese are translated into waste gas recycling, are that the sub-fraction that engine is produced to waste gas sends cylinder ginseng back to again With burning, effect is to reduce NOx discharge capacity.

NOx is a kind of great gas of harm to the human body, is mainly generated under conditions of high-temperature oxygen-enriched, ignition temperature and Oxygen concentration is higher, and the duration is longer, and NOx product is also more.In engine working process, if in good time, in appropriate amount Portion is introduced back into cylinder, because the Main Ingredients and Appearance CO2 specific heat capacities in waste gas are larger, so waste gas can produce burning Partial heat absorb and take cylinder out of, and have certain diluting effect to air inlet, therefore reduce the highest of engine combustion Temperature and oxygen content, so as to reduce the generation of NOx compounds.

On turbocharged and intercooled diesel engine, the major way for realizing waste gas recycling is that the waste gas before turbine is introduced into charge air cooler Afterwards, referred to as high pressure exhaust gas recycles, and in order to ensure the EGR rate of different operating modes, best mode is to use variable cross section turbine Booster, by the changes of section of booster come adjust PT before turbine with it is cold after PK pressure difference, drive EGR valve.

It is at present to increase swivel nozzle blade in turbine interior using most variable-area turbochargers, by changing Become the aperture of nozzle vane to change the circulation passage of turbine, control is more convenient.But due to the waste gas tool of engine discharge Have the exhaust high temperature of 700 degrees centigrades, and have the trend further lifted, exhaust high temperature to nozzle vane, transmission mechanism, Nozzle ring support plate and the control system of outside have a strict requirements, and the impurity in the high-temp waste gas of engine discharge is to complexity Moving component cause reliability hidden danger.

Moreover, price factor of such product due to costliness, is only applied to high-end engine supercharging field, the type is variable Section turbocharger limits marketing in terms of cost and reliability two.In addition to above-mentioned principal element, there is also one A little other technologies problems：

Problem 1, when the flow if reduced, nozzle vane aperture need to be turned down, turbine inflow circumferential speed increases, and turbine is changed into rushing Dynamic formula impeller, it is unfavorable for making full use of for exhaust energy, turbine efficiency is relatively low, and causes engine exhaust back pressure too high.

Problem 2, during vanelets aperture, the increase of turbine inflow flow path, increased along journey flow losses；Nozzle vane distance Too far, air-flow losses by mixture rises turbine.

Problem 3, blade both ends must leave gap, and in order to which blade rotates, but this gap can cause air loss, reduce Turbine efficiency.

Another is increased using the double-layer channel variable cross section turbine that more variable cross section application is Kang Yue science and technology research and development Depressor, by the structure design to conventional turbine shell, combined using the inside and outside double-deck inlet channel, form different through-flow sections Face, effective segmentation utilize the exhaust energy of engine, it is possible to achieve the institute of variable-area turbine is functional, and need not set The Spiralism type Pneumatic adjusting mechanism for adjusting of complexity is put, cost substantially reduces, reliability greatly promotes, and will be following research side To.

The structural principle of such product low pressure, is adjusted as shown in figure 1, when engine operates in low speed, underload Section valve 5 is closed, and turbine case 1 only has air inlet inner flow passage 3 to work, and air-flow flows into along inner flow passage flow direction 4, and driving turbine is done Work(.

As shown in Fig. 2 when boost pressure reaches to a certain degree, control actuator 7 promotes valve selling sheet component 6, valve pin Piece component 6 drives control valve 5 to open, and air inlet inner flow passage 3 works simultaneously with air inlet outer flow passage 2, and air-flow flows along inner flow passage Direction 4 and outer flow passage flow direction 8 flow into, driving turbine acting.But this structure reality with examination and application process in, It is found that many problems.

It is as follows：

First, during high engine speeds, the exhausted air quantity of discharge is larger, in order to ensure high speed performance, turbine pressure when avoiding high speed Power is excessive and exceeds the speed limit, and double-layer channel area is larger, but in the area distributions of double-layer channel, if inner flow passage area distributions compared with Greatly, then the low-speed performance and EGR rate of engine are influenceed, if inner flow passage distribution is smaller, inside and outside pipes' analysis product moment is very big, then adjusts When saving the opening of valve 5, the expansion-loss of moment is excessive, and the middling speed of engine, middle load section are more difficult to control.

2nd, the middling speed in engine, middle load section, Fig. 1, the simple valve mechanism shown in 2 can not accurate controlling streams Amount and pressure, and the control deviation of flow, pressure can not only influence matching performance, can more influence the control of EGR rate, cause to start Machine discharge is exceeded.

3rd, the distribution of inside and outside runner can produce multiple vortex tongues, and gas flowing is easy to influence each other, and causes turbine efficiency Reduce；

4th, the turbine structure provided with inside and outside dual channel is complicated, and turbine is again cast member, therefore conformity of production is difficult Control, and the casting deviation of dual channel is big, and the matching performance of turbine is had a great influence.

The content of the invention

To solve above-mentioned technical problem one, the present invention provides a kind of variable cross section exhaust gas bypass for meeting EGR circulation needs Turbine, the turbine can reduce the expansion-loss of moment when control valve is opened again on the premise of EGR rate is met.

The variable cross section exhaust gas bypass turbine provided by the invention for meeting EGR circulation needs, including turbine case and power Turbine, the turbine case are provided with water conservancy diversion engine exhaust to the power turbine and sentence the air inlet for driving the power turbine rotation Inner flow passage and air inlet outer flow passage,

The turbine case is additionally provided with without the power turbine and discharges the exhaust gas bypass pipeline of waste gas, and control institute State the exhaust gas bypass valve of exhaust gas bypass pipeline break-make；It is described when the air inflow that waste gas enters the turbine exceedes predetermined value Exhaust gas bypass valve is opened so that portion can be discharged by the exhaust gas bypass pipeline.

Optionally, in addition to the adjustable control valve of aperture, for adjusting the air inflow of the air inlet outer flow passage；And

The control valve is configured to the exhaust gas by-pass valve door linkage：The control valve is opened into predetermined angular When, drive the exhaust gas bypass valve to open, now, air inflow reaches the predetermined value.

Optionally, the control valve is puts valve in rotatable, and during rotation, waste gas can enter through the both sides of valve body Enter.

Optionally, the control valve and the exhaust gas bypass valve, alternative one have in control valve rotation direction On, the regulation face of axial height change, another one has the linkage portion being engaged with the regulation face, so as to the regulating valve Door can drive the exhaust gas bypass valve to move axially and open along the control valve when rotating.

Optionally, the control valve can be axially contact along the control valve with the exhaust gas bypass valve；And also Including drive division, the drive division includes the end cap for being installed on the turbine case, the one of control valve described in the end cap card lid End face is to drive the control valve to rotate；

The end cap and the control valve, alternative one have in control valve rotation direction, axial height change Regulation face, another one has the linkage portion that is engaged with the regulation face, being capable of band when being rotated so as to the control valve The exhaust gas bypass valve is moved to move axially and open along the control valve.

Optionally, the axial height in the regulation face is around the center of rotation spiral of the control valve, the linkage Portion is the adjusting rod being engaged with the regulation face.

Optionally, the regulation face has along the gentle raised convex portion of the control valve rotation direction, correspondingly in institute Recess is formed on the regulation face of stating；The linkage portion is axial projection, described when the axial projection rotates relative to the regulation face Axial projection can slip over the recess, the convex portion successively.

Optionally, the control valve be provided with concomitant rotation cam, the exhaust gas bypass valve be provided with can with it is described The adjusting rod that cam edge is engaged.

Optionally, in addition to spring, it is described when the linkage power of the control valve and the exhaust gas bypass valve cancels Spring controls the exhaust gas bypass valve to be reset to closed mode.

Optionally, in addition to valve seat, it offers valve seat inner flow passage interface, valve seat outflow pipeline joint, valve seat Exhaust gas bypass entrance, the outlet of valve seat exhaust gas bypass；The control valve and the exhaust gas bypass valve are all provided with the valve Seat；

The valve seat is located between the blast pipe and the inlet end of the turbine case.

Optionally, the exhaust gas bypass valve is directly mounted at the turbine case, and the control valve is plugged in the whirlpool In hub, directly to adjust the air inflow for entering the air inlet outer flow passage.

Optionally, the turbine is provided with corresponding to air inlet outer flow passage, air inlet inner flow passage described in two groups of six cylinder engine And exhaust gas bypass pipeline, the control valve include two valve bodies to connect, after inserting the turbine case, two institutes State the air inflow of two air inlet outer flow passages of valve body difference while corresponding control.

Optionally,

Also include being located at the power turbine air inlet endface position and stator support plate annular in shape；

The stator support plate along its it is circumferentially-spaced be disposed with some first flow-guiding channels and the second flow-guiding channel, described One flow-guiding channel and second flow-guiding channel have predetermined angle, so that the waste gas of air inlet inner flow passage outflow can be through institute State the first flow-guiding channel and be guided to the power turbine, the waste gas of the air inlet outer flow passage outflow can lead to through second water conservancy diversion Road is guided to the power turbine.

Optionally, the anchor ring of the stator support plate is circumferentially with some stators for being raised in the anchor ring, the stator The guiding gutter for penetrating the stator is provided with, to form fluting stator；

Passage between the adjacent fluting stator forms first flow-guiding channel, and the return guide trough is into described second Flow-guiding channel.

Optionally, the anchor ring of the stator support plate is provided with and is raised in the anchor ring and spaced long stator and short-range missile Leaf, according to counterclockwise, the long stator to the passage between the short-range missile leaf forms second flow-guiding channel, described short Stator to the passage between the long stator forms first flow-guiding channel.

Optionally, the arrangement angle B of the long stator is 68 °~80 °, the arrangement angle A of the short-range missile leaf, is met：B-A =0 °~5 °.

Turbine provided by the invention is provided with the exhaust gas bypass pipeline that waste gas is discharged without power turbine, now, also The exhaust gas bypass valve of control exhaust gas bypass pipeline break-make is set.Also, the air inflow for entering the turbine when waste gas exceedes During predetermined value, exhaust gas bypass valve is opened so that portion can be discharged by the exhaust gas bypass pipeline.Therefore, when starting When machine is in high-speed working condition, exhaust gas bypass valve can be opened, so that portion can discharge through exhaust gas bypass pipeline, avoids increasing Depressor exceeds the speed limit.Then air inlet outer flow passage in order to avoid booster hypervelocity during high speed without being arranged to large area, it can be provided compared with Small area with ensure middling speed, the turbine drives performance of middle load and circulation；Moreover, in being gone to by low speed, running on the lower load Fast operating mode and when opening control valve, the relatively small area official post of inside and outside runner obtains expansion-loss and is reduced.

The present invention provides a kind of variable cross section exhaust gas bypass turbine for meeting EGR circulation needs, including turbine case, described Air inlet inner flow passage and air inlet outer flow passage are provided with turbine case, non-all-round knot is respectively adopted in air inlet inner flow passage and air inlet outer flow passage Structure, air inlet inner flow passage undertake the air inlet of 0 ° of power turbine~(150~230) °, air inlet outer flow passage undertake (150~230) °~ 360 ° of air inlet；Exhaust gas bypass pipeline is additionally provided with the turbine case, the exhaust gas bypass pipeline in air inlet outer flow passage, air inlet with flowing Road be arranged in parallel, but without power turbine.

It is further optimization of the present invention to such scheme below：

The turbine also includes power turbine, valve seat, blast pipe and its control annex, the turbine case, valve seat, row Tracheae is sealed connected together.

Further optimization：The control valve of adjustable air inlet outer flow passage charge flow rate is installed in the valve seat.

Further optimization：Control valve is arranged in valve seat by control valve axle sleeve, wherein one end of control valve It is connected with control accessory drive.

Further optimization：The other end of control valve is provided with regulation face, and regulation face is spiral-shaped structure, its axial height around Pivot Point Center helically rises.

Further optimization：

The exhaust gas bypass valve of action, exhaust gas bypass can be engaged with control valve by being provided with the exhaust gas bypass pipeline Valve is arranged in valve seat by exhaust gas by-pass valve axle sleeve, and exhaust gas bypass valve is provided with bullet with exhaust gas by-pass valve shaft room Spring, exhaust gas bypass valve are provided with the adjusting rod that action is engaged with regulation face close to the side of control valve.

During action, control annex drives control valve rotation, while adjusting air inlet outer flow passage air inflow, control valve Regulation face promotes adjusting rod, and exhaust gas bypass valve is opened, and compression spring, and now, bypass exhaust is discharged from exhaust gas bypass pipeline, When control valve return, exhaust gas bypass valve return, waste gas under spring force effect no longer bypass.

Further optimization：Position in the turbine case close to power turbine is provided with stator support plate, stator support plate On be provided with several fluting stator, several fluting stators it is evenly distributed in a ring.

Fluting stator centre position is provided with guiding gutter, and the arrangement angle for stator of slotting is 68 °~80 °, two grooves of guiding gutter While carrying out rotation acquisition around the center of stator support plate by line of cut, the most narrow place of groove width is controlled by 3mm.

The fluting stator uses gas-solid combining nozzle form, during low engine speed underload, turbine inlet inner flow passage Work, now the flow inlet angle of air inlet inner flow passage is obtained by formula tan (α)=2 π b/ (A/r), and wherein b is turbine inlet width, It is definite value, flow inlet angle is determined by the A/r of air inlet inner flow passage,

The stator angle of air inlet inner flow passage is designed by air inlet inner flow passage flow inlet angle, it is ensured that two angles are basically identical, gas Enter stator along air inlet inner flow passage, then enter power turbine along stator, centre does not have corner loss, pneumatic efficiency height.

As engine speed is gradually lifted, gas flow increases, and air inlet outer flow passage can join with the opening of control valve With air inlet, outer flow passage flow inlet angle is also determined by the A/r of air inlet outer flow passage, and the water conservancy diversion angle of the v-groove presses in gas outer flow passage flow inlet angle and set Meter, it is ensured that two angles are basically identical, and gas enters guiding gutter along air inlet outer flow passage, then enters turbine along guiding gutter, avoids producing Shock loss and loss of turning round when installing complete stator (without guiding gutter), not only increase efficiency, have even more widened flow. Moreover, with the quickening of air velocity, radial velocity component rises faster, the presence of guiding gutter, widens the flow of high regime It is more obvious.

In real work, when engine is in low speed, underload, control valve is closed, and air inlet is along blast pipe, valve seat Gas access, valve seat inner flow passage interface, turbine case inner flow passage entrance, air inlet inner flow passage, fluting stator flow into turbine, drive whirlpool Wheel acting, now, air-flow flow to turbine along two fluting stator intermediate regions, driving turbine acting, now only air inlet inner flow passage Work, section is smaller, and also only enters along stator angular flux when flowing through stator, in air flow collection, can improve pressure, lifting before whirlpool EGR rate.

When engine speed, load gradually rise, control valve starts to open, and fraction flows through control valve, edge Valve seat outflow pipeline joint, turbine case outer flow passage entrance, air inlet outer flow passage, fluting stator flow into turbine, to adapt to gradually increase Traffic demand, in this process, by adjusting the aperture of control valve, pressure before whirlpool can be adjusted, it is determined that suitable EGR rate.

During control valve is adjusted, after control valve goes to certain angle, it can be applied by regulation face to adjusting rod Add thrust, adjusting rod drives exhaust gas bypass valve compression spring, opens waste gate passage, and waste gas bypasses out along tail pipe exhaust Mouth, the outlet of valve seat exhaust gas bypass entrance, valve seat exhaust gas bypass, turbine case exhaust gas bypass entrance, turbine case exhaust gas bypass go out Mouth outflow, a part of exhaust energy of draining, it is ensured that pressure will not be excessive before booster whirlpool when high engine speeds, high load capacity.Moreover, With the increase of air inflow, air inlet can flow into along the guiding gutter on fluting stator, avoid the Airflow obstruction of high regime.

Another prioritization scheme：Fluting stator includes long stator and short-range missile leaf, and the length of long stator is more than the length of short-range missile leaf Degree, long stator and short-range missile interlobar septum are set.

The leading edge of the trailing edge of small stator and long stator is spaced apart in a circumferential direction.It is easy to air-flow in engine height Flowed into during fast operating mode from this, flow can be widened, reduce blocking, realization is functionally similar to stator of slotting.

The arrangement angle of long stator is 68 °~80 °, the arrangement angle B of the long stator and arrangement angle A of short-range missile leaf 33 angle Spending difference is：B-A=0 °~5 °.

The present invention uses gas-solid combining nozzle, with reference to the advantages of both flow-passage-changeable and swivel nozzle blade, solves him Existing above mentioned problem, form the variable cross section solution of an innovation.Moreover, fluting stator, length in the present invention Guide vane structure, compared to the total length guide vane structure for having had application, flow inlet angle can be changed, widen high speed range of flow, take into account hair The turbine performance of the high low speed of motivation, with fixed stator, realize the flow inlet angle adjustment that swivel nozzle blade could be realized, whirlpool Turbine efficiency is obviously improved, and the presence of stator, reduces airflow reflux, is not only increased turbine efficiency, is more made air current flow It is smooth, the flow perturbation at aditus laryngis is avoided, rate of fuel consumption realizes being greatly lowered on whole piece matched line.

Brief description of the drawings

Accompanying drawing 1 is the principle of double-layer channel variable-area turbocharger valve-closed state in background of invention Figure；

Accompanying drawing 2 is the principle of double-layer channel variable-area turbocharger valve opening state in background of invention Figure；

Accompanying drawing 3 is the overall installation schematic diagram of the embodiment of the present invention 1, and this illustrates turbine and is connected with blast pipe；

Accompanying drawing 4 is the structural representation of turbine in the embodiment of the present invention 1, and the figure mainly shows turbine end air inlet end face position Put and internal motivation turbine；

Accompanying drawing 5 is the turbine case structural representation in the embodiment of the present invention 1；

Accompanying drawing 6 is the exhaust pipe structure schematic diagram in the embodiment of the present invention 1；

Accompanying drawing 7 is valve regulated structural representation in the embodiment of the present invention 1, and this illustrates control actuator and valve seat peace Assembling is closed；

Accompanying drawing 8 is valve seat structural representation in the embodiment of the present invention 1；

Accompanying drawing 9 is that valve seat splits structural representation in the embodiment of the present invention 1；

Accompanying drawing 10 is control valve structural representation in the embodiment of the present invention 1, and this illustrates control valve and exhaust gas bypass The cooperation of valve；

Accompanying drawing 11 is control valve and end cap arrangement schematic diagram in the embodiment of the present invention 2；

Accompanying drawing 12 is end cap structure chart in the embodiment of the present invention 2；

Accompanying drawing 13 is control valve structure chart in the embodiment of the present invention 2；

It is control valve in the embodiment of the present invention 2, end cap, the schematic diagram of exhaust gas bypass valve cooperation that Figure 14, which is,；

Accompanying drawing 15 is that exhaust gas bypass valve assembly is matched somebody with somebody with the control valve with cam type regulation face in the embodiment of the present invention 3 The structural representation of conjunction；

Accompanying drawing 16 is the arrangement schematic diagram that exhaust gas bypass valve assembly is installed on turbine in the embodiment of the present invention 3；

Accompanying drawing 17 is the control valve and peace that exhaust gas bypass valve assembly coordinates screw type regulation face in the embodiment of the present invention 3 Schematic diagram loaded on turbine；

Accompanying drawing 18 is the cooperation schematic diagram of exhaust gas bypass valve assembly and control valve in Figure 17；

Accompanying drawing 19 is the axial section of exhaust gas bypass valve assembly in Figure 18；

Accompanying drawing 20 is the profile that exhaust gas bypass valve assembly and control valve are plugged in turbine case in Figure 18；

Accompanying drawing 21 is turbine arrangement schematic diagram in the embodiment of the present invention 4；

Accompanying drawing 22 is control valve and bypath valve structural representation in the embodiment of the present invention 4；

Accompanying drawing 23 is the structural representation of fluting stator in the embodiment of the present invention 1；

Accompanying drawing 24 is turbine case A, r schematic diagram；

Accompanying drawing 25 is not add stator gas flow schematic diagram in the embodiment of the present invention 1；

Accompanying drawing 26 is in the embodiment of the present invention 1 plus stator gas flow schematic diagram；

Accompanying drawing 27 is efficiency comparative's figure, wherein, A lines are turbine efficiency line of the present invention, and B lines are the turbine before not improving Engine efficiency line；

Accompanying drawing 28 is turbine and oil consumption contrast curve during engine cooperation；

Accompanying drawing 29 is long and short guide vane structure schematic diagram in the embodiment of the present invention 5；

Accompanying drawing 30 is long and short stator turbine and fluting stator turbine, the efficiency of existing general exhaust gas bypass turbine Compare curve map.

In figure：1- turbine cases；2- air inlet outer flow passages；3- air inlet inner flow passages；4- inner flow passages flow direction；5- control valves； 6- valve selling sheet components；7- controls actuator；8- outer flow passages flow direction；9- turbine case exhaust gas bypass entrances；Outside 10- turbine cases Flow channel entry point；11- turbine case inner flow passage entrances；12- fluting stators；13- turbine cases exhaust gas bypass exports；14- blast pipes；15- Valve seat；16- tail pipe exhaust Bypass outlets；17- blast pipe gas vents；18- valve seat inner flow passage interfaces；19- valve seats Outflow pipeline joint；20- valve seats exhaust gas bypass exports；21- exhaust gas by-pass valve axle sleeves；22- control valve axle sleeves；23- valve seats Gas access；24- valve seat exhaust gas bypass entrances；25- adjusts face；26- exhaust gas bypass valves；27- springs；28- adjusting rods； 29- guiding gutters；30- stator support plates；31- power turbines；The long stators of 32-；33- short-range missile leaves；34- trailing edges；35- leading edges；36- is cut Secant；37- bypath valve assemblies；38- upper shells；39- upper-lower casing sealing gaskets；40- bypath valve assembly sealing gaskets；Under 41- Housing；41a- assemblies exhaust gas bypass exports；42- bypath valve support shafts；43- guide sleeves；44th, bolt；45- screws；46th, hold Lid；47- coordinates regulation face；47a- axial projections；48- exhaust gas bypass Valve controlling actuators.

Embodiment

In order that those skilled in the art more fully understands technical scheme, it is below in conjunction with the accompanying drawings and specific real Applying example, the present invention is described in further detail.

Embodiment 1, as shown in Fig. 3,4,5, a kind of variable cross section exhaust gas bypass turbine for meeting EGR circulation needs, bag Include turbine case 1, power turbine 31, valve seat 15, blast pipe 14 and its control annex, valve seat 15 and be located at blast pipe 14 and turbine Between shell 1.In order to ensure effectively to work, the turbine case 1, valve seat 15, blast pipe 14 are sealed connected together.

Air inlet inner flow passage 3 and air inlet outer flow passage 2, the waste gas that the exhaust pipe of engine 14 is discharged are provided with the turbine case 1 Air inlet inner flow passage 3 and air inlet outer flow passage 2 can be entered.In the present embodiment, air inlet inner flow passage 3 and air inlet outer flow passage 2 are respectively adopted Non- all-round structure, as shown in figure 5, air inlet inner flow passage 3 undertakes the air inlet of 0 ° of power turbine~(150~230) °, air inlet outer flow passage 2 Undertake the air inlet of (150~230) °~360 °.Sunykatuib analysis and practice have shown that, the distribution of this kind of angle is set, under each operating mode Efficiency optimization.

The end face area (i.e. the air inlet end face of turbine case 1) being connected on the turbine case 1 with valve seat 15 be provided with respectively with Turbine case outer flow passage entrance 10 that air inlet outer flow passage 2 connects with air inlet inner flow passage 3, turbine case inner flow passage entrance 11, blast pipe 14 The waste gas of discharge can flow into from two entrances, and flow into power turbine 31 from air inlet outer flow passage 2, air inlet inner flow passage 3 respectively, with driving Power turbine 31 rotates, so as to drive the generator terminal action of calming the anger of turbocharger, to implement plenum.

Exhaust gas bypass pipeline is additionally provided with the turbine case 1, the exhaust gas bypass pipeline in air inlet outer flow passage 2, air inlet with flowing Road 3 is set up in parallel, but without power turbine 31.I.e. portion can flow to exhaust gas bypass pipeline, but can be expelled to outside, and The rotation of driving power turbine 31 is not played.

Now, the end face area being connected on the turbine case 1 with valve seat 15 is additionally provided with and exhaust gas bypass pipeline connection Turbine case exhaust gas bypass entrance 9, the exhaust end inner hole wall of the turbine case 1 are provided with the turbine case with exhaust gas bypass pipeline connection Exhaust gas bypass outlet 13.

Valve seat 15 is provided with valve seat inner flow passage interface 18, valve seat outflow pipeline joint 19, the outlet of valve seat exhaust gas bypass 20, connected respectively with turbine case inner flow passage entrance 11, turbine case outer flow passage entrance 10, turbine case exhaust gas bypass entrance 9；Valve seat 15 are additionally provided with valve seat gas access 23 and valve seat exhaust gas bypass entrance 24.In Fig. 7,8, valve seat inner flow passage interface 18, valve Gate seat outflow pipeline joint 19, valve seat exhaust gas bypass outlet 20 are located at the top of valve seat 15, valve seat gas access 23 and valve Seat exhaust gas bypass entrance 24 is located at bottom.

Correspondingly, as shown in fig. 6, the blast pipe 14 be provided with by valve seat 15 and turbine case outer flow passage entrance 10 and The blast pipe gas vent 17 and connected by valve seat 15 and turbine case exhaust gas bypass entrance 9 that turbine case inner flow passage entrance 11 connects Logical tail pipe exhaust Bypass outlet 16.

The waste gas part that blast pipe 14 is discharged is flowed out by blast pipe gas vent 17, and whirlpool is flowed into by valve seat 15 Power turbine 31 is entered back into after being allocated in hub outer flow passage entrance 10 and turbine case inner flow passage entrance 11.

Another part bypass exhaust flows out from tail pipe exhaust Bypass outlet 16, is flowed into and linked together by valve seat 15 Turbine case exhaust gas bypass entrance 9, from turbine case exhaust gas bypass outlet 13 outflow, without power turbine 31, be expelled directly out whirlpool Hub 1.

As shown in Fig. 7,8,9,10, valve seat inner flow passage interface 18, valve seat outer flow passage are provided with the valve seat 15 Interface 19 and valve seat exhaust gas bypass outlet 20, the both ends of valve seat inner flow passage interface 18 respectively with turbine case inner flow passage entrance 11 Connected with blast pipe gas vent 17, valve seat outflow pipeline joint 19 both ends respectively with turbine case outer flow passage entrance 10 and exhaust Pipe gas vent 17 connects；

Valve seat exhaust gas bypass outlet 20 and valve seat exhaust gas bypass entrance 24 respectively with turbine case exhaust gas bypass entrance 9 and Tail pipe exhaust Bypass outlet 16 connects.

In the present embodiment, the regulating valve of the adjustable charge flow rate of air inlet outer flow passage 2 is also equipped with the valve seat 15 Door 5；

Specifically, control valve 5 is arranged in valve seat 15 by control valve axle sleeve 22, and wherein the one of control valve 5 End is connected with valve selling sheet component 6, is connected by valve selling sheet component 6 with control accessory drive.

Control annex includes the control actuator 7 being connected with valve selling sheet component 6；Control actuator 7 and valve selling sheet group Part 6 is arranged on the outside of turbine case 1.

Valve is put during the control valve 5 preferably use is rotatable, as shown in Figure 10, control valve 5 can be around central shaft Line rotates.In Fig. 9, passage that the door body of control valve 5 outflows valve seat between pipeline joint 19 and valve seat gas access 23 All block, in valve selling sheet component 6 when being rotated by, the inwall of its both sides and above-mentioned passage is formed to be opened control valve 5 Mouthful, then allow waste gas to pass through.

Compared to the deflation valve mechanism shown in background technology, valve mechanism is put in this kind, when rotarily opening, it is opened Proportional between degree and the anglec of rotation, air inflow and admission pressure can be realized and be precisely controlled, so as to realize and start The matched well of machine, and improve and EGR rate is precisely controlled, engine is met discharge standard.

The turbine provided in above-described embodiment is provided with discharges the exhaust gas bypass pipeline of waste gas without power turbine 31, Now, the exhaust gas bypass valve 26 of control exhaust gas bypass pipeline break-make is also set up.Also, when waste gas enters entering for the turbine When tolerance exceedes predetermined value, exhaust gas bypass valve is opened so that portion can be discharged by the exhaust gas bypass pipeline.Cause This, when engine is in high-speed working condition, can open exhaust gas bypass valve 26, so that portion can be through exhaust gas bypass pipeline Discharge, avoids booster from exceeding the speed limit.Then air inlet outer flow passage 2 need not be arranged to large area in order to avoid booster hypervelocity during high speed, It can be arranged to compared with small area to ensure that middling speed, the turbine drives performance of middle load and EGR are circulated；Moreover, by low speed, low When load condition goes to middling speed operating mode and opens control valve 5, the relatively small area official post of inside and outside runner obtains expansion-loss and subtracted It is small.

Further, exhaust gas bypass valve 26 and control valve 25 can link and be configured to：Control valve 5 is opened into pre- When determining angle, the exhaust gas bypass valve 26 is driven to open, now, air inflow reaches the predetermined value.

Specific linked manner can be as follows：

As shown in figure 9, one end of control valve 5 is installed on valve seat 15 by control valve axle sleeve 22, control valve 5 The other end is provided with regulation face 25, and regulation face 25 is spiral-shaped structure, and its axial height helically rises around Pivot Point Center.

The exhaust gas bypass valve 26 of action, waste gas can be engaged with control valve 5 by being provided with the exhaust gas bypass pipeline Bypath valve 26 is arranged in valve seat 15 by exhaust gas by-pass valve axle sleeve 21, exhaust gas bypass valve 26 and exhaust gas by-pass valve axle sleeve Spring 27 is installed, exhaust gas bypass valve 26 is provided with close to one end of control valve 5 and is engaged action with regulation face 25 between 21 Adjusting rod 28.As shown in figure 9, exhaust gas bypass valve 26 and the diameter parallel of control valve 5 set, adjusting rod 28 is towards regulation Face 25, and contact cooperation.

During action, the control actuator 7 promotes valve selling sheet component 6, and valve selling sheet component 6 drives control valve 5 to revolve Turn, while adjusting air inlet 2 air inflow of outer flow passage, when the anglec of rotation reaches certain value, adjusting rod 28 can be along regulation face 25 The hand of spiral moves, then the regulation face 25 of control valve 5 can promote adjusting rod 28 to move axially, and exhaust gas bypass valve 26 is opened, And compression spring 27, now, bypass exhaust flows into from valve seat exhaust gas bypass entrance 24, from the stream of valve seat exhaust gas bypass outlet 20 Flowed out to turbine case exhaust gas bypass entrance 9, and from turbine case exhaust gas bypass outlet 13, when 5 return of control valve, exhaust gas bypass Valve 26 return, waste gas under the effect of the elastic force of spring 27 no longer bypass.

An embodiment 2 is also provided below, it is substantially the same manner as Example 1, but employ different linked manners, control valve 5 structures also slightly change (will refer to later), please continue to refer to Figure 11-14.

In the embodiment, one end that control valve 5 is connected with valve selling sheet component 6 is provided with the regulation of axial height change Face 25.Now, in addition to the end Ka Gai of control valve 5 end cap 46 coordinated, end cap 46 are securable to the housing of turbine case 1 On, end cap 46 is provided with the structure that regulation face 25 corresponding thereto coordinates, and valve selling sheet component 6 is located at the outside of end cap 46, and can drive Dynamic control valve 5 rotates.

Specifically, end cap 46 is provided with the cooperation coordinated with regulation face 25 and adjusts face 47 in this embodiment, coordinates regulation face 47 With axial projection 47a；Regulation face 25 is provided with the recess set along the rotation direction, correspondingly forms convex portion, recess is relative Gently transit to convex portion.As shown in Figure 11,14, when valve selling sheet component 6, which rotates driving control valve 5, to be rotated, face is adjusted 25 relative engagements regulation face 46 rotates, and when axial projection 47a slips over recess and when contacting convex portion, is rotated further, then axial projection 47a slowly jacks up regulation face 25, and control valve 5 is correspondingly axially moveable.

Therefore be designed as control valve 5 can be axially contact along control valve with exhaust gas bypass valve 26, then control valve 5 exists When coordinating axial movement under the driving of regulation face 46, also exhaust gas bypass valve 26 is driven to move axially simultaneously, to open by waste gas Port valve door 26.

Linkage set-up mode in above-mentioned two embodiment, it is the regulation face that axial height change is formed on a part 25, the linkage portion (such as adjusting rod 28, the axial projection for coordinating regulation face 47) of matched contact is set then at another part, So as to be linear motion by convert rotational motion, coordinated signals are realized.Understand, in above-described embodiment, adjust face 25 and with its The linkage portion set-up mode matched somebody with somebody is not limited to above two, such as, regulation face 25 can be located at exhaust gas bypass valve 26, and adjust Bar 28 is located at control valve 5, and certainly, adjusting rod 28 can avoid regulation face 25 from interfering waste gas circulation located at exhaust gas bypass valve 26； Regulation face 25 can be located at end cap, and coordinate regulation face 46 to be located at control valve 5.

The engaging matching of above-mentioned end cap and control valve 5 is set, and also make it that the stability of whole link gear is preferable.According to This, as shown in Figure 12,13, axial projection, recess are set to two, and along the center line symmetrical setting of corresponding component end face, then After cooperation, stability is higher, is not susceptible to offset.

The present invention also provides a kind of embodiment 3, and as shown in figure 15, the embodiment is roughly the same with embodiment 1,2, but uses The different modes that is linked, the structure of exhaust gas bypass valve 26 and control valve 5 are also slightly changed, hereafter will table successively State.

One end connecting valve selling sheet component 6 of control valve 5, the other end are provided with the regulation face 25 of cam-type, exhaust gas by-pass valve Door 26 is provided with the adjusting rod 28 that can be engaged with cam edge.Then when control valve 5 rotates, adjusting rod 8 is along by waste gas Port valve door 26 moves axially, so as to open valve.Herein, the regulation face of cam-type 25 should be designed as, and turn to predetermined angular When, the ability of adjusting rod 28 contacts with cam edge and opens movement by top, just to be opened when meeting that foregoing air inflow reaches to a certain degree Open exhaust gas bypass valve 26.

In above-described embodiment, exhaust gas bypass valve 26 and control valve 5 realize coordinated signals, then need to only set control valve 5 drive division is compact-sized, simple without separately setting the part of control exhaust gas bypass valve 26；Moreover, exhaust gas by-pass valve Door 26 is changed by the aperture of control valve 5 and controlled, then the keying control of exhaust gas bypass valve 25 can meet actual air inflow Change, compared to relatively individually control, it is clear that it is more accurate to control.

It should be noted that in above-described embodiment, valve seat 15 is set with installation and adjustment valve 5, exhaust gas bypass valve 26 Deng part, consequently facilitating the installation of each part, and realize that turbine case 1 connects with the controllable of blast pipe 14.The present invention also provides another A kind of valve set-up mode, and structure is compacter, as shown in figs. 15 to 20.

In the embodiment, provided with exhaust gas bypass valve assembly 37, it is provided separately with control valve 5, exhaust gas bypass valve 37 Assembly is directly mounted at turbine case 1, and control valve 5 is directly mounted in turbine case 1, as shown in figure 20, the door body of control valve 5 It is inserted directly into air inlet outer flow passage 2, the periphery of door body can coordinate with the inner wall sealing of air inlet outer flow passage 2, when door body rotates, shape Into opening to turn on waste gas.In figure, control valve 5 runs through the air inlet installation end of turbine case 1, and one end connection exhaust gas bypass valve is total Into 37, other end connection drives the valve selling sheet component 6 that it is rotated.

Now, the air inlet installation end face of turbine case 1 directly can then connect with blast pipe 14, and correspondingly, blast pipe 14 is corresponding Ground set out respectively with air inlet inner flow passage 3,2 corresponding exhaust outlet of air inlet outer flow passage.

Because linked manner is different, the installation requirement of valve is also different.Comparable Figure 16,17 understandings, the regulation of screw type Face 25, the regulation face 25 of axial projection type, exhaust gas bypass valve 26 and control valve 5 are axially parallel set, and are arranged to convex During regulation face 25 of wheel-type, then exhaust gas bypass valve 26 and control valve 5 are by setting at an angle, and Figure 15,16, the two is several It is vertically arranged.

As shown in Figure 18,19, the bypath valve assembly 37 specifically includes exhaust gas bypass valve 26, upper shell 38, lower house 41, upper shell 38 is connected with lower house 41 and forms valve pocket, and the side wall of lower house 41 offers assembly exhaust gas bypass outlet 41a. Exhaust gas bypass valve 26 can be supported connection by bypath valve support shaft 42, and bypath valve support shaft 42 is placed in valve pocket, and with The end of upper shell 38 is provided with spring 27, to provide reset force.The end of lower house 41 is provided with valve port, when exhaust gas bypass valve 26 During unlatching, waste gas enters assembly exhaust gas bypass outlet 41a through valve port.

In Figure 19, the end face of exhaust gas bypass valve 26 protrudes to form adjusting rod 28, i.e. adjusting rod 28 is integrally formed at waste gas Bypath valve 26, it is easy to process, coordinated signals are also more reliable.

Guide sleeve 43 can also be set in the valve pocket of exhaust gas bypass valve assembly 37, and bypath valve support shaft 42 is led through this To set 43, when exhaust gas bypass valve 26 moves axially, bypath valve support shaft 42 is slided along guide sleeve 43, in order to avoid exhaust gas by-pass valve The skew axial movement of door 26, influences exhaust gas bypass.In Figure 19, bypath valve support shaft 42 has bigger diameter end, with support spring 27.

The turbine that above example provides is applicable not only to four cylinder engine, can be applicable to six cylinder engine.Figure 4-10 structure corresponds to four cylinders, needs two groups of air inlet inner flow passages 3 of setting, air inlet outer flow passage 2, exhaust gas bypass pipe during six cylinders Road, as shown in Figure 16,17, the air inlet installation end face of turbine case 1 is correspondingly provided with two turbine case exhaust gas bypass entrances 9, turbines Shell outer flow passage entrance 10, turbine case inner flow passage entrance 11.At this point it is possible to two groups of above-mentioned valves are set.

One kind is also provided herein and is directed to six cylinder engine, structure is more compact, small volume, and controls more simple, accurate Valve mechanism.

As shown in Figure 13,18,20, control valve 5 includes two valve bodies to connect, after inserting turbine case 1, two Valve body corresponds to the air inflow of two outer flow passages 2 of control respectively.The control valve 5 still with an exhaust gas bypass valve 26 Dynamic installation, i.e., add a valve door body, you can suitable for six cylinder engine, equivalent to one valve on original control valve 5 Control the air inflow of two runners, it is easy to accomplish be precisely controlled.

The mode of a variety of control valve 5 and exhaust gas bypass valve 26 linkages is provided in above-described embodiment, it will be understood that single Solely control exhaust gas bypass valve 26 and feasible, the embodiment 4 as shown in Figure 21,22.With the air inlet referred in background technology Outer flow passage vent valve is similar, or exhaust gas bypass valve 26 is equipped with corresponding exhaust gas bypass Valve controlling actuator 48, then According to corresponding air inlet signal, the keying of exhaust gas bypass valve 26 can be controlled.Exhaust gas bypass Valve controlling actuator 48 and control The operation principle of actuator 7 is identical, and as shown in figure 22, the rod end of exhaust gas bypass Valve controlling actuator 48 can be stretched under pneumatic pressure It is long, the rotation of selling sheet component is driven, and then drive exhaust gas bypass valve 26 to rotate, to turn off or on valve port.

It should be noted that in above-described embodiment, when control valve 5 and exhaust gas bypass valve 26 link, when linkage power is removed During pin, by setting spring 27 so that exhaust gas bypass valve 26 can be reset to original state.Spring 27 combines above-mentioned a variety of regulations The linked manner that face 25 coordinates, simply and reliably realizes the unlatching of exhaust gas bypass valve 26.It is appreciated that work as by by waste gas When logical valve control actuator 48 controls the keying of exhaust gas bypass valve 26, then resetting means need not be set.In fact, except having carried The linkage scheme of exhaust gas bypass valve 26 arrived, there is the linkage that other schemes can realize exhaust gas bypass valve 26 and control valve 5, Without setting return structure.For example the end of control valve 5 is provided with gear, exhaust gas bypass valve 26 is provided with rack, or adjusts Section valve 5 is provided with nut, and exhaust gas bypass valve 26 is provided with screw rod, and certainly, above-mentioned set-up mode is relatively simple, is not easy to interfere Valve port.

The present invention is also improved the intake method of driving power turbine 31.

As shown in Fig. 4,23, non-blade nozzle is provided with close to the position of power power turbine 31 in the turbine case 1, to incite somebody to action The waste gas that air inlet inner flow passage 3 and air inlet outer flow passage 2 are discharged imported into the blade of power turbine 31, and the present embodiment is close to without foliar spray The position of mouth is provided with fluting stator 12, and the position in the turbine case 1 close to power turbine 31 is provided with stator support plate 30, Several fluting stators 12 are provided with stator support plate 30, ground air inlet is more uniformly distributed to realize, several fluting stators 12 are in Annular is evenly distributed.

The centre position of fluting stator 12 is provided with guiding gutter 29.It is i.e. circumferentially disposed some convex in the anchor ring of stator support plate 30 The stator of anchor ring is arised from, then opens up the guiding gutter 29 through stator, then forms fluting stator.The arrangement angle of fluting stator 12 (as shown in figure 23, the angle is the tangent line of fluting stator 12 axis, fluting stator 12 close to the center of stator support plate 30 to B Tip and the line of centres of stator support plate 30, the angle of the two) can be 68 °~80 °, two trough rims of guiding gutter 29 can be by line of cut 36 (fluting stator 12 is close to the tip at the center of stator support plate 30 and the center line lines of stator support plate 30) surround stator support plate 30 center carries out rotation acquisition, and the most narrow place of groove width is controlled by 3mm.

The fluting stator 12 uses gas-solid combining nozzle form, that is, combines the function of gas flowing and solid nozzle, During low engine speed underload, turbine inlet inner flow passage 3 works, skilled person will appreciate that, now air inlet inner flow passage 3 Flow inlet angle is obtained by formula tan (α)=2 π b/ (A/r), and wherein b is turbine inlet width, is definite value, flow inlet angle is then by air inlet The A/r decisions of runner 3, wherein, A is the sectional area of turbine case 1 zero, and R is distance of the zero section barycenter to the axle center of turbine case 1, is such as schemed Shown in 24, Figure 24 is turbine case A, r schematic diagram.

Stator angle (angle between two fluting stators 12) is designed by the flow inlet angle of air inlet inner flow passage 3, it is ensured that two corners Spend it is basically identical, then gas along air inlet inner flow passage 3 enter fluting stator 12, then along fluting stator 12 enter power turbine 31, in Between there is no a corner loss, pneumatic efficiency is high.

As engine speed is gradually lifted, gas flow increases, and air inlet outer flow passage 2 can be with the opening of control valve 5 Air inlet is participated in, the flow inlet angle of air inlet outer flow passage 2 is also determined that the angle of guiding gutter 29 presses air inlet outer flow passage 2 by the A/r of air inlet outer flow passage 2 Flow inlet angle is designed, it is ensured that and two angles are basically identical, and gas enters guiding gutter 29 along air inlet outer flow passage 2, then along guiding gutter 29 Into power turbine 31, avoid producing shock loss when installing complete stator (without guiding gutter 29) and loss of turning round, not only Efficiency is improved, has even more widened flow.Moreover, with the quickening of air velocity, air-flow radial velocity component rises faster, led The presence of chute 29, make high regime flow widen it is more obvious.

Have gas flow schematic diagram in Figure 23, in low engine speed underload, air-flow only along N to (angle α, i.e., Flow inlet angle) enter power turbine 31, when engine speed is gradually lifted, air-flow can be along M (angle β, i.e. flow inlet angle), N two Direction merges into H and worked to power turbine 31, and δ is the airflow direction excursion for flowing into power turbine 31 in figure.

This illustrates exhaust flow path exemplified by sentencing embodiment when setting valve seat 15.

In real work, when engine is in low speed, underload, control valve 5 is closed, and air inlet is along blast pipe 14, valve Gate seat gas access 23, valve seat inner flow passage interface 18, turbine case inner flow passage entrance 11, air inlet inner flow passage 3, adjacent notch stator Passage between 12 flows into power turbine 31, and driving power turbine 31 does work.

Now, air-flow flows to power turbine 31 along two fluting stator 12 intermediate regions, and driving power turbine 31 does work, only Air inlet inner flow passage 3 works, and section is smaller, and flow through fluting stator 12 when also only enter along stator angular flux, i.e. in Figure 20 N to, In air flow collection, pressure, lifting EGR rate before whirlpool can be improved.

When engine speed, load gradually rise, control valve 5 starts to open, and fraction flows through control valve 5, Power turbine 31 is flowed into along valve seat outflow pipeline joint 19, turbine case outer flow passage entrance 10, air inlet outer flow passage 2, fluting stator 12, To adapt to the traffic demand gradually increased, in this process, by adjusting the aperture of control valve 5, pressure before whirlpool can be adjusted, really Fixed suitable EGR rate.

During control valve 5 is adjusted, control valve 5 (generally corresponds to high engine speeds after going to certain angle Section), thrust can be applied to adjusting rod 28 by adjusting face 25, adjusting rod 28 drives the compression spring 27 of exhaust gas bypass valve 26, beaten Open exhaust gas bypass pipeline, waste gas is along tail pipe exhaust Bypass outlet 16, valve seat exhaust gas bypass entrance 24, valve seat exhaust gas bypass Outlet 20, turbine case exhaust gas bypass entrance 9, the outflow of turbine case exhaust gas bypass outlet 13, a part of exhaust energy of draining, it is ensured that hair Pressure will not be excessive before booster whirlpool when motivation high speed, high load capacity.

Moreover, with the increase of air inflow, air inlet can flow into along the guiding gutter 29 on fluting stator 12, i.e. in Figure 23 M to, M avoids the Airflow obstruction of high regime to, N to air inlet simultaneously.

As shown in Figure 25,26, the presence of stator, reduce airflow reflux, not only increase turbine efficiency, more make air-flow Flow smooth, avoid the flow perturbation at aditus laryngis, ensure turbine efficiency.

In addition, the pressure ratio of turbine, flow are larger to its performance impact, and to flow its decisive action it is through-flow section Face, prior art control passage section by the runner design of turbine case 1, but as stated in the Background Art, the life of cast turbine engine Production uniformity is difficult to control, and correspondingly flow is difficult to control.Guide vane structure is provided with the present embodiment, then can be through-flow by wicket gate control Area, and guide vane structure can Precision Machining formed, flow area can obtain accurate control, so as to not by turbine case 1 itself add The influence of work precision.

After stator is set so that turbine, engine obtain obvious performance boost, as follows：

1st, turbine efficiency is obviously improved, and efficiency comparative's figure is as shown in figure 27, and the thicker black line A in top is imitated for the present invention Rate line, the thinner black line B in lower section are the turbine efficiency line before not improving.

2nd, it is as shown in figure 28 with engine cooperation oil consumption correlation curve, using the turbocharger of the present invention, oil consumption Rate realizes being greatly lowered on whole piece matched line.

Embodiment 5, on the basis of above-described embodiment, the present invention also provides another stator and sets form, as shown in figure 29, Stator includes long stator 32 and short-range missile leaf 33, and the length of long stator 32 is more than the length of short-range missile leaf 33, long stator 32 and short-range missile leaf 33 are arranged at intervals.

The size of long stator 32 and short-range missile leaf 33 is determined according to flow analysis, but the trailing edge 34 of short-range missile leaf 33 and long stator 32 Leading edge 35 to have a segment distance in a circumferential direction, be easy to air-flow in high engine speeds operating mode from this inflow, can widen Flow, reduce blocking, the fluting stator 12 for being functionally similar to previous embodiment of realization.I.e. long stator 32 is according to certain angle edge The circumferential array of stator support plate 30, short-range missile leaf 33 arrange according to another angle, then according to counter clockwise direction, long stator 32 and short-range missile Passage between leaf 33 forms the water conservancy diversion runner turned on air inlet inner flow passage 3, the passage shape between short-range missile leaf 33 and long stator 32 Into the water conservancy diversion runner turned on air inlet outer flow passage 2.Specific work process can refer to above-mentioned fluting stator 12 and understand.

The arrangement angle B of long stator 32 may be designed as 68 °~80 °, the arrangement angle B of long stator 32 and the row of short-range missile leaf 33 The differential seat angle of row angle A is：B-A=0 °~5 °.

Wherein, arrangement angle B is, the tangent line of the long axis of stator 32, long stator 32 are close to the center of stator support plate 30 Tip and the line of centres of stator support plate 30, the angle of the two；Arrangement angle A is tangent line, the short-range missile of the axis of short-range missile leaf 31 Leaf 31 is close to the tip at the center of stator support plate 30 and the line of centres of stator support plate 30, the angle of the two.

The turbine efficiency of this kind of stator set-up mode is more excellent, and efficiency comparative's figure is as shown in figure 30：

The most thin black line A in top is that the most thick black C lines in length stator turbine efficiency line, lower section are by general waste gas Logical turbine efficiency line, middle black line B are fluting stator turbine efficiency line.By upper table as can be seen that setting length to lead Leaf 32, the turbine efficiency of short-range missile leaf 33 are even higher than the fluting structure of stator 12.

It can be seen that from the above description, stator 12 of either slotting, or long stator 32, short-range missile leaf 33 are equipped with, It is that there is the first flow-guiding channel of predetermined angle, the second flow-guiding channel (i.e. the two not parallel setting, the angle in order to form two kinds Value is relevant with the flow inlet angle of air inlet inner flow passage 3, air inlet outer flow passage 2), so that the waste gas that air inlet inner flow passage 3 flows out can be through first Flow-guiding channel is guided to the power turbine 31, and the waste gas that air inlet outer flow passage 2 flows out can be through the second flow-guiding channel water conservancy diversion To the power turbine 31.As above, then the passage between adjacent notch stator 12 forms first flow-guiding channel, guiding gutter 29 Form the second flow-guiding channel；According to counterclockwise, long stator 32 to the passage between short-range missile leaf 33 forms the second flow-guiding channel, Short-range missile leaf 33 to the passage between long stator 32 forms the first flow-guiding channel.

As long as into power turbine 31 can be guided the waste gas of air inlet inner flow passage 3 and air inlet outer flow passage 2 respectively, flow model is widened Enclose, you can to produce technique effect as described above, it is clear that the generation type of two kinds of runners is not limited to above-mentioned fluting stator 12 and long stator 32, short-range missile leaf 33, certainly, the structure of above-described embodiment is easy to process, and does not hinder air-flow, water conservancy diversion effect Fruit is best.In addition, water conservancy diversion support plate 30 sets up separately with turbine case 31, and water conservancy diversion support plate 30 can take finishing, and precision is easy to Ensure, so as to be further ensured that the distribution of air-flow, it is ensured that turbine efficiency.

Invention is described in detail according to national patent method for we now, for those skilled in the art The improvement or replacement of specific embodiment disclosed herein can be identified.These modifications are within the spirit and scope of the present invention.

Claims (22)

1. a kind of variable cross section exhaust gas bypass turbine for meeting EGR circulation needs, including turbine case (1) and power turbine (31), the turbine case (1) sentences the driving power turbine provided with water conservancy diversion engine exhaust to the power turbine (31) (31) the air inlet inner flow passage (3) and air inlet outer flow passage (2) of rotation, it is characterised in that

The turbine case (1) is additionally provided with without the power turbine (31) and discharges the exhaust gas bypass pipeline of waste gas, and control Make the exhaust gas bypass valve (26) of the exhaust gas bypass pipeline break-make；The air inflow that waste gas enters the turbine exceedes predetermined value When, the exhaust gas bypass valve (26) is opened so that portion can be discharged by the exhaust gas bypass pipeline；

Also include the adjustable control valve of aperture (5), for adjusting the air inflow of the air inlet outer flow passage (2)；And

The control valve (5) is configured to the exhaust gas bypass valve (26) linkage：The control valve (5) is opened into predetermined During angle, the exhaust gas bypass valve (26) is driven to open, now, air inflow reaches the predetermined value.

2. variable cross section exhaust gas bypass turbine as claimed in claim 1, it is characterised in that the control valve (5) is can Put valve in rotation, during rotation, waste gas can the both sides through valve body enter.

3. variable cross section exhaust gas bypass turbine as claimed in claim 2, it is characterised in that the control valve (5) and institute Exhaust gas bypass valve (26) is stated, alternative one has in control valve (5) rotation direction, the regulation face of axial height change (25), another one has the linkage portion being engaged with the regulation face (25), can when being rotated so as to the control valve (5) The exhaust gas bypass valve (26) is driven to move axially and open along the control valve (5).

4. variable cross section exhaust gas bypass turbine as claimed in claim 2, it is characterised in that the control valve (5) and institute Stating exhaust gas bypass valve (26) can be axially contact along the control valve (5)；And in addition to drive division, the drive division bag Include the end cap (46) for being installed on the turbine case (1), end cap (46) card covers the end face of the control valve (5) to drive The control valve (5) rotates；

The end cap (46) and the control valve (5), alternative one have in control valve (5) rotation direction, axially high The regulation face (25) of change is spent, another one has the linkage portion being engaged with the regulation face (25), so as to the regulating valve Door (5) can drive the exhaust gas bypass valve (26) to move axially and open along the control valve (5) when rotating.

5. variable cross section exhaust gas bypass turbine as claimed in claim 3, it is characterised in that the axial direction of the regulation face (25) For height around the center of rotation spiral of the control valve (5), the linkage portion is to be engaged with the regulation face (25) Adjusting rod (28).

6. variable cross section exhaust gas bypass turbine as claimed in claim 4, it is characterised in that the axial direction of the regulation face (25) For height around the center of rotation spiral of the control valve (5), the linkage portion is to be engaged with the regulation face (25) Adjusting rod (28).

7. variable cross section exhaust gas bypass turbine as claimed in claim 3, it is characterised in that the regulation face (25) has edge The gentle raised convex portion of control valve (5) rotation direction, correspondingly forms recess on the regulation face (25)；It is described Dynamic portion is axial projection (47a), the axial projection (47a) relative to the regulation face (25) rotate when, the axial projection (47a) can slip over the recess, the convex portion successively.

8. variable cross section exhaust gas bypass turbine as claimed in claim 4, it is characterised in that the regulation face (25) has edge The gentle raised convex portion of control valve (5) rotation direction, correspondingly forms recess on the regulation face (25)；It is described Dynamic portion is axial projection (47a), the axial projection (47a) relative to the regulation face (25) rotate when, the axial projection (47a) can slip over the recess, the convex portion successively.

9. variable cross section exhaust gas bypass turbine as claimed in claim 2, it is characterised in that the control valve (5) is provided with The cam of concomitant rotation, the exhaust gas bypass valve (26) are provided with the adjusting rod that can be engaged with the cam edge (28)。

10. the variable cross section exhaust gas bypass turbine as described in claim any one of 1-9, it is characterised in that also including spring (27), when the linkage power of the control valve (5) and the exhaust gas bypass valve (26) cancels, the spring (27) controls institute State exhaust gas bypass valve (26) and be reset to closed mode.

11. the variable cross section exhaust gas bypass turbine as described in claim any one of 1-9, it is characterised in that also including valve Seat (15), it offers valve seat inner flow passage interface (18), valve seat outflow pipeline joint (19), valve seat exhaust gas bypass entrance (23), valve seat exhaust gas bypass outlet (20)；The control valve (5) and the exhaust gas bypass valve (26) are located at the valve Gate seat (15)；

The valve seat (15) is located between blast pipe (14) and the inlet end of the turbine case (1).

12. the variable cross section exhaust gas bypass turbine as described in claim any one of 1-9, it is characterised in that by the waste gas Port valve door (26) is directly mounted at the turbine case (1), and the control valve (5) is plugged in the turbine case (1), with direct Regulation enters the air inflow of the air inlet outer flow passage (2).

13. variable cross section exhaust gas bypass turbine as claimed in claim 12, it is characterised in that the turbine is provided with corresponding In air inlet outer flow passage (2), air inlet inner flow passage (3) and exhaust gas bypass pipeline, the regulating valve described in two groups of six cylinder engine Door (5) includes two valve bodies connecting, after inserting the turbine case (1), two valve bodies difference while right The air inflow of two air inlet outer flow passages (2) should be controlled.

14. the variable cross section exhaust gas bypass turbine as described in claim any one of 1-9, it is characterised in that

Also include being located at the power turbine (31) air inlet endface position and stator support plate (30) annular in shape；

The stator support plate (30) along its it is circumferentially-spaced be disposed with some first flow-guiding channels and the second flow-guiding channel, described One flow-guiding channel and second flow-guiding channel have predetermined angle, so that the waste gas of the air inlet inner flow passage (3) outflow can The power turbine (31) is guided to through first flow-guiding channel, the waste gas of air inlet outer flow passage (2) outflow can be through institute State the second flow-guiding channel and be guided to the power turbine (31).

15. variable cross section exhaust gas bypass turbine as claimed in claim 14, it is characterised in that the stator support plate (30) Anchor ring be circumferentially with some stators for being raised in the anchor ring, the stator is provided with the guiding gutter (29) for penetrating the stator, To form fluting stator (12)；

Passage between adjacent fluting stator (12) forms first flow-guiding channel, described in the guiding gutter (29) is formed Second flow-guiding channel.

16. variable cross section exhaust gas bypass turbine as claimed in claim 14, it is characterised in that the stator support plate (30) Anchor ring be provided with and be raised in the anchor ring and spaced long stator (32) and short-range missile leaf (33), according to counter clockwise direction, institute The passage stated between long stator (32) to the short-range missile leaf (33) forms second flow-guiding channel, the short-range missile leaf (33) to institute State the passage between long stator (32) and form first flow-guiding channel.

17. variable cross section exhaust gas bypass turbine as claimed in claim 16, it is characterised in that the row of the long stator (32) Row angle B is 68 °~80 °, the arrangement angle A of the short-range missile leaf (33), is met：B-A=0 °~5 °.

18. a kind of variable cross section exhaust gas bypass turbine for meeting EGR circulation needs, including turbine case (1), the turbine case (1) air inlet inner flow passage (3) and air inlet outer flow passage (2) are provided with, air inlet inner flow passage (3) and air inlet outer flow passage (2) are respectively adopted Non- all-round structure, air inlet inner flow passage undertake the air inlet of 0 ° of power turbine~(150~230) °, air inlet outer flow passage undertake (150~ ° 230)~360 ° of air inlet；Exhaust gas bypass pipeline is additionally provided with the turbine case (1), the exhaust gas bypass pipeline outflows with air inlet Road (2), air inlet inner flow passage (3) be arranged in parallel, but without power turbine (31)；

The turbine also includes power turbine (31), valve seat (15), blast pipe (14) and its control annex, the turbine case (1), valve seat (15), blast pipe (14) are sealed connected together；Adjustable air inlet outflow is installed in the valve seat (15) The control valve (5) of road (2) charge flow rate；The other end of control valve (5) is provided with regulation face (25), and regulation face (25) is spiral Type structure, its axial height helically rise around Pivot Point Center.

19. a kind of variable cross section exhaust gas bypass turbine for meeting EGR circulation needs according to claim 18, its feature It is：The exhaust gas bypass valve (26) of action, waste gas can be engaged with control valve (5) by being provided with the exhaust gas bypass pipeline Bypath valve (26) is arranged in valve seat (15) by exhaust gas by-pass valve axle sleeve (21), by exhaust gas bypass valve (26) and waste gas Spring (27) is installed, exhaust gas bypass valve (26) is provided with and adjusted close to the side of control valve (5) between port valve axle sleeve (21) Nodal section (25) is engaged the adjusting rod (28) of action；During action, control annex drives control valve (5) rotation, adjusts outside air inlet While runner (2) air inflow, the regulation face (25) of control valve (5) promotes adjusting rod (28), and exhaust gas bypass valve (26) is beaten Open, and compression spring (27), now, bypass exhaust is discharged from exhaust gas bypass pipeline, when control valve (5) return, by waste gas Port valve door (26) return, waste gas under the effect of spring (27) elastic force no longer bypass.

20. a kind of variable cross section exhaust gas bypass turbine for meeting EGR circulation needs according to claim 18, its feature It is：

Position in the turbine case (1) close to power turbine (31) is provided with stator support plate (30), stator support plate (30) On be provided with several fluting stator (12), several fluting stators (12) it is evenly distributed in a ring；

The fluting stator (12) uses gas-solid combining nozzle form, during low engine speed underload, turbine inlet inner flow passage (3) work, now the flow inlet angle of air inlet inner flow passage (3) is obtained by formula tan (α)=2 π b/ (A/r), and wherein b enters for turbine Mouth width, is definite value, A is the sectional area of turbine case zero, and r is distance of the zero section barycenter to turbine case axle center, and α is flow inlet angle, is entered Air horn determines by the A/r of air inlet inner flow passage (3),

The stator angle of air inlet inner flow passage (3) is designed by air inlet inner flow passage (3) flow inlet angle, it is ensured that two angles are basically identical, gas Body enters stator along air inlet inner flow passage (3), then enters power turbine (31) along stator, and centre does not have corner loss.

21. a kind of variable cross section exhaust gas bypass turbine for meeting EGR circulation needs according to claim 20, its feature It is：

Fluting stator (12) centre position is provided with guiding gutter (29), and the arrangement angle (B) of fluting stator (12) is 68 °~80 °, is led Two trough rims of chute (29) carry out rotation acquisition by line of cut (36) around the center of stator support plate (30), and the most narrow place of groove width is pressed 3mm is controlled.

22. a kind of variable cross section exhaust gas bypass turbine for meeting EGR circulation needs according to claim 20, its feature It is：Fluting stator (12) includes long stator (32) and short-range missile leaf (33), and the length of long stator (32) is more than short-range missile leaf (33) Length, long stator (32) and short-range missile leaf (33) are arranged at intervals；The trailing edge (34) of small stator (33) and the leading edge of long stator (32) (35) it is spaced apart in a circumferential direction.